Energy Conservation Program: Test Procedures for Central Air Conditioners and Heat Pumps, 69277-69456 [2015-23439]
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Vol. 80
Monday,
No. 216
November 9, 2015
Part II
Department of Energy
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10 CFR Parts 429 and 430
Energy Conservation Program: Test Procedures for Central Air Conditioners
and Heat Pumps; Proposed Rule
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DEPARTMENT OF ENERGY
10 CFR Parts 429 and 430
[Docket No. EERE–2009–BT–TP–0004]
RIN 1904–AB94
Energy Conservation Program: Test
Procedures for Central Air
Conditioners and Heat Pumps
Office of Energy Efficiency and
Renewable Energy, Department of
Energy.
ACTION: Supplemental notice of
proposed rulemaking.
AGENCY:
The U.S. Department of
Energy (DOE) proposes to revise its test
procedures for central air conditioners
and heat pumps established under the
Energy Policy and Conservation Act.
DOE proposed amendments to the test
procedure in a June 2010 notice of
proposed rulemaking (NOPR), an April
2011 supplemental notice of proposed
rulemaking (SNOPR), and an October
2011 SNOPR. DOE provided additional
time for stakeholder comment in a
December 2011 extension of the
comment period for the October 2011
SNOPR. DOE received further public
comment for revising the test procedure
in a November 2014 Request for
Information for energy conservation
standards for central air conditioners
and heat pumps. DOE proposes in this
SNOPR: A new basic model definition
as it pertains to central air conditioners
and heat pumps and revised rating
requirements; revised alternative
efficiency determination methods;
termination of active waivers and
interim waivers; revised procedures to
determine off mode power
consumption; changes to the test
procedure that would improve test
repeatability and reduce test burden;
clarifications to ambiguous sections of
the test procedure intended also to
improve test repeatability; inclusion of,
amendments to, and withdrawals of test
procedure revisions proposed in
published test procedure notices in the
rulemaking effort leading to this
supplemental notice of proposed
rulemaking; and changes to the test
procedure that would improve field
representativeness. Some of these
proposals also include incorporation by
reference of updated industry standards.
DOE welcomes comments from the
public on any subject within the scope
of this test procedure rulemaking.
DATES: DOE will accept comments, data,
and information regarding this
supplemental notice of proposed
rulemaking (SNOPR) no later than
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SUMMARY:
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December 9, 2015. See section V,
‘‘Public Participation,’’ for details.
ADDRESSES: Any comments submitted
must identify the SNOPR for test
procedures for central air conditioners
and heat pumps, and provide docket
number EE–2009–BT–TP–0004 and/or
regulatory information number (RIN)
number 1904–AB94. Comments may be
submitted using any of the following
methods:
1. Federal eRulemaking Portal:
www.regulations.gov. Follow the
instructions for submitting comments.
2. Email: RCAC-HP-2009-TP-0004@
ee.doe.gov. Include the docket number
EE–2009–BT–TP–0004 and/or 1904–
AB94 RIN in the subject line of the
message.
3. Mail: Ms. Brenda Edwards, U.S.
Department of Energy, Building
Technologies Office, Mailstop EE–2J,
1000 Independence Avenue SW.,
Washington, DC 20585–0121. If
possible, please submit all items on a
CD, in which case it is not necessary to
include printed copies.
4. Hand Delivery/Courier: Ms. Brenda
Edwards, U.S. Department of Energy,
Building Technologies Office, 950
L’Enfant Plaza SW., Suite 600,
Washington, DC 20024.
Telephone: (202) 586–2945. If
possible, please submit all items on a
CD, in which case it is not necessary to
include printed copies.
For detailed instructions on submitting
comments and additional information
on the rulemaking process, see section
V of this document (Public
Participation).
Docket: The docket, which includes
Federal Register notices, public meeting
attendee lists and transcripts,
comments, and other supporting
documents/materials, is available for
review at www.regulations.gov. All
documents in the docket are listed in
the regulations.gov index. However,
some documents listed in the index,
such as those containing information
that is exempt from public disclosure,
may not be publicly available.
A link to the docket Web page can be
found at: www1.eere.energy.gov/
buildings/appliance_standards/
rulemaking.aspx/ruleid/72. This Web
page will contain a link to the docket for
this notice on the www.regulations.gov
site. The www.regulations.gov Web page
will contain simple instructions on how
to access all documents, including
public comments, in the docket. See
section V for information on how to
submit comments through
regulations.gov.
FOR FURTHER INFORMATION CONTACT:
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Ashley Armstrong, U.S. Department of
Energy, Office of Energy Efficiency
and Renewable Energy, Building
Technologies Program, EE–2J, 1000
Independence Avenue SW.,
Washington, DC 20585–0121.
Telephone: (202) 586–6590. Email:
Ashley.Armstrong@ee.doe.gov.
Johanna Hariharan, U.S. Department of
Energy, Office of the General Counsel,
GC–33, 1000 Independence Avenue
SW., Washington, DC, 20585–0121.
Telephone: (202) 287–6307. Email:
Johanna.Hariharan@hq.doe.gov.
For further information on how to
submit a comment, review other public
comments and the docket, or participate
in the public meeting, contact Ms.
Brenda Edwards at (202) 586–2945 or by
email: Brenda.Edwards@ee.doe.gov.
SUPPLEMENTARY INFORMATION: DOE
intends to incorporate by reference the
following industry standards into Part
430:
(1) ANSI/AHRI 210/240–2008 with
Addenda 1 and 2: Performance Rating of
Unitary Air-Conditioning & Air-Source
Heat Pump Equipment, 2012;
(2) AHRI 210/240-Draft: Performance
Rating of Unitary Air-Conditioning &
Air-Source Heat Pump Equipment;
(3) ANSI/AHRI 1230–2010 with
Addendum 2: Performance Rating of
Variable Refrigerant Flow (VRF) MultiSplit Air-Conditioning and Heat Pump
Equipment, 2010;
(4) ASHRAE 23.1–2010: Methods of
Testing for Rating the Performance of
Positive Displacement Refrigerant
Compressors and Condensing Units that
Operate at Subcritical Temperatures of
the Refrigerant;
(5) ASHRAE Standard 37–2009,
Methods of Testing for Rating
Electrically Driven Unitary AirConditioning and Heat Pump
Equipment;
(6) ASHRAE 41.1–2013: Standard
Method for Temperature Measurement;
ASHRAE 41.6–2014: Standard Method
for Humidity Measurement;
(7) ASHRAE 41.9–2011: Standard
Methods for Volatile-Refrigerant Mass
Flow Measurements Using Calorimeters;
(8) ASHRAE/AMCA 51–07/210–07,
Laboratory Methods of Testing Fans for
Certified Aerodynamic Performance
Rating.
Copies of ANSI/AHRI 210/240–2008
and ANSI/AHRI 1230–2010 can be
obtained from the Air-Conditioning,
Heating, and Refrigeration Institute,
2111 Wilson Boulevard, Suite 500,
Arlington, VA 22201, USA, 703–524–
8800, or by going to https://
www.ahrinet.org/site/686/Standards/
HVACR-Industry-Standards/SearchStandards. A copy of AHRI 210/240-
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Draft is available on the rulemaking
Web page (Docket EERE–2009–BT–TP–
0004–0045).
Copies of ASHRAE 23.1–2010,
ASHRAE Standard 37–2009, ASHRAE
41.1–2013, and ASHRAE 41.9–2011 can
be purchased from ASHRAE’s Web site
at https://www.ashrae.org/resourcespublications.
Copies of ASHRAE/AMCA 51–07/
210–07 can be purchases from AMCA’s
Web site at https://www.amca.org/store/
index.php.
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Table of Contents
I. Authority and Background
A. Authority
B. Background
II. Summary of the Supplementary Notice of
Proposed Rulemaking
III. Discussion
A. Definitions, Testing, Rating, and
Compliance of Basic Models of Central
Air Conditioners and Heat Pumps
1. Basic Model Definition
2. Additional Definitions
3. Determination of Certified Rating
4. Compliance With Federal (National or
Regional) Standards
5. Certification Reports
6. Represented Values
7. Product-Specific Enforcement Provisions
B. Alternative Efficiency Determination
Methods
1. General Background
2. Terminology
3. Elimination of the Pre-Approval
Requirement
4. AEDM Validation
5. Requirements for Independent Coil
Manufacturers
6. AEDM Verification Testing
7. Failure to Meet Certified Ratings
8. Action Following a Determination of
Noncompliance
C. Waiver Procedures
1. Termination of Waivers Pertaining to
Air-to-Water Heat Pump Products With
Integrated Domestic Water Heating
2. Termination of Waivers Pertaining to
Multi-Circuit Products
3. Termination of Waiver and Clarification
of the Test Procedure Pertaining to
Multi-Blower Products
4. Termination of Waiver Pertaining to
Triple-Capacity, Northern Heat Pump
Products
D. Measurement of Off Mode Power
Consumption
1. Test Temperatures
2. Calculation and Weighting of P1 and P2
3. Products With Large, Multiple or
Modulated Compressors
4. Procedure for Measuring Low-Voltage
Component Power
5. Revision of Off-Mode Power
Consumption Equations
6. Off-Mode Power Consumption for Split
Systems
7. Time Delay Credit
8. Test Metric for Off-Mode Power
Consumption
9. Impacts on Product Reliability
10. Representative Measurement of Energy
Use
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E. Test Repeatability Improvement and
Test Burden Reduction
1. Indoor Fan Speed Settings
2. Requirements for the Refrigerant Lines
and Mass Flow Meter
3. Outdoor Room Temperature Variation
4. Method of Measuring Inlet Air
Temperature on the Outdoor Side
5. Requirements for the Air Sampling
Device
6. Variation in Maximum Compressor
Speed With Outdoor Temperature
7. Refrigerant Charging Requirements
8. Alternative Arrangement for Thermal
Loss Prevention for Cyclic Tests
9. Test Unit Voltage Supply
10. Coefficient of Cyclic Degradation
11. Break-in Periods Prior to Testing
12. Industry Standards That Are
Incorporated by Reference
13. Withdrawing References to ASHRAE
Standard 116–1995 (RA 2005)
14. Additional Changes Based on AHRI
210/240-Draft
15. Damping Pressure Transducer Signals
F. Clarification of Test Procedure
Provisions
1. Manufacturer Consultation
2. Incorporation by Reference of ANSI/
AHRI Standard 1230–2010
3. Replacement of the Informative
Guidance Table for Using the Federal
Test Procedure
4. Clarifying the Definition of a Mini-Split
System
5. Clarifying the Definition of a Multi-Split
System
G. Test Procedure Reprint
H. Improving Field Representativeness of
the Test Procedure
1. Minimum External Static Pressure
Requirements for Conventional Central
Air Conditioners and Heat Pumps
2. Minimum External Static Pressure
Adjustment for Blower Coil Systems
Tested With Condensing Furnaces
3. Default Fan Power for Coil-Only Systems
4. Revised Heating Load Line
5. Revised Heating Mode Test Procedure
for Products Equipped With VariableSpeed Compressors
I. Identified Test Procedure Issues DOE
May Consider in Future Rulemakings
1. Controlling Variable Capacity Units to
Field Conditions
2. Revised Ambient Test Conditions
3. Performance Reporting at Certain Air
Volume Flow Rates
4. Cyclic Test With a Wet Coil
5. Inclusion of the Calculation for Sensible
Heating Ratio
J. Compliance With Other Energy Policy
and Conservation Act Requirements
1. Test Burden
2. Potential Incorporation of International
Electrotechnical Commission Standard
62301 and International Electrotechnical
Commission Standard 62087
IV. Procedural Issues and Regulatory Review
A. Review Under Executive Order 12866
B. Review Under the Regulatory Flexibility
Act
C. Review Under the Paperwork Reduction
Act of 1995
D. Review Under the National
Environmental Policy Act of 1969
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E. Review Under Executive Order 13132
F. Review Under Executive Order 12988
G. Review Under the Unfunded Mandates
Reform Act of 1995
H. Review Under the Treasury and General
Government Appropriations Act, 1999
I. Review Under Executive Order 12630
J. Review Under the Treasury and General
Government Appropriations Act, 2001
K. Review Under Executive Order 13211
L. Review Under Section 32 of the Federal
Energy Administration Act of 1974
M. Description of Materials Incorporated
by Reference
V. Public Participation
A. Attendance at Public Meeting
B. Procedure for Submitting Prepared
General Statements for Distribution
C. Conduct of Public Meeting
D. Submission of Comments
E. Issues on Which DOE Seeks Comment
VI. Approval of the Office of the Secretary
I. Authority and Background
A. Authority
Title III, Part B of the Energy Policy
and Conservation Act of 1975 (EPCA or
the Act), Pub. L. 94–163 (42 U.S.C.
6291¥6309, as codified), established
the Energy Conservation Program for
Consumer Products Other Than
Automobiles, a program covering most
major household appliances, including
the single phase central air conditioners
and heat pumps 1 with rated cooling
capacities less than 65,000 British
thermal units per hour (Btu/h) that are
the focus of this notice.2 (42 U.S.C.
6291(1)–(2), (21) and 6292(a)(3))
Under EPCA, the program consists of
four activities: (1) Testing; (2) labeling;
(3) Federal energy conservation
standards; and (4) certification,
compliance, and enforcement. The
testing requirements consist of test
procedures that manufacturers of
covered products must use as the basis
for certifying to DOE that their products
comply with applicable energy
conservation standards adopted
pursuant to EPCA and for representing
the efficiency of those products. (42
U.S.C. 6293(c); 42 U.S.C. 6295(s))
Similarly, DOE must use these test
procedures in any enforcement action to
determine whether covered products
comply with these energy conservation
standards. (42 U.S.C. 6295(s)) Under 42
U.S.C. 6293, EPCA sets forth criteria and
procedures for DOE’s adoption and
amendment of such test procedures.
Specifically, EPCA provides that an
amended test procedure shall produce
results which measure the energy
1 Where this notice uses the terms ‘‘HVAC’’ or
‘‘CAC/CHP’’, they are in reference specifically to
central air conditioners and heat pumps as covered
by EPCA.
2 For editorial reasons, upon codification in the
U.S. Code, Part B was re-designated Part A.
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efficiency, energy use, or estimated
annual operating cost of a covered
product over an average or
representative period of use, and shall
not be unduly burdensome to conduct.
(42 U.S.C. 6293(b)(3)) In addition, if
DOE determines that a test procedure
amendment is warranted, it must
publish proposed test procedures and
offer the public an opportunity to
present oral and written comments on
them. (42 U.S.C. 6293(b)(2))
Furthermore, DOE must review test
procedures at least once every 7 years.
(42 U.S.C 6293(b)(1)(A)) DOE last
published a test procedure final rule for
central air conditioner and heat pumps
on October 22, 2007. 72 FR 59906.
Finally, in any rulemaking to amend a
test procedure, DOE must determine
whether and the extent to which the
proposed test procedure would change
the measured efficiency of a system that
was tested under the existing test
procedure. (42 U.S.C. 6293(e)(1)) If DOE
determines that the amended test
procedure would alter the measured
efficiency of a covered product, DOE
must amend the applicable energy
conservation standard accordingly. (42
U.S.C. 6293(e)(2))
DOE’s existing test procedures for
central air conditioners and heat pumps
adopted pursuant to these provisions
appear under Title 10 of the Code of
Federal Regulations (CFR) Part 430,
Subpart B, Appendix M (‘‘Uniform Test
Method for Measuring the Energy
Consumption of Central Air
Conditioners and Heat Pumps’’). These
procedures establish the currently
permitted means for determining energy
efficiency and annual energy
consumption of these products. Some
amendments proposed in this SNOPR
will not alter the measured efficiency of
central air conditioners and heat pumps,
and thus are being proposed as revisions
to the current Appendix M. Other
amendments proposed in this SNOPR
will alter the measured efficiency, as
represented in the regulating metrics of
energy efficiency ratio (EER), seasonal
energy efficiency ratio (SEER), and
heating seasonal performance factor
(HSPF). These amendments are
proposed as part of a new Appendix
M1. The test procedure changes
proposed in this notice as part of a new
Appendix M1, if adopted, would not
become mandatory until the existing
energy conservation standards are
revised. (42 U.S.C. 6293(e)(2)) In
revising the energy conservation
standards, DOE would create a crosswalk from the existing standards under
the current test procedure to what the
standards would be if tested using the
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revised test procedure. DOE would then
use the cross-walked equivalent of the
existing standard as the baseline for its
standards analysis to prevent backsliding as required under 42 U.S.C.
6295(o)(1).
On December 19, 2007, the President
signed the Energy Independence and
Security Act of 2007 (EISA 2007), Pub.
L. 110–140, which contains numerous
amendments to EPCA. Section 310 of
EISA 2007 established that the
Department’s test procedures for all
covered products must account for
standby mode and off mode energy
consumption. (42 U.S.C. 6295(gg)(2)(A))
For central air conditioners and heat
pumps, standby mode is incorporated
into the SEER metric, while off mode
power consumption is separately
regulated. This SNOPR includes
proposals relevant to the determination
of both SEER (including standby mode)
and off mode power consumption.
10 CFR 430.27 allows manufacturers
to submit an application for an interim
waiver and/r a petition for a waiver
granting relief from adhering to the test
procedure requirements found under 10
CFR part 430, subpart B, Appendix M.
For those waivers that are active,
however, 10 CFR 430.27(l) requires DOE
to amend its regulations so as to
eliminate any need for the continuation
of such waivers. To this end, this notice
proposes relevant amendments to its
test procedure concerning such waivers.
B. Background
This SNOPR addresses proposals and
comments from three separate
rulemakings, two guidance documents,
and a working group: (1) Proposals for
off mode test procedures made in earlier
notices as part of this rulemaking
(Docket No. EERE–2009–BT–TP–0004);
(2) proposals regarding alternative
efficiency determination methods
(Docket No. EERE–2011–BT–TP–0024);
(3) stakeholder comments from a request
for information regarding energy
conservation standards (Docket No.
EERE–2014–BT–STD–0048); (4) a draft
guidance document related to testing
and rating split systems with blower
coil units (Docket No. EERE–2014–BT–
GUID–0033); (5) a draft guidance
document that deals with selecting units
for testing, rating, and certifying splitsystem combinations, including
discussion of basic models and of
condensing units and evaporator coils
sold separately for replacement
installation (Docket No. EERE–2014–
BT–GUID–0032); and (6) the
recommendations of the regional
standards enforcement Working Group
(Docket No. EERE–2011–BT–CE–0077).
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DOE’s initial proposals for estimating
off mode power consumption in the test
procedure for central air conditioners
and heat pumps were shared with the
public in a notice of proposed
rulemaking published in the Federal
Register on June 2, 2010 (June 2010
NOPR; 75 FR 31224) and at a public
meeting at DOE headquarters in
Washington, DC on June 11, 2010.
Subsequently, DOE published a
supplemental notice of proposed
rulemaking (SNOPR) on April 1, 2011,
in response to comments received on
the June 2010 NOPR and due to the
results of additional laboratory testing
conducted by DOE. (April 2011 SNOPR)
76 FR 18105, 18127. DOE received
additional comments in response to the
April 2011 SNOPR and proposed an
amended version of the off mode
procedure that addressed those
comments in a second SNOPR on
October 24, 2011 (October 2011
SNOPR). 76 FR 65616. DOE received
additional comments during the
comment period of the October 24, 2011
SNOPR and the subsequent extended
comment period. 76 FR 79135.
Between the April 2011 and October
2011 SNOPRs, DOE published a direct
final rule (DFR) in the Federal Register
on June 27, 2011 that set forth amended
energy conservation standards for
central air conditioners and central air
conditioning heat pumps, including a
new standard for off mode electrical
power consumption. (June 2011 DFR) 76
FR 37408. Units manufactured on or
after January 1, 2015, are subject to that
standard for off mode electrical power
consumption. 10 CFR 430.32(c)(6).
However, on July 8, 2014, DOE
published an enforcement policy
statement regarding off mode standards
for central air conditioners and central
air conditioning heat pumps 3 (July 2014
Enforcement Policy Statement)
specifying that DOE will not assert civil
penalty authority for violation of the off
mode standard until 180 days following
publication of a final rule establishing a
test method for measuring off mode
electrical power consumption.
DOE also pursued, in a request for
information (RFI) published on April
18, 2011 (AEDM RFI) (76 FR 21673),
and a NOPR published on May 31, 2012
(AEDM NOPR) (77 FR 32038), revisions
to its existing alternative efficiency
determination methods (AEDM) and
alternative rating methods (ARM)
requirements to improve the approach
by which manufacturers may use
3 Available at: https://energy.gov/sites/prod/files/
2014/07/f17/
Enforcement%20Policy%20Statement%20%20cac%20off%20mode.pdf (Last accessed March
30, 2015.)
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Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
modeling techniques as the basis to
certify consumer products and
commercial and industrial equipment
covered under EPCA. DOE also
published a final rule regarding AEDM
requirements for commercial and
industrial equipment only (Commercial
Equipment AEDM FR). 78 FR 79579.
This SNOPR addresses the proposals
made and comments received in the
AEDM NOPR applicable to central air
conditioners and heat pumps and makes
additional proposals.
On June 13, 2014, DOE published a
notice of intent to form a working group
to negotiate enforcement of regional
standards for central air conditioners
and requested nominations from parties
interested in serving as members of the
Working Group. 79 FR 33870. On July
16, 2014, the Department published a
notice of membership announcing the
eighteen nominations that were selected
to serve as members of the Working
Group, in addition to two members from
Appliance Standards and Rulemaking
Federal Advisory Committee (ASRAC),
and one DOE representative. 79 FR
41456. The Working Group identified a
number of issues related to testing and
certification that are being addressed in
this rule. In addition, all
nongovernmental participants of the
Working Group approved the final
report contingent on upon the issuance
of the final guidance on Docket No.
EERE–2014–BT–GUID–0032 0032 and
Docket No. EERE–2014–BT–GUID–0033
consistent with the understanding of the
Working Group as set forth in its
recommendations. (Docket No. EERE–
2011–BT–CE–0077–0070, Attachment)
This SNOPR responds to comments on
the August 19 and 20, 2014, guidance
documents related to testing and rating
split systems, which are discussed in
more detail in section III.A. The
proposed changes supplant these two
draft guidance documents; DOE will not
finalize the draft guidance documents
and instead will provide any necessary
clarity through this notice and the final
rule. DOE believes the proposed
changes are consistent with the intent of
the Working Group.
On November 5, 2014, DOE published
a request for information for energy
conservation standards (ECS) for central
air conditioners and heat pumps
(November 2014 ECS RFI). 79 FR 65603.
In response, several stakeholders
provided comments suggesting that DOE
amend the current test procedure. This
SNOPR responds to those test
procedure-related comments.
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II. Summary of the Supplementary
Notice of Proposed Rulemaking
This supplementary notice of
proposed rulemaking (SNOPR) proposes
revising the certification requirements
and test procedure for central air
conditioners and heat pumps based on
various published material as discussed
in section I.B.
DOE proposes to revise the basic
model definition, add additional
definitions for clarity, make certain
revisions to the testing requirements for
determination of certified ratings, add
certain certification reporting
requirements, revise requirements for
determination of represented values,
and add product-specific enforcement
provisions. Some of the proposed
revisions to the certification
requirements would impact the energy
conservation standard and thus would
not be effective until the compliance
date of any amended energy
conservation standards.
DOE proposes to update requirements
for Alternative Rating Methods (ARMs)
used to determine performance metrics
for central air conditioners and heat
pumps based on the regulations for
Alternative Efficiency Determination
Methods (AEDMs) that are used to
estimate performance for commercial
HVAC equipment. Specifically, for
central air conditioners and heat pumps,
DOE proposes: (1) Revisions to
nomenclature regarding ARMs; (2)
rescinding DOE pre-approval of an ARM
prior to use; (3) AEDM validation
requirements; (4) a verification testing
process; (5) actions a manufacturer
could take following a verification test
failure; and (6) consequences for invalid
ratings. These proposed changes do not
impact the energy conservation
standard.
DOE proposes to revise the test
procedure such that tests of multicircuit products, triple-capacity
northern heat pump products, and
multi-blower products can be performed
without the need of an interim waiver
or a waiver. Existing interim waivers
and waivers, as applicable, regarding
these products would terminate on the
effective date of a final rule
promulgating the proposals in this
SNOPR. DOE also reaffirms that the
waivers associated with multi-split
products have already terminated and
that these products can also be tested
using the current and proposed test
procedure. These proposed changes do
not impact the energy conservation
standard and thus are proposed as part
of revisions to Appendix M.
DOE also proposes to clarify that airto-water heat pump products integrated
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with domestic water heating are not
subject to central air conditioner and
heat pump energy conservation
standards. Accordingly, the waiver
regarding these products would
terminate effective 180 days after
publication of a final rule that
incorporates the proposals in this
SNOPR.
DOE proposes revisions to the test
methods and calculations for off mode
power consumption that were proposed
or modified in the June 2010 NOPR,
April 2011 SNOPR, and October 2011
SNOPR. These revisions address
comments received in response to the
October 2011 SNOPR suggesting that
test methods and calculations more
accurately represent off-mode power
consumption in field applications.
These proposed changes do not impact
the energy conservation standard.
Specifically, DOE proposes the
following:
(1) Establishment of separate testing
and calculations that would depend on
whether the tested unit is equipped
with a crankcase heater and whether the
crankcase heater is controlled during
the test;
(2) Alteration of the testing
temperatures such that the crankcase
heater is tested in outdoor air conditions
that are representative of the shoulder
and heating seasons;
(3) Changing of the testing
methodology for determining the power
consumption of the low-voltage
components (PX);
(4) Changing of the calculation of the
off mode power rating (PW,OFF) such that
the off mode power for the shoulder and
heating seasons are equally weighted;
(5) Implementation of a time delay
credit for energy consumption,
including credits in the form of scaling
factors and multipliers for energyefficient products that require larger
crankcase heaters to maintain product
reliability;
(6) Addition of an alternative energy
determination method for determining
off mode power for coil-only splitsystems; and
(7) Inclusion of a means for
calculating a basic model’s annual off
mode energy use, from which
manufacturers could make
representations about their products’ off
mode energy use.
DOE also proposes changes to
improve the repeatability and reduce
the test burden of the test procedure.
These proposed changes do not impact
the energy conservation standard.
Specifically, DOE proposes the
following:
(1) Clarification of fan speed settings;
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(2) Clarification of insulation
requirements for refrigerant lines and
addition of a requirement for insulating
mass flow meters;
(3) Addition of a requirement to
demonstrate inlet air temperature
uniformity for the outdoor unit using
thermocouples;
(4) Addition of a requirement that
outdoor air conditions be measured
using sensors measuring the air
captured by the air sampling device(s)
rather than the temperature sensors
located in the air stream approaching
the inlets;
(5) Addition of a requirement that the
air sampling device and the tubing that
transfers the collected air to the dry bulb
temperature sensor be at least two
inches from the test chamber floor, and
a requirement that humidity
measurements be based on dry bulb
temperature measurements made at the
same location as the corresponding wet
bulb temperature measurements used to
determine humidity;
(6) Clarification of maximum speed
for variable-speed compressors;
(7) Addition of requirements that
improve consistency of refrigerant
charging procedures;
(8) Allowance of an alternative
arrangement for cyclic tests to replace
the currently-required damper in the
inlet portion of the indoor air ductwork
for single-package ducted units;
(9) Clarification of the proper supply
voltage for testing;
(10) Revision of the determination of
the coefficient of cyclic degradation
(CD);
(11) Option for a break-in period of up
to 20 hours;
(12) Update of references to industry
standards where appropriate;
(13) Withdrawal of all references to
ASHRAE Standard 116–1995;
(14) Inclusion of information from the
draft AHRI 210/240; and
(15) Provisions regarding damping of
pressure transducer signals to avoid
exceeding test operating tolerances due
to high frequency fluctuations.
Lastly, DOE proposes clarifications of
any sections of the test procedure that
may be ambiguous. Specifically, DOE
proposes to add reference to an industry
standard for testing variable refrigerant
flow multi-split systems; replace the
informative guidance table for using the
test procedure; and clarify definitions of
multi-split systems and mini-split
systems, which DOE now proposes to
call single-zone-multiple-unit systems.
These proposed changes do not impact
the energy conservation standard.
DOE notes that all the above-listed
proposed changes to the test procedure
would not impact the energy
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conservation standard and as such are
proposed as part of a revised Appendix
M. Given the extensive changes
proposed for Appendix M, DOE has
provided a full re-print of Appendix M
in the regulatory text of this SNOPR that
includes the changes proposed in this
SNOPR as well as those proposed in the
June 2010 NOPR and the April 2011 and
October 2011 SNOPRs that have not
been withdrawn.
DOE also proposes various changes to
the test procedure that would affect the
energy conservation standard and
proposes incorporating these changes in
a new appendix, Appendix M1 to
Subpart B of 10 CFR part 430, which
includes the text of Appendix M to
Subpart B of 10 CFR part 430 with
amendments as proposed in this
SNOPR. Specifically, DOE proposes the
following:
(1) Increase the minimum external
static pressure requirements for
conventional central air conditioners
and heat pumps to better represent the
external static pressure conditions in
field installations; 4
(2) Add a minimum external static
pressure adjustment to correct for
potentially unrepresentative external
static pressure conditions for blower
coil systems tested with condensing
furnaces;
(3) Raise the default fan power for
coil-only systems;
(4) Adjust the heating load line
equation such that the zero load point
occurs at 55 °F for Region IV, the
adjustment factor is 1.3, and the heating
load is tied with the heat pump’s
cooling capacity; and
(5) Revise the heating mode test
procedure to allow more options for
products equipped with variable-speed
compressors.
DOE proposes to make the test
procedure revisions in this SNOPR as
reflected in the revised Appendix M to
Subpart B of 10 CFR part 430 effective
on a date 180 days after publication of
the test procedure final rule in the
Federal Register and mandatory for
testing to determine compliance with
the existing energy conservation
standards for central air conditioners
and heat pumps as of that date. DOE
proposes to make the test procedure
revisions in this SNOPR as reflected in
the proposed new Appendix M1 to
Subpart B of 10 CFR part 430 effective
on the compliance date of the revised
energy conservation standards for
central air conditioners and heat pumps
4 Conventional
central air conditioners and heat
pumps are those products that are not short duct
systems (see section III.F.2) or small-duct, highvelocity systems.
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and mandatory for testing to determine
compliance with said revised standards
as of that date. DOE will address any
comments received in response to this
SNOPR in the test procedure final rule.
As noted in section I.A, 42 U.S.C.
6293(e) requires that DOE shall
determine to what extent, if any, the
proposed test procedure would alter the
measured energy efficiency and
measured energy use. DOE has
determined that some of these proposed
amendments would result in a change
in measured energy efficiency and
measured energy use for central air
conditioners and heat pumps.
Therefore, DOE is conducting a separate
rulemaking to amend the energy
conservation standards for central air
conditioners and heat pumps with
respect to the revised test procedure,
once its proposals become final. (Docket
No. EERE–2014–BT–STD–0048)
III. Discussion
This section discusses the revisions to
the certification requirements and test
procedure that DOE proposes in this
SNOPR.
A. Definitions, Testing, Rating, and
Compliance of Basic Models of Central
Air Conditioners and Heat Pumps
On August 19 and 20, 2014, DOE
issued two draft guidance documents
regarding the test procedure for central
air conditioners and heat pumps. One
guidance document dealt with testing
and rating split systems with blower
coil indoor units (Docket No. EERE–
2014–BT–GUID–0033); and the other
dealt more generally with selecting
units for testing, rating, and certifying
split-system combinations, including
discussion of basic models and of
condensing units and evaporator coils
sold separately for replacement
installation (Docket No. EERE–2014–
BT–GUID–0032). The comments in
response to these draft guidance
documents are discussed in this section
of the notice. DOE has proposed
changes to the substance of the draft
guidance that reflects the comments
received as well as the
recommendations of the regional
standards enforcement Working Group
(Docket No. EERE–2011–BT–CE–0077–
0070, Attachment). The proposed
changes supplant the two draft guidance
documents; DOE will not finalize the
draft guidance documents and instead
will provide any necessary clarity
through this notice and the final rule.
1. Basic Model Definition
In the August 20, 2014 draft guidance
document (Docket No. EERE–2014–BT–
GUID–0032), DOE clarified that a basic
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model means all units of a given type
(or class thereof) having the same
primary energy source, and which have
essentially identical electrical, physical,
and functional characteristics that affect
energy efficiency. 10 CFR 430.2. DOE
noted that for split-system units, this
includes a condensing (outdoor) unit
and a coil-only or blower coil indoor
unit.5
In the guidance document, DOE also
stated that if a company intended to
claim ratings for each combination of
outdoor unit and indoor unit, it must
certify all possible model combinations
as separate basic models. Only the basic
model combinations that include a
highest sales volume combination
(HSVC) indoor unit for a given outdoor
unit must be tested, while the other
basic models may be rated with an
ARM. Alternatively, the manufacturer
could make all combinations of a given
model of outdoor unit part of the same
basic model and not rate all individual
combinations. However, all
combinations within the basic model
would have to have the same
represented efficiency, based on the
least efficient combination. This
association would be included in the
certification report.
In response to the draft guidance
document, AHRI and Johnson Controls
(JCI) stated that there was a difference
between DOE’s definition of Basic
Model and the industry’s use of Basic
Model Groups (Docket No. EERE–2014–
BT–GUID–0032, AHRI, No. 8 at p. 1; JCI,
No. 5 at p. 3) Johnson Controls specified
that most manufacturers consider a
specific outdoor model with all
combinations of indoor units to be a
basic model and notes that DOE’s
definition appeared to allow outdoor
units to be combined into a basic model
if they share the same ratings. (Id.)
DOE reviewed AHRI’s Operations
Manual for Unitary Small AirConditioners and Air-Source Heat
Pumps (Includes Mixed-Match Coils)
(Rated Below 65,000 Btu/h) Certification
Program (AHRI OM 210/240—January
2014).6 This document specifies the
following definitions:
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A Split System BMG [Basic Model Group 7]
consists of products with the same Outdoor
5 DOE notes that a blower coil indoor unit may
consist of separate units, one that includes the
indoor coil and another that is an air mover, either
a modular blower or a furnace. Alternatively, a
blower coil indoor unit may be a single unit that
includes both the indoor coil and the indoor fan.
Hence, in further discussion, ‘‘blower coil indoor
unit’’ may be any one of these three options.
6 Available at: www.ahrinet.org/App_Content/
ahri/files/Certification/OM%20pdfs/USE_OM.pdf
(Last accessed March 20, 2015.)
7 According to the AHRI General Operations
Manual, a basic model is a product possessing a
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Unit used with several Indoor Unit
combinations (i.e. horizontal, vertical, A-coil,
etc.). Same Outdoor Unit refers to models
with the same or comparable compressor,
used with the same outdoor coil surface area
and the same outdoor air quantity.
An ICM [Independent Coil Manufacturer]
BMG consists of coils (Indoor Units) with
matching capacity ranges of 6,000 Btu/h and
the following identical geometry parameters:
Air-handler, evaporator fan type, evaporator
number of rows, type of equipment (aircooled, water-cooled or evaporativelycooled), evaporator tube centers, evaporator
fin types, evaporator fins/inch, evaporator
tube OD, evaporator expansion device, fin
length per slab, fin height per slab, number
of slabs in the coil, fin material type, tube
material type, and total number of active
tubes (refer to Table H1).
In order to create consistency within
the industry, DOE proposes to modify
its basic model definition for central air
conditioners and heat pumps.
Specifically, DOE proposes that
manufacturers would have a choice in
how to assign individual models (for
single-package units) or combinations
(for split systems) to basic models.
Specifically, manufacturers may
consider each individual model/
combination its own basic model, or
manufacturers may assign all individual
models of the same single-package
system or all individual combinations
using the same model of outdoor unit
(for outdoor unit manufacturers (OUM))
or model of indoor unit (for
independent coil manufacturers (ICM))
to the same basic model.
DOE believes that this proposal is
consistent with the existing general
definition of basic model which refers to
all units having the same primary
energy source and having essentially
identical electrical, physical, and
functional characteristics that affect
energy consumption or energy
efficiency. However, DOE proposes to
further define the physical
characteristics necessary to assign
individual models or combinations to
the same basic model:
(i) For split-systems manufactured by
independent coil manufacturers (ICMs)
and for small-duct, high velocity
systems: All individual combinations
having the same model of indoor unit,
which means the same or comparably
performing indoor coil(s) [same face
area; fin material, depth, style (e.g.
wavy, louvered), and density (fins per
inch); tube pattern, material, diameter,
discrete performance rating, whereas a basic model
group is a set of models that share characteristics
that allow the performance of one model to be
representative of the group, although the group does
not have to share discrete performance. (General
OM—October 2013). Available at: www.ahrinet.org/
App_Content/ahri/files/Certification/OM%20pdfs/
General_OM.pdf. (Last accessed March 24, 2015.)
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wall thickness, and internal
enhancement], indoor fan(s) [same air
flow with the same indoor coil and
external static pressure, same power
input], auxiliary refrigeration system
components if present (e.g. expansion
valve), and controls.
(ii) for split-systems manufactured by
outdoor unit manufacturers (OUMs): All
individual combinations having the
same model of outdoor unit, which
means the same or comparably
performing compressor(s) [same
displacement rate (volume per time) and
same capacity and power input when
tested under the same operating
conditions], outdoor coil(s) [same face
area; fin material, depth, style (e.g.
wavy, louvered), and density (fins per
inch); tube pattern, material, diameter,
wall thickness, and internal
enhancement], outdoor fan(s) [same air
flow with the same outdoor coil, same
power input], auxiliary refrigeration
system components if present (e.g.
suction accumulator, reversing valve,
expansion valve), and controls.
The proposed requirements for singlepackage models combine the
requirements listed describing the
characteristics of the same models of
indoor units and same models of
outdoor units. DOE requests comment
on its proposal to modify the definition
of ‘‘basic model’’, as well as the
proposed physical characteristics
required for assigning individual
models or combinations to the same
basic model, as described above.
If manufacturers assign each
individual model or combination to its
own basic model, DOE proposes that
each individual model/combination
must be tested and that an AEDM
cannot be applied. This option would
limit a manufacturer’s risk in terms of
noncompliance but would represent
increased testing burden compared to
the other option.
If manufacturers assign all individual
combinations of a model of outdoor unit
(for OUMs) or model of indoor unit (for
ICMs) to a single basic model, DOE
further proposes that, in contrast to the
draft guidance document and DOE’s
current regulations, each individual
combination within a basic model (i.e.,
having the same model of outdoor unit
for OUMs, or having the same model of
indoor unit for ICMs) must be certified
with a rating determined for that
individual combination. In other words,
individual combinations within the
same basic model that have different
SEER ratings, for example, would be
certified with their individual ratings,
rather than with the lowest SEER of the
basic model. However, only one
individual combination in each basic
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model would have to be tested (see
section III.A.3.a), while the others may
be rated using an AEDM. This option
reduces testing burden but increases
risk. Specifically, if any one of the
combinations within a basic model fails
to meet the applicable standard, then all
of the combinations within the basic
model fail, and the entire basic model
must be taken off the market (i.e., the
model of outdoor unit for OUMs and the
model of indoor unit for ICMs). All
combinations offered for sale (e.g., for
OUMs, based on a given model of
outdoor unit which is the basis of the
basic model) must be certified, and all
of these combinations within the basic
model must meet applicable standards.
DOE notes that under this proposed
rule, ICMs and OUMs will continue to
have an independent obligation to test,
provide certified ratings, and ensure
compliance with applicable standards.
By way of example, a manufacturer
has two models of outdoor units,
models A and B. Each of models A and
B can be paired with any of three
models of indoor units—models 1, 2,
and 3. Per the guidance document, the
manufacturer could either: (1) Make
each combination a separate basic
model (i.e., A–1, A–2, A–3, B–1, B–2,
and B–3), test the HSVC for each model
of outdoor unit (A and B), and rate the
other basic models with an ARM; (2)
make each combination a separate basic
model and test each of them; or (3) make
combinations A–2 and A–3 part of basic
model A–1 (and similarly B–2 and B–3
part of B–1) and represent the efficiency
of all three with the same certified
rating at the least efficient combination
in the basic model. In this proposal, the
manufacturer could either: (1) Make
each combination a separate basic
model and test and rate each
combination; or (2) make combinations
A–2 and A–3 part of basic model A–1
(and similarly B–2 and B–3 part of B–
1), test the HSVC combination for the
model of outdoor unit, and test or use
an AEDM to rate the efficiency of all
other combinations in the basic model.
DOE notes that unlike in the current
‘‘basic model’’ definition that contains
less detail on what constitutes
essentially identical characteristics,
under DOE’s new proposal,
manufacturers would not be able to
assign different models of outdoor units
(for OUMs) or models of indoor units
(for ICMs) to a single basic model Based
on a review of certification data, it
appears that most manufacturers are not
currently doing this, so DOE expects
this proposal to have limited impact on
current practices.
Additional rating and certification
requirements for single-package models
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and multi-split, multi-circuit, and
single-zone-multiple-coil models are
described in section III.A.3.c.
Revisions to the test procedure as
proposed in section III.D of this SNOPR
enable the determination of off mode
power consumption, which reflects the
operation of the contributing
components: Crankcase heater and lowvoltage controls. Varying designs of
these components produce different off
mode power consumption. DOE
proposes that if individual
combinations that are otherwise
identical are offered with multiple
options for off mode related
components, manufacturers at a
minimum must rate the individual
combination with the crankcase heater
and controls which are the most
consumptive (i.e., would result in the
largest value of PW,OFF). If a
manufacturer wishes to also make
representations for less consumptive off
mode options for the same individual
combination, the manufacturer may
provide separate ratings, but the
manufacturer must differentiate the
individual model numbers for these
ratings. These individual combinations
would be within the same basic model.
DOE discusses this in relation to singlepackage units in section III.A.3.e.
DOE also proposes to clarify that a
central air conditioner or central air
conditioning heat pump may consist of:
A single-package unit; an outdoor unit
and one or more indoor units (e.g., a
single-split or multi-split system); an
indoor unit only (rated as a combination
by an ICM with an OUM’s outdoor unit);
or an outdoor unit only (with no match,
rated by an OUM with the coil specified
in this test procedure). DOE has
proposed adding these specifications to
the definition of central air conditioner
or central air conditioning heat pump in
10 CFR 430.2. In the certification reports
submitted by OUMs for split systems,
DOE proposes that manufacturers must
report the basic model number as well
as the individual model numbers of the
indoor unit(s) and the air mover where
applicable.
2. Additional Definitions
In order to specify differences in the
proposed basic model definition for
ICMs and OUMs, DOE also proposes the
following definitions:
Independent coil manufacturer (ICM)
means a manufacturer that manufactures
indoor units but does not manufacture singlepackage units or outdoor units.
Outdoor unit manufacturer (OUM) means
a manufacturer of single-package units,
outdoor units, and/or both indoor units and
outdoor units.
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With respect to any given basic
model, a manufacturer could be an ICM
or an OUM. DOE notes that the use of
the term ‘‘manufacturer’’ in these
definitions refers to any person who
manufactures, produces, assembles, or
imports a consumer product. See 42
U.S.C. 6291(10, 12).
DOE also proposes to define variable
refrigerant flow (VRF) systems as a kind
of multi-split system. DOE notes that
not all VRF systems are commercial
equipment. Therefore, the proposed
definition also clarifies that VRF
systems that are single-phase and less
than 65,000 btu/h are a kind of central
air conditioners and central air
conditioning heat pumps.
DOE also proposes to modify the
definition of indoor unit. DOE noted in
market research that ICMs may not
always provide cooling mode expansion
devices with indoor units. Therefore to
provide clarity in the testing and rating
requirements, DOE proposes to change
the definition of ‘‘indoor unit’’ to clarify
that it may not include the cooling
mode expansion device. Also, for
reasons discussed in section III.A.3.f,
DOE proposes to include the casing in
the definition so that uncased coils will
not be considered indoor units:
Indoor unit transfers heat between the
refrigerant and the indoor air, and consists of
an indoor coil and casing and may include
a cooling mode expansion device and/or an
air moving device.
DOE proposes to specify in Appendix
M that if the indoor unit does not ship
with a cooling mode expansion device,
the system should be tested using the
device as specified in the installation
instructions provided with the indoor
unit, or if no device is specified, using
a TXV. DOE notes that the AHRI
program does not appear to assume that
the expansion device is necessarily
provided with the coil, i.e., AHRI’s
operations manual specifies that for
testing for the AHRI certification
program, the ICM must provide an
indoor coil and expansion device.
Finally, DOE is proposing to clarify
several other definitions currently in 10
CFR 430.2 with minor wording changes
and move them to 10 CFR 430, Subpart
B, Appendix M. The proposed
definition of central air conditioner or
central air conditioning heat pump in 10
CFR 430.2 refers the reader to the
additional central air conditionerrelated definitions in Appendix M.
Locating all of the relevant definitions
in the appendix will make it easier to
find and reference them. DOE also
proposes to remove entirely the
definitions for ‘‘condenser-evaporator
coil combination’’ and ‘‘coil family’’ as
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those terms no longer appear in the
proposed regulations.
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3. Determination of Certified Rating
During the regional standards
Working Group meetings, participants
invested a great deal of time and energy
discussing the relationship between
system ratings and an effective
enforcement plan. As part of the
negotiations, the Working Group
requested that DOE issue guidance
regarding the applicability of regional
standards to indoor units and outdoor
units distributed separately and the
applicability of regional standards to
different combinations of indoor and
outdoor units. DOE developed two draft
guidance documents to address these
issues. After consideration of the
Working Group’s discussions and the
comments received on the two draft
guidance documents, DOE determined
that regulatory changes would be
necessary to implement the approach
agreed to by the Working Group. DOE is
proposing several of those regulatory
changes as part of this rulemaking. The
remainder of the necessary regulatory
changes will be addressed in a
forthcoming regional standards
enforcement notice of proposed
rulemaking.
During the pendency of the
rulemakings (CAC TP and Regional
Standards), DOE reaffirms its
commitment to the approach advocated
by the Working Group, subject to
consideration of comments received in
the rulemakings to effectuate the
necessary changes to the regulations.
The following sections describe the two
guidance documents and DOE’s
proposals to address them as part of this
rulemaking.
a. Single-Split-System Air Conditioners
Rated by OUMs
In the August 20, 2014 draft guidance
document (Aug 20 Guidance) (EERE–
2014–BT–GUID–0032), DOE proposed
to clarify that when selecting which
split-system air conditioner and heat
pump units to test (in accordance with
the DOE test procedure), a unit of each
outdoor model must be paired with a
unit of one selected indoor model. 10
CFR 429.16(a)(2)(i). Specifically, the
manufacturer must test the condenserevaporator coil combination that
includes the model of evaporator coil
that is likely to have the largest volume
of retail sales with the particular model
of condensing unit. 10 CFR
429.16(a)(2)(ii) (This combination is also
known as the highest sales volume
combination or HSVC.) That is, the
HSVC for each condensing unit may not
be rated using an ARM. (See section
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III.B regarding DOE’s proposal to switch
from ARMs to AEDMs for this product.)
The guidance further stated that for
any other split-system combination that
includes the same outdoor unit model
but a different indoor unit model than
the HSVC, manufacturers may
determine represented values of energy
efficiency (including those values that,
for each combination, must be reported
in certifications to DOE) of a splitsystem central air conditioner or heat
pump basic model combination either
by testing the combination in
accordance with the DOE test procedure
or by applying an ARM that has been
approved by DOE in accordance with
the provisions of 10 CFR 429.70(e)(1)
and (2). 10 CFR 429.16(a)(2)(ii)(A) and
(B)(1).
In the August 19, 2014 draft guidance
document (August 19 Guidance) (EERE–
2014–BT–GUID–0033), DOE proposed
to clarify that split-system central air
conditioners other than those with
single-speed compressors may be tested
and rated using a blower coil only if the
condensing unit is sold exclusively for
use with a blower coil indoor unit. 10
CFR 429.16(a)(2)(ii). The guidance
stated that there is no provision in the
Code of Federal Regulations (CFR)
permitting use of a blower coil for
testing and rating a split-system central
air conditioner where the condensing
unit is also offered for sale with a coilonly indoor unit, and that, furthermore,
there is no provision in the CFR
permitting the use of a blower coil for
testing and rating a condensing unit
with a single-speed compressor.
Commenters generally agreed with the
information in the August 20 Guidance
regarding selecting units for testing,
rating, and certifying split-system
combinations. In addition, in response
to the August 19 Guidance, DOE
received nearly identical comments
from several stakeholders generally
agreeing with the intent of the guidance
to emphasize that single-speed
compressor products must be tested and
rated with a coil-only system as HSVC.
(Docket No. EERE–2014–BT–GUID–
0033, AHRI No. 8 at p. 2; Nordyne, No.
9 at p. 1; Lennox, No. 4 at p. 2; Ingersoll
Rand, No. 3 at p. 1; Goodman, No. 10
at p. 1; Rheem, No. 2 at p. 2; JCI, No.
5 at p. 2–3) These stakeholders, as well
as Mortex, clarified that other
combinations besides the HSVC,
including blower coil combinations, can
be rated through testing or using an
ARM. (Id.; Mortex, No. 6 at p. 1)
Stakeholders recommended language
identical to or similar to the following:
Split-system central air conditioners with
single-speed compressors must be tested and
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rated using a coil-only for the HSVC. 10 CFR
429.16(a)(2)(ii). Such single-speed systems
may be rated with other coil-only and blower
coil indoor units through the use of a DOE
approved ARM or by testing. 10 CFR
429.16(a)(2)(ii)(A) and 10 CFR
429.16(a)(2)(ii)(B). Furthermore, there is no
provision in the CFR permitting the use of a
blowercoil for testing and rating a
condensing unit with a single-speed
compressor for the HSVC, unless:
• [Version 1] the unit is a mini-split, multisplit or through-the-wall, OR
• [Version 2] the unit is sold and installed
only with blower-coil indoor units.
(Version 1: Docket No. EERE–2014–BT–
GUID–0033, Lennox, No. 4 at p. 2; Ingersoll
Rand, No. 3 at p. 2; Goodman, No. 10 at p.
3; Rheem, No. 2 at p. 3; JCI, No. 5 at p. 4;
Version 2: AHRI No. 8 at p. 3; Nordyne, No.
9 at p. 2)
AHRI and several manufacturers
disputed that when using a compressor
other than single speed, the HSVC can
never be a blower coil unless it is
exclusively used with a blower coil.
AHRI and the manufacturers reported
that many multi-stage capacity products
are tested and rated with high efficiency
blower coil or furnace products as the
HSVC even though those systems are
also rated for coil-only use. (Docket No.
EERE–2014–BT–GUID–0033, AHRI No.
8 at p. 2; Nordyne, No. 9 at p. 2; Lennox,
No. 4 at p. 2; Ingersoll Rand, No. 3 at
p. 2; Goodman, No. 10 at p. 2; Rheem,
No. 2 at p. 2; Carrier, No. 7 at p. 1)
Johnson Controls responded that they
test and rate multi-speed compressor
units with blower coils or furnace/coils
as the HSVC. (JCI, No. 5 at p. 3). AHRI
and the manufacturers reported that not
allowing this could limit the application
of high performing products, and that it
is important for units designed for
blower coil to also be rated as coil-only
to offer certain consumers a compromise
of cost and performance. AHRI and the
manufacturers proposed the following
modified language:
Split-system central air conditioners other
than those with single-speed compressors
(two-stage or multi-stage) may be tested and
rated using a blower-coil only as HSVC only
if the condensing unit design intent is for use
with a blower-coil indoor unit (e.g. the
evaporator coil that is likely to have the
largest volume of retails sales with the
particular model of condensing unit is a
blower-coil).
(Docket No. EERE–2014–BT–GUID–0033,
AHRI No. 8 at p. 3; Nordyne, No. 9 at p. 2;
Lennox, No. 4 at p. 3; Ingersoll Rand, No. 3
at p. 2; Goodman, No. 10 at p. 3; Rheem, No.
2 at p. 3; JCI, No. 5 at p. 4; Carrier, No. 7 at
p. 2 with slightly different language)
After reviewing the comments, DOE
proposes to make changes to 10 CFR
429.16 to revise the testing and rating
requirements for single-split-system air
conditioners. (See section III.F.4
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regarding discussion of new definitions
including ‘‘single-split-system.’’) These
changes will occur in two phases. In the
first phase, prior to the compliance date
of any amended energy conservation
standards, DOE proposes only a slight
change to the current requirements.
Specifically, DOE proposes that for
single-split-system air conditioners with
single capacity condensing units, each
model of outdoor unit must be tested
with the model of coil-only indoor unit
that is likely to have the largest volume
of retail sales with the particular model
of outdoor unit. For split-system air
conditioners with other than single
capacity condensing units each model
of outdoor unit must also be tested with
the model of coil-only indoor unit likely
to have the largest sales volume unless
the model of outdoor unit is sold only
with model(s) of blower coil indoor
units, in which case it must be tested
and rated with the model of blower coil
indoor unit likely to have the highest
sales volume. However, any other
combination may be rated through
testing or use of an AEDM. (See section
III.B regarding proposed changes from
ARM to AEDM.) Therefore, both single
capacity and other than single capacity
systems may be rated with models of
both coil-only or blower coil indoor
units, but if the system is sold with a
model of coil-only indoor unit, it must,
at a minimum, be tested in that
combination.
In the second phase, DOE anticipates
that any amended energy conservation
standards will be based on blower coil
ratings. Therefore, DOE proposes that all
single-split-system air conditioner basic
models be tested and rated with the
model of blower coil indoor unit likely
to have the largest volume of retail sales
with that model of outdoor unit.
Manufacturers would be required to also
rate all other blower coil and coil-only
combinations within the basic model
but would be permitted do so through
testing or an AEDM. DOE believes that
this proposal will offer the benefits of
design for high performance through the
use of blower coils as well as providing
appropriate representations for coil-only
combinations. In addition, given that
most basic models are currently
submitted as blower coil ratings, this
change will align DOE requirements
with industry practice. This proposed
change would also be accounted for in
the parallel energy conservation
standards rulemaking, and is contingent
upon any proposed amended standards
being based on blower coil ratings.
Table III.1 summarizes these proposed
changes.
TABLE III.1—TEST REQUIREMENTS FOR SINGLE-SPLIT-SYSTEM NON-SPACE-CONSTRAINED AIR CONDITIONERS RATED BY
OUMS
Date
Equipment type
Before the compliance date
for any amended energy
conservation standards.
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After the compliance date
for any amended energy
conservation standards.
Must test each:
With:
Split-System AC with single capacity condensing
unit.
Split-System AC with other
than single capacity condensing unit.
Model of Outdoor Unit .......
Split-system AC .................
Model of Outdoor Unit .......
The model of coil-only indoor unit that is likely to have
the largest volume of retail sales with the particular
model of outdoor unit.
The model of coil-only indoor unit that is likely to have
the largest volume of retail sales with the particular
model of outdoor unit, unless the model of outdoor
unit is only sold with model(s) of blower coil indoor
units in which case, the model of blower coil indoor
unit that is likely to have the largest volume of retail
sales with the particular model of outdoor unit.
The model of blower coil indoor unit that is likely to
have the largest volume of retail sales with the particular model of outdoor unit.
In order to facilitate these changes,
DOE also proposes definitions of blower
coil indoor unit and coil-only indoor
unit:
• Blower coil indoor unit means the
indoor unit of a split-system central air
conditioner or heat pump that includes
a refrigerant-to-air heat exchanger coil,
may include a cooling-mode expansion
device, and includes either an indoor
blower housed with the coil or a
separate designated air mover such as a
furnace or a modular blower (as defined
in Appendix AA).
• Blower coil system refers to a splitsystem that includes one or more blower
coil indoor units.
• Coil-only indoor unit means the
indoor unit of a split-system central air
conditioner or heat pump that includes
a refrigerant-to-air heat exchanger coil
and may include a cooling-mode
expansion device, but does not include
an indoor blower housed with the coil,
and does not include a separate
designated air mover such as a furnace
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Model of Outdoor Unit .......
or a modular blower (as defined in
Appendix AA). A coil-only indoor unit
is designed to use a separately-installed
furnace or a modular blower for indoor
air movement.
• Coil-only system refers to a system
that includes one or more coil-only
indoor units.
DOE notes that these proposed testing
requirements, when combined with the
proposed definition for basic model,
require that each basic model have at
least one rating determined through
testing; no basic model can be rated
solely using an AEDM.
DOE also proposes that in the
certification report, manufacturers state
whether each rating is for a coil-only or
blower coil combination.
DOE seeks comment on its proposed
changes to the determination of certified
ratings for single-split-system air
conditioners when rated by an OUM, as
well as on the proposed definitions for
blower coil and coil-only indoor units.
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b. Split-System Heat Pumps and SpaceConstrained Split Systems
The current requirements for splitsystem heat pumps in 10 CFR 429.16
require testing a condenser-evaporator
coil combination with the evaporator
coil likely to have the largest volume of
retail sales with the particular model of
condensing unit. The coil-only
requirement does not apply to splitsystem heat pumps, because central heat
pump indoor units nearly always
include both a coil and a fan.
In this notice, DOE proposes to
slightly modify the wording explaining
this requirement; specifically, the
requirement would use the more general
terms ‘‘indoor unit’’ and ‘‘outdoor unit,’’
rather than ‘‘evaporator coil’’ and
‘‘condensing unit,’’ since the
requirement addresses heat pumps. DOE
also proposes to apply this same test
requirement to space-constrained splitsystem air conditioners and heat pumps.
The current requirements in 10 CFR
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429.16 do not specifically call out
space-constrained systems, and as such,
the current coil-only requirements for
split-system air conditioners apply to
space-constrained split-system air
conditioners. Therefore, this proposal
will change test procedures for spaceconstrained split-system air
conditioners but will not change, other
than in nomenclature, the test
procedures for space-constrained splitsystem heat pumps.
c. Multi-Split, Multi-Circuit, and SingleZone-Multiple-Coil Units
The current requirements in 10 CFR
429.16(a)(2)(ii) specify that multi-split
systems and mini-split systems
designed to always be installed with
more than one indoor unit (now
proposed to be called single-zonemultiple-coil units, see section III.F.4)
be tested using a ‘‘tested combination’’
as defined in 10 CFR 430.2. For multisplit systems, each model of condensing
unit currently must be tested with a
non-ducted tested combination and a
ducted tested combination.
Furthermore, current requirements for
testing with a coil-only indoor unit do
not apply to mini-splits or multi-splits,
as the general use of these terms in the
industry refers to specific types of
systems with blower coil indoor units.
Id.
The current requirements also state
that for other multi-split systems that
combination’’ composed entirely of
short-ducted indoor units would be
required to be tested. DOE also proposes
the manufacturers may rate a mixed
non-ducted/short-ducted combination
as the mean of the represented values
for the tested non-ducted and shortducted combinations.
Under the proposed definition of
basic model, these three combinations
(non-ducted, short-ducted, and mixed)
would represent a single basic model.
When certifying the basic model,
manufacturers should report ‘‘* * *’’
for the indoor unit model number, and
report the test sample size as the total
of all the units tested for the basic
model, not just the units tested for each
combination. For example, if the
manufacturer tests 2 units of a nonducted combination and 2 units of a
short-ducted combination, and also
rates a mix-match combination, the
manufacturer should specify ‘‘4’’ as the
test sample size for the basic model,
while providing the rating for each
combination. DOE also proposes that
manufacturers be allowed to test and
rate specific individual combinations as
separate basic models, even if they share
the same model of outdoor unit. In this
case, the manufacturer must provide the
individual model numbers for the
indoor units rather than stating
‘‘* * *’’. Table III.2 provides an
example of both situations.
include the same model of condensing
unit but a different set of evaporator
coils, whether the evaporator coil(s) are
manufactured by the same manufacturer
or by a component manufacturer (i.e.,
ICM), the rating must be: (1) Set equal
to the rating for the non-ducted indoor
unit system tested (for systems
composed entirely of non-ducted units),
(2) set equal to the rating for the ducted
indoor unit system tested (for systems
composed entirely of ducted units), or
(3) set equal to the mean of the values
for the two systems (for systems having
a mix of non-ducted and ducted indoor
units). (10 CFR 429.16(a)(2)(ii))
In this notice, DOE proposes a slight
modification to the testing requirements
for single-zone-multiple-coil and multisplit systems, and adds similar
requirements for testing multi-circuit
systems (see section III.C.2 for more
information about these systems). DOE
also clarifies that these requirements
apply to VRF systems that are singlephase and less than 65,000 Btu/h (see
section III.A.3.c for more details). For all
multi-split, multi-circuit, and singlezone-multiple-coil split systems, DOE
proposes that at a minimum, each
model of outdoor unit must be tested as
part of a tested combination (as defined
in the CFR) composed entirely of nonducted indoor units. For any models of
outdoor units also sold with shortducted indoor units, a second ‘‘tested
TABLE III.2—EXAMPLE RATINGS FOR MULTI-SPLIT SYSTEMS
Individual model
(outdoor unit)
Individual model
(indoor unit)
ABC ..............................
ABC1 ............................
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Basic model
ABC .............................
ABC .............................
* * * ............................
2–A123; 3–JH746 .......
DOE requests comment on whether
additional requirements are necessary
for multi-split systems paired with
models of conventional ducted indoor
units rather than short-duct indoor
units.
DOE also notes that the test procedure
currently allows testing of only nonducted or short-ducted systems, and not
combinations of the two. Therefore to
rate individual mix-match
combinations, manufacturers would
have to test 4 units—2 ducted and 2
short-ducted. DOE requests comment on
whether manufacturers should have the
ability to test mix-match systems using
the test procedure rather than rating
them using an average of the other
tested systems. DOE also requests
comment on whether manufacturers
should be able to rate mix-match
systems using other than a straight
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Sample size
Ducted rating
4
2
14
........................
average, such as a weighting by the
number of non-ducted or short-ducted
units. Finally, DOE requests comment
on whether the definition of ‘‘tested
combination’’ is appropriate for rating
specific individual combinations, or
whether manufacturers should be given
more flexibility, such as testing with
more than 5 indoor units.
In reviewing the market for multi-split
systems, DOE determined that some are
sold by OUMs with only models of
small-duct, high velocity (SDHV) indoor
units, or with a mix of models of shortduct and SDHV units. (See section
III.F.2 regarding the proposed definition
of short ducted systems.) These kinds of
units are not currently explicitly
addressed in DOE’s test requirements.
Therefore, DOE proposes to add a
requirement that for any models of
outdoor units also sold with models of
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Non-ducted
rating
15
17
Mix rating
14.5
........................
SDHV indoor units, a ‘‘tested
combination’’ composed entirely of
SDHV indoor units must be used for
testing and rating. However, such a
system must be certified as a different
basic model.
DOE notes that multi-split systems
consisting of a model of outdoor unit
paired with models of non-ducted or
short-ducted units must meet the energy
conservation standards for split-system
air conditioners or heat pumps, while
systems consisting of a model of
outdoor unit paired with models of
small-duct, high-velocity indoor units
must meet SDHV standards. DOE
proposes to add a limitations section in
429.16 that would require models of
outdoor units that are rated and
distributed in combinations that span
multiple product classes to be tested
and certified as compliant with the
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applicable standard for each product
class. Even if a manufacturer sells a
combination including models of both
SDHV and other non-ducted or shortducted indoor units, DOE proposes that
the manufacturer may not provide a
mix-match rating for such combinations.
DOE requests comment on whether
manufacturers would want to rate such
combinations, and if so, how they
would prefer to rate them (i.e., by by
taking the mean of a sample of tested
non-ducted units and a sample of tested
SDHV units or by testing a combination
on non-ducted and SDHV units), and
whether the SDHV or split-system
standard would be most appropriate.
DOE understands that manufacturers
of multi-split systems commonly only
test one sample rather than complying
with the sampling plan requirements in
429.16(a)(2)(i), which require a sample
of two. DOE may consider moving
toward a single unit sample for singlezone multiple-coil and multi-split
system models, but in order to do so,
DOE requires information on
manufacturing and testing variability
associated with these systems. In
particular, DOE requires data to allow it
to understand how a single unit sample
may be representative of the population.
DOE also requests information on what
tolerances would need to be applied to
the ratings of these units based on a
single unit sample in order to account
for the variability.
d. Basic Models Rated by ICMs
The current requirements in 10 CFR
429.16(a) require that each condensing
unit of a split system must be tested
using the HSVC associated with that
condensing unit. There are no current
requirements for testing each model of
indoor unit of a split system. Non-HSVC
combinations can be rated using an
ARM, assuming the condensing unit of
the combination has a separate HSVC
rating based on testing. DOE
understands that ICMs typically do not
test all of their models of indoor units,
but rather use OUM test data for outdoor
units to generate ratings for their
models. (See section III.B on AEDMs for
further information.) In this notice, DOE
proposes that ICMs must test and
provide certified ratings for each model
of indoor unit (i.e., basic model) with
the least-efficient model of outdoor unit
with which it will be paired, where the
least- efficient model of outdoor unit is
the outdoor unit in the lowest-SEER
combination as certified by the OUM. If
more than one model of outdoor unit
(with which the ICM wishes to rate the
model of indoor unit) has the same
lowest-SEER rating, the ICM may select
one for testing purposes. This applies to
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both conventional (i.e., non-short-duct,
non-SDHV) split-systems and SDHV
systems. ICMs must rate all other
individual combinations of the same
model of indoor unit, but may
determine those ratings through testing
or use of an AEDM.
DOE understands that this proposal
would increase test burden for ICMs
beyond the testing they currently
conduct to meet ARM validation
requirements. However, DOE believes
this burden is outweighed by the benefit
of providing more accurate ratings for
models of indoor units sold by ICMs.
Additional discussion regarding
potential test requirements for ICMs can
be found in the stakeholder comments
regarding AEDMs in section III.B.5.
DOE understands that the proposed
definition of basic model for an ICM,
including what constitutes the ‘‘same’’
model of indoor unit and thus would be
required to be tested, is important for
accurately assessing the test burden for
manufacturers as a result of this test
proposal. DOE seeks comment on the
basic model definition in section III.A.1.
DOE also seeks comment on the
proposed testing requirements for ICMs.
e. Single-Package Systems
In the current regulations, 10 CFR
429.16(a)(2)(i) states that each singlepackage system a must have a sample of
sufficient size tested in accordance with
the applicable provisions of Subpart B.
In this notice, DOE proposes that the
lowest SEER individual model within
each basic model must be tested. DOE
expects that in most cases, each singlepackage system will represent its own
basic model. However, based on the
proposal for the definition of basic
model in section III.A.1, this may not
always be the case. DOE notes that
regardless, AEDMs do not apply to
single-package models—manufacturers
may either test and rate each individual
single-package model, or if multiple
individual models are assigned to the
same basic model per the proposed
requirements in the basic model
definition, the manufacturer would be
required to test only the lowest SEER
individual model within the basic
model and use that to determine the
rating for the basic model.
DOE requests comment on the
likelihood of multiple individual
models of single-package units meeting
the requirements proposed in the basic
model definition to be assigned to the
same basic model. DOE also requests
comment on whether, if manufacturers
are able to assign multiple individual
models to a single basic model,
manufacturers would want to use an
AEDM to rate other individual models
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within the same basic model other than
the lowest SEER individual model.
Finally, DOE requests comment on
whether manufacturers would want to
employ an AEDM to rate the off-mode
power consumption for other variations
of off-mode associated with the basic
model other than the variation tested.
DOE also proposes to specify this
same requirement for space-constrained
single-package air conditioners and heat
pumps, which are currently not
explicitly identified in the test
requirement section.
f. Replacement Coils
DOE stated in the August 20 Guidance
that an individual condensing unit or
coil must meet the current Federal
standard (National or regional) when
paired with the appropriate other new
part to make a system when tested in
accordance with the DOE test procedure
and sampling plan.
In response, AHRI and manufacturers
commented that they believed the intent
of the guidance was to clarify how the
outdoor section of a split system used in
a replacement situation can be tested
and rated to meet the appropriate
efficiency requirements. However, they
felt this language should not apply to
the indoor coil. AHRI stated that indoor
coil is rarely changed and when it is,
such as for an irreparable leak, it
requires an exact replacement. In
addition, they note that warranties can
extend up to 10 years. Commenters also
expressed the view that the guidance
would not result in an improvement to
installed product efficiency. (Docket No.
EERE–2014–BT–GUID–0032, AHRI, No.
8 at pp. 2–3; Rheem, No. 2 at p. 3;
Goodman, No. 10 at pp. 2–3; Ingersoll
Rand, No. 3 at p. 2; Lennox, No. 4 at p.
2; Nordyne, No. 9 at p. 2) AHRI and the
manufacturers recommended removing
indoor coils from the draft guidance
language on replacement. (Id.; JCI, No.
5 at p. 6)
Johnson Controls added further detail
that using the term coil does not
differentiate between service parts
(listed with part numbers) and finished
component assemblies (listed as a coil
model) or between evaporator coils and
condenser coils. Johnson Controls
added that replacement parts cannot be
rated as a finished coil assembly
because the replacement parts do not
contain sheet metal parts required to
complete the installation. They also
added that where the physical
characteristics of an evaporator coil are
significantly different when compared
to a new system, replacing the old
evaporator coil with a new coil model
rather than a replacement part could
result in increased cost and reduced
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performance, reliability, and comfort.
(Docket No. EERE–2014–BT–GUID–
0032, JCI, No. 5 at pp. 4–6)
Mortex also commented that
replacement with a different evaporator
coil design and size could lead to issues
of fitting or size constraint problems and
refrigerant metering and charging
differences. The end result (if design air
volume rate is hampered and refrigerant
circuit performance is modified) could
lead to less efficiency than the prefailure situation. (Docket No. EERE–
2014–BT–GUID–0032, Mortex, No. 6 at
p. 1)
DOE also notes that the ASRAC
regional standards enforcement Working
Group agreed that manufacturers do not
need to keep track of components
including uncased coils. (Docket No.
EERE–2011–BT–CE–0077–0070,
Attachment)
In consideration of the comments and
the Working Group proposals, DOE
notes that its proposed definition of
‘‘indoor unit’’ refers to the box rather
than just a coil. Accordingly, legacy
indoor coil replacements and uncased
coils would not meet the definition of
indoor unit. Furthermore, by defining
air conditioners and heat pumps as
consisting of a single-package unit, an
outdoor unit and one or more indoor
units, an indoor unit only, or an outdoor
unit only, legacy indoor coil
replacements and uncased coils would
not meet the definition of a central air
conditioner or heat pump. Hence, they
would not need to be tested or certified
as meeting the standard.
g. Outdoor Units With No Match
For split-system central air
conditioners and heat pumps, current
DOE regulations require that
manufacturers test the condensing unit
and ‘‘the evaporator coil that is likely to
have the largest volume of retail sales
with the particular model of condensing
unit’’ (commonly referred to as the
highest sales volume combination). 10
CFR 4429.16(a)(2)(ii). Effective January
1, 2010, the U.S. Environmental
Protection Agency (EPA) banned the
sale and distribution of those central air
conditioning systems and heat pump
systems that are designed to use HCFC–
22 refrigerant. 74 FR 66450 (Dec. 15,
2009). EPA’s rulemaking included an
exception for the manufacture and
importation of replacement
components, as long as those
components are not pre-charged with
HCFC–22. Id. at 66459–60.
Because complete HCFC–22 systems
can no longer be distributed,
manufacturers inquired how to test and
rate individual components—because
these components are sold separately,
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there are no highest sales volume
combinations. Because the EPA
prohibits distribution of new HCFC–22
condensing unit and coil combinations
(i.e., complete systems), there is no such
thing as a HSVC, and hence, testing and
rating of new HCFC–22 combinations
cannot be conducted using the existing
test procedure.
DOE expects that the HCFC–22 indoor
and outdoor units remaining on the
market are part of legacy offerings that
were initially sold five or more years
ago. These components of HCFC–22
systems were in production for sale as
part of matched systems before the EPA
regulations became effective on January
1, 2010. While EPA’s rulemaking bans
the sale of HCFC–22 systems that are
charged with refrigerant while allowing
sale of uncharged components of such
systems, EPA’s rule has no effect on the
efficiency rating of these systems or on
requirements for DOE efficiency
standards that they must meet. The DOE
test procedure used prior to January 15,
2010 that would have been used to rate
these systems is no longer valid, thus
these ratings can no longer be used as
the basis for representing their
efficiency. The individual indoor coils
and outdoor units of such systems that
could potentially meet the current
standard may continue to be
manufactured only if the manufacturer
uses a valid test procedure to ensure
compliance (i.e., to certify compliance)
and for representations.
Generally, when a model cannot be
tested in accordance with the DOE test
procedure, manufacturers must submit a
petition for a test procedure waiver for
DOE to assign an alternative test
method. 10 CFR 430.27(a)(1) Instead,
DOE proposes in this notice a test
procedure that may be used for rating
and certifying the compliance of these
outdoor units. DOE proposes in this
notice to specify coil characteristics that
should be used when testing models of
outdoor units that do not have a HSVC.
Specifically, these requirements include
limitations on coil tube geometries and
dimensions and coil fin surface area.
These outdoor unit models, when tested
with the specified indoor units, must
meet applicable Federal standards. (See
section III.A.4 for more information on
compliance.) This proposal is consistent
with the regional standards enforcement
Working Group recommendation that a
person cannot install a replacement
outdoor unit unless it is certified as part
of a combination that meets the
applicable standard. (Docket No. EERE–
2011–BT–CE–0077–0070, Attachment)
The new test procedure would be
effective (i.e., allowed for use for such
certifications) 30 days after it is
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finalized and would be required for use
for such systems (i.e., rather than any
granted waiver test procedure)
beginning 180 days after it is finalized.
In response to the August 20, 2014
draft guidance document, Carrier
requested clarification that the finalized
guidance would replace DOE’s draft
guidance document issued on January 1,
2012, regarding central air conditioning
systems and air conditioning heat pump
systems that are designed to use dry R–
22 condensing units. (Docket No. EERE–
2014–BT–GUID–0032, Carrier, No. 7 at
p. 2) If finalized, this proposed test
procedure would replace both the 2012
guidance document for dry R–22 units
as well as the 2014 draft guidance
document on unit selection regarding
condensing units for replacement
applications.
4. Compliance With Federal (National or
Regional) Standards
In the August 20, 2014 draft guidance
document (EERE–2014–BT–GUID–
0032), DOE discussed whether each
basic model of split-system air
conditioner or heat pump has to meet
the applicable standard. DOE stated that
compliance with standards is based on
the statistical concept that an entire
population of units (where ‘‘unit’’ refers
to a complete system) of a basic model
must meet the standard, recognizing
that efficiency measurements for some
units may be better or worse than the
standard due to manufacturing or
testing variation. Manufacturers apply
the statistical formulae in 10 CFR 429.16
to demonstrate compliance, and DOE
applies the statistical formulae in 10
CFR part 429, subpart C, Appendix A to
determine compliance.
Further, DOE stated that the only
condensing units and coils that may be
installed in the region are those that can
meet the regional standard when tested
and rated as a new system in accordance
with the test procedure and sampling
plan as described above.
In response, AHRI and several
manufacturers recommended the
following additions to DOE’s statements
regarding compliance:
‘‘Compliance with national or regional
standards is based on the statistical concept
that an entire population of units (where
‘‘unit’’ refers to a complete system) of a basic
model including Highest Sales Volume
Tested Combination and all other
combinations must meet the standard,
recognizing that some individual units may
perform slightly better or worse than the
design due to manufacturing or testing
variation.’’
(Docket No. EERE–2014–BT–GUID–0032,
AHRI, No. 8 at p. 2; Rheem, No. 2 at p. 2;
Goodman, No. 10 at p. 2; Ingersoll Rand, No.
3 at p. 1; Lennox, No. 4 at p. 2; Nordyne, No.
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9 at pp. 1–2; JCI, No. 5 at p. 3; Carrier, No.
7 at p. 6)
In addition, Carrier commented that
with respect to the discussion about
selection of units for testing, the HSVC
should be determined for the applicable
region. (Docket No. EERE–2014–BT–
GUID–0032, Carrier, No. 7 at p. 4)
AHRI and several manufacturers
recommended the following addition to
the paragraph on condensing units sold
as replacements:
‘‘In summary, DOE interprets for the
regional standard to require that the least
efficient rating combination for a specified
model of condensing unit must be 14 SEER
with a coil only rating where 14 SEER is the
regional standard. Any model that has a
certified combination below the regional
standard cannot be installed in the region.
This interpretation of the regional standard
also applies to units shipped without
refrigerant charge.’’
(Docket No. EERE–2014–BT–GUID–0032,
AHRI, No. 8 at p. 2; Rheem, No. 2 at p. 3;
Goodman, No. 10 at p. 3; Ingersoll Rand, No.
3 at p. 3; Lennox, No. 4 at p. 3; Nordyne, No.
9 at pp. 2–3; JCI, No. 5 at p. 6)
Carrier provided slightly different
recommended language:
‘‘Given the different Federal standards,
National and regional, the least efficient
rating combination for a specified model of
condensing unit must: (i) in the regions
where the regional standard applies, be rated
and certified on as performing at or above the
current regional standard with a coil only
rating; and (ii) where the National standard
applies, be rated and certified as performing
at or above the current National standard
with a coil only rating. For purposes of
clarity, any basic model that has a certified
Basic model
AB12
AB12
AB12
CD13
CD13
CD13
EF12
EF12
EF12
combination below the current regional
standard cannot be installed in the region.
This interpretation also applies to dry
condensing units.’’ (Docket No. EERE–2014–
BT–GUID–0032, Carrier, No. 7 at pp. 1–2)
In contrast, Carrier also suggested that
the guidance document discussion of
unit selection and basic models should
replace references to ‘‘Federal standard’’
with ‘‘Federal (national or regional)
standard’’. (Carrier, No. 7 at pp. 4–5)
The regional standards enforcement
Working Group suggested the regional
standards required clarification because
a particular condensing unit may have
a range of efficiency ratings when paired
with various indoor evaporator coils
and/or blowers. The Working Group
provided the following four
recommendations to clarify the regional
standards: That (1) the least-efficient
rated combination for a specified model
of condensing unit must be 14 SEER for
models installed in the Southeast and
Southwest regions; (2) the least-efficient
rated combination for a specified model
of condensing unit must meet the
minimum EER for models installed in
the Southwest region; (3) any
condensing unit model that has a
certified combination that is below the
regional standard(s) cannot be installed
in that region; and (4) a condensing unit
model certified below a regional
standard by the original equipment
manufacturer cannot be installed in a
region subject to a regional standard(s)
even with an independent coil
manufacturer’s indoor coil or air
handler combination that may have a
certified rating meeting the applicable
regional standard(s). (Docket No. EERE–
2011–BT–CE–0077–0070, Attachment)
After reviewing stakeholder
comments and the Working Group
report, DOE agrees that all individual
models or combinations within a basic
model must meet the applicable
national or regional standard. DOE
proposes to add requirements to the
relevant provisions of section 430.32
that the least-efficient combination of
each basic model must comply with the
regional SEER and EER standards.
In addition, as noted in section
III.A.1, DOE proposes that if any
individual combination within a basic
model fails to meet the standard, the
entire basic model (i.e., model of
outdoor unit) must be removed from the
market. In order to clarify the
limitations on sales of models of
outdoor units across regions with
different standards, DOE proposes to
add a limitation in section 429.16 that
any model of outdoor unit that is
certified in a combination that does not
meet all regional standards cannot also
be certified in a combination that meets
the regional standard(s). Outdoor unit
model numbers cannot span regions
unless the model of outdoor unit is
compliant with all standards in all
possible combinations. If a model of
outdoor unit is certified below a
regional standard, then it must have a
unique individual model number for
distribution in each region. For
example:
Certified rating
(SEER/EER)
Individual model # (outdoor unit)
.................
.................
.................
.................
.................
.................
.................
.................
.................
Individual model # (indoor unit)
ABC**#**-*** ...............................................
ABC**#**-*** ...............................................
ABC**#**-*** ...............................................
CDESO**-*#* ..............................................
CDESW**-*#* .............................................
CDEN***-*#* ...............................................
EFCS**#**-*** .............................................
EFCS**#**-*** .............................................
EFCN**#**-*** .............................................
SO123 ........................................................
SW123 ........................................................
N123 ...........................................................
SO123 ........................................................
SW123 ........................................................
N123 ...........................................................
SO123 ........................................................
SW123 ........................................................
N123 ...........................................................
5. Certification Reports
To maximize test repeatability and
reproducibility for assessment and
enforcement testing, DOE proposes to
amend the certification reporting
requirements.
Permitted?
14.5/12.0
15.0/12.8
13.9/11.7
14.5/12.0
15.0/12.8
13.9/11.7
14.5/12.2
14.6/12.4
13.9/11.7
NO.
YES.
YES.
DOE proposes to clarify what basic
model number and individual model
numbers must be reported for central air
conditioners and heat pumps:
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Individual model number(s)
Equipment type
Basic model number
1
Single Package .............................
Split System (rated by OUM) .......
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Number unique
model.
Number unique
model.
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2
3
to
the
basic
Package ............
N/A ....................
N/A.
to
the
basic
Outdoor Unit .....
Indoor Unit(s) ....
Air Mover (or N/A if rating coilonly system or fan is part of indoor unit model number).
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Individual model number(s)
Equipment type
Basic model number
1
Outdoor Unit Only .........................
Split-System or SDHV (rated by
ICM).
Number unique
model.
Number unique
model.
Each basic model number must be
unique in some way so that all
individual models or combinations
within the same basic model can be
identified.
DOE also proposes to require productspecific information at 10 CFR
429.16(c)(4) that is not public and will
not be displayed in DOE’s database.
Several proposed requirements are
addressed in the remainder of this
notice in response to comments on
specific issues or in relation to test
procedure changes. In addition, several
other requirements are discussed in this
section.
In order for DOE to replicate the test
setup for its assessment tests, DOE
proposes that manufacturers that wish
to certify multi-split, multiple-circuit,
and single-zone-multiple-coil systems
report the number of indoor units tested
with the outdoor unit, the nominal
cooling capacity of each indoor unit and
outdoor unit, and the indoor units that
are not providing heating or cooling for
part-load tests. Manufacturers that wish
to certify systems that operate with
multiple indoor fans within a single
indoor unit shall report the number of
indoor fans; the nominal cooling
capacity of the indoor unit and outdoor
unit; which fan(s) are operating to attain
the full-load air volume rate when
controls limit the simultaneous
operation of all fans within the single
indoor unit; and the allocation of the
full-load air volume rate to each
operational fan when different capacity
blowers are connected to the common
duct.
Similarly, DOE proposes that for those
models of indoor units designed for
2
3
to
the
basic
Outdoor Unit .....
N/A ....................
N/A.
to
the
basic
Outdoor Unit .....
Indoor Unit(s) ....
N/A.
both horizontal and vertical installation
or for both up-flow and down-flow
vertical installations, the orientation
used during certification testing shall be
included on the certification test
reports.
DOE also proposes that the maximum
time between defrosts as allowed by the
controls be included on the certification
test reports. For units with timeadaptive defrost control, the frosting
interval used during the Frost
Accumulation tests and the associated
procedure for manually initiating
defrost at the specified time, if
applicable, should also be included on
the certification test reports.
DOE also proposes that for variablespeed units, the compressor frequency
set points and the required dip switch/
control settings for step or variable
components should be included. For
variable-speed heat pumps, DOE
proposes that manufacturers report
whether the unit controls restrict use of
minimum compressor speed operation
for some range of operating ambient
conditions, whether the unit controls
restrict use of maximum compressor
speed operation for any ambient
temperatures below 17 °F, and whether
the optional H42 low temperature test
was used to characterize performance at
temperatures below 17 °F.
Finally, DOE proposes that
manufactures report air volume rates
and airflow-control settings.
DOE recognizes that additional
reporting requirements in certification
test reports increases reporting burden
because manufacturers must spend
additional time to add such content to
the report. However, DOE believes that
a knowledgeable person in the field
would not find the additional
information difficult to provide and
could do so in a reasonable amount of
time. Thus, DOE does not believe that
the added reporting requirements are
significantly burdensome to warrant
excluding them. DOE requests comment
on this issue.
6. Represented Values
DOE proposes to make several
additions to the represented value
requirements in 10 CFR 429.16. First,
DOE proposes to add a requirement that
the represented value of cooling
capacity, heating capacity, and sensible
heat ratio (SHR) shall be the mean of the
values measured for the sample.
Second, DOE proposes to move the
provisions currently in 10 CFR 430.23
regarding calculations of various
measures of energy efficiency and
consumption for central air conditioners
to 10 CFR 429.16. Specifically, while
Part 430 would refer to the test
procedure appendix and section therein
to use for each metric and the rounding
requirements for test results of
individual units, Part 429 would refer to
how to calculate annual operating cost
for the sample based on represented
values of cooling capacity and SEER,
and how to round the represented
values based on the sample for other
measures of energy efficiency and
consumption. DOE proposes minor
changes to the calculations of annual
operating cost to address changes
proposed in Appendix M and M1. Table
III.3 shows the proposed rounding
requirements for each section. DOE
requests comment on these values.
TABLE III.3—ROUNDING PROPOSALS
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Measure
10 CFR 430.23
(one unit)
Cooling capacity/heating capacity:
<20,000 Btu/h .............................................
≥20,000 Btu/h and <38,000 Btu/h ..............
≥38,000 Btu/h and <65,000 Btu/h ..............
Annual operating cost ........................................
EER/SEER/HSPF/APF ......................................
Off-mode power consumption ...........................
Sensible heat ratio .............................................
nearest 50 Btu/h ...............................................
nearest 100 Btu/h .............................................
nearest 250 Btu/h .............................................
N/A ....................................................................
nearest 0.025 ...................................................
nearest 0.5 watt ................................................
nearest 0.5% ....................................................
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10 CFR 429.16
(sample)
nearest
nearest
nearest
nearest
nearest
nearest
nearest
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100 Btu/h.
200 Btu/h.
500 Btu/h
dollar per year.
0.05.
watt.
percent (%).
09NOP2
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7. Product-Specific Enforcement
Provisions
DOE proposes to verify during
assessment or enforcement testing the
cooling capacity certified for each basic
model or individual combination. DOE
proposes to measure the cooling
capacity of each tested unit pursuant to
the test requirements of 10 CFR part
430. The results of the measurement(s)
will be compared to the value of cooling
capacity certified by the manufacturer.
If the measurement is within five
percent of the certified cooling capacity,
DOE will use the certified cooling
capacity as the basis for determining
SEER. Otherwise, DOE will use the
measured cooling capacity as the basis
for determining SEER.
DOE also proposes to require
manufacturers to report the cyclic
degradation coefficient (CD) value used
to determine efficiency ratings. In this
proposal, DOE would run CD testing as
part of any assessment or verification
testing, except when testing an outdoor
unit with no match. If the measurement
is 0.02 or more greater than the certified
value, DOE would use the measurement
as the basis for calculation of SEER or
HSPF. Otherwise, DOE would use the
certified value. For models of outdoor
units with no match, DOE would always
use the default value.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
B. Alternative Efficiency Determination
Methods
1. General Background
For certain consumer products and
commercial equipment, DOE’s existing
regulations allow the use of an
alternative efficiency determination
method (AEDM) or alternative rating
method (ARM), in lieu of actual testing,
to estimate the ratings of energy
consumption or efficiency of basic
models by simulating their energy
consumption or efficiency at the test
conditions required by the applicable
DOE test procedure. The simulation
method permitted by DOE for use in
rating split-system central air
conditioners and heat pumps, in
accordance with 10 CFR 429.70(e), is
referred to as an ARM. In contrast to an
AEDM, an ARM must be approved by
DOE prior to its use.
The simulation methods represented
by AEDMs or ARMs are computer
modeling or mathematical tools that
predict the performance of non-tested
individual or basic models. They are
derived from mathematical models and
engineering principles that govern the
energy efficiency and energy
consumption of a particular basic model
of covered product based on its design
characteristics. (In the context of this
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discussion, the term ‘‘covered product’’
applies both to consumer products and
commercial and industrial equipment
that are covered under EPCA.) These
computer modeling and mathematical
tools can provide a relatively
straightforward means to predict the
energy usage or efficiency
characteristics of an individual or basic
model of a given covered product and
reduce the burden and cost associated
with testing certain covered products
that are inherently difficult or expensive
to test. When properly developed, they
can predict the performance of a
product accurately enough to be
statistically representative under DOE’s
sampling requirements.
On April 18, 2011, DOE published a
Request for Information (AEDM RFI) in
the Federal Register. 76 FR 21673.
Through the AEDM RFI, DOE requested
suggestions, comments, and information
relating to the Department’s intent to
expand and revise its existing AEDM
and ARM requirements for consumer
products and commercial and industrial
equipment covered under EPCA. In
response to comments it received on the
AEDM RFI, DOE published a Notice of
Proposed Rulemaking (AEDM NOPR) in
the Federal Register on May 31, 2012.
77 FR 32038. DOE also held a public
meeting on June 5, 2012, to present
proposals in the AEDM NOPR and to
receive comments from stakeholders. In
the AEDM NOPR, DOE proposed the
elimination of ARMs, and the expansion
of AEDM applicability to those products
for which DOE allowed the use of an
ARM (i.e., split-system central air
conditioners and heat pumps). 77 FR at
32055. Furthermore, DOE proposed a
number of requirements that
manufacturers must meet in order to use
an AEDM as well as a method that DOE
would employ to determine if an AEDM
was used appropriately along with
specific consequences for misuse of an
AEDM. 77 FR at 32055–56.
The purpose of the AEDM rulemaking
was to establish a uniform, systematic,
and fair approach to the use of modeling
techniques that would enable DOE to
ensure that products in the marketplace
are correctly rated—irrespective of
whether they are rated based on
physical testing or modeling—without
unnecessarily burdening regulated
entities. DOE solicited suggestions,
comments, and information related to
its proposal and accepted written
comments on the AEDM NOPR through
July 2, 2012. DOE subsequently formed
a working group through the Appliance
Standards and Rulemaking Federal
Advisory Committee (ASRAC) (see the
Notice of Intent To Form the
Commercial HVAC, WH, and
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Refrigeration Certification Working
Group and Solicit Nominations To
Negotiate Commercial Certification
Requirements for Commercial HVAC,
WH, and Refrigeration Equipment,
published on March, 12, 2013, 78 FR
15653), which addressed revisions to
the AEDM requirements for commercial
and industrial equipment covered by
EPCA and resulted in the subsequent
publishing of a SNOPR on October 22,
2013 (78 FR 62472) and a final rule on
December 31, 2013 (78 FR 79579). In the
final rule, DOE made, among others
changes, revisions to pre-approval
requirements, validation requirements,
and DOE verification testing
requirements for the AEDM process for
commercial HVAC equipment.
In this notice, DOE proposes
modifications to the central air
conditioners and heat pump AEDM
requirements proposed in the AEDM
NOPR with consideration of the
comments received on the AEDM NOPR
specific to these products, as well as the
requirements implemented for
commercial HVAC equipment in the
December 2013 AEDM final rule.
2. Terminology
In the AEDM NOPR, DOE proposed to
eliminate the term ‘‘alternate rating
method’’ (ARM) and instead use the
term ‘‘alternative efficiency
determination method’’ (AEDM) to refer
to any modeling technique used to rate
and certify covered products. 77 FR
32038, 32040 (May 31, 2012). DOE
proposed to refer to any technique used
to model product performance as an
AEDM, but recognized that there are
product-specific considerations that
should be accounted for in the
development of an AEDM and thus, in
the proposed methodology for
validating product-specific AEDMs. Id.
DOE received a number of comments
in response to its proposal to solely
apply the term AEDM to any modeling
technique used to rate and certify
covered products. Bradford White
Corporation (Bradford White), United
Technologies Climate, Controls &
Security and ITS Carrier (UTC/Carrier),
and Nordyne, LLC (Nordyne) agreed
with DOE that one term should be used.
(Docket No. EERE–2011–BT–TP–0024,
Bradford White, No. 38 at p. 1; UTC/
Carrier, No. 56 at p. 1; Nordyne, No. 55
at p. 1) 8 AAON, Inc. (AAON) supported
8 Unless otherwise specified, further references in
this section (section III.B) to comments received by
DOE are to those associated with the AEDM
rulemaking (Docket No. EERE–2011–BT–TP–0024).
References to the public meeting are to the June 5,
2012 public meeting on the AEDM NOPR, the
transcript of which is in the AEDM rulemaking
docket.
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tkelley on DSK3SPTVN1PROD with PROPOSALS2
DOE’s proposal to combine
requirements for ARMs and AEDMs, but
did not differentiate between the
terminology and the methodological
changes proposed. (AAON, No. 40 at p.
2) DOE also received a number of
comments, both written and at the
public meeting, regarding the
differences in ARM and AEDM
methodology. Those comments are
discussed in section III.B.3 of this
document. In addition, DOE received
numerous comments regarding the
validation of AEDMs for different
product types, which are discussed in
section III.B.4 of this document.
In response to comments received,
DOE is continuing to propose the use of
one term, AEDM, to refer to all
modeling techniques used to develop
certified ratings of covered products.
DOE believes that since the two
methods are conceptually similar, the
use of one term is appropriate. DOE
would like to clarify that the use of one
term to refer to all modeling techniques
used to develop certified ratings of
covered products and equipment does
not indicate a uniform process or
requirements for their use across all
covered products, nor does it imply that
DOE will not include any of the current
ARM provisions as part of the proposed
AEDM provisions. Further, similar to
the differences between AEDMs for
distribution transformers and
commercial HVAC products, DOE
proposes validation requirements that
will account for the differences between
HVAC products and other covered
equipment.
3. Elimination of the Pre-Approval
Requirement
Under current regulations, ARMs
used by manufacturers of split-system
central air conditioners and central heat
pumps must be approved by the
Department before use. (10 CFR
429.70(e)(2)) Manufacturers who elect to
use an ARM to rate untested basic
models pursuant to 10 CFR
429.16(a)(2)(ii)(B)(1) must, among other
requirements, submit to the Department
full documentation of the rating method
including a description of the
methodology, complete test data on four
mixed systems per each ARM, and
product information on each indoor and
outdoor unit of those systems.
Furthermore, manufacturers are not
permitted to use the ARM as a rating
tool prior to receiving Departmental
approval.
In the AEDM RFI, DOE requested
comment on the necessity of a preapproval requirement for AEDMs and/or
ARMs. 76 FR 21673, 21674 (April 18,
2011). Based on the comments received
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in response to the AEDM RFI, DOE
perceived no benefit in the additional
burden imposed by a pre-approval
requirement and that a pre-approval
process could cause time-to-market
delays. Pursuant to those comments,
DOE proposed in the AEDM NOPR to
eliminate the pre-approval process
currently in place for central air
conditioner and heat pump ARMs. 77
FR 32038, 32040–41 (May 31, 2012).
DOE believed that this would reduce the
burden currently placed on
manufacturers by eliminating the timeto-market delays caused by completing
the necessary request for approval
before bringing products to market.
Furthermore, DOE believed that
elimination of the pre-approval
requirement would promote innovation
because an ARM would not need to be
approved or re-approved to account for
any changes in technology. Id.
In the AEDM NOPR, DOE sought
comment regarding its proposal to
eliminate the pre-approval requirement
for ARMs for central air conditioners
and heat pumps and received mixed
responses. Modine Manufacturing
Corporation (Modine) supported DOE’s
proposal to eliminate the pre-approval
requirement. (Modine, No. 42 at p. 1)
Lennox International, Inc. (Lennox) and
Unico, Inc. (Unico), however, suggested
that removal of the pre-approval
requirement could lead to incorrect
ratings and unfair competition in the
marketplace, which could negatively
impact consumers. (Lennox, No. 46 at p.
2; Unico, No. 54 at p. 2) Furthermore,
Johnson Controls, Inc. (JCI) commented
that it was particularly important that
manufacturers continue to be allowed to
use pre-approved ARMs because the
new AEDM provisions, by eliminating
pre-approval, introduce regulatory risk
that is not present under current ARM
requirements. (JCI, No. 66 at pp. 2)
Other interested parties specifically
recommended that participation in a
voluntary industry certification program
(VICP),9 or review of an AEDM or ARM
by a qualified engineer, could reduce or
eliminate the need for pre-approval.
AHRI, Rheem Manufacturing Company
(Rheem), Goodman Global, Inc.
(Goodman), and Unico suggested that
DOE should consider pre-approval for
manufacturers not participating in a
VICP, and that at a minimum, review by
a professional engineer should be
required. (AHRI, No. 61 at p. 2; Rheem,
No. 59 at p. 2; Goodman, No. 53 at p.
1; Unico, No. 54 at p. 5) Likewise,
9 A Voluntary Industry Certification Program, or
VICP, is an independent, third-party program that
conducts ongoing verification testing of members’
products.
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Lennox agreed that if DOE does not
maintain pre-approval in general, it
could still require pre-approval for those
who do not participate in a VICP .
(Lennox, No. 46 at pp. 2 and 4) Lennox
and Rheem commented that a preapproval requirement for manufacturers
who do not participate in a VICP could
protect consumers from unsubstantiated
ratings. (Rheem, No. 59 at p. 2; Lennox,
No. 46 at p. 2)
DOE does not agree with JCI’s
suggestion that the elimination of preapproval could create additional burden
for manufacturers in cases where they
fail to meet certified ratings and are
subsequently required to re-substantiate
their AEDM. DOE also does not agree
with Rheem Lennox, and Unico who
claim that the elimination of preapproval will lead to incorrect ratings in
the marketplace or create unfair
competition. Pre-approval of an ARM
that is used to certify a basic model
rating does not mean that the basic
model is correctly rated. Products that
are certified using an approved ARM are
subject to the same assessment testing
and enforcement actions as those
products certified through testing and/
or use of an AEDM. Further, DOE
currently has the authority to review
approved ARMs at any time, including
review of documentation of tests used to
support the ARM. DOE may also test
products that were certified using an
ARM to determine compliance with the
applicable sampling provisions, as well
as with federal standards. Should DOE
determine that products were
incorrectly rated, DOE may require that
the ARM is no longer used. Similarly,
AEDMs used to certify ratings are
subject to review at any time, as well as
the potential for suspension should DOE
determine that products were
incorrectly rated. Additionally, as
discussed in section III.A.3.a, each basic
model must have at least one rating
determined through testing; no basic
model can be rated solely using an
AEDM, which reduces the likelihood of
significant error. Finally, use of a preapproved ARM does not insulate a
manufacturer from responsibility for the
accuracy of their ratings, and the
misconception that it does presents
another reason to eliminate DOE review.
Most manufacturers have not updated
their ARMs and submitted the revised
ARM for DOE review as required by
regulation since prior to the last
standards update and, thus, are
effectively using unapproved or
outdated ARMs currently. For these
reasons, it is DOE’s view that the
elimination of the pre-approval process
would not have a substantive
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detrimental effect on the accuracy of a
manufacturer’s ratings, will improve
manufacturers’ ability to introduce new
products into the marketplace, and will
not represent a significant change from
the status quo.
For the forgoing reasons, in this
SNOPR, DOE proposes to eliminate the
pre-approval process for ARMs for splitsystem central air conditioners and heat
pumps. As stated in the AEDM NOPR,
DOE believes that this will reduce timeto-market delays, facilitate innovation,
and eliminate the time required to
complete the approval process.
Furthermore, DOE emphasizes that the
Department’s treatment of products that
are currently rated and certified with
the use of an ARM does not differ from
its treatment of products currently rated
and certified using an AEDM, except for
the pre-approval requirement. (See for
example 10 CFR 429.70(c).)
In addition, DOE proposes that
manufacturers may only apply an
AEDM if it (1) is derived from a
mathematical model that estimates
performance as measured by the
applicable DOE test procedure; and (2)
has been validated with individual
combinations that meet current Federal
energy conservation standards (as
discussed in the next section).
Furthermore, DOE proposes records
retention requirements and additional
manufacturer requirements to permit
DOE to audit AEDMs through
simulations, review of data and
analyses, and/or certification testing.
4. AEDM Validation
In the AEDM NOPR, DOE proposed
product-specific AEDM validation
requirements meant to reduce confusion
and allow for easier development and
utilization of AEDMs by manufacturers.
77 FR 32044–32045. The proposed
validation requirements applicable to
central air conditioner and heat pump
products would have required
manufacturers to:
a. Test a minimum of five basic
models, including at least one basic
model from each product class to which
the AEDM would be applied.
b. Test the smallest and largest
capacity basic models from the product
class with the highest sales volume.
c. Test the basic model with the
highest sales volume from the previous
year, or the basic model which is
expected to have the highest sales
volume for newly introduced basic
models.
d. Validate only with test data that
meets applicable Federal energy
conservation standards and was derived
using applicable DOE testing
procedures.
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In response to these proposed
validation requirements, DOE received a
number of comments from stakeholders
addressing specific products covered by
the AEDM rule. Comments applicable to
the proposed requirements for central
air conditioner and heat pump products
are discussed in the following sections.
a. Number of Basic Models From a
Product Class Necessary To Validate an
AEDM
Commenter responses with regard to
the minimum sample size of one unit
each of five different basic models were
mixed, with some commenters agreeing
with DOE’s proposal and some offering
alternative sample sizes. Both AAON
and Goodman agreed with DOE’s
proposal that a minimum of one unit
each of five basic models be tested to
validate the AEDM. (AAON, No. 40 at
p. 6; Goodman, No. 53 at p. 2) AHRI,
however, commented that it was not
realistic for a manufacturer who
produces two basic models, for
example, to be required to validate an
AEDM based on a minimum sample of
five units of the same two basic models.
(AHRI, Public Meeting Transcript, No.
69 at p. 154) Furthermore, AHRI stated
that it is disproportionately burdensome
to require testing of at least five basic
models for small manufacturers who
manufacture or wish to use an AEDM
for only a few basic models compared
to manufacturers who offer many basic
models and many product classes. AHRI
recommended that DOE require testing
of only 3 basic models if the AEDM is
to be applied to 15 or fewer basic
models. (AHRI No. 61 at p. 3) United
Cool Air agreed with AHRI’s concerns
and stated that to obtain data that are
statistically robust enough to meet the
validation requirements, testing of at
least two to five units of many basic
models would be necessary, which may
be too burdensome for built-to-order
and small manufacturers. This would be
particularly burdensome in cases where
models used for testing cannot be sold.
(United Cool Air, No. 51 at pp. 7, 10,
and 11) Acknowledging the amount of
work and complex testing required for
validation of an AEDM, Zero Zone, Inc.
(Zero Zone) noted that it would be
difficult for small manufacturers to
comply. Zero Zone recommended that
small manufacturers could be exempt or
have a different sample size
requirement. (Zero Zone, Public
Meeting Transcript, No. 69 at p. 65)
Other stakeholders commented on the
validation requirements for specific
products. JCI stated that testing of five
units is unnecessarily burdensome and
suggested that testing a minimum of
three units would be sufficient to
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validate HVAC AEDMs. (JCI, No. 66 at
p. 6) First Co. stated that DOE’s
proposed requirements would
unreasonably burden small
manufacturers, especially independent
coil manufacturers because they would
not have knowledge of which
condensing unit model is expected to
have the highest sales volume in the
coming year. First Co. stated that this
proposed requirement is unnecessary
and should be eliminated given that the
proposed validation requirements
already include testing of the smallest
and largest capacity basic model from
the product class with the highest sales
volume, and that the current minimum
number of tests required for obtaining
ARM approval is four. (First Co., No. 45
at p. 2) JCI agreed with First Co., stating
that the proposal would create an
overrepresentation of the highest sales
volume product class because the
highest sales volume basic model is
most likely from that product class, and
along with the requirement to test the
smallest and largest capacity basic
model from that product class, would
require testing of three basic models
from the highest sales volume product
class. (JCI, No. 66 at p. 7) Goodman, on
the other hand, stated that an additional
test beyond the currently required four
tests would not cause significant
burden. (Goodman, No. 53 at p. 2)
DOE notes that in its proposed
revisions to the determination of
certified ratings for central air
conditioners and heat pumps (discussed
in section III.A.3), manufacturers must
test each basic model; specifically for
split-system air conditioners and heat
pumps, OUMs must test each model of
outdoor unit with at least one model of
indoor unit (highest sales volume), and
ICMs must test each model of indoor
unit with at least one model of outdoor
unit (lowest SEER). Manufacturers
would only be able to use AEDMs for
other individual combinations within
the same basic model—in other words,
other combinations of models of indoor
units with the same model of outdoor
unit. DOE does not seek to require
additional testing to validate an AEDM
beyond what is proposed under 10 CFR
429.16(a)(1)(ii). Therefore, the testing
burden required to validate an AEDM
would depend on the number of basic
models each manufacturer must rate.
Furthermore, because ICMs must test
each model of indoor unit with the
lowest-SEER model of outdoor unit with
which it is paired, First Co.’s concerns
related to predicting the highest sales
volume model would no longer be
relevant. DOE requests comment on its
proposal related to the testing
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requirements for validation of an
AEDM.
Regarding the proposed requirement
to test a basic model from each
applicable product class for HVAC
products, Goodman believes that the
current definition of ‘‘product class’’
does not address the specific issues
raised by split-system central air
conditioners and heat pumps, which
consist of separate indoor and outdoor
coils that only function as intended
when paired with one another to form
a unitary split-system central air
conditioner or heat pump. Hence,
Goodman suggested that DOE consider
the following product types to
constitute individual validation classes:
Split-system air conditioners, splitsystem heat pumps, single-package air
conditioners, and single-package heat
pumps. (Goodman, No. 53 at p. 4) UTC/
Carrier proposed separate validation
classes for the categories mentioned by
Goodman, but also proposed that central
air conditioners and heat pumps should
include distinct validation classes for
space-constrained air conditioners and
space-constrained heat pumps. (UTC/
Carrier, No. 56 at p. 2) United Cool Air
stated that DOE did not properly
address classification of spaceconstrained HVAC systems. (United
Cool Air, No. 51 at p. 4, 13) United Cool
Air’s comments align with comments
from Carrier that DOE should create a
separate product class for spaceconstrained equipment.
In response, DOE notes that the
proposed testing requirements in 429.16
require testing at least one individual
model/combination within each basic
model. Therefore, by default
manufacturers would be testing all basic
models from each product class in
which they manufacture units.
b. Selection of Capacity Variations of a
Basic Model for Validating an AEDM
Regarding selection of basic models
for validating an AEDM, both Nordyne
and Goodman agreed with DOE’s
proposal that the basic models selected
for validating an AEDM must include
the smallest capacity basic model as
well as the largest capacity basic model
(or a basic model within 25 percent of
the largest capacity). (Nordyne, No. 55
at p. 2; Goodman, No. 53 at p. 2) Rheem,
however, disagreed and stated that the
requirement to test the smallest and
largest capacity basic model was too
restrictive and does not account for
outliers or differences in technology
across product classes. (Rheem, No. 59
at p. 4) Furthermore, Lennox noted that
the manufacturer is most suited to
determine which models should be used
for validation and that requirements for
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particular capacities do not account for
variation in product design and
construction. (Lennox, No. 46 at p. 4)
DOE’s intention when proposing to
require that a manufacturer test both the
smallest and largest capacity basic
models within the product class with
the highest sales volume was to ensure
that the AEDM could accurately predict
the efficiency of those products at the
extremes of a manufacturer’s product
line. As variations in product design
and construction across all capacities
should be accounted for when testing all
basic models, DOE withdraws the
proposal regarding selecting the
smallest and largest capacity basic
models from the product class with the
highest sales volume for testing for
validation of the AEDM. DOE notes that
in the proposed revisions to the
determination of certified ratings, each
basic model must be tested and an
AEDM can only be used to certify other
individual combinations that are part of
the same basic model.
c. Use of the Highest Sales Volume
Basic Model for Validating an AEDM
Many interested parties recommended
that DOE continue to require that splitsystem manufacturers test each
condensing unit they manufacture with
the evaporator coil that is likely to have
the largest volume of retail sales (i.e.,
the highest sales volume combination,
or HSVC) because the data resulting
from these test combinations are critical
to independent coil manufacturers
(ICMs) in determining accurate ratings
for their products since they must
determine their ratings based on
pairings with condensing units offered
by other manufacturers. AHRI stated
that DOE should retain requirements for
testing based on the HSVC for central air
conditioners and heat pumps. (AHRI,
No. 61 at p. 2) UTC/Carrier agreed that
DOE should allow split-systems to
retain the HSVC process, as is required
by current ARM regulations. (UTC/
Carrier, No. 56 at p. 1) Lennox disagreed
with removing the requirement for
testing based on HSVC because the
current AHRI certification program and
independent coil manufacturing
industry depend on this requirement,
and the data from HSVC test results are
used by independent coil manufacturers
(ICMs) as the input to their ARM.
(Lennox, No. 46 at p. 4)
Unico stated that DOE should
maintain the current ARM requirements
for central air conditioners and heat
pumps because as an indoor coil
manufacturer, Unico relies on the
accuracy of the ratings published by the
manufacturer of the outdoor unit and
decreasing the accuracy of those ratings
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69295
would increase their own risk of failure.
Unico stressed that it was particularly
important for DOE to allow
manufacturers’ rating methodology to
rely on curve fit data, and specifically
proposed that for validating an AEDM,
matched system manufacturers should
test at least the highest sales volume
combination for each outdoor unit.
(Unico, No. 54 at pp. 2, 4, and 6) Mortex
Products, Inc. (Mortex) stated that in
order for ICMs to rate indoor coils
accurately using the ARM, the system
manufacturer’s HSVC data is necessary,
and if HSVC data were no longer
obtained from tests, but generated using
an AEDM, the accuracy of the indoor
coil ratings would be affected. (Mortex,
No. 58 at p. 1)
DOE recognizes the concerns of
stakeholders who commented that
eliminating the requirement to test the
HSVC for split-system products could
increase the burden on ICMs. DOE does
not intend to eliminate that requirement
and notes that such requirement is
proposed to be retained in this notice,
as discussed in section III.A.3.a.
However, DOE also proposes additional
requirements for ICMs that are
discussed in section III.B.5. DOE also
notes that the ARM provisions in the
current regulations do not clearly apply
to ICMs, and most ICMs do not have
DOE-approved ARMs.
DOE’s proposal in the AEDM NOPR
required re-validation when the HSVC
changes. In response, Goodman stated
that for split-system CACs and HPs,
testing the highest or expected highest
sales volume combination basic model
would be appropriate as long as DOE
does not require re-validation of the
AEDM if another basic model
subsequently becomes the highest sales
volume combination. Determination of
the highest volume basic model should
be based on sales data of the prior year,
or sales data or forecasts of the year of
the AEDM’s validation. (Goodman, No.
53 at p. 3) United Cool Air was also
concerned that additional testing would
be required if the highest selling basic
model changed. (United Cool Air, No.
51 at p. 9)
In response to the concerns of
Goodman and United Cool Air regarding
re-validation if the HSVC changed, DOE
agrees that re-validation should not be
required if test data used to validate the
AEDM was based on an expected HSVC
that subsequently becomes a lower sales
volume model and is not proposing
such a requirement in this notice. DOE
agrees with Goodman that
determination of the highest volume
basic model should be based on sales
data of the prior year, sales data or
forecasts of the year of the AEDM’s
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validation, or other similar information.
Selection of the highest volume basic
model should reflect a good faith effort
by the manufacturer to predict the
combination most likely to result in the
highest volume of sales. DOE notes that
it may verify compliance with this
HSVC testing requirement.
d. Requirements for Test Data Used for
Validation
In AEDM NOPR, DOE did not propose
requirements on the test data used for
validation of an AEDM because any
non-testing approaches to certifying
central air conditioners and heat pumps
via an ARM were to be approved by
DOE prior to use. 77 FR 32043.
However, if DOE adopts the current
proposal to remove the pre-approval
requirement, certified ratings generated
using an AEDM would be unreliable
without other requirements to validate
the AEDM against actual test data.
Therefore, DOE proposes in this notice
to adopt requirements on test data
similar to those used for validation for
commercial HVAC and water heating
equipment, as published in the AEDM
final rule 78 FR 79579, 79584 (Dec. 31,
2013). Specifically, (1) for energyefficiency metrics, the predicted
efficiency using the AEDM may not be
more than 3 percent greater than that
determined through testing; (2) for
energy consumption metrics, the
predicted efficiency using the AEDM
may not be more than 3 percent less
than that determined through testing;
and (3) the predicted efficiency or
consumption for each individual
combination calculated using the AEDM
must comply with the applicable
Federal energy conservation standard.
Furthermore, the test results used to
validate the AEDM must meet or exceed
the applicable Federal standards, and
the test must have been performed in
accordance with the applicable DOE test
procedure. If DOE has ordered the use
of an alternative test method for a
particular basic model through the
issuance of a waiver, that is the
applicable test procedure.
DOE proposes a validation tolerance
of 3 percent because the variability in a
manufacturer’s lab and within a basic
model should be more limited than labto-lab variability. DOE proposes
tolerances for verification testing of 5
percent to account for added lab-to-lab
variability.
5. Requirements for Independent Coil
Manufacturers
In the AEDM NOPR, DOE did not
propose a statistical sampling
requirement for independent coil
manufacturers (ICMs) that would be
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distinct from the sampling required to
validate an AEDM for HVAC products.
77 FR at 32043. In response, Unico
commented that ICMs should test coils
of each fin-pattern, varying the number
of rows, fin density, tube type,
circuiting, and frontal area. (Unico, No.
54 at p. 4) Mortex stated that their
ARMs are based on data from a
‘‘matched system’’ tested by an OUM.
Mortex uses an ARM to simulate the
performance of their own coil in a
matched system by substituting the
geometry of the indoor evaporator coil
used by the manufacturer of the
condensing unit with the geometry of
their own coil. (Mortex, No. 58 at p. 1)
While DOE understands that ICMs
currently use ratings from OUMs to
predict the efficiency of their coil
models, as discussed in section
III.A.3.d, DOE is now proposing to
require that ICMs test each of model of
indoor units (i.e., basic models) with the
least efficient model of outdoor unit
with which it will be paired. In order to
validate an AEDM for split-systems
rated by ICMs for other individual
combinations within each basic model,
DOE also proposes that ICMs must use
the individual combinations the ICMs
would be required to test under the
proposed text in 10 CFR 429.16. DOE
seeks comment on this proposal.
In regard to Unico’s suggestion to test
indoor units with coils of varying finpatterns, DOE refers stakeholders to the
definition of a basic model in section
III.A.1, and particularly what constitutes
the same model of indoor unit. DOE
notes that the manner in which
manufacturers apply the basic model
provisions would impact what models
of indoor units are required for testing.
6. AEDM Verification Testing
DOE may randomly select and test a
single unit of a basic model pursuant to
10 CFR 429.104. This authority extends
to all DOE covered products, including
those certified using an AEDM. In the
AEDM NOPR, DOE clarified that a
selected unit would be tested using the
applicable DOE test procedure at an
independent, third-party laboratory
accredited to the International
Organization for Standardization (ISO)/
International Electrotechnical
Commission (IEC), ‘‘General
requirements for the competence of
testing and calibration laboratories,’’
ISO/IEC 17025:2005E. 77 FR 32038,
32057 (May 31, 2012).
In this notice, DOE proposes further
verification testing methods.
Specifically, DOE proposes that
verification testing conducted by the
DOE will be (1) on a retail unit or a unit
provided by the manufacturer if a retail
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unit is not available, (2) at an
independent, third-party testing facility
or a manufacturer’s facility upon DOE’s
request if the former is not capable of
testing such a unit, and (3) conducted
with no communication between the lab
and the manufacturer without DOE
authorization.
DOE also proposes clarification of
requirements for determining that a
model does not meet its certified rating,
as proposed in the AEDM NOPR.
Specifically, DOE proposes that an
individual combination would be
considered as having not met its
certified rating if, even after applying
the five percent tolerance between the
test results and the rating as specified in
the proposed 10 CFR 429.70(e)(5)(vi),
the test results indicate the individual
combination being tested is less efficient
or consumes more energy than indicated
by its certified rating. DOE notes that
this approach will not penalize
manufacturers for applying conservative
ratings to their products. That is, if the
test results indicate that the individual
combination being tested is more
efficient or consumes less energy than
indicated by its certified rating, DOE
would consider that individual
combination to meet its certified rating.
DOE seeks comment on whether this is
a reasonable approach to identify an
individual combination’s failure to meet
its certified rating.
In the AEDM NOPR, DOE also
proposed the actions DOE would take in
response to individual models that fail
to meet their certified ratings. 77 FR at
32056. Many stakeholders submitted
comments suggesting that DOE should
determine the cause of the test failure
prior to taking any additional action.
UTC/Carrier commented that failure of
a single unit test result could be a result
of a defective unit and further urged
DOE to define a process to contest test
results from a third party lab. (UTC/
Carrier, No. 56 at p. 2) JCI had a similar
concern regarding potential errors in
test set-up and proposed that DOE
should work with the manufacturer to
determine the root cause of the failure,
performing additional testing if
necessary. (JCI, No. 66 at p. 8) Rheem
agreed with JCI that DOE should work
with the manufacturer to determine
whether the root cause is associated
with test variability, AEDM model
inaccuracy, or manufacturing
variability. Rheem added that DOE
should clarify what constitutes a
‘‘failure’’ as well as develop a detailed
plan for selection, testing, evaluation,
manufacturer notification, and
resolution. (Rheem, No. 59 at p. 4)
Lennox also agreed that DOE should not
immediately require modification of an
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AEDM without first finding the cause of
the failure. (Lennox, No. 46 at pp. 4–5)
Additionally, Ingersoll Rand requested
that DOE allow for a dialogue with the
manufacturer to ensure that the sample
unit was not defective and that the test
was set up correctly. (Ingersoll Rand,
Public Meeting Transcript, No. 69 at p.
187) AHRI agreed that it would be
valuable to specify particular steps
manufacturers and DOE must take in the
case of a test failure and incorporate a
defective sample provision, and
recommended that DOE provide data, a
failure report, and other necessary
information to the manufacturer for
proper analysis of the test failure.
(AHRI, No. 61 at pp. 6–7)
Unico and manufacturers of products
other than HVAC suggested that DOE
should not only share the data with the
manufacturer, but also allow the
manufacturer to review or witness
testing done by a lab. This would allow
for better understanding of potential
discrepancies in test results and ensure
that failure was not merely a result of
variation in test set-up. (Unico, No. 54
at p. 4) AHRI and UTC/Carrier suggested
that manufacturers should be allowed to
participate in commissioning of their
equipment prior to the assessment test
since proper set-up is critical. AHRI
added that manufacturers should have
an opportunity to repair a unit, if
defective, while it is in the assessment
lab. (AHRI, No. 61 at pp. 6–7; Carrier,
Public Meeting Transcript, No. 69 at p.
218) Further, UTC/Carrier urged DOE to
specify an appeals process for tests that
a manufacturer believes were tested
with improper test set-up. (UTC/Carrier,
Public Meeting Transcript, No. 69 at p.
195; UTC/Carrier, No. 56 at p. 3)
DOE agrees that determining the root
cause of the failure to meet certified
ratings is important; however, DOE
stresses that this would be the
manufacturer’s responsibility. DOE is
aware that in order to determine the
cause of the failure, the manufacturer
will need to review the data from DOE’s
testing. DOE therefore proposes that
when an individual combination fails to
meet certified ratings, DOE will provide
to the manufacturer a test report that
includes a description of test set-up, test
conditions, and test results. DOE will
provide the manufacturer with an
opportunity to respond to the lab report
by presenting all claims regarding
testing validity, and if the manufacturer
was not on-site for initial set-up, to
purchase an additional unit from retail
to test following the requirements in
429.110(a)(3). This process is designed
to provide manufacturers the
opportunity to raise concerns about the
test set-up, taking into account various
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comments from stakeholders. DOE will
consider any response offered by the
manufacturer within a designated time
frame before deciding upon the validity
of the test results. Only after following
these steps will the Department make a
determination that the rating for the
basic model is invalid and require the
manufacturer to take subsequent action,
as described in section III.B.7.
7. Failure To Meet Certified Ratings
In the AEDM NOPR, DOE proposed a
method of determining whether a model
meets its certified rating whereby the
assessment test result would be
compared to the certified rating for that
model. If the test result was not within
the tolerance in the proposed section
429.70(c), the model would be
considered as having not met its
certified rating. In this case DOE
proposed to require that manufacturers
re-validate the AEDM that was used to
certify the product within 30 days of
receiving the test report from the
Department. DOE also proposed to
require that manufacturers incorporate
DOE’s test data into the re-validation of
the AEDM. If after inclusion of DOE’s
test data and re-validation, the AEDMcertified ratings change for any models,
then the manufacturer would be
required to re-rate and re-certify those
models. The manufacturer would not be
required to perform additional testing in
this re-validation process unless the
manufacturer finds it necessary in order
to meet the requirements enumerated in
the proposed section 429.70. 77 FR
32028, 32056.
A few stakeholders provided
comments on the aforementioned
proposals. Zero Zone commented that
the failure of a single test unit to meet
its certified rating should not
automatically necessitate re-validation,
but suggested that the manufacturer
should decide on the appropriate course
of action. (Zero Zone, No. 64 at p. 3)
UTC/Carrier commented that DOE
should not require re-validation based
on a single unit’s test result because the
failure could be a result of a defective
unit. (UTC/Carrier, No. 56 at p. 2)
Lennox opposed DOE’s proposal to
require manufacturers to incorporate
DOE test data into their AEDM if a
model is determined not to meet its
certified rating because they believe that
DOE data may be erroneous and only
the best available data should be used
to validate an AEDM. (Lennox, No. 46
at p. 5) JCI stated that without
additional information as to why a
particular product failed a test, it is not
reasonable to assume that all models
rated with the AEDM must be re-rated.
(JCI, No. 66 at pp. 9–10).
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In consideration of the above
mentioned comments, DOE proposed to
allay concerns via the proposal in
section III.B.6, which provides
manufacturers an opportunity to review
the data from DOE’s testing and present
claims regarding testing validity. Based
on these comments, DOE also proposes
an exception to re-validation of the
AEDM in cases where the determination
of an invalid rating for that basic model
is the first for models certified with an
AEDM. In such cases, the manufacturer
must conduct additional testing and rerate and re-certify the individual
combinations within the basic model
that were improperly rated using the
AEDM.
DOE also proposes that if DOE has
determined that a manufacturer made
invalid ratings on individual
combinations within two or more basic
models rated using the manufacturer’s
AEDM within a 24 month period, the
manufacturer must test the least
efficient and most efficient combination
within each basic model in addition to
the combination specified in
429.16(a)(1)(ii). The twenty-four month
period begins with a DOE determination
that a rating is invalid through the
process outlined above. If DOE has
determined that a manufacturer made
invalid ratings on more than four basic
models rated using the manufacturer’s
AEDM within a 24-month period, the
manufacturer may no longer use an
AEDM.
Finally, DOE proposes additional
requirements for manufacturers to
regain the privilege of using an AEDM,
including identifying the cause(s) for
failure, taking corrective action,
performing six new tests per basic
model, and obtaining DOE
authorization.
DOE created this proposal under the
expectation that each manufacturer will
use only a single AEDM for all central
air conditioner and central air
conditioning heat pumps. DOE requests
comment on whether manufacturers
would typically apply more than one
AEDM and if they would, the
differences between such AEDMs.
8. Action Following a Determination of
Noncompliance
In the AEDM NOPR, DOE explained
that if a model failed to meet the
applicable Federal energy conservation
standard during assessment testing,
DOE may pursue enforcement testing
pursuant to 10 CFR 429.110. DOE also
stated that if an individual model was
determined to be noncompliant, then all
other individual models within that
basic model would be considered
noncompliant. This is consistent with
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DOE’s approach for all covered
products. All other basic models rated
with the AEDM would be unaffected
pending additional investigation.
Furthermore, DOE proposed that if a
noncompliant model was used for
validation of an AEDM, the AEDM must
be re-validated within 30 days of
notification, pursuant to requirements
enumerated in 10 CFR 429.70. Notably,
DOE did not propose that manufacturers
must re-test basic models used to
validate an AEDM when there is no
determination of noncompliance. 77 FR
32056.
In response, JCI agreed that all AEDMrated models should not be disqualified
if one model is found out of compliance.
(JCI, No. 66 at p. 9)
DOE reiterates that for central air
conditioners and central air
conditioning heat pumps, if an
individual combination was determined
to be noncompliant, then all other
individual combinations within that
basic model would be considered
noncompliant. DOE is not proposing in
this SNOPR that other basic models
rated with the AEDM be considered
non-compliant. However, DOE notes
that an AEDM must be validated using
test data for individual combinations
that meet the current Federal energy
conservation standards. Therefore, if a
noncompliant model was used for
validation of an AEDM, manufacturers
would be expected to re-validate the
AEDM in order to continue using it. The
requirements for additional testing
based on invalid ratings, as discussed in
the previous section, may also apply.
C. Waiver Procedures
10 CFR 430.27(l) requires DOE to
publish in the Federal Register a notice
of proposed rulemaking to amend its
regulations so as to eliminate any need
for the continuation of waivers and as
soon thereafter as practicable, DOE will
publish a final rule in the Federal
Register. As of the issuance date of this
notice, a total of four waivers (and one
interim waiver) for central air
conditioner and heat pump products are
active. They are detailed in the Table
III.4, with the section reference to this
notice included for discussion regarding
DOE’s proposed amended regulations
and intention for subsequent waiver
termination.
TABLE III.4—ACTIVE WAIVERS AND ACTIVE INTERIM WAIVERS
Air Conditioners and Heat Pumps, Consumer
Scope
Decision & order
ECR International, Inc., Multi-zone Unitary Small Air Conditioners and Heat Pumps
(Petition & Interim Waiver, 78 FR 47681,
8/6/2013).
76 FR 11438, 3/2/2011 .............................
75 FR 34731, 6/18/2010 ...........................
75 FR 6013, 2/5/2010 ...............................
73 FR 50787, 8/28/2008 ...........................
Daikin AC (Americas), Inc., Heat Pump & Water Heater Combination .......................
Daikin AC (Americas), Inc., Heat Pump & Water Heater Combination .......................
Hallowell International, Triple-Capacity Northern Heat Pumps ...................................
Cascade Group, LLC, Multi-blower Air-Conditioning and Heating Equipment ............
DOE notes that four waivers
previously associated with both
commercial equipment and consumer
products, as listed in Table III.3, were
terminated for consumer products as of
the October 22, 2007 Final Rule (72 FR
59906, 59911) and for commercial
equipment as of the May 16, 2012 Final
Rule (77 FR 28928, 28936). In this
SNOPR, DOE reaffirms that these
waivers have been terminated for
consumer products and that the
Termination
III.C.2
III.C.1
III.C.1
III.C.4
III.C.3
products in question can be tested using
the current and proposed test procedure
for central air conditioners and heat
pumps.
TABLE III.5—TERMINATED WAIVERS
Scope
Decision & order
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Daikin U.S. Corporation, Multi-split Heat Pumps and Heat Recovery Systems ......
Mitsubishi Electric and Electronics USA, Inc., Variable Refrigerant Flow Zoning
Air Conditioners and Heat Pumps.
Fujitsu General Limited, Multi-split Products ............................................................
Samsung Air Conditioning, Multi-split Products ........................................................
1. Termination of Waivers Pertaining to
Air-to-Water Heat Pump Products With
Integrated Domestic Water Heating
DOE has granted two waivers to
Daikin Altherma for the air-to-water
heat pump with integrated domestic
water heating; one on June 18, 2010 and
a second on March 2, 2011. 75 FR 34731
and 76 FR 11438. As described in
Daikin’s petitions, the Daikin Altherma
system consists of an air-to-water heat
pump that provides hydronic space
heating and cooling as well as domestic
hot water functions. It operates either as
a split system with the compressor unit
outdoors and the hydronic components
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73 FR 39680, 7/10/2008.
72 FR 17528, 4/9/2007.
72 FR 71383, 12/17/2007.
72 FR 71387, 12/17/2007.
in an indoor unit, or as a single-package
configuration in which all system
components are combined in a single
outdoor unit. In both the single-package
and the split-system configurations, the
system can include a domestic hot water
supply tank that is located indoors.
These waivers were granted on the
grounds that the existing DOE test
procedure contained in Appendix M to
Subpart B of 10 CFR part 430 addresses
only air-to-air heat pumps and does not
include any provisions to account for
the operational characteristics of an airto-water heat pump, or any central airconditioning heat pump with an
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integrated domestic hot water
component.
According to the definition set forth
in EPCA and 10 CFR 430.2, a central air
conditioner is a product, other than a
packaged terminal air conditioner,
which is powered by single phase
electric current, air cooled, rated below
65,000 Btu per hour, not contained
within the same cabinet as a furnace,
the rated capacity of which is above
225,000 Btu per hour, and is a heat
pump or a cooling unit only. (42 U.S.C.
6291(21)) The heat pump definition in
EPCA and 10 CFR 430.2 requires that a
heat pump utilize a refrigerant-to-
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outdoor air heat exchanger, effectively
excluding heat pump products
classified as air-to-water. (42 U.S.C.
6291(24)) In addition, because the
definition of a central air conditioner,
which also applies to heat pumps,
requires products to be ‘‘air cooled,’’
products that rely exclusively on
refrigerant-to-water heat exchange on
the indoor side are effectively excluded
from the definition of, and the existing
efficiency standards for, central air
conditioners and heat pumps.
Based upon the description in the
waiver petitions for the Daikin Altherma
air-to-water heat pumps with integrated
domestic water heater, DOE has
determined that these products rely
exclusively on refrigerant-to-water heat
exchange on the indoor side, and thus
would not be subject to the central air
conditioner or heat pump standards and
would not be required to be tested and
rated for the purpose of compliance
with DOE standards for central air
conditioners or heat pumps. Thus, if
this interpretation is adopted, these
waivers would terminate on the
effective date of a notice finalizing the
proposals in this notice.
2. Termination of Waivers Pertaining to
Multi-Circuit Products
DOE granted ECR International (ECR)
an interim waiver on August 6, 2013, for
its line of Enviromaster International
(EMI) products. 78 FR 47681. ECR
describes in its petitions that its multizone air conditioners and heat pumps
each comprise a single outdoor unit
combined with two or more indoor
units, which each comprise a
refrigeration circuit, a single air handler,
a single control circuit, and an
expansion valve, intended for
independent zone-conditioning. The
outdoor unit contains one fixed-speed
compressor for each refrigeration
circuit; all zones utilize the same
condenser fan and defrost procedures
but refrigerant is not mixed among the
zones. 78 FR at 47686. These products
are similar to multiple-split (or multisplit) air conditioners or heat pumps,
which are defined and covered by
current test procedure (Appendix M to
Subpart B of 10 CFR part 430). However,
they are distinct from, and therefore not
classified as, multi-split products due to
differences in refrigerant circuitry. The
separate refrigeration circuits of the ECR
product line are not amenable to the test
procedures for multi-split systems,
specifically the procedures calling for
operation at different levels of
compressor speed or staging, because
the individual compressors are not
necessarily variable-speed. Hence,
alternative procedures have been
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developed, as described in the interim
waiver. DOE proposes to address
products such as the ECR product line
in the DOE test procedure. DOE also
proposes to define such a product as a
‘‘multi-circuit air conditioner or heat
pump’’ and provide testing
requirements for such for such products
at 10 CFR 429.16(a)(1)(ii)(A).
For the duration of the interim waiver
period, either until 180 days after the
publication of the interim waiver (the
interim waiver period) or until DOE
issued its determination on the petition
for waiver, whichever occurred earlier,
DOE granted ECR permission to use the
proposed alternative test procedure to
test and rate its multi-circuit products.
78 FR 47681, 47682 (Aug. 6, 2013). The
requirements in the alternative test
procedure comprise methods to
establish air volume rate, procedures for
testing, and adjustments to equations
used to calculate SEER and HSPF.
Following publication of the Notice of
Grant of Interim Waiver, DOE received
no comments regarding this alternative
test procedure. After the interim waiver
period, DOE did not issue a final
decision and order on ECR’s petition for
waiver, therefore, the interim waiver
will terminate upon the publication of
a test procedure final rule for central air
conditioners and heat pumps, and the
alternative test procedure included
therein shall cease from being
applicable to testing and rating ECR’s
multi-circuit products and multi-circuit
products in general, absent amendments
regarding provisions for testing such
products. Therefore, DOE proposes in
this notice testing requirements for
manufacturers who wish to certify
multi-circuit products.
According to Appendix M to Subpart
B of 10 CFR part 430, Section 2.4.1b,
systems with multiple indoor coils are
tested in a manner where each indoor
unit is outfitted with an outlet plenum
connecting to a common duct so that
each indoor coil ultimately connects to
an airflow measuring apparatus.10 In
testing a multi-circuit system in this
manner, the data collection,
performance measurement, and
reporting is done only on the system
level. ECR took issue with this, citing
inadequate data accountability, and thus
argued in its petition for waiver to
individually test each indoor unit. Id.
Current test procedures for systems with
multiple indoor coils, however, produce
ratings that are repeatable and accurate
even though monitoring of all indoor
10 When the indoor units are installed in separate
indoor chambers for the test, the test procedure
allows common ducting to a separate airflow
measuring apparatus for each indoor chamber.
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units are not required by regulation, or
common industry practice. DOE also
notes that the common duct testing
approach has been adopted by industry
standards and is an accepted method for
testing systems having multiple indoor
units. ECR’s petition did not identify
specific differences between the indoor
units of its new product line and the
indoor units of multi-splits that would
make the common-duct approach
unsuitable for its products. Further, the
interim waiver approach of using
multiple airflow measuring devices, one
for each indoor unit, represents
unnecessary test burden. Therefore,
DOE proposes to adopt for multi-circuit
products the same common duct testing
approach used for testing multi-split
products.
The alternative test procedure in the
interim waiver calls for separate
measurement of performance for each
indoor unit for each required test
condition, and requires that all indoor
units be operating during each of these
separate measurements. The overall
system performance for the given test
condition is calculated by summing the
capacities and power inputs measured
for all of the indoor units and adding to
the power input sum the average of the
power measurements made for outdoor
unit for the set of tests. Id. In contrast,
DOE’s current proposal involves use of
the common duct to measure the full
system capacity, thus allowing use of a
single test for each operating condition.
DOE requests comment on whether this
method will yield accurate results that
are representative of the true
performance of these systems.
3. Termination of Waiver and
Clarification of the Test Procedure
Pertaining to Multi-Blower Products
On August 28, 2008, DOE published
a decision and order granting Cascade
Group, LLC a waiver from the Central
Air Conditioner and Heat Pump Test
Procedure for its line of multi-blower
indoor units that may be combined with
one single-speed heat pump outdoor
unit, one two-capacity heat pump
outdoor unit, or two separate singlespeed heat pump outdoor units. 73 FR
50787, 50787–97. DOE proposed
revisions to the test procedure in the
June 2010 NOPR to accommodate the
certification testing of such products. 75
FR 31237. NEEA responded in the
subsequent public comment period,
recommending DOE defer action on test
procedure changes until such a product
is actually being tested, certified and
sold. (NEEA, No. 7 at pp. 4–5).
Mitsubishi recommended DOE either
use AHRI Standard 1230–2010 to rate
such a product or does not amend the
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test procedure to allow coverage of such
a product. (Mitsubishi, No. 12 at p. 2).
DOE notes that AHRI Standard 1230–
2010, which provides testing procedures
for products with variable speed or
multi-capacity compressors, may not be
suitable for testing the subject products,
which are equipped with single-speed
compressors; however, the test
procedure, as proposed in the June 2010
NOPR enables testing of such products.
DOE therefore retains its proposal in the
June 2010 NOPR to adopt that test
procedure, except for the following
revisions.
The proposal in the June 2010 NOPR
amended Appendix M to Subpart B of
10 CFR part 430 with language in
sections 3.1.4.1.1e and 3.1.4.2e that
suggested that test setup information
may be obtained directly from
manufacturers. DOE is revising that
proposal to eliminate the need for
communication between third-party test
laboratories and manufacturers, such
that the test setup is conducted based on
information found in the installation
manuals included with the unit by the
manufacturer. DOE is proposing that
much of that information be provided to
DOE as part of certification reporting.
These proposed modifications regarding
test setup can be found in section
3.1.4.1.1d and 3.1.4.2e of the proposed
Appendix M in this notice. DOE
requests comment on its proposals for
multi-blower products, including
whether individual adjustments of each
blower are appropriate and whether
external static pressures measured for
individual tests may be different.
Because the proposed test procedure
amendments would allow testing of
Cascade Group, LLC’s line of multiblower products, DOE proposes to
terminate the waiver currently in effect
for those multi-blower products
effective 180 days after publication of
the test procedure final rule.
4. Termination of Waiver Pertaining to
Triple-Capacity, Northern Heat Pump
Products
On February 5, 2010, DOE granted
Hallowell International a waiver from
the DOE Central Air Conditioner and
Heat Pump Test Procedure for its line of
boosted compression heat pumps. 75 FR
6014, 6014–18. DOE proposed revisions
to its test procedures in the June 2010
NOPR to accommodate the certification
testing of such products. 75 FR 31223,
31238 (June 2, 2010). NEEA expressed
support for DOE’s proposal in the
subsequent public comment period but
urged DOE to ensure that the northern
climate test procedure can be used by
variable speed systems that can meet the
appropriate test conditions, and that the
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procedures can accurately assess the
performance of these systems relative to
more conventional ones. (NEEA, No. 7
at p. 5). NEEA also urged DOE to require
publishing of Region V ratings for heat
pumps. Mitsubishi supported DOE’s
proposed changes to cover triplecapacity, northern heat pumps but
requested that DOE reevaluate the
testing of inverter-driven compressor
systems to permit better demonstration
of the system’s capabilities at heating at
low ambient conditions. (Mitsubishi,
No. 12 at p. 3).
DOE believes that the test procedure
as proposed in the June 2010 NOPR,
along with the proposed revisions to the
test procedure for heating tests
conducted on units equipped with
variable-speed compressors, as
discussed in section III.H.5, would
produce performance that represents an
average period of use of such products.
Because the proposed test procedure
amendments would allow testing of
Hallowell International’s line of triplecapacity, northern heat pump products,
DOE proposes to terminate the waiver
currently in effect for those products
effective 180 days after publication of
the test procedure final rule.
D. Measurement of Off Mode Power
Consumption
In the June 2010 NOPR, DOE
proposed a first draft of testing
procedures and calculations for off
mode power consumption. 75 FR 31223,
31238 (June 2, 2010). In the following
April 2011 SNOPR, DOE proposed a
second draft, revising said testing
procedures and calculations based on
stakeholder-identified issues and
changes to the test procedure proposals
in the 2010 June NOPR and on DOEconducted laboratory testing. 76 FR
18105, 18111 (April 1, 2011). In the
October 2011 SNOPR, DOE proposed a
third draft, further revising the testing
procedures and calculations for off
mode power consumption based
primarily on stakeholder comments
regarding burden of test as received
during the April 2011 SNOPR comment
period. 76 FR 65616, 65618–22 (Oct. 24,
2011). From the original and extended
comment period of the October 2011
SNOPR DOE received stakeholder
comments, which are the basis of DOE’s
proposed fourth draft in this notice,
further revising testing procedures and
calculations for off mode power
consumption. None of the proposals
listed in this section impact the energy
conservation standard.
1. Test Temperatures
In the October 2011 SNOPR, DOE
proposed to base the off mode power
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consumption rating (PW,OFF) on an
average of wattages P1 and P2, which
would be recorded at the different
outdoor ambient temperatures of 82 °F
and 57 °F, respectively. DOE intended
that, for systems with crankcase heater
controls, the measurement at the higher
ambient temperature would measure the
off mode contribution that was more
representative of the shoulder seasons.
The lower measurement was intended
to represent off mode power use for an
air conditioner during the heating
season. 76 FR at 65621.
In response to the October 2011
SNOPR, a joint comment from Pacific
Gas and Electric and Southern
California Edison, hereafter referred to
as the California State Investor Owned
Utilities (CA IOUs), and a joint
comment from the American Council for
an Energy-Efficient Economy (ACEEE)
and Appliance Standards Awareness
Program (ASAP) expressed concern that
the 57 °F test point could create a
loophole wherein a crankcase heater
could be designed to turn on just below
57 °F and result in an underestimation
of the system’s energy consumption.
The off mode power consumption
would be underestimated because the
energy consumption of the crankcase
heater would not be included in either
P1 or P2. (CA IOUs, No. 33 at p. 2;
ACEEE and ASAP, No. 34 at p. 2) A
joint comment from the Northwest
Energy Efficiency Alliance (NEEA) and
the Northwest Power and Conservation
Council (NPCC), hereafter referred to as
the Joint Efficiency Advocates, also
disputed DOE’s proposal to test units at
two fixed temperatures and disagreed
with DOE’s contention that the
proposed P2 test temperature (57 °F) is
sufficiently low that the crankcase
heater would be energized. (Joint
Efficiency Advocates, No. 35 at p. 3)
Both the CA IOUs and the Joint
Efficiency Advocates proposed that DOE
require manufacturers to specify the
temperature at which the crankcase
heater turns on and off, and then to run
one off mode test 3–5 °F below the point
at which the crankcase heater turns on
(‘‘on’’ set point temperature) and the
other off mode test 3–5 °F above the
temperature at which the crankcase
heater turns off (‘‘off’’ set point
temperature). (CA IOUs, No. 33 at p. 2;
Joint Efficiency Advocates, No. 35 at p.
3) However, the Joint Efficiency
Advocates only proposed this rating
method for constant wattage crankcase
heaters. (Joint Efficiency Advocates, No.
35 at p. 3) The Joint Efficiency
Advocates stated that two
measurements are insufficient for
systems that have a heater with wattage
that varies according to temperature and
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suggested that the crankcase heater
power for systems with variable wattage
be tested at three temperatures.
Specifically, the Joint Efficiency
Advocates recommended testing at 3–5
°F below the ‘‘on’’ set point
temperature, at 47 °F, and at 17 °F.
(Joint Efficiency Advocates, No. 35 at p.
4) The Joint Efficiency Advocates
additionally recommended that systems
with temperature-controlled crankcase
heaters should be tested for off mode
power use when cold (i.e., before the
system is run). (Joint Efficiency
Advocates, No. 35 at p. 4)
In the December 2011 extension
notice for comments on the October
2011 SNOPR, DOE requested comment
on the CA IOUs’ suggestion that the test
procedure should measure P1 at a
temperature that is 3–5 °F above the
manufacturer’s reported ‘‘off’’ set point
and measure P2 at a temperature that is
3–5 °F lower than the ‘‘on’’ set point. 76
FR 79135 (Dec. 21, 2011). The Joint
Efficiency Advocates commented in
support of the CA IOU proposal. (Joint
Efficiency Advocates, No. 43 at p. 2)
However, they also reiterated that
crankcase heater power for systems with
variable wattage should be tested at
three temperatures, namely, 3–5 °F
below the ‘‘on’’ set point temperature,
47 °F, and 17 °F. (Joint Efficiency
Advocates, No. 43 at p. 2)
AHRI commented that DOE should
modify the test procedure by having up
to three rating temperatures, depending
on the manufacturer control protocol.
The first test would be conducted at 72
°F immediately after the B, C, or D test
to verify whether the crankcase heater is
on. The second test would be conducted
at 5 °F below the temperature at which
the manufacturer specifies the crankcase
heater turns on. The third test would be
conducted at 5 °F below the temperature
at which the crankcase heater turns off
and would only apply to air
conditioners with crankcase heater
controls that turn off the crankcase
heater during winter. AHRI commented
that it could accept the CA IOUs
proposal to test at 3–5 °F below the
heater turn-on temperature and at 3–5
°F above the heater turn-off temperature
if DOE did not accept AHRI’s proposal.
(AHRI, No. 41 at p. 2) Goodman
commented in support of AHRI’s
recommendation. (Goodman, No. 42 at
p. 1)
Many of the commenters’
recommended changes are reflected in
this proposed rule. DOE proposes to
require manufacturers to include in
certification reports the temperatures at
which the crankcase heater is designed
to turn on and turn off for the heating
season, if applicable. These
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temperatures are used in the proposed
tests described in the following
paragraphs.
DOE proposes to replace the off mode
test at 82 °F with a test at 72±2 °F and
replace the off mode test at 57 °F with
a test at a temperature which is 5±2 °F
below a manufacturer-specified turn-on
temperature. This approach maintains
the intent of the off mode power
consumption rating (PW,OFF) as a
representation of the off mode power
consumption for the shoulder and
heating seasons, addresses AHRI’s
proposed modification of the test
procedure, and addresses ACEEE and
ASAP’s concerns regarding the potential
for a loophole at the 57 °F test point.
DOE does not propose to adopt an
additional test point at a temperature of
17 °F, as recommended by the
stakeholders; (Efficiency Advocates, No.
35 at p. 4; AHRI, No. 41 at p. 2) at a
temperature 5 °F below the temperature
at which the crankcase heater turns off,
as recommended by AHRI; (AHRI, No.
41 at p. 2) or at a temperature 3–5 °F
above the heater turn-off temperature, as
recommended by the CA IOUs and the
Joint Efficiency Advocates. (CA IOUs,
No. 33 at p. 2; Joint Efficiency
Advocates, No. 35 at p. 3) Manufacturer
literature provides data on variable
wattage crankcase heaters, otherwise
known as self-regulating crankcase
heaters, which show that power input
for such heaters is a linear function of
outdoor ambient temperature (i.e., the
input power can be represented with
insignificant error as a constant times
the outdoor ambient temperature plus
another constant). As such, DOE
maintains that two test points are
adequate for characterizing the off mode
power consumption for self-regulating
crankcase heaters by establishing a
linear fit from the two test outputs. DOE
also believes that one of the two test
points is adequate for characterizing the
off mode power consumption for
constant wattage crankcase. DOE does
not believe that the additional accuracy
gained from additional test points
merits the additional test burden. The
modifications in this proposal should
help to minimize the test burden while
maintaining the accuracy of off mode
power ratings. DOE requests comments
on these proposals.
2. Calculation and Weighting of P1 and
P2
Stakeholders submitted comments
discussing the most appropriate way to
weight P1 and P2 in order to measure
the total off mode power draw. In the
October 2011 SNOPR, DOE proposed to
require calculation of the total off mode
power consumption based upon an
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69301
arithmetic mean of the power readings
P1 and P2. 76 FR 65616, 65621 (Oct. 24,
2011).
The Joint Efficiency Advocates
opposed the DOE’s proposal in the
October 2011 SNOPR. (Joint Efficiency
Advocates, No. 35 at p. 4) The CA IOUs
proposed to weight P1 by 25% and P2
by 75%, because this weighting would
be more representative of actual heater
operation than equally weighting P1 and
P2. (Joint Utilities, No. 33 at p. 2)
Conversely, Goodman and AHRI
opposed the CA IOUs’ proposal because
there was inadequate data available to
support weighting P1 by 25% and P2 by
75%. Further, Goodman and AHRI
stated that the CA IOUs’ proposal would
not fairly differentiate between products
with different crankcase heater turn-on
and turn-off temperatures. A unit with
a lower turn-on and a higher turn-off
temperature would consume less overall
energy, but a manufacturer would have
no incentive to use the lowest possible
temperatures because the rating would
not change. (Goodman, No. 42 at p. 2;
AHRI, No. 41 at p. 3)
AHRI, Goodman, and the Joint
Efficiency Advocates suggested that
average power should be calculated by
weighting the off mode hours using a
bin method, in a manner consistent with
the calculations of seasonal activemode. (AHRI, No. 41 at p.3; Goodman,
No. 42 at p. 1; Joint Efficiency
Advocates, No. 35 at p. 5; Joint
Efficiency Advocates, No. 43 at p. 3)
AHRI provided a detailed methodology
for calculating the off mode power
rating in an excel spreadsheet submitted
with its written comments. (AHRI, No.
41 at p. 2) AHRI introduced bin
calculations to calculate seasonal P1
and P2 values, including recommending
a different set of fractional bin-hours for
the shoulder season. Goodman
supported AHRI’s proposal. (Goodman,
No. 42 at p. 1) However, AHRI and
Goodman commented that if DOE did
not accept AHRI’s proposed calculation,
DOE should implement a 50%
weighting of P1 and P2 as proposed in
the October 2011 SNOPR. (AHRI, No. 41
at p. 3; Goodman, No. 42 at p. 2)
After reviewing the Off-Mode Power
excel spreadsheet from AHRI and the
comments received from stakeholders,
DOE retains its proposal from the
October 2011 SNOPR, which gives equal
weighting to P1 and P2 for the
calculation of the off mode power rating
(PW,OFF). 76 FR 65616, 65620 (Oct. 24,
2011). Comments from the stakeholders
did not provide any data that support
selection of specific weights for P1 and
P2. Therefore DOE cannot confirm that
AHRI’s suggested temperature bin-hour
calculation method is representative of
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the off mode power for the shoulder and
heating seasons.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
3. Products With Large, Multiple or
Modulated Compressors
In the October 2011 SNOPR, DOE
proposed to adjust the measured off
mode power draw for systems with
multiple compressors and apply a
scaling factor to systems larger than 3
tons. 76 FR at 65621–22. The CA IOUs
and the Joint Efficiency Advocates
disagreed with DOE’s approach. (Joint
Efficiency Advocates, No. 35 at p. 5; CA
IOUs, No. 33 at p. 2; CA IOUs, No. 40
at p. 1) The CA IOUs commented that
adjusting the off mode power draw for
systems with multiple compressors and
applying a scaling factor to extra-large
systems would not represent actual off
mode power consumption and
recommended that DOE not reduce the
calculated off mode power based on the
number of compressors. (CA IOUs, No.
33 at p. 2)
AHRI and Goodman disagreed with
CA IOUs’ suggestion to eliminate the
adjustment based on the number of
compressors as it may potentially
discourage the development and use of
higher efficiency products. (AHRI, No.
36 at p. 2; AHRI, No. 41 at p. 3;
Goodman, No. 42 at p. 2) Moreover,
AHRI requested that a similar credit be
given to products using modulating
compressors due to the typical
application where a higher charge is a
requirement of the high efficiency
systems. (AHRI, No. 36 at p. 2) AHRI
also disagreed with the idea of
eliminating the scaling factor proposed
for rating larger compressors. (AHRI,
No. 41 at p. 3) Lastly, AHRI
recommended that the measurement of
the off mode power consumption and of
the low-voltage power from the controls
for the shoulder season be divided by
the number of compressors or number of
discrete controls, as is currently done
for the measurements in the heating
season. (AHRI, No. 36 at p. 2)
DOE is aware that some systems may
require higher wattage heaters to protect
system reliability. Specifically, largercapacity units may have larger-capacity
compressors, which (at a high level)
have larger shells with more surface
area that can cool them off, thus
requiring more heater wattage. They
may also have more lubricant, thus it
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takes more heater wattage to heat up the
lubricant to acceptable level (for
example after a power outage) before
restart. To avoid situations that force
manufacturers to potentially
compromise the reliability of their
systems by downsizing crankcase heater
wattages to meet off mode power
requirements, DOE proposes to retain
the recommended scaling factor for
large capacity systems.
Additionally, DOE does not want to
penalize manufacturers of multiple
compressor systems, which are highly
efficient but also need to employ larger
crankcase heaters for safe and reliable
operation given the additional shell
surface area and lubricant. Therefore,
DOE agrees with AHRI’s
recommendation and proposes that the
off mode power consumption for the
shoulder season and heating season, as
well as the low-voltage power from the
controls, be divided by the number of
compressors to determine off mode
power consumption on a percompressor basis.
The direct final rule also did not
consider the possible applicability of
the new off mode standards to highefficiency air conditioners and heat
pumps that achieve high SEER and
HSPF ratings using both large heat
exchangers and compressor modulation.
The correlation of the use of modulating
compressors with high refrigerant
charge, which is indicative of larger heat
exchangers, was mentioned in the AHRI
comment. (AHRI, No. 41 at p. 3) DOE
does not want to penalize manufacturers
for selling high efficiency units.
Therefore, DOE agrees with AHRI’s
recommendation to apply a multiplier
to the calculation of the per-compressor
off mode power for the shoulder season
and heating season for modulated
compressors, but proposes a multiplier
of 1.5, as modulating technology is not
a multiple-compressor technology (with
a multiplier of 2+). DOE requests
comment on the multiplier of 1.5 for
calculating the shoulder season and
heating season per-compressor off mode
power for modulated compressors.
4. Procedure for Measuring Low-Voltage
Component Power
In the October 2011 SNOPR, DOE
proposed to measure the power from
low-voltage components, Px, after each
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of the two tests conducted at T1 and T2.
76 FR 65628–30. Although this would
ensure that the low-voltage power
consumption at each temperature test
point would be removed from the
respective off mode power
consumption, AHRI expressed concern
about excessive manufacturer test
burden. AHRI recommended that Px not
be re-measured, as it does not change
with temperature and not re-measuring
it avoids automatic and unwanted
operation of the crankcase heater.
(AHRI, No. 36 at p. 3)
DOE agrees with AHRI that the low
voltage power consumption does not
change with temperature, although
slight and insignificant fluctuations in
the low-voltage power may occur due to
the relationship of resistivity and
conductivity to temperature. Moreover,
DOE does not believe that these
fluctuations outweigh the test burden
added from reconfiguring the system for
measuring the low-voltage power a
second time. As such, the test procedure
has been revised so that the
measurement of Px is not repeated. DOE
proposes to require that the
measurement of Px occur after the
measurement of the heating season total
off mode power, P2x, which reduces test
burden by requiring a single
disconnection of the low-voltage wires.
Additionally, DOE is aware that many
control types exist for crankcase heaters,
and certain control methodologies cycle
the crankcase heater on and off during
the 5-minute interval during which Px is
being measured. Since Px measures the
power of functioning components, only
non-zero values of measured power
should be used in the calculations. DOE
has therefore included in the proposed
test procedure a requirement to record
only non-zero data for the determination
of Px.
5. Revision of Off-Mode Power
Consumption Equations
As a result of the proposed revisions
to the test procedure discussed in
section III.D.3 and section III.D.4, the
equations from the October 2011
SNOPR for determining P1 for crankcase
heaters without controls and for
determining P2 for crankcase heaters
with controls are simplified in this
proposal. The revised equations are:
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69303
section III.D.3); (2) The value of Px
would not vary with temperature and
would thus be the same at T1 as it is at
T2 (as discussed in section III.D.4); (3)
The following would apply under the
proposed method: P2 = P2x ¥ Pxi P1 =
P1x ¥ Px. (As discussed in the October
2011 SNOPR at 76 FR 65629). Applying
the three premises to the equations for
P1 and P2 from the October 2011
SNOPR results in the following
simplification:
required to be tested to determine off
mode power consumption.
Additionally, upon reviewing the test
procedures of furnace products, DOE
found that the indoor off mode power in
coil-only split-systems (that would be
installed in the field with a furnace) was
accounted for in the furnace test
methodology. The indoor power for
coil-only systems consists of the
controls for the electronic expansion
valve drawing power from control
boards either indoor in the furnace
assembly or outdoor in the condensing
unit. To avoid double-counting indoor
off mode power between two products,
DOE proposes to exclude measurement
of the low-voltage power if the controls
for the indoor components receive
power from a control board dedicated to
a furnace assembly. For blower coil
indoor units in which the air mover is
a furnace, the same proposal applies.
For blower coil indoor units in which
the designated air mover is not a
furnace, since the off mode power of the
indoor components is not accounted for
in any other product’s test methodology,
DOE proposes to adopt language to
include the low-voltage power from the
indoor unit when measuring off mode
power consumption for blower coil
systems.
7. DOE requests comment on its
proposal to exclude low-voltage power
from the indoor unit when measuring
off mode power consumption for coilonly split-system air conditioners and
for blower coil split system air
conditioners for which the air mover is
a furnace. DOE also requests comment
on its proposal to include the lowvoltage power from the indoor unit
when measuring off mode power
consumption for blower coil splitsystem air conditioners with an indoor
blower housed with the coil and for heat
pumps.
AHRI commented that language in the
October 2011 SNOPR may have caused
stakeholders to infer that every blower
coil indoor unit combination and every
coil-only indoor unit combination must
be tested to determine off mode power
consumption. (AHRI, No. 36 at p. 2)
AHRI recommended that DOE only
require testing of the outdoor
condensing unit for the highest salevolume combination of each basic
model to determine the off mode power
consumption and allow use of an
alternative rating method (ARM) to
reduce test burden. (AHRI, No. 36 at p.
2)
In this SNOPR, DOE proposes
generally that each basic model would
be required to have all applicable
represented values (SEER, EER, HSPF,
or PW,OFF) of a specified individual
combination determined through
testing. The other individual
combinations within each basic model
may be tested or rated using AEDMs. As
such, only one individual combination
within each basic model would be
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Time Delay Credit
To provide an additional incentive for
manufacturers to reduce energy
consumption, AHRI and Goodman
suggested adding a credit for crankcase
heaters that incorporate a time delay
before turning on during the shoulder
season. (AHRI, No. 41 at p. 2; Goodman,
No. 42 at p. 1) The off mode period in
the calculation methodology designates
extended periods during which the unit
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The proposed revisions to section
III.D.3 (per-compressor representation of
P1) and section III.D.4 (temperatureindependence of Px) of this notice allow
for the simplification of the equations
that would be used to calculate power
for crankcase heaters with or without
controls. The two proposed revisions
are based on the following three
premises: (1) The representations of P1
and P2 would both be calculated on a
per-compressor basis (as discussed in
6. Off-Mode Power Consumption for
Split Systems
tkelley on DSK3SPTVN1PROD with PROPOSALS2
respectively. 76 FR 65616, 65629–30
(Oct. 24, 2011). P1D is the off mode
power with the crankcase heater
disconnected, which is equal to the lowvoltage power, Px. P1x is the shoulderseason total off mode power, P2x is the
heating-season total off mode power, P1
is the per-compressor shoulder-season
total off mode power, and P2 is the percompressor heating-season total off
mode power.
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tkelley on DSK3SPTVN1PROD with PROPOSALS2
is idle. DOE proposes to adopt an energy
consumption credit that would be
proportional to the duration of the
delay, as implemented in the
calculation of the off mode energy
consumption for the shoulder season,
E1, in the proposed off mode test
procedure. DOE is also proposing, for
products in which a time delay relay is
installed but the duration of the delay
is not specified in the manufacturer’s
installation instructions shipped with
the product or in the certification report,
a default period of non-operation of 15
minutes out of every hour, resulting in
a 25% savings in shoulder-season off
mode energy consumption. To reduce
potential instances of the misuse of this
incentive, DOE also proposes requiring
manufacturers to report the duration of
the crankcase heater time delay for the
shoulder season and heating season that
was used during certification testing.
DOE is also considering adding a
verification method to 429.134. DOE
requests comment on the proposed
method for accounting for the use of a
time delay, the default period of nonoperation, and the possibility of a
verification test for length of time delay.
8. Test Metric for Off-Mode Power
Consumption
The June 2010 NOPR proposed a test
procedure that would measure the
average off mode power consumption,
PW,OFF, of a central air conditioner or
heat pump. 75 FR 31238–39.
Additionally, the amended energy
conservation standards for central air
conditioners and heat pumps in the
June 2011 DFR included standards for
off mode power consumption that were
defined in terms of PW,OFF. 76 FR 37408,
37411. The Joint Efficiency Advocates
and the CA IOUs commented that the
test procedure should calculate energy
use and not average power draw. (Joint
Efficiency Advocates, No. 43 at p. 3; CA
IOUs, No. 33 at p. 1) The CA IOUs
stated that DOE should measure energy
use because control systems on the
crankcase heater can save power by
reducing run time, which is not
captured by a power-draw metric. (CA
IOUs, No. 33 at p. 1) The Joint
Efficiency Advocates also requested that
any standards promulgated should be
based on energy use. (Joint Efficiency
Advocates, No. 43 at p. 2) To maintain
consistency with the off mode
standards, the test procedure must
measure off mode power consumption
rather than energy use. However, DOE
recognizes that adopting a bin-based
approach to calculate PW,OFF does not
provide a final off mode value that is
indicative of actual power consumption.
DOE is aware of alternative methods to
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determine a power rating. However, in
consideration of testing burden, DOE
proposes to implement a method of
calculation that would closely
approximate the actual off mode power
consumption via a simple average of the
shoulder and heating season measured
values. Although this metric will not
directly translate into instantaneous off
mode power consumption, annual
energy costs, or national energy
consumption, it does provide a
standardized method of calculation that
is representative of average off mode
power consumption. The average off
mode power calculation can be used for
ranking models based on their
performance when idle, as well as for
comparing a model’s performance to the
DOE standards.
DOE is aware that measurement of
energy use for a specified test period
would enable calculation of annual
energy consumption and operating costs
and, on a larger scale, national energy
savings and national energy
consumption solely due to equipment
idling. Therefore, DOE has proposed
optional equations that a manufacturer
could use to determine the actual off
mode energy consumption, based on the
hours of off mode operation and off
mode power for the shoulder and
heating seasons, to provide additional
information to consumers. Energy
consumption would be specific to a
single location and its unique set of
cooling, heating, and shoulder season
hours. DOE requests comment on such
equations.
9. Impacts on Product Reliability
AHRI and Bristol Compressors
submitted comments expressing
concern that regulating crankcase heater
energy consumption could have a
negative impact on product reliability
(AHRI, No. 41 at pp. 1–2; Bristol, No. 39
at p. 1) Bristol Compressors remarked
that simply turning the crankcase heater
off at specific outdoor ambient
temperatures would expose many
compressors to conditions that would
reduce the effective life of the product
or, at worst, cause immediate failure.
Bristol requested that DOE allow
additional time for research on
technological options that could save
energy in a manner similar to controls
based on outdoor ambient temperature,
but that do not impact the reliability of
the product. (Bristol, No. 39 at p. 1)
AHRI asked DOE to conduct further
research to determine if regulating
crankcase heater energy consumption
has a negative impact on product
reliability and to consider additional
amendments to the test procedure, if
deemed necessary, to limit impacts on
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product reliability. (AHRI, No. 41 at p.
2)
DOE expects that this proposed off
mode test method will allow
manufacturers to meet the June 2011 off
mode standards without causing a shift
in the reliability of the overall market of
central air conditioners and heat pumps.
DOE requests comments on the issue of
compressor reliability as it relates to
crankcase heater operation in light of
the test method proposed in this rule.
10. Representative Measurement of
Energy Use
In the April 2011 SNOPR DOE
proposed modifications to the
laboratory tests and algorithms for
determining the off mode power of
central air conditioners and heat pumps.
76 FR 18105, 18107–09 (April 1, 2011).
DOE received comments indicating that
the April 2011 SNOPR was overly
burdensome, and the October 2011
SNOPR proposed a revised method that
was intended to reduce this burden. 76
FR 65616 (Oct. 24, 2011).
Following the October 2011 SNOPR,
the Joint Efficiency Advocates stated
that, while minimizing test burden is
important, DOE is also obligated by
statute to prescribe a test procedure that
measures the energy use of a covered
product during a representative average
use cycle or period of use. (42 U.S.C.
629(b)(3)) The Joint Efficiency
Advocates stated that the Department’s
proposal was far from accomplishing
that statutory requirement. (Joint
Efficiency Advocates, No. 35 at p. 2)
The CA IOUs noted that the test
procedure revisions presented in the
October 2011 SNOPR would not
encourage innovative designs of heating
systems in off mode, and that the results
produced by the test procedure would
be misleading to consumers, because the
reported values would not be indicative
of actual power draw if DOE were to
require measurements based on fixed
outdoor temperatures and use a simple
average of P1 and P2. (CA IOUs, No. 33
at p. 1)
However, in the December 2011
extension notice, DOE proposed to
consider the suggestion by the CA IOUs
to use the actual outdoor temperatures
at which the crankcase heater turns on
or off to measure P1 and P2, as
discussed in section III.D.2. The CA
IOUs subsequently submitted comments
that reaffirmed this proposal, and
recommended that DOE consider its
proposals to use a weighted average of
P1 and P2 and to not adjust power draw
for systems with multiple compressors
or large-capacity systems. (CA IOUs, No.
40 at p.1) The Joint Efficiency
Advocates conveyed strong support for
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the CA IOUs’ proposal and remarked
that the test procedure would not be
indicative of actual energy use if DOE
did not adopt the CA IOUs’ proposal.
(Joint Efficiency Advocates, No. 43 at p.
1; Joint Efficiency Advocates, No. 43 at
p. 3)
As previously discussed, DOE must
develop test procedures to measure
energy use that balance test burden with
measurement accuracy. The off mode
test procedures published in the original
NOPR and the first SNOPR were judged
by stakeholders to be too complex and
burdensome. As a result, DOE proposed
a test method in the second SNOPR that
was simplified and designed to result in
comparatively less test burden. The
simplified test procedure, however, may
have impacted the ability to provide a
measurement that is representative of an
average use cycle or period of use. In
this third SNOPR, DOE has made
additional revisions and believes that
this new proposed off mode test
procedure limits test burden to a
reasonable extent and will provide a
means for measuring off mode power
use in a representative manner.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
E. Test Repeatability Improvement and
Test Burden Reduction
42 U.S.C. 6293(b)(3) states that any
test procedure prescribed or amended
shall be reasonably designed to produce
test results which measure energy
efficiency and energy use of a covered
product during a representative average
period of use and shall not be unduly
burdensome to conduct. This section
discusses proposals to improve test
procedure clarity and to reduce test
burden. None of the proposals listed in
this section would alter the average
measured energy consumption of a
representative set of models.
1. Indoor Fan Speed Settings
Indoor unit fan speed is typically
adjustable during test set-up to assure
that the provided air volume rate is
appropriate for the field-installed
ductwork system serving the building in
which the unit is actually installed. The
DOE test procedure accounts for these
variable settings by establishing specific
requirements for external static pressure
and air volume rate during the test. For
an indoor coil tested with an indoor fan
installed, DOE’s test procedure requires
that (a) external static pressure be not
less than a minimum value that depends
on cooling capacity 11 and product class,
ranging from 1.10 to 1.20 inches of
water column (in. wc.) for small-duct,
high-velocity systems and from 0.10 to
11 Or heating capacity for heating-only heat
pumps.
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0.20 in. wc. for all other systems except
non-ducted units (see 10 CFR part 430,
subpart B, Appendix M, Table 2); and
(b) the air volume rate divided by the
total cooling capacity not exceed a
maximum value of 37.5 cubic feet per
minute of standard air (scfm) per 1000
Btu/h of cooling capacity 12 (see 10 CFR
part 430, subpart B, Appendix M,
Section 3.1.4.1.1).
Requirement (a) is more easily met
using higher fan speeds, while
requirement (b) is more easily met by
lower fan speeds. DOE realizes that
more than one speed setting may meet
both the minimum static pressure and
the maximum air volume rate
requirements. Section 3.1.4.1.1(a)(6) of
the current DOE test procedure for air
conditioners and heat pumps allows
adjustment of the fan speed to a higher
setting if the first selected setting does
not meet the minimum static pressure
requirement at 95 percent of the cooling
full-load air volume rate.13 This step
suggests that common test practice
would be to initially select lower fan
speeds to meet the requirements before
attempting higher speeds. However, the
test procedure does not, for cases in
which two different settings could both
meet the air volume rate and static
pressure requirements, explicitly
specify that the lower of the two settings
should be used for the test. The fan
power consumption would generally be
less at lower speeds, but compressor
power consumption may be reduced at
conditions of higher air volume rate—
hence it is not known prior to testing
whether a higher or lower air volume
rate will maximize the SEER or HSPF
for a given individual model. However,
DOE is aware that efficiency ratings are
generally better when products are
tested at the lowest airflow-control
settings intended for cooling (or heating)
operation that will satisfy both the
minimum static pressure and maximum
air volume rate requirements. DOE
therefore proposes that blower coil
products tested with an indoor fan
installed be tested using the lowest
speed setting that satisfies the minimum
static pressure and the maximum air
volume rate requirements, if applicable,
if more than one of these settings
satisfies both requirements. This is
addressed in section 2.3.1.a of
Appendix M.
12 Such a requirement does not exist for heatingonly heat pumps.
13 For heating-only heat pumps, Section
3.1.4.4.3(a)(6) allows adjustment of the fan speed to
a higher setting if the first selected setting does not
meet the requirements minimum static pressure
requirement at 95 percent of the heating full-load
air volume rate.
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For a coil-only system, i.e., a system
that is tested without an indoor fan
installed, the pressure drop across the
indoor unit must not exceed 0.3 inches
of water for the A test (or A2 test for twocapacity or variable-capacity systems),
and the maximum air volume rate per
capacity must not exceed 37.5 cubic feet
per minute of standard air (scfm) per
1000 Btu/h. (10 CFR part 430, subpart
B, Appendix M, Section 3.1.4.1.1) For
such systems, higher air volume rates
enhance the heat transfer rate of the
indoor coil, and therefore may
maximize the measured system capacity
and efficiency. In addition, the energy
use and heat input attributed to the fan
energy for such products is a fixed
default value in the test procedure, and
is set at 365 W per 1,000 scfm (10 CFR
part 430, subpart B, Appendix M,
Section 3.3(d)). Thus, the impact from
fan power on the efficiency
measurement if air volume rate is
increased may be more modest than for
a unit tested with the indoor fan
installed. However, a maximum external
static pressure of 0.3 in. wc. is specified
for the indoor coil assembly in order to
represent the field-installed conditions.
To minimize potential testing variability
due to the use of different air volume
rates, DOE proposes to require for coilonly systems for which the maximum
air flow (37.5 scfm/1000 Btuh) or
maximum pressure drop (0.3 in wc) are
exceeded when using the specified air
flow rate, the highest air flow rate that
satisfies both the maximum static
pressure and the maximum air volume
rate requirements should be used. This
is specified in section 3.1.4.1.1.c of
Appendix M.
Improper fan speed implemented
during testing may have a marked
impact on product performance, and
inconsistent implementation of speed
adjustments may be detrimental to test
repeatability. DOE therefore proposes to
require that manufacturers include in
their certification report the speed
setting and/or alternative instructions
for setting fan speed to the speed upon
which the rating is based.
For consistency with the furnace fan
test procedure, DOE proposes to add to
Appendix M (and also Appendix M1)
the definition for ‘‘airflow-control
setting’’ that has been adopted in
Appendix AA to refer to control settings
used to obtain fan motor operation for
specific functions.
DOE requests comment on its
proposals regarding requirements on fan
speed settings during test setup.
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2. Requirements for the Refrigerant
Lines and Mass Flow Meter
Section 2.2(a) of 10 CFR part 430,
subpart B, Appendix M provides
instructions for insulating the ‘‘lowpressure’’ line(s) of a split-system. In the
cooling mode, the vapor refrigerant line
connecting the indoor and outdoor units
is operating at low refrigerant pressure.
However, in the heating mode, the
vapor refrigerant line connecting the
indoor and outdoor units operates at
high pressure, providing high pressure
vapor to the indoor unit. To improve
clarity and ensure that the language of
the test procedure refers specifically to
the actual functions of the refrigerant
lines, DOE proposes to refer to the lines
as ‘‘vapor refrigerant line’’ and ‘‘liquid
refrigerant line’’.
Section 2.2(a) of 10 CFR part 430,
subpart B, Appendix M and AHRI 210/
240–2008 Section 6.1.3.5 both require
insulation on the vapor refrigerant line
and do not state what insulation, if any,
is required on the liquid refrigerant line.
Differences in product design and in the
parts manufacturers decide to ship with
the unit may lead to varying
interpretations regarding the need to
insulate the liquid refrigerant line
during the test and may therefore
introduce test variability. Furthermore,
there may be unnecessary burden on
test laboratories if they choose to add
insulation when manufacturers do not
to ship liquid refrigerant line insulation
with the unit. While DOE wishes to
clarify requirements for insulation of
refrigerant lines, there are two factors
that make such a determination
difficult: (1) There may be reasons both
for insulating and for not insulating the
liquid refrigerant tubing—if not
insulated, additional subcooling of the
refrigerant liquid as it passes through
the line prior to its expansion in the
indoor unit may increase cooling
capacity and thus increase the measured
SEER. However, the increased
subcooling of the liquid would increase
the load on the outdoor coil during the
heating mode of a heat pump, which
may slightly reduce evaporating
temperature and thus both reduce heat
pump capacity and increase compressor
power input. On the other hand,
insulating the liquid line would result
in higher measurements of HSPF for a
heat pump when compared with
measurements with the liquid line not
insulated, but would result in lower
measurements of the SEER; (2) DOE has
observed that installation manuals for
air conditioners and heat pumps
generally indicate that liquid lines
should be insulated in special
circumstances (e.g., running the line
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through a warm space or extra-long
refrigerant line runs), but do not provide
guidance on the use of insulation in the
absence of such conditions.
Because DOE seeks to minimize test
variability associated with the use of
insulation, this notice includes a
proposal for determining the insulation
requirement for the test based on the
materials and information included by
the manufacturer with the test unit.
Under this proposal, test laboratories
would install the insulation shipped
with the unit. If the unit is not shipped
with insulation, the test laboratory
would install the insulation specified in
the installation manuals included with
the unit by the manufacturer. Should
the installation instructions not provide
sufficient guidance on the means of
insulating, liquid line insulation would
be used only if the product is a heatingonly heat pump. These proposed
requirements are intended to reduce test
burden and improve test repeatability
for cooling and heating products, as
well as heating-only products. DOE
requests comment on its proposal to
require that test laboratories install the
insulation included with the unit or, if
insulation was not furnished with the
unit, follow the insulation specifications
in the manufacturer’s installation
instructions. DOE also requests
comment on its proposal to require
liquid line insulation of heating-only
heat pumps.
In cases where the refrigerant
enthalpy method is used as a secondary
measurement of indoor space
conditioning capacity, uninsulated
surfaces of the refrigerant lines and the
mass flow meter may also contribute to
thermal losses. DOE does not believe
that preventing the incremental thermal
losses associated with the mass flow
meter components and its support
structure would make a measurable
impact on efficiency measurements.
However, DOE does recognize the
possibility that thermal loss might
reduce the efficiency measurement,
particularly during heating mode tests if
the mass flow meter is placed on the test
chamber floor, which might be cooler
than the air within the room. To
enhance test repeatability among
various laboratories that may use
different mass flow meters with varying
materials for support structures, DOE
proposes to require use of a thermal
barrier to prevent such thermal transfers
between the flow meter and the test
chamber floor if the meter is not
mounted on a pedestal or other support
elevating it at least two feet from the
floor. DOE proposes to add these
requirements to Appendix M, section
2.10.3. DOE requests comment on this
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means to prevent meter-to-floor thermal
transfer.
3. Outdoor Room Temperature Variation
Depending on the operating
characteristics of the test laboratory’s
outdoor room conditioning equipment,
temperature or humidity levels in the
room may vary during testing. For this
reason, a portion of the air approaching
the outdoor unit’s coil is sampled using
an air sampling device (see Appendix
M, section 2.5). The air sampling device,
described in ASHRAE Standard 41.1–
2013, consists of multiple manifolded
tubes with a number of inlet holes, and
is often called an air sampling tree. If,
during testing, the air entering the
outdoor unit of a product is monitored
only on one of its faces and there is
significant spatial variation of the
room’s air conditions, the measured
conditions for the monitored face may
not be indicative of the average
conditions for the inlet air across all
faces.
To ensure that the measurements
account for variation in the conditions
in the outdoor room of the test chamber,
DOE proposes to require demonstration
of air temperature uniformity over all of
the air-inlet surfaces of the outdoor unit
using thermocouples, if sampling tree
air collection is performed only on one
face of the outdoor unit. Specifically,
DOE would require that the
thermocouples be evenly distributed
over the inlet air surfaces such that
there is one thermocouple measurement
representing each square foot of air-inlet
area. The maximum temperature spread
to demonstrate uniformity, i.e., the
maximum allowable difference in
temperature between the measurements
at the warmest location and at the
coolest location, would be 1.5 °F (DOE
proposes to add these requirements to
Appendix M, section 2.11.b). This is the
same maximum spread allowable for
measurement of indoor unit capacity
using thermocouple grids, as described
in 10 CFR part 430, subpart B,
Appendix M, Section 3.1.8, in which
the maximum spread among the
measured temperatures on the
thermocouple grid in the outlet plenum
of the indoor coil must not exceed 1.5 °F
dry bulb. If this specified measurement
of temperature uniformity cannot be
demonstrated, DOE would require
sampling tree collection of air from all
air-inlet surfaces of the outdoor unit.
DOE seeks comment for the proposed
1.5 °F maximum spread for
demonstration of outdoor air
temperature uniformity, the proposed
one square foot per thermocouple basis
for thermocouple distribution, and the
proposed requirement that an air
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sampling device be used on all outdoor
unit air-inlet surfaces if temperature
uniformity is not demonstrated. DOE
proposes to add these requirements to
Appendix M, section 2.11.b.
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4. Method of Measuring Inlet Air
Temperature on the Outdoor Side
To ensure test repeatability, DOE
seeks to ensure that temperature
measurements taken during the test are
as accurate as possible. DOE is aware
that measurement of outdoor inlet
temperatures is commonly based on
measurements of the air collected by
sampling devices that use high-accuracy
dry bulb temperature and humidity
measurement devices, and that the
accuracy of these devices may be better
than that of thermocouples. DOE
proposes to require that the dry bulb
temperature and humidity
measurements, that are used to verify
that the required outdoor air conditions
have been maintained, be measured for
the air collected by the air sampling
devices (e.g., rather than being
measured by temperature sensors
located in the air stream approaching
the air inlets). DOE requests comment
on this proposal.
5. Requirements for the Air Sampling
Device
In evaluating various test setups and
laboratory conditions, DOE has
observed that certain setup conditions
of the air sampling equipment could
lead to measurement error or variability
between laboratories. Specifically, the
temperature of air collected by indoor
and outdoor room air sampling devices
could potentially change as it passes
through the air collection system,
leading to inaccurate temperature
measurement if the air collection
devices or the conduits conducting the
air to the measurement location are in
contact with the chamber floor or with
ambient air at temperatures different
from the indoor or outdoor room. To
prevent this potential cause of error or
uncertainty, DOE proposes to require
that no part of the room air sampling
device or the means of air conveyance
to the dry bulb temperature sensor be
within two inches of the test chamber
floor. DOE also proposes to require
those surfaces of the air sampling device
and the means of air conveyance that
are not in contact with the indoor and
outdoor room air be insulated.
A potential contributor to error or
uncertainty in the measurement of
humidity is the taking of dry bulb and
wet bulb measurements in different
locations, if there is significant cool
down of air between the two locations.
While ASHRAE Standard 41.1–2013
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provides an example of an air sampling
device with a dry bulb and wet bulb
thermometer placed close together, the
figure is merely illustrative. To
minimize measurement error or
uncertainty, DOE proposes to require
that humidity measurements and dry
bulb temperature measurements used to
determine the moisture content of air be
made at the same location in the air
sampling device.
As discussed in section III.E.14, DOE
has also proposed several amendments
to air sampling procedures that are
included in a draft revision of AHRI
210/240–2008. DOE requests comments
on all of these related proposals,
including its proposal to require that the
air sampling device and its components
be prevented from touching the test
chamber floor, to require insulation of
those surfaces of the air sampling device
and components that are not in contact
with the chamber room air, and that dry
bulb temperature and humidity
measurements used to determine the
moisture content of air be made at the
same location in the air sampling
device.
6. Variation in Maximum Compressor
Speed With Outdoor Temperature
When testing an air conditioner or
heat pump with a variable-speed
compressor, the compressor must be
tested at three different speeds:
Maximum, intermediate, and minimum.
Some air conditioners and heat pumps
with a variable-speed compressor
operate such that their maximum
allowed compressor speed varies with
the outdoor temperature. However, the
test procedure does not explicitly state
whether the maximum compressor
speed refers to a fixed value or a
temperature-dependent value. As such,
DOE proposes that the maximum
compressor speed be fixed during
testing through modification of the
control algorithm used for the particular
product such that the speed does not
change with the outdoor temperature.
DOE requests comment on this
proposal.
7. Refrigerant Charging Requirements
Near-azeotropic and zeotropic
refrigerant blends are composed of
multiple refrigerants with a range of
boiling points. Gaseous charging of
refrigerant blends is inappropriate
because it can result in higher
concentrations of the higher-vapor
pressure constituents being charged into
the unit, which can alter refrigerant
performance characteristics and thus,
unit performance. DOE recognizes that
technicians certified to handle
refrigerants via the Environment
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Protection Agency’s (EPA) Section 608
Technician Certification Program, as
mandated by 40 CFR 82.161, are
required to be knowledgeable of
charging methods for refrigerant blends.
However, to ensure consistent practices
within the context of the DOE test
procedure, DOE proposes to require that
near-azeotropic and zeotropic
refrigerant blends be charged in the
liquid state rather than the vapor state.
This is found in section 2.2.5.8 of
Appendix M. DOE requests comments
on this proposal.
Current language in Appendix M to
Subpart B of 10 CFR part 430 does not
prohibit testers from changing the
amount of refrigerant charge in a system
during the course of air conditioner and
heat pump performance tests. Changing
the amount of refrigerant may result in
a higher SEER and/or a higher HSPF
that does not reflect the actual
performance of a unit in the field. In the
June 2010 NOPR, DOE proposed to
adopt into the test procedure select
parts of the 2008 AHRI General
Operations Manual that contains
language disallowing changing the
refrigerant charge after system setup. (75
FR 31234–5) AHRI and NEEA supported
this proposal. (AHRI, No. 6 at p. 3;
NEEA, No. 7 at p. 4) To ensure that
performance tests reflect operation in
the field, and to improve consistency in
results between test facilities, DOE
intends to retain the proposal made in
the June 2010 NOPR. Specifically, DOE
retains the proposed requirement that
once the system has been charged with
refrigerant consistent with the
installation instructions shipped with
the unit (or with other provisions of the
test procedure, if the installation
instructions are not provided or not
clear), all tests must be conducted with
this charge.
DOE is aware that refrigerant charging
instructions are different for different
products, but that in some cases, such
instructions may not be provided. More
specifically, the appropriate charging
method may vary among products based
upon their refrigerant metering devices.
The thermostatic expansion valve (TXV)
type metering device is designed to
maintain a specific degree of
superheat.14 Electronic expansion valve
(EXV) type metering devices function
similarly to TXV type metering devices,
but use sensors, a control system, and
an actuator to set the valve position to
allow more sophisticated control of the
degree of superheat. Fixed orifice is
14 The degree of superheat is the extent to which
a fluid is warmer than its bubble point temperature
at the measured pressure, i.e., the difference
between a fluid’s measured temperature and the
saturation temperature at its measured pressure.
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another type of expansion device
commonly used for air conditioners. In
contrast to a TXV or EXV, a fixed orifice
does not actively respond to system
pressures or temperatures to maintain a
fixed degree of superheat. The
refrigerant charge can affect the
measured system efficiency. Systems
with different expansion devices react
differently to variation in the charge,
and they also generally require different
procedures for ensuring that the system
is properly charged. As the charging
operation may differ among these types
of metering devices, and
misidentification may lead to
inconsistent charging and unrepeatable
testing, DOE proposes to require
manufacturers to report the type of
metering device used during
certification testing.
If charging instructions are not
provided in the manufacturer’s
installation instructions shipped with
the unit, DOE proposes standardized
charging procedures to ensure
consistent testing in a manner that
reflects field practices. For a unit
equipped with a fixed orifice type
metering device for which the
manufacturer’s installation instructions
shipped with the unit do not provide
refrigerant charging procedures, DOE
proposes that the unit be charged at the
A or A2 test condition, requiring
addition of charge until the superheat
temperature measured at the suction
line upstream of the compressor is 12 °F
with tolerance discussed in section III
E.14.15 For a unit equipped with a TXV
or EXV type metering device for which
the manufacturer’s installation
instructions shipped with the unit do
not provide refrigerant charging
procedures, DOE proposes that the unit
be charged at the A or A2 condition,
requiring addition of charge until the
subcooling 16 temperature measured at
the condenser outlet is 10 °F with
tolerance discussed in section III E.14.17
For heating-only heat pumps for
which refrigerant charging instructions
are not provided in the manufacturer’s
installation instructions shipped with
the unit, the proposed standardized
15 The range of superheating temperatures was
generalized from industry-accepted practice and
state-level authority regulations on refrigerant
charging for non-TXV systems.
16 The degree of subcooling or subcooling
temperature is the extent to which a fluid is cooler
than its refrigerant bubble point temperature at the
measured pressure, i.e., the bubble point
temperature at a fluid’s measured pressure minus
its measured temperature. Bubble point temperature
is the temperate at a given pressure at which vapor
bubbles just begin to form in the refrigerant liquid.
17 The range of subcooling temperatures was
generalized from manufacturer-published and
technician-provided service instructions and are
typical of industry practice.
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charging procedure would be followed
while performing refrigerant charging at
the H1 or H12 condition. DOE also
proposes that charging be done for the
H1 or H12 test condition for cooling/
heating heat pumps which fail to
operate properly in heating mode when
charged using the standardized charging
procedure for the A or A2 test condition.
In such cases, some of the tests
conducted using the initial charge may
have to be repeated to ensure that all
tests (cooling and heating) are
conducted using the same refrigerant
charge. DOE proposes to add these
requirements to Appendix M in a new
section 2.2.5.8.
DOE requests comments on the
proposed standardized charging
procedures to be applied to units for
which the installation instructions
shipped with the unit do not provide
charging instructions.
DOE understands that manufacturers
may provide installation instructions
with different charging procedures for
the indoor and outdoor units. In such
cases, DOE proposes to require charging
based on the installation instructions
shipped with the outdoor unit for
outdoor unit manufacturer products and
based on the installation instructions
shipped with the indoor unit for
independent coil manufacturer
products, unless otherwise specified by
either installation instructions. DOE
requests comments on this proposal.
Single-package central air
conditioners and heat pumps may be
shipped with refrigerant already
charged into the unit. Verifying the
proper amount of refrigerant charge is
valuable for increasing test repeatability.
To this end, DOE believes that the
benefits of installing pressure gauges on
a single-package unit to help verify
charge and to monitor refrigerant
conditions generally outweigh the
potential drawbacks associated with
connecting the gauges (e.g., refrigerant
transfer from the product into the
gauges and hoses or refrigerant leakage);
calculating the superheat or subcooling
quantities used to determine whether
the unit is charged properly requires
knowledge of the refrigerant pressure,
and the quantity of charge transferred
from the unit when connecting a
pressure gauge set is generally a very
small percentage of the unit’s charge.
Further, assessing the refrigerant charge
may improve repeatability of the tests
and measured efficiency. DOE therefore
proposes that refrigerant line pressure
gauges be installed during the setup of
single-package and split-system central
air conditioner and heat pump products,
unless otherwise specified by the
instructions. DOE also proposes that the
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refrigerant charge be verified per the
charging instructions and, if charging
instructions are not provided in the
installation instructions shipped with
the unit, the refrigerant charge would be
verified based on the standardized
charging procedure described above.
DOE requests comments on these
proposals.
As discussed in section III.E.14, DOE
has also proposed several amendments
to charging procedures that are included
in a draft revision of AHRI 210/240–
2008. DOE requests comment on all
aspects of its proposals to amend the
refrigerant charging procedures.
8. Alternative Arrangement for Thermal
Loss Prevention for Cyclic Tests
10 CFR part 430, subpart B, Appendix
M, Section 2.5(c) requires use of damper
boxes in the inlet and outlet ducts of
ducted units to prevent thermal losses
during the OFF period of the
compressor OFF/ON cycle for the
cooling or heating cyclic tests. However,
DOE is aware that installation of such
dampers for single-package ducted units
can be burdensome because the unit
must be located in the outdoor chamber
and there may be limited space in the
chamber and in between the inlet and
outlet ducts to install the required
transition ducts, insulation, and
dampers. To preserve the intent of the
air damper boxes, reduce testing
burden, and accommodate variations in
chamber size, DOE proposes an
alternative testing arrangement to
prevent thermal losses during the
compressor OFF period that would
eliminate the need to install a damper
in the inlet duct that conveys indoor
chamber air to the indoor coil.
The proposed alternative testing
arrangement would allow the use of a
duct configuration that relies on
changes in duct height, rather than a
damper, to eliminate natural convection
thermal transfer out of the indoor duct
during OFF periods of the ‘‘cold’’ or
heat generated by the system during the
ON periods. An example of such an
arrangement would be an upturned duct
installed at the inlet of the indoor duct,
such that the indoor duct inlet opening,
facing upwards, is sufficiently high to
prevent natural convection transfer out
of the duct. DOE also proposes to
require installation of a dry bulb
temperature sensor near the inlet
opening of the indoor duct at a
centerline location not higher than the
lowest elevation of the duct edges at the
inlet. Measurement and recording of dry
bulb temperature at this location would
be required at least every minute during
the compressor OFF period to confirm
that no thermal loss occurs. DOE
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proposes a maximum permissible
variation in temperature measured at
this location during the OFF period of
±1.0 °F.
DOE seeks comment on its proposal
in section 2.5(c) of Appendix M to
allow, for cyclic tests, alternative
arrangements to replace the currentlyrequired damper in the inlet portion of
the indoor air ductwork for singlepackage ducted units. DOE also requests
comment on the proposed requirements
for ensuring that there are no thermal
losses during the OFF portion of the
test, including the location of the
proposed dry bulb temperature sensor,
the requirements for recorded
temperatures, and the ±1.0 °F allowable
variation in temperature measured by
this sensor.
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9. Test Unit Voltage Supply
The current DOE test procedure
references ARI Standard 210/240–2006
Section 6.1.3.2 for selecting the proper
electrical voltage supply, which
generally requires that, for tests
performed at standard rating conditions
(referred to as ‘‘Standard Rating tests’’ in
Standard 210/240), the tests be
conducted at the product’s nameplate
rated voltage and frequency. This
section also requires that Standard
Rating tests be performed at 230 V for
air-cooled equipment rated with 208–
230 V dual nameplate voltages, and that
all other dual nameplate voltage
equipment be tested at both voltages or
at the lower of the two voltages if only
a single Standard Rating is to be
published. DOE recognizes that
nameplate voltages may differ for indoor
and outdoor units. This may result in a
difference of voltage supplied to the
indoor and outdoor units in accordance
with the current test requirement. DOE
realizes that, in most cases, this voltage
difference that may occur during testing
is not representative of field operation
where indoor and outdoor units are
typically supplied with the same
voltage. As such, DOE proposes to
clarify that the outdoor voltage supply
requirement supersedes the indoor
requirement if the provisions result in a
difference for the indoor and outdoor
voltage supply. That is, both the indoor
and outdoor units shall be tested at the
same voltage supplied to the outdoor
unit.
10. Coefficient of Cyclic Degradation
The cooling coefficient of
degradation, C, is the ratio of the EER
measured for cycling (or intermittent)
operation to the EER that would be
measured for steady operation. The
heating coefficient of degradation, C, is
a similar factor that characterizes
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efficiency reduction for cycling
operation during heat pump operation.
The test procedures to determine these
two coefficients are the same except for
the testing conditions and unit
operation mode, and the changes
discussed in this section are applied to
both metrics. Therefore, for the sake of
simplicity and clarity, only the cooling
coefficient of degradation is discussed
here.
The current test procedure gives
manufacturers the option to use a
default cyclic degradation coefficient
(CD) value of 0.25 instead of running the
optional cyclic test. In response to the
June 2010 NOPR, which proposed some
modifications related to the optional
tests but not the default value, NEEA
commented that its laboratory testing
demonstrated that the default value 0.25
is not representative of system
performance, especially for TXVequipped systems, and instead
supported using the actual tested values
in determining ratings. (NEEA, No. 7 at
pp. 6–7) DOE reviewed results from its
own testing of 19 split-system and
single-package air conditioners and heat
pumps from 1.5 to 5 tons and found that
the tested CD values range from 0.02 to
0.18, with an average of 0.09. It also
found no correlation between CD and
SEER, EER, or cooling capacity. DOE
also reviewed the AHRI 210/240-Draft
(see section III.E.14), which updates the
cooling C value to 0.2. DOE believes
this default value may be more in-line
with actual tested values, and DOE
proposes to update the default cooling
C value in Appendix M to 0.2. At this
time, DOE is not proposing to update
the default heating C value. In
evaluating appropriate default values,
DOE also reviewed its testing
requirements to measure CD.
DOE is aware of various issues that
occur when conducting the test
procedure to measure the degradation
coefficient, such as the inability to
attain stable capacity measurements
from cycle to cycle and burdensome
testing time to attain stability, and
believes that these are symptoms of
cyclic instability. DOE believes that the
variation in cooling capacity during the
test to determine C is exacerbated by
the short compressor on-time specified
for each cycle and by the effect of
response time, sensitivity, and
repeatability errors. DOE understands
the importance of having a minimally
burdensome test procedure. However,
DOE recognizes that the current test
method for measuring C, although clear
in description and intent, does not
provide requirements for cyclic stability
of measured capacity over successive
on-cycles during the test. Therefore,
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DOE proposes the following procedure
based on cyclic testing data to clarify
the test procedure, address cyclic
stability, and offer default procedures to
allow for test burden relief.
DOE has obtained cyclic test data that
show that as cycles are tested, either
capacity reaches steady-state or capacity
fluctuates constantly and consistently.
Therefore, DOE proposes that before
determining C, three ‘‘warm up’’ cycles
for a unit with a single-speed
compressor or two-speed compressor or
two ‘‘warm up’’ cycles for a unit with
a variable speed compressor must be
conducted. Then, conduct a minimum
of three complete cycles after the warmup period, taking a running average of
C after each additional cycle. If after
three cycles, the average of three cycles
does not differ from the average of two
cycles by more than 0.02, the threecycle average should be used. If it
differs by more than 0.02, up to two
more valid cycles will be conducted. If
the average C of the last three cycles
are within 0.02 of or lower than the
previous three cycles, use the average
C of all valid cycles. After the fifth
valid cycle, if the average C of the last
three cycles is more than 0.02 higher
than the previous three cycles, the
default value will be used. The same
changes are proposed for the test
method to determine the heating
coefficient of degradation.
Given these changes to address, DOE
proposes that unlike the current test
procedure, manufacturers must conduct
the specified testing required to measure
CD for each tested unit. The default
value may only be used if stability or
the test tolerance is not achieved or
when testing outdoor units with no
match.
DOE requests comment regarding the
proposed revisions to the cyclic test
procedure for the determination of both
the cooling and heating coefficient of
degradation. DOE also requests
additional test data that would support
the proposed specifications, or changes
to, the number of warm-up cycles, the
cycle time for variable speed units, the
number of cycles averaged to obtain the
value, and the stability criteria.
11. Break-In Periods Prior to Testing
On June 1, 2012, AHRI submitted a
supplement to the comments it
submitted on January 20, 2012, as part
of the extended comment period on the
October 2011 SNOPR. In these
supplementary comments, AHRI
requested that DOE implement an
optional 75-hour break-in period for
testing central air conditioners and heat
pumps. It stated that scroll compressors,
which are the type of compressors most
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commonly used in central air
conditioners and heat pumps, achieve
their design efficiency after 75 hours of
operation, so the allowance for a breakin period of this length would ensure
that the product being tested is
operating as intended by the
manufacturer and would provide a
result that is more representative of
average use. AHRI also cited a study of
compressor break-in periods to justify
this period of time,18 and added that,
while AHRI’s certification program for
central air conditioners and heat pumps
does not specify a minimum break-in
period, it does allow manufacturers to
specify a break-in period for their
products. According to AHRI’s
comments, some manufacturers request
a break-in period in excess of 100 hours,
while others request 50 hours or less.
Furthermore, AHRI commented that
implementation of an optional break-in
period for central air conditioners and
heat pumps would be consistent with a
similar provision in the DOE test
procedures for commercial heating and
air-conditioning equipment, which DOE
adopted in a final rule published May
16, 2012. 77 FR 28928. As stated in the
final rule, the purpose of including this
option for testing commercial HVAC
equipment was to ensure that the
equipment being tested would have
time to achieve its optimal performance
prior to conducting the test. DOE placed
a maximum limit of 20 hours on the
allowed period of break-in, regardless of
the break-in period recommended by
the manufacturer, explaining that such
a limit was necessary to minimize the
burden imposed by this provision. In
addition, DOE required that
manufacturers who use the optional
break-in period report the duration of
their break-in as part of the test data
underlying the certification that is
required to be maintained under 10 CFR
429.71. DOE stated that it would use the
same break-in period for any DOEinitiated testing as the manufacturer
used in its certified ratings or, in the
case of ratings based upon use of an
alternate efficiency determination
method (AEDM), the maximum 20-hour
break-in period. 77 FR 28928, 28944.
After consideration of the potential
improvement in performance and
increased test burden that may result
from implementation of an optional 75hour break-in period, DOE believes that
the lengthy break-in period is not
appropriate or justified. In reviewing the
paper that AHRI cited in its comments,
DOE noted that, while the data indicate
18 Khalifa, H.E. ‘‘Break-in Behavior of Scroll
Compressors’’ (1996). International Compressor
Engineering Conference. Paper 1145.
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that products with scroll compressors
do appear to converge upon a more
consistent result after compressor breakin periods exceeding 75 hours, the most
significant improvement in compressor
performance and reduction in variation
among compressor models both appear
to occur during roughly the first 20
hours of run time.19 Moreover, scroll
compressors in use at the time of this
paper’s publication in 1996 may have
required longer break-in periods to
address the surface quality of the
internal components resulting from the
manufacturing processes of that time,
whereas compressors in use today have
benefitted from improvements in the
manufacturing technology for scroll
compressors over the past 20 years. In
addition, while the paper also supports
AHRI’s comment that smaller
compressors require more time to reach
their optimal performance than larger
compressors, it does not show the
absolute size of the compressors that
were studied and makes comparisons
based only on their relative sizes.
Therefore, it is difficult to precisely
determine how this data would apply to
a central air conditioner or heat pump
compressor versus a commercial air
conditioner or heat pump. Finally, since
DOE determined in the May 16, 2012
commercial HVAC equipment final rule
that a 20 hour maximum break-in time
would be sufficient for small
commercial air-conditioning products,
which are of a capacity similar to
central air-conditioning products, DOE
does not see justification for a break-in
period longer than 20 hours for
products. 77 FR 28928.
In consideration of AHRI’s comments
on the merits of conducting a break-in
period prior to testing of central air
conditioners and heat pumps, DOE
proposes in this SNOPR to allow
manufacturers the option of specifying a
break-in period to be conducted prior to
testing of these products under the DOE
test procedure. However, due to the
excessive test burden that could be
imposed by allowing lengthy break-in
times, DOE proposes to limit the
optional break-in period to 20 hours,
which is consistent with the test
procedure final rule for commercial
HVAC equipment. DOE also proposes to
adopt the same provisions as the
commercial HVAC rule regarding the
requirement for manufacturers to report
the use of a break-in period and its
duration as part of the test data
underlying their product certifications,
the use of the same break-in period
specified in product certifications for
testing conducted by DOE, and use of
19 Ibid.
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the 20 hour break-in period for products
certified using an AEDM.
DOE requests comments on its
proposal to allow an optional break-in
period of up to 20 hours prior to testing
as part of the DOE test procedure for
central air conditioners and heat pumps.
12. Industry Standards That Are
Incorporated by Reference
In the June 2010 NOPR, DOE
proposed two ‘‘housekeeping’’ updates
throughout Appendix M regarding test
procedure references. 75 FR 31243. The
first is an update of the incorporation by
reference (IBR) from ARI Standard 210/
240–2006 to ANSI/AHRI 210/240–2008,
which provides additional test unit
installation requirements and
requirements on apparatus used during
testing. The second update involves
changes to references from 10 CFR
430.22 to 10 CFR 430.3, as the listing of
those materials incorporated by
reference was relocated. In the public
comment period following the NOPR,
AHRI expressed support for updating
the test procedure to reference current
AHRI and ASHRAE standards. (AHRI,
No. 6 at p. 6). DOE is maintaining its
position in the June 2010 NOPR for both
proposals and therefore implemented
the reference updates in the reprint of
Appendix M of this notice. However,
DOE proposes in this SNOPR to
incorporate by reference the 210/240
standard having the most recent
amendments at the time of this notice,
i.e., ANSI/AHRI 210/240–2008 with
Addendum 2.20 The changes
incorporated by these amendments
relate to replacing the Integrated Part
Load Value (IPLV) efficiency metric
with the Integrated Energy Efficiency
Ratio (IEER) metric, as well as adding
the methodology for determining IEER
for water- and evaporatively-cooled
products. These changes are relevant
only to commercial equipment and are
not relevant to the DOE test procedure
for central air conditioners and heat
pumps. Therefore updating references to
the latest version of ANSI/AHRI 210/
240 will not impact the ratings or energy
conservation standards for central air
conditioners and heat pumps.
In addition, in this SNOPR, DOE
proposes to update the IBR from
ASHRAE Standard 37–2005, Methods of
Testing for Rating Unitary AirConditioning and Heat Pump
Equipment to ASHRAE Standard 37–
2009, Methods of Testing for Rating
Electrically Driven Unitary AirConditioning and Heat Pump
20 ANSI/AHRI 210/240–2008 with Addendum 2
is named as such but includes changes per an
Addendum 1 on the same standard.
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Equipment; ASHRAE 41.9–2000,
Calorimeter Test Standard Methods for
Mass Flow Measurements of Volatile
Refrigerants to ASHRAE 41.9–2011,
Standard Methods for VolatileRefrigerant Mass Flow Measurements
Using Calorimeters; and ASHRAE/
AMCA 51–1999/210–1999, Laboratory
Methods of Testing Fans for
Aerodynamic Performance Rating to
ASHRAE/AMCA 51–07/210–07,
Laboratory Methods of Testing Fans for
Certified Aerodynamic Performance
Rating. None of these updates includes
significant changes to the sections
referenced in the DOE test procedure
and thus will not impact the ratings or
energy conservation standards for
central air conditioners and heat
pumps.21
Additionally, DOE proposes to update
the IBR from ASHRAE 41.1–1986
(Reaffirmed 2006), Standard Method for
Temperature Measurement to ASHRAE
41.1–2013, Standard Method for
Temperature Measurement, as well as
the IBR to ASHRAE 41.6–1994,
Standard Method for Measurement of
Moist Air Properties to ASHRAE 41.6–
2014, Standard Method for Humidity
Measurement. In the updated versions
of these standards, specifications for
measuring wet-bulb temperature were
moved from ASHRAE 41.1 to ASHRAE
41.6. None of these updates includes
significant changes to the sections
referenced in the DOE test procedure
and thus will not impact the ratings or
energy conservation standards for
central air conditioners and heat pumps.
Also, DOE proposes to update the IBR
from ASHRAE 23–2005, Methods of
Testing for Rating Positive Displacement
Refrigerant Compressors and
Condensing Units to ASHRAE 23.1–
2010 Methods of Testing for Rating the
Performance of Positive Displacement
Refrigerant Compressors and
Condensing Units That Operate at
Subcritical Temperatures of the
Refrigerant. ASHRAE 23 has been
withdrawn and has been replaced by
ASHRAE 23.1 and ASHRAE 23.2.
ASHRAE 23.2 deals with supercritical
pressure conditions, which are not
relevant to the DOE test procedure, so
will not be referenced. None of these
updates includes significant changes to
the sections referenced in the DOE test
procedure and thus will not impact the
ratings or energy conservation standards
for central air conditioners and heat
pumps.
21 ASHRAE 37–2009 only updates to more recent
versions of other standards it references. ASHRAE/
AMCA 51–07/210–07 made slight changes to the
figure referenced by DOE, which DOE has
determined to be insignificant.
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DOE also proposes to revise its
existing IBRs to AHRI 210/240–2008
with Addendums 1 and 2, ANSI/AHRI
1230–2010 with Addendum 2, ASHRAE
23.1–2010 (updated from ASHRAE 23–
2005), ASHRAE 37–2009 (updated from
2005), ASHRAE 41.1–2013 (updated
from 1986 version), ASHRAE 41.2–
1987, ASHRAE 41.6–2014 (updated
from 1994 reaffirmed in 2001 version),
ASHRAE 41.9–2011 (updated from 2000
version), and ASHRAE/AMCA 51–07/
210–07 (updated from 1999 version) to
incorporate only the sections currently
referenced or proposed to be referenced
in the DOE test procedure. DOE requests
comment on its proposed sections for
incorporation and specifically on
whether any additional sections may be
necessary to conduct a test of a unit.
DOE also proposes to revise the
definition of ‘‘continuously recorded’’
based on changes to ASHRAE 41.1.
ASHRAE 41.1–86 specified the
maximum time intervals for sampling
dry-bulb temperature. The updated
version, ASHRAE 41.1–2013 does not
contain specifications for sampling
intervals. DOE proposes to require that
dry-bulb temperature, wet bulb
temperature, dew point temperature,
and relative humidity data be
‘‘continuously recorded,’’ that is,
sampled and recorded at 5 second
intervals or less. DOE is proposing this
requirement as a means of verifying that
temperature condition requirements are
met for the duration of the test. DOE
requests comment on its revised
sampling interval for dry-bulb
temperature, wet bulb temperature, dew
point temperature, and relative
humidity.
13. Withdrawing References to ASHRAE
Standard 116–1995 (RA 2005)
In the June 2010 NOPR, DOE
proposed referencing ASHRAE Standard
116–1995 (RA 2005) within the DOE test
procedure to provide additional
informative guidance for the equations
used to calculate SEER and HSPF for
variable-speed systems. 75 FR 31223,
31243 (June 2, 2010). In the subsequent
public comment period, AHRI
expressed support for DOE’s proposal to
reference ASHRAE 116. (AHRI, No. 6 at
p. 6). However, in section III.H.4 of this
notice, DOE proposes to change the
heating load line, and as such the
equations for HSPF in ASHRAE
Standard 116 are no longer applicable.
In order to prevent confusion, DOE
proposes in this notice to withdraw the
proposal made in the June 2010 NOPR
to reference ASHRAE 116 for both HSPF
and SEER and is removing those
instances of references to said standard
from the test procedure.
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Appendix M only references ASHRAE
116 in one other location, regarding the
requirements for the air flow measuring
apparatus. Upon review, DOE has
determined that referencing ASHRAE
Standard 37 instead provides sufficient
information. As a result, in this NOPR,
DOE also proposes to revise its reference
for the requirements of the air flow
measuring apparatus to ASHRAE
Standard 37–2009 rather than ASHRAE
116, and proposes to remove the
incorporation by reference to ASHRAE
116 from the code of federal regulations
related to central air conditioners and
heat pumps.
14. Additional Changes Based on AHRI
210/240-Draft
In August 2015, AHRI provided a
draft version of AHRI 210/240 for the
docket that will supersede the 2008
version once it is published. (AHRI
Standard 210/240-Draft, No. 45, See
EERE–2009–BT–TP–0004–0045) The
draft version includes a number of
revisions from the 2008 version, some of
which already exist in DOE’s test
procedure, and some of which do not.
Regarding test installation
requirements, the AHRI 210/240-Draft
added new size requirements for the
inlet duct to the indoor unit. If used, the
inlet duct size to the indoor unit is
required to equal the size of the inlet
opening of the air-handling (blowercoil) unit or furnace, with a minimum
length of 6 inches. Regarding the testing
procedure, the AHRI 210/240-Draft
added new external static pressure
requirements for units intended to be
installed with the airflow to the outdoor
coil ducted. These new requirements
provide for testing of these products
more consistently with the way that
they are intended to be used in the field.
Also regarding the testing procedure,
the AHRI 210/240-Draft specified a new
requirement for the dew point
temperature of the indoor test room
when the air surrounding the indoor
unit is not supplied from the same
source as the air entering the indoor
unit. DOE proposes to adopt these three
revisions in this SNOPR.
The AHRI 210/240-Draft includes
several differences as compared to the
current DOE test procedure for setting
air volume rates during testing.
Specifically:
(a) Air volume rates would be
specified by the manufacturer;
(b) For systems tested with indoor
fans installed in which the fans have
permanent-split-capacitor (PSC) or
constant-torque motors, there would be
minimum external static pressure
requirements for operating modes other
than full-load cooling; and
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(c) A criterion is defined for
acceptable air flow stability for systems
tested with constant-air-volume indoor
fans (these are fans with controls that
vary fan speed to maintain a constant air
volume rate).
DOE proposes to adopt these changes
because they will improve repeatability
and the consistency of testing among
different laboratories.
The AHRI 210/240-Draft also includes
a more thorough procedure for setting of
refrigerant charge than exists in the DOE
test procedure. The new approach
addresses potential issues associated
with conflicting guidelines that might
be provided by manufacturer’s
installation instructions and indicates
how to address ranges of target values
provided in instructions. DOE is
proposing these changes because they
improve test repeatability. The AHRI
210/240-Draft also specifies both a target
value tolerance and a maximum
tolerance but does not specify in what
circumstances each of these apply. DOE
proposes to adopt the maximum
tolerance only. However, DOE may
consider adopting only the target value
tolerance or both the target value and
maximum tolerance. DOE requests
comment on the appropriate use of the
target value and maximum tolerances,
as well as data to support the
appropriate selection of tolerance. DOE
notes that the tolerances adopted in the
DOE test procedure should be
achievable by test lab personnel without
the presence or direct input of the
manufacturer.
Finally, the AHRI 210/240-Draft
includes specifications for air sampling
that provide more detail than provided
in existing standards. DOE proposes to
incorporate these specifications by
reference in order to improve test
procedure repeatability and consistency.
The proposal currently cites the AHRI
210/240-Draft, which is not possible for
the final rule associated with this
rulemaking. However, DOE expects that
the AHRI standard will be finalized in
time to allow the final rule to amend the
CFR to incorporate this material.
DOE notes that the final published
version of what is currently the AHRI
210/240-Draft may not be identical to
the current draft. If AHRI makes other
than minor editorial changes to the
sections DOE references in this SNOPR
after publication of this SNOPR, DOE
proposes to adopt the current draft
content into its regulations and not
incorporate by reference the modified
test procedure.
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15. Damping Pressure Transducer
Signals
ASHRAE 37–2009, which DOE
proposes in this SNOPR to be
incorporated by reference into the DOE
test procedure, includes requirements
for maximum allowable variation of
specific measurements for a valid test.
Specifically, Table 2 of the standard
indicates that the test operating
tolerance (total observed range) of the
nozzle pressure drop may be no more
than 2 percent of the average value of
reading. Section 5.3.1 of the standard
indicates that the nozzle pressure drop
(or the nozzle throat velocity pressure)
may be measured with manometers or
electronic pressure transducers. These
measurements are made to determine air
flow. Section 8.7.2 of the standard
requires that measurements shall be
recorded at equal intervals that span
five minutes or less when evaluating
cooling capacity.
DOE is aware that when nozzle
pressure drop measurements are made
with pressure transducers and recorded
using a computer-based data acquisition
system, high frequency pressure
fluctuations can cause observed
pressure variations in excess of the 2
percent test operating tolerance, even
when air flows are steady and nonvarying. DOE proposes to add clarifying
language in the test procedure that
would allow for damping of the
measurement system to prevent such
high-frequency fluctuations from
affecting recorded pressure
measurements. The proposal would
allow for damping of the measurement
system so that the time constant for
response to a step change in pressure
(i.e. the time required for the indicated
measurement to change 63% of the way
from its initial value to its final value)
is no more than five seconds. This
damping could be achieved in any
portion of the measurement system.
Examples of damping approaches
include adding flow resistance to the
pressure signal tubing between the
pressure tap and the transducer, using a
transducer with internal averaging of its
output, or filtering the transducer
output signal, digital averaging of the
measured pressure signals. DOE
requests comment on this proposal,
including on whether the proposed
maximum time constant is appropriate.
F. Clarification of Test Procedure
Provisions
Ensuring repeatability of test results
requires that all parties that test a unit
use the same set of instructions to set up
the unit, conduct the test, and calculate
test results. A test laboratory may be
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tempted to contact the product’s
manufacturer or other sources of
information not referenced or allowed
by the test procedure if there is a lack
of clarity in the installation instructions
shipped with the unit or ambiguities
within the test procedure itself.
Currently, certain sections of the DOE
test procedure for central air
conditioners and heat pumps in
Appendix M to Subpart B of 10 CFR
part 430 permit such consultation with
the manufacturer. In the June 2010
NOPR, DOE proposed to allow labmanufacturer communication as long as
test unit installation and laboratory
testing are conducted in complete
compliance with all requirements in the
DOE test procedure and the unit is
installed according to the
manufacturer’s installation instructions.
75 FR 31223, 31235 (June 2, 2010). In
the subsequent public comment period,
AHRI expressed support regarding
DOE’s proposal. (AHRI, No. 6 at p. 3).
Mitsubishi also supported adding test
procedure to clarify that interaction
with the manufacturer is allowed.
(Mitsubishi, No. 12 at p. 2). NEEA did
not object to DOE’s proposal. (NEEA,
No. 7 at p. 4). Because the reliance upon
such consultation could lead to
variability in test results among
laboratories by manufacturers providing
different testing instructions, DOE seeks
to limit such occurrences to the
maximum extent possible by ensuring
that all required testing conditions and
product setup information is either
specified in the test procedure, certified
to DOE, or stated in installation manuals
shipped with the unit by the
manufacturer. DOE believes that the
proposed revisions in this rule provide
such clarity and allow for models to be
tested and rated in an equitable manner
across manufacturers. Upon
implementing such clarifications,
laboratories will no longer need to
contact the manufacturer for advice on
implementation of the test procedure. If
questions arise about a specific test
procedure provision, the test lab and/or
the manufacturer should seek guidance
from DOE. DOE believes that this
change will eliminate inconsistent
testing due to different test laboratories
seeking and receiving different
information regarding unclear
instructions. Thus, DOE proposes the
following changes to the test procedure
to address test procedure provisions that
may be ambiguous or unclear in their
intent and also withdraws the proposal
it made in the June 2010 NOPR that
placed no restrictions on interactions
between manufacturers and third-party
test laboratories 75 FR at 31235.
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1. Manufacturer Consultation
DOE proposes to clarify the test
procedure provisions regarding the
specifications for refrigerant charging
prior to testing, with input on certain
details from the AHRI 210/240-Draft, as
discussed in section III.E.14. Section
2.2.5 of the test procedure provides
refrigerant charging instructions but also
states, ‘‘For third-party testing, the test
laboratory may consult with the
manufacturer about the refrigerant
charging procedure and make any
needed corrections so long as they do
not contradict the published installation
instructions.’’ The more thorough
refrigerant charging requirements
proposed in this notice should preclude
the need for any manufacturer
consultation, since they include steps to
take in cases where manufacturer’s
installation instructions fail to provide
information regarding refrigerant
charging or provide conflicting
requirements. Consultation with the
manufacturer should thus become
unnecessary, and DOE proposes to
remove the current test procedure’s
allowance for contacting the
manufacturer to receive charging
instructions. In instances where
multiple sets of instructions are
specified or are included with the unit
and the instructions are unclear on
which set to test with, DOE proposed in
the June 2010 NOPR to use the
instructions ‘‘most appropriate for a
normal field installation.’’ 75 FR 31235,
31250. (June 2, 2010) NEEA supported
this proposal. (NEEA, No. 7 at p. 4).
DOE proposes to maintain this position
in this rulemaking, proposing the use of
field installation criteria if instructions
are provided for both field and lab
testing applications.
In the June 2010 NOPR, DOE
proposed requirements for the lowvoltage transformer used when testing
coil-only air conditioners and heat
pumps, and required metering of such
low-voltage component energy
consumption during all tests. 75 FR
31238. In the April 2011 SNOPR, in
response to the June 2010 NOPR public
meeting comments, DOE proposed
revised requirements such that metering
of low-voltage component energy
consumption is required during only the
proposed off mode testing, citing that
such changes would require
adjustments to the standard levels
currently being considered. 76 FR
18109. The proposal therein consisted
of language that suggested that test
setup information may be obtained
directly from manufacturers. In the
effort to remain objective during testing,
DOE is hereby revising certain language
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in the proposal such that
communication between third party test
laboratories and manufacturers are
eliminated, and such information when
needed for test setup can be found in
the installation manuals included with
the unit by the manufacturer.
Regarding the use of an inlet plenum,
section 2.4.2 of the test procedure states,
‘‘When testing a ducted unit having an
indoor fan (and the indoor coil is in the
indoor test room), the manufacturer has
the option to test with or without an
inlet plenum installed. Space
limitations within the test room may
dictate that the manufacturer choose the
latter option.’’ To eliminate the need for
the test laboratory to confirm with the
manufacturer whether the inlet plenum
was installed during the manufacturer’s
test, DOE proposes to require
manufacturers to report on their
certification report whether the test was
conducted with or without an inlet
plenum installed.
Further, it is unclear in certain
sections of the test procedure which
‘‘test setup instructions’’ are to be
referenced for preparing the unit for
testing. Ambiguous references to ‘‘test
setup instructions’’ and/or
‘‘manufacturer specifications’’ may lead
to the use of instructions or
specifications provided by the
manufacturer that are possibly out-ofdate or otherwise not applicable to the
products being tested. DOE therefore
proposes to amend references in the test
procedure to test setup instructions or
manufacturer specifications by
specifying that these refer to the test
setup instructions included with the
unit. DOE proposes to implement this
change in the following sections: 2.2.2,
3.1.4.2(c), 3.1.4.4.2(c), 3.1.4.5(d), and
3.5.1(b)(3).
2. Incorporation by Reference of ANSI/
AHRI Standard 1230–2010
ANSI/AHRI Standard 1230–2010
‘‘Performance Rating of Variable
Refrigerant Flow (VFR) Multi-Split AirConditioning and Heat Pump
Equipment’’ with Addendum 2 (AHRI
Standard 1230–2010) prescribes test
requirements for both consumer and
commercial variable refrigerant flow
multi-split systems. On May 16, 2012,
DOE incorporated this standard by
reference into test procedures for testing
commercial variable refrigerant flow
multi-split systems at 10 CFR 431.96. 77
FR 28928. DOE recognizes that
consumer variable refrigerant flow
multi-split systems have similarities to
their commercial counterparts.
Therefore, to maintain consistency of
testing consumer and commercial
variable refrigerant flow multi-split
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systems, DOE proposes to incorporate
by reference the sections of AHRI
Standard 1230–2010 that are relevant to
consumer variable refrigerant flow
multi-split systems (namely, sections 3
(except 3.8, 3.9, 3.13, 3.14, 3.15, 3.16,
3.23, 3.24, 3.26, 3.27, 3.28, 3.29, 3.30,
and 3.31), 5.1.3, 5.1.4, 6.1.5 (except
Table 8), 6.1.6, and 6.2) into the existing
test procedure for central air
conditioners and heat pumps at
Appendix M to Subpart B of 10 CFR
part 430. To ensure that there is no
confusion with future definition
changes in industry test procedures,
DOE is including the terms ‘‘Multiplesplit (or multi-split) system’’, ‘‘Smallduct, high-velocity system’’, ‘‘Tested
combination’’, ‘‘Variable refrigerant flow
system’’ and ‘‘Variable-speed
compressor system’’ into its list of
definitions in Appendix M to Subpart B
of 10 CFR part 430.
10 CFR 429.16 requires the use of a
‘‘tested combination,’’ as defined in 10
CFR 430, subpart B, Appendix M,
section 1.B, when rating multi-split
systems. In response to a May 27, 2008
letter from AHRI to DOE, DOE proposed
changes in the ‘‘tested combination’’
definition in the June 2010 NOPR. 75 FR
31223, 31231 (June 2, 2010). In
comments responding to the NOPR,
AHRI urged DOE to adopt AHRI
Standard 1230–2010 for all
requirements pertaining to multi-split
systems. (AHRI, No. 6 at pp. 1–2)
Mitsubishi recommended likewise.
(Mitsubishi, No. 12 at p. 1) AHRI
Standard 1230–2010, published after the
June 2010 NOPR, duplicates most of the
requirements for tested combinations
that DOE proposed in the June 2010
NOPR except for the following
requirements, which DOE proposes in
this notice to adopt to reduce
manufacturer test burden: lower the
maximum number of indoor units
matched to an outdoor unit; and the
option to use another indoor model
family if units from the highest sales
volume model family cannot be
combined so that the sum of their
nominal capacities is in the required
range of the outdoor unit’s nominal
capacity (between 95 and 105 percent).
The proposal in June 2010 NOPR also
used the term ‘‘nominal cooling
capacity,’’ which may be ambiguous;
DOE also intends to clarify that such a
term should be interpreted as the
highest cooling capacity listed in
published product literature for 95 °F
outdoor dry bulb temperature and 80 °F
dry bulb, 67 °F wet bulb indoor
conditions, and for outdoor units as the
lowest cooling capacity listed in
published product literature for these
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conditions. If incomplete or no
operating conditions are reported, the
highest (for indoor units) or lowest (for
outdoor units) such cooing capacity
shall be used. Finally, AHRI 1230 uses
the term ‘‘model family’’ but does not
define the term. DOE requests comment
on an appropriate definition of ‘‘model
family’’ for DOE to adopt in the final
rule. In summary, DOE proposes to omit
AHRI’s definition of tested combination,
found in section 3.26, from the IBR of
AHRI Standard 1230–2010 into
Appendix M to Subpart B of 10 CFR
part 430, and make amendments to the
proposal from the June 2010 NOPR.
During testing for ducted systems
with indoor fans installed, the rise in
static pressure between the air inlet and
the outlet (called external static pressure
(ESP)) must be adjusted to a prescribed
minimum that varies with system
cooling capacity. The minimum ESPs
are 0.10 in. wc. for units with cooling
capacity less than 28,800 Btu/h; 0.15 in.
wc. for units with cooling capacity from
29,000 Btu/h to 42,500 Btu/h; and 0.20
in. wc. for units with cooling capacity
greater than 43,000 Btu/h. Multi-split
systems are composed of multiple
indoor units, which may be designed for
installation with short-run ducts. Such
indoor units generally cannot deliver
the minimum ESPs prescribed by the
current test procedure. Hence, lower
minimum ESP requirements may be
necessary for testing of ducted multisplit systems.
In the June 2010 NOPR, DOE
proposed lower minimum ESP
requirements for ducted multi-split
systems: 0.03 in. wc. for units less than
28,800 Btu/h; 0.05 in. wc. for units
between 29,000 Btu/h and 42,500 Btu/
h; and 0.07 in. wc. for units greater than
43,000 Btu/h. 75 FR at 31232. In its
comments, AHRI urged DOE to adopt
the minimum ESP requirements from
AHRI Standard 1230–2010 as DOE was
aware that the standard was being
developed at that time. AHRI expressed
concern over the potential abuse of
lower multi-split minimum ESPs
requirements by manufacturers of
ducted single-indoor-unit split-system
products. Specifically, they were
concerned that the lower ESP were
allowed for very specific installation
applications which could not be assured
by the manufacturer, and thus might be
used more widely than intended. AHRI
therefore argued against changing ESP
requirements. (AHRI, No. 6 at p. 2).
Mitsubishi recommended likewise.
(Mitsubishi, No. 12 at p. 2). NEEA
recommended establishing minimum
ESP requirements that are the same as
those of conventional systems. (NEEA,
No. 7 at p. 2) AHRI Standard 1230–2010
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does not include minimum ESP
requirements for multi-split systems
with short-run ducted indoor units. In
order to accommodate the design
differences of these indoor units, DOE
proposes to omit Table 8 of AHRI
Standard 1230–2010 from the IBR into
Appendix M and to set minimum ESP
requirements for systems with short-run
ducted indoor units at the levels and
cooling capacity thresholds as proposed
in the June 2010 NOPR. Furthermore,
DOE proposes to implement these
requirements by (a) defining the term
‘‘Short duct systems,’’ to refer to ducted
systems whose indoor units can deliver
no more than 0.07 in. wc. ESP when
delivering the full load air volume rate
for cooling operation, and (b) adding the
NOPR-proposed minimum ESP levels to
Table 3 of Appendix M (this is the table
that specifies minimum ESP), indicating
that these minimum ESPs are for short
duct systems. DOE proposes using the
new term ‘‘Short duct system’’ rather
than ‘‘Multi-split system’’ for these
minimum ESPs because multi-circuit or
mini-split systems could potentially
also include similar short-ducted indoor
units. DOE proposes a limitation in the
level of ESP that eligible indoor units
can deliver in order to prevent the
potential abuse of the reduced ESP
requirement mentioned by AHRI. DOE
requests comment on these proposals,
including the value of maximum ESP
attainable by eligible systems.
DOE notes that in conjunction with
the adopted portions of the AHRI
Standard 1230–2010 , the following
sections of the proposed test procedure
found in Appendix M may apply to
testing VRF multi-split systems: section
1 (definitions); section 3.12 (rounding of
space conditioning capacities for
reporting purposes); sections 2.2.a,
2.2.b, 2.2.c, 2.2.1, 2.2.2, 2.2.3(a), 2.2.3(c),
2.2.4, 2.2.5, and 2.4 to 2.12 (test unit
installation requirements); Table 3 in
section 3.1.4.1.1c (external static
pressure requirements); section 3.1
except section 3.1.3 and 3.1.4 (general
requirements of the testing procedure);
sections 3.3, 3.4, and 3.5 (procedures for
cooling-mode tests); sections 3.7, 3.8,
3.9, and 3.10 (procedures for heatingmode tests); section 3.13 (procedure for
off mode average power rating); and
section 4 (calculations of seasonal
performance descriptors).
DOE requests comment on the
incorporation by reference of AHRI
1230–2010, and in particular the
specific sections of Appendix M and
AHRI 1230–2010 that DOE proposes to
apply to testing VRF systems.
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3. Replacement of the Informative
Guidance Table for Using the Federal
Test Procedure
The intent of the set of four tables at
the beginning of ‘‘Section 2, Testing
Conditions’’ of the current test
procedure (10 CFR part 430, subpart B,
Appendix M) is to provide guidance to
manufacturers regarding testing
conditions, testing procedures, and
calculations appropriate to a product
class, system configuration, modulation
capability, and special features of
products. DOE recognizes that the
current table format may be difficult to
follow. Therefore, DOE has developed a
more concise table and proposes using
it in place of the current table. DOE
requests comment on this proposed
change and/or whether additional
modifications to the new table could be
implemented to further improve clarity.
4. Clarifying the Definition of a MiniSplit System
Current definitions in 10 CFR part
430, subpart B, Appendix M define a
mini-split air conditioner and heat
pump as ‘‘a system that has a single
outdoor section and one or more indoor
sections, which cycle on and off in
unison in response to a single indoor
thermostat.’’ When DOE introduced this
definition, mini-split systems solely
employed one or more non-ducted or
short-duct wall-, ceiling-, or floormounted indoor units (i.e., nonconventional units), and the market for
mini-split products reflected such type
and quantity of indoor units. It was
common understanding that when
testing or purchasing a mini-split
system, the system would have a nonconventional indoor unit.
Nevertheless, DOE recognizes that
further clarification and specificity in
terminology would alleviate ambiguity
in how to categorize mini-split
products. To differentiate the two types
of products, DOE proposes deleting the
definition of mini-split air conditioners
and heat pumps, and adding two
definitions for: (1) Single-zone-multiplecoil split-system, representing a splitsystem that has one outdoor unit and
that has two or more coil-only or blower
coil indoor units connected with a
single refrigeration circuit, where the
indoor units operate in unison in
response to a single indoor thermostat;
and (2) single-split-system, representing
a split-system that has one outdoor unit
and that has one coil-only or blower coil
indoor unit connected to its other
component(s) with a single refrigeration
circuit. DOE seeks comment on this
proposal.
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5. Clarifying the Definition of a MultiSplit System
A multiple-split (or multi-split)
system is currently defined in 10 CFR
part 430, subpart B, Appendix M as ‘‘a
split-system having two or more indoor
units, which respond to multiple
thermostats.’’ Technologies exist on the
market that operate like multi-split
systems but incorporate multiple
outdoor units into the same package. To
clearly define what arrangement
qualifies as a multi-split system, DOE
proposes to clarify the definition of
multi-split system to specify that multisplit systems are to have only one
outdoor unit. (DOE notes that it
proposes to separately define multicircuit units as units that incorporate
multiple outdoor units into the same
package. This is discussed in section
III.C.2.) Finally, DOE proposes to clarify
that if a model of outdoor unit could be
used both for single-zone-multiple-coil
split-systems and for multi-splitsystems, it should be tested as a multisplit system.
G. Test Procedure Reprint
The test procedure changes proposed
in this SNOPR as well as in the June
2010 NOPR, April 2011 SNOPR, and
October 2011 SNOPR occur throughout
large portions of Appendix M to 10 CFR
part 430 Subpart B. In order to improve
clarity regarding the proposed test
procedure, in the regulatory text for this
SNOPR, DOE has reprinted the entirety
of Appendix M, including all changes
proposed in this SNOPR as well as those
in the previous NOPR and SNOPRs that
are still applicable. Table III.6 lists those
proposals from the previous notices that
appear without modification in this
regulatory text reprint, and provides
69315
reference to the respective revised
section(s) in the regulatory text. Table
III.7 lists those proposals from the
previous notices that either are
proposed to be withdrawn or amended
in this SNOPR or propose no
amendments to the test procedure, and
provides reference to the respective
preamble section for the discussion of
the revision, including stakeholder
comments from the original proposal,
and the revised section(s) in the
regulatory text, if any. The proposed
amendments to Appendix M would not
change the rated values.
Because Appendix M1, as discussed
in I.A, is substantially similar to
Appendix M, DOE is only printing the
proposed regulatory text for Appendix
M1 where it differs from the proposed
regulatory text for Appendix M.
Proposed changes relevant to Appendix
M1 are discussed in section III.H.
TABLE III.6—PROPOSALS FROM PRIOR NOTICES ADOPTED WITHOUT MODIFICATION IN THIS SNOPR
Section
Proposal to . . .
Reference
Preamble discussion
Action
Regulatory text
location *
June 2010 NOPR
A.7 ..................
A.10 ................
B.4 ..................
B.5 ..................
B.6 ..................
B.7 ..................
B.8 ..................
B.9 ..................
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B.10 ................
B.11 ................
B.12 ................
B.13 ................
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Add Calculations for Sensible Heat
Ratio.
Add Definitions Terms Regarding
Standby Power.
Allow a Wider Tolerance on Air Volume
Rate To Yield More Repeatable Laboratory Setups.
Change the Magnitude of the Test Operating Tolerance Specified for the
External Resistance to Airflow.
Change the Magnitude of the Test Operating Tolerance Specified for the
Nozzle Pressure Drop.
Modify Refrigerant Charging Procedures: Disallow Charge Manipulation
after the Initial Charge.
Require All Tests be Performed with
the
Same
Refrigerant
Charge
Amount.
When Determining the Cyclic Degradation Coefficient CD, Correct the Indoor-Side
Temperature
Sensors
Used During the Cyclic Test To Align
With the Temperature Sensors Used
During the Companion Steady-State
Test, If Applicable: Equation.
When Determining the Cyclic Degradation Coefficient CD, Correct the Indoor-Side
Temperature
Sensors
Used During the Cyclic Test To Align
With the Temperature Sensors Used
During the Companion Steady-State
Test, If Applicable: Sampling Rate.
Clarify Inputs for the Demand Defrost
Credit Equation.
Add Calculations for Sensible Heat
Ratio.
Incorporate Changes To Cover Testing
and Rating of Ducted Systems Having More Than One Indoor Blower.
75 FR 31229 .........
Upheld ...................
III.I.5 ......................
3.3c, 4.6.
75 FR 31231 .........
Upheld ...................
None ......................
Definitions.
75 FR 31233 .........
Upheld ...................
None ......................
3.1.4.1.1a.4b.
75 FR 31234 .........
Upheld ...................
None ......................
3.3d Table, 3.5h Table, 3.7a Table,
3.8.1 Table, 3.9f Table.
75 FR 31234 .........
Upheld ...................
None ......................
3.3d Table, 3.5h Table, 3.7a Table,
3.8.1 Table.
75 FR 31234 .........
Upheld ...................
III.E.7 .....................
2.2.5.
75 FR 31235,
31250.
Upheld ...................
III.F.1 .....................
2.2.5.8.
75 FR 31235 .........
Upheld ...................
None ......................
3.4c, 3.5i, 3.7e, 3.8.
75 FR 31236 .........
Upheld ...................
None ......................
3.3b, 3.7a, 3.9e, 3.11.1.1, 3.11.1.3,
3.11.2a.
75 FR 31236 .........
Upheld ...................
None ......................
3.9.2a.
75 FR 31237 .........
Upheld ...................
III.I.5 ......................
3.3c, 4.6.
75 FR 31237 .........
Upheld ...................
III.C.3 .....................
Add Changes To Cover Triple-Capacity, Northern Heat Pumps.
Specify Requirements for the Low-Voltage Transformer Used When Testing
for Off-Mode Power Consumption.
75 FR 31238 .........
Upheld ...................
III.C.4 .....................
2.2.3, 2.2.3b, 2.4.1b, 3.1.4.1.1d,
3.1.4.2e, 3.1.4.4.2d, 3.1.4.5.2f, 3.2.2,
3.2.2.1, 3.6.2, 3.2.6, 3.6.7, 4.1.5,
4.1.5.1, 4.1.5.2, 4.2.7, 4.2.7.1,
4.2.7.2, 3.2.2.2 Table, 3.6.2 Table.
3.6.6, 4.2.6.
75 FR 31238 .........
Upheld ...................
III.F.1 .....................
2.2d.
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TABLE III.6—PROPOSALS FROM PRIOR NOTICES ADOPTED WITHOUT MODIFICATION IN THIS SNOPR—Continued
Section
B.14 ................
Reference
Proposal to . . .
Add Testing Procedures and Calculations for Off Mode Power Consumption.
Action
Preamble discussion
Regulatory text
location *
75 FR 31238 .........
Upheld ...................
III.D ........................
Definitions, 3.13, 4.3, 4.4.
April 2011 SNOPR
III.A .................
III.B .................
III.D .................
III.E .................
Revise Test Methods and Calculations
for Off-Mode Power and Energy
Consumption.
Revise Requirements for Selecting the
Low-Voltage Transformer Used During Off-Mode Test(s).
Add Calculation of the Energy Efficiency Ratio for Cooling Mode
Steady-State Tests.
Revise Off-Mode Performance Ratings
76 FR 18107 .........
Upheld ...................
III.D ........................
Definitions, 3.13, 4.3, 4.4.
76 FR 18109 .........
Upheld ...................
III.F.1 .....................
2.2d.
76 FR 18111 .........
Upheld ...................
None ......................
4.7.
75 FR 31238 .........
Upheld ...................
III.D ........................
Definitions, 3.13, 4.3, 4.4.
October 2011 SNOPR
III.A .................
III.B .................
III.C .................
III.D .................
III.D.1 ..............
III.D.2 ..............
Reduce Testing Burden and Complexity.
Add Provisions for Individual Component Testing.
Add Provisions for Length of Shoulder
and Heating Seasons.
Revise Test Methods and Calculations
for Off-Mode Power and Energy
Consumption.
Add Provisions for Large Tonnage Systems.
Add Requirements for Multi-Compressor Systems.
76 FR 65618 .........
Upheld ...................
III.D ........................
Definitions, 3.13, 4.3, 4.4.
76 FR 65619 .........
Upheld ...................
III.D ........................
Definitions, 3.13, 4.3, 4.4.
76 FR 65620 .........
Upheld ...................
III.D ........................
Definitions, 3.13, 4.3, 4.4.
76 FR 65620 .........
Upheld ...................
III.D ........................
Definitions, 3.13, 4.3, 4.4.
76 FR 65621 .........
Upheld ...................
III.D ........................
Definitions, 3.13, 4.3, 4.4.
76 FR 65622 .........
Upheld ...................
III.D ........................
Definitions, 3.13, 4.3, 4.4.
* Section numbers in this column refer to the proposed Appendix M test procedure in this notice.
TABLE III.7—PROPOSALS FROM PRIOR NOTICES WITHDRAWN OR AMENDED IN THIS SNOPR OR PROPOSED NO CHANGE
TO THE TEST PROCEDURE
Section
Proposal to . . .
Reference
Preamble discussion
Action
Regulatory text
location *
June 2010 NOPR
A.1 ..................
A.2 ..................
A.3 ..................
A.4 ..................
A.5 ..................
A.6 ..................
A.8 ..................
A.9 ..................
B.1 ..................
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B.2 ..................
B.3 ..................
B.6 ..................
B.7 ..................
VerDate Sep<11>2014
Set a Schedule for Coordinating the
Publication of the Test Procedure
and Energy Conservation Standards.
Bench Testing of Third-Party Coils .......
No Change to Default Values for Fan
Power.
No Change to External Static Pressure
Values.
No Conversion to Wet-Coil Cyclic Testing.
No Change to Test Procedure for Testing Systems with ‘‘Inverter-Driven
Compressor Technology’’.
Regional Rating Procedure ...................
Modify Definition of Tested Combination.
Add Minimum ESP for Short Duct Systems.
Clarify That Optional Tests May Be
Conducted without Forfeiting Use of
the Default Value(s).
Modify the Definition of ‘‘Tested Combination’’.
Add Minimum ESP for Short Duct Systems.
Add Indoor Unit Design Characteristics
for Limiting Application of Minimum
ESP for Short Duct Systems.
Clarify That Optional Tests May Be
Conducted Without Forfeiting Use of
the Default Value(s).
No Adoption of Requirement of Manufacturer Sign-Off after Charging Refrigerant.
Allow Interactions between Manufacturers and Third-Party Testing Laboratory.
04:57 Nov 07, 2015
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75 FR 31227 .........
No Change ** .........
None ......................
None.
75 FR 31227 .........
75 FR 31227 .........
No Change ** .........
Amended ...............
None ......................
III.H.3 .....................
75 FR 31228 .........
Amended ...............
III.H.1 .....................
75 FR 31228 .........
No Change ** .........
III.I.4 ......................
None.
10 CFR Part 430, Subpart B, Appendix
M1 3.3d, 3.5.1, 3.7c, 3.9.1b.
10 CFR Part 430, Subpart B, Appendix
M1 3.1.4.1.1c. Table.
None.
75 FR 31229 .........
No Change ** .........
None ......................
None.
75 FR 31229 .........
75 FR 31230 .........
Withdrawn † ...........
Amended ...............
None ......................
III.F.2 .....................
None.
10 CFR 430.2
75 FR 31230 .........
Amended ...............
III.F.2 .....................
3.1.4.1.1c. Table.
75 FR 31230 .........
Withdrawn † ...........
None ......................
None.
75 FR 31231 .........
Amended ...............
III.F.2 .....................
10 CFR 430.2
75 FR 31232 .........
Amended ...............
III.F.2 .....................
3.1.4.1.1c. Table.
75 FR 31232 .........
Amended ...............
III.F.2 .....................
3.1.4.1.1c. Table header.
75 FR 31233 .........
Withdrawn † ...........
None ......................
None.
75 FR 31234 .........
No Change ** .........
None ......................
None.
75 FR 31235 .........
Withdrawn .............
III.F ........................
None.
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69317
TABLE III.7—PROPOSALS FROM PRIOR NOTICES WITHDRAWN OR AMENDED IN THIS SNOPR OR PROPOSED NO CHANGE
TO THE TEST PROCEDURE—Continued
Section
B.15 ................
B.15a ..............
B.15b ..............
B.15c ..............
B.15d ..............
B.16 ................
B.17 ................
Reference
Action
Preamble discussion
75 FR 31239 .........
Withdrawn † ...........
None ......................
None.
75 FR 31240 .........
Withdrawn † ...........
None ......................
None.
75 FR 31240 .........
75 FR 31241 .........
Withdrawn † ...........
Withdrawn † ...........
None ......................
None ......................
None.
None.
75 FR 31242 .........
Withdrawn † ...........
None ......................
None.
75 FR 31243 .........
Withdrawn .............
III.E.13 ...................
None.
75 FR 31243 .........
Amended ...............
III.E.12 ...................
10 CFR 430.3
None ......................
None.
Proposal to . . .
Add Parameters for Establishing Regional Standards.
Use a Bin Method for Single-Speed
SEER Calculations for the Hot-Dry
Region and National Rating.
Add New Hot-Dry Region Bin Data ......
Add Optional Testing at the A and B
Test Conditions With the Unit in a
Hot-Dry Region Setup.
Add a New Equation for Building Load
Line in the Hot-Dry Region.
Add References to ASHRAE 116–1995
for Equations That Calculate SEER
and HSPF for Variable Speed Systems.
Update Test Procedure References .....
Regulatory text
location *
Definitions.
April 2011 SNOPR
III.C .................
Withdraw of the Proposal To Add the
New Regional Performance Metric
SEER Hot-Dry.
76 FR 18110 .........
No Change ** .........
October 2011 SNOPR
Proposals are Upheld
* Section numbers in this column refer to the proposed Appendix M test procedure in this Notice, unless otherwise specified.
** These items were discussed in the NOPR or SNOPR but did not propose changes to the test procedure.
† Associated proposals regarding the SEER Hot-Dry metric, as indicated, are withdrawn because DOE withdrew the SEER Hot-Dry metric in the April 2011
SNOPR. 76 FR 18110.
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H. Improving Field Representativeness
of the Test Procedure
DOE received comments from
stakeholders during the public comment
period following the November 2014
ECS RFI requesting changes to the test
procedure that would improve field
representativeness. Such changes would
impact the rated efficiency of central air
conditioners and heat pumps. As
discussed in section I.A, any
amendments proposed in this SNOPR
that would alter the measured
efficiency, as represented in the
regulating metrics of EER, SEER, and
HSPF, are proposed as part of a new
Appendix M1 to Subpart B of 10 CFR
part 430. The test procedure changes
proposed as part of a new Appendix
M1, if adopted, would not become
mandatory until the existing energy
conservation standards are revised to
account for the changes to rated values.
(42 U.S.C. 6293(e)(2)) These changes,
including the relevant stakeholder
comments, are discussed in the
following subsections.
1. Minimum External Static Pressure
Requirements for Conventional Central
Air Conditioners and Heat Pumps
Most of the central air conditioners
and heat pumps used in the United
States use ductwork to distribute air in
a residence, using either a fan inside the
indoor unit or housed in a separate
component, such as a furnace, to move
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the air. External static pressure (ESP) for
a central air conditioner or heat pump
is the static pressure rise between the
inlet and outlet of the indoor unit that
is needed to overcome frictional losses
in the ductwork. The ESP imposed by
the ductwork affects the power
consumed by the indoor blower, and
therefore also affects the SEER and/or
HSPF of a central air conditioner or heat
pump.
The current DOE test procedure 22
stipulates that certification tests for
central air conditioners and heat pumps
which are not short duct systems (see
section III.F.2) or small-duct, highvelocity systems 23 (i.e., conventional
central air conditioners and heat
pumps) must be performed with an ESP
at or above 0.10 in. wc. if cooling
capacity is rated at 28,800 Btu/h or less;
at or above 0.15 in. wc. if cooling
capacity is rated from 29,000 Btu/h to
42,500 Btu/h; and at or above 0.20 in.
wc. if cooling capacity is rated at 43,000
Btu/h or more.
22 Table
3 of 10 CFR 430 Subpart B Appendix M
CFR 430 Subpart B Appendix M Section 1.
Definitions defines a small-duct, high-velocity
system as a system that contains a blower and
indoor coil combination that is designed for, and
produces, at least 1.2 inches (of water) of external
static pressure when operated at the full-load air
volume rate of 220–350 cfm per rated ton of
cooling. When applied in the field, small-duct
products use high-velocity room outlets (i.e.,
generally greater than 1000 fpm) having less than
6.0 square inches of free area.
23 10
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DOE decided in the June 2010 NOPR
not to propose revisions to minimum
external static pressure requirements,
stating that new values and a consensus
standard were not readily available. 75
FR 13223, 31228 (June 2, 2010). NEEA
responded during the subsequent public
comment period that current ESP
minimums were too low and
recommended DOE adopt an ESP test
requirement of 0.5 in. wc. (NEEA, No.
7 at p. 3). Earthjustice commented that
retention of the existing ESP values is
not supported by evidence.
(Earthjustice, No. 15 at pp. 1–2).
Southern California Edison (SCE), the
Southern California Gas Company
(SCGC), and San Diego Gas and Electric
(SDGE) (together, the Joint California
Utilities) included with its comments
two studies showing field
measurements of ESP with an average of
0.5–0.8 in. w.c and urged the
Department to adopt an external static
pressure test point of 0.5 in. wc. (Joint
California Utilities, No. 9 at p. 3).
ACEEE suggested that field data is
available for DOE to consider new
values of ESP. (ACEEE, No. 8 at pp. 2–
3).
Stakeholders also commented in
response to the November 2014 ECS RFI
that the current requirements for
minimum ESP are unrepresentative of
field practice. PG&E commented that the
ESP for central air conditioners and heat
pumps needs to be set at 0.5 in. wc. or
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higher for ducted systems. (Docket No.
EERE–2014–BT–STD–0048, PG&E, No.
15 at p. 3) ACEEE advocated similarly:
Default ESP used in the current federal
test procedure should be raised from the
current 0.1 to 0.2 in. wc. to at least 0.5
in. wc. to represent field practice. (Id.;
ACEEE, No. 21 at p. 2) ASAP & ASE &
NRDC commented that the ESP in the
current test procedure is unrealistically
low, adding that DOE should reference
to the ESP values adopted by the
recently finalized furnace fan
rulemaking which has an ESP value of
0.5 in. wc.24 (Id.; ASAP & ASE & NRDC,
No. 20 at p. 1).
Central air conditioners and heat
pumps are generally equipped with air
filters when used in the field. Section
3.1.4.1.1c of 10 CFR part 430, subpart B,
Appendix M requires that any unit
tested without an air filter installed be
tested with ESP increased by 0.08 in.
wc. to represent the filter pressure drop.
University of Alabama commented
during the public comment period of
the November 2014 ECS RFI that the
actual combined ESP requirements in
the field are typically 3 to 5 times
greater with more effective filters and
typical duct designs. The unrealistically
low rating conditions result in little
incentive for manufacturers to
incorporate improved fan wheel
designs. Improvements in SEER gained
by replacing inexpensive forward-curve
fan wheels will be negligible but
demand and energy savings in actual
installations will be significant. (Docket
No. EERE–2014–BT–STD–0048,
University of Alabama, No. 6 at p. 1).
Furnaces use the same ductwork as
central air conditioners and heat pumps
to distribute air in a residence. NEEA &
NPCC commented that the ESP selected
for testing of furnace fans is
substantially higher than the 0.1 to 0.2
in. wc. prescribed by the federal CAC/
HP test procedure. They also mentioned
that field data from Pacific Northwest
shows that the minimum required ESP
is 0.5 in. wc. regardless of system
capacity. NEEA & NPCC recommended
that the ESP requirement for
measurement of cooling efficiency be
close to 0.6 in. wc. because air volume
rates for cooling (and heating for heat
pumps) are greater than typical furnace
heating air volume rates. However, they
suggested DOE adopt the ESP level
required for testing of furnace fans as a
simple approach. (Docket No. EERE–
2014–BT–STD–0048, NEEA & NPCC,
No. 19 at p. 2).
In response to stakeholder comment
over multiple public meetings that the
minimum ESP values intended for
24 Docket
No. EERE–2010–BT–TP–0010–0043.
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testing are indeed unrepresentative of
the ESPs in field installations, and field
studies indeed demonstrating the same,
DOE proposes in this SNOPR revising
the ESP requirements for most central
air conditioners and heat pumps, e.g.,
those that do not meet the proposed
requirements for short duct systems or
the established requirements for smallduct, high-velocity (SDHV) systems.
DOE is not considering revising the
minimum ESP requirement for SDHV
systems. DOE is, however, proposing to
establish a new category of ducted
systems, short duct systems, which
would have lower ESP requirements for
testing—this is discussed in section
III.F.2.
To meet the requirement set forth in
42 U.S.C. 6293(b)(3) providing that test
procedures be reasonably designed to
produce test results which measure
energy efficiency of a covered product
during a representative average period
of use, DOE reviewed available field
data to determine appropriate ESP
values. DOE gathered field studies and
research reports, where publically
available, to estimate field ESPs. DOE
previously reviewed most of these
studies when developing test
requirements for furnace fans. The 20
studies, published from 1995 to 2007,
provided 1,010 assessments of location
and construction characteristics of
central air conditioner or heat pump
systems in residences, with the data
collected varying by location,
representation of system static pressure
measurements, and equipment’s age and
ductwork arrangement, vintage, and airtightness. 79 FR 500 (Jan. 3, 2014). DOE
observed measured ESPs to range from
0.20 to 0.70 in. wc. DOE used three
statistical approaches to determine an
average representation of ESP from the
range of ESPs: a simple-average
approach, a sample-size-exclusion
approach, and a most-samples
approach. DOE then performed
reconciliation, through equal weighting
of the results from the three approaches,
to obtain a ‘‘middle ground’’ value of
0.32 in. wc. as the ESP representing a
typical residence with a new space
conditioning system.
DOE is aware that units used in
certification laboratory testing have not
aged and are thus not representative of
seasoned systems in the field. Namely,
dust, dander, and other airborne
particulates, commonly deposited as
foulant onto in-duct components in
field installations, are unaccounted for
in controlled testing environments.
Foulant fills air gaps of the air filter and
evaporator coil and restricts air volume
rate, thus increasing ESP. This
occurrence is not accounted for in
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certification testing environments.
Therefore, DOE included an ESP adder
for component foulant build-up to the
test procedure to better reflect a
representative average period of use. To
determine the value of this adder, DOE
examined the aforementioned field
studies that captured the ESP
contribution from vintage, and certainly
fouled, air filters and evaporator coils.
From the contributing studies, DOE
estimates an average pressure drop due
to the filter’s foulant of 0.13 in. wc.
based on the difference in static
pressure contributions between fouled
filters and clean filters. DOE also
examined publicly available reference
material and research to determine the
pressure drop from the build-up of
foulant on evaporator coils. Three
resources in the public domain were
identified that documented the impact
of evaporator coil fouling on ESP in
applications.25 From this literature,
DOE estimates an average pressure drop
resulting from evaporator coil fouling of
0.07 in. wc. These additional pressure
drops result in a total of 0.20 in. wc.
being added to the revised ESP value, as
mentioned. DOE seeks comment on its
proposal to include in the ESP
requirement a pressure drop
contribution associated with average
typical filter and indoor coil fouling
levels and its use of residential-based
indoor coil and filter fouling pressure
drop data to estimate the appropriate
ESP contribution. DOE also requests any
data that would validate the proposed
ESP contributions or suggestions of
adjustments that should be made to
improve representativeness of the
values in this proposal. DOE notes that
addition of these pressure drop
contributions is consistent with the
approach adopted for testing of furnace
fans, which are tested without the filter
and air conditioning coil, and for which
the ESP selected for testing reflects the
field fouling associated with these
components.
Consistent with the current
motivation in current certification
procedures to promulgate policy that
represents the majority of products in
the field (10 CFR 429.16(a)(2)(ii)), DOE
selected the capacity with the largest
volume of retail sales, 3 tons, as the
rated cooling capacity category to adopt
25 Siegel, J., Walker, I., and Sherman, M. 2002.
‘‘Dirty Air Conditioners: Energy Implications of Coil
Fouling’’ Lawrence Berkeley National Laboratory
report, number LBNL–49757.
ACCA. 1995. Manual D: Duct Systems.
Washington, DC, Air Conditioning Contractors of
America.
Parker, D. S., J. R. Sherwin, et al. 1997. ‘‘Impact
of evaporator coil airflow in air conditioning
systems’’ ASHRAE Transactions 103(2): 395–405.
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housed modular blower; (3) a coil
paired with a separate furnace. The
existing federal test procedure for
central air conditioners and heat pumps
does not require different minimum
ESPs for these different blower coil
configurations, even though the heat
exchanger of a furnace may impose
additional pressure drop on the air
stream. The additional pressure drop
can contribute to higher blower power,
which may negatively affect the
performance rating for a central air
conditioner. Further, condensing
furnaces, which have more heat transfer
surface exposed to the flowing air than
non-condensing furnaces, may impose
even more pressure drop.
Given the potential disadvantage
associated with the rating of an air
conditioner with a condensing furnace
as the designated air mover, DOE
proposes an adjustment to the minimum
external static pressure requirement for
a rated blower coil combination using a
condensing furnace as the air mover in
order to mitigate the impact on airconditioner ratings of furnace efficiency
improvements. To aid the selection of
representative ESP adjustments, DOE
conducted laboratory testing for two
condensing and three non-condensing
furnaces to determine typical furnace
heat exchanger pressure drop levels.
TABLE III.8—PROPOSED MINIMUM ESP DOE measured the pressure rise
REQUIREMENTS FOR CENTRAL AIR provided by each furnace when
CONDITIONERS AND HEAT PUMPS operating in the maximum airflowOTHER THAN MULTI-SPLIT SYSTEMS control setting at a representative air
AND SMALL-DUCT, HIGH-VELOCITY volume rate, first as delivered and then
with the furnace heat exchanger(s)
SYSTEMS 27
removed. DOE measured average
furnace heat exchanger pressure drop
Rated cooling or heating capacMinimum
equal to 0.47 in. wc. for the condensing
ity
ESP
(Btu/h)
(in. wc.)
furnaces and 0.27 in. wc. for the noncondensing furnaces. The data suggest
Up Thru 28,800 ..........................
0.45
29,000 to 42,500 ........................
0.50 that condensing furnace pressure drop
43,000 and Above ......................
0.55 is roughly 0.2 in. wc. higher than noncondensing furnace pressure drop.
However, DOE notes that cooling
operation may be at lower air volume
2. Minimum External Static Pressure
rates than the maximum cooling air
Adjustment for Blower Coil Systems
volume rate used in the tests, since
Tested With Condensing Furnaces
furnaces can be paired with airAs discussed in section III.H.1, DOE
conditioners having a range of
proposes to increase the minimum ESP
capacities. Based on these results, DOE
required for testing blower coil central
proposes to include in Appendix M1 of
air conditioners and heat pumps. DOE
10 CFR part 430 Subpart B a
notes that there are three different
requirement of a downward adjustment
blower coil configurations: (1) An air
of the required ESP equal to 0.1 in. wc.
handling unit which is a single piece of
when testing an air conditioner in a
equipment containing a blower and a
blower-coil configuration (or singlecoil; (2) a coil paired with a separatelypackage configuration) in which a
condensing furnace is in the air flow
26 Docket No. EERE–2014–BT–STD–0048.
path. DOE is not making such a revision
27 DOE did not increase the ESP requirement for
in 10 CFR part 430, subpart B,
small-duct, high-velocity units because the existing
Appendix M. DOE requests comments
values in the test procedure represent field
on this proposal.
operations.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
the minimum ESP requirement based on
the field data and the adjustments. For
the other cooling capacity categories,
NEEA commented that ESP should not
vary with capacity. (NEEA, No. 7 at p.
3). DOE considered the stakeholder
comment and the higher ESPs indicative
of larger homes, and proposes a
compromise approach to use the current
0.05 in. wc. step variation among
capacities.
In conclusion, DOE proposes to adopt,
for inclusion into 10 CFR part 430,
subpart B, Appendix M1, for systems
other than multi-split systems and
small-duct, high-velocity systems,
minimum ESP requirements of 0.45 in.
wc. for units with rated cooling capacity
of 28,800 Btu/h or less; 0.50 in. wc. for
units with rated cooling capacity of
29,000 Btu/h or more and 42,500 Btu/
h or less; and 0.55 in. wc. for units with
rated cooling capacity of 43,000 Btu/h
or more. (DOE is not making such a
revision in 10 CFR part 430, subpart B,
Appendix M.) The proposed minimum
ESP requirements are shown in Table
III.8. DOE is aware that such changes
will impact the certification ratings
SEER, HSPF, and EER and is addressing
such impact in the current energy
conservation standards rulemaking.26
DOE requests comment on these
proposals.
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69319
3. Default Fan Power for Coil-Only
Systems
The default fan power is used to
represent fan power input when testing
coil-only air conditioners, which do not
include their own fans.28 The default
was discussed in the June 2010 NOPR,
in which DOE did not propose to revise
it due to uncertainty on whether higher
default values better represent field
installations. 75 FR 31227 (June 2,
2010). In response to the June 2010
NOPR, Earthjustice commented that the
existing default fan power for coil-only
units in the DOE test procedure is not
supported by substantial evidence. ESPs
measured from field data show
significant higher values than the
requirements in the existing test
procedure. (Earthjustice, No. 15 at p. 2)
However, to be consistent with the
increase in ESP used for testing blower
coil products, as discussed in section
III.H.1, this notice proposes updating
the default fan power (hereinafter
referred to as ‘‘the default value’’) used
for testing coil-only products. DOE used
circulation blower electrical power data
collected for the furnace fan rulemaking
(79 FR 38129, July 3, 2014) to determine
an appropriate default value for coilonly products.
DOE collected circulation blower
consumption data from product
literature, testing, and exchanges with
manufacturers as part of the furnace fan
rulemaking. These data are often
provided in product literature in the
form of tables listing air volume rate and
circulation blower electrical power
input across a range of ESP for each of
the blower’s airflow-control settings.
DOE collected such data for over 100
furnace fans of non-weatherized gas
furnace products for the furnace fan
rulemaking. DOE used this database to
calculate an appropriate default value to
represent circulation blower electrical
power for typical field operating
conditions for air conditioning,
consistent with the required ESP values
proposed for blower coil split-systems.
From the perspective of the furnace
providing the air movement, the ESP is
higher than that required for testing
blower coil systems to account for the
cooling coil and the air filter that would
be installed for a coil-only test, since
furnace airflow performance is
determined without the coil and filter
installed. DOE used pressure drop
associated with the filter equal to 0.08
in. wc., consistent with the required
ESP addition when testing without an
air filter installed. In addition, DOE
28 See 10 CFR 430 Subpart B Appendix M section
3.3.d.
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estimates that the typical pressure drop
associated with an indoor coil is 0.16 in.
wc. DOE added the resulting sum, 0.24
in. wc., to the required ESP levels for
testing a blower coil system to obtain
the ESP levels it used to calculate the
power input for furnaces in the furnace
fan database.
The air volume rate at which central
air conditioner and heat pumps are
required to operate according to the
DOE test procedure varies with
capacity. Typically, units are tested and
operated in the field while providing
between 350 and 450 cfm per ton of
cooling capacity. For the purpose of
determining the appropriate default
value, DOE investigated furnace fan
performance at the ESP values
discussed above while providing 400
cfm per ton of cooling capacity.
A product that incorporates a furnace
fan can often be paired with one of
multiple air conditioners of varying
cooling capacities, depending on the
installation. For example, a nonweatherized gas furnace model may be
designed to be paired with either a 2, 3,
or 4 ton coil-only indoor unit. These
combinations are possible because the
circulation blower in the furnace has
multiple airflow-control settings.
Multiple airflow-control settings allow
the furnace to be configured to provide
the target air volume rate for either 2, 3,
or 4 ton coil-only indoor units by
designating a different airflow-control
setting for cooling. For furnaces with
multiple such airflow-control settings
that are suitable for air conditioning
units, DOE calculated fan power for
each of these settings since they all
represent valid field operating
conditions.
DOE then organized the results of the
calculations by blower motor
technology used and manufacturer,
averaging over both to calculate an
overall average default value. The
distribution of motor technology follows
projected distribution of motors used in
furnaces in the field in the year 2021. By
this time, there will be some small
impact on this distribution associated
with the furnace fan rule. DOE averaged
by manufacturer based on market share.
The default fan power in the existing
DOE test procedure does not vary
among different capacities. DOE
maintains the same approach for the
adjusted default fan power. Using the
aforementioned methodology, DOE
calculated the adjusted default fan
power to be 441 W/1000 cfm and
proposes to use this value in Appendix
M1 of 10 CFR part 430 Subpart B where
Appendix M included a default fan
power of 365 W/1000 cfm. DOE is not
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making such replacements in Appendix
M of 10 CFR part 430 Subpart B.
4. Revised Heating Load Line
In the current test procedure, the
heating seasonal performance factor
(HSPF) determined for heat pumps in
heating mode is calculated by
evaluating the energy usage of both the
heat pump unit (reverse refrigeration
cycle) and the resistive heat component
when matching the house heating load
for the range of outdoor temperatures
representing the heating season. The
temperature range is split into 5-degree
‘‘bins’’, and an average temperature and
total number of hours are assigned to
each bin, based on weather data for each
climate region used to represent the
heating season—for the HSPF rating,
this is Region IV. The amount of heating
delivered at each temperature increases
as the temperature decreases. This
amount is dependent on the size of the
house that the unit is heating. In
addition, there is a relationship between
the size of the house and the capacity
of the heat pump selected to heat it. For
the current test procedure, the heating
load is proportional to the heating
capacity of the heat pump when
operating at 47 °F outdoor temperature.
The heating load is also proportional to
the difference between 65 °F and the
outdoor temperature. The resulting
relationship between heating load and
outdoor temperature is called the
heating load line—it slopes downward
from low temperatures, dropping to zero
at 65 °F. The slope of the heating load
line affects HSPF both by dictating the
heat pump capacity level used by twocapacity or variable-capacity heat
pumps at a given outdoor temperature,
and also by changing the amount of
auxiliary electric resistance heat
required when the unit’s heat pumping
capacity is lower than the heating load
line. The current test procedure defines
two load levels, called the minimum
heating load line and maximum heating
load line. However, it is the minimum
heating load line in region IV that is
used to determine HSPF for rating
purposes.29
Studies have indicated that the
current HSPF test and calculation
procedure overestimates ratings because
the current minimum heating load line
is too low compared to real world
situations.30 In response to the
29 See 10 CFR 430 Subpart B Appendix M Section
1. Definitions.
30 Erbs, D.G., C.E. Bullock, and R.J. Voorhis, 1986.
‘‘New Testing and Rating Procedures for Seasonal
Performance of Heat Pumps with Variable-Speed
Compressors’’, ASHRAE Transactions, Volume 92,
Part 2B.
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November 2014 ECS RFI, NEEA and
NPCC commented that the federal test
procedure does a poor job representing
balance point temperatures and electric
heat energy use in the case of heat pump
systems. They pointed out the inability
of the test procedure to capture dynamic
response to heating needs, such as use
of electric resistance (strip) heat during
morning or afternoon temperature setup
(i.e., rewarming of the space after a
thermostat setback period). They also
expressed concerns about capturing the
use of electric resistance heat during
defrost cycles and at times when it
shouldn’t be needed, such as when
outdoor temperatures are above 30 °F.
(NEEA & NPCC, No. 19 at p. 2)
DOE agrees with NEEA and NPCC and
notes that the heating balance point
determined for a typical heat pump
using the current minimum heating load
line in Region IV is near 17 °F, while
the typical balance point is in the range
26 to 32 °F, resulting from installing a
proper sized unit based on the design
cooling load according to ACCA Manual
S, 2014. The low heating balance point
means that the test procedure
calculation adds in much less auxiliary
heat than would actually be needed in
cooler temperatures, thus inflating the
calculated HSPF. Furthermore, the zero
load point of 65 °F ambient, which is
higher than the typical 50–60 °F zero
load point,31 causes the test procedure
calculation to include more hours of
operation at warmer outdoor
temperatures, for which heat pump
operation requires less energy input,
again inflating the calculated HSPF.
These effects result in overestimation of
rated HSPF up to 30% compared to field
performance, according to a paper by
the Florida Solar Energy Center
(FSEC).32 For these reasons, DOE
reviewed the choice of heating load line
for HSPF ratings and proposes to modify
it.
Francisco, Paul W., Larry Palmiter, and David
Baylon, 2004. ‘‘Understanding Heating Seasonal
Performance Factors for Heat Pumps’’, 2004
Proceedings of the ACEEE Summer Study on
Energy Efficiency in Buildings.
Fairey, Philip, Danny S. Parker, Bruce Wilcox,
and Matthew Lombardi, 2004. ‘‘Climatic Impacts on
Seasonal Heating Performance Factor (HSPF) and
Seasonal Energy Efficiency Ratio (SEER) for AirSource Heat Pumps’’, ASHRAE Transactions,
Volume 110, Part 2.
31 Francisco, Paul W., Larry Palmiter, and David
Baylon, 2004. ‘‘Understanding Heating Seasonal
Performance Factors for Heat Pumps’’, 2004
Proceedings of the ACEEE Summer Study on
Energy Efficiency in Buildings.
32 Fairey, Philip, Danny S. Parker, Bruce Wilcox,
and Matthew Lombardi, 2004. ‘‘Climatic Impacts on
Seasonal Heating Performance Factor (HSPF) and
Seasonal Energy Efficiency Ratio (SEER) for AirSource Heat Pumps’’, ASHRAE Transactions,
Volume 110, Part 2.
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As part of this review, ORNL
conducted building load analysis using
the EnergyPlus simulation tool on a
prototype residential house based on the
2006 IECC code and summarized the
study in a report to DOE.33 In general,
the studies indicate that a heating load
level closer to the maximum load line
and with a lower zero load ambient
temperature is more representative than
the minimum load line presently used
for HSPF rating values.
Tj = the outdoor bin temperature, °F
TOD = the outdoor design temperature, °F
DHR = the design heating requirement,
Btu/h
Tzl = the zero load temperature, °F
• The equation form does not differ
by region;
• The zero load temperature varies by
climate region, as shown in Table III.6,
and for Region IV is at 55 °F, which is
closer to what occurs in the field;
• The design heating requirement is a
function of the adjustment factor, or the
slope of the heating load line, and is 1.3
rather than 0.77; and
The proposed equation includes the
following changes from the current
heating load line used for calculation of
HSPF: 34
Based on the results from the ORNL
studies, DOE proposes the new heating
load line equation to be used for
calculation of HSPF as:
Where
• The heating load is tied with the
nominal heat pump cooling capacity
used for unit sizing rather than the
heating capacity (except for heatingonly heat pumps).
Revised heating load hours were
determined for the new zero load
temperatures of each climate region.
The revised heating load hours are given
below in Table III.9.
TABLE III.9—GENERALIZED CLIMATIC REGIONAL INFORMATION
Region No.
I
Heating Load Hours .........................................................................................................
Zero Load Temperature, TZL ...........................................................................................
II
562
60
909
58
III
1,363
57
IV
1,701
55
V
2,202
55
VI
* 1,974
58
The proposed heating load line
simulates the actual building load in
different climate regions, so the
maximum and minimum heating load
lines of the current test procedure are
not needed. The ORNL building
simulation results show that the same
equation matching the building load
applies well to all regions. DOE
therefore proposes eliminating
maximum and minimum DHR
definitions.
DOE believes that it is more
appropriate to base the heating load line
on nominal cooling capacity rather than
nominal heating capacity, because heat
pumps are generally sized based on a
residence’s cooling load. For the special
case of heating-only heat pumps, which
clearly would be sized based on heating
capacity rather than cooling capacity,
DOE proposes that the nominal heating
capacity at 47 °F would replace the
cooling capacity in the proposed load
line equation. This is consistent with
the building heating load analysis.
The proposed altered heating load
line would alter the measurement of
HSPF. DOE estimates that HSPF would
be reduced on average about 16 percent
for single speed heat pumps and two
capacity heat pumps. The impact on the
measurement for variable-speed heat
pumps is discussed in section III.H.5.
Consistent with the requirements of 42
U.S.C. 6293(e), DOE will account for
these changes in any proposed energy
conservation standard, and this test
procedure proposal would not become
effective until the compliance date of
any new energy conservation standard.
In response to the November 2014
ECS RFI, University of Alabama
commented that the current test
procedure for central air conditioners
and heat pumps include cooling bin
data at 67 °F and heating bin data at 62
°F. This results in a dead band of 5 °F.
Because the current test procedure
prescribes the indoor temperature set
point to be 70 °F for heating, and 80 °F
for cooling, the temperature difference
of 10 °F is inconsistent with the dead
band of 5 °F from the temperature bin.
University of Alabama also suggested
adopting 62 °F and 52 °F as the zero
load points for cooling and heating
modes, respectively. (University of
Alabama, No. 6 at p. 1–2)
The indoor dry bulb set temperature
of 70 °F for heating and 80 °F for cooling
represent field set temperature for
central air conditioners and heat pumps
in a typical residential household.
These two temperatures are also used in
other product or equipment classes such
as the commercial unitary air
conditioners and heat pumps.35
In this notice, DOE proposes to revise
the heating load line which shifts the
heating balance point and zero load
point to lower ambient temperatures.
These amendments reflect more
representative unit field operations and
energy use characteristics. The revised
heating load line lowers the zero load
point for heating in region IV to 55 °F.
Given the cooling-mode zero load point
of 65 °F, the proposed change would
increase the temperature difference
between the heating and cooling zero
load points to 10 °F, which equals the
temperature difference between cooling
and heating modes thermostat set
points. The proposal would hence make
these values more consistent with each
other, whether or not this consistency is
necessary for accuracy of the test
procedure.
As a result of this proposed heating
load line change, DOE also proposes
that cyclic testing for variable speed
heat pumps be run at 47 °F instead of
62 °F, as required by the current test
procedure (see Appendix M, section
3.6.4 Table 11). The test would still be
33 ORNL, Rice, C. Keith, Bo Shen, and Som S.
Shrestha, 2015. An Analysis of Representative
Heating Load Lines for Residential HSPF Ratings,
ORNL/TM–2015/281, July. (Docket No. EERE–
2009–BT–TP–0004–0046).
34 Most commonly used heating load equation
based on minimum design heating requirement and
region IV: Qh(47) * 0.77*(65–Tj)/60.
35 See ANSI/AHRI Standard 340/360–2007 with
Addenda 1 and 2, Performance rating of commercial
and industry unitary air-conditioning and heat
pump equipment.
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conducted using minimum compressor
speed. With the modified heating load
line there would be no heat pump
operation at 62 °F, so cyclic testing at
47 °F would be more appropriate. DOE
seeks comment on this proposal.
DOE proposes to make the changes to
the test procedure as mentioned in this
subsection only in Appendix M1 of 10
CFR part 430 Subpart B, and is not
making such changes to Appendix M of
the same Part and Subpart.
5. Revised Heating Mode Test Procedure
for Products Equipped With VariableSpeed Compressors
A recent Bonneville Power
Administration (BPA) commissioned
study done by Ecotope, Inc., and an Oak
Ridge National Lab (ORNL)/Tennessee
Valley Authority (TVA) field test found
the heating performance of a variable
speed heat pump, based on field data,
is much lower than the rated HSPF.36
Therefore, DOE revisited the heating
season ratings procedure for variable
speed heat pumps, is are found in
section 4.2.4 of Appendix M of 10 CFR
part 430 Subpart B.
The HSPF is calculated by evaluating
the energy usage of both the heat pump
unit (reverse refrigeration cycle) and the
resistive heat component when
matching the dwelling heating load at
each outdoor bin temperature.
Currently, both the minimum and the
maximum capacities are calculated at
each outdoor bin temperature to
determine whether the variable speed
heat pump capacity can or cannot meet
the building heating load. At an outdoor
bin temperature where the heat pump
minimum capacity is higher than the
building heating load, the heat pump
cycles at minimum speed. The energy
usage at such outdoor bin temperature
is determined by the energy usage of the
heat pump at minimum speed and the
unit cyclic loss. At an outdoor bin
temperature where the heat pump
maximum capacity is lower than the
building heating load, the heat pump
operates at maximum speed. The energy
usage at such outdoor bin temperature
is determined by the energy usage of the
heat pump at maximum speed and of
the additional resistive heat required to
meet the building load.
In the current test procedure, the
capacity and the corresponding energy
usage at minimum speeds are
determined by the two minimum speed
36 Larson, Ben, Bob Davis, Jeffrey Uslan, and
Lucinda Gilman, 2013. Variable Capacity Heat
Pump Field Study, Final Report, Ecotope, Inc.,
Bonneville Power Administration, August.
Munk, J.D., Halford, C., and Jackson, R.K., 2013.
Component and System Level Research of Variable
Capacity Heat Pumps, ORNL/TM–2013/36, August.
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tests at 47 °F and 62 °F (outdoor
temperature 37), assuming the capacity
and energy usage is linear to the outdoor
temperature and the compressor speed
does not change with the outdoor
temperature. The capacity and the
corresponding energy usage at
maximum speeds are determined by the
two maximum speed tests at 47 °F and
at 17 °F, assuming the compressor speed
does not change with the outdoor
temperature. Both the minimum and the
maximum capacities and energy usages
are also used to estimate the heat pump
operating capacity and energy usage
when the heat pump operates at an
intermediate speed to match the
building heating load.
In reviewing these calculations, DOE
compared the efficiencies (capacity
divided by energy usage; at maximum
speed, intermediate speed, and
minimum speed at ambient
temperatures representing the heating
season) calculated using the method in
current test procedure to the efficiencies
tested in the lab at each of the 5 °F bin
temperatures representing the heating
season, and found two discrepancies
where the efficiencies are not predicted
accurately by the test procedure.
The first discrepancy occurs only for
the variable speed heat pump that
prevents minimum speed operation at
outdoor temperatures below 47 °F. In
the mid-range outdoor temperature
range (17–47 °F), the efficiencies are
over-predicted. The cause of this overprediction is that the unit’s actual
minimum capacity is higher than the
calculated minimum capacity in the
range of outdoor temperature 17–47 °F.
The calculated minimum capacity is
based on the assumption that the unit
can operate at the minimum speed in
this range, which is not true with such
units.
DOE considered two alternative
methods to provide more accurate
efficiency predictions for mid-range
outdoor temperatures. In the first
method, the minimum capacity and the
corresponding energy usage for outdoor
temperatures lower than 47 °F would be
determined by the minimum speed tests
at 47 °F and the intermediate speed test
at 35 °F, which are both required test
points in current test procedure. The
new calculation method results in the
capacity and energy usage more
representative of the unit operation
performance in the temperature region
35–47 °F. The HSPF calculated with this
option agrees with the tested HSPF
within 6%. This option does not require
37 All temperatures in section III.H.5, if not noted
otherwise, mean outdoor temperature.
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additional testing beyond what is
required in the current test procedure.
In the second method, the minimum
capacity and the corresponding energy
usage for outdoor temperature lower
than 47 °F would be determined by
minimum speed tests at 47 °F and at 35
°F, where the test point of minimum
speed at 35 °F is an additional test point
that is not required in the current test
procedure. In addition, the intermediate
capacity and the corresponding energy
usage would be modified for more
accurate efficiency prediction at the
outdoor temperature range 17–35 °F.
This is done by defining the medium
speed test as the average of the
maximum and minimum speed and
using the medium speed test at 17 °F
and the intermediate speed test at 35 °F
to determine the intermediate capacity
and the corresponding energy usage,
where the test at the medium speed at
17 °F is a test point not required in the
current test procedure. With this
method, the unit’s calculated
performance is well matched with the
unit’s actual operation in the outdoor
temperature region 17–35 °F. The HSPF
calculated with this option aligns with
the tested HSPF within 2%. However,
this option requires two additional test
points, medium speed at 17 °F and
minimum speed at 35 °F, which adds
test burden for manufacturers.
After considering these two
alternative methods with regard to the
current test procedure, DOE further
evaluated the impact of the proposed
heating load line change (see section
III.H.4) on the variable speed HSPF
rating. DOE found that efficiencies
calculated with the modified heating
load line and with the current variable
speed heat pump rating method match
rather closely with those calculated
from a more detailed set of test data at
each outdoor bin temperature. The
calculated HSPFs agree within 1
percent. Use of the proposed load line
greatly reduces the error in the test
procedure calculation from the speed
limiting controls at ambient
temperatures below 47 °F. The net effect
is that the ratings calculation approach
using the proposed load line with the
current test points gives results close to
those with more detailed data sets.
However, because this also removes an
artificial HSPF benefit that such units
were obtaining, the net reduction in
rated HSPF for such units could be as
much as 26%.38 DOE believes that this
indicates that the modified heating load
38 Rice et al. (2015) Review of Test Procedure for
Determining HSPFs of Residential Variable-Speed
Heat pumps. (Docket No. EERE–2009–BT–TP–
0004–0047).
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line is sufficient to address the HSPF
over-prediction issue for the variable
speed heat pumps. Therefore, at this
time, DOE does not propose changes
specifically to the variable speed test
points or heating calculations in the
proposed Appendix M1. However, DOE
notes that should stakeholder comments
on this notice provide sufficient
justification to retract the proposal to
adopt the proposed modified heating
load line, DOE would instead adopt, as
part of Appendix M1, modifications to
the variable speed heating calculations
for units that prevent minimum speed
operation. DOE requests comment on
whether, in the case that the proposed
heating load line is not adopted, DOE
should modify the HSPF rating
procedure for variable speed heat
pumps using option 1, which is less
accurate but has no additional test
burden, or option 2, which is more
accurate but with higher test burden.
The second potential discrepancy
between the efficiencies (capacity
divided by energy usage) calculated
using the method in the current test
procedure with the efficiencies tested in
the lab at each outdoor bin temperature
occurs at temperatures lower than 17 °F,
where the test procedure assumes the
heat pump operates at the maximum
speed. The capacity and the
corresponding energy usage at
maximum speed at different outdoor bin
temperatures are determined by the two
maximum speed tests at 47 °F and at 17
°F, assuming the compressor speed does
not change with the outdoor
temperature. However, DOE found that
some variable speed heat pumps do not
allow maximum speed operation when
the outdoor temperature is below 17 °F.
For such units, the assumption in the
current test procedure is not
appropriate. The impact of this
discrepancy on the HSPF is not
significantly changed by the proposed
heating load line revision.
DOE proposes as part of Appendix M1
that for the variable speed units that
limit the maximum speed operation
below 17 °F and have a low cutoff
temperature less than 12 °F, the
manufacturer could choose to calculate
the maximum heating capacity and the
corresponding energy usage through two
maximum speed tests at: (1) 17 °F
outdoor temperature, and (2) 2 °F
outdoor temperature or at a low cutoff
temperature, whichever is higher.39
With this proposed change,
manufacturers could choose to conduct
one additional steady state test, at
maximum compressor speed and at a
low temperature of 2 °F or at a low
cutoff temperature, whichever is higher.
The testing done by ORNL found that
the unit efficiency at maximum speed
below 17 °F is slightly higher than the
extrapolated values in the current test
procedure, and this proposed option
would provide a more accurate
prediction of heat pump low ambient
performance not only for those units
that limit maximum speed operation
below 17 °F, but also for those that do
not.40 DOE therefore proposes to revise
Appendix M1 such that, for variable
speed units that do not limit maximum
speed operation below 17 °F,
manufacturers would also have the
option to use this revised method if it
is more representative of low ambient
performance.
DOE believes that the proposed
revision reflects field energy use more
accurately. However, DOE
acknowledges that the limited test
results available show very small
improvements in the accuracy of the
rating method. Because the proposed
revision adds an additional test burden
(one new test), DOE has proposed to
make it optional rather than mandatory.
However, DOE would consider making
this proposal mandatory for some or all
variable speed units, given additional
information. Specifically, DOE requests
test results and other data that
demonstrate whether HSPF results for
other variable speed heat pumps would
be more significantly impacted by this
proposed option, as well as whether the
additional test burden would offset the
advantages of the proposed
modification.
DOE notes that the proposed revision
also adds additional complexity to the
test procedure in terms of which
combinations of tests need to be
conducted. In the current test
procedure, to calculate the maximum
speed performance in the temperature
range 17–45 °F, the maximum speed
performance at 35 °F is required.
However, the maximum speed 35 °F test
is not required and performance at 35 °F
may instead be calculated from the two
maximum speed tests at 17 °F and 47 °F.
Therefore, even though manufacturers
who choose to rate with the optional
low ambient point would no longer
need the maximum speed 47 °F point to
calculate energy use at maximum speed
below 17 °F, they would need either the
maximum speed 47 °F test point or 35
°F test point to calculate the capacity
and energy use at maximum speed at 35
°F. They may also wish to conduct the
maximum speed 47 °F test point to rate
heating capacity, although in the
proposed Appendix M1, this is only
required for heating-only heat pumps.
In summary, with the proposed
option for calculating maximum speed
performance below 17 °F, manufacturers
would test at both maximum speed at 2
°F (or low cutoff temperature) and
maximum speed at 17 °F. For rating at
35 °F, they would also test at either
maximum speed at 35 °F or maximum
speed at 47 °F. Finally, to rate heating
capacity or nominal heating capacity
(for units whose controls do not allow
maximum speed operation at 47 °F),
they may also choose to test at either
maximum speed at 47 °F allowed by
their standard controls or cooling
capacity maximum speed at 47 °F,
respectively. Table III.10 lists the
maximum speed test combination
options for the variable speed heat
pumps. The test combination option 1 is
the default in current test procedure.
TABLE III.10—PROPOSED MAXIMUM SPEED HEATING TEST COMBINATION OPTIONS FOR UNITS HAVING A VARIABLE-SPEED
COMPRESSOR
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Test description (outdoor dry bulb temperatures)
Current test procedure
(Option 1)
Option 2
Option 3
Option 4
Option 5
H1N (2 °F) ....................
........................
......................................
H12 (47 °F) ...................
optional if using nominal heating capacity.
X ..................................
X
for nominal heating capacity.
X.
H22 (35 °F) ...................
H32 (17 °F) ...................
......................................
X ..................................
........................
X
for heating capacity
only.
X ..................................
X ..................................
for nominal heating capacity.
......................................
X ..................................
X ..................................
X.
39 In the case that the low cutoff temperature is
higher than 12 °F, the manufacturer would not be
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allowed to utilize this option for calculation of the
maximum heating load capacity.
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TABLE III.10—PROPOSED MAXIMUM SPEED HEATING TEST COMBINATION OPTIONS FOR UNITS HAVING A VARIABLE-SPEED
COMPRESSOR—Continued
Test description (outdoor dry bulb temperatures)
Current test procedure
(Option 1)
Option 2
Option 3
Option 4
H42 (2 °F) * ...................
......................................
X
X ..................................
X ..................................
Option 5
X.
* Or low cutoff temperature, whichever is higher.
Note: For units with a low cutoff temperature higher than 12 °F, options 2 through 5 are not available.
DOE additionally notes that all
proposed changes in this subsection
would change the efficiency ratings of
units and are therefore proposed as part
of Appendix M1 of 10 CFR 430 Subpart
B. Such proposed changes would not
appear in Appendix M of the same Part
and Subpart.
I. Identified Test Procedure Issues DOE
may Consider in Future Rulemakings
Various comments from stakeholders
during the public comment period
following the publication of the
November 2014 ECS RFI raised
additional test procedure issues. The
stakeholders requested that DOE
consider these issues when amending
its test procedures. After careful
consideration of these issues, DOE
believes that either they cannot be
resolved or that they require additional
action at this time, and therefore
declines to address them in this SNOPR.
Discussion of these test procedure
issues follows in the subsequent
subsections.
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1. Controlling Variable Capacity Units to
Field Conditions
Central air conditioners and heat
pumps can be divided into single-speed,
two-capacity, or variable capacity (or
speed) units based on capacity
modulation. System controls are
typically more complex with the
increasing modulating capability. The
DOE test procedure prescribes different
testing requirements for units
depending on whether they are singlespeed, two-capacity, or variable capacity
(or speed) in order to characterize the
efficiency ratings accurately.
In response to the RFI, stakeholders
submitted several comments that
address the more complex operation of
variable capacity central air
conditioners and heat pumps.
Stakeholders also submitted comments
highlighting the need for improvement
in the test procedure’s ability to
accurately predict energy use in the
field, even for units that do not have
variable capacity capability. PG&E urged
DOE to revise the current test procedure
to reflect the more nuanced operation of
modern variable speed central air
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conditioners and heat pumps over the
full range of outdoor conditions, given
that variable speed units operate
differently from the traditional singlespeed or two-capacity units. (PG&E, No.
15 at p. 2)
Edison Electric Institute commented
that the current test procedure for
central air conditions and heat pumps
need to be updated to avoid ‘‘gaming’’
of system controls to maximize rated
SEER and EER, as there is an increase
in using variable speed controls for
motors, compressors, and variable
refrigerant flow. (EEI, No. 18 at p. 3)
NEEA & NPCC commented that the
current test procedure does not
appropriately test the operation of
variable capacity systems. These
systems operate much differently in the
field than the forced operating
conditions with which they are
currently tested under waivers and
artificially created laboratory
conditions. As a result, the efficiency
ratings and estimated energy use of
these systems cannot be reliably
determined. NEEA & NPCC also claimed
that the field data shows that systems
from different manufacturers with
identical HSPF and SEER ratings and
identical rated capacity will use
significantly different amounts of energy
under identical environmental
conditions. (NEEA & NPCC, No. 19 at p.
2) NEEA & NPCC also showed the field
energy use profiles for six units. They
further commented that variable
capacity systems behave in a nearly
infinite variety of ways under similar
outdoor and indoor temperature
conditions, and much of this behavior
occurs outside the bounds of the test
procedure conditions. (NEEA & NPCC,
No. 19 at p. 4) NEEA and NPCC
commented that test procedure updates
to variable capacity equipment will
have an impact on the energy savings of
these systems. They also commented
that the test procedure more accurately
representing the field energy use for
heat pump systems could vary
significantly by climate zone. (NEEA &
NPCC, No. 19 at p. 10)
ASAP, ASE, and NRDC commented
that the current method for testing
variable-capacity units used by
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manufacturers who have obtained test
procedure waivers may not provide
good representation of energy use in the
field or reasonable relative rankings of
product. Representative ratings of
variable-capacity products will become
more important in the future as variablecapacity units become more widely
adopted. (ASAP & ASE & NRDC, No. 20
at p. 1)
PG&E commented that central air
conditioners and heat pumps should be
tested at part load and cyclic testing
under conditions that represent field
operations. (PG&E, No. 15 at p. 3)
However, PG&E did not provide further
detail on what part load and cyclic
conditions would be field
representative.
ACEEE commented that the current
federal test procedure has been
awkward for rating new technologies,
notably ductless equipment, and
probably some types of modulating
equipment. (ACEEE, No. 21 at p. 2)
As discussed in section III.H.5, DOE
proposes to amend the testing
requirements for units equipped with a
variable speed compressor during
heating mode operation. These
proposed amendments would improve
the field representativeness of variable
speed units and better characterize the
field energy use. However, DOE
acknowledges that further
improvements as suggested by the
stakeholders could be possible if more
detailed field testing data is available.
DOE may consider in a future
rulemaking additional amendments to
improve the test procedure’s
representation of field energy use. In
regards to ductless and modulating
equipment, DOE’s existing test
procedure already covers testing and
rating of these technologies.
2. Revised Ambient Test Conditions
Central air conditioners and heat
pumps operate in a wide range of
weather conditions throughout the year.
Further, both the range of temperature
and humidity conditions associated
with most of these products’ energy use
also varies from one climate region to
another. The test procedure prescribes
calculation of seasonal energy efficiency
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metrics for cooling and heating based on
a finite set of test conditions intended
to represent the range of operating
conditions while avoiding excess test
burden.
DOE decided in the June 2010 NOPR
not to propose modifications to convert
to wet-coil cyclic testing as data and
information were not available to
quantify subsequent impacts. 75 FR
31223, 31228 (June 2, 2010). In response
to the June 2010 NOPR, SCE, SCGC and
SDGE submitted a joint comment
recommending DOE require that
manufacturers disclose performance
data at a range of test conditions, as
specified in the Consensus Agreement.
The joint comment further explained
that program designers need to know
how equipment performs in a range of
conditions in order for rebate and
incentive programs to be effective. This
could also make it possible for
consumers to select products with
performance characteristics that meet
their needs. (Docket EERE–2009–BT–
TP–0004, SCE, SCGC, and SDGE, No. 9,
at p.3)
In the current AHRI certified
directory,41 manufacturers report the
full load capacity and EER in addition
to SEER for central air conditioners.
Manufacturers also report heating
capacities and EERs at both 47 °F and
17 °F ambient test conditions in
addition to the seasonal efficiency
metric HSPF for heat pumps. Cooling
capacity and EER at full load are also
reported in addition to SEER for heat
pumps. DOE believes that this rating
data provides sufficient information for
determining rebate and incentive
programs for program designers.
NREL commented that the existing
DOE testing and certification
requirements for central air conditioners
and heat pumps do not provide
sufficient data to compare different
units. NREL also urged DOE to adopt
different testing conditions for the hot
dry and hot humid region. NREL further
commented that measurement of water
condensation must be reported with
higher fidelity than the sensible heat
ratio. Latent loads and moisture removal
should be reported in each test
condition. (EERE–2009–BT–TP–0004,
NREL, No. 14 at p. 1)
DOE does not intend to establish
different test conditions for various
regions of this country. DOE believes
that it would add significant burden to
manufacturers to report the latent loads
and moisture removal in each test
condition. In this SNOPR, DOE revises
the certification requirement to include
41 https://www.ahridirectory.org/ahridirectory/
pages/home.aspx.
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reporting the sensible heat ratio. See
section III.I.5 for more details. DOE
believes that the sensible heat ratio
provides a good indication of the
moisture removal capability for central
air conditioners and heat pumps.
Stakeholders submitted a number of
comments on the revised ambient test
condition in response to the RFI
published on November 5, 2014. 79 FR
65603. University of Alabama
commented that the testing conditions
prescribed in the federal test procedure
for central air conditioners and heat
pumps are not representative of actual
operation in the field. The outdoor
temperatures used for rating should be
expanded from 2 to 3 for constant speed
units and from 5 to 6 for multi-capacity
and variable speed units. The rating
points can be used to determine more
appropriate SEER and HSPF for climates
outside of the current DOE zone 4
conditions. Specifically, University of
Alabama proposed the cooling indoor
dry bulb and wet bulb temperatures to
be 77 °F and 64.4 °F, instead of the
current requirement of 80 °F and 67 °F,
respectively. Heating indoor dry bulb
temperature should use 68 °F instead of
the current requirement of 70 °F. For the
outdoor conditions, testing at 113 °F, 95
°F, and 77 °F have been proposed for the
cooling mode, and 41 °F, 23 °F, and 5
°F have been proposed for the heating
mode, respectively. (University of
Alabama, No. 6 at p. 1–2)
PG&E commented that DOE should
amend the test procedure to require
testing at 76 °F dry bulb with 50%
relative humidity indoor conditions to
represent the comfort desired in
dwellings. (PG&E, No. 15 at p. 3)
However, PG&E did not provide further
detail on why the revised test condition
is more representative than the
requirements in the current federal test
procedure.
PG&E also commented that the
current cooling condition at 95 °F does
not fully capture the peak load
experienced by consumers in the hottest
summer weather. PG&E further urged
DOE to revise the test procedure to
account for ambient dry bulb conditions
of 105 °F or 115 °F experienced by
consumers in the desert climates.
(PG&E, No. 15 at p. 3)
Moreover, PG&E commented that DOE
should adopt the testing at outdoor
ambient temperatures that generate a
performance map of the system for use
in annual energy use simulation. (PG&E,
No. 15 at p. 3) However, there is no
further detail provided regarding this
comment.
EEI suggested that DOE revise the
indoor air inlet dry bulb/wet bulb
temperatures to be lowered from 80 °F/
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67 °F to 78 °F/61 °F, respectively. Such
a change would create more realistic
indoor conditions that would require
dehumidification to ensure properly
managed indoor air quality. (EEI, No. 18
at p. 4) However, EEI did not provide
further detailed justifications why such
a change would create more realistic
indoor conditions than the current
federal testing requirements.
NEEA and NPCC commented that the
current federal test procedure does not
capture performance under the full
range of operating conditions for which
many of these systems are designed.
Some air conditioners perform
significantly better at temperatures
above 100 °F than others, but based on
the current test procedure, there is no
testing requirement for temperatures
above 95 °F. For heat pumps, systems
may perform differently above 47 °F and
below 17 °F conditions. NEEA and
NPCC commented that the test
procedure and the resulting ratings
should expose these differences and
allow the market to properly select the
systems that are most appropriate and
most efficient for individual climate
conditions. (NEEA & NPCC, No. 19 at
p. 2)
ASAP, ASE, and NRDC commented
that the test conditions defined in the
current test procedure do not reflect
field conditions. Adding a test point for
SEER ratings at an outdoor temperature
above 95 °F and adding a test point for
HSPF ratings at an outdoor temperature
below 17 °F would incentivize
manufacturers to provide good
efficiency performance at these
temperatures. In addition, requiring
reporting of performance at each of the
outdoor temperature test points would
allow efficiency program administrators
to incentivize equipment that will
perform well in their region. (ASAP &
ASE & NRDC, No. 20 at p. 2)
DOE appreciates that there may be
value in providing more performance
data, and that the range of operating
conditions in the field may be more
extensive than that represented by the
current test. However, the extensive
study and test work that would have to
be conducted to properly assess and
choose a better range of test conditions
has not been completed. Hence,
although DOE has proposed some
changes to the test conditions required
for testing of variable-speed heat pumps
in heating mode, DOE has not proposed
changes as extensive as the comments
suggest. DOE may consider additional
changes addressing these issues in
future test procedure rulemakings.
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3. Performance Reporting at Certain Air
Volume Flow Rates
Central air conditioners and heat
pumps condition the indoor air to
satisfy cooling and heating requirements
of a house. For ducted central air
conditioners and heat pumps, indoor air
is driven by the blower of the air
handling unit or the furnace. Air
volume rate affects the heat transferred
between the air conditioning device and
indoor air, and also affects the
performance ratings of an air
conditioner or heat pump.
University of Alabama recommended
that all performance results for central
air conditioners and heat pumps be
reported within the air volume rate
range of 375 to 425 cfm per ton, and that
the air volume rates be included in the
reporting requirements. Higher air
volume rates will result in reduced
dehumidification capability and cause
thermal comfort issue. (University of
Alabama, No. 9 at p. 1)
The current DOE test procedure
requires that full load air volume rate be
no more than 37.5 standard cfm (scfm)
per 1,000 Btu/h of cooling capacity (see
10 CFR part 430, subpart B, Appendix
M, Section 3.1.4.1.1), but the test
procedure does not have a minimum air
volume rate requirement. DOE has
proposed in this notice to require
reporting of the cooling full load air
volume rate as part of certification
reporting. See section III.I.5 for more
details. The air volume rate is also
reported in the AHRI certification
database.42 DOE believes that these
requirements will ensure that air
volume rates used for rating central air
conditioners and heat pumps are in an
appropriate range.
4. Cyclic Test With a Wet Coil
The DOE test procedure for central air
conditioners and heat pumps prescribe
specific test conditions under which
units are to be tested. These test
conditions include both steady-state and
cyclic tests. A dry coil test refers to the
test conditions that do not result in
moisture condensing on the indoor coil,
and a wet coil test refers to the test
conditions that result in moisture
condensing on the indoor coil. DOE
proposed in the June 2010 NOPR not to
amend the existing cyclic testing
requirement from dry coil test to wet
coil test. DOE concluded that there was
no sufficient data to show a greater
benefit to using wet coil cyclic test
versus the dry coil cyclic test. 75 FR
31223, 31227 (June 2, 2010).
42 AHRI Directory of Certified Product
Performance: https://www.ahridirectory.org/
ahridirectory/pages/home.aspx.
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In response to the RFI regarding
central air conditioners and heat pumps
(79 FR 65603, November 5, 2014), ASAP
& ASE & NRDC commented that the
cyclic test in the current test procedure
is conducted using a dry coil, which is
not representative of field conditions.
Using the same indoor conditions (i.e.,
80 °F dry bulb and 67 °F wet bulb) for
the cyclic tests as used for the steadystate test would better reflect the cyclic
performance of central air conditioners
and heat pumps. (ASAP & ASE & NRDC,
No. 20 at p. 2) DOE believes this
approach may have merit, but has not
sufficiently studied it to have proposed
its inclusion in the test procedure at this
time. DOE may consider adopting the
approach in a future rulemaking.
5. Inclusion of the Calculation for
Sensible Heating Ratio
Air conditioning reduces air
temperature and also reduces humidity.
Cooling associated with air temperature
reduction is called sensible capacity,
while cooling associated with
dehumidification is called latent
capacity. The balance of these capacities
for a given air conditioner operating in
a given set of operating conditions is
represented as sensible heat ratio (SHR),
which is equal to sensible cooling
divided by total cooling. Air
conditioners can be designed to operate
with high or low SHR depending on the
air conditioning needs. Similarly, an air
conditioner can be optimized to
maximize efficiency depending on the
indoor humidity level.
In the June 2010 NOPR, DOE
proposed including the calculation for
(SHR at the B, B1, or B2 test condition
(82 °F dry bulb, 65 °F wet bulb, outside
air) in the test procedure. 75 FR 31223,
31229 (June 2, 2010). DOE received
comments regarding the inclusion of
calculations for SHR in the subsequent
public comment period. AHRI
supported adoption of the SHR,
provided that it is based off the total net
capacity and is a reported value only.
(AHRI, No. 6 at p. 4) Ingersoll Rand
agreed with AHRI. (Ingersoll Rand, No.
10 at pp. 2–3) Lennox likewise agreed
with AHRI regarding adding
calculations for SHR and further
requested that DOE provide calculations
for SHR at outdoor ambient conditions
of 82 °F. (Lennox, No. 11 at p. 1)
Building Science Corporation stated that
the calculation of the SHR was a
favorable step towards inclusion of a
dehumidification performance rating,
but requested determining SHR at
multiple outdoor and indoor conditions
and reporting a metric for moisture
removal efficacy. (Building Science
Corporation, No. 16 at p. 1) NEEA
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concurred with DOE’s proposal in the
NOPR to add calculations of sensible
heat ratio (SHR) to the test procedure
requirements. (NEEA, No. 7 at p. 6) The
People’s Republic of China World Trade
Organization Technical Barriers to
Trade National Notification and Enquiry
Center (China WTO) suggested that SHR
be calculated at the same SEER test
conditions. (China WTO, No. 18 at p. 4).
DOE does not believe that
measurements at multiple indoor or
outdoor conditions are necessary to
obtain a SHR value that represents unit
operation during an average use cycle or
period. (42 U.S.C. 6293(b)(3)) Therefore,
DOE is maintaining its position in the
NOPR to include calculation for
sensible heat ratio at only the condition
at which products are rated (82 °F dry
bulb, 65 °F wet bulb, outside air), and
proposes to include this change to the
revised Appendix M test procedure in
this notice. DOE notes that the addition
of these calculations does not add
significant test burden because the
existing measurement instruments, used
for determining the inputs for SEER, can
also determine the inputs for SHR.
The June 2010 NOPR highlighted a
Joint Utilities recommendation that DOE
should require all units be certified and
rated for sensible heat ratio (SHR) at 82
°F ambient dry bulb temperature. 75 FR
31223, 31229 (June 2, 2010). DOE
believes that the existing certification
test procedures and ratings are sufficient
to determine product efficiency; efforts
to establish dehumidification
performance for central air conditioner
and heat pumps are not currently
necessary given that the primary
function of the subject products is not
dehumidification, nor would doing so
be helpful in improving the accuracy of
product efficiency.
In response to the RFI regarding
central air conditioners and heat pumps
(79 FR 65603, November 5, 2014),
stakeholders submitted several
comments on the reporting
requirements related to the SHR. PG&E
commented that the test procedure
should adopt testing that characterizes
the sensible heat ratios for high (western
dry climates, approximately 500 cfm/
ton) and low (eastern humid climates,
approximately 350 cfm/ton) evaporator
coil air volume rate. (Docket No. EERE–
2014–BT–STD–0048, PG&E, No. 15 at p.
3) Edison Electric Institute commented
that the test procedure should take into
account a dehumidification requirement
as homes are getting tighter with fewer
air changes. (Id.; EEI, No. 18 at p. 3)
ASAP & ASE & NRDC requested DOE
require reporting sensible heat ratio for
central air conditioners and heat pumps.
Sensible heat ratio would provide more
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information to consumers and
contractors about appropriate units for
their region and also allow efficiency
program administrators to better target
efficiency programs for central air
conditioners and heat pumps. (Id.;
ASAP & ASE & NRDC, No. 20 at p. 2)
In response to the stakeholder
comments, DOE understands that air
volume rate can be controlled properly
to suit the dehumidification purposes.
However, manufacturers can design
their products to meet the needs of
consumers in different climate regions.
Therefore, DOE does not intend at this
time to develop a test procedure that
requires different air volume rates based
on the climate region. DOE does,
however, realize the merit of reporting
SHR for consumer choices. As such,
DOE proposes to simply require the
reporting of the SHR value calculated
based on full-load cooling test
conditions at the outdoor ambient
conditions proposed earlier in this
section: 82 °F dry bulb and 65 °F wet
bulb.
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J. Compliance With Other Energy Policy
and Conservation Act Requirements
1. Test Burden
EPCA requires that any test
procedures prescribed or amended shall
be reasonably designed to produce test
results which measure energy
efficiency, energy use, or estimated
annual operating cost of a covered
product during a representative average
use cycle or period of use, and shall not
be unduly burdensome to conduct. (42
U.S.C. 6293(b)(3)) For the reasons that
follow, DOE has tentatively concluded
that revising the DOE test procedure,
per the proposals in this SNOPR, to
measure the energy consumption of
central air conditioners and heat pumps
in active mode and off mode would
produce the required test results and
would not result in any undue burdens.
As discussed in section IV.B of this
SNOPR, the proposed test procedures to
determine the active-mode and standbymode energy use would require use of
the same testing equipment and
facilities that manufacturers are
currently using for testing to determine
CAC and CHP ratings for certifying
performance to DOE. While this notice
proposes clarifications to the test
procedures, and proposes adopting into
regulation the test procedures associated
with a number of test procedure
waivers, most of the proposals would
not affect test time or the equipment and
facilities required to conduct testing.
Possible changes in test burden
associated with the proposals of this
notice apply to off mode testing and
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requirements for testing of basic models
by ICMs.
The proposals include additional
testing to determine off mode energy
use, as required by EPCA. (42 U.S.C.
6295(gg)(2)(A)) This additional testing
may require investment in additional
temperature-controlled facilities.
However, DOE’s proposal does not
require that every individual
combination be tested for off mode,
allowing sufficient use of AEDMs in
order to reduce test burden.
The proposals also call for testing to
determine performance for ICMs.
Specifically, the proposals call for
testing of one split system combination
for each model of indoor unit sold by an
ICM. While this change would increase
test burden for these manufacturers,
DOE believes it is the appropriate
minimum test burden to validate ratings
for these systems, as it is consistent with
current requirements for OUMs, for
which testing is required for every
model of outdoor unit. DOE requests
comment on this issue.
DOE allows manufacturers to pursue
an alternative efficiency determination
method process to certify products
without the need of testing. In this
notice, DOE revises and clarifies such
requirements, as detailed in section
III.B, to continue to enable
manufacturers who wish to reduce
testing burden to utilize this method.
As detailed in section III.C,
manufacturers of certain products
covered by test procedures waivers,
have already utilized the alternative test
procedures provided to them for
certification testing. Thus, the inclusion
of said alternative test procedures into
the test procedure, as revised in this
notice, does not add additional test
burden.
In addition, DOE carefully considered
the testing burden on manufacturers in
proposing a modified off mode test
procedure that is less burdensome than
the proposals it made in the April 2011
SNOPR and October 2011 SNOPR and
that addresses stakeholder comment
regarding the test burden of such prior
proposals. Further discussion regarding
test burden associated with the
proposals set forth in this notice for
determining off mode power
consumption can be found in section
III.D.
DOE set forth proposals to improve
test repeatability, improve the
readability and clarity of the test
procedure, and utilize industry
procedures that manufacturers may be
aware of in an effort to reduce the test
burden. Sections III.E, III.F, and III.G
presents additional detail regarding
such proposals.
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Although DOE proposes to change the
current test procedure in a manner that
would impact measured energy
efficiency, amend existing requirements,
and increase the testing time for such
tests, DOE carefully considered the
impact on testing burden and made
efforts to balance accuracy,
repeatability, and test burden during the
course of the development of such
proposals. Further discussion is found
in section III.H.
Therefore, DOE determined that the
proposed revisions to the central air
conditioner and heat pump test
procedure would produce test results
that measure energy consumption
during a period of representative use,
and that the test procedure would not be
unduly burdensome to conduct.
2. Potential Incorporation of
International Electrotechnical
Commission Standard 62301 and
International Electrotechnical
Commission Standard 62087
Under 42 U.S.C. 6295(gg)(2)(B), EPCA
directs DOE to consider IEC Standard
62301 and IEC Standard 62087 when
amending test procedures for covered
products to include standby mode and
off mode power measurements.
DOE reviewed IEC Standard 62301,
‘‘Household electrical appliances—
Measurement of standby power’’
(Edition 2.0 2011–01),43 and determined
that the procedures contained therein
for preparation of the unit under test
and for conducting the test are already
set forth in the amended test procedure,
as proposed in this notice, for
determining off mode power
consumption and for determining the
components (cyclic degradation
coefficient) that make up standby power
for central air conditioners and heat
pumps. Therefore, DOE determined that
referencing IEC Standard 62301 is not
necessary for the proposed test
procedure that is the subject of this
rulemaking.
DOE reviewed IEC Standard 62087,
‘‘Methods of measurement for the power
consumption of audio, video, and
related equipment’’ (Edition 3.0 2011–
04), and determined that it would not be
applicable to measuring power
consumption of HVAC products such as
central air conditioners and heat pumps.
Therefore, DOE determined that
referencing IEC Standard 62087 is not
necessary for the proposed test
procedure that is the subject of this
rulemaking.
43 IEC Standard 62301 covers measurement of
power consumption for standby mode and low
power modes, as defined therein.
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IV. Procedural Issues and Regulatory
Review
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A. Review Under Executive Order 12866
The Office of Management and Budget
(OMB) has determined that test
procedure rulemakings do not constitute
‘‘significant regulatory actions’’ under
section 3(f) of Executive Order 12866,
Regulatory Planning and Review, 58 FR
51735 (Oct. 4, 1993). Accordingly, this
action was not subject to review under
the Executive Order by the Office of
Information and Regulatory Affairs
(OIRA) in the Office of Management and
Budget.
B. Review Under the Regulatory
Flexibility Act
The Regulatory Flexibility Act (5
U.S.C. 601 et seq.) requires preparation
of an initial regulatory flexibility
analysis (IFRA) for any rule that by law
must be proposed for public comment,
unless the agency certifies that the rule,
if promulgated, will not have a
significant economic impact on a
substantial number of small entities. As
required by Executive Order 13272,
‘‘Proper Consideration of Small Entities
in Agency Rulemaking,’’ 67 FR 53461
(August 16, 2002), DOE published
procedures and policies on February 19,
2003, to ensure that the potential
impacts of its rules on small entities are
properly considered during the DOE
rulemaking process. 68 FR 7990. DOE
has made its procedures and policies
available on the Office of the General
Counsel’s Web site: https://energy.gov/
gc/office-general-counsel.
DOE reviewed this proposed rule,
which would amend the test procedure
for central air conditioners and heat
pumps, under the provisions of the
Regulatory Flexibility Act and the
procedures and policies published on
February 19, 2003. DOE tentatively
concludes and certifies that the
proposed rule, if adopted, would not
result in a significant impact on a
substantial number of small entities.
The factual basis for this certification is
set forth below.
For the purpose of the regulatory
flexibility analysis for this rule, the DOE
adopts the Small Business
Administration (SBA) definition of a
small entity within this industry as a
manufacturing enterprise with 750
employees or fewer. DOE used the small
business size standards published on
January 31, 1996, as amended, by the
SBA to determine whether any small
entities would be required to comply
with the rule. 61 FR 3280, 3286, as
amended at 67 FR 3041, 3045 (Jan. 23,
2002) and at 69 FR 29192, 29203 (May
21, 2004); see also 65 FR 30836, 30850
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(May 15, 2000), as amended at 65 FR
53533, 53545 (Sept. 5, 2000). The size
standards are codified at 13 CFR part
121. The standards are listed by North
American Industry Classification
System (NAICS) code and industry
description and are available at
www.sba.gov/idc/groups/public/
documents/sba_homepage/serv_sstd_
tablepdf.pdf.
Central air conditioner and heat pump
manufacturing is classified under
NAICS 333415, ‘‘Air-Conditioning and
Warm Air Heating Equipment and
Commercial and Industrial Refrigeration
Equipment Manufacturing.’’ 70 FR
12395 (March 11, 2005). DOE reviewed
AHRI’s listing of central air conditioner
and heat pump product manufacturer
members and surveyed the industry to
develop a list of domestic
manufacturers. As a result of this
review, DOE identified 22
manufacturers of central air
conditioners and heat pumps, of which
15 would be considered small
manufacturers with a total of
approximately 3 percent of the market
sales. DOE seeks comment on its
estimate of the number of small entities
that may be impacted by the proposed
test procedure.
Potential impacts of the proposed test
procedure on all manufacturers,
including small businesses, come from
impacts associated with the cost of
proposed additional testing. In the June
2010 NOPR, DOE estimated the
incremental cost of the proposed
additional tests described in 10 CFR
part 430, subpart B, Appendix M
(proposed section 3.13) to be an increase
of $1,000 to $1,500 per unit tested,
indicating that the largest additional
cost would be associated with
conducting steady-state cooling mode
tests and the dry climate tests for the
SEER–HD rating). 75 FR at 31243 (June
2, 2010). DOE has eliminated tests
associated with the SEER–HD rating
from the proposals in this notice. DOE
conservatively estimates that off mode
testing might cost $1,000 (roughly onefifth of the $5000 cost of active mode
testing—see 75 FR at 31243 (June 2,
2010)). Assuming two off mode tests per
tested model, this is an average test cost
of $2,000 per model.
The proposals of this notice also
require that ICMs test one combination
of every basic model (i.e., model of
indoor unit). Based on a test cost
estimate of $5000 and two tests per
model, the costs for this proposal are
$10,000 for each basic model.
Because the incremental cost of
running the extra off mode tests is the
same for all manufacturers, DOE
believes that all manufacturers would
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incur comparable costs for testing to
certify off mode power use for basic
models as a result of the proposed test
procedure. DOE expects that small
manufacturers will incur less testing
expense compared with larger
manufacturers as a result of the
proposed testing requirements because
they have fewer basic models and thus
require proportionally less testing when
compared with large manufacturers that
have many basic models. DOE
recognizes, however, that smaller
manufacturers may have less capital
available over which to spread the
increased costs of testing.
With respect to the provisions
addressing AEDMs, the proposals
contained herein would not increase the
testing or reporting burden of outdoor
unit manufacturers who currently use,
or are eligible to use, an AEDM to certify
their products. The proposal would
eliminate the ARM nomenclature and
treat these methods as AEDMs,
eliminate the pre-approval requirement
for product AEDMs, revise the
requirements for validation of an AEDM
in a way that would not require more
testing than that required by the AEDM
provisions included in the March 7,
2011 Certification, Compliance and
Enforcement Final Rule (76 FR 12422)
(‘‘March 2011 Final Rule’’), and amend
the process that DOE promulgated in the
March 2011 Final Rule for validating
AEDMs and verifying certifications
based on the use of AEDMs. Because
these AEDM-related proposals would
either have no effect on test burden or
decrease burden related to testing (e.g.,
elimination of ARM pre-approval), DOE
has determined these proposals would
result in no significant change in testing
or reporting burden. The proposals
contained herein would not increase the
testing or reporting burden of outdoor
unit or independent coil manufacturers
besides the revision to the requirements
for validation of an AEDM, of which
burden is outweighed by the benefit of
providing more accurate ratings for
models of indoor units sold by ICMs, as
discussed in section III.A.3.d.
To evaluate the potential cost impact
of the other test-related proposals, DOE
compared the cost of the testing to the
total value added by the manufacturers
to determine whether the impact of the
proposed test procedure amendments is
significant. The value added represents
the net economic value that a business
creates when it takes manufacturing
inputs (e.g., materials) and turns them
into manufacturing outputs (e.g.,
manufactured goods). Specifically, as
defined by the U.S. Census, the value
added statistic is calculated as the total
value of shipments (products
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manufactured plus receipts for services
rendered) minus the cost of materials,
supplies, containers, fuel, purchased
electricity, and contract work expenses.
DOE analyzed the impact on the
smallest manufacturers of central air
conditioners and heat pumps because
these manufacturers would likely be the
most vulnerable to cost increases. DOE
calculated the additional testing
expense as a percentage of the average
value added statistic for the five
individual firms in the 25 to 49
employee size category in NAICS
333415 as reported by the U.S. Census
(U.S. Bureau of the Census, American
Factfinder, 2002 Economic Census,
Manufacturing, Industry Series,
Industry Statistics by Employment Size,
https://factfinder.census.gov/servlet/
EconSectorServlet?_lang=en&ds_
name=EC0200A1&_SectorId=31&_
ts=288639767147). The average annual
value for manufacturers in this size
range from the census data was $1.26
million in 2001$, per the 2002
Economic Census, or approximately
$1.52 million per year in 2009$ after
adjusting for inflation using the implicit
price deflator for gross domestic product
(U.S. Department of Commerce Bureau
of Economic Analysis, www.bea.gov/
national/nipaweb/SelectTable.asp).
DOE also examined the average value
added statistic provided by census for
all manufacturers with fewer than 500
employees in this NAICS classification
as the most representative value from
the 2002 Economic Census data of the
central air conditioner manufacturers
with fewer than 750 employees that are
considered small businesses by the SBA
(15 manufacturers). The average annual
value added statistic for all small
manufacturers with fewer than 500
employees was $7.88 million (2009$).
Given this data, and assuming the
range of estimates of additional costs,
$2,000 for OUMs and $10,000 for ICMs
for the additional testing costs, DOE
concluded that the additional costs for
testing of a single basic model product
under the proposed requirements would
be up to approximately 0.7 percent of
annual value added for the 5 smallest
firms, and approximately 0.13 percent
of the average annual value added for all
small central air conditioner or heat
pump manufacturers (15 firms). DOE
estimates that testing of basic models
may not have to be updated more than
once every 5 years, and therefore the
average incremental burden of testing
one basic model may be one fifth of
these values when the cost is spread
over several years.
DOE requires that only the highest
sales volume split-system combinations
be laboratory tested. 10 CFR 430.24(m).
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The majority of central air conditioners
and heat pumps offered by a
manufacturer are typically split-systems
that are not required to be laboratory
tested but can be certified using an
alternative rating method that does not
require DOE testing of these units. DOE
reviewed the available data for five of
the smallest manufacturers to estimate
the incremental testing cost burden for
those small firms that might experience
the greatest relative burden from the
revised test procedure. These
manufacturers had an average of 10
models requiring testing (AHRI
Directory of Certified Product
Performance, www.ahridirectory.org/
ahridirectory/pages/home.aspx), while
large manufacturers will have well over
100 such models. The additional testing
cost for final certification for 10 models
was estimated at $4,000 to $100,000.
Meanwhile, these certifications would
be expected to last the product life,
estimated to be at least 5 years based on
the time frame established in EPCA for
DOE review of central air conditioner
efficiency standards. This test burden is
therefore estimated to be approximately
1.3 percent of the estimated 5-year value
added for the smallest five
manufacturers. DOE believes that these
costs are not significant given other,
much more significant costs that the
small manufacturers of central air
conditioners and heat pumps incur in
the course of doing business. DOE seeks
comment on its estimate of the impact
of the proposed test procedure
amendments on small entities and its
conclusion that this impact is not
significant.
Accordingly, as stated above, DOE
tentatively concludes and certifies that
this proposed rule would not have a
significant economic impact on a
substantial number of small entities.
Accordingly, DOE has not prepared an
initial regulatory flexibility analysis
(IRFA) for this rulemaking. DOE will
provide its certification and supporting
statement of factual basis to the Chief
Counsel for Advocacy of the SBA for
review under 5 U.S.C. 605(b).
C. Review Under the Paperwork
Reduction Act of 1995
Manufacturers of central air
conditioners and heat pumps must
certify to DOE that their products
comply with any applicable energy
conservation standards. In certifying
compliance, manufacturers must test
their products according to the DOE test
procedures for central air conditioners
and heat pumps, including any
amendments adopted for those test
procedures. DOE has established
regulations for the certification and
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69329
recordkeeping requirements for all
covered consumer products and
commercial equipment, including
central air conditioners and heat pumps.
76 FR 12422 (March 7, 2011); 80 FR
5099 (Jan. 30, 2015). The collection-ofinformation requirement for the
certification and recordkeeping is
subject to review and approval by OMB
under the Paperwork Reduction Act
(PRA). This requirement has been
approved by OMB under OMB control
number 1910–1400. Public reporting
burden for the certification is estimated
to average 20 hours per response,
including the time for reviewing
instructions, searching existing data
sources, gathering and maintaining the
data needed, and completing and
reviewing the collection of information.
Notwithstanding any other provision
of the law, no person is required to
respond to, nor shall any person be
subject to a penalty for failure to comply
with, a collection of information subject
to the requirements of the PRA, unless
that collection of information displays a
currently valid OMB Control Number.
D. Review Under the National
Environmental Policy Act of 1969
In this supplemental proposed rule,
DOE proposes test procedure
amendments that it expects will be used
to develop and implement future energy
conservation standards for central air
conditioners and heat pumps. DOE has
determined that this rule falls into a
class of actions that are categorically
excluded from review under the
National Environmental Policy Act of
1969 (42 U.S.C. 4321 et seq.) and DOE’s
implementing regulations at 10 CFR part
1021. Specifically, this proposed rule
would amend the existing test
procedures without affecting the
amount, quality or distribution of
energy usage, and, therefore, would not
result in any environmental impacts.
Thus, this rulemaking is covered by
Categorical Exclusion A5 under 10 CFR
part 1021, subpart D, which applies to
any rulemaking that interprets or
amends an existing rule without
changing the environmental effect of
that rule. Accordingly, neither an
environmental assessment nor an
environmental impact statement is
required.
DOE’s CX determination for this
proposed rule is available at https://
energy.gov/nepa/categorical-exclusioncx-determinations-cx
E. Review Under Executive Order 13132
Executive Order 13132, ‘‘Federalism,’’
64 FR 43255 (August 4, 1999) imposes
certain requirements on agencies
formulating and implementing policies
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or regulations that preempt State law or
that have Federalism implications. The
Executive Order requires agencies to
examine the constitutional and statutory
authority supporting any action that
would limit the policymaking discretion
of the States and to carefully assess the
necessity for such actions. The
Executive Order also requires agencies
to have an accountable process to
ensure meaningful and timely input by
State and local officials in the
development of regulatory policies that
have Federalism implications. On
March 14, 2000, DOE published a
statement of policy describing the
intergovernmental consultation process
it will follow in the development of
such regulations. 65 FR 13735. DOE has
examined this proposed rule and has
determined that it would not have a
substantial direct effect on the States, on
the relationship between the national
government and the States, or on the
distribution of power and
responsibilities among the various
levels of government. EPCA governs and
prescribes Federal preemption of State
regulations as to energy conservation for
the products that are the subject of this
proposed rule. States can petition DOE
for exemption from such preemption to
the extent, and based on criteria, set
forth in EPCA. (42 U.S.C. 6297(d)) No
further action is required by Executive
Order 13132.
F. Review Under Executive Order 12988
Regarding the review of existing
regulations and the promulgation of
new regulations, section 3(a) of
Executive Order 12988, ‘‘Civil Justice
Reform,’’ 61 FR 4729 (Feb. 7, 1996),
imposes on Federal agencies the general
duty to adhere to the following
requirements: (1) Eliminate drafting
errors and ambiguity; (2) write
regulations to minimize litigation; (3)
provide a clear legal standard for
affected conduct rather than a general
standard; and (4) promote simplification
and burden reduction. Section 3(b) of
Executive Order 12988 specifically
requires that Executive agencies make
every reasonable effort to ensure that the
regulation: (1) Clearly specifies the
preemptive effect, if any; (2) clearly
specifies any effect on existing Federal
law or regulation; (3) provides a clear
legal standard for affected conduct
while promoting simplification and
burden reduction; (4) specifies the
retroactive effect, if any; (5) adequately
defines key terms; and (6) addresses
other important issues affecting clarity
and general draftsmanship under any
guidelines issued by the Attorney
General. Section 3(c) of Executive Order
12988 requires Executive agencies to
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review regulations in light of applicable
standards in sections 3(a) and 3(b) to
determine whether they are met or it is
unreasonable to meet one or more of
them. DOE has completed the required
review and determined that, to the
extent permitted by law, the proposed
rule meets the relevant standards of
Executive Order 12988.
G. Review Under the Unfunded
Mandates Reform Act of 1995
Title II of the Unfunded Mandates
Reform Act of 1995 (UMRA) requires
each Federal agency to assess the effects
of Federal regulatory actions on State,
local, and Tribal governments and the
private sector. Pub. L. 104–4, sec. 201
(codified at 2 U.S.C. 1531). For a
proposed regulatory action likely to
result in a rule that may cause the
expenditure by State, local, and Tribal
governments, in the aggregate, or by the
private sector of $100 million or more
in any one year (adjusted annually for
inflation), section 202 of UMRA requires
a Federal agency to publish a written
statement that estimates the resulting
costs, benefits, and other effects on the
national economy. (2 U.S.C. 1532(a), (b))
The UMRA also requires a Federal
agency to develop an effective process
to permit timely input by elected
officers of State, local, and Tribal
governments on a proposed ‘‘significant
intergovernmental mandate,’’ and
requires an agency plan for giving notice
and opportunity for timely input to
potentially affected small governments
before establishing any requirements
that might significantly or uniquely
affect small governments. On March 18,
1997, DOE published a statement of
policy on its process for
intergovernmental consultation under
UMRA. 62 FR 12820; also available at
https://energy.gov/gc/office-generalcounsel. DOE examined this proposed
rule according to UMRA and its
statement of policy and determined that
the rule contains neither an
intergovernmental mandate, nor a
mandate that may result in the
expenditure of $100 million or more in
any year, so these requirements do not
apply.
H. Review Under the Treasury and
General Government Appropriations
Act, 1999
Section 654 of the Treasury and
General Government Appropriations
Act, 1999 (Pub. L. 105–277) requires
Federal agencies to issue a Family
Policymaking Assessment for any rule
that may affect family well-being. This
rule would not have any impact on the
autonomy or integrity of the family as
an institution. Accordingly, DOE has
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concluded that it is not necessary to
prepare a Family Policymaking
Assessment.
I. Review Under Executive Order 12630
DOE has determined, under Executive
Order 12630, ‘‘Governmental Actions
and Interference with Constitutionally
Protected Property Rights’’ 53 FR 8859
(March 18, 1988), that this regulation
would not result in any takings that
might require compensation under the
Fifth Amendment to the U.S.
Constitution.
J. Review Under the Treasury and
General Government Appropriations
Act, 2001
Section 515 of the Treasury and
General Government Appropriations
Act, 2001 (44 U.S.C. 3516 note) provides
for agencies to review most
disseminations of information to the
public under guidelines established by
each agency pursuant to general
guidelines issued by OMB. OMB’s
guidelines were published at 67 FR
8452 (Feb. 22, 2002), and DOE’s
guidelines were published at 67 FR
62446 (Oct. 7, 2002). DOE has reviewed
this proposed rule under the OMB and
DOE guidelines and has concluded that
it is consistent with applicable policies
in those guidelines.
K. Review Under Executive Order 13211
Executive Order 13211, ‘‘Actions
Concerning Regulations That
Significantly Affect Energy Supply,
Distribution, or Use,’’ 66 FR 28355 (May
22, 2001), requires Federal agencies to
prepare and submit to OMB, a
Statement of Energy Effects for any
proposed significant energy action. A
‘‘significant energy action’’ is defined as
any action by an agency that
promulgated or is expected to lead to
promulgation of a final rule, and that:
(1) Is a significant regulatory action
under Executive Order 12866, or any
successor order; and (2) is likely to have
a significant adverse effect on the
supply, distribution, or use of energy; or
(3) is designated by the Administrator of
OIRA as a significant energy action. For
any proposed significant energy action,
the agency must give a detailed
statement of any adverse effects on
energy supply, distribution, or use
should the proposal be implemented,
and of reasonable alternatives to the
action and their expected benefits on
energy supply, distribution, and use.
The proposed regulatory action to
amend the test procedure for measuring
the energy efficiency of central air
conditioners and heat pumps is not a
significant regulatory action under
Executive Order 12866. Moreover, it
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would not have a significant adverse
effect on the supply, distribution, or use
of energy, nor has it been designated as
a significant energy action by the
Administrator of OIRA. Therefore, it is
not a significant energy action, and,
accordingly, DOE has not prepared a
Statement of Energy Effects.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
L. Review Under Section 32 of the
Federal Energy Administration Act of
1974
Under section 301 of the Department
of Energy Organization Act (Pub. L. 95–
91; 42 U.S.C. 7101), DOE must comply
with section 32 of the Federal Energy
Administration Act of 1974, as amended
by the Federal Energy Administration
Authorization Act of 1977. (15 U.S.C.
788; FEAA) Section 32 essentially
provides in relevant part that, where a
proposed rule authorizes or requires use
of commercial standards, the notice of
proposed rulemaking must inform the
public of the use and background of
such standards. In addition, section
32(c) requires DOE to consult with the
Attorney General and the Chairman of
the Federal Trade Commission (FTC)
concerning the impact of the
commercial or industry standards on
competition.
The proposed rule incorporates
testing methods contained in the
following commercial standards: AHRI
210/240–2008 with Addendum 1 and 2,
Performance Rating of Unitary AirConditioning & Air-Source Heat Pump
Equipment; and ANSI/AHRI 1230–2010
with Addendum 2, Performance Rating
of Variable Refrigerant Flow Multi-Split
Air-Conditioning and Heat Pump
Equipment. While the proposed test
procedure is not exclusively based on
AHRI 210/240–2008 or ANSI/AHRI
1230–2010, one component of the test
procedure, namely test setup
requirements, adopts language from
AHRI 210/240–2008 without
amendment; and another component of
the test procedure, namely test setup
and test performance requirements for
multi-split-systems, adopts language
from ANSI/AHRI 1230–2010 without
amendment. The Department has
evaluated these standards and is unable
to conclude whether they fully comply
with the requirements of section 32(b) of
the FEAA, (i.e., that they were
developed in a manner that fully
provides for public participation,
comment, and review). DOE will
consult with the Attorney General and
the Chairman of the FTC concerning the
impact of these test procedures on
competition, prior to prescribing a final
rule.
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M. Description of Materials
Incorporated by Reference
In this SNOPR, DOE proposes to
incorporate by reference (IBR) the
following two test standards published
by AHRI: ANSI/AHRI 210/240–2008
with Addenda 1 and 2, titled
‘‘Performance Rating of Unitary AirConditioning & Air-Source Heat Pump
Equipment;’’ and ANSI/AHRI 1230–
2010 with Addendum 2, titled
‘‘Performance Rating of Variable
Refrigerant Flow (VRF) Multi-Split AirConditioning and Heat Pump
Equipment.’’ DOE also proposes to IBR
a draft version of ASHRAE 210/240
which has not yet been published. DOE
also proposes to update its IBR to the
most recent version of the following
standards published by ASHRAE:
ASHRAE 23.1–2010 titled ‘‘Methods of
Testing for Rating the Performance of
Positive Displacement Refrigerant
Compressors and Condensing Units that
Operate at Subcritical Temperatures of
the Refrigerant’’, ASHRAE Standard 37–
2009, Methods of Testing for Rating
Electrically Driven Unitary AirConditioning and Heat Pump
Equipment, ASHRAE 41.1–2013 titled
‘‘Standard Method for Temperature
Measurement’’, ASHRAE 41.6–2014
titled ‘‘Standard Method for Humidity
Measurement’’, and ASHRAE 41.9–
2011titled ‘‘Standard Methods for
Volatile-Refrigerant Mass Flow
Measurements Using Calorimeters’’.
Finally, DOE proposes to updates its
IBR to the most recent version of the
following test procedure from ASHRAE
and AMCA: ASHRAE/AMCA 51–07/
210–07, Laboratory Methods of Testing
Fans for Certified Aerodynamic
Performance Rating.
ANSI/AHRI 210/240–2008 is an
industry accepted test procedure that
measures the cooling and heating
performance of central air conditioners
and heat pumps and is applicable to
products sold in North America. The
test procedure proposed in this SNOPR
references various sections of ANSI/
AHRI 210/240–2008 that address test
setup, test conditions, and rating
requirements. ANSI/AHRI 210/240–
2008 is readily available on AHRI’s Web
site at https://www.ahrinet.org/site/686/
Standards/HVACR-Industry-Standards/
Search-Standards. AHRI Standard 210/
240-Draft is a draft version of AHRI 210/
240 that AHRI provided to DOE in 2015.
AHRI Standard 210/240-Draft will
supersede the 2008 version once it is
published. The draft version is available
on the rulemaking Web page (Docket
EERE–2009–BT–TP–0004–0045).
ANSI/AHRI 1230–2010 is an industry
accepted test procedure that measures
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the cooling and heating performance of
variable refrigerant flow (VRF) multisplit air conditioners and heat pumps
and is applicable to products sold in
North America. The test procedure
proposed in this SNOPR for VRF multisplit systems references various sections
of ANSI/AHRI 1230–2010 that address
test setup, test conditions, and rating
requirements. ANSI/AHRI 1230–2010 is
readily available on AHRI’s Web site at
https://www.ahrinet.org/site/686/
Standards/HVACR-Industry-Standards/
Search-Standards.
ASHRAE 23.1–2010 is an industry
accepted test procedure for rating the
thermodynamic performance of positive
displacement refrigerant compressors
and condensing units that operate at
subcritical temperatures. The test
procedure proposed in this SNOPR
references sections of ASHRAE 23.1–
2010 that address requirements,
instruments, methods of testing, and
testing procedure specific to compressor
calibration. ASHRAE 23.1–2010 can be
purchased from ASHRAE’s Web site at
https://www.ashrae.org/resourcespublications.
ASHRAE Standard 37–2009 is an
industry accepted standard that
provides test methods for determining
the cooling capacity of unitary airconditioning equipment and the cooling
or heating capacities, or both, of unitary
heat pump equipment. The test
procedure proposed in this SNOPR
references various sections of ASHRAE
Standard 37–2009 that address test
conditions and test procedures. The
current DOE test procedure references a
previous version of this standard,
ASHRAE 37–2005. ASHRAE Standard
37–2009 can be purchased from
ASHRAE’s Web site at https://
www.ashrae.org/resources-publications.
ASHRAE 41.1–2013 is an industry
accepted method for measuring
temperature in testing heating,
refrigerating, and air-conditioning
equipment. The test procedure proposed
in this SNOPR references sections of
ASHRAE 41.1–2013 that address
requirements, instruments, and methods
for measuring temperature. ASHRAE
41.1–2013 can be purchased from
ASHRAE’s Web site at https://
www.ashrae.org/resources-publications.
ASHRAE 41.6–2014 is an industry
accepted test method for measuring
humidity of moist air. The test
procedure proposed in this SNOPR
references sections of ASHRAE 41.6–
2014 that address requirements,
instruments, and methods for measuring
humidity. ASHRAE 41.6–2014 can be
purchased from ASHRAE’s Web site at
https://www.ashrae.org/resourcespublications.
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ASHRAE 41.9–2011 is an industry
accepted standard that provides
recommended practices for measuring
the mass flow rate of volatile
refrigerants using calorimeters. The test
procedure proposed in this SNOPR
references sections of ASHRAE 41.9–
2011 that address requirements,
instruments, and methods for measuring
refrigerant flow during compressor
calibration. ASHRAE 41.9–2011 can be
purchased from ASHRAE’s Web site at
https://www.ashrae.org/resourcespublications.
ASHRAE/AMCA 51–07/210–07 is an
industry accepted standard that
establishes uniform test methods for a
laboratory test of a fan or other air
moving device to determine its
aerodynamic performance in terms of
air flow rate, pressure developed, power
consumption, air density, speed of
rotation, and efficiency for rating or
guarantee purposes. The test procedure
in this SNOPR references various
sections of ASHRAE/AMCA 51–07/210–
07 that address test conditions. The
current DOE test procedure references a
previous version of this standard,
ASHRAE/AMCA 51–99/210–99.
ASHRAE/AMCA 51–07/210–07 can be
purchased from AMCA’s Web site at
https://www.amca.org/store/index.php.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
V. Public Participation
A. Submission of Comments
DOE will accept comments, data, and
information regarding this proposed
rule no later than the date provided in
the DATES section at the beginning of
this proposed rule. Interested parties
may submit comments using any of the
methods described in the ADDRESSES
section at the beginning of this notice.
Submitting comments via
regulations.gov. The regulations.gov
Web page will require you to provide
your name and contact information.
Your contact information will be
viewable to DOE Building Technologies
staff only. Your contact information will
not be publicly viewable except for your
first and last names, organization name
(if any), and submitter representative
name (if any). If your comment is not
processed properly because of technical
difficulties, DOE will use this
information to contact you. If DOE
cannot read your comment due to
technical difficulties and cannot contact
you for clarification, DOE may not be
able to consider your comment.
However, your contact information
will be publicly viewable if you include
it in the comment or in any documents
attached to your comment. Any
information that you do not want to be
publicly viewable should not be
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included in your comment, nor in any
document attached to your comment.
Persons viewing comments will see only
first and last names, organization
names, correspondence containing
comments, and any documents
submitted with the comments.
Do not submit to regulations.gov
information for which disclosure is
restricted by statute, such as trade
secrets and commercial or financial
information (hereinafter referred to as
Confidential Business Information
(CBI)). Comments submitted through
regulations.gov cannot be claimed as
CBI. Comments received through the
Web site will waive any CBI claims for
the information submitted. For
information on submitting CBI, see the
Confidential Business Information
section.
DOE processes submissions made
through regulations.gov before posting.
Normally, comments will be posted
within a few days of being submitted.
However, if large volumes of comments
are being processed simultaneously,
your comment may not be viewable for
up to several weeks. Please keep the
comment tracking number that
regulations.gov provides after you have
successfully uploaded your comment.
Submitting comments via email, hand
delivery, or mail. Comments and
documents submitted via email, hand
delivery, or mail also will be posted to
regulations.gov. If you do not want your
personal contact information to be
publicly viewable, do not include it in
your comment or any accompanying
documents. Instead, provide your
contact information on a cover letter.
Include your first and last names, email
address, telephone number, and
optional mailing address. The cover
letter will not be publicly viewable as
long as it does not include any
comments.
Include contact information each time
you submit comments, data, documents,
and other information to DOE. If you
submit via mail or hand delivery, please
provide all items on a CD, if feasible. It
is not necessary to submit printed
copies. No facsimiles (faxes) will be
accepted.
Comments, data, and other
information submitted to DOE
electronically should be provided in
PDF (preferred), Microsoft Word or
Excel, WordPerfect, or text (ASCII) file
format. Provide documents that are not
secured, written in English and free of
any defects or viruses. Documents
should not contain special characters or
any form of encryption and, if possible,
they should carry the electronic
signature of the author.
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Campaign form letters. Please submit
campaign form letters by the originating
organization in batches of between 50 to
500 form letters per PDF or as one form
letter with a list of supporters’ names
compiled into one or more PDFs. This
reduces comment processing and
posting time.
Confidential Business Information.
According to 10 CFR 1004.11, any
person submitting information that he
or she believes to be confidential and
exempt by law from public disclosure
should submit via email, postal mail, or
hand delivery two well-marked copies:
One copy of the document marked
confidential including all the
information believed to be confidential,
and one copy of the document marked
non-confidential with the information
believed to be confidential deleted.
Submit these documents via email or on
a CD, if feasible. DOE will make its own
determination about the confidential
status of the information and treat it
according to its determination.
Factors of interest to DOE when
evaluating requests to treat submitted
information as confidential include: (1)
A description of the items; (2) whether
and why such items are customarily
treated as confidential within the
industry; (3) whether the information is
generally known by or available from
other sources; (4) whether the
information has previously been made
available to others without obligation
concerning its confidentiality; (5) an
explanation of the competitive injury to
the submitting person which would
result from public disclosure; (6) when
such information might lose its
confidential character due to the
passage of time; and (7) why disclosure
of the information would be contrary to
the public interest.
It is DOE’s policy that all comments
may be included in the public docket,
without change and as received,
including any personal information
provided in the comments (except
information deemed to be exempt from
public disclosure).
B. Issues on Which DOE Seeks Comment
Although DOE welcomes comments
on any aspect of this proposal, DOE is
particularly interested in receiving
comments and views of interested
parties concerning the following issues:
1. The details characterizing the same
model of indoor unit, same model of
outdoor unit, and same single-package
model;
2. Its proposed changes to the
determination of certified ratings for
single-split-system air conditioners,
specifically in its proposed phased
approach where in the first phase
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manufacturers must certify all models of
outdoor units with the model of coilonly indoor unit that is likely to have
the largest volume of retail sales with
the particular model of outdoor unit but
may use the model of blower coil indoor
unit likely to have the highest sales if
the model of outdoor unit is sold only
with models of blower coil indoor units,
and may use testing or AEDMs to rate
other combinations; and in the second
phase manufacturers must certify all
models of outdoor units with the model
of blower coil indoor unit that is likely
to have the largest volume of retail sales
with that model of outdoor unit but
must rate other blower coil or coil-only
combinations through testing or
AEDMs;
3. Its proposed definitions for blower
coil and coil-only indoor units;
4. Whether additional testing and
rating requirements are necessary for
multi-split systems paired with models
of conventional ducted indoor units
rather than short-duct units;
5. Whether manufacturers or other
stakeholders support ratings for mixmatch multi-split systems including
models of both SDHV and non-ducted
or short-ducted indoor units, and if so,
how they should be rated (i.e., by by
taking the mean of a sample of tested
non-ducted units and a sample of tested
SDHV units or by testing a combination
on non-ducted and SDHV units), and
whether the SDHV or split-system
standard would be most appropriate;
6. Whether manufacturers support
having the ability to test mix-match
systems using the test procedure rather
than rating them using an average of the
other tested systems;
7. Whether manufacturers support the
rating of mix-match systems using other
than a straight mean, such as a
weighting by the number of non-ducted
or short-ducted units;
8. Whether the definition of ‘‘tested
combination’’ is appropriate for rating
specific individual combinations, or
whether manufacturers want more
flexibility such as testing with more
than 5 indoor units;
9. Information and data on
manufacturing and testing variability
associated with multi-split systems that
would allow it to understand how a
single unit may be representative of the
population and what tolerances would
need to be applied to ratings based on
a single unit sample in order to account
for variability;
10. The basic model definition in
section III.A.1;
11. Its proposal for ICMs to test each
model of indoor unit with the lowestSEER model of outdoor unit that is
certified as a part of a basic model by
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an OUM as well as any test burden
associated with this proposal;
12. The likelihood of multiple
individual models of single-package
units meeting the requirements
proposed in the basic model definition
to be assigned to the same basic model;
13. Whether, if manufacturers are able
to assign multiple individual singlepackage models to a single basic model,
whether manufacturers would want to
use an AEDM to rate other individual
models within the same basic model
other than the lowest SEER individual
model;
14. Whether manufacturers would
want to employ an AEDM to rate the offmode power consumption for other
variations of off-mode associated with
the single-package basic model other
than the variation tested;
15. The reporting burden associated
with the proposed certification
reporting requirements proposed in this
notice;
16. The additions to the represented
value requirements for cooling capacity,
heating capacity, and SHR, as well as
the proposed rounding requirements;
17. The proposal to not require
additional testing to validate an AEDM
beyond the testing required under
429.16(a)(2)(ii) for split-system air
conditioners and heat pumps where
manufacturers must test each basic
model, being each model of outdoor
unit, with at least one model of indoor
unit;
18. The proposal that ICMs must use
the combinations they would be
required to test, under 429.16, to
validate an AEDM that is intended to be
used for other individual combinations
within each basic model;
19. Whether the approach to not
penalize manufacturers for applying
conservative ratings to their products is
reasonable to identify an individual
combination’s failure to meet its
certified rating;
20. Whether manufacturers would
typically apply more than one AEDM,
and if they would, the differences
between such AEDMs;
21. Its proposal for multi-circuit
products to adopt the same common
duct testing approach used for testing
multi-split products; and whether this
method will yield accurate results that
are representative of the true
performance of these systems;
22. Its proposals for multi-blower
products, including whether individual
adjustments of each blower are
appropriate and whether external static
pressures measured for individual tests
may be different;
23. Its proposal to require a test for off
mode power consumption at 72±2 °F, a
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second test at the temperature below a
turn-on temperature specified by the
manufacturer, a tolerance on the
temperature, and the proposal that
manufacturers include in certification
reports the temperatures at which the
crankcase heater is designed to turn on
and turn off for the heating season, if
applicable;
24. The proposal to replace the off
mode test at 57 °F with a test at a
temperature which is 5±2 °F below a
manufacturer-specified turn-on
temperature to maintain the intent of
the off mode power consumption rating
as a rating that measures the off mode
power consumption for the heating
season, and allay the stakeholders’
concerns of a loophole at the 57 °F test
point;
25. The proposal to use a percompressor off mode power
consumption metric so as to not
penalize manufacturers of products with
multiple compressor systems, which are
highly efficient and require larger
crankcase heaters for safe and reliable
operation;
26. The proposal on the multiplier of
1.5 for determining the shoulder season
and heating season per-compressor off
mode power so as to not penalize
manufacturers of products with
modulated compressors, which require
a larger crankcase heater to ensure safe
and reliable operation;
27. The proposal to more accurately
reflect the off mode power consumption
for coil-only and blower coil splitsystem units by excluding the lowvoltage power from the indoor unit
when measuring off mode power
consumption for coil-only split-system
air conditioners and including the lowvoltage power from the indoor unit
when measuring off mode power
consumption for blower coil splitsystem air conditioning and heat
pumps;
28. The proposal to incent
manufacturers of products with time
delays by adopting a credit to shoulder
season energy consumption that is
proportional to the duration of the delay
or a default of 25% savings in shoulder
season off mode energy consumption
and the possibility of a verification test
for length of time delay;
29. The proposal to add optional
informational equations to determine
the actual off mode energy
consumption, based on the hours of off
mode operation and off mode power for
the shoulder and heating seasons;
30. Whether regulating crankcase
heater energy consumption has a
negative impact on product reliability in
light of the test method proposed in this
rule;
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31. The proposal to improve
repeatability of testing central air
conditioner and heat pump products by
requiring the lowest fan speed setting
that meets minimum static pressure and
maximum air volume rate requirements
for blower coil systems and requiring
the lowest fan speed settings that meets
the maximum static pressure and
maximum air volume rate requirements
for coil-only indoor units;
32. The proposal to mirror how
insulation is installed in the field by
requiring test laboratories either install
the insulation shipped with the unit or
use insulation as specified in the
manufacturer’s installation manuals
included with the unit;
33. The proposal to clarify liquid
refrigerant line insulation requirements
by requiring such insulation only if the
product is a heating-only heat pump;
34. The proposal to prevent thermal
losses from the refrigerant mass flow
meter to the floor by requiring a thermal
barrier if the meter is not mounted on
a pedestal or is not elevated;
35. The proposal to require either an
air sampling device used on all outdoor
unit air-inlet surfaces or demonstration
of air temperature uniformity for the
outdoor unit vis-a-vis 1.5 °F maximum
spread of temperatures measured by
thermocouples distributed one
thermocouple per square feet of air-inlet
surface of the outdoor unit;
36. The proposal to require that the
dry bulb temperature and humidity
measurements used to verify that the
required outdoor air conditions have
been maintained be measured for the air
collected by the air sampling device
(e.g., rather than being measured by
temperature sensors located in the air
stream approaching the air inlets);
37. The proposal to limit thermal
losses by preventing the air sampling
device from nearing the test chamber
floor, insulating air sampling device
surfaces, and requiring dry bulb and
humidity measurements be made at the
same location in the air sampling
device;
38. The proposal to fix maximum
compressor speed when testing at each
of the outdoor temperature for those
control systems that vary maximum
compressor speed with outdoor
temperature;
39. The proposal to prevent improper
refrigerant charging techniques by
requiring charging of near-azeotropic
and zeotropic refrigerant blends in the
liquid state only;
40. The proposal to require, for air
conditioners and cooling-and-heating
heat pumps refrigerant charging at the A
or A2 test condition, and for heatingonly heat pumps refrigerant charging at
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the H1 or H12 test condition, to meet a
12 ± 2 °F superheat temperature
requirement for units equipped with
fixed orifice type metering devices and
a 10 ± 2 °F subcooling temperature
requirement for units equipped with
thermostatic expansion valve or
electronic expansion valve type
metering devices, if no manufacturer
installation instructions provide
guidance on charging procedures;
41. The proposal to verify
functionality of heat pumps at the H1 or
H12 test condition after charging at the
A or A2 test condition, and if nonfunctional, the proposal to adjust
refrigerant charge to the requirements of
the proposed standardized charging
procedure at the H1 or H12 test
condition;
42. The proposal to require refrigerant
charging based on the outdoor
installation instructions for outdoor unit
manufacturer products and refrigerant
charging based on the indoor
installation instructions for independent
coil manufacturer products, where both
the indoor and outdoor installation
instructions are provided and advise
differently, unless otherwise specified
by either installation instructions;
43. The proposal to require
installation of pressure gauges and
verification of refrigerant charge amount
and, if charging instructions are not
available adjust charge based on the
proposed refrigerant charging
procedure;
44. All aspects of its proposals to
amend the refrigerant charging
procedures;
45. The proposal to allow for cyclic
tests of single-package ducted units an
upturned duct as an alternative
arrangement to replace the currentlyrequired damper in the inlet portion of
the indoor air ductwork;
46. The proposal to further justify
adequacy of the alternative arrangement
in preventing thermal losses during the
OFF portion of the cyclic test by
proposing installing a dry bulb
temperature sensor near the indoor inlet
and requiring the maximum permissible
range of the recorded temperatures
during the OFF period be no greater
than 1.0 °F;
47. The proposed revisions to the
cyclic test procedure for the
determination of both the cooling and
heating coefficient of degradation,
including additional test data that
would support the proposed
specifications, or changes to, the
number of warm-up cycles, the cycle
time for variable speed units, the
number of cycles averaged to obtain the
value, and the stability criteria;
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48. The proposal to allay stakeholder
concerns regarding compressor break-in
period by allowing an optional break-in
period of up to 20 hours prior to testing;
49. Its proposed limitation of
incorporation by reference to industry
standards to specific sections necessary
for the test procedure, including any
specific sections stakeholders feel
should be referenced that are not;
50. The proposed sampling interval
for dry-bulb temperatures, wet bulb
temperature, dew point temperature,
and relative humidity;
51. The appropriate use of the target
value and maximum tolerances for
refrigerant charging, as well as data to
support the appropriate selection of
tolerance;
52. The proposal for damping
pressure transducer signals including
whether the proposed maximum time
constant is appropriate;
53. Setting a definition for short duct
systems to mean ducted systems whose
indoor units can deliver no more than
0.07 in. wc. ESP when delivering the
full load air volume rate for cooling
operation, and requiring such systems
meet the minimum ESP levels as
proposed in the NOPR: 0.03 in. wc. for
units less than 28,800 Btu/h; 0.05 in.
wc. for units between 29,000 Btu/h and
42,500 Btu/h; and 0.07 in. wc. for units
greater than 43,000 Btu/h;
54. The incorporation by reference of
AHRI 1230–2010, and in particular the
specific sections of Appendix M and
AHRI 1230–2010 that DOE proposes to
apply to testing VRF systems;
55. The proposed change to the
informative tables at the beginning of
Section 2. Testing Conditions and/or
whether additional modifications to the
new table could be implemented to
further improve clarity;
56. Its proposal to delete the
definition of mini-split air conditioners
and heat pumps, and define (1) singlezone-multiple-coil split-system to
represent a split-system that has one
outdoor unit and that has two or more
coil-only or blower coil indoor units
connected with a single refrigeration
circuit, where the indoor units operate
in unison in response to a single indoor
thermostat; and (2) single-split-system
to represent a split-system that has one
outdoor unit and that has one coil-only
or blower coil indoor unit connected to
its other component(s) with a single
refrigeration circuit;
57. Its proposal to include in the ESP
requirement a pressure drop
contribution associated with average
typical filter and indoor coil fouling
levels and its use of residential-based
indoor coil and filter fouling pressure
drop data to estimate the appropriate
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ESP contribution; DOE also requests
data that would validate the proposed
ESP contributions or suggest
adjustments that should be made to
improve representativeness of the
values in this proposal;
58. Its proposals to set higher
minimum ESP requirements for systems
other than multi-split systems and
small-duct, high-velocity systems and
report the external static pressure used
during their certification tests;
59. Its proposal to implement an
allowance in ESP for air-conditioning
units tested in blower-coil (or singlepackage) configuration in which a
condensing furnace is in the air flow
path during the test. DOE seeks
comment regarding the proposed 0.1 in.
wc. ESP reduction for such tests,
including test data to support
suggestions regarding different
reductions.
60. Its proposal to revise the heating
load line that shifts the heating balance
point and zero load point to lower
ambient temperatures that better reflect
field operations and energy use
characteristics, as well as its proposal to
perform cyclic testing for variable speed
heat pumps at 47 °F instead of at 62 °F;
61. Whether, in the case that the
proposed heating load line is not
adopted, DOE should modify the HSPF
rating procedure for variable speed heat
pumps at mid-range outdoor
temperatures using option 1: Which
entails basing performance on minimum
speed tests at 47 °F and intermediate
speed test at 35 °F and is the less
accurate option but has no additional
test burden; or option 2: Which entails
basing performance on minimum speed
tests at 47 °F and at 35 °F and is more
accurate but with higher test burden;
62. Test results and other data
regarding whether HSPF results for
other variable speed heat pumps would
be more significantly impacted by this
change to the test procedure to test at
maximum speed at 2 °F outdoor
temperature or at low cutoff
temperature, whichever is higher (in
conjunction with the test at maximum
speed at 17 °F outdoor temperature) as
well as whether the additional test
burden would offset the advantages of
the proposed modification;
63. The estimate of the number of
small entities that may be impacted by
the proposed test procedure and its
conclusion that the impact is not
significant.
VI. Approval of the Office of the
Secretary
The Secretary of Energy has approved
publication of this proposed rule.
List of Subjects
10 CFR Part 429
Administrative practice and
procedure, Confidential business
information, Energy conservation,
Reporting and recordkeeping
requirements.
10 CFR Part 430
Administrative practice and
procedure, Confidential business
information, Energy conservation,
Energy conservation test procedures,
Household appliances, Imports,
Incorporation by reference,
Intergovernmental relations, Small
businesses.
Issued in Washington, DC, on August 21,
2015.
Kathleen B. Hogan,
Deputy Assistant Secretary for Energy
Efficiency, Energy Efficiency and Renewable
Energy.
For the reasons set forth in the
preamble, DOE proposes to amend parts
429 and 430 of chapter II of Title 10,
Subpart B, Code of Federal Regulations,
to read as follows:
PART 429—CERTIFICATION,
COMPLIANCE, AND ENFORCEMENT
FOR CONSUMER PRODUCTS AND
COMMERCIAL AND INDUSTRIAL
EQUIPMENT
1. The authority citation for part 429
continues to read as follows:
■
Authority: 42 U.S.C. 6291–6317.
2. Amend § 429.12 by revising
paragraphs (b)(8) and (12) to read as
follows:
■
§ 429.12 General requirements applicable
to certification reports.
*
*
*
*
*
(b) * * *
(8) The test sample size (i.e., number
of units tested for the basic model, or in
the case of single- split-system central
air conditioners and central air
conditioning heat pumps, for each
individual combination). Enter ‘‘0’’ if an
AEDM was used in lieu of testing;
*
*
*
*
*
(12) If the test sample size is listed as
‘‘0’’ to indicate the certification is based
upon the use of an alternate way of
determining measures of energy
Category
Equipment type
Single-Package Unit ............
Single-Package AC ...........
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conservation, identify the method used
for determining measures of energy
conservation (such as ‘‘AEDM,’’ or
linear interpolation). Manufacturers of
commercial packaged boilers,
commercial water heating equipment,
commercial refrigeration equipment,
and commercial HVAC equipment must
provide the manufacturer’s designation
(name or other identifier) of the AEDM
used; and
*
*
*
*
*
■ 3. Section 429.16 is revised to read as
follows:
§ 429.16 Central air conditioners and
central air conditioning heat pumps.
(a) Determination of Certified Rating.
Determine the certified rating for each
basic model through testing pursuant to
paragraph (a)(1)(ii) of this section. For
single-split-systems, manufacturers
must certify additional ratings for each
individual combination within the same
basic model either based on testing or
by using an AEDM subject to the
limitations of paragraph (a)(2) of this
section. This includes blower coil and
coil-only systems both before and after
the compliance date of any amended
energy conservation standards. For
multi-split, multi-circuit, and singlezone-multiple-coil systems, each basic
model must include a rating for a nonducted combination and may also
include ratings for a ducted
combination and a mixed non-ducted/
short-ducted combination per the
requirements specified in this section. If
individual models of single-package
systems or individual combinations of
split-systems that are otherwise
identical are offered with multiple
options for off mode-related
components, rate the individual model/
combination with the crankcase heater
and controls that are the most
consumptive. A manufacturer may also
certify less consumptive off mode
options; however, the manufacturer
must differentiate the individual model
numbers in its certification report.
(1) Units to be tested.
(i) General. The general requirements
of § 429.11 apply to central air
conditioners and heat pumps; and
(ii) Model selection for testing. (A)
Except for single-split-system nonspace-constrained air conditioners,
determine represented values for each
basic model through testing of the
following, specific, individual model or
combination pursuant to the table
below.
Must test each:
With:
Basic Model .......................
Lowest SEER individual model.
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Category
Must test each:
Single-Package HP.
Space-Constrained SinglePackage AC.
Space-Constrained SinglePackage HP.
Single-Split-System HP .....
Space-Constrained SplitSystem AC.
Space-Constrained SplitSystem HP.
Multi-Split, Multi-Circuit, or
Single-Zone-Multiple-Coil
Split System.
Indoor Unit Only (Rated by
ICM).
Outdoor Unit Only ................
With:
Model of Outdoor Unit .......
The model of indoor unit that is likely to have the largest volume of retail sales with the particular model
of outdoor unit.
Model of Outdoor Unit .......
At a minimum, a ‘‘tested combination’’ composed entirely of non-ducted indoor units. For any models of
outdoor units also sold with models of short-ducted
indoor units, a second ‘‘tested combination’’ composed entirely of short-ducted indoor units must be
tested (in addition to the non-ducted combination).
For any models of outdoor units also sold with models of SDHV indoor units, a second (or third) ‘‘tested
combination’’ composed entirely of SDHV units must
be tested (in addition to the non-ducted combination
and, if tested, the short-ducted combination).
Least efficient model of outdoor unit with which it will
be paired, where the least efficient model of outdoor
unit is the outdoor unit in the lowest SEER combination as certified by the OUM). If there are multiple
models of outdoor units with the same lowest-SEER
rating, the ICM may select one for testing purposes.
Single-Split-System ...........
Model of Indoor Unit ..........
Small-Duct, High Velocity
Systems.
Outdoor Unit Only .............
Model of Outdoor Unit .......
(B) For single-split-system, non-spaceconstrained air conditioners rated by
OUMs, determine represented values for
Model of indoor unit meeting the requirements of section 2.2e of Appendix M (or M1) to Subpart B of 10
CFR Part 430.
each basic model through testing of the
following, specific, individual
combination, with requirements
Date
Equipment type
Before the compliance date
of any amended energy
conservation standards
(with a compliance date
after January 1, 2017).
depending on date and pursuant to the
table below.
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With:
Split-System AC with single capacity condensing
unit.
Model of Outdoor Unit .......
The model of coil-only indoor unit that is likely to have
the largest volume of retail sales with the particular
model of outdoor unit.
Split-System AC with other
than single capacity condensing unit.
On or after the compliance
date of any amended energy conservation standards with which compliance is required on or
after January 1, 2017.
Must test each:
Model of Outdoor Unit .......
Split-system AC .................
Model of Outdoor Unit .......
The model of coil-only indoor unit that is likely to have
the largest volume of retail sales with the particular
model of outdoor unit, unless the model of outdoor
unit is only sold with model(s) of blower coil indoor
units, in which case the model of blower coil indoor
unit (with designated air mover as applicable) that is
likely to have the largest volume of retail sales with
the particular model of outdoor unit.
The model of blower coil indoor unit that is likely to
have the largest volume of retail sales with the particular model of outdoor unit.
(iii) Sampling plans and
representative values. (A) Each basic
model (for single-package systems) or
individual combination (for split–
systems) tested must have a sample of
sufficient size tested in accordance with
the applicable provisions of this
subpart. The represented values for any
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basic model or individual combination
must be assigned such that:
(1) Any represented value of power
consumption or other measure of energy
consumption for which consumers
would favor lower values must be
greater than or equal to the higher of:
(i) The mean of the sample, where:
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¯
and x is the sample mean; n is the number
of samples; and xi is the ith sample; Or,
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Outdoor Unit and Indoor
Unit (Rated by OUM).
Equipment type
¯
And x is the sample mean; s is the sample
standard deviation; n is the number of
samples; and t0.90 is the t statistic for a
90% one-tailed confidence interval with
n–1 degrees of freedom (from Appendix
D).
(2) Any represented value of the
energy efficiency or other measure of
energy consumption for which
consumers would favor higher values
shall be less than or equal to the lower
of:
(i) The mean of the sample, where:
¯
and, x is the sample mean; n is the number
of samples; and xi is the ith sample; or,
(ii) The lower 90 percent confidence
limit (LCL) of the true mean divided by
0.95, where:
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¯
And x is the sample mean; s is the sample
standard deviation; n is the number of
samples; and t0.90 is the t statistic for a
90% one-tailed confidence interval with
n–1 degrees of freedom (from Appendix
D).
(3) The represented value of cooling
capacity is the mean of the capacities
measured for the sample, rounded:
(i) To the nearest 100 Btu/h if cooling
capacity is less than 20,000 Btu/h,
(ii) To the nearest 200 Btu/h if cooling
capacity is greater than or equal to
20,000 Btu/h but less than 38,000 Btu/
h, and
(iii) To the nearest 500 Btu/h if
cooling capacity is greater than or equal
to 38,000 Btu/h and less than 65,000
Btu/h.
(4) The represented value of heating
capacity is the mean of the capacities
measured for the sample, rounded:
(i) To the nearest 100 Btu/h if heating
capacity is less than 20,000 Btu/h,
(ii) To the nearest 200 Btu/h if heating
capacity is greater than or equal to
20,000 Btu/h but less than 38,000 Btu/
h, and
(iii) To the nearest 500 Btu/h if
heating capacity is greater than or equal
to 38,000 Btu/h and less than 65,000
Btu/h.
(5) The represented value of sensible
heat ratio (SHR) is the mean of the SHR
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measured for the sample, rounded to the
nearest percent (%).
(B) For heat pumps (other than
heating-only heat pumps), all units of
the sample population must be tested in
both the cooling and heating modes and
the results used for determining all
representations.
(C) Determine the represented value
of estimated annual operating cost for
cooling-only units or the cooling portion
of the estimated annual operating cost
for air-source heat pumps that provide
both heating and cooling by calculating
the product of:
(1) The quotient of the represented
value of cooling capacity, in Btu’s per
hour as determined in paragraph
(a)(1)(iii)(A)(3) of this section, divided
by the represented value of SEER, in
Btu’s per watt-hour, as determined in
paragraph (a)(1)(iii)(A)(2) of this section;
(2) The representative average use
cycle for cooling of 1,000 hours per
year;
(3) A conversion factor of 0.001
kilowatt per watt; and
(4) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act.
(D) Determine the represented value
of estimated annual operating cost for
air-source heat pumps that provide only
heating or for the heating portion of the
estimated annual operating cost for airsource heat pumps that provide both
heating and cooling, as follows:
(1) When using appendix M to
subpart B of part 430, the product of:
(i) The quotient of the mean of the
standardized design heating
requirement for the sample, in Btu’s per
hour, nearest to the Region IV minimum
design heating requirement, determined
for each unit in the sample in section
4.2 of appendix M to subpart B of part
430, divided by the represented value of
heating seasonal performance factor
(HSPF), in Btu’s per watt-hour,
calculated for Region IV corresponding
to the above-mentioned standardized
design heating requirement, as
determined in paragraph (a)(1)(iii)(A)(2)
of this section;
(ii) The representative average use
cycle for heating of 2,080 hours per
year;
(iii) The adjustment factor of 0.77,
which serves to adjust the calculated
design heating requirement and heating
load hours to the actual load
experienced by a heating system;
(iv) A conversion factor of 0.001
kilowatt per watt; and
(v) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act; and
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(2) When using appendix M1 to
subpart B of part 430, the product of:
(i) The quotient of the represented
value of cooling capacity (for air-source
heat pumps that provide both cooling
and heating) in Btu’s per hour, as
determined in paragraph (a)(1)(iii)(A)(3)
of this section, or the represented value
of heating capacity (for air-source heat
pumps that provide only heating), as
determined in paragraph (a)(1)(iii)(A)(4)
of this section, divided by the
represented value of heating seasonal
performance factor (HSPF), in Btu’s per
watt-hour, calculated for Region IV, as
determined in paragraph (a)(1)(iii)(A)(2)
of this section;
(ii) The representative average use
cycle for heating of 1,572 hours per
year;
(iii) The adjustment factor of 1.30,
which serves to adjust the calculated
design heating requirement and heating
load hours to the actual load
experienced by a heating system;
(iv) A conversion factor of 0.001
kilowatt per watt; and
(v) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act;
(E) Determine the represented value of
estimated annual operating cost for airsource heat pumps that provide both
heating and cooling by calculating the
sum of the quantity determined in
paragraph (a)(1)(iii)(C) of this section
added to the quantity determined in
paragraph (a)(1)(iii)(D) of this section.
(F) Determine the represented value of
estimated regional annual operating cost
for cooling-only units or the cooling
portion of the estimated regional annual
operating cost for air-source heat pumps
that provide both heating and cooling by
calculating the product of:
(1) The quotient of the represented
value of cooling capacity, in Btu’s per
hour, determined in paragraph
(a)(1)(iii)(A)(3) of this section divided by
the represented value of SEER, in Btu’s
per watt-hour, determined in paragraph
(a)(1)(iii)(A)(2) of this section;
(2) The estimated number of regional
cooling load hours per year determined
from Table 21 in section 4.3.2 of
appendix M or Table 20 in section 4.3.2
of appendix M1, as applicable, to
subpart B of part 430;
(3) A conversion factor of 0.001
kilowatts per watt; and
(4) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act.
(G) Determine the represented value
of estimated regional annual operating
cost for air-source heat pumps that
provide only heating or for the heating
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1.05, where:
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portion of the estimated regional annual
operating cost for air-source heat pumps
that provide both heating and cooling as
follows:
(1) When using Appendix M to
subpart B of Part 430, the product of:
(i) The estimated number of regional
heating load hours per year determined
from Table 21 in section 4.3.2 of
appendix M to subpart B of part 430;
(ii) The quotient of the mean of the
standardized design heating
requirement for the sample, in Btu’s per
hour, for the appropriate generalized
climatic region of interest (i.e.,
corresponding to the regional heating
load hours from ‘‘A’’) and determined
for each unit in the sample in section
4.2 of appendix M to subpart B of Part
430, divided by the represented value of
HSPF, in Btu’s per watt-hour, calculated
for the appropriate generalized climatic
region of interest and corresponding to
the above-mentioned standardized
design heating requirement, and
determined in paragraph (a)(1)(iii)(A)(2);
(iii) The adjustment factor of 0.77;
which serves to adjust the calculated
design heating requirement and heating
load hours to the actual load
experienced by a heating system;
(iv) A conversion factor of 0.001
kilowatts per watt; and
(v) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act; and
(2) When using Appendix M1 to
subpart B of Part 430, the product of:
(i) The estimated number of regional
heating load hours per year determined
from Table 20 in section 4.2 of appendix
M1 to subpart B of Part 430;
(ii) The quotient of the represented
value of cooling capacity (for air-source
heat pumps that provide both cooling
and heating) in Btu’s per hour, as
determined in section (a)(1)(iii)(A)(3), or
the represented value of heating
capacity (for air-source heat pumps that
provide only heating), as determined in
section (a)(1)(iii)(A)(4), divided by the
represented value of HSPF, in Btu’s per
watt-hour, calculated for the appropriate
generalized climatic region of interest,
and determined in (a)(1)(iii)(A)(2);
(iii) The adjustment factor of 1.30,
which serves to adjust the calculated
design heating requirement and heating
load hours to the actual load
experienced by a heating system;
(iv) A conversion factor of 0.001
kilowatts per watt; and
(v) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act.
(H) For air-source heat pumps that
provide both heating and cooling, the
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estimated regional annual operating cost
is the sum of the quantity determined in
paragraph (a)(1)(iii)(F) of this section
added to the quantity determined in
paragraph (a)(1)(iii)(G) of this section.
(I) The cooling mode efficiency
measure for cooling-only units and for
air-source heat pumps that provide
cooling is the represented value of the
SEER, in Btu’s per watt-hour, pursuant
to paragraph (a)(1)(iii)(A)(2) of this
section.
(J) The heating mode efficiency
measure for air-source heat pumps is the
represented value of the HSPF, in Btu’s
per watt-hour for each applicable
standardized design heating
requirement within each climatic
region, pursuant to paragraph
(a)(1)(iii)(A)(2) of this section.
(K) Round represented values of
estimated annual operating cost to the
nearest dollar per year. Round
represented values of EER, SEER, HSPF,
and APF to the nearest 0.05. Round
represented values of off-mode power
consumption, pursuant to paragraph
(a)(1)(iii)(A)(1) to the nearest watt.
(2) Units not required to be tested.
(i) For basic models rated by ICMs
and single-split-system air conditioners,
split-system heat pumps, spaceconstrained split-system heat pumps,
and space-constrained split-system air
conditioners. For every individual
combination within a basic model other
than the individual combination
required to be tested pursuant to
paragraph (a)(1)(ii) of this section,
either:
(A) A sample of sufficient size,
comprised of production units or
representing production units, must be
tested as complete systems with the
resulting ratings for the combination
obtained in accordance with paragraphs
(a)(1)(i) and (iii) of this section; or
(B) The representative values of the
measures of energy efficiency must be
assigned through the application of an
AEDM in accordance with paragraph
(a)(3) of this section and § 429.70. An
AEDM may only be used to rate
individual combinations in a basic
model other than the combination
required for mandatory testing under
paragraph (a)(1)(ii) of this section. No
basic model may be rated with an
AEDM.
(ii) For multi-split systems, multicircuit systems, and single-zonemultiple-coil systems. The following
applies:
(A) For basic models composed of
both non-ducted and short-ducted units,
the represented value for the mixed
non-ducted/short-ducted combination is
the mean of the represented values for
the non-ducted and short-ducted
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combinations as determined in
accordance with paragraph (a)(1)(iii)(A)
of this section.
(B) All other individual combinations
of models of indoor units for the same
model of outdoor unit for which the
manufacturer chooses to make
representations must be rated as a
different basic model, and the
provisions of (a)(1)(i) through (a)(1)(iii)
and (a)(2)(ii)(A) of this section apply.
(3) Alternative efficiency
determination methods. In lieu of
testing, represented values of efficiency
or consumption may be determined
through the application of an AEDM
pursuant to the requirements of § 429.70
and the provisions of this section.
(i) Power or energy consumption. Any
represented value of the average off
mode power consumption or other
measure of energy consumption of an
individual combination for which
consumers would favor lower values
must be greater than or equal to the
output of the AEDM.
(ii) Energy efficiency. Any represented
value of the SEER, EER, HSPF or other
measure of energy efficiency of an
individual combination for which
consumers would favor higher values
must be less than or equal to the output
of the AEDM.
(b) Limitations. The following section
explains the limitations for certification
of models.
(1) Regional. Any model of outdoor
unit that is certified in a combination
that does not meet all regional standards
cannot also be certified in a
combination that meets the regional
standard(s). Outdoor unit model
numbers cannot span regions unless the
model of outdoor unit is compliant with
all standards in all possible
combinations. If a model of outdoor unit
is certified below a regional standard,
then it must have a unique individual
model number for distribution in each
region.
(2) Multiple product classes. Models
of outdoor units that are rated and
distributed in combinations that span
multiple product classes must be tested
and certified pursuant to paragraph (a)
as compliant with the applicable
standard for each product class.
(c) Certification reports. This
paragraph specifies the information that
must be included in a certification
report.
(1) General. The requirements of
§ 429.12 apply to central air
conditioners and heat pumps.
(2) Public product-specific
information. Pursuant to § 429.12(b)(13),
for each basic model (for single-package
systems) or individual combination (for
split-systems), a certification report
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must include the following public
product-specific information: The
seasonal energy efficiency ratio (SEER
in British thermal units per Watt-hour
(Btu/W-h)); the average off mode power
consumption (PW,OFF in Watts); the
cooling capacity in British thermal units
per hour (Btu/h); the sensible heat ratio
calculated based on full-load cooling
conditions at the outdoor ambient
conditions of 82 °F dry bulb and 65 °F
wet bulb; and
(i) For heat pumps, the heating
seasonal performance factor (HSPF in
British thermal units per Watt-hour
(Btu/W-h));
(ii) For air conditioners (excluding
space constrained), the energy efficiency
ratio (EER in British thermal units per
Watt-hour (Btu/W-h));
(iii) For single-split-system
equipment, whether the rating is for a
coil-only or blower coil system; and
(iv) For multi-split, multiple-circuit,
and single-zone-multiple-coil systems
(including VRF), whether the rating is
for a non-ducted, short-ducted, SDHV,
or mixed non-ducted and short-ducted
system.
(3) Basic and individual model
numbers. The basic model number and
individual model number(s) required to
be reported under § 429.12(b)(6) must
consist of the following:
Individual model No(s).
Equipment type
Basic model No.
1
Single Package .................
Split System (rated by
OUM).
Outdoor Unit Only .............
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Split-System or SDHV
(rated by ICM).
2
Number unique to the
basic model.
Number unique to the
basic model.
Package ............................
N/A ....................................
N/A.
Outdoor Unit ......................
Indoor Unit(s) ....................
Number unique to the
basic model.
Number unique to the
basic model.
Outdoor Unit ......................
N/A ....................................
Air Mover (or N/A if rating
coil-only system or fan is
part of indoor unit model
number).
N/A.
Outdoor Unit ......................
Indoor Unit(s) ....................
N/A.
(4) Additional product-specific
information. Pursuant to § 429.12(b)(13),
for each individual model/combination,
a certification report must include the
following additional product-specific
information: The cooling full load air
volume rate for the system or for each
indoor unit as applicable (in cubic feet
per minute (cfm)); the air volume rates
for other test conditions including
minimum cooling air volume rate,
intermediate cooling air volume rate,
full load heating air volume rate,
minimum heating air volume rate,
intermediate heating air volume rate,
and nominal heating air volume rate
(cfm) for the system or for each indoor
unit as applicable, if different from the
cooling full load air volume rate;
whether the individual model uses a
fixed orifice, thermostatic expansion
valve, electronic expansion valve, or
other type of metering device; the
duration of the compressor break-in
period, if used; the C value used to
represent cooling mode cycling losses;
the temperatures at which the crankcase
heater with controls is designed to turn
on and designed to turn off for the
heating season, if applicable; the
duration of the crankcase heater time
delay for the shoulder season and
heating season, if such time delay is
employed; the maximum time between
defrosts as allowed by the controls (in
hours); whether an inlet plenum was
installed during testing; and
(i) For heat pumps, the C value used;
(ii) For multi-split, multiple-circuit,
and single-zone-multiple-coil systems,
the number of indoor units tested with
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the outdoor unit; the nominal cooling
capacity of each indoor unit and
outdoor unit in the combination; and
the indoor units that are not providing
heating or cooling for part-load tests;
(iii) For ducted systems having
multiple indoor fans within a single
indoor unit, the number of indoor fans;
the nominal cooling capacity of the
indoor unit and outdoor unit; which
fan(s) are operating to attain the fullload air volume rate when controls limit
the simultaneous operation of all fans
within the single indoor unit; and the
allocation of the full-load air volume
rate to each operational fan when
different capacity blowers are connected
to the common duct;
(iv) For models tested with an indoor
blower installed, the airflow-control
settings associated with full load
cooling operation; and the airflowcontrol settings or alternative
instructions for setting fan speed to the
speed upon which the rating is based;
(v) For models with time-adaptive
defrost control, the frosting interval to
be used during Frost Accumulation tests
and the procedure for manually
initiating the defrost at the specified
time;
(vi) For models of indoor units
designed for both horizontal and
vertical installation or for both up-flow
and down-flow vertical installations, the
orientation used for testing;
(vii) For variable speed units, the
compressor frequency set points, and
the required dip switch/control settings
for step or variable components; and
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3
(viii) For variable speed heat pumps,
whether the unit controls restrict use of
minimum compressor speed operation
for some range of operating ambient
conditions, whether the unit controls
restrict use of maximum compressor
speed operation for any ambient
temperatures below 17 °F, and whether
the optional H42 low temperature test
was used to characterize performance at
temperatures below 17 °F.
(d) Alternative efficiency
determination methods. Alternative
methods for determining efficiency or
energy use for central air conditioners
and heat pumps can be found in
§ 429.70(e) of this subpart.
■ 4. Amend § 429.70 by revising
paragraph (e) to read as follows:
§ 429.70 Alternative methods for
determining energy efficiency or energy
use.
*
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*
*
(e) Alternate Efficiency Determination
Method (AEDM) for central air
conditioners and heat pumps. This
paragraph sets forth the requirements
for a manufacturer to use an AEDM to
rate central air conditioners and heat
pumps
(1) Criteria an AEDM must satisfy. A
manufacturer may not apply an AEDM
to an individual combination to
determine its certified ratings (SEER,
EER, HSPF, and/or PW,OFF) pursuant to
this section unless authorized pursuant
to § 429.16(a)(2) and:
(i) The AEDM is derived from a
mathematical model that estimates the
energy efficiency or energy
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consumption characteristics of the
individual combination (SEER, EER,
HSPF, and/or PW,OFF) as measured by
the applicable DOE test procedure; and
(ii) The manufacturer has validated
the AEDM in accordance with
paragraph (e)(2) of this section and
using individual combinations that meet
the current Federal energy conservation
standards.
(2) Validation of an AEDM. Before
using an AEDM, the manufacturer must
validate the AEDM’s accuracy and
reliability as follows:
(i) The manufacturer must complete
testing of each basic model as required
under § 429.16(a)(1)(ii). Using the
AEDM, calculate the energy use or
efficiency for each of the tested
individual combinations within each
basic model. Compare the rating based
on testing and the AEDM energy use or
efficiency output according to paragraph
(e)(2)(ii) of this section. The
manufacturer is responsible for ensuring
the accuracy and reliability of the
AEDM.
(ii) Individual combination
tolerances. This paragraph provides the
tolerances applicable to individual
combinations rated using an AEDM.
(A) For an energy-efficiency metric,
the predicted efficiency for each
individual combination calculated by
applying the AEDM may not be more
than three percent greater than the
efficiency determined from the
corresponding test of the combination.
(B) For an energy-consumption
metric, the predicted energy
consumption for each individual
combination, calculated by applying the
AEDM, may not be more than three
percent less than the energy
consumption determined from the
corresponding test of the combination.
(C) The predicted energy efficiency or
consumption for each individual
combination calculated by applying the
AEDM must meet or exceed the
applicable federal energy conservation
standard.
(iii) Additional test unit requirements.
Each test must have been performed in
accordance with the DOE test procedure
applicable at the time the individual
combination being rated with the AEDM
is distributed in commerce.
(3) AEDM records retention
requirements. If a manufacturer has
used an AEDM to determine
representative values pursuant to this
section, the manufacturer must have
available upon request for inspection by
the Department records showing:
(i) The AEDM, including the
mathematical model, the engineering or
statistical analysis, and/or computer
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simulation or modeling that is the basis
of the AEDM;
(ii) Product information, complete test
data, AEDM calculations, and the
statistical comparisons from the units
tested that were used to validate the
AEDM pursuant to paragraph (e)(2) of
this section; and
(iii) Product information and AEDM
calculations for each individual
combination certified using the AEDM.
(4) Additional AEDM requirements. If
requested by the Department and at
DOE’s discretion, the manufacturer
must perform at least one of the
following:
(i) Conduct simulations before
representatives of the Department to
predict the performance of particular
individual combinations; or
(ii) Provide analyses of previous
simulations conducted by the
manufacturer; or
(iii) Conduct certification testing of
individual combinations selected by the
Department.
(5) AEDM verification testing. DOE
may use the test data for a given
individual combination generated
pursuant to § 429.104 to verify the
certified rating determined by an AEDM
as long as the following process is
followed:
(i) Selection of units. DOE will obtain
one or more units for test from retail, if
available. If units cannot be obtained
from retail, DOE will request that a unit
be provided by the manufacturer;
(ii) Lab requirements. DOE will
conduct testing at an independent,
third-party testing facility of its
choosing. In cases where no third-party
laboratory is capable of testing the
equipment, testing may be conducted at
a manufacturer’s facility upon DOE’s
request.
(iii) Testing. At no time during
verification testing may the lab and the
manufacturer communicate without
DOE authorization. If during test set-up
or testing, the lab indicates to DOE that
it needs additional information
regarding a given individual
combination in order to test in
accordance with the applicable DOE test
procedure, DOE may organize a meeting
between DOE, the manufacturer and the
lab to provide such information.
(iv) Failure to meet certified rating. If
an individual combination tests worse
than its certified rating (i.e., lower than
the certified efficiency rating or higher
than the certified consumption rating)
by more than 5%, or the test results in
a different cooling capacity than its
certified cooling capacity by more than
5%, DOE will notify the manufacturer.
DOE will provide the manufacturer with
all documentation related to the test set
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up, test conditions, and test results for
the unit. Within the timeframe allotted
by DOE, the manufacturer:
(A) May present any and all claims
regarding testing validity; and
(B) If not on site for the initial test setup, must test at least one additional unit
of the same combination obtained from
a retail source at its own expense,
following the test requirements in
§ 429.110(a)(3). When testing at an
independent lab, the manufacturer may
choose to have DOE and the
manufacturer present.
(v) Tolerances. This subparagraph
specifies the tolerances DOE will permit
when conducting verification testing.
(A) For consumption metrics, the
result from a DOE verification test must
be less than or equal to 1.05 multiplied
by the certified rating.
(B) For efficiency metrics, the result
from a DOE verification test must be
greater than or equal to 1.05 multiplied
by the certified rating.
(vi) Invalid rating. If, following
discussions with the manufacturer and
a retest where applicable, DOE
determines that the verification testing
was conducted appropriately in
accordance with the DOE test
procedure, DOE will issue a
determination that the ratings for the
basic model are invalid. The
manufacturer must conduct additional
testing and re-rate and re-certify the
individual combinations within the
basic model that were rated using the
AEDM based on all test data collected,
including DOE’s test data.
(vii) AEDM use. This subparagraph
specifies when a manufacturer’s use of
an AEDM may be restricted due to prior
invalid ratings.
(A) If DOE has determined that a
manufacturer made invalid ratings on
individual combinations within two or
more basic models rated using the
manufacturer’s AEDM within a 24
month period, the manufacturer must
test the least efficient and most efficient
combination within each basic model in
addition to the combination specified in
§ 429.16(a)(1)(ii). The twenty-four
month period begins with a DOE
determination that a rating is invalid
through the process outlined above.
(B) If DOE has determined that a
manufacturer made invalid ratings on
more than four basic models rated using
the manufacturer’s AEDM within a 24month period, the manufacturer may no
longer use an AEDM.
(C) If a manufacturer has lost the
privilege of using an AEDM, the
manufacturer may regain the ability to
use an AEDM by:
(1) Investigating and identifying
cause(s) for failures;
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(2) Taking corrective action to address
cause(s);
(3) Performing six new tests per basic
model, a minimum of two of which
must be performed by an independent,
third-party laboratory from units
obtained from retail to validate the
AEDM; and
(4) Obtaining DOE authorization to
resume use of an AEDM.
*
*
*
*
*
■ 5. Amend § 429.134 by adding
paragraph (g) to read as follows:
(B) For all other cases, the certified C
or C value will be used as the basis for
calculation of SEER or HSPF for the
basic model/individual combination.
(ii) For models of outdoor units with
no match, or for tests in which the
criteria for the cyclic test in 10 CFR part
430, subpart B, Appendix M or M1, as
applicable, section 3.5e, cannot be
achieved, DOE will use the default C
and/or C value pursuant to 10 CFR part
430.
§ 429.134 Product-specific enforcement
provisions.
PART 430—ENERGY CONSERVATION
PROGRAM FOR CONSUMER
PRODUCTS
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(g) Central air conditioners and heat
pumps.—(1) Verification of cooling
capacity. The cooling capacity of each
tested unit of the basic model (for single
package systems) or individual
combination (for split-systems) will be
measured pursuant to the test
requirements of § 430.23(m). The results
of the measurement(s) will be compared
to the value of cooling capacity certified
by the manufacturer.
(i) If the measurement(s) (either the
measured cooling capacity for a single
unit sample or the average of the
measured cooling capacities for a
multiple unit sample) is less than or
equal to 1.05 multiplied by the certified
cooling capacity and greater than or
equal to 0.95 multiplied by the certified
cooling capacity, the certified cooling
capacity will be used as the basis for
determining SEER.
(ii) Otherwise, the measurement(s)
(either the measured cooling capacity
for a single unit sample or the average
of the measured cooling capacities for a
multiple unit sample, as applicable) will
be used as the basis for determining
SEER.
(2) Verification of CD value—(i) For
central air conditioners and heat pumps
other than models of outdoor units with
no match, the C and/or C value of the
basic model (for single package systems)
or individual combination (for splitsystems), as applicable, will be
measured pursuant to the test
requirements of § 430.23(m) for each
unit tested. The results of the
measurement(s) for each C or C value
will be compared to the C or C value
certified by the manufacturer.
(A) If the results of the
measurement(s) (either the measured
value for a single unit sample or the
average of the measured values for a
multiple unit sample) is 0.02 or more
greater than the certified C or C value,
the average measured C or C value
will serve as the basis for calculation of
SEER or HSPF for the basic model/
individual combination.
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6. The authority citation for part 430
continues to read as follows:
■
Authority: 42 U.S.C. 6291–6309; 28 U.S.C.
2461 note.
7. Section 430.2 is amended by:
a. Removing the definitions of ‘‘ARM/
simulation adjustment factor,’’ ‘‘coil
family,’’ ‘‘condenser-evaporator coil
combination’’, ‘‘condensing unit,’’
‘‘evaporator coil’’, ‘‘heat pump,’’
‘‘indoor unit,’’ ‘‘outdoor unit,’’ ‘‘small
duct, high velocity system,’’ and ‘‘tested
combination;’’ and
■ b. Revising the definitions of ‘‘basic
model;’’ and ‘‘central air conditioner’’ to
read as follows:
■
■
§ 430.2
Definitions.
*
*
*
*
*
Basic model means all units of a given
type of covered product (or class
thereof) manufactured by one
manufacturer; having the same primary
energy source; and, which have
essentially identical electrical, physical,
and functional (or hydraulic)
characteristics that affect energy
consumption, energy efficiency, water
consumption, or water efficiency; and
(1) With respect to general service
fluorescent lamps, general service
incandescent lamps, and incandescent
reflector lamps: Lamps that have
essentially identical light output and
electrical characteristics—including
lumens per watt (lm/W) and color
rendering index (CRI).
(2) With respect to faucets and
showerheads: Have the identical flow
control mechanism attached to or
installed within the fixture fittings, or
the identical water-passage design
features that use the same path of water
in the highest flow mode.
(3) With respect to furnace fans: Are
marketed and/or designed to be
installed in the same type of
installation; and
(4) With respect to central air
conditioners and central air
conditioning heat pumps:
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(i) Essentially identical electrical,
physical, and functional (or hydraulic)
characteristics means:
(A) For split-systems manufactured by
independent coil manufacturers (ICMs)
and for small-duct, high velocity
systems: All individual combinations
having the same model of indoor unit,
which means the same or comparably
performing indoor coil(s) [same face
area; fin material, depth, style (e.g.,
wavy, louvered), and density (fins per
inch); tube pattern, material, diameter,
wall thickness, and internal
enhancement], indoor blower(s) [same
air flow with the same indoor coil and
external static pressure, same power
input], auxiliary refrigeration system
components if present (e.g., expansion
valve), and controls.
(B) for split-systems manufactured by
outdoor unit manufacturers (OUMs): All
individual combinations having the
same model of outdoor unit, which
means the same or comparably
performing compressor(s) [same
displacement rate (volume per time) and
same capacity and power input when
tested under the same operating
conditions], outdoor coil(s) [same face
area; fin material, depth, style (e.g.,
wavy, louvered), and density (fins per
inch); tube pattern, material, diameter,
wall thickness, and internal
enhancement], outdoor fan(s) [same air
flow with the same outdoor coil, same
power input], auxiliary refrigeration
system components if present (e.g.,
suction accumulator, reversing valve,
expansion valve), and controls.
(C) for single-package models: All
individual models having the same or
comparably performing compressor(s)
[same displacement rate (volume per
time) and same capacity and power
input when tested under the same
operating conditions], outdoor coil(s)
and indoor coil(s) [same face area; fin
material, depth, style (e.g., wavy,
louvered), and density (fins per inch);
tube pattern, material, diameter, wall
thickness, and internal enhancement],
outdoor fan(s) [same air flow with the
same outdoor coil, same power input],
indoor blower(s) [same air flow with the
same indoor coil and external static
pressure, same power input], auxiliary
refrigeration system components if
present (e.g. suction accumulator,
reversing valve, expansion valve), and
controls.
(ii) For single-split-system and singlepackage models, manufacturers may
instead choose to make each individual
combination or model its own basic
model provided the testing and rating
requirements in 10 CFR 429.16 are met.
(iii) For multi-split, multi-circuit, and
single-zone-multiple-coil models, a
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basic model may not include both
individual SDHV combinations and
non-SDHV combinations even when
they include the same model of outdoor
unit. The manufacturer may choose to
identify specific individual
combinations as additional basic
models.
*
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Central air conditioner or central air
conditioning heat pump means a
product, other than a packaged terminal
air conditioner or packaged terminal
heat pump, which is powered by single
phase electric current, air cooled, rated
below 65,000 Btu per hour, not
contained within the same cabinet as a
furnace, the rated capacity of which is
above 225,000 Btu per hour, and is a
heat pump or a cooling unit only. A
central air conditioner or central air
conditioning heat pump may consist of:
A single-package unit; an outdoor unit
and one or more indoor units; an indoor
unit only; or an outdoor unit only. In
the case of an indoor unit only or an
outdoor unity only, the unit must be
tested and rated as a system
(combination of both an indoor and an
outdoor unit). For all central air
conditioner and central air conditioning
heat pump-related definitions, see
appendices M or M1 of subpart B of this
part.
■ 8. Section 430.3 is amended by:
■ a. Revising paragraphs (c)(1) and
(g)(2);
■ b. Adding paragraphs (c)(3) and (c)(4);
■ c. Removing paragraphs (g)(3);
■ d. Redesignating paragraphs (g)(4)
through (g)(14) as (g)(3) through (g)(13);
and
■ e. Revising newly redesignated (g)(3)
through (g)(9).
The revisions and additions read as
follows:
§ 430.3 Materials incorporated by
reference.
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(c) * * *
(1) AHRI 210/240–2008 with
Addendums 1 and 2 (formerly ARI
Standard 210/240), Performance Rating
of Unitary Air-Conditioning & AirSource Heat Pump Equipment, sections
6.1.3.2, 6.1.3.4, 6.1.3.5 and figures D1,
D2, D4, approved by ANSI December,
2012, IBR approved for appendix M and
M1 to subpart B.
*
*
*
*
*
(3) ANSI/AHRI 1230–2010 with
Addendum 2, Performance Rating of
Variable Refrigerant Flow Multi-Split
Air-Conditioning and Heat Pump
Equipment, sections 3 (except 3.8, 3.9,
3.13, 3.14, 3.15, 3.16, 3.23, 3.24, 3.26,
3.27, 3.28, 3.29, 3.30, and 3.31), 5.1.3,
5.1.4, 6.1.5 (except Table 8), 6.1.6, and
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6.2, approved August 2, 2010,
Addendum 2 dated June 2014, IBR
approved for appendices M and M1 to
subpart B.
(4) AHRI 210/240-Draft, Performance
Rating of Unitary Air-Conditioning &
Air-Source Heat Pump Equipment,
appendix E, section E4, Docket No.
EERE–2009–BT–TP–0004 No. 45.
*
*
*
*
*
(g) * * *
(2) ASHRAE 23.1–2010, Methods of
Testing for Rating the Performance of
Positive Displacement Refrigerant
Compressors and Condensing Units that
Operate at Subcritical Temperatures of
the Refrigerant, sections 5, 6, 7, and 8
only, approved January 28, 2010, IBR
approved for appendices M and M1 to
subpart B.
(3) ASHRAE 37–2009, Methods of
Testing for Rating Electrically Driven
Unitary Air-Conditioning and Heat
Pump Equipment, approved June 25,
2009, IBR approved for appendix AA
subpart to B. Sections 5.1.1, 5.2, 5.5.1,
6.1.1, 6.1.2, 6.1.4, 6.4, 6.5, 7.3, 7.4, 7.5,
7.7.2.1, 7.7.2.2, 8.1.2, 8.1.3, 8.2, 8.6.2;
figures 1, 2, 4, 7a, 7b, 7c, 8; and table
3 only IBR approved for appendices M
and M1 to subpart B.
*
*
*
*
*
(4) ASHRAE 41.1–1986 (Reaffirmed
2006), Standard Method for
Temperature Measurement, approved
February 18, 1987, IBR approved for
appendices E and AA to subpart B.
(5) ASHRAE 41.1–2013, Standard
Method for Temperature Measurement,
approved January 30, 2013, IBR
approved for appendix X1 to subpart B.
Sections 4, 5, 6, 7.2, and 7.3 only, IBR
approved for appendices M and M1 to
subpart B.
(6) ASHRAE 41.2–1987 (Reaffirmed
1992), Standard Methods for Laboratory
Airflow Measurement, section 5.2.2 and
figure 14, approved October 1, 1987, IBR
approved for appendices M and M1 to
subpart B.
(7) ASHRAE 41.6–2014, Standard
Method for Humidity Measurement,
sections 4, 5, 6, and 7.1, approved July
3, 2014, sections 4, 5, 6, and 7 only IBR
approved for appendices M and M1 to
subpart B.
(8) ASHRAE 41.9–2011, Standard
Methods for Volatile-Refrigerant Mass
Flow Measurements Using Calorimeters,
approved February 3, 2011, sections 5,
6, 7, 8, 9, and 11 only IBR approved for
appendices M and M1 to subpart B.
(9) ASHRAE/AMCA 51–07/210–07,
Laboratory Methods of Testing Fans for
Certified Aerodynamic Performance
Rating, figures 2A and 12, approved
August 17, 2007, IBR approved for
appendices M and M1 to subpart B.
*
*
*
*
*
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9. Section 430.23 is amended by
revising paragraph (m) to read as
follows:
■
§ 430.23 Test procedures for the
measurement of energy and water
consumption.
*
*
*
*
*
(m) Central air conditioners and heat
pumps. See the note at the beginning of
appendix M and M1 to determine the
appropriate test method. All values
discussed in this section must be
determined using a single appendix.
(1) Cooling capacity must be
determined from the steady-state wetcoil test (A or A2 Test), as described in
section 3.2 of appendix M or M1 to this
subpart, and rounded off to the nearest
(i) to the nearest 50 Btu/h if cooling
capacity is less than 20,000 Btu/h, (ii) to
the nearest 100 Btu/h if cooling capacity
is greater than or equal to 20,000 Btu/
h but less than 38,000 Btu/h, and (iii)
to the nearest 250 Btu/h if cooling
capacity is greater than or equal to
38,000 Btu/h and less than 65,000 Btu/
h.
(2) Seasonal energy efficiency ratio
(SEER) must be determined from section
4.1 of appendix M or M1 to this subpart,
and rounded off to the nearest 0.025
Btu/W-h.
(3) When representations are made of
energy efficiency ratio (EER), EER must
be determined in section 4.7 of
appendix M or M1 to this subpart, and
rounded off to the nearest 0.025 Btu/Wh.
(4) Heating seasonal performance
factors (HSPF) must be determined in
section 4.2 of appendix M or M1 to this
subpart, and rounded off to the nearest
0.025 Btu/W-h.
(5) Average off mode power
consumption must be determined
according to section 4.3 of appendix M
or M1 to this subpart, and rounded off
to the nearest 0.5 W.
(6) Sensible heat ratio (SHR) must be
determined according to section 4.6 of
appendix M or M1 to this subpart, and
rounded off to the nearest 0.5 percent
(%).
(7) All other measures of energy
efficiency or consumption or other
useful measures of performance must be
determined using appendix M or M1 of
this subpart.
*
*
*
*
*
■ 10. Revise appendix M to subpart B of
part 430 to read as follows:
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Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
APPENDIX M TO SUBPART B OF
PART 430—UNIFORM TEST METHOD
FOR MEASURING THE ENERGY
CONSUMPTION OF CENTRAL AIR
CONDITIONERS AND HEAT PUMPS
Note: Prior to May 9, 2016, any
representations, including compliance
certifications, made with respect to the
energy use, power, or efficiency of central air
conditioners and central air conditioning
heat pumps must be based on the results of
testing pursuant to either this appendix or
the procedures in Appendix M as it appeared
at 10 CFR part 430, subpart B, Appendix M,
in the 10 CFR parts 200 to 499 edition
revised as of January 1, 2015. Any
representations made with respect to the
energy use or efficiency of such central air
conditioners and central air conditioning
heat pumps must be in accordance with
whichever version is selected.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
On or after May 9, 2016 and prior to
the compliance date for any amended
energy conservation standards, any
representations, including compliance
certifications, made with respect to the
energy use, power, or efficiency of
central air conditioners and central air
conditioning heat pumps must be based
on the results of testing pursuant to this
appendix.
On or after the compliance date for
any amended energy conservation
standards, any representations,
including compliance certifications,
made with respect to the energy use,
power, or efficiency of central air
conditioners and central air
conditioning heat pumps must be based
on the results of testing pursuant to
appendix M1 of this subpart.
1. Scope and Definitions
1.1 Scope.
This test procedure provides a method of
determining SEER, EER, HSPF and PW,OFF for
central air conditioners and central air
conditioning heat pumps including the
following categories:
(a) Split-system air conditioners; and
single-zone-multiple-coil, multi-split
(including VRF), and multi-circuit systems
(b) Split-system heat pumps and singlezone-multiple-coil, multi-split (including
VRF), and multi-circuit systems
(c) Single-package air conditioners
(d) Single-package heat pumps
(e) Small-duct, high-velocity systems
(including VRF)
(f) Space-constrained products—air
conditioners
(g) Space-constrained products—heat
pumps
For purposes of this appendix, the
Department of Energy incorporates by
reference specific sections of several industry
standards, as listed in § 430.3. In cases where
there is a conflict, the language of the test
procedure in this appendix takes precedence
over the incorporated standards.
All section references refer to sections
within this appendix unless otherwise stated.
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1.2 Definitions.
Airflow-control settings are programmed or
wired control system configurations that
control a fan to achieve discrete, differing
ranges of airflow—often designated for
performing a specific function (e.g., cooling,
heating, or constant circulation)—without
manual adjustment other than interaction
with a user-operable control (i.e., a
thermostat) that meets the manufacturer
specifications for installed-use. For the
purposes of this appendix, manufacturer
specifications for installed-use are those
found in the product literature shipped with
the unit.
Airflow prevention device denotes a
device(s) that prevents airflow via natural
convection by mechanical means, such as an
air damper box, or by means of changes in
duct height, such as an upturned duct.
Annual performance factor means the total
heating and cooling done by a heat pump in
a particular region in one year divided by the
total electric energy used in one year.
Blower coil indoor unit means the indoor
unit of a split-system central air conditioner
or heat pump that includes a refrigerant-toair heat exchanger coil, may include a
cooling-mode expansion device, and
includes either an indoor blower housed
with the coil or a separate designated air
mover such as a furnace or a modular blower
(as defined in Appendix AA to the subpart).
Blower coil system refers to a split-system
that includes one or more blower coil indoor
units.
CFR means Code of Federal Regulations.
Coefficient of Performance (COP) means
the ratio of the average rate of space heating
delivered to the average rate of electrical
energy consumed by the heat pump. These
rate quantities must be determined from a
single test or, if derived via interpolation,
must be determined at a single set of
operating conditions. COP is a dimensionless
quantity. When determined for a ducted unit
tested without an indoor blower installed,
COP must include the section 3.7 and 3.9.1
default values for the heat output and power
input of a fan motor.
Coil-only indoor unit means the indoor
unit of a split-system central air conditioner
or heat pump that includes a refrigerant-toair heat exchanger coil and may include a
cooling-mode expansion device, but does not
include an indoor blower housed with the
coil, and does not include a separate
designated air mover such as a furnace or a
modular blower (as defined in Appendix AA
to this subpart. A coil-only indoor unit is
designed to use a separately-installed furnace
or a modular blower for indoor air
movement. Coil-only system refers to a
system that includes one or more coil-only
indoor units.
Condensing unit removes the heat absorbed
by the refrigerant to transfer it to the outside
environment, and which consists of an
outdoor coil, compressor(s), and air moving
device.
Constant-air-volume-rate indoor blower
means a fan that varies its operating speed to
provide a fixed air-volume-rate from a ducted
system.
Continuously recorded, when referring to a
dry bulb measurement, dry bulb temperature
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used for test room control, wet bulb
temperature, dew point temperature, or
relative humidity measurements, means that
the specified value must be sampled at
regular intervals that are equal to or less than
5 seconds
Cooling load factor (CLF) means the ratio
having as its numerator the total cooling
delivered during a cyclic operating interval
consisting of one ON period and one OFF
period. The denominator is the total cooling
that would be delivered, given the same
ambient conditions, had the unit operated
continuously at its steady-state, spacecooling capacity for the same total time (ON
+ OFF) interval.
Crankcase heater means any electrically
powered device or mechanism for
intentionally generating heat within and/or
around the compressor sump volume often
done to minimize the dilution of the
compressor’s refrigerant oil by condensed
refrigerant. Crankcase heater control may be
achieved using a timer or may be based on
a change in temperature or some other
measurable parameter, such that the
crankcase heater is not required to operate
continuously. A crankcase heater without
controls operates continuously when the
compressor is not operating.
Cyclic Test means a test where the unit’s
compressor is cycled on and off for specific
time intervals. A cyclic test provides half the
information needed to calculate a
degradation coefficient.
Damper box means a short section of duct
having an air damper that meets the
performance requirements of section 2.5.7.
Degradation coefficient (CD) means a
parameter used in calculating the part load
factor. The degradation coefficient for cooling
is denoted by CDc. The degradation
coefficient for heating is denoted by CDh.
Demand-defrost control system means a
system that defrosts the heat pump outdoor
coil only when measuring a predetermined
degradation of performance. The heat pump’s
controls monitor one or more parameters that
always vary with the amount of frost
accumulated on the outdoor coil (e.g., coil to
air differential temperature, coil differential
air pressure, outdoor fan power or current,
optical sensors) at least once for every ten
minutes of compressor ON-time when space
heating. One acceptable alternative to the
criterion given in the prior sentence is a
feedback system that measures the length of
the defrost period and adjusts defrost
frequency accordingly. In all cases, when the
frost parameter(s) reaches a predetermined
value, the system initiates a defrost. In a
demand-defrost control system, defrosts are
terminated based on monitoring a
parameter(s) that indicates that frost has been
eliminated from the coil. (Note: Systems that
vary defrost intervals according to outdoor
dry-bulb temperature are not demand-defrost
systems.) A demand-defrost control system,
which otherwise meets the above
requirements, may allow time-initiated
defrosts if, and only if, such defrosts occur
after 6 hours of compressor operating time.
Design heating requirement (DHR) predicts
the space heating load of a residence when
subjected to outdoor design conditions.
Estimates for the minimum and maximum
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DHR are provided for six generalized U.S.
climatic regions in section 4.2.
Dry-coil tests are cooling mode tests where
the wet-bulb temperature of the air supplied
to the indoor coil is maintained low enough
that no condensate forms on this coil.
Ducted system means an air conditioner or
heat pump that is designed to be
permanently installed equipment and
delivers conditioned air to the indoor space
through a duct(s). The air conditioner or heat
pump may be either a split-system or a
single-package unit.
Energy efficiency ratio (EER) means the
ratio of the average rate of space cooling
delivered to the average rate of electrical
energy consumed by the air conditioner or
heat pump. These rate quantities must be
determined from a single test or, if derived
via interpolation, must be determined at a
single set of operating conditions. EER is
expressed in units of
When determined for a ducted unit tested
without an indoor blower installed, EER
must include the section 3.3 and 3.5.1 default
values for the heat output and power input
of a fan motor.
Evaporator coil absorbs heat from an
enclosed space and transfers the heat to a
refrigerant.
Heat pump means a kind of central air
conditioner, which consists of one or more
assemblies, utilizing an indoor conditioning
coil, compressor, and refrigerant-to-outdoor
air heat exchanger to provide air heating, and
may also provide air cooling, air
dehumidifying, air humidifying, air
circulating, and air cleaning.
Heat pump having a heat comfort
controller means equipment that regulates
the operation of the electric resistance
elements to assure that the air temperature
leaving the indoor section does not fall below
a specified temperature. This specified
temperature is usually field adjustable. Heat
pumps that actively regulate the rate of
electric resistance heating when operating
below the balance point (as the result of a
second stage call from the thermostat) but do
not operate to maintain a minimum delivery
temperature are not considered as having a
heat comfort controller.
Heating load factor (HLF) means the ratio
having as its numerator the total heating
delivered during a cyclic operating interval
consisting of one ON period and one OFF
period. The denominator is the total heating
that would be delivered, given the same
ambient conditions, if the unit operated
continuously at its steady-state space heating
capacity for the same total time (ON plus
OFF) interval.
Heating season means the months of the
year that require heating, e.g., typically, and
roughly, October through April.
Heating seasonal performance factor
(HSPF) means the total space heating
required during the space heating season,
expressed in Btu’s, divided by the total
electrical energy consumed by the heat pump
system during the same season, expressed in
watt-hours. The HSPF used to evaluate
compliance with the Energy Conservation
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Standards (see 10 CFR 430.32(c)) is based on
Region IV, the minimum standardized design
heating requirement, and the sampling plan
stated in 10 CFR 429.16(a).
Independent coil manufacturer (ICM)
means a manufacturer that manufactures
indoor units but does not manufacture singlepackage units or outdoor units.
Indoor unit transfers heat between the
refrigerant and the indoor air and consists of
an indoor coil and casing and may include
a cooling mode expansion device and/or an
air moving device.
Multiple-circuit (or multi-circuit) system
means a split system that has one outdoor
unit and that has two or more indoor units
installed on two or more refrigeration circuits
such that each refrigeration circuit serves a
compressor and one and only one indoor
unit, and refrigerant is not shared from
circuit to circuit.
Multiple-split (or multi-split) system means
a split system that has one outdoor unit and
two or more indoor coil-only or indoor
blower coil units connected to its other
component(s) with a single refrigerant
circuit. The indoor units operate
independently and can condition multiple
zones in response to at least two indoor
thermostats or temperature sensors. The
outdoor unit operates in response to
independent operation of the indoor units
based on control input of multiple indoor
thermostats or temperature sensors, and/or
based on refrigeration circuit sensor input
(e.g., suction pressure).
Nominal capacity means the capacity that
is claimed by the manufacturer in the
product name plate. Nominal cooling
capacity is approximate to the air conditioner
cooling capacity tested at A or A2 condition.
Nominal heating capacity is approximate to
the heat pump heating capacity tested in H12
test (or the optional H1N test).
Non-ducted system means a split-system
central air conditioner or heat pump that is
designed to be permanently installed and
that directly heats or cools air within the
conditioned space using one or more indoor
units that are mounted on room walls and/
or ceilings. The system may be of a modular
design that allows for combining multiple
outdoor coils and compressors to create one
overall system.
Normalized Gross Indoor Fin Surface
(NGIFS) means the gross fin surface area of
the indoor unit coil divided by the cooling
capacity measured for the A or A2 Test
whichever applies.
Off-mode power consumption means the
power consumption when the unit is
connected to its main power source but is
neither providing cooling nor heating to the
building it serves.
Off-mode season means, for central air
conditioners, the shoulder season and the
entire heating season; and for heat pumps,
the shoulder season only.
Outdoor unit transfers heat between the
refrigerant and the outdoor air, and consists
of an outdoor coil, compressor(s), an air
moving device, and in addition for heat
pumps, could include a heating mode
expansion device, reversing valve, and
defrost controls.
Outdoor unit manufacturer (OUM) means
a manufacturer of single-package units,
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outdoor units, and/or both indoor units and
outdoor units.
Part-load factor (PLF) means the ratio of
the cyclic energy efficiency ratio (coefficient
of performance) to the steady-state energy
efficiency ratio (coefficient of performance),
where both energy efficiency ratios
(coefficients of performance) are determined
based on operation at the same ambient
conditions.
Seasonal energy efficiency ratio (SEER)
means the total heat removed from the
conditioned space during the annual cooling
season, expressed in Btu’s, divided by the
total electrical energy consumed by the
central air conditioner or heat pump during
the same season, expressed in watt-hours.
Short ducted system means a ducted split
system whose one or more indoor sections
produce greater than zero but no greater than
0.1 inches (of water) of external static
pressure when operated at the full-load air
volume not exceeding 450 cfm per rated ton
of cooling.
Shoulder season means the months of the
year in between those months that require
cooling and those months that require
heating, e.g., typically, and roughly, April
through May, and September through
October.
Single-package unit means any central air
conditioner or heat pump that has all major
assemblies enclosed in one cabinet.
Single-split-system means a split system
that has one outdoor unit and that has one
indoor coil-only or indoor blower coil unit
connected to its other component(s) with a
single refrigeration circuit.
Single-zone-multiple-coil split system
means a split system that has one outdoor
unit and that has two or more indoor units
connected with a single refrigeration circuit.
The indoor units operate in unison in
response to a single indoor thermostat.
Small-duct, high-velocity system means a
system that contains a blower and indoor coil
combination that is designed for, and
produces, at least 1.2 inches (of water) of
external static pressure when operated at the
full-load air volume rate of 220–350 cfm per
rated ton of cooling. When applied in the
field, uses high-velocity room outlets (i.e.,
generally greater than 1000 fpm) having less
than 6.0 square inches of free area.
Split system means any air conditioner or
heat pump that has one or more of the major
assemblies separated from the others. Splitsystems may be either blower coil systems or
coil-only systems.
Standard Air means dry air having a mass
density of 0.075 lb/ft3.
Steady-state test means a test where the
test conditions are regulated to remain as
constant as possible while the unit operates
continuously in the same mode.
Temperature bin means the 5 °F
increments that are used to partition the
outdoor dry-bulb temperature ranges of the
cooling (≥65 °F) and heating (<65 °F) seasons.
Test condition tolerance means the
maximum permissible difference between the
average value of the measured test parameter
and the specified test condition.
Test operating tolerance means the
maximum permissible range that a
measurement may vary over the specified test
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interval. The difference between the
maximum and minimum sampled values
must be less than or equal to the specified
test operating tolerance.
Tested combination means a single-zonemultiple-coil, multi-split, or multi-circuit
system having the following features:
(1) The system consists of one outdoor unit
with one or more compressors matched with
between two and five indoor units;
(2) The indoor units shall:
(i) Collectively, have a nominal cooling
capacity greater than or equal to 95 percent
and less than or equal to 105 percent of the
nominal cooling capacity of the outdoor unit;
(ii) Represent the highest sales volume
model family that can meet the 95 percent
nominal cooling capacity of the outdoor unit
[Note: another indoor model family may be
used if five indoor units from the highest
sales volume model family do not provide
sufficient capacity to meet the 95 percent
threshold level].
(iii) Individually not have a nominal
cooling capacity greater than 50 percent of
the nominal cooling capacity of the outdoor
unit, unless the nominal cooling capacity of
the outdoor unit is 24,000 Btu/h or less;
(iv) Operate at fan speeds consistent with
manufacturer’s specifications; and
(v) All be subject to the same minimum
external static pressure requirement while
able to produce the same external static
pressure at the exit of each outlet plenum
when connected in a manifold configuration
as required by the test procedure.
(vi) Where referenced, ‘‘nominal cooling
capacity’’ is to be interpreted for indoor units
as the highest cooling capacity listed in
published product literature for 95 °F
outdoor dry bulb temperature and 80 °F dry
bulb, 67 °F wet bulb indoor conditions, and
for outdoor units as the lowest cooling
capacity listed in published product
literature for these conditions. If incomplete
or no operating conditions are reported, the
highest (for indoor units) or lowest (for
outdoor units) such cooing capacity shall be
used.
Time-adaptive defrost control system is a
demand-defrost control system that measures
the length of the prior defrost period(s) and
uses that information to automatically
determine when to initiate the next defrost
cycle.
Time-temperature defrost control systems
initiate or evaluate initiating a defrost cycle
only when a predetermined cumulative
compressor ON-time is obtained. This
predetermined ON-time is generally a fixed
value (e.g., 30, 45, 90 minutes) although it
may vary based on the measured outdoor
dry-bulb temperature. The ON-time counter
accumulates if controller measurements (e.g.,
outdoor temperature, evaporator
temperature) indicate that frost formation
conditions are present, and it is reset/remains
at zero at all other times. In one application
of the control scheme, a defrost is initiated
whenever the counter time equals the
predetermined ON-time. The counter is reset
when the defrost cycle is completed.
In a second application of the control
scheme, one or more parameters are
measured (e.g., air and/or refrigerant
temperatures) at the predetermined,
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cumulative, compressor ON-time. A defrost
is initiated only if the measured parameter(s)
falls within a predetermined range. The ONtime counter is reset regardless of whether or
not a defrost is initiated. If systems of this
second type use cumulative ON-time
intervals of 10 minutes or less, then the heat
pump may qualify as having a demand
defrost control system (see definition).
Triple-capacity, northern heat pump
means a heat pump that provides two stages
of cooling and three stages of heating. The
two common stages for both the cooling and
heating modes are the low capacity stage and
the high capacity stage. The additional
heating mode stage is the booster capacity
stage, which offers the highest heating
capacity output for a given set of ambient
operating conditions.
Triple-split system means a central air
conditioner or heat pump that is composed
of three separate components: An outdoor fan
coil section, an indoor blower coil section,
and an indoor compressor section.
Two-capacity (or two-stage) compressor
system means a central air conditioner or
heat pump that has a compressor or a group
of compressors operating with only two
stages of capacity. For such systems, low
capacity means the compressor(s) operating
at low stage, or at low load test conditions.
The low compressor stage for heating mode
tests may be the same or different from the
cooling mode value.
For such systems, high capacity means the
compressor(s) operating at low stage, or at
full load test conditions.
Two-capacity, northern heat pump means
a heat pump that has a factory or fieldselectable lock-out feature to prevent space
cooling at high-capacity. Two-capacity heat
pumps having this feature will typically have
two sets of ratings, one with the feature
disabled and one with the feature enabled.
The certified indoor coil model number
should reflect whether the ratings pertain to
the lockout enabled option via the inclusion
of an extra identifier, such as ‘‘+LO’’. When
testing as a two-capacity, northern heat
pump, the lockout feature must remain
enabled for all tests.
Variable refrigerant flow (VRF) system
means a multi-split system with at least three
compressor capacity stages, distributing
refrigerant through a piping network to
multiple indoor blower coil units each
capable of individual zone temperature
control, through proprietary zone
temperature control devices and a common
communications network. Single-phase VRF
systems less than 65,000 Btu/h are a kind of
central air conditioners and central air
conditioning heat pumps.
Variable-speed compressor system means a
central air conditioner or heat pump that has
a compressor that uses a variable-speed drive
to vary the compressor speed to achieve
variable capacities.
For such a system, maximum speed means
the maximum operating speed, measured by
RPM or frequency (Hz), that the unit is
designed to operate in cooling mode or
heating mode. Maximum speed does not
change with ambient temperature, and it can
be different from cooling mode to heating
mode. Maximum speed does not necessarily
mean maximum capacity.
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For such systems, minimum speed means
the minimum speed, measured by RPM or
frequency (Hz), that the unit is designed to
operate in cooling mode or heating mode.
Minimum speed does not change with
ambient temperature, and it can be different
from cooling mode to heating mode.
Minimum speed does not necessarily mean
minimum capacity.
Wet-coil test means a test conducted at test
conditions that typically cause water vapor to
condense on the test unit evaporator coil.
2. Testing Overview and Conditions
(A) Test VRF systems using ANSI/AHRI
Standard 1230–2010 sections 3 (except 3.8,
3.9, 3.13, 3.14, 3.15, 3.16, 3.23, 3.24, 3.26,
3.27, 3.28, 3.29, 3.30, and 3.31), 5.1.3, 5.1.4,
6.1.5 (except Table 8), 6.1.6, and 6.2
(incorporated by reference, see § 430.3) and
Appendix M. Where ANSI/AHRI Standard
1230–2010 refers to the Appendix C therein
substitute the provisions of this appendix. In
cases where there is a conflict, the language
of the test procedure in this appendix takes
precedence over ANSI/AHRI Standard 1230–
2010.
For definitions use section 1 of Appendix
M and section 3 of ANSI/AHRI Standard
1230–2010, excluding sections 3.8, 3.9, 3.13,
3.14, 3.15, 3.16, 3.23, 3.24, 3.26, 3.27, 3.28,
3.29, 3.30, and 3.31. For rounding
requirements refer to § 430.23 (m). For
determination of certified rating
requirements refer to § 429.16.
For test room requirements, refer to section
2.1 from Appendix M. For test unit
installation requirements refer to sections
2.2.a, 2.2.b, 2.2.c, 2.2.1, 2.2.2, 2.2.3(a),
2.2.3(c), 2.2.4, 2.2.5, and 2.4 to 2.12 from
Appendix M, and sections 5.1.3 and 5.1.4 of
ANSI/AHRI Standard 1230–2010.
For general requirements for the test
procedure refer to section 3.1 of Appendix M,
except for sections 3.1.3 and 3.1.4, which are
requirements for indoor air volume and
outdoor air volume. For indoor air volume
and outdoor air volume requirements, refer
instead to section 6.1.5 (except Table 8) and
6.1.6 of ANSI/AHRI Standard 1230–2010. For
external static pressure requirements, refer to
Table 3 in Appendix M.
For the test procedure, refer to sections 3.3
to 3.5 and 3.7 to 3.13 in Appendix M. For
cooling mode and heating mode test
conditions, refer to section 6.2 of ANSI/AHRI
Standard 1230–2010. For calculations of
seasonal performance descriptors use section
4 of Appendix M.
(B) For systems other than VRF, only a
subset of the sections listed in this test
procedure apply when testing and rating a
particular unit. Table 1 shows the sections of
the test procedure that apply to each system.
This table is meant to assist manufacturers in
finding the appropriate sections of the test
procedure; the appendix sections rather than
the table provide the specific requirements
for testing, and given the varied nature of
available units, manufacturers are
responsible for determining which sections
apply to each unit tested. To use this table,
first refer to the sections listed under ‘‘all
units’’. Then refer to additional requirements
based on: (1) System configuration(s), (2) the
compressor staging or modulation capability,
and (3) any special features.
E:\FR\FM\09NOP2.SGM
09NOP2
69346
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
tkelley on DSK3SPTVN1PROD with PROPOSALS2
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BILLING CODE 6450–01–P
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Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
04:57 Nov 07, 2015
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Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
04:57 Nov 07, 2015
BILLING CODE 6450–01–C
VerDate Sep<11>2014
3.1.4.4.2c;
Two-capacity northem heat pump
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
† Use ANSI/AHRI Standard 1230–2010
with Addendum 2, with the sections
referenced in section 2(A) of this Appendix,
in conjunction with the sections set forth in
the table to perform test setup, testing, and
calculations for rating VRF multiple-split and
VRF SDHV systems.
NOTE: For all units, use section 3.13 for off
mode testing procedures and section 4.3 for
off mode calculations. For all units subject to
an EER standard, use section 4.7 to determine
the energy efficiency ratio.
2.1 Test room requirements.
a. Test using two side-by-side rooms, an
indoor test room and an outdoor test room.
For multiple-split, single-zone-multi-coil or
multi-circuit air conditioners and heat
pumps, however, use as many available
indoor test rooms as needed to accommodate
the total number of indoor units. These
rooms must comply with the requirements
specified in sections 8.1.2 and 8.1.3 of
ASHRAE Standard 37–2009 (incorporated by
reference, see § 430.3).
b. Inside these test rooms, use artificial
loads during cyclic tests and Frost
Accumulation tests, if needed, to produce
stabilized room air temperatures. For one
room, select an electric resistance heater(s)
having a heating capacity that is
approximately equal to the heating capacity
of the test unit’s condenser. For the second
room, select a heater(s) having a capacity that
is close to the sensible cooling capacity of the
test unit’s evaporator. When applied, cycle
the heater located in the same room as the
test unit evaporator coil ON and OFF when
the test unit cycles ON and OFF. Cycle the
heater located in the same room as the test
unit condensing coil ON and OFF when the
test unit cycles OFF and ON.
2.2 Test unit installation requirements.
a. Install the unit according to section 8.2
of ASHRAE Standard 37–2009 (incorporated
by reference, see § 430.3), subject to the
following additional requirements:
(1) When testing split systems, follow the
requirements given in section 6.1.3.5 of AHRI
210/240–2008 (incorporated by reference, see
§ 430.3) with Addendum 1 and 2. For the
vapor refrigerant line(s), use the insulation
included with the unit; if no insulation is
provided, refer to the specifications for the
insulation in the installation instructions
included with the unit by the manufacturer;
if no insulation is included with the unit and
the installation instructions do not contain
provisions for insulating the line(s), fully
insulate the vapor refrigerant line(s) with
vapor proof insulation having an inside
diameter that matches the refrigerant tubing
and a nominal thickness of at least 0.5
inches. For the liquid refrigerant line(s), use
the insulation included with the unit; if no
insulation is provided, refer to the
specifications for the insulation in the
installation instructions included with the
unit by the manufacturer; if no insulation is
included with the unit and the installation
instructions do not contain provisions for
insulating the line(s), leave the liquid
refrigerant line(s) exposed to the air for air
conditioners and heat pumps that heat and
cool; or, for heating-only heat pumps,
insulate the liquid refrigerant line(s) with
insulation having an inside diameter that
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Jkt 238001
matches the refrigerant tubing and a nominal
thickness of at least 0.5 inches;
(2) When testing split systems, if the
indoor unit does not ship with a cooling
mode expansion device, test the system using
the device as specified in the installation
instructions provided with the indoor unit. If
none is specified, test the system using a
thermostatic expansion valve with internal
pressure equalization that the valve
manufacturer’s product literature indicates is
appropriate for the system.
(3) When testing triple-split systems (see
section 1.2, Definitions), use the tubing
length specified in section 6.1.3.5 of AHRI
210/240–2008 (incorporated by reference, see
§ 430.3) with Addendum 1 and 2 to connect
the outdoor coil, indoor compressor section,
and indoor coil while still meeting the
requirement of exposing 10 feet of the tubing
to outside conditions; or
(4) When testing split systems having
multiple indoor coils, connect each indoor
blower-coil to the outdoor unit using: (a) 25
feet of tubing, or (b) tubing furnished by the
manufacturer, whichever is longer.
If they are needed to make a secondary
measurement of capacity, install refrigerant
pressure measuring instruments as described
in section 8.2.5 of ASHRAE Standard 37–
2009 (incorporated by reference, see § 430.3).
Refer to section 2.10 of this appendix to learn
which secondary methods require refrigerant
pressure measurements. At a minimum,
insulate the low-pressure line(s) of a split
system with insulation having an inside
diameter that matches the refrigerant tubing
and a nominal thickness of 0.5 inch.
b. For units designed for both horizontal
and vertical installation or for both up-flow
and down-flow vertical installations, the
manufacturer must use the orientation for
testing specified in the certification report.
Conduct testing with the following installed:
(1) The most restrictive filter(s);
(2) Supplementary heating coils; and
(3) Other equipment specified as part of the
unit, including all hardware used by a heat
comfort controller if so equipped (see section
1, Definitions). For small-duct, high-velocity
systems, configure all balance dampers or
restrictor devices on or inside the unit to
fully open or lowest restriction.
c. Testing a ducted unit without having an
indoor air filter installed is permissible as
long as the minimum external static pressure
requirement is adjusted as stated in Table 3,
note 3 (see section 3.1.4). Except as noted in
section 3.1.10, prevent the indoor air
supplementary heating coils from operating
during all tests. For coil-only indoor units
that are supplied without an enclosure,
create an enclosure using 1 inch fiberglass
ductboard having a nominal density of 6
pounds per cubic foot. Or alternatively, use
some other insulating material having a
thermal resistance (‘‘R’’ value) between 4 and
6 hr·ft2· °F/Btu. For units where the coil is
housed within an enclosure or cabinet, no
extra insulating or sealing is allowed.
d. When testing coil-only central air
conditioners and heat pumps, install a
toroidal-type transformer to power the
system’s low-voltage components, complying
with any additional requirements for this
transformer mentioned in the installation
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69349
manuals included with the unit by the
manufacturer. If the installation manuals do
not provide specifications for the
transformer, use a transformer having the
following features: (1) A nominal volt-amp
rating that results in the transformer being
loaded at a level that is between 25 and 90
percent based on the highest power value
expected and then confirmed during the off
mode test; (2) designed to operate with a
primary input of 230 V, single phase, 60 Hz;
and (3) that provides an output voltage that
is within the specified range for each lowvoltage component. The power consumption
of the components connected to the
transformer must be included as part of the
total system power consumption during the
off mode tests, less if included the power
consumed by the transformer when no load
is connected to it.
e. An outdoor unit with no match (i.e., that
is not sold with indoor units) shall be tested
without an indoor blower installed, with a
single cooling air volume rate, using an
indoor unit whose coil has (1) round tubes
of outer diameter no less than 0.375 inches,
and (2) a normalized gross indoor fin surface
(NGIFS) no greater than 1.15 square inches
per British thermal unit per hour (sq. in./Btu/
hr). NGIFS is calculated as follows:
˙
NGIFS = 2 × Lf × Wf × Nf ÷ Qc(95)
where,
Lf = Indoor coil fin length in inches, also
height of the coil transverse to the tubes.
Wf = Indoor coil fin width in inches, also
depth of the coil.
Nf = Number of fins.
˙
Qc(95) = the measured space cooling capacity
of the tested outdoor unit/indoor unit
combination as determined from the A2
or A Test whichever applies, Btu/h.
2.2.1 Defrost control settings.
Set heat pump defrost controls at the
normal settings which most typify those
encountered in generalized climatic region
IV. (Refer to Figure 1 and Table 19 of section
4.2 for information on region IV.) For heat
pumps that use a time-adaptive defrost
control system (see section 1.2, Definitions),
the manufacturer must specify the frosting
interval to be used during Frost
Accumulation tests and provide the
procedure for manually initiating the defrost
at the specified time. To ease testing of any
unit, the manufacturer should provide
information and any necessary hardware to
manually initiate a defrost cycle.
2.2.2 Special requirements for units
having a multiple-speed outdoor fan.
Configure the multiple-speed outdoor fan
according to the installation manual included
with the unit by the manufacturer, and
thereafter, leave it unchanged for all tests.
The controls of the unit must regulate the
operation of the outdoor fan during all lab
tests except dry coil cooling mode tests. For
dry coil cooling mode tests, the outdoor fan
must operate at the same speed used during
the required wet coil test conducted at the
same outdoor test conditions.
2.2.3 Special requirements for multi-split
air conditioners and heat pumps, systems
composed of multiple single-zone-multiplecoil split-system units (having multiple
outdoor units located side-by-side), and
ducted systems using a single indoor section
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Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
containing multiple blowers that would
normally operate using two or more indoor
thermostats.
Because these systems will have more than
one indoor blower and possibly multiple
outdoor fans and compressor systems,
references in this test procedure to a singular
indoor blower, outdoor fan, and compressor
means all indoor blowers, all outdoor fans,
and all compressor systems that are
energized during the test.
a. Additional requirements for multi-split
air conditioners and heat pumps and systems
composed of multiple single-zone-multiplecoil split-system units. For any test where the
system is operated at part load (i.e., one or
more compressors ‘‘off’’, operating at the
intermediate or minimum compressor speed,
or at low compressor capacity), the
manufacturer shall designate the indoor
coil(s) that are not providing heating or
cooling during the test such that the sum of
the nominal heating or cooling capacity of
the operational indoor units is within 5
percent of the intended part load heating or
cooling capacity. For variable-speed systems,
the manufacturer must designate at least one
indoor unit that is not providing heating or
cooling for all tests conducted at minimum
compressor speed. For all other part-load
tests, the manufacturer shall choose to turn
off zero, one, two, or more indoor units. The
chosen configuration shall remain unchanged
for all tests conducted at the same
compressor speed/capacity. For any indoor
coil that is not providing heating or cooling
during a test, cease forced airflow through
this indoor coil and block its outlet duct.
b. Additional requirements for ducted
systems with a single indoor section
containing multiple blowers where the
blowers are designed to cycle on and off
independently of one another and are not
controlled such that all blowers are
modulated to always operate at the same air
volume rate or speed. This Appendix covers
systems with a single-speed compressor or
systems offering two fixed stages of
compressor capacity (e.g., a two-speed
compressor, two single-speed compressors).
For any test where the system is operated at
its lowest capacity—i.e., the lowest total air
volume rate allowed when operating the
single-speed compressor or when operating
at low compressor capacity—blowers
accounting for at least one-third of the fullload air volume rate must be turned off
unless prevented by the controls of the unit.
In such cases, turn off as many blowers as
permitted by the unit’s controls. Where more
than one option exists for meeting this ‘‘off’’
blower requirement, the manufacturer shall
include in its installation manuals included
with the unit which blower(s) are turned off.
The chosen configuration shall remain
unchanged for all tests conducted at the same
lowest capacity configuration. For any indoor
coil turned off during a test, cease forced
airflow through any outlet duct connected to
an ‘‘off’’ blower.
c. For test setups where it is physically
impossible for the laboratory to use the
required line length listed in Table 3 of
ANSI/AHRI Standard 1230–2010
(incorporated by reference, see § 430.3) with
Addendum 2, then the actual refrigerant line
VerDate Sep<11>2014
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Jkt 238001
length used by the laboratory may exceed the
required length and the refrigerant line
length correction factors in Table 4 of ANSI/
AHRI Standard 1230–2010 with Addendum
2 are applied.
2.2.4 Wet-bulb temperature requirements
for the air entering the indoor and outdoor
coils.
2.2.4.1 Cooling mode tests. For wet-coil
cooling mode tests, regulate the water vapor
content of the air entering the indoor unit to
the applicable wet-bulb temperature listed in
Tables 4 to 7. As noted in these same tables,
achieve a wet-bulb temperature during drycoil cooling mode tests that results in no
condensate forming on the indoor coil.
Controlling the water vapor content of the air
entering the outdoor side of the unit is not
required for cooling mode tests except when
testing:
(1) Units that reject condensate to the
outdoor coil during wet coil tests. Tables 4–
7 list the applicable wet-bulb temperatures.
(2) Single-package units where all or part
of the indoor section is located in the outdoor
test room. The average dew point
temperature of the air entering the outdoor
coil during wet coil tests must be within ±3.0
°F of the average dew point temperature of
the air entering the indoor coil over the 30minute data collection interval described in
section 3.3. For dry coil tests on such units,
it may be necessary to limit the moisture
content of the air entering the outdoor side
of the unit to meet the requirements of
section 3.4.
2.2.4.2 Heating mode tests.
For heating mode tests, regulate the water
vapor content of the air entering the outdoor
unit to the applicable wet-bulb temperature
listed in Tables 11 to 14. The wet-bulb
temperature entering the indoor side of the
heat pump must not exceed 60 °F.
Additionally, if the Outdoor Air Enthalpy
test method is used while testing a singlepackage heat pump where all or part of the
outdoor section is located in the indoor test
room, adjust the wet-bulb temperature for the
air entering the indoor side to yield an
indoor-side dew point temperature that is as
close as reasonably possible to the dew point
temperature of the outdoor-side entering air.
2.2.5 Additional refrigerant charging
requirements.
2.2.5.1 The ‘‘manufacturer’s published
instructions,’’ as stated in section 8.2 of
ASHRAE Standard 37–2009 (incorporated by
reference, see § 430.3) and ‘‘manufacturer’s
installation instructions’’ discussed in this
Appendix mean the manufacturer’s
installation instructions that come packaged
with or appear in the labels applied to the
unit. This does not include online manuals.
Installation instructions that are shipped
with the unit shall take precedence over
installation instructions that appear in the
labels applied to the unit.
2.2.5.2 Instructions to Use for Charging.
a. Where the manufacturer’s installation
instructions contain two sets of refrigerant
charging criteria, one for field installations
and one for lab testing, use the field
installation criteria.
b. For systems consisting of an outdoor
unit manufacturer’s outdoor section and
indoor section with differing charging
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procedures the refrigerant charge shall be
adjusted per the outdoor installation
instructions.
c. For systems consisting of an outdoor
unit manufacturer’s outdoor section and an
independent coil manufacturer’s indoor
section with differing charging procedures
the refrigerant charge shall be adjusted per
the indoor installation instructions.
2.2.5.3 Test(s) to Use for Charging.
a. Use the tests or operating conditions
specified in the manufacturer’s installation
instructions for charging.
b. If the manufacturer’s installation
instructions do not specify a test or operating
conditions for charging or there are no
manufacturer’s instructions, use the
following test(s):
(1) For air conditioners or cooling and
heating heat pumps, use the A or A2 test.
(2) For cooling and heating heat pumps
that do not function in the H1 or H12 test
with the charge set for the A or A2 test and
for heating-only heat pumps, use the H1 or
H12 test.
2.2.5.4 Parameters to Set and Their Target
Values.
a. Consult the manufacturer’s installation
instructions regarding which parameters to
set and their target values. If the instructions
provide ranges of values, select target values
equal to the midpoints of the provided
ranges.
b. In the event of conflicting information
between charging instructions (defined as
multiple conditions given for charge
adjustment where all conditions specified
cannot be met), follow the following
hierarchy.
(1) For fixed orifice systems:
(i) Superheat
(ii) High side pressure or corresponding
saturation or dew-point temperature
(iii) Low side pressure or corresponding
saturation or dew-point temperature
(iv) Low side temperature
(iii) High side temperature
(iv) Charge weight
(2) For expansion valve systems:
(i) Subcooling
(ii) High side pressure or corresponding
saturation or dew-point temperature
(iii) Low side pressure or corresponding
saturation or dew-point temperature
(iv) Approach temperature (difference
between temperature of liquid leaving
condenser and condenser average inlet
air temperature)
(v) Charge weight
c. If there are no installation instructions
and/or they do not provide parameters and
target values, set superheat to a target value
of 12 °F for fixed orifice systems or set
subcooling to a target value of 10 °F for
expansion valve systems.
2.2.5.5 Charging Tolerances.
a. If the manufacturer’s installation
instructions specify tolerances on target
values for the charging parameters, set the
values using these tolerances.
b. Otherwise, use the following tolerances
for the different charging parameters:
1. Superheat: +/¥2.0 °F
2. Subcooling: +/¥0.6 °F
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3. High side pressure or corresponding
saturation or dew point temperature: +/¥4.0
psi or +/¥1.0 °F
4. Low side pressure or corresponding
saturation or dew point temperature: +/¥2.0
psi or +/¥0.8 °F
5. High side temperature: +/¥2.0 °F
6. Low side temperature: +/¥2.0 °F
7. Approach temperature: +/¥1.0 °F
8. Charge weight: +/¥2.0 ounce
2.2.5.6 Special Charging Instructions.
a. Cooling and Heating Heat Pumps
If, using the initial charge set in the A or
A2 test, the conditions are not within the
range specified in manufacturer’s
instructions for the H1 or H12 test, make as
small as possible an adjustment to obtain
conditions for this test in the specified range.
After this adjustment, recheck conditions in
the A or A2 test to confirm that they are still
within the specified range for this test.
b. Single-Package Systems
Unless otherwise directed by the
manufacturer’s installation instructions,
install one or more refrigerant line pressure
gauges during the setup of the unit if setting
of refrigerant charge is based on certain
operating parameters:
(1) Install a pressure gauge on the liquid
line if charging is on the basis of subcooling,
or high side pressure or corresponding
saturation or dew point temperature;
(2) Install a pressure gauge on the suction
line if charging is on the basis of superheat,
or low side pressure or corresponding
saturation or dew point temperature. If
manufacturer’s installation instructions
indicate that pressure gauges are not to be
installed, setting of charge shall not be based
on any of the parameters listed in b.(1) and
(2) of this section.
2.2.5.7 Near-azeotropic and zeotropic
refrigerants.
Charging of near-azeotropic and zeotropic
refrigerants shall only be performed with
refrigerant in the liquid state.
2.2.5.8 Adjustment of charge between
tests.
After charging the system as described in
this test procedure, use the set refrigerant
charge for all tests used to determine
performance. Do not adjust the refrigerant
charge at any point during testing.
2.3 Indoor air volume rates.
If a unit’s controls allow for overspeeding
the indoor blower (usually on a temporary
basis), take the necessary steps to prevent
overspeeding during all tests.
2.3.1 Cooling tests.
a. Set indoor blower airflow-control
settings (e.g., fan motor pin settings, fan
motor speed) according to the installation
instructions that are provided with the
equipment while meeting the airflow
requirements that are specified in section
3.1.4 of this appendix. If the manufacturer
installation instructions do not provide
guidance on the airflow-control settings for a
system tested with the indoor blower
installed, select the lowest speed that will
satisfy the minimum external static pressure
specified in section 3.1.4.1.1 of this appendix
with an air volume rate at or higher than the
rated full-load cooling air volume rate while
meeting the maximum air flow requirement.
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b. Express the Cooling Full-load Air
Volume Rate, the Cooling Minimum Air
Volume Rate, and the Cooling Intermediate
Air Volume Rate in terms of standard air.
2.3.2 Heating tests.
a. If needed, set the indoor blower airflowcontrol settings (e.g., fan motor pin settings,
fan motor speed) according to the installation
instructions that are provided with the
equipment. Do this set-up while meeting all
applicable airflow requirements specified in
sections 3.1.4 of this appendix. For a cooling
and heating heat pump tested with an indoor
blower installed, if the manufacturer
installation instructions do not provide
guidance on the fan airflow-control settings,
use the same airflow-control settings used for
the cooling test. If the manufacturer
installation instructions do not provide
guidance on the airflow-control settings for a
heating-only heat pump tested with the
indoor blower installed, select the lowest
speed that will satisfy the minimum external
static pressure specified in section 3.1.4.4.3
of this appendix with an air volume rate at
or higher than the rated heating full-load air
volume rate.
b. Express the Heating Full-Load Air
Volume Rate, the Heating Minimum Air
Volume Rate, the Heating Intermediate Air
Volume Rate, and the Heating Nominal Air
Volume Rate in terms of standard air.
2.4 Indoor coil inlet and outlet duct
connections.
Insulate and/or construct the outlet
plenum described in section 2.4.1 of this
appendix and, if installed, the inlet plenum
described in section 2.4.2 of this appendix
with thermal insulation having a nominal
overall resistance (R-value) of at least 19
hr·ft2· °F/Btu.
2.4.1 Outlet plenum for the indoor unit.
a. Attach a plenum to the outlet of the
indoor coil. (NOTE: for some packaged
systems, the indoor coil may be located in
the outdoor test room.)
b. For systems having multiple indoor
coils, or multiple indoor blowers within a
single indoor section, attach a plenum to
each indoor coil or blower outlet. Connect
two or more outlet plenums to a single
common duct so that each indoor coil
ultimately connects to an airflow measuring
apparatus (section 2.6). If using more than
one indoor test room, do likewise, creating
one or more common ducts within each test
room that contains multiple indoor coils. At
the plane where each plenum enters a
common duct, install an adjustable airflow
damper and use it to equalize the static
pressure in each plenum. Each outlet air
temperature grid (section 2.5.4) and airflow
measuring apparatus are located downstream
of the inlet(s) to the common duct.
c. For small-duct, high-velocity systems,
install an outlet plenum that has a diameter
that is equal to or less than the value listed
below. The limit depends only on the
Cooling Full-Load Air Volume Rate (see
section 3.1.4.1.1 of this appendix) and is
effective regardless of the flange dimensions
on the outlet of the unit (or an air supply
plenum adapter accessory, if installed in
accordance with the manufacturer’s
installation instructions).
d. Add a static pressure tap to each face of
the (each) outlet plenum, if rectangular, or at
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four evenly distributed locations along the
circumference of an oval or round plenum.
Create a manifold that connects the four
static pressure taps. Figures 7a, 7b, 7c of
ASHRAE Standard 37–2009 (incorporated by
reference, see § 430.3) shows two of the three
options allowed for the manifold
configuration; the third option is the brokenring, four-to-one manifold configuration that
is shown in Figure 7a of ASHRAE Standard
37–2009. See Figures 7a, 7b, 7c, and 8 of
ASHRAE Standard 37–2009 for the crosssectional dimensions and minimum length of
the (each) plenum and the locations for
adding the static pressure taps for units
tested with and without an indoor blower
installed.
TABLE 2—SIZE OF OUTLET PLENUM
Cooling full-load air volume rate
(scfm)
≤500 ..................................
501 to 700 ........................
701 to 900 ........................
901 to 1100 ......................
1101 to 1400 ....................
1401 to 1750 ....................
Maximum
diameter * of
outlet plenum
(inches)
6
7
8
9
10
11
* If the outlet plenum is rectangular, calculate its equivalent diameter using (4A/P,)
where A is the cross-sectional area and P is
the perimeter of the rectangular plenum, and
compare it to the listed maximum diameter.
2.4.2 Inlet plenum for the indoor unit.
Install an inlet plenum when testing a coilonly indoor unit or a packaged system where
the indoor coil is located in the outdoor test
room. Add static pressure taps at the center
of each face of this plenum, if rectangular, or
at four evenly distributed locations along the
circumference of an oval or round plenum.
Make a manifold that connects the four
static-pressure taps using one of the three
configurations specified in section 2.4.1. See
Figures 7b, 7c, and Figure 8 of ASHRAE
Standard 37–2009 (incorporated by reference,
see § 430.3) for cross-sectional dimensions,
the minimum length of the inlet plenum, and
the locations of the static-pressure taps.
When testing a ducted unit having an indoor
blower (and the indoor coil is in the indoor
test room), test with an inlet plenum
installed unless physically prohibited by
space limitations within the test room. If
used, construct the inlet plenum and add the
four static-pressure taps as shown in Figure
8 of ASHRAE Standard 37–2009. If used, the
inlet duct size shall equal the size of the inlet
opening of the air-handling (blower coil) unit
or furnace, with a minimum length of 6
inches. Manifold the four static-pressure taps
using one of the three configurations
specified in section 2.4.1.d. Never use an
inlet plenum when testing a non-ducted
system.
2.5 Indoor coil air property
measurements and air damper box
applications.
Follow instructions for indoor coil air
property measurements as described in AHRI
210/240-Draft, appendix E, section E4, unless
otherwise instructed in this section.
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a. Measure the dry-bulb temperature and
water vapor content of the air entering and
leaving the indoor coil. If needed, use an air
sampling device to divert air to a sensor(s)
that measures the water vapor content of the
air. See Section 5.3 of ASHRAE Standard
41.1–2013 (incorporated by reference, see
§ 430.3) for guidance on constructing an air
sampling device. No part of the air sampling
device or the tubing transferring the sampled
air to the sensor shall be within two inches
of the test chamber floor, and the transfer
tubing shall be insulated. The sampling
device may also divert air to a remotely
located sensor(s) that measures dry bulb
temperature. The air sampling device and the
remotely located temperature sensor(s) may
be used to determine the entering air dry
bulb temperature during any test. The air
sampling device and the remotely located
leaving air dry bulb temperature sensor(s)
may be used for all tests except:
(1) Cyclic tests; and
(2) Frost accumulation tests.
b. An acceptable alternative in all cases,
including the two special cases noted above,
is to install a grid of dry bulb temperature
sensors within the outlet and inlet ducts. Use
a temperature grid to get the average dry bulb
temperature at one location, leaving or
entering, or when two grids are applied as a
thermopile, to directly obtain the
temperature difference. A grid of temperature
sensors (which may also be used for
determining average leaving air dry bulb
temperature) is required to measure the
temperature distribution within a crosssection of the leaving airstream.
c. Use an inlet and outlet air damper box,
an inlet upturned duct, or any combination
thereof when conducting one or both of the
cyclic tests listed in sections 3.2 and 3.6 on
ducted systems. Otherwise if not conducting
one or both of said cyclic tests, install an
outlet air damper box when testing ducted
and non-ducted heat pumps that cycle off the
indoor blower during defrost cycles if no
other means is available for preventing
natural or forced convection through the
indoor unit when the indoor blower is off.
Never use an inlet damper box or an inlet
upturned duct when testing a non-ducted
system. An inlet upturned duct is a length of
ductwork so installed upstream from the
inlet such that the indoor duct inlet opening,
facing upwards, is sufficiently high to
prevent natural convection transfer out of the
duct. If an inlet upturned duct is used, install
a dry bulb temperature sensor near the inlet
opening of the indoor duct at a centerline
location not higher than the lowest elevation
of the duct edges at the inlet, and ensure that
the variation of the dry bulb temperature at
this location, measured at least every minute
during the compressor OFF period of the
cyclic test, does not exceed 1.0 °F.
2.5.1 Test set-up on the inlet side of the
indoor coil: For cases where the inlet airflow
prevention device is installed.
a. Install an airflow prevention device as
specified in section 2.5.1.1 or 2.5.1.2 of this
appendix, whichever applies.
b. For an inlet damper box, locate the grid
of entering air dry-bulb temperature sensors,
if used, and the air sampling device, or the
sensor used to measure the water vapor
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content of the inlet air, at a location
immediately upstream of the damper box
inlet. For an inlet upturned duct, locate the
grid of entering air dry-bulb temperature
sensors, if used, and the air sampling device,
or the sensor used to measure the water
vapor content of the inlet air, at a location
at least one foot downstream from the
beginning of the insulated portion of the duct
but before the static pressure measurement;
install a dry-bulb temperature sensor at a
centerline location not higher than the lowest
elevation of the duct edges at the device
inlet.
2.5.1.1 If the section 2.4.2 inlet plenum is
installed.
Construct the airflow prevention device
having a cross-sectional flow area equal to or
greater than the flow area of the inlet
plenum. Install the airflow prevention device
upstream of the inlet plenum and construct
ductwork connecting it to the inlet plenum.
If needed, use an adaptor plate or a transition
duct section to connect the airflow
prevention device with the inlet plenum.
Insulate the ductwork and inlet plenum with
thermal insulation that has a nominal overall
resistance (R-value) of at least 19 hr · ft2 · °F/
Btu.
2.5.1.2 If the section 2.4.2 inlet plenum is
not installed.
Construct the airflow prevention device
having a cross-sectional flow area equal to or
greater than the flow area of the air inlet of
the indoor unit. Install the airflow prevention
device immediately upstream of the inlet of
the indoor unit. If needed, use an adaptor
plate or a short transition duct section to
connect the airflow prevention device with
the unit’s air inlet. Add static pressure taps
at the center of each face of a rectangular
airflow prevention device, or at four evenly
distributed locations along the circumference
of an oval or round airflow prevention
device. Locate the pressure taps between the
airflow prevention device and the inlet of the
indoor unit. Make a manifold that connects
the four static pressure taps. Insulate the
ductwork with thermal insulation that has a
nominal overall resistance (R-value) of at
least 19 hr · ft2 · °F/Btu.
2.5.2 Test set-up on the inlet side of the
indoor unit: For cases where no airflow
prevention device is installed.
If using the section 2.4.2 inlet plenum and
a grid of dry bulb temperature sensors, mount
the grid at a location upstream of the static
pressure taps described in section 2.4.2,
preferably at the entrance plane of the inlet
plenum. If the section 2.4.2 inlet plenum is
not used, but a grid of dry bulb temperature
sensors is used, locate the grid approximately
6 inches upstream from the inlet of the
indoor coil. Or, in the case of non-ducted
units having multiple indoor coils, locate a
grid approximately 6 inches upstream from
the inlet of each indoor coil. Position an air
sampling device, or the sensor used to
measure the water vapor content of the inlet
air, immediately upstream of the (each)
entering air dry-bulb temperature sensor grid.
If a grid of sensors is not used, position the
entering air sampling device (or the sensor
used to measure the water vapor content of
the inlet air) as if the grid were present.
2.5.3 Indoor coil static pressure
difference measurement.
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Section 6.5.2 of ASHRAE Standard 37–
2009 (incorporated by reference, see § 430.3)
describes the method for fabricating staticpressure taps. Also refer to Figure 2A of
ASHRAE Standard 51–07/AMCA Standard
210–07 (incorporated by reference, see
§ 430.3). Use a differential pressure
measuring instrument that is accurate to
within ±0.01 inches of water and has a
resolution of at least 0.01 inches of water to
measure the static pressure difference
between the indoor coil air inlet and outlet.
Connect one side of the differential pressure
instrument to the manifolded pressure taps
installed in the outlet plenum. Connect the
other side of the instrument to the
manifolded pressure taps located in either
the inlet plenum or incorporated within the
airflow prevention device. If an inlet plenum
or inlet airflow prevention device is not used,
leave the inlet side of the differential
pressure instrument open to the surrounding
atmosphere. For non-ducted systems that are
tested with multiple outlet plenums, measure
the static pressure within each outlet plenum
relative to the surrounding atmosphere.
2.5.4 Test set-up on the outlet side of the
indoor coil.
a. Install an interconnecting duct between
the outlet plenum described in section 2.4.1
of this appendix and the airflow measuring
apparatus described below in section 2.6.
The cross-sectional flow area of the
interconnecting duct must be equal to or
greater than the flow area of the outlet
plenum or the common duct used when
testing non-ducted units having multiple
indoor coils. If needed, use adaptor plates or
transition duct sections to allow the
connections. To minimize leakage, tape joints
within the interconnecting duct (and the
outlet plenum). Construct or insulate the
entire flow section with thermal insulation
having a nominal overall resistance (R-value)
of at least 19 hr · ft2 · °F/Btu.
b. Install a grid(s) of dry-bulb temperature
sensors inside the interconnecting duct. Also,
install an air sampling device, or the
sensor(s) used to measure the water vapor
content of the outlet air, inside the
interconnecting duct. Locate the dry-bulb
temperature grid(s) upstream of the air
sampling device (or the in-duct sensor(s)
used to measure the water vapor content of
the outlet air). Air that circulates through an
air sampling device and past a remote watervapor-content sensor(s) must be returned to
the interconnecting duct at a location:
(1) Downstream of the air sampling device;
(2) Upstream of the outlet air damper box,
if installed; and
(3) Upstream of the section 2.6 airflow
measuring apparatus.
2.5.4.1 Outlet air damper box placement
and requirements.
If using an outlet air damper box (see
section 2.5), install it within the
interconnecting duct at a location
downstream of the location where air from
the sampling device is reintroduced or
downstream of the in-duct sensor that
measures water vapor content of the outlet
air. The leakage rate from the combination of
the outlet plenum, the closed damper, and
the duct section that connects these two
components must not exceed 20 cubic feet
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per minute when a negative pressure of 1
inch of water column is maintained at the
plenum’s inlet.
2.5.4.2 Procedures to minimize
temperature maldistribution.
Use these procedures if necessary to
correct temperature maldistributions. Install
a mixing device(s) upstream of the outlet air,
dry-bulb temperature grid (but downstream
of the outlet plenum static pressure taps).
Use a perforated screen located between the
mixing device and the dry-bulb temperature
grid, with a maximum open area of 40
percent. One or both items should help to
meet the maximum outlet air temperature
distribution specified in section 3.1.8. Mixing
devices are described in sections 5.3.2 and
5.3.3 of ASHRAE Standard 41.1–2013 and
section 5.2.2 of ASHRAE Standard 41.2–87
(RA 92) (incorporated by reference, see
§ 430.3).
2.5.4.3 Minimizing air leakage.
For small-duct, high-velocity systems,
install an air damper near the end of the
interconnecting duct, just prior to the
transition to the airflow measuring apparatus
of section 2.6. To minimize air leakage,
adjust this damper such that the pressure in
the receiving chamber of the airflow
measuring apparatus is no more than 0.5 inch
of water higher than the surrounding test
room ambient. If applicable, in lieu of
installing a separate damper, use the outlet
air damper box of sections 2.5 and 2.5.4.1 of
this appendix if it allows variable
positioning. Also apply these steps to any
conventional indoor blower unit that creates
a static pressure within the receiving
chamber of the airflow measuring apparatus
that exceeds the test room ambient pressure
by more than 0.5 inches of water column.
2.5.5 Dry bulb temperature measurement.
a. Measure dry bulb temperatures as
specified in sections 4, 5.3, 6, 7.2, and 7.3 of
ASHRAE Standard 41.1–2013 (incorporated
by reference, see § 430.3).
b. Distribute the sensors of a dry-bulb
temperature grid over the entire flow area.
The required minimum is 9 sensors per grid.
2.5.6 Water vapor content measurement.
Determine water vapor content by
measuring dry-bulb temperature combined
with the air wet-bulb temperature, dew point
temperature, or relative humidity. If used,
construct and apply wet-bulb temperature
sensors as specified in sections 4, 5, 6, 7.2,
7.3, 7.4, and 7.5 of ASHRAE Standard 41.6–
2014 (incorporated by reference, see § 430.3).
The temperature sensor (wick removed) must
be accurate to within ±0.2 °F. If used, apply
dew point hygrometers as specified in
sections 4, 5, 6, and 7.1 of ASHRAE Standard
41.6–2014. The dew point hygrometers must
be accurate to within ±0.4 °F when operated
at conditions that result in the evaluation of
dew points above 35 °F. If used, a relative
humidity (RH) meter must be accurate to
within ±0.7% RH. Other means to determine
the psychrometric state of air may be used as
long as the measurement accuracy is
equivalent to or better than the accuracy
achieved from using a wet-bulb temperature
sensor that meets the above specifications.
2.5.7 Air damper box performance
requirements.
If used (see section 2.5), the air damper
box(es) must be capable of being completely
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opened or completely closed within 10
seconds for each action.
2.6 Airflow measuring apparatus.
a. Fabricate and operate an Air Flow
Measuring Apparatus as specified in section
6.2 and 6.3 of ASHRAE Standard 37–2009
(incorporated by reference, see § 430.3). Refer
to Figure 12 of ASHRAE Standard 51–07/
AMCA Standard 210–07 or Figure 14 of
ASHRAE Standard 41.2–87 (RA 92)
(incorporated by reference, see § 430.3) for
guidance on placing the static pressure taps
and positioning the diffusion baffle (settling
means) relative to the chamber inlet. When
measuring the static pressure difference
across nozzles and/or velocity pressure at
nozzle throats using electronic pressure
transducers and a data acquisition system, if
high frequency fluctuations cause
measurement variations to exceed the test
tolerance limits specified in section 9.2 and
Table 2 of ASHRAE Standard 37–2009,
dampen the measurement system such that
the time constant associated with response to
a step change in measurement (time for the
response to change 63% of the way from the
initial output to the final output) is no longer
than five seconds.
b. Connect the airflow measuring apparatus
to the interconnecting duct section described
in section 2.5.4. See sections 6.1.1, 6.1.2, and
6.1.4, and Figures 1, 2, and 4 of ASHRAE
Standard 37–2009; and Figures D1, D2, and
D4 of AHRI 210/240–2008 (incorporated by
reference, see § 430.3) with Addendum 1 and
2 for illustrative examples of how the test
apparatus may be applied within a complete
laboratory set-up. Instead of following one of
these examples, an alternative set-up may be
used to handle the air leaving the airflow
measuring apparatus and to supply properly
conditioned air to the test unit’s inlet. The
alternative set-up, however, must not
interfere with the prescribed means for
measuring airflow rate, inlet and outlet air
temperatures, inlet and outlet water vapor
contents, and external static pressures, nor
create abnormal conditions surrounding the
test unit. (Note: Do not use an enclosure as
described in section 6.1.3 of ASHRAE
Standard 37–2009 when testing triple-split
units.)
2.7 Electrical voltage supply.
Perform all tests at the voltage specified in
section 6.1.3.2 of AHRI 210/240–2008
(incorporated by reference, see § 430.3) with
Addendum 1 and 2 for ‘‘Standard Rating
Tests.’’ If the voltage on the nameplate of
indoor and outdoor units differs, the voltage
supply on the outdoor unit shall be selected
for testing. Measure the supply voltage at the
terminals on the test unit using a volt meter
that provides a reading that is accurate to
within ±1.0 percent of the measured quantity.
2.8 Electrical power and energy
measurements.
a. Use an integrating power (watt-hour)
measuring system to determine the electrical
energy or average electrical power supplied
to all components of the air conditioner or
heat pump (including auxiliary components
such as controls, transformers, crankcase
heater, integral condensate pump on nonducted indoor units, etc.). The watt-hour
measuring system must give readings that are
accurate to within ±0.5 percent. For cyclic
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tests, this accuracy is required during both
the ON and OFF cycles. Use either two
different scales on the same watt-hour meter
or two separate watt-hour meters. Activate
the scale or meter having the lower power
rating within 15 seconds after beginning an
OFF cycle. Activate the scale or meter having
the higher power rating active within 15
seconds prior to beginning an ON cycle. For
ducted units tested with a fan installed, the
ON cycle lasts from compressor ON to indoor
blower OFF. For ducted units tested without
an indoor blower installed, the ON cycle lasts
from compressor ON to compressor OFF. For
non-ducted units, the ON cycle lasts from
indoor blower ON to indoor blower OFF.
When testing air conditioners and heat
pumps having a variable-speed compressor,
avoid using an induction watt/watt-hour
meter.
b. When performing section 3.5 and/or 3.8
cyclic tests on non-ducted units, provide
instrumentation to determine the average
electrical power consumption of the indoor
blower motor to within ±1.0 percent. If
required according to sections 3.3, 3.4, 3.7,
3.9.1 of this appendix, and/or 3.10, of this
appendix this same instrumentation
requirement applies when testing air
conditioners and heat pumps having a
variable-speed constant-air-volume-rate
indoor blower or a variable-speed, variableair-volume-rate indoor blower.
2.9 Time measurements.
Make elapsed time measurements using an
instrument that yields readings accurate to
within ±0.2 percent.
2.10 Test apparatus for the secondary
space conditioning capacity measurement.
For all tests, use the Indoor Air Enthalpy
Method to measure the unit’s capacity. This
method uses the test set-up specified in
sections 2.4 to 2.6 of this appendix. In
addition, for all steady-state tests, conduct a
second, independent measurement of
capacity as described in section 3.1.1. For
split systems, use one of the following
secondary measurement methods: Outdoor
Air Enthalpy Method, Compressor
Calibration Method, or Refrigerant Enthalpy
Method. For single-package units, use either
the Outdoor Air Enthalpy Method or the
Compressor Calibration Method as the
secondary measurement.
2.10.1 Outdoor Air Enthalpy Method.
a. To make a secondary measurement of
indoor space conditioning capacity using the
Outdoor Air Enthalpy Method, do the
following:
(1) Measure the electrical power
consumption of the test unit;
(2) Measure the air-side capacity at the
outdoor coil; and
(3) Apply a heat balance on the refrigerant
cycle.
b. The test apparatus required for the
Outdoor Air Enthalpy Method is a subset of
the apparatus used for the Indoor Air
Enthalpy Method. Required apparatus
includes the following:
(1) On the outlet side, an outlet plenum
containing static pressure taps (sections 2.4,
2.4.1, and 2.5.3),
(2) An airflow measuring apparatus
(section 2.6),
(3) A duct section that connects these two
components and itself contains the
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instrumentation for measuring the dry-bulb
temperature and water vapor content of the
air leaving the outdoor coil (sections 2.5.4,
2.5.5, and 2.5.6), and
(4) On the inlet side, a sampling device and
temperature grid (section 2.11b.).
c. During the preliminary tests described in
sections 3.11.1 and 3.11.1.1, measure the
evaporator and condenser temperatures or
pressures. On both the outdoor coil and the
indoor coil, solder a thermocouple onto a
return bend located at or near the midpoint
of each coil or at points not affected by vapor
superheat or liquid subcooling. Alternatively,
if the test unit is not sensitive to the
refrigerant charge, install pressure gages to
the access valves or to ports created from
tapping into the suction and discharge lines
according to sections 7.4.2 and 8.2.5 of
ASHRAE Standard 37–2009. Use this
alternative approach when testing a unit
charged with a zeotropic refrigerant having a
temperature glide in excess of 1 °F at the
specified test conditions.
2.10.2 Compressor Calibration Method.
Measure refrigerant pressures and
temperatures to determine the evaporator
superheat and the enthalpy of the refrigerant
that enters and exits the indoor coil.
Determine refrigerant flow rate or, when the
superheat of the refrigerant leaving the
evaporator is less than 5 °F, total capacity
from separate calibration tests conducted
under identical operating conditions. When
using this method, install instrumentation,
measure refrigerant properties, and adjust the
refrigerant charge according to section 7.4.2
and 8.2.5 of ASHRAE Standard 37–2009
(incorporated by reference, see § 430.3). Use
refrigerant temperature and pressure
measuring instruments that meet the
specifications given in sections 5.1.1 and 5.2
of ASHRAE Standard 37–2009.
2.10.3 Refrigerant Enthalpy Method.
For this method, calculate space
conditioning capacity by determining the
refrigerant enthalpy change for the indoor
coil and directly measuring the refrigerant
flow rate. Use section 7.5.2 of ASHRAE
Standard 37–2009 (incorporated by reference,
see § 430.3) for the requirements for this
method, including the additional
instrumentation requirements, and
information on placing the flow meter and a
sight glass. Use refrigerant temperature,
pressure, and flow measuring instruments
that meet the specifications given in sections
5.1.1, 5.2, and 5.5.1 of ASHRAE Standard 37–
2009. Refrigerant flow measurement
device(s), if used, must be elevated at least
two feet from the test chamber floor or placed
upon insulating material having a total
thermal resistance of at least R–12 and
extending at least one foot laterally beyond
each side of the device(s)’ exposed surfaces,
unless the device(s) are elevated at least two
feet from the floor.
2.11 Measurement of test room ambient
conditions.
Follow instructions for measurement of
test room ambient conditions as described in
AHRI 210/240-Draft, appendix E, section E4,
unless otherwise instructed in this section.
a. If using a test set-up where air is ducted
directly from the conditioning apparatus to
the indoor coil inlet (see Figure 2, Loop Air-
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Enthalpy Test Method Arrangement, of
ASHRAE Standard 37–2009), add
instrumentation to permit measurement of
the indoor test room dry-bulb temperature.
b. For the outdoor side, install a grid of
evenly-distributed sensors on every airpermitting face on the inlet of the outdoor
unit, such that each measurement represents
an air-inlet area of no more than one square
foot. This grid must be constructed and
applied as per section 5.3 of ASHRAE
Standard 41.1–2013 (incorporated by
reference, see § 430.3). The maximum and
minimum temperatures measured by these
sensors may differ by no more than 1.5 °F—
otherwise adjustments to the test room must
be made to improve temperature uniformity.
The outdoor conditions shall be verified with
the air collected by air sampling device. Air
collected by an air sampling device at the air
inlet of the outdoor unit for transfer to
sensors for measurement of temperature and/
or humidity shall be protected from
temperature change as follows: Any surface
of the air conveying tubing in contact with
surrounding air at a different temperature
than the sampled air shall be insulated with
thermal insulation with a nominal thermal
resistance (R-value) of at least 19 hr ·ft 2 · °F/
Btu, no part of the air sampling device or the
tubing conducting the sampled air to the
sensors shall be within two inches of the test
chamber floor, and pairs of measurements
(e.g. dry bulb temperature and wet bulb
temperature) used to determine water vapor
content of sampled air shall be measured in
the same location. Take steps (e.g., add or reposition a lab circulating fan), as needed, to
maximize temperature uniformity within the
outdoor test room. However, ensure that any
fan used for this purpose does not cause air
velocities in the vicinity of the test unit to
exceed 500 feet per minute.
c. Measure dry bulb temperatures as
specified in sections 4, 5, 7.2, 6, and 7.3 of
ASHRAE Standard 41.1–2013. Measure water
vapor content as stated in section 2.5.6.
2.12 Measurement of indoor blower
speed.
When required, measure fan speed using a
revolution counter, tachometer, or
stroboscope that gives readings accurate to
within ±1.0 percent.
2.13 Measurement of barometric pressure.
Determine the average barometric pressure
during each test. Use an instrument that
meets the requirements specified in section
5.2 of ASHRAE Standard 37–2009
(incorporated by reference, see § 430.3).
3. Testing Procedures
3.1 General Requirements.
If, during the testing process, an equipment
set-up adjustment is made that would have
altered the performance of the unit during
any already completed test, then repeat all
tests affected by the adjustment. For cyclic
tests, instead of maintaining an air volume
rate, for each airflow nozzle, maintain the
static pressure difference or velocity pressure
during an ON period at the same pressure
difference or velocity pressure as measured
during the steady-state test conducted at the
same test conditions.
Use the testing procedures in this section
to collect the data used for calculating (1)
performance metrics for central air
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conditioners and heat pumps during the
cooling season; (2) performance metrics for
heat pumps during the heating season; and
(3) power consumption metric(s) for central
air conditioners and heat pumps during the
off mode season(s).
3.1.1 Primary and secondary test
methods.
For all tests, use the Indoor Air Enthalpy
Method test apparatus to determine the unit’s
space conditioning capacity. The procedure
and data collected, however, differ slightly
depending upon whether the test is a steadystate test, a cyclic test, or a Frost
Accumulation test. The following sections
described these differences. For all steadystate tests (i.e., the A, A2, A1, B, B2, B1, C,
C1, EV, F1, G1, H01, H1, H12, H11, HIN, H3,
H32, and H31 Tests), in addition, use one of
the acceptable secondary methods specified
in section 2.10 to determine indoor space
conditioning capacity. Calculate this
secondary check of capacity according to
section 3.11. The two capacity measurements
must agree to within 6 percent to constitute
a valid test. For this capacity comparison, use
the Indoor Air Enthalpy Method capacity that
is calculated in section 7.3 of ASHRAE
Standard 37–2009 (and, if testing a coil-only
system, do not make the after-test fan heat
adjustments described in section 3.3, 3.4, 3.7,
and 3.10 of this appendix). However, include
the appropriate section 3.3 to 3.5 and 3.7 to
3.10 fan heat adjustments within the Indoor
Air Enthalpy Method capacities used for the
section 4 seasonal calculations.
3.1.2 Manufacturer-provided equipment
overrides.
Where needed, the manufacturer must
provide a means for overriding the controls
of the test unit so that the compressor(s)
operates at the specified speed or capacity
and the indoor blower operates at the
specified speed or delivers the specified air
volume rate.
3.1.3 Airflow through the outdoor coil.
For all tests, meet the requirements given
in section 6.1.3.4 of AHRI 210/240–2008
(incorporated by reference, see § 430.3) with
Addendum 1 and 2 when obtaining the
airflow through the outdoor coil.
3.1.3.1 Double-ducted. For products
intended to be installed with the outdoor
airflow ducted, the unit shall be installed
with outdoor coil ductwork installed per
manufacturer installation instructions and
shall operate between 0.10 and 0.15 in H2O
external static pressure. External static
pressure measurements shall be made in
accordance with ASHRAE Standard 37–2009
Section 6.4 and 6.5.
3.1.4 Airflow through the indoor coil.
Airflow setting(s) shall be determined
before testing begins. Unless otherwise
specified within this or its subsections, no
changes shall be made to the airflow
setting(s) after initiation of testing.
3.1.4.1 Cooling Full-load Air Volume
Rate.
3.1.4.1.1 Cooling Full-Load Air Volume
Rate for Ducted Units.
The manufacturer must specify the cooling
full-load air volume rate and the instructions
for setting fan speed or controls. Adjust the
cooling full-load air volume rate if needed to
satisfy the additional requirements of this
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section. First, when conducting the A or A2
Test (exclusively), the measured air volume
rate, when divided by the measured indoor
air-side total cooling capacity must not
exceed 37.5 cubic feet per minute of standard
air (scfm) per 1000 Btu/h. If this ratio is
exceeded, reduce the air volume rate until
this ratio is equaled. Use this reduced air
volume rate for all tests that call for using the
Cooling Full-load Air Volume Rate. Pressure
requirements are as follows:
a. For all ducted units tested with an
indoor blower installed, except those having
a constant-air-volume-rate indoor blower:
1. Achieve the Cooling Full-load Air
Volume Rate, determined in accordance with
the previous paragraph;
2. Measure the external static pressure;
3. If this pressure is equal to or greater than
the applicable minimum external static
pressure cited in Table 3, the pressure
requirement is satisfied. Use the current air
volume rate for all tests that require the
Cooling Full-load Air Volume Rate.
4. If the Table 3 minimum is not equaled
or exceeded,
4a. reduce the air volume rate and increase
the external static pressure by adjusting the
exhaust fan of the airflow measuring
apparatus until the applicable Table 3
minimum is equaled or
4b. until the measured air volume rate
equals 90 percent of the air volume rate from
step 1, whichever occurs first.
5. If the conditions of step 4a occur first,
the pressure requirement is satisfied. Use the
step 4a reduced air volume rate for all tests
that require the Cooling Full-load Air
Volume Rate.
6. If the conditions of step 4b occur first,
make an incremental change to the set-up of
the indoor blower (e.g., next highest fan
motor pin setting, next highest fan motor
speed) and repeat the evaluation process
beginning at above step 1. If the indoor
blower set-up cannot be further changed,
reduce the air volume rate and increase the
external static pressure by adjusting the
exhaust fan of the airflow measuring
apparatus until the applicable Table 3
minimum is equaled. Use this reduced air
volume rate for all tests that require the
Cooling Full-load Air Volume Rate.
b. For ducted units that are tested with a
constant-air-volume-rate indoor blower
installed. For all tests that specify the
Cooling Full-load Air Volume Rate, obtain an
external static pressure as close to (but not
less than) the applicable Table 3 value that
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does not cause automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined as follows, greater than 10
percent.
Where:
Qmax = maximum measured airflow value
Qmin = minimum measured airflow value
QVar = airflow variance, percent
Additional test steps as described in
section 3.3.(e) of this appendix are required
if the measured external static pressure
exceeds the target value by more than 0.03
inches of water.
c. For ducted units that are tested without
an indoor fan installed. For the A or A2 Test,
(exclusively), the pressure drop across the
indoor coil assembly must not exceed 0.30
inches of water. If this pressure drop is
exceeded, reduce the air volume rate until
the measured pressure drop equals the
specified maximum. Use this reduced air
volume rate for all tests that require the
Cooling Full-load Air Volume Rate.
TABLE 3—MINIMUM EXTERNAL STATIC PRESSURE FOR DUCTED SYSTEMS TESTED WITH AN INDOOR BLOWER INSTALLED
Minimum external resistance 3 (inches of water)
Rated cooling 1 or
heating 2 capacity
(Btu/h)
Short ducted systems 4
Up Thru 28,800 ..........................................................................................................
29,000 to 42,500 ........................................................................................................
43,000 and Above .....................................................................................................
Small-duct, highvelocity systems 4 5
0.03
0.05
0.07
1.10
1.15
1.20
All other systems
0.10
0.15
0.20
d. For ducted systems having multiple
indoor blowers within a single indoor
section, obtain the full-load air volume rate
with all blowers operating unless prevented
by the controls of the unit. In such cases, turn
on the maximum number of blowers
permitted by the unit’s controls. Where more
than one option exists for meeting this ‘‘on’’
blower requirement, which blower(s) are
turned on must match that specified by the
manufacturer in the installation manuals
included with the unit. Conduct section
3.1.4.1.1 setup steps for each blower
separately. If two or more indoor blowers are
connected to a common duct as per section
2.4.1, either turn off the other indoor blowers
connected to the same common duct or
temporarily divert their air volume to the test
room when confirming or adjusting the setup
configuration of individual blowers. If the
indoor blowers are all the same size or
model, the target air volume rate for each
blower plenum equals the full-load air
volume rate divided by the number of ‘‘on’’
blowers. If different size blowers are used
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within the indoor section, the allocation of
the system’s full-load air volume rate
assigned to each ‘‘on’’ blower must match
that specified by the manufacturer in the
installation manuals included with the unit.
3.1.4.1.2 Cooling Full-load Air Volume
Rate for Non-ducted Units.
For non-ducted units, the Cooling Fullload Air Volume Rate is the air volume rate
that results during each test when the unit is
operated at an external static pressure of zero
inches of water.
3.1.4.2 Cooling Minimum Air Volume
Rate.
The manufacturer must specify the cooling
minimum air volume rate and the
instructions for setting fan speed or controls.
The target external static pressure, DPst_i, for
any test ‘‘i’’ with a specified air volume rate
not equal to the cooling full-load air volume
rate is determined as follows.
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Where:
DPst_i = target minimum external static
pressure for test i;
DPst_full = minimum external static pressure
for test A or A2 (Table 3);
Qi = air volume rate for test i; and
Qfull = cooling full-load air volume rate as
measured after setting and/or adjustment
as described in section 3.1.4.1.1.
a. For ducted units tested with an indoor
blower installed that is not a constant-airvolume indoor blower, adjust for external
static pressure as follows.
1. Achieve the manufacturer-specified
cooling minimum air volume rate;
2. Measure the external static pressure;
3. If this pressure is equal to or greater than
the target minimum external static pressure
calculated as described above, use the
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1 For air conditioners and heat pumps, the value cited by the manufacturer in published literature for the unit’s capacity when operated at the A
or A2 Test conditions.
2 For heating-only heat pumps, the value the manufacturer cites in published literature for the unit’s capacity when operated at the H1 or H1
2
Test conditions.
3 For ducted units tested without an air filter installed, increase the applicable tabular value by 0.08 inches of water.
4 See section 1.2, Definitions, to determine if the equipment qualifies as a short-ducted or a small-duct, high-velocity system.
5 If a closed-loop, air-enthalpy test apparatus is used on the indoor side, limit the resistance to airflow on the inlet side of the indoor blower coil
to a maximum value of 0.1 inch of water. Impose the balance of the airflow resistance on the outlet side of the indoor blower.
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current air volume rate for all tests that
require the cooling minimum air volume rate.
4. If the target minimum is not equaled or
exceeded,
4a. reduce the air volume rate and increase
the external static pressure by adjusting the
exhaust fan of the airflow measuring
apparatus until the applicable target
minimum is equaled or
4b. until the measured air volume rate
equals 90 percent of the air volume rate from
step 1, whichever occurs first.
5. If the conditions of step 4a occur first,
use the step 4a reduced air volume rate for
all tests that require the cooling minimum air
volume rate.
6. If the conditions of step 4b occur first,
make an incremental change to the set-up of
the indoor fan (e.g., next highest fan motor
pin setting, next highest fan motor speed)
and repeat the evaluation process beginning
at above step 1. If the indoor fan set-up
cannot be further changed, reduce the air
volume rate and increase the external static
pressure by adjusting the exhaust fan of the
airflow measuring apparatus until the
applicable target minimum is equaled. Use
this reduced air volume rate for all tests that
require the cooling minimum air volume rate.
b. For ducted units with constant-airvolume indoor blowers, conduct all tests that
specify the cooling minimum air volume
rate—(i.e., the A1, B1, C1, F1, and G1 Tests)—
at an external static pressure that does not
cause an automatic shutdown of the indoor
blower or air volume rate variation QVar,
defined in section 3.1.4.1.1.b, greater than 10
percent, while being as close to, but not less
than the target minimum external static
pressure. Additional test steps as described
in section 3.3(e) of this appendix are required
if the measured external static pressure
exceeds the target value by more than 0.03
inches of water.
c. For ducted two-capacity units that are
tested without an indoor blower installed,
the Cooling Minimum Air Volume Rate is the
higher of (1) the rate specified by the
installation instructions included with the
unit by the manufacturer or (2) 75 percent of
the Cooling Full-load Air Volume Rate.
During the laboratory tests on a coil-only
(fanless) unit, obtain this Cooling Minimum
Air Volume Rate regardless of the pressure
drop across the indoor coil assembly.
d. For non-ducted units, the Cooling
Minimum Air Volume Rate is the air volume
rate that results during each test when the
unit operates at an external static pressure of
zero inches of water and at the indoor fan
setting used at low compressor capacity (twocapacity system) or minimum compressor
speed (variable-speed system). For units
having a single-speed compressor and a
variable-speed variable-air-volume-rate
indoor fan, use the lowest fan setting allowed
for cooling.
e. For ducted systems having multiple
indoor blowers within a single indoor
section, operate the indoor blowers such that
the lowest air volume rate allowed by the
unit’s controls is obtained when operating
the lone single-speed compressor or when
operating at low compressor capacity while
meeting the requirements of section 2.2.3.2
for the minimum number of blowers that
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must be turned off. Adjust for external static
pressure and if necessary adjust air volume
rates as described in section 3.1.4.2.a if the
indoor fan is not a constant-air-volume
indoor fan or as described in section 3.1.4.2.b
if the indoor fan is a constant-air-volume
indoor fan. The sum of the individual ‘‘on’’
blowers’ air volume rates is the cooling
minimum air volume rate for the system.
3.1.4.3 Cooling Intermediate Air Volume
Rate.
The manufacturer must specify the cooling
intermediate air volume rate and the
instructions for setting fan speed or controls.
Calculate target minimum external static
pressure as described in section 3.1.4.2.
a. For ducted units tested with an indoor
blower, installed that is not a constant-airvolume indoor blower, adjust for external
static pressure as described in section
3.1.4.2.a for cooling minimum air volume
rate.
b. For ducted units tested with constantair-volume indoor blowers installed, conduct
the EV Test at an external static pressure that
does not cause an automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but
not less than the target minimum external
static pressure. Additional test steps as
described in section 3.3(e) of this appendix
are required if the measured external static
pressure exceeds the target value by more
than 0.03 inches of water.
c. For non-ducted units, the Cooling
Intermediate Air Volume Rate is the air
volume rate that results when the unit
operates at an external static pressure of zero
inches of water and at the fan speed selected
by the controls of the unit for the EV Test
conditions.
3.1.4.4 Heating Full-load Air Volume
Rate.
3.1.4.4.1 Ducted heat pumps where the
Heating and Cooling Full-load Air Volume
Rates are the same.
a. Use the Cooling Full-load Air Volume
Rate as the Heating Full-load Air Volume
Rate for:
1. Ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower that operates at the
same airflow-control setting during both the
A (or A2) and the H1 (or H12) Tests;
2. Ducted heat pumps tested with constantair-flow indoor blowers installed that provide
the same air flow for the A (or A2) and the
H1 (or H12) Tests; and
3. Ducted heat pumps that are tested
without an indoor blower installed (except
two-capacity northern heat pumps that are
tested only at low capacity cooling—see
3.1.4.4.2).
b. For heat pumps that meet the above
criteria ‘‘1’’ and ‘‘3,’’ no minimum
requirements apply to the measured external
or internal, respectively, static pressure. For
heat pumps that meet the above criterion
‘‘2,’’ test at an external static pressure that
does not cause an automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but
not less than, the same Table 3 minimum
external static pressure as was specified for
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the A (or A2) cooling mode test. Additional
test steps as described in section 3.9.1(c) of
this appendix are required if the measured
external static pressure exceeds the target
value by more than 0.03 inches of water.
3.1.4.4.2 Ducted heat pumps where the
Heating and Cooling Full-load Air Volume
Rates are different due to indoor blower
operation.
The manufacturer must specify the heating
full-load air volume rate and the instructions
for setting fan speed or controls. Calculate
target minimum external static pressure as
described in section 3.1.4.2.
a. For ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower, adjust for external
static pressure as described in section
3.1.4.2.a for cooling minimum air volume
rate.
b. For ducted heat pumps tested with
constant-air-volume indoor blowers installed,
conduct all tests that specify the heating fullload air volume rate at an external static
pressure that does not cause an automatic
shutdown of the indoor blower or air volume
rate variation QVar, defined in section
3.1.4.1.1.b, greater than 10 percent, while
being as close to, but not less than the target
minimum external static pressure. Additional
test steps as described in section 3.9.1(c) of
this appendix are required if the measured
external static pressure exceeds the target
value by more than 0.03 inches of water.
c. When testing ducted, two-capacity
northern heat pumps (see section 1.2,
Definitions), use the appropriate approach of
the above two cases for units that are tested
with an indoor blower installed. For coilonly northern heat pumps, the Heating Fullload Air Volume Rate is the lesser of the rate
specified by the manufacturer in the
installation instructions included with the
unit or 133 percent of the Cooling Full-load
Air Volume Rate. For this latter case, obtain
the Heating Full-load Air Volume Rate
regardless of the pressure drop across the
indoor coil assembly.
d. For ducted systems having multiple
indoor blowers within a single indoor
section, obtain the heating full-load air
volume rate using the same ‘‘on’’ blowers as
used for the cooling full-load air volume rate.
For systems where individual blowers
regulate the speed (as opposed to the cfm) of
the indoor blower, use the first section
3.1.4.2 equation for each blower individually.
Sum the individual blower air volume rates
to obtain the heating full-load air volume rate
for the system.
3.1.4.4.3 Ducted heating-only heat pumps.
The manufacturer must specify the Heating
Full-load Air Volume Rate.
a. For all ducted heating-only heat pumps
tested with an indoor blower installed,
except those having a constant-air-volumerate indoor blower. Conduct the following
steps only during the first test, the H1 or H12
Test.
1. Achieve the Heating Full-load Air
Volume Rate.
2. Measure the external static pressure.
3. If this pressure is equal to or greater than
the Table 3 minimum external static pressure
that applies given the heating-only heat
pump’s rated heating capacity, use the
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current air volume rate for all tests that
require the Heating Full-load Air Volume
Rate.
4. If the Table 3 minimum is not equaled
or exceeded,
4a. reduce the air volume rate and increase
the external static pressure by adjusting the
exhaust fan of the airflow measuring
apparatus until the applicable Table 3
minimum is equaled or
4b. until the measured air volume rate
equals 90 percent of the manufacturerspecified Full-load Air Volume Rate,
whichever occurs first.
5. If the conditions of step 4a occurs first,
use the step 4a reduced air volume rate for
all tests that require the Heating Full-load Air
Volume Rate.
6. If the conditions of step 4b occur first,
make an incremental change to the set-up of
the indoor blower (e.g., next highest fan
motor pin setting, next highest fan motor
speed) and repeat the evaluation process
beginning at above step 1. If the indoor
blower set-up cannot be further changed,
reduce the air volume rate until the
applicable Table 3 minimum is equaled. Use
this reduced air volume rate for all tests that
require the Heating Full-load Air Volume
Rate.
b. For ducted heating-only heat pumps that
are tested with a constant-air-volume-rate
indoor blower installed. For all tests that
specify the Heating Full-load Air Volume
Rate, obtain an external static pressure that
does not cause an automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but
not less than, the applicable Table 3
minimum. Additional test steps as described
in section 3.9.1(c) of this appendix are
required if the measured external static
pressure exceeds the target value by more
than 0.03 inches of water.
c. For ducted heating-only heat pumps that
are tested without an indoor blower installed.
For the H1 or H12 Test, (exclusively), the
pressure drop across the indoor coil assembly
must not exceed 0.30 inches of water. If this
pressure drop is exceeded, reduce the air
volume rate until the measured pressure drop
equals the specified maximum. Use this
reduced air volume rate for all tests that
require the Heating Full-load Air Volume
Rate.
3.1.4.4.4 Non-ducted heat pumps,
including non-ducted heating-only heat
pumps.
For non-ducted heat pumps, the Heating
Full-load Air Volume Rate is the air volume
rate that results during each test when the
unit operates at an external static pressure of
zero inches of water.
3.1.4.5 Heating Minimum Air Volume Rate.
3.1.4.5.1 Ducted heat pumps where the
Heating and Cooling Minimum Air Volume
Rates are the same.
a. Use the Cooling Minimum Air Volume
Rate as the Heating Minimum Air Volume
Rate for:
1. Ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower that operates at the
same airflow-control setting during both the
A1 and the H11 tests;
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2. Ducted heat pumps tested with constantair-flow indoor blowers installed that provide
the same air flow for the A1 and the H11
Tests; and
3. Ducted heat pumps that are tested
without an indoor blower installed (except
two-capacity northern heat pumps that are
tested only at low capacity cooling—see
3.1.4.4.2).
b. For heat pumps that meet the above
criteria ‘‘1’’ and ‘‘3,’’ no minimum
requirements apply to the measured external
or internal, respectively, static pressure. For
heat pumps that meet the above criterion
‘‘2,’’ test at an external static pressure that
does not cause an automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but
not less than, the same target minimum
external static pressure as was specified for
the A1 cooling mode test. Additional test
steps as described in section 3.9.1(c) of this
appendix are required if the measured
external static pressure exceeds the target
value by more than 0.03 inches of water.
3.1.4.5.2 Ducted heat pumps where the
Heating and Cooling Minimum Air Volume
Rates are different due to indoor blower
operation.
The manufacturer must specify the heating
minimum volume rate and the instructions
for setting fan speed or controls. Calculate
target minimum external static pressure as
described in section 3.1.4.2.
a. For ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower, adjust for external
static pressure as described in section
3.1.4.2.a for cooling minimum air volume
rate.
b. For ducted heat pumps tested with
constant-air-volume indoor blowers installed,
conduct all tests that specify the Heating
Minimum Air Volume Rate—(i.e., the H01,
H11, H21, and H31 Tests)—at an external
static pressure that does not cause an
automatic shutdown of the indoor blower
while being as close to, but not less thanor
air volume rate variation QVar, defined in
section 3.1.4.1.1.b, greater than 10 percent,
while being as close to, but not less than the
target minimum external static pressure.
Additional test steps as described in section
3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the
target value by more than 0.03 inches of
water.
c. For ducted two-capacity northern heat
pumps that are tested with an indoor blower
installed, use the appropriate approach of the
above two cases.
d. For ducted two-capacity heat pumps
that are tested without an indoor blower
installed, use the Cooling Minimum Air
Volume Rate as the Heating Minimum Air
Volume Rate. For ducted two-capacity
northern heat pumps that are tested without
an indoor blower installed, use the Cooling
Full-load Air Volume Rate as the Heating
Minimum Air Volume Rate. For ducted twocapacity heating-only heat pumps that are
tested without an indoor blower installed,
the Heating Minimum Air Volume Rate is the
higher of the rate specified by the
manufacturer in the test setup instructions
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69357
included with the unit or 75 percent of the
Heating Full-load Air Volume Rate. During
the laboratory tests on a coil-only system,
obtain the Heating Minimum Air Volume
Rate without regard to the pressure drop
across the indoor coil assembly.
e. For non-ducted heat pumps, the Heating
Minimum Air Volume Rate is the air volume
rate that results during each test when the
unit operates at an external static pressure of
zero inches of water and at the indoor blower
setting used at low compressor capacity (twocapacity system) or minimum compressor
speed (variable-speed system). For units
having a single-speed compressor and a
variable-speed, variable-air-volume-rate
indoor blower, use the lowest fan setting
allowed for heating.
f. For ducted systems with multiple indoor
blowers within a single indoor section,
obtain the heating minimum air volume rate
using the same ‘‘on’’ blowers as used for the
cooling minimum air volume rate. For
systems where individual blowers regulate
the speed (as opposed to the cfm) of the
indoor blower, use the first section 3.1.4.5
equation for each blower individually. Sum
the individual blower air volume rates to
obtain the heating minimum air volume rate
for the system.
3.1.4.6 Heating Intermediate Air Volume
Rate.
The manufacturer must specify the heating
intermediate air volume rate and the
instructions for setting fan speed or controls.
Calculate target minimum external static
pressure as described in section 3.1.4.2.
a. For ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower, adjust for external
static pressure as described in section
3.1.4.2.a for cooling minimum air volume
rate.
b. For ducted heat pumps tested with
constant-air-volume indoor blowers installed,
conduct the H2V Test at an external static
pressure that does not cause an automatic
shutdown of the indoor blower or air volume
rate variation QVar, defined in section
3.1.4.1.1.b, greater than 10 percent, while
being as close to, but not less than the target
minimum external static pressure. Additional
test steps as described in section 3.9.1(c) of
this appendix are required if the measured
external static pressure exceeds the target
value by more than 0.03 inches of water.
c. For non-ducted heat pumps, the Heating
Intermediate Air Volume Rate is the air
volume rate that results when the heat pump
operates at an external static pressure of zero
inches of water and at the fan speed selected
by the controls of the unit for the H2V Test
conditions.
3.1.4.7 Heating Nominal Air Volume
Rate.
The manufacturer must specify the heating
nominal air volume rate and the instructions
for setting fan speed or controls. Calculate
target minimum external static pressure as
described in section 3.1.4.2. Make
adjustments as described in section 3.14.6 for
heating intermediate air volume rate so that
the target minimum external static pressure
is met or exceeded.
3.1.5 Indoor test room requirement when
the air surrounding the indoor unit is not
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supplied from the same source as the air
entering the indoor unit.
If using a test set-up where air is ducted
directly from the air reconditioning
apparatus to the indoor coil inlet (see Figure
2, Loop Air-Enthalpy Test Method
Arrangement, of ASHRAE Standard 37–
2009), maintain the dry bulb temperature
within the test room within ±5.0 °F of the
applicable sections 3.2 and 3.6 dry bulb
temperature test condition for the air entering
the indoor unit. Dew point shall be within
2 °F of the required inlet conditions.
3.1.6 Air volume rate calculations.
For all steady-state tests and for Frost
Accumulation (H2, H21, H22, H2V) tests,
calculate the air volume rate through the
indoor coil as specified in sections 7.7.2.1
and 7.7.2.2 of ASHRAE Standard 37–2009
(incorporated by reference, see § 430.3).
When using the Outdoor Air Enthalpy
Method, follow sections 7.7.2.1 and 7.7.2.2 to
calculate the air volume rate through the
outdoor coil. To express air volume rates in
terms of standard air, use:
Where,
Ô
Vs = air volume rate of standard (dry) air, (ft3/
Ô min)da
Vmx = air volume rate of the air-water vapor
mixture, (ft3/min)mx
vn′ = specific volume of air-water vapor
mixture at the nozzle, ft3 per lbm of the
air-water vapor mixture
Wn = humidity ratio at the nozzle, lbm of
water vapor per lbm of dry air
0.075 = the density associated with standard
(dry) air, (lbm/ft3)
vn = specific volume of the dry air portion
of the mixture evaluated at the dry-bulb
temperature, vapor content, and
barometric pressure existing at the
nozzle, ft3 per lbm of dry air.
(Note: In the first printing of ASHRAE
Standard 37–2009, the second IP equation for
Qmi should read,
ducted heating-only heat pumps, conduct the
H1 or H12 Test first to establish the Heating
Full-load Air Volume Rate. When conducting
an cyclic test, always conduct it immediately
after the steady-state test that requires the
same test conditions. For variable-speed
systems, the first test using the Cooling
Minimum Air Volume Rate should precede
the EV Test, and the first test using the
Heating Minimum Air Volume Rate must
precede the H2V Test. The test laboratory
makes all other decisions on the test
sequence.
3.1.8 Requirement for the air temperature
distribution leaving the indoor coil.
For at least the first cooling mode test and
the first heating mode test, monitor the
temperature distribution of the air leaving the
indoor coil using the grid of individual
sensors described in sections 2.5 and 2.5.4.
For the 30-minute data collection interval
used to determine capacity, the maximum
spread among the outlet dry bulb
temperatures from any data sampling must
not exceed 1.5 °F. Install the mixing devices
described in section 2.5.4.2 to minimize the
temperature spread.
3.1.9 Requirement for the air temperature
distribution entering the outdoor coil.
Monitor the temperatures of the air
entering the outdoor coil using the grid of
temperature sensors described in section
2.11. For the 30-minute data collection
interval used to determine capacity, the
maximum difference between dry bulb
temperatures measured at any of these
locations must not exceed 1.5 °F.
3.1.10 Control of auxiliary resistive
heating elements.
Except as noted, disable heat pump
resistance elements used for heating indoor
air at all times, including during defrost
cycles and if they are normally regulated by
a heat comfort controller. For heat pumps
equipped with a heat comfort controller,
enable the heat pump resistance elements
only during the below-described, short test.
For single-speed heat pumps covered under
section 3.6.1, the short test follows the H1 or,
if conducted, the H1C Test. For two-capacity
heat pumps and heat pumps covered under
section 3.6.2, the short test follows the H12
Test. Set the heat comfort controller to
provide the maximum supply air
temperature. With the heat pump operating
and while maintaining the Heating Full-load
Air Volume Rate, measure the temperature of
the air leaving the indoor-side beginning 5
minutes after activating the heat comfort
controller. Sample the outlet dry-bulb
temperature at regular intervals that span 5
minutes or less. Collect data for 10 minutes,
obtaining at least 3 samples. Calculate the
average outlet temperature over the 10minute interval, TCC.
3.2 Cooling mode tests for different types
of air conditioners and heat pumps.
3.2.1 Tests for a unit having a singlespeed compressor, or a multi-circuit system,
that is tested with a fixed-speed indoor
blower installed, with a constant-air-volumerate indoor blower installed, or with no
indoor blower installed.
Conduct two steady-state wet coil tests, the
A and B Tests. Use the two dry-coil tests, the
steady-state C Test and the cyclic D Test, to
determine the cooling mode cyclic
degradation coefficient, CDc. If testing
outdoor units of central air conditioners or
heat pumps that are not sold with indoor
units, assign CDc the default value of 0.2.
Table 4 specifies test conditions for these
four tests.
3.1.7 Test sequence.
Manufacturers may optionally operate the
equipment under test for a ‘‘break-in’’ period,
not to exceed 20 hours, prior to conducting
the test method specified in this section. A
manufacturer who elects to use this optional
compressor break-in period in its
certification testing should record this
information (including the duration) in the
test data underlying the certified ratings that
are required to be maintained under 10 CFR
429.71. When testing a ducted unit (except if
a heating-only heat pump), conduct the A or
A2 Test first to establish the Cooling Fullload Air Volume Rate. For ducted heat
pumps where the Heating and Cooling Fullload Air Volume Rates are different, make the
first heating mode test one that requires the
Heating Full-load Air Volume Rate. For
TABLE 4—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A FIXED-SPEED
INDOOR BLOWER, A CONSTANT AIR VOLUME RATE INDOOR BLOWER, OR NO INDOOR BLOWER
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Dry bulb
A Test—required (steady, wet coil) .........
B Test—required (steady, wet coil) .........
C Test—required (steady, dry coil) ..........
D Test—required (cyclic, dry coil) ............
Air entering outdoor unit temperature (°F)
Wet bulb
80
80
80
80
Dry bulb
67
67
(3)
(3)
Cooling air volume rate
Wet bulb
95
82
82
82
175
165
........................
........................
Cooling full-load.2
Cooling full-load.2
Cooling full-load.2
( 4)
1 The
specified test condition only applies if the unit rejects condensate to the outdoor coil.
in section 3.1.4.1.
3 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wetbulb temperature of 57 °F or less be used.)
2 Defined
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Air entering indoor unit temperature (°F)
Test description
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4 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C Test.
Conduct four steady-state wet coil tests:
The A2, A1, B2, and B1 Tests. Use the two drycoil tests, the steady-state C1 Test and the d
D1 Test, to determine the cooling mode cyclic
degradation coefficient, CDc.
3.2.2.2 Indoor blower capacity
modulation based on adjusting the sensible
to total (S/T) cooling capacity ratio.
3.2.2 Tests for a unit having a singlespeed compressor where the indoor section
uses a single variable-speed variable-airvolume rate indoor blower or multiple
blowers.
3.2.2.1 Indoor blower capacity
modulation that correlates with the outdoor
dry bulb temperature or systems with a single
indoor coil but multiple blowers.
The testing requirements are the same as
specified in section 3.2.1 and Table 4. Use a
Cooling Full-load Air Volume Rate that
represents a normal installation. If
performed, conduct the steady-state C Test
and the cyclic D Test with the unit operating
in the same S/T capacity control mode as
used for the B Test.
TABLE 5—COOLING MODE TEST CONDITIONS FOR UNITS WITH A SINGLE-SPEED COMPRESSOR THAT MEET THE SECTION
3.2.2.1 INDOOR UNIT REQUIREMENTS
Air entering indoor unit
temperature (°F)
Test description
Dry bulb
A2 Test—required (steady, wet coil) ........
A1 Test—required (steady, wet coil) ........
B2 Test—required (steady, wet coil) ........
B1 Test—required (steady, wet coil) ........
C1 Test 4—required (steady, dry coil) ......
D1 Test 4—required (cyclic, dry coil) ........
Air entering outdoor unit
temperature (°F)
Wet bulb
80
80
80
80
80
80
Dry bulb
67
67
67
67
(4)
(4)
Cooling air volume rate
Wet bulb
1 75
95
95
82
82
82
82
1 75
1 65
1 65
........................
(5)
Cooling
Cooling
Cooling
Cooling
Cooling
full-load.2
minimum.3
full-load.2
minimum.3
minimum.3
1 The
specified test condition only applies if the unit rejects condensate to the outdoor coil.
in section 3.1.4.1.
3 Defined in section 3.1.4.2.
4 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wetbulb temperature of 57 °F or less be used.)
5 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C1 Test.
2 Defined
3.2.3 Tests for a unit having a twocapacity compressor. (see section 1.2,
Definitions)
a. Conduct four steady-state wet coil tests:
The A2, B2, B1, and F1 Tests. Use the two drycoil tests, the steady-state C1 Test and the
cyclic D1 Test, to determine the cooling-mode
cyclic-degradation coefficient, CDc. Table 6
specifies test conditions for these six tests.
b. For units having a variable speed indoor
blower that is modulated to adjust the
sensible to total (S/T) cooling capacity ratio,
use Cooling Full-load and Cooling Minimum
Air Volume Rates that represent a normal
installation. Additionally, if conducting the
dry-coil tests, operate the unit in the same S/
T capacity control mode as used for the B1
Test.
c. Test two-capacity, northern heat pumps
(see section 1.2, Definitions) in the same way
as a single speed heat pump with the unit
operating exclusively at low compressor
capacity (see section 3.2.1 and Table 4).
d. If a two-capacity air conditioner or heat
pump locks out low-capacity operation at
higher outdoor temperatures, then use the
two dry-coil tests, the steady-state C2 Test
and the cyclic D2 Test, to determine the
cooling-mode cyclic-degradation coefficient
that only applies to on/off cycling from high
capacity, CDc(k=2). The default CDc(k=2) is
the same value as determined or assigned for
the low-capacity cyclic-degradation
coefficient, CDc [or equivalently, CDc(k=1)].
TABLE 6—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR
Air entering indoor unit
temperature (°F)
Test description
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Dry bulb
A2 Test—required (steady, wet
coil).
B2 Test—required (steady, wet
coil).
B1 Test—required (steady, wet
coil).
C2 Test—required (steady, drycoil).
D2 Test—required (cyclic, dry-coil)
C1 Test—required (steady, drycoil).
D1 Test—required (cyclic, dry-coil)
F1 Test—required (steady, wet
coil).
Air entering outdoor unit
temperature (°F)
Wet bulb
Dry bulb
Compressor
capacity
Cooling air
volume rate
Wet bulb
80
67
95
1 75
...................
High ...................
80
67
82
1 65
...................
High ...................
80
67
82
1 65
...................
Low ....................
80
( 4)
82
High ..................
80
80
(4)
( 4)
82
82
High ..................
Low ...................
80
80
(4)
67
82
67
Low ...................
153.5 .................
Cooling FullLoad2.
(5) ......................
Cooling Minimum3.
(6) ......................
Low ....................
1 The
Cooling FullLoad.2
Cooling FullLoad. 2
Cooling Minimum. 3
Cooling Minimum.3
specified test condition only applies if the unit rejects condensate to the outdoor coil.
in section 3.1.4.1.
3 Defined in section 3.1.4.2.
4 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air
wet-bulb temperature of 57 °F or less.
2 Defined
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5 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the C2 Test.
6 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the C1 Test.
3.2.4 Tests for a unit having a variablespeed compressor.
a. Conduct five steady-state wet coil tests:
The A2, EV, B2, B1, and F1 Tests. Use the two
dry-coil tests, the steady-state G1 Test and the
cyclic I1 Test, to determine the cooling mode
cyclic degradation coefficient, CDc. Table 7
specifies test conditions for these seven tests.
Determine the intermediate compressor
speed cited in Table 7 using:
where a tolerance of plus 5 percent or the
next higher inverter frequency step from
that calculated is allowed.
b. For units that modulate the indoor
blower speed to adjust the sensible to total
(S/T) cooling capacity ratio, use Cooling Fullload, Cooling Intermediate, and Cooling
Minimum Air Volume Rates that represent a
normal installation. Additionally, if
conducting the dry-coil tests, operate the unit
in the same S/T capacity control mode as
used for the F1 Test.
c. For multiple-split air conditioners and
heat pumps (except where noted), the
following procedures supersede the above
requirements: For all Table 7 tests specified
for a minimum compressor speed, at least
one indoor unit must be turned off. The
manufacturer shall designate the particular
indoor unit(s) that is turned off. The
manufacturer must also specify the
compressor speed used for the Table 7 EV
Test, a cooling-mode intermediate
compressor speed that falls within 1⁄4 and 3⁄4
of the difference between the maximum and
minimum cooling-mode speeds. The
manufacturer should prescribe an
intermediate speed that is expected to yield
the highest EER for the given EV Test
conditions and bracketed compressor speed
range. The manufacturer can designate that
one or more indoor units are turned off for
the EV Test.
TABLE 7—COOLING MODE TEST CONDITION FOR UNITS HAVING A VARIABLE-SPEED COMPRESSOR
Air entering indoor unit
temperature (°F)
Test description
Dry bulb
A2 Test—required (steady, wet
coil).
B2 Test—required (steady, wet
coil).
EV Test—required (steady, wet
coil).
B1 Test—required (steady, wet
coil).
F1 Test—required (steady, wet
coil).
G1 Test 5—required (steady, drycoil).
I1 Test 5—required (cyclic, dry-coil)
Air entering outdoor unit
temperature (°F)
Wet bulb
80
Dry bulb
Compressor
speed
Wet bulb
95
67
Cooling air
volume rate
1 75
...................
Maximum ...........
...................
Maximum ...........
80
67
82
1 65
80
67
87
1 69
...................
Intermediate ......
...................
Minimum ............
80
67
82
1 65
80
67
67
1 53.5
80
( 6)
67
Minimum ...........
80
(6)
67
Minimum ...........
................
Minimum ............
Cooling FullLoad.2
Cooling FullLoad.2
Cooling Intermediate.3
Cooling Minimum.4
Cooling Minimum.4
Cooling Minimum 4.
(6).
1 The
3.2.5 Cooling mode tests for northern heat
pumps with triple-capacity compressors.
Test triple-capacity, northern heat pumps
for the cooling mode in the same way as
specified in section 3.2.3 for units having a
two-capacity compressor.
3.2.6 Tests for an air conditioner or heat
pump having a single indoor unit having
multiple blowers and offering two stages of
compressor modulation.
Conduct the cooling mode tests specified
in section 3.2.3.
3.3 Test procedures for steady-state wet
coil cooling mode tests (the A, A2, A1, B, B2,
B1, EV, and F1 Tests).
a. For the pretest interval, operate the test
room reconditioning apparatus and the unit
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to be tested until maintaining equilibrium
conditions for at least 30 minutes at the
specified section 3.2 test conditions. Use the
exhaust fan of the airflow measuring
apparatus and, if installed, the indoor blower
of the test unit to obtain and then maintain
the indoor air volume rate and/or external
static pressure specified for the particular
test. Continuously record (see section 1.2,
Definitions):
(1) The dry-bulb temperature of the air
entering the indoor coil,
(2) The water vapor content of the air
entering the indoor coil,
(3) The dry-bulb temperature of the air
entering the outdoor coil, and
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(4) For the section 2.2.4 cases where its
control is required, the water vapor content
of the air entering the outdoor coil.
Refer to section 3.11 for additional
requirements that depend on the selected
secondary test method.
b. After satisfying the pretest equilibrium
requirements, make the measurements
specified in Table 3 of ASHRAE Standard
37–2009 for the Indoor Air Enthalpy method
and the user-selected secondary method.
Make said Table 3 measurements at equal
intervals that span 5 minutes or less.
Continue data sampling until reaching a 30minute period (e.g., four consecutive 10minute samples) where the test tolerances
specified in Table 8 are satisfied. For those
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specified test condition only applies if the unit rejects condensate to the outdoor coil.
2 Defined in section 3.1.4.1.
3 Defined in section 3.1.4.3.
4 Defined in section 3.1.4.2.
5 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air
wet bulb temperature of 57 °F or less.
6 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the G1 Test.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
continuously recorded parameters, use the
entire data set from the 30-minute interval to
evaluate Table 8 compliance. Determine the
average electrical power consumption of the
air conditioner or heat pump over the same
30-minute interval.
c. Calculate indoor-side total cooling
capacity and sensible cooling capacity as
specified in sections 7.3.3.1 and 7.3.3.3 of
ASHRAE Standard 37–2009 (incorporated by
reference, see § 430.3). Do not adjust the
parameters used in calculating capacity for
the permitted variations in test conditions.
Evaluate air enthalpies based on the
measured barometric pressure. Use the
values of the specific heat of air given in
section 7.3.3.1 for calculation of the sensible
cooling capacities. Assign the average total
space cooling capacity, average sensible
cooling capacity, and electrical power
consumption over the 30-minute data
˙
collection interval to the variables Qck(T),
˙
˙
Qsck(T) and Eck(T), respectively. For these
three variables, replace the ‘‘T’’ with the
nominal outdoor temperature at which the
test was conducted. The superscript k is used
only when testing multi-capacity units. Use
the superscript k=2 to denote a test with the
unit operating at high capacity or maximum
speed, k=1 to denote low capacity or
minimum speed, and k=v to denote the
intermediate speed.
d. For units tested without an indoor
˙
blower installed, decrease Qck(T) by
69361
˙
where Vs is the average measured indoor air
volume rate expressed in units of cubic feet
per minute of standard air (scfm).
TABLE 8—TEST OPERATING AND TEST CONDITION TOLERANCES FOR SECTION 3.3 STEADY-STATE WET COIL COOLING
MODE TESTS AND SECTION 3.4 DRY COIL COOLING MODE TESTS
Test operating
tolerance 1
Indoor dry-bulb, °F ...................................................................................................................................................
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
Indoor wet-bulb, °F ..................................................................................................................................................
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
Outdoor dry-bulb, °F ................................................................................................................................................
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
Outdoor wet-bulb, °F ...............................................................................................................................................
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
External resistance to airflow, inches of water ........................................................................................................
Electrical voltage, % of rdg. .....................................................................................................................................
Nozzle pressure drop, % of rdg. .............................................................................................................................
Test condition
tolerance 1
........................
2.0
2.0
........................
1.0
2 1.0
........................
2.0
3 2.0
........................
1.0
3 1.0
0.12
2.0
8.0
........................
0.5
........................
........................
2 0.3
........................
........................
0.5
........................
........................
4 0.3
........................
5 0.02
1.5
........................
1 See
section 1.2, Definitions.
applies during wet coil tests; does not apply during steady-state, dry coil cooling mode tests.
applies when using the Outdoor Air Enthalpy Method.
4 Only applies during wet coil cooling mode tests where the unit rejects condensate to the outdoor coil.
5 Only applies when testing non-ducted units.
2 Only
3 Only
the corresponding external static pressure
(DP1) during or immediately following the 30minute interval used for determining
capacity.
2. After completing the 30-minute interval
and while maintaining the same test
conditions, adjust the exhaust fan of the
airflow measuring apparatus until the
external static pressure increases to
approximately DP1 + (DP1 ¥ DPmin).
3. After re-establishing steady readings of
the fan motor power and external static
pressure, determine average values for the
˙
indoor blower power (Efan,2) and the external
static pressure (DP2) by making
measurements over a 5-minute interval.
4. Approximate the average power
consumption of the indoor blower motor at
DPmin using linear extrapolation:
5. Increase the total space cooling capacity,
˙
˙
˙
Qck(T), by the quantity (Efan,1 ¥ Efan,min),
when expressed on a Btu/h basis. Decrease
˙
the total electrical power, Eck(T), by the same
fan power difference, now expressed in
watts.
3.4 Test procedures for the steady-state
dry-coil cooling-mode tests (the C, C1, C2, and
G1 Tests).
a. Except for the modifications noted in
this section, conduct the steady-state dry coil
cooling mode tests as specified in section 3.3
for wet coil tests. Prior to recording data
during the steady-state dry coil test, operate
the unit at least one hour after achieving dry
coil conditions. Drain the drain pan and plug
the drain opening. Thereafter, the drain pan
should remain completely dry.
b. Denote the resulting total space cooling
capacity and electrical power derived from
˙
˙
the test as Qss,dry and Ess,dry.With regard to a
˙
section 3.3 deviation, do not adjust Qss,dry for
duct losses (i.e., do not apply section 7.3.3.3
of ASHRAE Standard 37–2009). In preparing
for the section 3.5 cyclic tests, record the
´
average indoor-side air volume rate, V,
specific heat of the air, Cp,a (expressed on
dry air basis), specific volume of the air at
the nozzles, v′n, humidity ratio at the nozzles,
Wn, and either pressure difference or velocity
pressure for the flow nozzles. For units
having a variable-speed indoor fan (that
provides either a constant or variable air
volume rate) that will or may be tested
during the cyclic dry coil cooling mode test
with the indoor fan turned off (see section
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e. For air conditioners and heat pumps
having a constant-air-volume-rate indoor
blower, the five additional steps listed below
are required if the average of the measured
external static pressures exceeds the
applicable sections 3.1.4 minimum (or target)
external static pressure (DPmin) by 0.03 inches
of water or more.
1. Measure the average power consumption
˙
of the indoor blower motor (Efan,1) and record
69362
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
among the regularly sampled data. Beginning
at the start of the 30-minute data collection
period, measure and compute the indoor-side
air dry-bulb temperature difference using
both sets of instrumentation, DT (Set SS) and
DT (Set CYC), for each equally spaced data
sample. If using a consistent data sampling
rate that is less than 1 minute, calculate and
record minutely averages for the two
temperature differences. If using a consistent
sampling rate of one minute or more,
calculate and record the two temperature
differences from each data sample. After
having recorded the seventh (i=7) set of
temperature differences, calculate the
following ratio using the first seven sets of
values:
Each time a subsequent set of temperature
differences is recorded (if sampling more
frequently than every 5 minutes), calculate
FCD using the most recent seven sets of
values. Continue these calculations until the
30-minute period is completed or until a
value for FCD is calculated that falls outside
the allowable range of 0.94–1.06. If the latter
occurs, immediately suspend the test and
identify the cause for the disparity in the two
temperature difference measurements.
Recalibration of one or both sets of
instrumentation may be required. If all the
values for FCD are within the allowable range,
save the final value of the ratio from the 30minute test as FCD*. If the temperature
sensors used to provide the primary
measurement of the indoor-side dry bulb
temperature difference during the steadystate dry-coil test and the subsequent cyclic
dry-coil test are the same, set FCD*= 1.
3.5 Test procedures for the cyclic dry-coil
cooling-mode tests (the D, D1, D2, and I1
Tests).
a. After completing the steady-state drycoil test, remove the Outdoor Air Enthalpy
method test apparatus, if connected, and
begin manual OFF/ON cycling of the unit’s
compressor. The test set-up should otherwise
be identical to the set-up used during the
steady-state dry coil test. When testing heat
pumps, leave the reversing valve during the
compressor OFF cycles in the same position
as used for the compressor ON cycles, unless
automatically changed by the controls of the
unit. For units having a variable-speed
indoor blower, the manufacturer has the
option of electing at the outset whether to
conduct the cyclic test with the indoor
blower enabled or disabled. Always revert to
testing with the indoor blower disabled if
cyclic testing with the fan enabled is
unsuccessful.
b. For units having a single-speed or twocapacity compressor, cycle the compressor
OFF for 24 minutes and then ON for 6
minutes (Dtcyc,dry = 0.5 hours). For units
having a variable-speed compressor, cycle
the compressor OFF for 48 minutes and then
ON for 12 minutes (Dtcyc,dry = 1.0 hours).
Repeat the OFF/ON compressor cycling
pattern until the test is completed. Allow the
controls of the unit to regulate cycling of the
outdoor fan. If an upturned duct is used,
measure the dry-bulb temperature at the inlet
of the device at least once every minute and
ensure that its test operating tolerance is
within 1.0 °F for each compressor OFF
period.
c. Sections 3.5.1 and 3.5.2 specify airflow
requirements through the indoor coil of
ducted and non-ducted systems, respectively.
In all cases, use the exhaust fan of the airflow
measuring apparatus (covered under section
2.6) along with the indoor blower of the unit,
if installed and operating, to approximate a
step response in the indoor coil airflow.
Regulate the exhaust fan to quickly obtain
and then maintain the flow nozzle static
pressure difference or velocity pressure at the
same value as was measured during the
steady-state dry coil test. The pressure
difference or velocity pressure should be
within 2 percent of the value from the steadystate dry coil test within 15 seconds after
airflow initiation. For units having a variablespeed indoor blower that ramps when
cycling on and/or off, use the exhaust fan of
the airflow measuring apparatus to impose a
step response that begins at the initiation of
ramp up and ends at the termination of ramp
down.
d. For units having a variable-speed indoor
blower, conduct the cyclic dry coil test using
the pull-thru approach described below if
any of the following occur when testing with
the fan operating:
(1) The test unit automatically cycles off;
(2) Its blower motor reverses; or
(3) The unit operates for more than 30
seconds at an external static pressure that is
0.1 inches of water or more higher than the
value measured during the prior steady-state
test.
For the pull-thru approach, disable the
indoor blower and use the exhaust fan of the
airflow measuring apparatus to generate the
specified flow nozzles static pressure
difference or velocity pressure. If the exhaust
fan cannot deliver the required pressure
difference because of resistance created by
the unpowered blower, temporarily remove
the blower.
e. Conduct a minimum of six complete
compressor OFF/ON cycles for a unit with a
single-speed or two-speed compressor, and a
minimum of five complete compressor OFF/
ON cycles for a unit with a variable speed
compressor. The first three cycles for a unit
with a single-speed compressor or two-speed
compressor and the first two cycles for a unit
with a unit with a variable speed compressor
are the warm-up period—the later cycles are
called the active cycles. Calculate the
degradation coefficient CD for each complete
active cycle if the test tolerances given in
Table 9 are satisfied. If the average CD for the
first three active cycles is within 0.02 of the
average CD for the first two active cycles, use
the average CD of the three active cycles as
the final result. If these averages differ by
more than 0.02, continue the test to get CD
for the fourth cycle. If the average CD of the
last three cycles is lower than or no more
than 0.02 greater than the average CD of the
first three cycles, use the average CD of all
four active cycles as the final result.
Otherwise, continue the test with a fifth
cycle. If the average CD of the last three
cycles is 0.02 higher than the average for the
previous three cycles, use the default CD,
otherwise use the average CD of all five active
cycles. If the test tolerances given in Table 9
are not satisfied, use default CD value. The
default CD value for cooling is 0.2.
f. With regard to the Table 9 parameters,
continuously record the dry-bulb
temperature of the air entering the indoor
and outdoor coils during periods when air
flows through the respective coils. Sample
the water vapor content of the indoor coil
inlet air at least every 2 minutes during
periods when air flows through the coil.
Record external static pressure and the air
volume rate indicator (either nozzle pressure
difference or velocity pressure) at least every
minute during the interval that air flows
through the indoor coil. (These regular
measurements of the airflow rate indicator
are in addition to the required measurement
at 15 seconds after flow initiation.) Sample
the electrical voltage at least every 2 minutes
beginning 30 seconds after compressor startup. Continue until the compressor, the
outdoor fan, and the indoor blower (if it is
installed and operating) cycle off.
g. For ducted units, continuously record
the dry-bulb temperature of the air entering
(as noted above) and leaving the indoor coil.
Or if using a thermopile, continuously record
the difference between these two
temperatures during the interval that air
flows through the indoor coil. For nonducted units, make the same dry-bulb
temperature measurements beginning when
the compressor cycles on and ending when
indoor coil airflow ceases.
h. Integrate the electrical power over
complete cycles of length Dtcyc,dry. For ducted
units tested with an indoor blower installed
and operating, integrate electrical power from
indoor blower OFF to indoor blower OFF.
For all other ducted units and for non-ducted
units, integrate electrical power from
compressor OFF to compressor OFF. (Some
cyclic tests will use the same data collection
intervals to determine the electrical energy
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3.5), include the electrical power used by the
indoor fan motor among the recorded
parameters from the 30-minute test.
c. If the temperature sensors used to
provide the primary measurement of the
indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the
subsequent cyclic dry-coil test are different,
include measurements of the latter sensors
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
and the total space cooling. For other units,
terminate data collection used to determine
the electrical energy before terminating data
69363
collection used to determine total space
cooling.)
TABLE 9—TEST OPERATING AND TEST CONDITION TOLERANCES FOR CYCLIC DRY COIL COOLING MODE TESTS
Test operating
tolerance 1
Indoor entering dry-bulb temperature 2, °F ..............................................................................................................
Indoor entering wet-bulb temperature, °F ...............................................................................................................
Outdoor entering dry-bulb temperature 2, °F ...........................................................................................................
External resistance to airflow 2, inches of water .....................................................................................................
Airflow nozzle pressure difference or velocity pressure 2, % of reading .................................................................
Electrical voltage 5, % of rdg. ..................................................................................................................................
Test condition
tolerance 1
2.0
........................
2.0
0.12
8.0
2.0
0.5
(3)
0.5
........................
42.0
1.5
1 See
section 1.2, Definitions.
during the interval that air flows through the indoor (outdoor) coil except for the first 30 seconds after flow initiation. For units having a
variable-speed indoor blower that ramps, the tolerances listed for the external resistance to airflow apply from 30 seconds after achieving full
speed until ramp down begins.
3 Shall at no time exceed a wet-bulb temperature that results in condensate forming on the indoor coil.
4 The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state dry coil test.
5 Applies during the interval when at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are operating except for the first 30 seconds after compressor start-up.
2 Applies
the total space cooling delivered, qcyc,dry, in
units of Btu using,
The automatic controls that are normally
installed with the test unit must govern the
OFF/ON cycling of the air moving equipment
on the indoor side (exhaust fan of the airflow
measuring apparatus and, if installed, the
indoor blower of the test unit). For example,
for ducted units tested without an indoor
blower installed but rated based on using a
fan time delay relay, control the indoor coil
airflow according to the rated ON and/or OFF
delays provided by the relay. For ducted
units having a variable-speed indoor blower
that has been disabled (and possibly
removed), start and stop the indoor airflow
at the same instances as if the fan were
enabled. For all other ducted units tested
without an indoor blower installed, cycle the
indoor coil airflow in unison with the cycling
of the compressor. If air damper boxes are
used, close them on the inlet and outlet side
during the OFF period. Airflow through the
indoor coil should stop within 3 seconds
after the automatic controls of the test unit
(act to) de-energize the indoor blower. For
ducted units tested without an indoor blower
installed (excluding the special case where a
variable-speed fan is temporarily removed),
increase ecyc,dry by the quantity,
Ô
where Vs is the average indoor air volume
rate from the section 3.4 dry coil steady-state
test and is expressed in units of cubic feet per
minute of standard air (scfm). For units
having a variable-speed indoor blower that is
disabled during the cyclic test, increase
ecyc,dry and decrease qcyc,dry based on:
a. The product of [t2 ¥ t1] and the indoor
blower power measured during or following
the dry coil steady-state test; or,
b. The following algorithm if the indoor
blower ramps its speed when cycling.
1. Measure the electrical power consumed
by the variable-speed indoor blower at a
minimum of three operating conditions: At
the speed/air volume rate/external static
pressure that was measured during the
steady-state test, at operating conditions
associated with the midpoint of the ramp-up
interval, and at conditions associated with
the midpoint of the ramp-down interval. For
these measurements, the tolerances on the
airflow volume or the external static pressure
are the same as required for the section 3.4
steady-state test.
2. For each case, determine the fan power
from measurements made over a minimum of
5 minutes.
3. Approximate the electrical energy
consumption of the indoor blower if it had
operated during the cyclic test using all three
power measurements. Assume a linear
profile during the ramp intervals. The
manufacturer must provide the durations of
the ramp-up and ramp-down intervals. If the
test setup instructions included with the unit
by the manufacturer specifies a ramp interval
that exceeds 45 seconds, use a 45-second
ramp interval nonetheless when estimating
the fan energy.
3.5.2 Procedures when testing nonducted systems.
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electrical energy consumption as ecyc,dry and
express it in units of watt-hours. Calculate
where Ô, Cp,a, vn′ (or vn), Wn, and FCD* are
v
the values recorded during the section 3.4
dry coil steady-state test and
Tal(t) = dry bulb temperature of the air
entering the indoor coil at time t, °F.
Ta2(t) = dry bulb temperature of the air
leaving the indoor coil at time t, °F.
t1 = for ducted units, the elapsed time
when airflow is initiated through the indoor
coil; for non-ducted units, the elapsed time
when the compressor is cycled on, hr.
t2 = the elapsed time when indoor coil
airflow ceases, hr.
3.5.1 Procedures when testing ducted
systems.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
i. If the Table 9 tolerances are satisfied over
the complete cycle, record the measured
69364
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
Do not use airflow prevention devices
when conducting cyclic tests on non-ducted
units. Until the last OFF/ON compressor
cycle, airflow through the indoor coil must
cycle off and on in unison with the
compressor. For the last OFF/ON compressor
cycle—the one used to determine ecyc,dry and
qcyc,dry—use the exhaust fan of the airflow
measuring apparatus and the indoor blower
of the test unit to have indoor airflow start
3 minutes prior to compressor cut-on and
end three minutes after compressor cutoff.
Subtract the electrical energy used by the
indoor blower during the 3 minutes prior to
compressor cut-on from the integrated
electrical energy, ecyc,dry. Add the electrical
energy used by the indoor blower during the
3 minutes after compressor cutoff to the
integrated cooling capacity, qcyc,dry. For the
case where the non-ducted unit uses a
variable-speed indoor blower which is
disabled during the cyclic test, correct ecyc,dry
and qcyc,dry using the same approach as
prescribed in section 3.5.1 for ducted units
having a disabled variable-speed indoor
blower.
3.5.3 Cooling-mode cyclic-degradation
coefficient calculation.
Use the two dry-coil tests to determine the
cooling-mode cyclic-degradation coefficient,
CDc. Append ‘‘(k=2)’’ to the coefficient if it
corresponds to a two-capacity unit cycling at
high capacity. The default value for twocapacity units cycling at high capacity,
however, is the low-capacity coefficient, i.e.,
CDc(k=2) = CDc. Evaluate CDc using the above
results and those from the section 3.4 drycoil steady-state test.
the average energy efficiency ratio during the
cyclic dry coil cooling mode test, Btu/W·h
the average energy efficiency ratio during the
steady-state dry coil cooling mode test, Btu/
W·h
the cooling load factor dimensionless
Round the calculated value for CDc to the
nearest 0.01. If CDc is negative, then set it
equal to zero.
3.6 Heating mode tests for different types
of heat pumps, including heating-only heat
pumps.
3.6.1 Tests for a heat pump having a
single-speed compressor that is tested with a
fixed speed indoor blower installed, with a
constant-air-volume-rate indoor blower
installed, or with no indoor blower installed.
Conduct the High Temperature Cyclic (H1C)
Test to determine the heating mode cyclicdegradation coefficient, CDh. Test conditions
for the four tests are specified in Table 10.
TABLE 10—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A FIXED-SPEED
INDOOR BLOWER, A CONSTANT AIR VOLUME RATE INDOOR BLOWER, OR NO INDOOR BLOWER
Air entering indoor unit
temperature (°F)
Test description
Dry bulb
H1 Test (required, steady) ....................................
H1C Test (required, cyclic) ...................................
H2 Test (required) ................................................
H3 Test (required, steady) ....................................
Wet bulb
70
70
70
70
Air entering outdoor unit
temperature (°F)
Dry bulb
60(max)
60(max)
60(max)
60(max)
Heating air volume rate
Wet bulb
47
47
35
17
43
43
33
15
Heating Full-load.1
(2).
Heating Full-load.1
Heating Full-load.1
1 Defined
in section 3.1.4.4.
the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the H1 Test.
2 Maintain
Tests (H12 and H11), one Frost Accumulation
Test (H22), and two Low Temperature Tests
(H32 and H31). Conducting an additional
Frost Accumulation Test (H21) is optional.
Conduct the High Temperature Cyclic (H1C1)
Test to determine the heating mode cyclicdegradation coefficient, CDh. Test conditions
for the seven tests are specified in Table 11.
If the optional H21 Test is not performed, use
the following equations to approximate the
capacity and electrical power of the heat
pump at the H21 test conditions:
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3.6.2 Tests for a heat pump having a
single-speed compressor and a single indoor
unit having either (1) a variable speed,
variable-air-rate indoor blower whose
capacity modulation correlates with outdoor
dry bulb temperature or (2) multiple blowers.
Conduct five tests: Two High Temperature
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where,
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Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
˙
˙
˙
The quantities Qhk=2(47), Ehk=2(47), Qhk=1(47),
˙
and Ehk=1(47) are determined from the H12
and H11 Tests and evaluated as specified in
˙
section 3.7; the quantities Qhk=2(35) and
˙
Ehk=2(35) are determined from the H22 Test
and evaluated as specified in section 3.9; and
˙
˙
the quantities Qhk=2(17), Ehk=2(17), Qhk=1(17),
˙
and Ehk=1(17), are determined from the H32
and H31 Tests and evaluated as specified in
section 3.10.
TABLE 11—HEATING MODE TEST CONDITIONS FOR UNITS WITH A SINGLE-SPEED COMPRESSOR THAT MEET THE SECTION
3.6.2 INDOOR UNIT REQUIREMENTS
Air entering indoor unit
temperature (°F)
Test description
Dry bulb
H12 Test (required, steady) ..................................
H11 Test (required, steady) ..................................
H1C1 Test (required, cyclic) .................................
H22 Test (required) ...............................................
H21 Test (optional) ................................................
H32 Test (required, steady) ..................................
H31 Test (required, steady) ..................................
Air entering outdoor unit
temperature (°F)
Wet bulb
70
70
70
70
70
70
70
Dry bulb
60(max)
60(max)
60(max)
60(max)
60(max)
60(max)
60(max)
Heating air volume rate
Wet bulb
47
47
47
35
35
17
17
43
43
43
33
33
15
15
Heating
Heating
(3)
Heating
Heating
Heating
Heating
Full-load.1
Minimum.2
Full-load.1
Minimum.2
Full-load.1
Minimum.2
1 Defined
in section 3.1.4.4.
in section 3.1.4.5.
3 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the H11 Test.
2 Defined
3.6.3 Tests for a heat pump having a twocapacity compressor (see section 1.2,
Definitions), including two-capacity,
northern heat pumps (see section 1.2,
Definitions).
a. Conduct one Maximum Temperature
Test (H01), two High Temperature Tests
(H12and H11), one Frost Accumulation Test
(H22), and one Low Temperature Test (H32).
Conduct an additional Frost Accumulation
Test (H21) and Low Temperature Test (H31)
if both of the following conditions exist:
1. Knowledge of the heat pump’s capacity
and electrical power at low compressor
capacity for outdoor temperatures of 37 °F
and less is needed to complete the section
4.2.3 seasonal performance calculations; and
2. The heat pump’s controls allow lowcapacity operation at outdoor temperatures of
37 °F and less.
If the above two conditions are met, an
alternative to conducting the H21 Frost
Accumulation is to use the following
equations to approximate the capacity and
electrical power:
˙
Determine the quantities Qhk=1 (47) and
˙
Ehk=1 (47) from the H11 Test and evaluate
them according to Section 3.7. Determine the
˙
˙
quantities Qhk=1 (17) and Ehk=1 (17) from the
H31 Test and evaluate them according to
Section 3.10.
b. Conduct the High Temperature Cyclic
Test (H1C1) to determine the heating mode
cyclic-degradation coefficient, CDh. If a twocapacity heat pump locks out low capacity
operation at lower outdoor temperatures,
conduct the High Temperature Cyclic Test
(H1C2) to determine the high-capacity
heating mode cyclic-degradation coefficient,
CDh (k=2). The default CDh (k=2) is the same
value as determined or assigned for the lowcapacity cyclic-degradation coefficient, CDh
[or equivalently, CDh (k=1)]. Table 12
specifies test conditions for these nine tests.
TABLE 12—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR
Dry bulb
Wet bulb
Air entering outdoor unit
temperature (°F)
Dry bulb
Compressor
capacity
Wet bulb
70
60 (max)
62
56.5
Low ................
H12 Test (required, steady) ...............
70
60 (max)
47
43
High ...............
H1C2 Test (required,7 cyclic) .............
H11 Test (required) ............................
tkelley on DSK3SPTVN1PROD with PROPOSALS2
H01 Test (required, steady) ...............
70
70
60 (max)
60 (max)
47
47
43
43
High ...............
Low ................
H1C1 Test (required, cyclic) ..............
H22 Test (required) ............................
70
70
60 (max)
60 (max)
47
35
43
33
Low ................
High ...............
H21 Test 5 6 (required) ........................
70
60 (max)
35
33
Low ................
H32 Test (required, steady) ...............
70
60 (max)
17
15
High ...............
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Heating air
volume rate
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09NOP2
Heating Minimum.1
Heating FullLoad.2
(3).
Heating Minimum.1
(4).
Heating FullLoad.2
Heating Minimum.1
Heating FullLoad.2
EP09NO15.025</GPH>
Air entering indoor unit
temperature (°F)
Test description
69366
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
TABLE 12—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR—Continued
Air entering indoor unit
temperature (°F)
Test description
Dry bulb
H31 Test 5 (required, steady) .............
Wet bulb
Air entering outdoor unit
temperature (°F)
Dry bulb
60 (max)
70
Compressor
capacity
Heating air
volume rate
Wet bulb
17
15
Low ................
Heating Minimum.1
1 Defined
in section 3.1.4.5.
in section 3.1.4.4.
3 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H12 Test.
4 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H11 Test.
5 Required only if the heat pump’s performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is needed to complete the section 4.2.3 HSPF calculations.
6 If table note #5 applies, the section 3.6.3 equations for Q k=1 (35) and E k=1 (17) may be used in lieu of conducting the H2 Test.
˙h
˙h
1
7 Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.
2 Defined
3.6.4 Tests for a heat pump having a
variable-speed compressor.
a. Conduct one Maximum Temperature
Test (H01), two High Temperature Tests (H12
and H11), one Frost Accumulation Test
(H2V), and one Low Temperature Test (H32).
Conducting one or both of the following tests
is optional: An additional High Temperature
Test (H1N) and an additional Frost
Accumulation Test (H22). Conduct the
Maximum Temperature Cyclic (H0C1) Test to
determine the heating mode cyclic-
degradation coefficient, CDh. Test conditions
for the eight tests are specified in Table 13.
Determine the intermediate compressor
speed cited in Table 13 using the heating
mode maximum and minimum compressors
speeds and:
Where a tolerance of plus 5 percent or the
next higher inverter frequency step from that
calculated is allowed. If the H22Test is not
done, use the following equations to
approximate the capacity and electrical
power at the H22 test conditions:
˙
b. Determine the quantities Qhk=2(47) and
˙
from Ehk=2(47) from the H12 Test and
evaluate them according to section 3.7.
˙
Determine the quantities Qhk=2(17) and
˙
Ehk=2(17) from the H32 Test and evaluate
them according to section 3.10. For heat
pumps where the heating mode maximum
compressor speed exceeds its cooling mode
maximum compressor speed, conduct the
H1N Test if the manufacturer requests it. If
the H1N Test is done, operate the heat
pump’s compressor at the same speed as the
speed used for the cooling mode A2 Test.
Refer to the last sentence of section 4.2 to see
how the results of the H1N Test may be used
in calculating the heating seasonal
performance factor.
TABLE 13—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A VARIABLE-SPEED COMPRESSOR
Dry bulb
Wet bulb
Air entering outdoor unit
temperature (°F)
Dry bulb
Compressor
speed
Heating air
volume rate
Heating Minimum.1
(2).
Heating FullLoad.3
Heating Minimum.1
Heating Nominal.4
Wet bulb
70
60 (max)
62
56.5
Minimum ........
H0C1 Test (required, steady) .............
H12 Test (required, steady) ...............
70
70
60 (max)
60 (max)
62
47
56.5
43
Minimum ........
Maximum .......
H11 Test (required, steady) ...............
70
60 (max)
47
43
Minimum ........
H1N Test (optional, steady) ...............
tkelley on DSK3SPTVN1PROD with PROPOSALS2
H01 Test (required, steady) ...............
70
60 (max)
47
43
H22 Test (optional) .............................
70
60 (max)
35
33
Cooling Mode
Maximum.
Maximum .......
H2V Test (required) ...........................
70
60 (max)
35
33
Intermediate ...
H32 Test (required, steady) ...............
70
60 (max)
17
15
Maximum .......
1 Defined
Heating FullLoad.3
Heating Intermediate.5
Heating FullLoad.3
in section 3.1.4.5.
the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H01 Test.
2 Maintain
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Air entering indoor unit
temperature (°F)
Test description
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
3 Defined
4 Defined
5 Defined
69367
in section 3.1.4.4.
in section 3.1.4.7.
in section 3.1.4.6.
c. For multiple-split heat pumps (only), the
following procedures supersede the above
requirements. For all Table 13 tests specified
for a minimum compressor speed, at least
one indoor unit must be turned off. The
manufacturer shall designate the particular
indoor unit(s) that is turned off. The
manufacturer must also specify the
compressor speed used for the Table 13 H2V
Test, a heating mode intermediate
compressor speed that falls within 1⁄4 and 3⁄4
of the difference between the maximum and
minimum heating mode speeds. The
manufacturer should prescribe an
intermediate speed that is expected to yield
the highest COP for the given H2V Test
conditions and bracketed compressor speed
range. The manufacturer can designate that
one or more specific indoor units are turned
off for the H2V Test.
3.6.5 Additional test for a heat pump
having a heat comfort controller.
Test any heat pump that has a heat comfort
controller (see section 1.2, Definitions)
according to section 3.6.1, 3.6.2, or 3.6.3,
whichever applies, with the heat comfort
controller disabled. Additionally, conduct
the abbreviated test described in section 3.1.9
with the heat comfort controller active to
determine the system’s maximum supply air
temperature. (Note: Heat pumps having a
variable speed compressor and a heat comfort
controller are not covered in the test
procedure at this time.)
3.6.6 Heating mode tests for northern heat
pumps with triple-capacity compressors.
Test triple-capacity, northern heat pumps
for the heating mode as follows:
(a) Conduct one maximum-temperature test
(H01), two high-temperature tests (H12 and
H11), one Frost Accumulation test (H22), two
low-temperature tests (H32, H33), and one
minimum-temperature test (H43). Conduct an
additional Frost Accumulation test (H21) and
low- temperature test (H31) if both of the
following conditions exist: (1) Knowledge of
the heat pump’s capacity and electrical
power at low compressor capacity for
outdoor temperatures of 37 °F and less is
needed to complete the section 4.2.6 seasonal
performance calculations; and (2) the heat
pump’s controls allow low-capacity
operation at outdoor temperatures of 37 °F
and less. If the above two conditions are met,
an alternative to conducting the H21 Frost
˙
Accumulation Test to determine Qhk=1(35)
˙
and Ehk=1(35) is to use the following
equations to approximate this capacity and
electrical power:
In evaluating the above equations,
˙
determine the quantities Qhk=1(47) from the
H11 Test and evaluate them according to
section 3.7. Determine the quantities
˙
˙
Qhk=1(17) and Ehk=1(17) from the H31 Test
and evaluate them according to section 3.10.
˙
Use the paired values of Qhk=1(35) and
˙
Ehk=1(35) derived from conducting the H21
Frost Accumulation Test and evaluated as
specified in section 3.9.1 or use the paired
values calculated using the above default
equations, whichever contribute to a higher
Region IV HSPF based on the DHRmin.
(b) Conducting a Frost Accumulation Test
(H23) with the heat pump operating at its
booster capacity is optional. If this optional
test is not conducted, determine Qhk=3(35)
and Ehk=3(35) using the following equations
to approximate this capacity and electrical
power:
˙
˙
Qhk=3(35) and Ehk=3(35) derived from
conducting the H23Frost Accumulation Test
and calculated as specified in section 3.9.1 or
use the paired values calculated using the
above default equations, whichever
contribute to a higher Region IV HSPF based
on the DHRmin.
(c) Conduct the high-temperature cyclic
test (H1C1) to determine the heating mode
cyclic-degradation coefficient, CDh. If a triplecapacity heat pump locks out low capacity
operation at lower outdoor temperatures,
conduct the high-temperature cyclic test
(H1C2) to determine the high-capacity
heating mode cyclic-degradation coefficient,
CDh (k=2). The default CDh (k=2) is the same
value as determined or assigned for the lowcapacity cyclic-degradation coefficient, CDh
[or equivalently, CDh (k=1)]. Finally, if a
triple-capacity heat pump locks out both low
and high capacity operation at the lowest
outdoor temperatures, conduct the lowtemperature cyclic test (H3C3) to determine
the booster-capacity heating mode cyclic-
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˙
Determine the quantities Qhk=2(47) and
˙
Ehk=2(47) from the H12 Test and evaluate
them according to section 3.7. Determine the
˙
˙
quantities Qhk=2(35) and Ehk=2(35) from the
H22Test and evaluate them according to
section 3.9.1. Determine the quantities
˙
˙
Qhk=2(17) and Ehk=2(17) from the H32Test,
˙
determine the quantities Qhk=3(17) and
˙
Ehk=3(17) from the H33Test, and determine
˙
˙
the quantities Qhk=3(2) and Ehk=3(2) from the
H43Test. Evaluate all six quantities according
to section 3.10. Use the paired values of
EP09NO15.028</GPH> EP09NO15.029</GPH>
tkelley on DSK3SPTVN1PROD with PROPOSALS2
where:
69368
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
degradation coefficient, CDh (k=3). The
default CDh (k=3) is the same value as
determined or assigned for the high-capacity
cyclic-degradation coefficient, CDh [or
equivalently, CDh (k=2)]. Table 14 specifies
test conditions for all 13 tests.
TABLE 14—HEATING MODE TEST CONDITIONS FOR UNITS WITH A TRIPLE-CAPACITY COMPRESSOR
Air entering indoor unit
temperature (°F)
Test description
Dry bulb
Wet bulb
Air entering outdoor unit
temperature (°F)
Dry bulb
Compressor
capacity
Heating air volume rate
Wet bulb
H01 Test (required, steady) ...............
70
60 (max)
62
56.5
Low ................
H12 Test (required, steady) ...............
70
60 (max)
47
43
High ...............
H1C2 Test (required,8 cyclic) .............
H11 Test (required) ............................
70
70
60 (max)
60 (max)
47
47
43
43
High ...............
Low ................
H1C1 Test (required, cyclic) ..............
H23 Test (optional, steady) ................
70
70
60 (max)
60 (max)
47
35
43
33
Low ................
Booster ..........
H22 Test (required) ............................
70
60 (max)
35
33
High ...............
H21 Test (required) ............................
70
60 (max)
35
33
Low ................
H33 Test (required, steady) ...............
70
60 (max)
17
15
Booster ..........
H3C3 Test 5 6 (required, cyclic) ..........
H32 Test (required, steady) ...............
70
70
60 (max)
60 (max)
17
17
15
15
Booster ..........
High ...............
H31 Test 5 (required, steady) .............
70
60 (max)
17
15
Low ................
H43 Test (required, steady) ...............
70
60 (max)
2
1
Booster ..........
Heating Minimum.1
Heating FullLoad.2
3.
Heating Minimum 1.
4.
Heating FullLoad.2
Heating FullLoad.2
Heating Minimum.1
Heating FullLoad.2
7.
Heating FullLoad.2
Heating Minimum.1
Heating FullLoad.2
1 Defined
in section 3.1.4.5.
in section 3.1.4.4.
the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H12 Test.
4 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H11Test.
5 Required only if the heat pump’s performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is needed to complete the section 4.2.6 HSPF calculations.
6 If table note 5 applies, the section 3.6.6 equations for Q k=1 (35) and E k=1 (17) may be used in lieu of conducting the H2 Test.
˙h
˙h
1
7 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H33 Test.
8 Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.
2 Defined
3 Maintain
3.6.7 Tests for a heat pump having a
single indoor unit having multiple blowers
and offering two stages of compressor
modulation. Conduct the heating mode tests
specified in section 3.6.3.
3.7 Test procedures for steady-state
Maximum Temperature and High
Temperature heating mode tests (the H01, H1,
H12, H11, and H1N Tests).
a. For the pretest interval, operate the test
room reconditioning apparatus and the heat
pump until equilibrium conditions are
maintained for at least 30 minutes at the
specified section 3.6 test conditions. Use the
exhaust fan of the airflow measuring
apparatus and, if installed, the indoor blower
of the heat pump to obtain and then maintain
the indoor air volume rate and/or the
external static pressure specified for the
particular test. Continuously record the drybulb temperature of the air entering the
indoor coil, and the dry-bulb temperature
and water vapor content of the air entering
the outdoor coil. Refer to section 3.11 for
additional requirements that depend on the
selected secondary test method. After
satisfying the pretest equilibrium
requirements, make the measurements
specified in Table 3 of ASHRAE Standard
37–2009 (incorporated by reference, see
§ 430.3) for the Indoor Air Enthalpy method
and the user-selected secondary method.
Make said Table 3 measurements at equal
intervals that span 5 minutes or less.
Continue data sampling until a 30-minute
period (e.g., four consecutive 10-minute
samples) is reached where the test tolerances
specified in Table 15 are satisfied. For those
continuously recorded parameters, use the
entire data set for the 30-minute interval
when evaluating Table 15 compliance.
Determine the average electrical power
consumption of the heat pump over the same
30-minute interval.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
TABLE 15—TEST OPERATING AND TEST CONDITION TOLERANCES FOR SECTION 3.7 AND SECTION 3.10 STEADY-STATE
HEATING MODE TESTS
Test
operating
tolerance 1
Indoor dry-bulb, °F:
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
Indoor wet-bulb, °F:
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
Outdoor dry-bulb, °F:
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Test
condition
tolerance 1
2.0
2.0
0.5
........................
1.0
1.0
........................
........................
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69369
TABLE 15—TEST OPERATING AND TEST CONDITION TOLERANCES FOR SECTION 3.7 AND SECTION 3.10 STEADY-STATE
HEATING MODE TESTS—Continued
Test
operating
tolerance 1
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
Outdoor wet-bulb, °F:
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
External resistance to airflow, inches of water ........................................................................................................
Electrical voltage, % of rdg ..............................................................................................................................
Nozzle pressure drop, % of rdg .......................................................................................................................
1 See
2 Only
3 Only
2.0
2 2.0
1.0
2 1.0
0.12
2.0
8.0
Test
condition
tolerance 1
0.5
........................
0.3
........................
3 0.02
1.5
........................
section 1.2, Definitions.
applies when the Outdoor Air Enthalpy Method is used.
applies when testing non-ducted units.
power consumption of the indoor blower
˙
motor (Efan,1):
1. The section 3.8 cyclic test will be
conducted and the heat pump has a variablespeed indoor blower that is expected to be
disabled during the cyclic test; or
2. The heat pump has a (variable-speed)
constant-air volume-rate indoor blower and
during the steady-state test the average
external static pressure (DP1) exceeds the
applicable section 3.1.4.4 minimum (or
targeted) external static pressure (DPmin) by
0.03 inches of water or more.
˙
Determine Efan,1 by making measurements
during the 30-minute data collection interval,
or immediately following the test and prior
to changing the test conditions. When the
above ‘‘2’’ criteria applies, conduct the
˙
following four steps after determining Efan,1
(which corresponds to DP1):
i. While maintaining the same test
conditions, adjust the exhaust fan of the
airflow measuring apparatus until the
external static pressure increases to
approximately DP1 + (DP1 ¥ DPmin).
ii. After re-establishing steady readings for
fan motor power and external static pressure,
determine average values for the indoor
˙
blower power (Efan,2) and the external static
pressure (DP2) by making measurements over
a 5-minute interval.
iii. Approximate the average power
consumption of the indoor blower motor if
the 30-minute test had been conducted at
DPmin using linear extrapolation:
iv. Decrease the total space heating
˙
˙
capacity, Qhk(T), by the quantity (Efan,1 ¥
˙
Efan,min), when expressed on a Btu/h basis.
˙
Decrease the total electrical power, Ehk(T) by
the same fan power difference, now
expressed in watts.
e. If the temperature sensors used to
provide the primary measurement of the
indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the
subsequent cyclic dry-coil test are different,
include measurements of the latter sensors
among the regularly sampled data. Beginning
at the start of the 30-minute data collection
period, measure and compute the indoor-side
air dry-bulb temperature difference using
both sets of instrumentation, DT (Set SS) and
DT (Set CYC), for each equally spaced data
sample. If using a consistent data sampling
rate that is less than 1 minute, calculate and
record minutely averages for the two
temperature differences. If using a consistent
sampling rate of one minute or more,
calculate and record the two temperature
differences from each data sample. After
having recorded the seventh (i=7) set of
temperature differences, calculate the
following ratio using the first seven sets of
values:
tkelley on DSK3SPTVN1PROD with PROPOSALS2
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EP09NO15.031</GPH> EP09NO15.032</GPH>
Ô
where Vs is the average measured indoor air
volume rate expressed in units of cubic feet
per minute of standard air (scfm). During the
30-minute data collection interval of a High
Temperature Test, pay attention to
preventing a defrost cycle. Prior to this time,
allow the heat pump to perform a defrost
cycle if automatically initiated by its own
controls. As in all cases, wait for the heat
pump’s defrost controls to automatically
terminate the defrost cycle. Heat pumps that
undergo a defrost should operate in the
heating mode for at least 10 minutes after
defrost termination prior to beginning the 30minute data collection interval. For some
heat pumps, frost may accumulate on the
outdoor coil during a High Temperature test.
If the indoor coil leaving air temperature or
the difference between the leaving and
entering air temperatures decreases by more
than 1.5 °F over the 30-minute data
collection interval, then do not use the
collected data to determine capacity. Instead,
initiate a defrost cycle. Begin collecting data
no sooner than 10 minutes after defrost
termination. Collect 30 minutes of new data
during which the Table 15 test tolerances are
satisfied. In this case, use only the results
from the second 30-minute data collection
˙
˙
interval to evaluate Qhk(47) and Ehk(47).
d. If conducting the cyclic heating mode
test, which is described in section 3.8, record
Ô
the average indoor-side air volume rate, V,
specific heat of the air, Cp,a (expressed on dry
air basis), specific volume of the air at the
nozzles, vn′ (or vn), humidity ratio at the
nozzles, Wn, and either pressure difference or
velocity pressure for the flow nozzles. If
either or both of the below criteria apply,
determine the average, steady-state, electrical
b. Calculate indoor-side total heating
capacity as specified in sections 7.3.4.1 and
7.3.4.3 of ASHRAE Standard 37–2009
(incorporated by reference, see § 430.3). Do
not adjust the parameters used in calculating
capacity for the permitted variations in test
conditions. Assign the average space heating
capacity and electrical power over the 30minute data collection interval to the
˙
˙
variables Qhk and Ehk(T) respectively. The
‘‘T’’ and superscripted ‘‘k’’ are the same as
described in section 3.3. Additionally, for the
heating mode, use the superscript to denote
results from the optional H1N Test, if
conducted.
c. For heat pumps tested without an indoor
˙
blower installed, increase Qhk(T) by
69370
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
temperature difference during the steadystate dry-coil test and the subsequent cyclic
dry-coil test are the same, set FCD*= 1.
3.8 Test procedures for the cyclic heating
mode tests (the H0C1, H1C, H1C1 and H1C2
Tests).
a. Except as noted below, conduct the
cyclic heating mode test as specified in
section 3.5. As adapted to the heating mode,
replace section 3.5 references to ‘‘the steadystate dry coil test’’ with ‘‘the heating mode
steady-state test conducted at the same test
conditions as the cyclic heating mode test.’’
Use the test tolerances in Table 16 rather
than Table 9. Record the outdoor coil
entering wet-bulb temperature according to
the requirements given in section 3.5 for the
outdoor coil entering dry-bulb temperature.
Drop the subscript ‘‘dry’’ used in variables
cited in section 3.5 when referring to
quantities from the cyclic heating mode test.,
The default CD value for heating is 0.25. If
available, use electric resistance heaters (see
section 2.1) to minimize the variation in the
inlet air temperature. Determine the total
space heating delivered during the cyclic
heating test, qcyc, as specified in section 3.5
except for making the following changes:
(1) When evaluating Equation 3.5–1, use
Ô
the values of V, Cp,a,vn′, (or vn), and Wn that
were recorded during the section 3.7 steadystate test conducted at the same test
conditions.
(2) Calculate G using,
where FCD* is the value recorded during the
section 3.7 steady-state test conducted at
the same test condition.
b. For ducted heat pumps tested without
an indoor blower installed (excluding the
special case where a variable-speed fan is
temporarily removed), increase qcyc by the
amount calculated using Equation 3.5–3.
Additionally, increase ecyc by the amount
calculated using Equation 3.5–2. In making
these calculations, use the average indoor air
Ô
volume rate (Vs) determined from the section
3.7 steady-state heating mode test conducted
at the same test conditions.
c. For non-ducted heat pumps, subtract the
electrical energy used by the indoor blower
during the 3 minutes after compressor cutoff
from the non-ducted heat pump’s integrated
heating capacity, qcyc.
d. If a heat pump defrost cycle is manually
or automatically initiated immediately prior
to or during the OFF/ON cycling, operate the
heat pump continuously until 10 minutes
after defrost termination. After that, begin
cycling the heat pump immediately or delay
until the specified test conditions have been
re-established. Pay attention to preventing
defrosts after beginning the cycling process.
For heat pumps that cycle off the indoor
blower during a defrost cycle, make no effort
here to restrict the air movement through the
indoor coil while the fan is off. Resume the
OFF/ON cycling while conducting a
minimum of two complete compressor OFF/
ON cycles before determining qcyc and ecyc.
3.8.1 Heating mode cyclic-degradation
coefficient calculation.
Use the results from the required cyclic test
and the required steady-state test that were
conducted at the same test conditions to
determine the heating mode cyclicdegradation coefficient CDh. Add ‘‘(k=2)’’ to
the coefficient if it corresponds to a twocapacity unit cycling at high capacity. For the
below calculation of the heating mode cyclic
degradation coefficient, do not include the
duct loss correction from section 7.3.3.3 of
ASHRAE Standard 37–2009 (incorporated by
reference, see § 430.3) in determining
˙
Qhk(Tcyc) (or qcyc). The default value for twocapacity units cycling at high capacity,
however, is the low-capacity coefficient, i.e.,
CDh (k=2) = CDh. The tested CDhis calculated
as follows:
EP09NO15.037</GPH>
Each time a subsequent set of temperature
differences is recorded (if sampling more
frequently than every 5 minutes), calculate
FCD using the most recent seven sets of
values. Continue these calculations until the
30-minute period is completed or until a
value for FCD is calculated that falls outside
the allowable range of 0.94–1.06. If the latter
occurs, immediately suspend the test and
identify the cause for the disparity in the two
temperature difference measurements.
Recalibration of one or both sets of
instrumentation may be required. If all the
values for FCD are within the allowable range,
save the final value of the ratio from the 30minute test as FCD*. If the temperature
sensors used to provide the primary
measurement of the indoor-side dry bulb
EP09NO15.035</GPH>
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the cyclic heating mode test,
dimensionless.
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the average coefficient of performance during
the steady-state heating mode test
conducted at the same test conditions—
i.e., same outdoor dry bulb temperature,
Tcyc, and speed/capacity, k, if
Dtcyc = the duration of the OFF/ON intervals;
0.5 hours when testing a heat pump
having a single-speed or two-capacity
compressor and 1.0 hour when testing a
the heating load factor, dimensionless.
Tcyc = the nominal outdoor temperature at
which the cyclic heating mode test is
conducted, 62 or 47 °F.
applicable—as specified for the cyclic
heating mode test, dimensionless.
heat pump having a variable-speed
compressor.
Round the calculated value for CDh to the
nearest 0.01. If CDh is negative, then set it
equal to zero.
TABLE 16—TEST OPERATING AND TEST CONDITION TOLERANCES FOR CYCLIC HEATING MODE TESTS
Test
operating
tolerance 1
Indoor entering dry-bulb temperature,2 °F ..............................................................................................................
Indoor entering wet-bulb temperature,2 °F ..............................................................................................................
Outdoor entering dry-bulb temperature,2 °F ............................................................................................................
Outdoor entering wet-bulb temperature,2 °F ...........................................................................................................
External resistance to air-flow,2 inches of water .....................................................................................................
Airflow nozzle pressure difference or velocity pressure,2% of reading ..................................................................
Electrical voltage,4% of rdg .....................................................................................................................................
2.0
1.0
2.0
2.0
0.12
2.0
8.0
Test
condition
tolerance 1
0.5
........................
0.5
1.0
........................
3 2.0
1.5
1 See
section 1.2, Definitions.
during the interval that air flows through the indoor (outdoor) coil except for the first 30 seconds after flow initiation. For units having a
variable-speed indoor blower that ramps, the tolerances listed for the external resistance to airflow shall apply from 30 seconds after achieving
full speed until ramp down begins.
3 The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state test conducted at
the same test conditions.
4 Applies during the interval that at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are operating, except for the first 30 seconds after compressor start-up.
3.9 Test procedures for Frost
Accumulation heating mode tests (the H2,
H22, H2V, and H21 Tests).
a. Confirm that the defrost controls of the
heat pump are set as specified in section
2.2.1. Operate the test room reconditioning
apparatus and the heat pump for at least 30
minutes at the specified section 3.6 test
conditions before starting the ‘‘preliminary’’
test period. The preliminary test period must
immediately precede the ‘‘official’’ test
period, which is the heating and defrost
interval over which data are collected for
evaluating average space heating capacity
and average electrical power consumption.
b. For heat pumps containing defrost
controls which are likely to cause defrosts at
intervals less than one hour, the preliminary
test period starts at the termination of an
automatic defrost cycle and ends at the
termination of the next occurring automatic
defrost cycle. For heat pumps containing
defrost controls which are likely to cause
defrosts at intervals exceeding one hour, the
preliminary test period must consist of a
heating interval lasting at least one hour
followed by a defrost cycle that is either
manually or automatically initiated. In all
cases, the heat pump’s own controls must
govern when a defrost cycle terminates.
c. The official test period begins when the
preliminary test period ends, at defrost
termination. The official test period ends at
the termination of the next occurring
automatic defrost cycle. When testing a heat
pump that uses a time-adaptive defrost
control system (see section 1.2, Definitions),
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however, manually initiate the defrost cycle
that ends the official test period at the instant
indicated by instructions provided by the
manufacturer. If the heat pump has not
undergone a defrost after 6 hours,
immediately conclude the test and use the
results from the full 6-hour period to
calculate the average space heating capacity
and average electrical power consumption.
For heat pumps that turn the indoor blower
off during the defrost cycle, take steps to
cease forced airflow through the indoor coil
and block the outlet duct whenever the heat
pump’s controls cycle off the indoor blower.
If it is installed, use the outlet damper box
described in section 2.5.4.1 to affect the
blocked outlet duct.
d. Defrost termination occurs when the
controls of the heat pump actuate the first
change in converting from defrost operation
to normal heating operation. Defrost
initiation occurs when the controls of the
heat pump first alter its normal heating
operation in order to eliminate possible
accumulations of frost on the outdoor coil.
e. To constitute a valid Frost Accumulation
test, satisfy the test tolerances specified in
Table 17 during both the preliminary and
official test periods. As noted in Table 17,
test operating tolerances are specified for two
sub-intervals: (1) When heating, except for
the first 10 minutes after the termination of
a defrost cycle (Sub-interval H, as described
in Table 17) and (2) when defrosting, plus
these same first 10 minutes after defrost
termination (Sub-interval D, as described in
Table 17). Evaluate compliance with Table 17
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test condition tolerances and the majority of
the test operating tolerances using the
averages from measurements recorded only
during Sub-interval H. Continuously record
the dry bulb temperature of the air entering
the indoor coil, and the dry bulb temperature
and water vapor content of the air entering
the outdoor coil. Sample the remaining
parameters listed in Table 17 at equal
intervals that span 5 minutes or less.
f. For the official test period, collect and
use the following data to calculate average
space heating capacity and electrical power.
During heating and defrosting intervals when
the controls of the heat pump have the
indoor blower on, continuously record the
dry-bulb temperature of the air entering (as
noted above) and leaving the indoor coil. If
using a thermopile, continuously record the
difference between the leaving and entering
dry-bulb temperatures during the interval(s)
that air flows through the indoor coil. For
heat pumps tested without an indoor blower
installed, determine the corresponding
cumulative time (in hours) of indoor coil
airflow, Dta. Sample measurements used in
calculating the air volume rate (refer to
sections 7.7.2.1 and 7.7.2.2 of ASHRAE
Standard 37–2009) at equal intervals that
span 10 minutes or less. (Note: In the first
printing of ASHRAE Standard 37–2009, the
second IP equation for Qmi should read:)
Record the electrical energy consumed,
expressed in watt-hours, from defrost
termination to defrost termination, eDEFk(35),
as well as the corresponding elapsed time in
hours, DtFR.
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TABLE 17—TEST OPERATING AND TEST CONDITION TOLERANCES FOR FROST ACCUMULATION HEATING MODE TESTS
Test operating tolerance 1
Sub-interval H 2
Indoor entering dry-bulb temperature, °F ....................................................................
Indoor entering wet-bulb temperature, °F ...................................................................
Outdoor entering dry-bulb temperature, °F .................................................................
Outdoor entering wet-bulb temperature, °F .................................................................
External resistance to airflow, inches of water ............................................................
Electrical voltage, % of rdg ..........................................................................................
Sub-interval D 3
Test condition
tolerance 1
Sub-interval H2
4 4.0
0.5
10.0
2.0
1.0
2.0
1.5
0.12
2.0
1.0
0.5
5 0.02
1.5
1 See
section 1.2, Definitions.
when the heat pump is in the heating mode, except for the first 10 minutes after termination of a defrost cycle.
3 Applies during a defrost cycle and during the first 10 minutes after the termination of a defrost cycle when the heat pump is operating in the
heating mode.
4 For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies during the 10 minute interval that follows defrost termination.
5 Only applies when testing non-ducted heat pumps.
2 Applies
a. Evaluate average space heating capacity,
˙
Qhk(35), when expressed in units of Btu per
hour, using:
Where,
Ô
V = the average indoor air volume rate
measured during Sub-interval H, cfm.
Cp,a = 0.24 + 0.444 · Wn, the constant pressure
specific heat of the air-water vapor
mixture that flows through the indoor
coil and is expressed on a dry air basis,
Btu/lbmda · °F.
vn′ = specific volume of the air-water vapor
mixture at the nozzle, ft3/lbmmx.
Wn = humidity ratio of the air-water vapor
mixture at the nozzle, lbm of water vapor
per lbm of dry air.
DtFR = t2 ¥ t1, the elapsed time from defrost
termination to defrost termination, hr.
Tal(t) = dry bulb temperature of the air
entering the indoor coil at elapsed time
t, °F; only recorded when indoor coil
airflow occurs; assigned the value of zero
during periods (if any) where the indoor
blower cycles off.
Ta2(t) = dry bulb temperature of the air
leaving the indoor coil at elapsed time t,
°F; only recorded when indoor coil
airflow occurs; assigned the value of zero
during periods (if any) where the indoor
blower cycles off.
t1 = the elapsed time when the defrost
termination occurs that begins the
official test period, hr.
t2 = the elapsed time when the next
automatically occurring defrost
termination occurs, thus ending the
official test period, hr.
vn = specific volume of the dry air portion
of the mixture evaluated at the dry-bulb
temperature, vapor content, and
barometric pressure existing at the
nozzle, ft3 per lbm of dry air.
To account for the effect of duct losses
between the outlet of the indoor unit and the
section 2.5.4 dry-bulb temperature grid,
˙
adjust Qhk(35) in accordance with section
7.3.4.3 of ASHRAE Standard 37–2009
(incorporated by reference, see § 430.3).
b. Evaluate average electrical power,
˙
Ehk(35), when expressed in units of watts,
using:
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3.9.1 Average space heating capacity and
electrical power calculations.
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˙
and increase Ehk(35) by,
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For heat pumps tested without an indoor
Ç
blower installed, increase Qhk(35) by,
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by the same quantity, now expressed in
watts.
3.9.2 Demand defrost credit.
a. Assign the demand defrost credit, Fdef,
that is used in section 4.2 to the value of 1
in all cases except for heat pumps having a
demand-defrost control system (see section
1.2, Definitions). For such qualifying heat
pumps, evaluate Fdef using,
Where,
Dtdef = the time between defrost terminations
(in hours) or 1.5, whichever is greater. A
value of 6 must be assigned to Dtdef if
this limit is reached during a Frost
Accumulation test and the heat pump
has not completed a defrost cycle.
Dtmax = maximum time between defrosts as
allowed by the controls (in hours) or 12,
whichever is less, as provided in the
installation manuals included with the
unit by the manufacturer.
b. For two-capacity heat pumps and for
section 3.6.2 units, evaluate the above
equation using the Dtdef that applies based on
the Frost Accumulation Test conducted at
high capacity and/or at the Heating Full-load
Air Volume Rate. For variable-speed heat
pumps, evaluate Dtdef based on the required
Frost Accumulation Test conducted at the
intermediate compressor speed.
3.10 Test procedures for steady-state Low
Temperature heating mode tests (the H3, H32,
and H31 Tests).
Except for the modifications noted in this
section, conduct the Low Temperature
heating mode test using the same approach
as specified in section 3.7 for the Maximum
and High Temperature tests. After satisfying
the section 3.7 requirements for the pretest
interval but before beginning to collect data
˙
˙
to determine Qhk(17) and Ehk(17), conduct a
defrost cycle. This defrost cycle may be
manually or automatically initiated. The
defrost sequence must be terminated by the
action of the heat pump’s defrost controls.
Begin the 30-minute data collection interval
˙
described in section 3.7, from which Qhk(17)
˙
and Ehk(17) are determined, no sooner than
10 minutes after defrost termination. Defrosts
should be prevented over the 30-minute data
collection interval.
3.11 Additional requirements for the
secondary test methods.
3.11.1 If using the Outdoor Air Enthalpy
Method as the secondary test method.
During the ‘‘official’’ test, the outdoor airside test apparatus described in section
2.10.1 is connected to the outdoor unit. To
help compensate for any effect that the
addition of this test apparatus may have on
the unit’s performance, conduct a
‘‘preliminary’’ test where the outdoor air-side
test apparatus is disconnected. Conduct a
preliminary test prior to the first section 3.2
steady-state cooling mode test and prior to
the first section 3.6 steady-state heating mode
test. No other preliminary tests are required
so long as the unit operates the outdoor fan
during all cooling mode steady-state tests at
the same speed and all heating mode steadystate tests at the same speed. If using more
than one outdoor fan speed for the cooling
mode steady-state tests, however, conduct a
preliminary test prior to each cooling mode
test where a different fan speed is first used.
This same requirement applies for the
heating mode tests.
3.11.1.1 If a preliminary test precedes the
official test.
a. The test conditions for the preliminary
test are the same as specified for the official
test. Connect the indoor air-side test
apparatus to the indoor coil; disconnect the
outdoor air-side test apparatus. Allow the test
room reconditioning apparatus and the unit
being tested to operate for at least one hour.
After attaining equilibrium conditions,
measure the following quantities at equal
intervals that span 5 minutes or less:
1. The section 2.10.1 evaporator and
condenser temperatures or pressures;
2. Parameters required according to the
Indoor Air Enthalpy Method.
Continue these measurements until a 30minute period (e.g., four consecutive 10minute samples) is obtained where the Table
8 or Table 15, whichever applies, test
tolerances are satisfied.
b. After collecting 30 minutes of steadystate data, reconnect the outdoor air-side test
apparatus to the unit. Adjust the exhaust fan
of the outdoor airflow measuring apparatus
until averages for the evaporator and
condenser temperatures, or the saturated
temperatures corresponding to the measured
pressures, agree within ±0.5 °F of the
averages achieved when the outdoor air-side
test apparatus was disconnected. Calculate
the averages for the reconnected case using
five or more consecutive readings taken at
one minute intervals. Make these consecutive
readings after re-establishing equilibrium
conditions and before initiating the official
test.
3.11.1.2 If a preliminary test does not
precede the official test.
Connect the outdoor-side test apparatus to
the unit. Adjust the exhaust fan of the
outdoor airflow measuring apparatus to
achieve the same external static pressure as
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increases to approximately DP1 + (DP1 ¥
DPmin).
3. After re-establishing steady readings for
the fan motor power and external static
pressure, determine average values for the
˙
indoor blower power (Efan,2) and the external
static pressure (DP2) by making
measurements over a 5-minute interval.
4. Approximate the average power
consumption of the indoor blower motor had
the Frost Accumulation heating mode test
been conducted at DPmin using linear
extrapolation:
EP09NO15.043</GPH> EP09NO15.044</GPH>
1. Measure the average power consumption
˙
of the indoor blower motor (Efan,1) and record
the corresponding external static pressure
(DP1) during or immediately following the
Frost Accumulation heating mode test. Make
the measurement at a time when the heat
pump is heating, except for the first 10
minutes after the termination of a defrost
cycle.
2. After the Frost Accumulation heating
mode test is completed and while
maintaining the same test conditions, adjust
the exhaust fan of the airflow measuring
apparatus until the external static pressure
5. Decrease the total heating capacity,
˙
˙
˙
Qhk(35), by the quantity [(Efan,1 ¥Efan,min)· (Dt
a/Dt FR], when expressed on a Btu/h basis.
Decrease the total electrical power, Ehk(35),
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Ô
Where Vs is the average indoor air volume
rate measured during the Frost
Accumulation heating mode test and is
expressed in units of cubic feet per
minute of standard air (scfm).
c. For heat pumps having a constant-airvolume-rate indoor blower, the five
additional steps listed below are required if
the average of the external static pressures
measured during sub-Interval H exceeds the
applicable section 3.1.4.4, 3.1.4.5, or 3.1.4.6
minimum (or targeted) external static
pressure (DPmin) by 0.03 inches of water or
more:
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
measured during the prior preliminary test
conducted with the unit operating in the
same cooling or heating mode at the same
outdoor fan speed.
3.11.1.3 Official test.
a. Continue (preliminary test was
conducted) or begin (no preliminary test) the
official test by making measurements for both
the Indoor and Outdoor Air Enthalpy
Methods at equal intervals that span 5
minutes or less. Discontinue these
measurements only after obtaining a 30minute period where the specified test
condition and test operating tolerances are
satisfied. To constitute a valid official test:
(1) Achieve the energy balance specified in
section 3.1.1; and,
(2) For cases where a preliminary test is
conducted, the capacities determined using
the Indoor Air Enthalpy Method from the
official and preliminary test periods must
agree within 2.0 percent.
b. For space cooling tests, calculate
capacity from the outdoor air-enthalpy
measurements as specified in sections 7.3.3.2
and 7.3.3.3 of ASHRAE Standard 37–2009
(incorporated by reference, see § 430.3).
Calculate heating capacity based on outdoor
air-enthalpy measurements as specified in
sections 7.3.4.2 and 7.3.3.4.3 of the same
ASHRAE Standard. Adjust the outdoor-side
capacity according to section 7.3.3.4 of
ASHRAE Standard 37–2009 to account for
line losses when testing split systems. Use
the outdoor unit fan power as measured
during the official test and not the value
measured during the preliminary test, as
described in section 8.6.2 of ASHRAE
Standard 37–2009, when calculating the
capacity.
3.11.2 If using the Compressor
Calibration Method as the secondary test
method.
a. Conduct separate calibration tests using
a calorimeter to determine the refrigerant
flow rate. Or for cases where the superheat
of the refrigerant leaving the evaporator is
less than 5 °F, use the calorimeter to measure
total capacity rather than refrigerant flow
rate. Conduct these calibration tests at the
same test conditions as specified for the tests
in this appendix. Operate the unit for at least
one hour or until obtaining equilibrium
conditions before collecting data that will be
used in determining the average refrigerant
flow rate or total capacity. Sample the data
at equal intervals that span 5 minutes or less.
Determine average flow rate or average
capacity from data sampled over a 30-minute
period where the Table 8 (cooling) or the
Table 15 (heating) tolerances are satisfied.
Otherwise, conduct the calibration tests
according to sections 5, 6, 7, and 8 of
ASHRAE Standard 23.1–2010 (incorporated
by reference, see § 430.3); sections 5, 6, 7, 8,
9, and 11 of ASHRAE Standard 41.9–2011
(incorporated by reference, see § 430.3); and
section 7.4 of ASHRAE Standard 37–
2009(incorporated by reference, see § 430.3).
b. Calculate space cooling and space
heating capacities using the compressor
calibration method measurements as
specified in section 7.4.5 and 7.4.6
respectively, of ASHRAE Standard 37–2009.
3.11.3 If using the Refrigerant-Enthalpy
Method as the secondary test method.
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Conduct this secondary method according
to section 7.5 of ASHRAE Standard 37–2009.
Calculate space cooling and heating
capacities using the refrigerant-enthalpy
method measurements as specified in
sections 7.5.4 and 7.5.5, respectively, of the
same ASHRAE Standard.
3.12 Rounding of space conditioning
capacities for reporting purposes.
a. When reporting rated capacities, round
them off as specified in § 430.23 (for a single
unit) and in 10 CFR 429.16 (for a sample).
b. For the capacities used to perform the
section 4 calculations, however, round only
to the nearest integer.
3.13 Laboratory testing to determine off
mode average power ratings.
Conduct one of the following tests after the
completion of the B, B1, or B2 Test,
whichever comes last: If the central air
conditioner or heat pump lacks a compressor
crankcase heater, perform the test in Section
3.13.1; if the central air conditioner or heat
pump has compressor crankcase heater that
lacks controls, perform the test in Section
3.13.1; if the central air conditioner or heat
pump has a compressor crankcase heater
equipped with controls, perform the test in
Section 3.13.2.
3.13.1 This test determines the off mode
average power rating for central air
conditioners and heat pumps that lack a
compressor crankcase heater, or have a
compressor crankcase heater that lacks
controls.
a. Configure Controls: Configure the
controls of the central air conditioner or heat
pump so that it operates as if connected to
a building thermostat that is set to the OFF
position. This particular test contains no
requirements as to ambient conditions within
the test rooms, and room conditions are
allowed to change during the test. Ensure
that the low-voltage transformer and lowvoltage components are connected.
b. Measure P1x: Determine the average
power from non-zero value data measured
over a 5-minute interval of the non-operating
central air conditioner or heat pump and
designate the average power as P1x, the
shoulder season total off mode power.
c. Measure Px for coil-only split systems
(that would be installed in the field with a
furnace having a dedicated board for indoor
controls) and for blower-coil split systems for
which a furnace is the designated air mover:
Disconnect all low-voltage wiring for the
outdoor components and outdoor controls
from the low-voltage transformer. Determine
the average power from non-zero value data
measured over a 5-minute interval of the
power supplied to the (remaining) lowvoltage components of the central air
conditioner or heat pump, or low-voltage
power, Px.
d. Calculate P1:
Single-package systems and blower coil
split systems for which the designated air
mover is not a furnace: Divide the shoulder
season total off mode power (P1x) by the
number of compressors to calculate P1, the
shoulder season per-compressor off mode
power. If the compressor is a modulatingtype, assign a value of 1.5 for the number of
compressors. Round P1 to the nearest watt
and record as both P1 and P2, the latter of
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which is the heating season per-compressor
off mode power. The expression for
calculating P1 is as follows:
Coil-only split systems (that would be
installed in the field with a furnace having
a dedicated board for indoor controls) and
blower-coil split systems for which a furnace
is the designated air mover: Subtract the lowvoltage power (Px) from the shoulder season
total off mode power (P1x) and divide by the
number of compressors to calculate P1, the
shoulder season per-compressor off mode
power. If the compressor is a modulatingtype, assign a value of 1.5 for the number of
compressors. Round P1 to the nearest watt
and record as both P1 and P2, the latter of
which is the heating season per-compressor
off mode power. The expression for
calculating P1 is as follows:
3.13.2 This test determines the off mode
average power rating for central air
conditioners and heat pumps that have a
compressor crankcase heater equipped with
controls.
a. Configure Controls: Position a
temperature sensor to measure the outdoor
dry-bulb temperature in the air between 2
and 6 inches from the crankcase heater
temperature sensor or, if no such temperature
sensor exists, position it in the air between
2 and 6 inches from the crankcase heater.
Utilize the temperature measurements from
this sensor for this portion of the test
procedure. Configure the controls of the
central air conditioner or heat pump so that
it operates as if connected to a building
thermostat that is set to the OFF position.
Ensure that the low-voltage transformer and
low-voltage components are connected.
Adjust the outdoor temperature at a rate of
change of no more than 20 °F per hour and
achieve an outdoor dry-bulb temperature of
72 °F. Maintain this temperature within ±2 °F
for at least 5 minutes, while maintaining an
indoor dry-bulb temperature of between 75
°F and 85 °F.
b. Measure P1x: Determine the average
power from non-zero value data measured
over a 5-minute interval of the non-operating
central air conditioner or heat pump and
designate the average power as P1x, the
shoulder season total off mode power.
c. Reconfigure Controls: In the process of
reaching the target outdoor dry-bulb
temperature, adjust the outdoor temperature
at a rate of change of no more than 20 °F per
hour. This target temperature is the
temperature specified by the manufacturer in
the DOE Compliance Certification Database
at which the crankcase heater turns on,
minus five degrees Fahrenheit. Maintain this
temperature within ±2 °F for at least 5
minutes, while maintaining an indoor drybulb temperature of between 75 °F and 85 °F.
d. Measure P2x: Determine the average nonzero power of the non-operating central air
conditioner or heat pump over a 5-minute
interval and designate it as P2x, the heating
season total off mode power.
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f. Calculate P1:
Single-package systems and blower coil
split systems for which the air mover is not
a furnace: Divide the shoulder season total
off mode power (P1x) by the number of
compressors to calculate P1, the shoulder
season per-compressor off mode power.
Round to the nearest watt. If the compressor
is a modulating-type, assign a value of 1.5 for
the number of compressors. The expression
for calculating P1 is as follows:
Coil-only split systems (that would be
installed in the field with a furnace having
a dedicated board for indoor controls) and
blower-coil split systems for which a furnace
is the designated air mover: Subtract the lowvoltage power (Px) from the shoulder season
total off mode power (P1x) and divide by the
number of compressors to calculate P1, the
shoulder season per-compressor off mode
power. Round to the nearest watt. If the
compressor is a modulating-type, assign a
value of 1.5 for the number of compressors.
The expression for calculating P1 is as
follows:
h. Calculate P2:
Single-package systems and blower coil
split systems for which the air mover is not
a furnace: Divide the heating season total off
mode power (P2x) by the number of
compressors to calculate P2, the heating
season per-compressor off mode power.
Round to the nearest watt. If the compressor
is a modulating-type, assign a value of 1.5 for
the number of compressors. The expression
for calculating P2 is as follows:
Coil-only split systems (that would be
installed in the field with a furnace having
a dedicated board for indoor controls) and
blower-coil split systems for which a furnace
is the designated air mover: Subtract the low-
voltage power (Px) from the heating season
total off mode power (P2x) and divide by the
number of compressors to calculate P2, the
heating season per-compressor off mode
power. Round to the nearest watt. If the
compressor is a modulating-type, assign a
value of 1.5 for the number of compressors.
The expression for calculating P2 is as
follows:
4. Calculations of Seasonal Performance
Descriptors
4.1 Seasonal Energy Efficiency Ratio
(SEER) Calculations. SEER must be
calculated as follows: For equipment covered
under sections 4.1.2, 4.1.3, and 4.1.4,
evaluate the seasonal energy efficiency ratio,
EP09NO15.053</GPH>
e. Measure Px for coil-only split systems
(that would be installed in the field with a
furnace having a dedicated board for indoor
controls) and for blower-coil split systems for
which a furnace is the designated air mover:
Disconnect all low-voltage wiring for the
outdoor components and outdoor controls
from the low-voltage transformer. Determine
the average power from non-zero value data
measured over a 5-minute interval of the
power supplied to the (remaining) lowvoltage components of the central air
conditioner or heat pump, or low-voltage
power, Px.
EP09NO15.050</GPH>
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EP09NO15.051</GPH>
EP09NO15.052</GPH>
Where,
69376
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
season bin temperatures being 67, 72, 77,
82, 87, 92, 97, and 102 °F.
j = the bin number. For cooling season
calculations, j ranges from 1 to 8.
Additionally, for sections 4.1.2, 4.1.3, and
4.1.4, use a building cooling load, BL(Tj).
When referenced, evaluate BL(Tj) for cooling
using,
where,
˙
Qck=2(95) = the space cooling capacity
determined from the A2 Test and
calculated as specified in section 3.3,
Btu/h.
1.1 = sizing factor, dimensionless.
The temperatures 95 °F and 65 °F in the
building load equation represent the selected
outdoor design temperature and the zero-load
base temperature, respectively.
4.1.1 SEER calculations for an air
conditioner or heat pump having a singlespeed compressor that was tested with a
fixed-speed indoor blower installed, a
constant-air-volume-rate indoor blower
installed, or with no indoor blower installed.
a. Evaluate the seasonal energy efficiency
ratio, expressed in units of Btu/watt-hour,
using:
SEER = PLF(0.5) * EERB
where,
PLF(0.5) = 1 ¥ 0.5 · CDc, the part-load
performance factor evaluated at a cooling
load factor of 0.5, dimensionless.
b. Refer to section 3.3 regarding the
˙
definition and calculation of Qc(82) and
˙
Ec(82).
4.1.2 SEER calculations for an air
conditioner or heat pump having a singlespeed compressor and a variable-speed
variable-air-volume-rate indoor blower.
4.1.2.1 Units covered by section 3.2.2.1
where indoor blower capacity modulation
correlates with the outdoor dry bulb
temperature. The manufacturer must provide
information on how the indoor air volume
rate or the indoor blower speed varies over
the outdoor temperature range of 67 °F to 102
°F. Calculate SEER using Equation 4.1–1.
Evaluate the quantity qc(Tj)/N in Equation
4.1–1 using,
during the cooling season when the
outdoor temperature fell within the
range represented by bin temperature Tj
to the total number of hours in the
cooling season, dimensionless.
a. For the space cooling season, assign nj/
N as specified in Table 18. Use Equation 4.1–
2 to calculate the building load, BL(Tj).
˙
Evaluate Qc(Tj) using,
EP09NO15.056</GPH>
the space cooling capacity of the test unit at
outdoor temperature Tj if operated at the
Cooling Minimum Air Volume Rate, Btu/h.
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EP09NO15.057</GPH>
where,
˙
Qc(Tj) = the space cooling capacity of the test
unit when operating at outdoor
temperature, Tj, Btu/h.
nj/N = fractional bin hours for the cooling
season; the ratio of the number of hours
EP09NO15.058</GPH>
Tj = the outdoor bin temperature, °F. Outdoor
temperatures are grouped or ‘‘binned.’’
Use bins of 5 °F with the 8 cooling
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69377
the space cooling capacity of the test unit at
outdoor temperature Tj if operated at the
Cooling Full-load Air Volume Rate, Btu/h.
b. For units where indoor blower speed is
the primary control variable, FPck=1 denotes
the fan speed used during the required A1
and B1 Tests (see section 3.2.2.1), FPck=2
denotes the fan speed used during the
required A2 and B2 Tests, and FPc(Tj) denotes
the fan speed used by the unit when the
outdoor temperature equals Tj. For units
where indoor air volume rate is the primary
control variable, the three FPc’s are similarly
defined only now being expressed in terms
of air volume rates rather than fan speeds.
Refer to sections 3.2.2.1, 3.1.4 to 3.1.4.2, and
3.3 regarding the definitions and calculations
˙
˙
˙
of Qck=1(82), Qck=1(95),Qck=2(82), and
˙
Qck=2(95).
where,
PLFj = 1 ¥ CDc · [1 ¥ X(Tj)], the part load
factor, dimensionless.
˙
Ec(Tj) = the electrical power consumption of
the test unit when operating at outdoor
temperature Tj, W.
c. The quantities X(Tj) and nj/N are the
same quantities as used in Equation 4.1.2–1.
˙
d. Evaluate Ec(Tj) using,
e. The parameters FPck=1, and FPck=2, and
FPc(Tj) are the same quantities that are used
when evaluating Equation 4.1.2–2. Refer to
sections 3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3
regarding the definitions and calculations of
˙
˙
˙
˙
Eck=1(82), Eck=1(95), Eck=2(82), and Eck=2(95).
4.1.2.2 Units covered by section 3.2.2.2
where indoor blower capacity modulation is
used to adjust the sensible to total cooling
capacity ratio. Calculate SEER as specified in
section 4.1.1.
4.1.3 SEER calculations for an air
conditioner or heat pump having a two-
capacity compressor. Calculate SEER using
Equation 4.1–1. Evaluate the space cooling
˙
capacity, Qck=1 (Tj), and electrical power
˙
consumption, Eck=1 (Tj), of the test unit when
operating at low compressor capacity and
outdoor temperature Tj using,
˙
˙
where Qck=1 (82) and Eck=1 (82) are
˙
determined from the B1 Test, Qck=1 (67) and
˙
Eck=1 (67) are determined from the F1Test,
and all four quantities are calculated as
specified in section 3.3. Evaluate the space
˙
cooling capacity, Qck=2 (Tj), and electrical
˙
power consumption, Eck=2 (Tj), of the test
unit when operating at high compressor
capacity and outdoor temperature Tj using,
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EP09NO15.062</GPH>
EP09NO15.063</GPH>
the electrical power consumption of the test
unit at outdoor temperature Tj if operated at
the Cooling Minimum Air Volume Rate, W.
69378
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
˙
˙
where Qck=2(95) and Eck=2(95) are determined
˙
˙
from the A2 Test, Qck=2(82), and Eck=2(82), are
determined from the B2Test, and all are
calculated as specified in section 3.3.
The calculation of Equation 4.1–1
quantities qc(Tj)/N and ec(Tj)/N differs
depending on whether the test unit would
operate at low capacity (section 4.1.3.1),
cycle between low and high capacity (section
4.1.3.2), or operate at high capacity (sections
4.1.3.3 and 4.1.3.4) in responding to the
building load. For units that lock out low
capacity operation at higher outdoor
temperatures, the manufacturer must supply
information regarding this temperature so
that the appropriate equations are used. Use
Equation 4.1–2 to calculate the building load,
BL(Tj), for each temperature bin.
4.1.3.1 Steady-state space cooling
capacity at low compressor capacity is
greater than or equal to the building cooling
˙
load at temperature Tj, Qck=1(Tj) ≥ BL(Tj).
where,
˙
Xk=1(Tj) = BL(Tj)/Qck=1 (Tj), the cooling mode
low capacity load factor for temperature
bin j, dimensionless.
PLFj = 1 ¥ CDc · [1 ¥ Xk=1(Tj)], the part load
factor, dimensionless.
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 18. Use
Equations 4.1.3–1 and 4.1.3–2, respectively,
˙
˙
to evaluate Qck=1(Tj) and Eck=1(Tj).
TABLE 18—DISTRIBUTION OF FRACTIONAL HOURS WITHIN COOLING SEASON TEMPERATURE BINS
.................................................................................................................................
.................................................................................................................................
.................................................................................................................................
.................................................................................................................................
.................................................................................................................................
.................................................................................................................................
.................................................................................................................................
.................................................................................................................................
4.1.3.2 Unit alternates between high (k=2)
and low (k=1) compressor capacity to satisfy
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65–69
70–74
75–79
80–84
85–89
90–94
95–99
100–104
67
72
77
82
87
92
97
102
the building cooling load at temperature Tj,
˙
˙
Qck=1(Tj) <BL(Tj) <Qck=2(Tj).
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Fraction of total
temperature bin
hours, nj/N
0.214
0.231
0.216
0.161
0.104
0.052
0.018
0.004
EP09NO15.066</GPH>
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1
2
3
4
5
6
7
8
Representative
temperature for
bin °F
09NOP2
EP09NO15.064</GPH> EP09NO15.065</GPH>
Bin temperature
range °F
Bin number, j
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69379
where,
Equations 4.1.3–1 and 4.1.3–2, respectively,
˙
˙
to evaluate Qck=1(Tj) and Eck=1(Tj). Use
Equations 4.1.3–3 and 4.1.3–4, respectively,
˙
˙
to evaluate Qck=2(Tj) and Eck=2(Tj).
4.1.3.3 Unit only operates at high (k=2)
compressor capacity at temperature Tj and its
capacity is greater than the building cooling
load, BL(Tj) < Qck=2(Tj). This section applies
to units that lock out low compressor
capacity operation at higher outdoor
temperatures.
where,
˙
Xk=2(Tj) = BL(Tj)/Qck=2(Tj), the cooling mode
high capacity load factor for temperature
bin j, dimensionless.
PLFj = 1 ¥ CDc(k = 2) * [1 ¥ Xk=2(Tj) the part
load factor, dimensionless.
4.1.4 SEER calculations for an air
conditioner or heat pump having a variablespeed compressor. Calculate SEER using
Equation 4.1–1. Evaluate the space cooling
˙
capacity, Qck=1(Tj), and electrical power
˙
consumption, Eck=1(Tj), of the test unit when
operating at minimum compressor speed and
outdoor temperature Tj. Use,
EP09NO15.072</GPH>
Xk=2(Tj) = 1 ¥ Xk=1(Tj), the cooling mode,
high capacity load factor for temperature
bin j, dimensionless.
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 18. Use
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tkelley on DSK3SPTVN1PROD with PROPOSALS2
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 18. Use
Equations 4.1.3–3 and 4.1.3–4, respectively,
˙
˙
to evaluate Qck=2(Tj) and Eck=2(Tj).
EP09NO15.071</GPH>
4.1.3.4 Unit must operate continuously at
high (k=2) compressor capacity at
˙
temperature Tj, BL(Tj) ≥ Qck=2(Tj).
69380
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
operating at maximum compressor speed and
outdoor temperature Tj. Use Equations 4.1.3–
˙
3 and 4.1.3–4, respectively, where Qck=2(95)
˙
and Eck=2(95) are determined from the A2
˙
˙
Test, Qck=2(82) and Eck=2(82) are determined
from the B2 Test, and all four quantities are
calculated as specified in section 3.3.
4.1.4.1 Steady-state space cooling
capacity when operating at minimum
compressor speed is greater than or equal to
the building cooling load at temperature Tj,
˙
Qck=1(Tj) ≥ BL(Tj).
where,
˙
Xk=1(Tj) = BL(Tj)/Qck=1(Tj), the cooling mode
minimum speed load factor for
temperature bin j, dimensionless.
PLFj = 1 ¥ CDc ˙ [1 ¥ Xk=1(Tj)], the part load
·
factor, dimensionless.
nj/N = fractional bin hours for the cooling
season; the ratio of the number of hours
during the cooling season when the
outdoor temperature fell within the
range represented by bin temperature Tj
to the total number of hours in the
cooling season, dimensionless.
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 18. Use
Equations 4.1.3–1 and 4.1.3–2, respectively,
˙
˙
to evaluate Qck=1 (Tj) and Eck=1 (Tj).
4.1.4.2 Unit operates at an intermediate
compressor speed (k=i) in order to match the
building cooling load at temperature
˙
˙
Tj,Qck=1(Tj) < BL(Tj) < Qck=2(Tj).
where,
˙
Qck=i(Tj) = BL(Tj), the space cooling capacity
delivered by the unit in matching the
building load at temperature Tj, Btu/h.
The matching occurs with the unit
operating at compressor speed k = i.
the electrical power input required by the
test unit when operating at a compressor
speed of k = i and temperature Tj, W.
EERk=i(Tj) = the steady-state energy efficiency
ratio of the test unit when operating at
a compressor speed of k = i and
temperature Tj, Btu/h per W.
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 18. For each
temperature bin where the unit operates at an
intermediate compressor speed, determine
the energy efficiency ratio EERk=i(Tj) using,
EERk=i(Tj) = A + B · Tj + C · Tj2.
For each unit, determine the coefficients A,
B, and C by conducting the following
calculations once:
EP09NO15.075</GPH>
EP09NO15.076</GPH>
EP09NO15.077</GPH>
Calculate the space cooling capacity,
˙
Qck=v(Tj), and electrical power consumption,
˙
Eck=v(Tj), of the test unit when operating at
outdoor temperature Tj and the intermediate
compressor speed used during the section
3.2.4 (and Table 7) EV Test using,
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˙
˙
where Qck=1(82) and Eck=1(82) are determined
˙
˙
from the B1 Test, Qck=1(67) and Eck=1(67) are
determined from the F1 Test, and all four
quantities are calculated as specified in
section 3.3. Evaluate the space cooling
˙
capacity, Qck=2(Tj), and electrical power
˙
consumption, Eck=2(Tj), of the test unit when
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69381
T2 = the outdoor temperature at which the
unit, when operating at maximum
compressor speed, provides a space
cooling capacity that is equal to the
˙
building load (Qck=2 (T2) = BL(T2)), °F.
Determine T2 by equating Equations
4.1.3–3 and 4.1–2 and solving for
outdoor temperature.
as specified in section 4.1.3.4 with the
˙
˙
understanding that Qck=2(Tj) and Eck=2(Tj)
correspond to maximum compressor speed
operation and are derived from the results of
the tests specified in section 3.2.4.
4.1.5 SEER calculations for an air
conditioner or heat pump having a single
indoor unit with multiple blowers. Calculate
SEER using Eq. 4.1–1, where qc(Tj)/N and
ec(Tj)/N are evaluated as specified in
applicable below subsection.
4.1.5.1 For multiple blower systems that
are connected to a lone, single-speed outdoor
unit. a. Calculate the space cooling capacity,
˙
Qk=1(Tj), and electrical power consumption,
˙
Ek=1(Tj), of the test unit when operating at the
cooling minimum air volume rate and
outdoor temperature Tj using the equations
given in section 4.1.2.1. Calculate the space
˙
cooling capacity, Qk=2(Tj), and electrical
˙
power consumption, Ek=2(Tj), of the test unit
when operating at the cooling full-load air
volume rate and outdoor temperature Tj
using the equations given in section 4.1.2.1.
In evaluating the section 4.1.2.1 equations,
˙
determine the quantities Qk=1(82) and
˙
˙
Ek=1(82) from the B1 Test, Qk=1(95) and
˙
˙
Ek=1(82) from the Al Test, Qk=2(82) and
˙
˙
Ek=2(82) from the B2 Test, and Qk=2(95) and
˙
Ek=2(95) from the A2 Test. Evaluate all eight
quantities as specified in section 3.3. Refer to
section 3.2.2.1 and Table 5 for additional
information on the four referenced laboratory
tests. b. Determine the cooling mode cyclic
degradation coefficient, CDc, as per sections
3.2.2.1 and 3.5 to 3.5.3. Assign this same
value to CDc(K=2). c. Except for using the
˙
˙
˙
above values of Qk=1(Tj), Ek=1(Tj), Ek=2(Tj),
˙
Qk=2(Tj), CDc, and CDc (K=2), calculate the
quantities qc(Tj)/N and ec(Tj)/N as specified
˙
in section 4.1.3.1 for cases where Qk=1(Tj) ≥
BL(Tj). For all other outdoor bin
temperatures, Tj, calculate qc(Tj)/N and
ec(Tj)/N as specified in section 4.1.3.3 if
˙
Qk=2(Tj) > BL (Tj) or as specified in section
˙
4.1.3.4 if Qk=2(Tj) ≤ BL(Tj).
4.1.5.2 For multiple blower systems that
are connected to either a lone outdoor unit
having a two-capacity compressor or to two
separate but identical model single-speed
outdoor units. Calculate the quantities qc(Tj)/
N and ec(Tj)/N as specified in section 4.1.3.
4.2 Heating Seasonal Performance Factor
(HSPF) Calculations. Unless an approved
alternative efficiency determination method
is used, as set forth in 10 CFR 429.70(e),
HSPF must be calculated as follows: Six
generalized climatic regions are depicted in
Figure 1 and otherwise defined in Table 19.
For each of these regions and for each
applicable standardized design heating
requirement, evaluate the heating seasonal
performance factor using,
Where,
eh(Tj)/N = The ratio of the electrical energy
consumed by the heat pump during
periods of the space heating season when
the outdoor temperature fell within the
range represented by bin temperature Tj
to the total number of hours in the
heating season (N), W. For heat pumps
having a heat comfort controller, this
ratio may also include electrical energy
used by resistive elements to maintain a
minimum air delivery temperature (see
4.2.5).
RH(Tj)/N = The ratio of the electrical energy
used for resistive space heating during
periods when the outdoor temperature
fell within the range represented by bin
temperature Tj to the total number of
hours in the heating season (N), W.
Except as noted in section 4.2.5, resistive
space heating is modeled as being used
to meet that portion of the building load
that the heat pump does not meet
because of insufficient capacity or
because the heat pump automatically
turns off at the lowest outdoor
temperatures. For heat pumps having a
heat comfort controller, all or part of the
electrical energy used by resistive
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˙
temperature Tj, BL(Tj) ≥Qck=2(Tj). Evaluate
the Equation 4.1–1 quantities
EP09NO15.078</GPH> EP09NO15.079</GPH>
Tv = the outdoor temperature at which the
unit, when operating at the intermediate
compressor speed used during the
section 3.2.4 EV Test, provides a space
cooling capacity that is equal to the
˙
building load (Qck=v (Tv) = BL(Tv)), °F.
Determine Tv by equating Equations
4.1.4–1 and 4.1–2 and solving for
outdoor temperature.
4.1.4.3 Unit must operate continuously at
maximum (k=2) compressor speed at
tkelley on DSK3SPTVN1PROD with PROPOSALS2
where,
T1 = the outdoor temperature at which the
unit, when operating at minimum
compressor speed, provides a space
cooling capacity that is equal to the
˙
building load (Qck=1 (Tl) = BL(T1)), °F.
Determine T1 by equating Equations
4.1.3–1 and 4.1–2 and solving for
outdoor temperature.
69382
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
heaters at a particular bin temperature
may be reflected in eh(Tj)/N (see 4.2.5).
Tj = the outdoor bin temperature, °F. Outdoor
temperatures are ‘‘binned’’ such that
calculations are only performed based
one temperature within the bin. Bins of
5 °F are used.
nj/N = Fractional bin hours for the heating
season; the ratio of the number of hours
during the heating season when the
outdoor temperature fell within the
range represented by bin temperature Tj
to the total number of hours in the
heating season, dimensionless. Obtain
nj/N values from Table 19.
j = the bin number, dimensionless.
J = for each generalized climatic region, the
total number of temperature bins,
dimensionless. Referring to Table 19, J is
the highest bin number (j) having a
nonzero entry for the fractional bin hours
for the generalized climatic region of
interest.
Fdef = the demand defrost credit described in
section 3.9.2, dimensionless.
BL(Tj) = the building space conditioning load
corresponding to an outdoor temperature
of Tj; the heating season building load
also depends on the generalized climatic
region’s outdoor design temperature and
the design heating requirement, Btu/h.
TABLE 19—GENERALIZED CLIMATIC REGION INFORMATION
Region Number
I
II
III
Heating Load Hours, HLH .......................
Outdoor Design Temperature, TOD ..........
750
37
1250
27
j Tj (°F) .....................................................
1 62 ........................................................
.291
.215
2
3
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
.239
.194
.129
.081
.041
.019
.005
.001
0
0
0
0
0
0
0
0
0
.189
.163
.143
.112
.088
.056
.024
.008
.002
0
0
0
0
0
0
0
0
57 ........................................................
52 ........................................................
47 ........................................................
42 ........................................................
37 ........................................................
32 ........................................................
27 ........................................................
22 ........................................................
17 ......................................................
12 ......................................................
7 ........................................................
2 ........................................................
¥3 ....................................................
¥8 ....................................................
¥13 ..................................................
¥18 ..................................................
¥23 ..................................................
IV
1750
17
V
VI
2250
5
2750
¥10
* 2750
30
Fractional Bin Hours, nj/N
.153
.132
.106
.113
.092
.086
.076
.078
.087
.102
.094
.074
.055
.047
.038
.029
.018
.010
.005
.002
.001
.206
.215
.204
.141
.076
.034
.008
.003
0
0
0
0
0
0
0
0
0
.142
.138
.137
.135
.118
.092
.047
.021
.009
.005
.002
.001
0
0
0
0
0
.111
.103
.093
.100
.109
.126
.087
.055
.036
.026
.013
.006
.002
.001
0
0
0
* Pacific Coast Region.
Evaluate the building heating load using
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C = 0.77, a correction factor which tends to
improve the agreement between
calculated and measured building loads,
dimensionless.
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DHR = the design heating requirement (see
section 1.2, Definitions), Btu/h.
Calculate the minimum and maximum
design heating requirements for each
generalized climatic region as follows:
E:\FR\FM\09NOP2.SGM
09NOP2
EP09NO15.081</GPH> EP09NO15.082</GPH>
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Where,
TOD = the outdoor design temperature, °F. An
outdoor design temperature is specified
for each generalized climatic region in
Table 19.
69383
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
˙
Where Qhk(47) is expressed in units of Btu/
h and otherwise defined as follows:
1. For a single-speed heat pump tested as
˙
˙
per section 3.6.1, Qhk(47) = Qh(47), the space
heating capacity determined from the H1
Test.
2. For a variable-speed heat pump, a
section 3.6.2 single-speed heat pump, or a
two-capacity heat pump not covered by item
˙
˙
3, Qnk(47) = Qnk=2(47), the space heating
capacity determined from the H12 Test.
3. For two-capacity, northern heat pumps
˙
(see section 1.2, Definitions), Qkh(47) =
˙
Qk=1h(47), the space heating capacity
determined from the H11 Test.
If the optional H1N Test is conducted on
a variable-speed heat pump, the
manufacturer has the option of defining
˙
Qkh(47) as specified above in item 2 or as
˙
˙
Qkh(47)=Qk=Nh(47), the space heating
capacity determined from the H1N Test.
For all heat pumps, HSPF accounts for the
heating delivered and the energy consumed
by auxiliary resistive elements when
operating below the balance point. This
condition occurs when the building load
exceeds the space heating capacity of the
heat pump condenser. For HSPF calculations
for all heat pumps, see either section 4.2.1,
4.2.2, 4.2.3, or 4.2.4, whichever applies.
For heat pumps with heat comfort
controllers (see section 1.2, Definitions),
HSPF also accounts for resistive heating
contributed when operating above the heatpump-plus-comfort-controller balance point
as a result of maintaining a minimum supply
temperature. For heat pumps having a heat
comfort controller, see section 4.2.5 for the
additional steps required for calculating the
HSPF.
TABLE 20—STANDARDIZED DESIGN
HEATING REQUIREMENTS (BTU/H)
5,000
10,000
15,000
20,000
25,000
30,000
35,000
40,000
50,000
60,000
70,000
80,000
90,000
100,000
110,000
130,000
4.2.1 Additional steps for calculating the
HSPF of a heat pump having a single-speed
compressor that was tested with a fixedspeed indoor blower installed, a constant-airvolume-rate indoor blower installed, or with
no indoor blower installed.
where,
(If no such temperature exists, Tj is
always greater than Toff and Ton).
Ton = the outdoor temperature when the
compressor is automatically turned back
on, if applicable, following an automatic
shut-off, °F.
˙
˙
Calculate Qh(Tj) and Eh(Tj) using,
EP09NO15.086</GPH>
Use Equation 4.2–2 to determine BL(Tj).
Obtain fractional bin hours for the heating
season, nj/N, from Table 19.
Determine the low temperature cut-out
factor using
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˙
Eh(Tj) = the electrical power consumption of
the heat pump when operating at
outdoor temperature Tj, W.
d(Tj) = the heat pump low temperature cutout factor, dimensionless.
˙
PLFj = 1 ¥ CDh · [1 ¥X(Tj)] the part load
factor, dimensionless.
where,
Toff = the outdoor temperature when the
compressor is automatically shut off, °F.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
whichever is less; the heating mode load
factor for temperature bin j, dimensionless.
˙
Qh(Tj) = the space heating capacity of the
heat pump when operating at outdoor
temperature Tj, Btu/h.
69384
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
determined from the H3 Test and calculated
as specified in section 3.10.
4.2.2 Additional steps for calculating the
HSPF of a heat pump having a single-speed
compressor and a variable-speed, variableair-volume-rate indoor blower. The
manufacturer must provide information
about how the indoor air volume rate or the
indoor blower speed varies over the outdoor
temperature range of 65°F to ¥23°F.
Calculate the quantities
in Equation 4.2–1 as specified in section
4.2.1 with the exception of replacing
references to the H1C Test and section 3.6.1
with the H1C1 Test and section 3.6.2. In
addition, evaluate the space heating capacity
and electrical power consumption of the heat
˙
˙
pump Qh(Tj) and Eh(Tj) using
where the space heating capacity and
electrical power consumption at both low
capacity (k=1) and high capacity (k=2) at
outdoor temperature Tj are determined using
For units where indoor blower speed is the
primary control variable, FPhk=1 denotes the
fan speed used during the required H11 and
H31 Tests (see Table 11), FPhk=2 denotes the
fan speed used during the required H12, H22,
and H32 Tests, and FPh(Tj) denotes the fan
speed used by the unit when the outdoor
temperature equals Tj. For units where indoor
air volume rate is the primary control
variable, the three FPh’s are similarly defined
only now being expressed in terms of air
volume rates rather than fan speeds.
˙
˙
Determine Qhk=1(47) and Ehk=1(47) from the
˙
˙
H11 Test, and Qhk=2(47) and Ehk=2(47) from
the H12 Test. Calculate all four quantities as
˙
specified in section 3.7. Determine Qhk=1(35)
˙
and Ehk=1(35) as specified in section 3.6.2;
˙
˙
determine Qhk=2(35) and Ehk=2(35) and from
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09NOP2
EP09NO15.089</GPH>
the H22 Test and the calculation specified in
˙
˙
section 3.9. Determine Qhk=1(17) and Ehk=1(17
˙
from the H31 Test, and Qhk=2(17) and
˙
Ehk=2(17) from the H32 Test. Calculate all four
quantities as specified in section 3.10.
4.2.3 Additional steps for calculating the
HSPF of a heat pump having a two-capacity
compressor. The calculation of the Equation
4.2–1 quantities differ depending upon
EP09NO15.087</GPH> EP09NO15.088</GPH>
tkelley on DSK3SPTVN1PROD with PROPOSALS2
EP09NO15.090</GPH>
˙
˙
where Qh(47) and Eh(47) are determined from
the H1 Test and calculated as specified in
˙
˙
section 3.7; Qh(35) and Eh(35) are determined
from the H2 Test and calculated as specified
˙
˙
in section 3.9.1; and Qh(17) and Eh(17) are
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69385
regarding the cutoff temperature(s) so that the
appropriate equations can be selected.
b. Evaluate the space heating capacity and
˙
electrical power consumption (Qhk=2(Tj) and
˙
Ehk=2 (Tj)) of the heat pump when operating
at high compressor capacity and outdoor
temperature Tj by solving Equations 4.2.2–3
and 4.2.2–4, respectively, for k=2. Determine
˙
˙
Qhk=1(62) and Ehk=1(62) from the H01 Test,
˙
˙
Qhk=1(47) and Ehk=1(47) from the H11 Test,
˙
˙
and Qhk=2(47) and Ehk=2(47) from the H12
Test. Calculate all six quantities as specified
˙
in section 3.7. Determine Qhk=2(35) and
˙
Ehk=2(35) from the H22 Test and, if required
as described in section 3.6.3, determine
˙
˙
Qhk=1(35) and Ehk=1(35) from the H21 Test.
Calculate the required 35°F quantities as
˙
specified in section 3.9. Determine Qhk=2(17)
˙
and Ehk=2(17) from the H32 Test and, if
required as described in section 3.6.3,
˙
˙
determine Qhk=1(17) and Ehk=1(17) from the
H31 Test. Calculate the required 17 °F
quantities as specified in section 3.10.
4.2.3.1 Steady-state space heating
capacity when operating at low compressor
capacity is greater than or equal to the
building heating load at temperature Tj,
˙
Qhk=1(Tj) ≥BL(Tj).
Where,
˙
Xk=1(Tj) = BL(Tj) / Qhk=1(Tj), the heating mode
low capacity load factor for temperature
bin j, dimensionless.
PLFj = 1¥CDh · [ 1¥Xk=1(Tj)], the part load
factor, dimensionless.
d′(Tj) = the low temperature cutoff factor,
dimensionless.
Determine the low temperature cut-out
factor using
Where Toff and Ton are defined in section
4.2.1. Use the calculations given in
section 4.2.3.3, and not the above, if:
(a) The heat pump locks out low capacity
operation at low outdoor temperatures and
(b) Tj is below this lockout threshold
temperature.
4.2.3.2 Heat pump alternates between
high (k=2) and low (k=1) compressor
capacity to satisfy the building heating load
EP09NO15.094</GPH>
pump when operating at low compressor
capacity and outdoor temperature Tj using
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4.2.3.4) in responding to the building load.
For heat pumps that lock out low capacity
operation at low outdoor temperatures, the
manufacturer must supply information
a. Evaluate the space heating capacity and
electrical power consumption of the heat
tkelley on DSK3SPTVN1PROD with PROPOSALS2
whether the heat pump would operate at low
capacity (section 4.2.3.1), cycle between low
and high capacity (Section 4.2.3.2), or
operate at high capacity (sections 4.2.3.3 and
69386
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
˙
at a temperature Tj, Qhk=1(Tj) <BL(Tj)
˙
<Qhk=2(Tj).
Where,
Xk=2(Tj) = 1¥Xk=1(Tj) the heating mode, high
capacity load factor for temperature bin
j, dimensionless.
Determine the low temperature cut-out
factor, d′(Tj), using Equation 4.2.3–3.
4.2.3.3 Heat pump only operates at high
(k=2) compressor capacity at temperature Tj
and its capacity is greater than the building
˙
heating load, BL(Tj) <Qhk=2(Tj). This section
applies to units that lock out low compressor
capacity operation at low outdoor
temperatures.
Where,
˙
Xk=2(Tj) = BL(Tj)/Qhk=2(Tj). PLFj = 1¥CDh(k
= 2) * [1¥Xk=2(Tj)
If the H1C2 Test described in section 3.6.3
and Table 12 is not conducted, set CDh (k=2)
equal to the default value specified in section
3.8.1.
Determine the low temperature cut-out
factor, d(Tj), using Equation 4.2.3–3.
4.2.3.4 Heat pump must operate
continuously at high (k=2) compressor
˙
capacity at temperature Tj, BL(Tj) ≥ Qhk=2(Tj).
4.2–1. Evaluate the space heating capacity,
˙
Qhk=1(Tj), and electrical power consumption,
˙
Ehk=1(Tj), of the heat pump when operating at
minimum compressor speed and outdoor
temperature Tj using
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09NOP2
EP09NO15.097</GPH>
4.2.4 Additional steps for calculating the
HSPF of a heat pump having a variable-speed
compressor. Calculate HSPF using Equation
EP09NO15.095</GPH> EP09NO15.096</GPH>
tkelley on DSK3SPTVN1PROD with PROPOSALS2
EP09NO15.098</GPH>
EP09NO15.099</GPH>
Where
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69387
solving Equations 4.2.2–3 and 4.2.2–4,
respectively, for k=2. Determine the
Equation 4.2.2–3 and 4.2.2–4 quantities
˙
˙
Qhk=2(47) and Ehk=2(47) from the H12 Test
and the calculations specified in section
˙
˙
3.7. Determine Qhk=2(35) and Ehk=2(35)
from the H22 Test and the calculations
specified in section 3.9 or, if the H22 Test
is not conducted, by conducting the
calculations specified in section 3.6.4.
˙
˙
Determine Qhk=2(17) and Ehk=2(17) from
the H32 Test and the calculations
specified in section 3.10. Calculate the
˙
space heating capacity, Qhk=v(Tj), and
˙
electrical power consumption, Ehk=v(Tj),
of the heat pump when operating at
outdoor temperature Tj and the
intermediate compressor speed used
during the section 3.6.4 H2V Test using
˙
˙
Where Qhk=v(35) and Ehk=v(35) are determined
from the H2V Test and calculated as
specified in section 3.9. Approximate the
slopes of the k=v intermediate speed
heating capacity and electrical power
input curves, MQ and ME, as follows:
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compressor speed is greater than or equal to
the building heating load at temperature Tj,
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˙
Qhk=1(Tj ≥ BL(Tj). Evaluate the Equation 4.2–
1 quantities
E:\FR\FM\09NOP2.SGM
09NOP2
EP09NO15.102</GPH>
4.2.4.1 Steady-state space heating
capacity when operating at minimum
EP09NO15.100</GPH> EP09NO15.101</GPH>
tkelley on DSK3SPTVN1PROD with PROPOSALS2
EP09NO15.103</GPH>
˙
˙
Where Qhk=1(62) and Ehk=1(62) are determined
˙
from the H01 Test, Qhk=1(47) and
˙
Ehk=1(47) are determined from the
H11Test, and all four quantities are
calculated as specified in section 3.7.
Evaluate the space heating capacity,
˙
Qhk=2(Tj), and electrical power
˙
consumption, Ehk=2(Tj), of the heat pump
when operating at maximum compressor
speed and outdoor temperature Tj by
69388
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
as specified in section 4.2.3.1. Except now
use Equations 4.2.4–1 and 4.2.4–2 to evaluate
˙
˙
Qhk=1(Tj) and Ehk=1(Tj), respectively, and
replace section 4.2.3.1 references to ‘‘low
capacity’’ and section 3.6.3 with ‘‘minimum
speed’’ and section 3.6.4. Also, the last
sentence of section 4.2.3.1 does not apply.
4.2.4.2 Heat pump operates at an
intermediate compressor speed (k=i) in order
to match the building heating load at a
˙
˙
temperature Tj, Qhk=1(Tj) <BL(Tj) <Qhk=2(Tj).
Calculate
and d(Tj) is evaluated using Equation 4.2.3–
3 while,
˙
Qhk=i(Tj) = BL(Tj), the space heating capacity
delivered by the unit in matching the
building load at temperature (Tj), Btu/h.
The matching occurs with the heat pump
operating at compressor speed k=i.
COPk=i(Tj) = the steady-state coefficient of
performance of the heat pump when
operating at compressor speed k=i and
temperature Tj, dimensionless.
For each temperature bin where the heat
pump operates at an intermediate compressor
speed, determine COPk=i(Tj) using,
COPk=i(Tj) = A + B . Tj + C . Tj2.
For each heat pump, determine the
coefficients A, B, and C by conducting the
following calculations once:
Where,=
T3 = the outdoor temperature at which the
heat pump, when operating at minimum
compressor speed, provides a space
heating capacity that is equal to the
˙
building load (Qhk=1(T3) = BL(T3)), °F.
outdoor temperature.
Tvh = the outdoor temperature at which the
heat pump, when operating at the
intermediate compressor speed used
during the section 3.6.4 H2V Test,
provides a space heating capacity that is
˙
equal to the building load (Qhk=v(Tvh) =
BL(Tvh)), °F. Determine Tvh by equating
Equations 4.2.4–3 and 4.2–2 and solving
for outdoor temperature.
T4 = the outdoor temperature at which the
heat pump, when operating at maximum
Determine T3 by equating Equations
4.2.4–1 and 4.2–2 and solving for:
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compressor speed, provides a space
heating capacity that is equal to the
˙
building load (Qhk=2(T4) = BL(T4)), °F.
Determine T4 by equating Equations
4.2.2–3 (k=2) and 4.2–2 and solving for
outdoor temperature.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
requirements for calculating COPhk=i(Tj). For
each temperature bin where T3 > Tj > Tvh,
˙
speed at temperature Tj, BL(Tj) ≥ Qhk=2(Tj).
Evaluate the Equation 4.2–1 quantities
as specified in section 4.2.3.4 with the
˙
˙
understanding that Qhk=2(Tj) and Ehk=2(Tj)
correspond to maximum compressor speed
operation and are derived from the results of
the specified section 3.6.4 tests.
4.2.5 Heat pumps having a heat comfort
controller. Heat pumps having heat comfort
controllers, when set to maintain a typical
minimum air delivery temperature, will
cause the heat pump condenser to operate
less because of a greater contribution from
the resistive elements. With a conventional
heat pump, resistive heating is only initiated
if the heat pump condenser cannot meet the
building load (i.e., is delayed until a second
stage call from the indoor thermostat). With
a heat comfort controller, resistive heating
can occur even though the heat pump
condenser has adequate capacity to meet the
building load (i.e., both on during a first stage
call from the indoor thermostat). As a result,
the outdoor temperature where the heat
pump compressor no longer cycles (i.e., starts
to run continuously), will be lower than if
the heat pump did not have the heat comfort
controller.
4.2.5.1 Heat pump having a heat comfort
controller: additional steps for calculating the
HSPF of a heat pump having a single-speed
compressor that was tested with a fixed-
speed indoor blower installed, a constant-airvolume-rate indoor blower installed, or with
no indoor blower installed. Calculate the
space heating capacity and electrical power
of the heat pump without the heat comfort
controller being active as specified in section
4.2.1 (Equations 4.2.1–4 and 4.2.1–5) for each
outdoor bin temperature, Tj, that is listed in
Table 19. Denote these capacities and
electrical powers by using the subscript ‘‘hp’’
instead of ‘‘h.’’ Calculate the mass flow rate
(expressed in pounds-mass of dry air per
hour) and the specific heat of the indoor air
(expressed in Btu/lbmda · °F) from the results
of the H1 Test using:
outdoor bin temperature listed in Table
19, calculate the nominal temperature of
Evaluate eh(Tj/N), RH(Tj)/N, X(Tj), PLFj,
and d(Tj) as specified in section 4.2.1. For
each bin calculation, use the space heating
capacity and electrical power from Case 1 or
Case 2, whichever applies.
Case 1. For outdoor bin temperatures
where To(Tj) is equal to or greater than TCC
(the maximum supply temperature
determined according to section 3.1.9),
˙
˙
determine Qh(Tj) and Eh(Tj) as specified in
˙
˙
˙
section 4.2.1 (i.e., Qh(Tj) = Qhp(Tj) and Ehp(Tj)
˙
= Ehp(Tj)). Note: Even though To(Tj) ≥ Tcc,
resistive heating may be required; evaluate
Equation 4.2.1–2 for all bins.
Case 2. For outdoor bin temperatures
˙
˙
where To(Tj) >Tcc, determine Qh(Tj) and Eh(Tj)
using,
˙
˙
˙
Qh(Tj) = Qhp(Tj) + QCC(Tj)
˙
˙
˙
Eh(Tj) = Ehp(Tj) + ECC(Tj)
Where,
Note: Even though To(Tj) < Tcc, additional
resistive heating may be required; evaluate
Equation 4.2.1–2 for all bins.
4.2.5.2 Heat pump having a heat comfort
controller: additional steps for calculating the
HSPF of a heat pump having a single-speed
compressor and a variable-speed, variableair-volume-rate indoor blower. Calculate the
space heating capacity and electrical power
of the heat pump without the heat comfort
controller being active as specified in section
4.2.2 (Equations 4.2.2–1 and 4.2.2–2) for each
outdoor bin temperature, Tj, that is listed in
Table 19. Denote these capacities and
electrical powers by using the subscript ‘‘hp’’
instead of ‘‘h.’’ Calculate the mass flow rate
(expressed in pounds-mass of dry air per
hour) and the specific heat of the indoor air
the air leaving the heat pump condenser
coil using,
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tkelley on DSK3SPTVN1PROD with PROPOSALS2
Ô Ô
where Vs, Vmx, v′n (or vn), and Wn are defined
following Equation 3–1. For each
EP09NO15.112</GPH>
4.2.4.3 Heat pump must operate
continuously at maximum (k=2) compressor
EP09NO15.111</GPH>
For multiple-split heat pumps (only), the
following procedures supersede the above
69389
69390
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
(expressed in Btu/lbmda · °F) from the results
of the H12 Test using:
Ô Ô
Where Vs, Vmx, v′n (or vn), and Wn are defined
following Equation 3–1. For each
outdoor bin temperature listed in Table
19, calculate the nominal temperature of
the air leaving the heat pump condenser
coil using,
Case 1. For outdoor bin temperatures
where To(Tj) is equal to or greater than TCC
(the maximum supply temperature
determined according to section 3.1.9),
˙
˙
determine Qh(Tj) and Eh(Tj) as specified in
˙
˙
˙
section 4.2.2 (i.e. Qh(Tj) = Qhp(Tj) and Eh(Tj)
˙
= Ehp(Tj)). Note: Even though To(Tj) ≥ TCC,
resistive heating may be required; evaluate
Equation 4.2.1–2 for all bins.
Case 2. For outdoor bin temperatures
˙
where To(Tj) < TCC, determine Qh(Tj) and
˙
Eh(Tj) using,
˙
˙
˙
˙
˙
Qh(Tj) = Qhp(Tj) + QCC(Tj)
Eh(Tj) = Ehp(Tj)
˙
+ ECC(Tj)
Where,
Note: Even though To(Tj) < Tcc, additional
resistive heating may be required; evaluate
Equation 4.2.1–2 for all bins.
4.2.5.3 Heat pumps having a heat comfort
controller: additional steps for calculating the
HSPF of a heat pump having a two-capacity
compressor. Calculate the space heating
capacity and electrical power of the heat
pump without the heat comfort controller
being active as specified in section 4.2.3 for
both high and low capacity and at each
outdoor bin temperature, Tj, that is listed in
Table 19. Denote these capacities and
electrical powers by using the subscript ‘‘hp’’
instead of ‘‘h.’’ For the low capacity case,
calculate the mass flow rate (expressed in
pounds-mass of dry air per hour) and the
specific heat of the indoor air (expressed in
Btu/lbmda · °F) from the results of the H11
Test using:
outdoor bin temperature listed in Table
19, calculate the nominal temperature of
the air leaving the heat pump condenser
04:57 Nov 07, 2015
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operating at high capacity by using the
results of the H12 Test. For each outdoor bin
temperature listed in Table 19, calculate the
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nominal temperature of the air leaving the
heat pump condenser coil when operating at
high capacity using,
E:\FR\FM\09NOP2.SGM
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Repeat the above calculations to determine
˙
the mass flow rate (mdak=2) and the specific
heat of the indoor air (Cp,dak=2) when
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coil when operating at low capacity
using,
EP09NO15.113</GPH> EP09NO15.114</GPH>
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Cp,da = 0.24 + 0.444 * Wn
Where
ÔÔ
Vs,Vmx, v′n (or vn), and Wn are defined
following Equation 3–1. For each
EP09NO15.117</GPH>
Evaluate eh(Tj)/N, RH(Tj)/N, X(Tj), PLFj,
and d(Tj) as specified in section 4.2.1 with
the exception of replacing references to the
H1C Test and section 3.6.1 with the H1C1
Test and section 3.6.2. For each bin
calculation, use the space heating capacity
and electrical power from Case 1 or Case 2,
whichever applies.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69391
Case 4. For outdoor bin temperatures
˙
where Tok=2(Tj) < TCC, determine Qhk=2(Tj)
˙
and Ehk=2(Tj) using,
Note: Even though Tok=2(Tj) < Tcc,
additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
4.2.5.4 Heat pumps having a heat comfort
controller: additional steps for calculating the
HSPF of a heat pump having a variable-speed
compressor. [Reserved]
4.2.6 Additional steps for calculating the
HSPF of a heat pump having a triple-capacity
compressor. The only triple-capacity heat
pumps covered are triple-capacity, northern
heat pumps.
For such heat pumps, the calculation of the
Eq. 4.2–1 quantities
differ depending on whether the heat pump
would cycle on and off at low capacity
(section 4.2.6.1), cycle on and off at high
capacity (section 4.2.6.2), cycle on and off at
booster capacity (4.2.6.3), cycle between low
and high capacity (section 4.2.6.4), cycle
between high and booster capacity (section
4.2.6.5), operate continuously at low capacity
(4.2.6.6), operate continuously at high
capacity (section 4.2.6.7), operate
continuously at booster capacity (4.2.6.8), or
heat solely using resistive heating (also
section 4.2.6.8) in responding to the building
load. As applicable, the manufacturer must
supply information regarding the outdoor
temperature range at which each stage of
compressor capacity is active. As an
informative example, data may be submitted
in this manner: At the low (k=1) compressor
capacity, the outdoor temperature range of
operation is 40 °F ≤ T ≤ 65 °F; At the high
(k=2) compressor capacity, the outdoor
temperature range of operation is 20 °F ≤ T
≤ 50 °F; At the booster (k=3) compressor
capacity, the outdoor temperature range of
operation is ¥20 °F ≤ T ≤ 30 °F.
a. Evaluate the space heating capacity and
electrical power consumption of the heat
pump when operating at low compressor
capacity and outdoor temperature Tj using
the equations given in section 4.2.3 for
˙
˙
Qhk=1(Tj) and Ehk=1 (Tj)) In evaluating the
˙
section 4.2.3 equations, Determine Qhk=1(62)
˙
˙
and Ehk=1(62) from the H01 Test, Qhk=1(47)
˙
and Ehk=1(47) from the H11 Test, and
˙
˙
Qhk=2(47) and Ehk=2(47) from the H12 Test.
Calculate all four quantities as specified in
section 3.7. If, in accordance with section
3.6.6, the H31 Test is conducted, calculate
˙
˙
Qhk=1(17) and Ehk=1(17) as specified in section
˙
˙
3.10 and determine Qhk=1(35) and Ehk=1(35) as
specified in section 3.6.6.
b. Evaluate the space heating capacity and
˙
electrical power consumption (Qhk=2(Tj) and
˙
Ehk=2 (Tj)) of the heat pump when operating
at high compressor capacity and outdoor
temperature Tj by solving Equations 4.2.2–3
and 4.2.2–4, respectively, for k=2. Determine
˙
˙
Qhk=1(62) and Ehk=1(62) from the H01 Test,
˙
˙
Qhk=1(47) and Ehk=1(47) from the H11 Test,
˙
˙
and Qhk=2(47) and Ehk=2(47) from the H12
Test, evaluated as specified in section 3.7.
˙
Determine the equation input for Qhk=2(35)
˙
and Ehk=2(35) from the H22, evaluated as
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˙
specified in section 4.2.3 (i.e., Qhk=2(Tj) =
˙
˙
˙
Qhpk=2(Tj) and Ehk=2(Tj) = Ehpk=2(Tj)).
Note: Even though Tok=2(Tj) < TCC, resistive
heating may be required; evaluate RH(Tj)/N
for all bins.
EP09NO15.121</GPH>
˙
˙
in section 4.2.3 (i.e., Qhk=1(Tj) = Qhpk=1(Tj) and
˙
˙
Ehk=1(Tj) = Ehpk=1(Tj).
Note: Even though Tok=1(Tj) ≥ TCC, resistive
heating may be required; evaluate RH(Tj)/N
for all bins.
Case 2. For outdoor bin temperatures
˙
where Tok=1(Tj) < TCC, determine Qhk=1(Tj)
˙
and Ehk=1(Tj) using,
EP09NO15.118</GPH> EP09NO15.119</GPH>
high-capacity space heating capacity and the
high-capacity electrical power from Case 3 or
Case 4, whichever applies.
Case 1. For outdoor bin temperatures
where Tok=1(Tj) is equal to or greater than TCC
(the maximum supply temperature
determined according to section 3.1.9),
˙
˙
determine Qhk=1(Tj) and Ehk=1(Tj) as specified
Note: Even though Tok=1(Tj) ≥Tcc,
additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
Case 3. For outdoor bin temperatures
where Tok=2(Tj) is equal to or greater than
˙
˙
TCC, determine Qhk=2(Tj) and Ehk=2(Tj) as
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Evaluate eh(Tj)/N, RH(Tj)/N, Xk=1(Tj), and/
or Xk=2(Tj), PLFj, and d′(Tj) or d″(Tj) as
specified in section 4.2.3.1. 4.2.3.2, 4.2.3.3, or
4.2.3.4, whichever applies, for each
temperature bin. To evaluate these quantities,
use the low-capacity space heating capacity
and the low-capacity electrical power from
Case 1 or Case 2, whichever applies; use the
69392
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
c. Evaluate the space heating capacity and
electrical power consumption of the heat
pump when operating at booster compressor
capacity and outdoor temperature Tj using
˙
˙
Determine Qhk=3(17) and Ehk=3(17) from the
˙
˙
H33 Test and determine Qhk=2(2) and Ehk=3(2)
from the H43 Test. Calculate all four
quantities as specified in section 3.10.
˙
Determine the equation input for Qhk=3(35)
˙
and Ehk=3(35) as specified in section 3.6.6.
4.2.6.1 Steady-state space heating
capacity when operating at low compressor
capacity is greater than or equal to the
building heating load at temperature Tj,
˙
Qhk=1(Tj) ≥BL(Tj)., and the heat pump permits
low compressor capacity at Tj. Evaluate the
quantities
using Eqs. 4.2.3–1 and 4.2.3–2, respectively.
Determine the equation inputs Xk=1(Tj), PLFj,
and d′(Tj) as specified in section 4.2.3.1. In
calculating the part load factor, PLFj, use the
low-capacity cyclic-degradation coefficient
CDh, [or equivalently, CDh(k=1)] determined
in accordance with section 3.6.6.
4.2.6.2 Heat pump only operates at high
(k=2) compressor capacity at temperature Tj
and its capacity is greater than or equal to the
˙
building heating load, BL(Tj) < Qhk=2(Tj).
Evaluate the quantities
as specified in section 4.2.3.3. Determine the
equation inputs Xk=2(Tj), PLFj, and d′(Tj) as
specified in section 4.2.3.3. In calculating the
part load factor, PLFj, use the high-capacity
cyclic-degradation coefficient, CDh(k=2)
determined in accordance with section 3.6.6.
4.2.6.3 Heat pump only operates at high
(k=3) compressor capacity at temperature Tj
and its capacity is greater than or equal to the
˙
building heating load, BL(Tj) ≤ Qhk=3(Tj).
Determine the low temperature cut-out
factor, d′(Tj), using Eq. 4.2.3–3. Use the
booster-capacity cyclic-degradation
coefficient, CDh(k=3) determined in
accordance with section 3.6.6.
4.2.6.4 Heat pump alternates between
high (k=2) and low (k=1) compressor
capacity to satisfy the building heating load
˙
at a temperature Tj, Qhk=1(Tj) < BL(Tj) <
˙
Qhk=2(Tj). Evaluate the quantities
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EP09NO15.126</GPH>
specified in section 3.9.1. Also, determine
˙
˙
Qhk=2(17) and Ehk=2(17) from the H32 Test,
evaluated as specified in section 3.10.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69393
capacity is less than the building heating
˙
load, BL(Tj) > Qhk=1(Tj).
Where the low temperature cut-out factor,
d′(Tj), is calculated using Eq. 4.2.3–3.
4.2.6.7 Heat pump only operates at high
(k = 2) capacity at temperature Tj and its
capacity is less than the building heating
˙
load, BL(Tj) > Qhk=2(Tj).Evaluate the
quantities
as specified in section 4.2.3.4. Calculate
d″(Tj) using the equation given in section
4.2.3.4.
4.2.6.8 Heat pump only operates at
booster (k = 3) capacity at temperature Tj and
its capacity is less than the building heating
˙
load, BL(Tj) > Qhk=3(Tj). or the system
converts to using only resistive heating.
Where d″(Tj) is calculated as specified in
section 4.2.3.4 if the heat pump is
operating at its booster compressor
capacity. If the heat pump system
converts to using only resistive heating
at outdoor temperature Tj, set d′(Tj) equal
to zero.
4.2.7 Additional steps for calculating the
HSPF of a heat pump having a single indoor
unit with multiple blowers. The calculation
of the Eq. 4.2–1 quantities eh(Tj)/N and
RH(Tj)/N are evaluated as specified in
applicable below subsection.
4.2.7.1 For multiple blower heat pumps
that are connected to a singular, single-speed
outdoor unit.
a. Calculate the space heating capacity,
˙
Qhk= 1(Tj), and electrical power consumption,
˙
Ehk= 1 (Tj), of the heat pump when operating
at the heating minimum air volume rate and
outdoor temperature Tj using Eqs. 4.2.2–3
and 4.2.2–4, respectively. Use these same
equations to calculate the space heating
˙
capacity, Qhk= 2 (Tj) and electrical power
˙
consumption, Ehk= 2 (Tj), of the test unit when
operating at the heating full-load air volume
rate and outdoor temperature Tj. In
evaluating Eqs. 4.2.2–3 and 4.2.2– 4,
˙
˙
determine the quantities Qhk= 1 (47) and Ehk=
˙h
1 (47) from the H1 Test; determine Q k= 2 (47)
1
˙
and Ehk= 2 (47) from the H12 Test. Evaluate
all four quantities according to section 3.7.
˙
˙
Determine the quantities Qhk= 1 (35) and Ehk=
1 (35) as specified in section 3.6.2. Determine
˙
˙
Qhk= 2 (35) and Ehk= 2 (35) from the H22 Frost
Accumulation Test as calculated according to
˙
section 3.9.1. Determine the quantities Qhk= 1
˙
(17) and Ehk= 1 (17) from the H31 Test, and
˙
˙
Qhk= 2 (17) and Ehk= 2 (17) from the H32 Test.
Evaluate all four quantities according to
section 3.10. Refer to section 3.6.2 and Table
11 for additional information on the
referenced laboratory tests.
b. Determine the heating mode cyclic
degradation coefficient, CDh, as per sections
3.6.2 and 3.8 to 3.8.1. Assign this same value
to CDh(k = 2).
˙
c. Except for using the above values of Qhk=
˙h
1 (Tj), E k= 1 (Tj), Q k= 2 (Tj), E k= 2 (Tj), CD ,
˙h
˙h
h
and CDh(k = 2), calculate the quantities
eh(Tj)/N as specified in section 4.2.3.1 for
˙
cases where Qhk= 1 (Tj) ≥ BL(Tj). For all other
outdoor bin temperatures, Tj, calculate eh(Tj)/
N and RHh(Tj)/N as specified in section
˙
4.2.3.3 if Qhk= 2 (Tj) > BL(Tj) or as specified
˙
in section 4.2.3.4 if Qhk= 2 (Tj) ≤ BL(Tj)
4.2.7.2 For multiple blower heat pumps
connected to either a lone outdoor unit with
a two-capacity compressor or to two separate
but identical model single-speed outdoor
units. Calculate the quantities eh(Tj)/N and
RH(Tj)/N as specified in section 4.2.3.
4.3 Calculations of Off-mode Seasonal
Power and Energy Consumption.
4.3.1 For central air conditioners and heat
pumps with a cooling capacity of:
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temperature cut-out factor, d′(Tj), using Eq.
4.2.3–3.
4.2.6.6 Heat pump only operates at low
(k=1) capacity at temperature Tj and its
EP09NO15.130</GPH>
˙
at a temperature Tj, Qhk=2(Tj) <BL(Tj)
˙
<Qhk=3(Tj).
EP09NO15.127</GPH> EP09NO15.128</GPH>
4.2.6.5 Heat pump alternates between
high (k=2) and booster (k=3) compressor
capacity to satisfy the building heating load
and Xk=3(Tj) = Xk=2(Tj) = the heating mode,
booster capacity load factor for temperature
bin j, dimensionless. Determine the low
tkelley on DSK3SPTVN1PROD with PROPOSALS2
as specified in section 4.2.3.2. Determine the
equation inputs Xk=1(Tj), Xk=2(Tj), and d′(Tj)
as specified in section 4.2.3.2.
69394
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
less than 36,000 Btu/h, determine the off
mode rating, PW,OFF, with the following
equation:
greater than or equal to 36,000 Btu/h,
calculate the capacity scaling factor
according to:
˙
Where, QC(95) is the total cooling capacity at
the A or A2 Test condition, and
determine
4.3.2 Calculate the off mode energy
consumption for both central air conditioner
and heat pumps for the shoulder season, E1,
using: E1 = P1 · SSH; and the off mode
energy consumption of a CAC, only, for the
heating season, E2, using: E2 = P2 · HSH;
where P1 and P2 is determined in Section
3.13. HSH can be determined by multiplying
the heating season-hours from Table 21 with
the fractional Bin-hours, from Table 19, that
pertain to the range of temperatures at which
the crankcase heater operates. If the
crankcase heater is controlled to disable for
the heating season, the temperature range at
which the crankcase heater operates is
defined to be from 72 °F to five degrees
Fahrenheit below a turn-off temperature
specified by the manufacturer in the DOE
Compliance Certification Database. If the
crankcase heater is operated during the
heating season, the temperature range at
which the crankcase heater operates is
defined to be from 72 °F to ¥23 °F, the latter
of which is a temperature that sets the range
of Bin-hours to encompass all outside air
temperatures in the heating season.
SSH can be determined by multiplying the
shoulder season-hours from Table 21 with
the fractional Bin-hours in Table 22.
TABLE 21—REPRESENTATIVE COOLING AND HEATING LOAD HOURS AND THE CORRESPONDING SET OF SEASONAL HOURS
FOR EACH GENERALIZED CLIMATIC REGION
Cooling load
hours
CLHR
Climatic region
2400
1800
1200
800
1000
400
200
Cooling season hours
CSHR
750
1250
1750
2250
2080
2750
2750
6731
5048
3365
2244
2805
1122
561
Heating season hours
HSHR
Shoulder season hours
SSHR
1826
3148
4453
5643
5216
6956
6258
203
564
942
873
739
682
1941
EP09NO15.133</GPH>
Region I: HSH = 2.4348HLH;
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I ............................................................................................
II ...........................................................................................
III ..........................................................................................
IV ..........................................................................................
Rating Values .......................................................................
V ...........................................................................................
VI ..........................................................................................
Heating load
hours
HLHR
69395
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
Region IV: HSH = 2.5078HLH;
Region V: HSH = 2.5295HLH;
Region VI: HSH = 2.2757HLH.
SSH is evaluated: SSH = 8760 ¥ (CSH +
HSH), where CSH = the cooling season hours
calculated using CSH = 2.8045 · CLH
TABLE 22—FRACTIONAL BIN HOURS
FOR THE SHOULDER SEASON HOURS
FOR ALL REGIONS
Fractional bin hours
Fractional bin hours
Tj(°F)
Tj(°F)
Air conditioners
72 ..........
67 ..........
TABLE 22—FRACTIONAL BIN HOURS
FOR THE SHOULDER SEASON HOURS
FOR ALL REGIONS—Continued
Air conditioners
Heat pumps
0.333
0.667
0.167
0.333
62 ..........
57 ..........
0
0
Heat pumps
0.333
0.167
C = defined in section 4.2 following Equation
4.2–2, dimensionless.
SEER = the seasonal energy efficiency ratio
calculated as specified in section 4.1,
Btu/W·h.
HSPF = the heating seasonal performance
factor calculated as specified in section
4.2 for the generalized climatic region
that includes the particular location of
interest (see Figure 1), Btu/W·h. The
HSPF should correspond to the actual
design heating requirement (DHR), if
known. If it does not, it may correspond
to one of the standardized design heating
requirements referenced in section 4.2.
P1 is the shoulder season per-compressor off
mode power, as determined in section
3.13, W.
SSH is the shoulder season hours, hr.
P2 is the heating season per-compressor off
mode power, as determined in section
3.13, W.
HSH is the heating season hours, hr.
4.4.2 Calculation of representative
regional annual performance factors (APFR)
for each generalized climatic region and for
each standardized design heating
requirement.
Where,
CLHR = the representative cooling hours for
each generalized climatic region, Table
23, hr.
HLHR = the representative heating hours for
each generalized climatic region, Table
23, hr.
HSPF = the heating seasonal performance
factor calculated as specified in section
4.2 for the each generalized climatic
region and for each standardized design
heating requirement within each region,
Btu/W.h.
˙
The SEER, Qck(95), DHR, and C are the
same quantities as defined in section 4.3.1.
Figure 1 shows the generalized climatic
regions. Table 20 lists standardized design
heating requirements.
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TABLE 23—REPRESENTATIVE COOLING
AND HEATING LOAD HOURS FOR
EACH GENERALIZED CLIMATIC REGION
Region
I .................
II ................
III ...............
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2400
1800
1200
HLHR
750
1250
1750
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particular location and for each standardized
design heating requirement.
EP09NO15.135</GPH> EP09NO15.136</GPH>
4.4 Calculations of the Actual and
Representative Regional Annual Performance
Factors for Heat Pumps.
4.4.1 Calculation of actual regional
annual performance factors (APFA) for a
Where,
CLHA = the actual cooling hours for a
particular location as determined using
the map given in Figure 2, hr.
˙
Qck(95) = the space cooling capacity of the
unit as determined from the A or A2
Test, whichever applies, Btu/h.
HLHA = the actual heating hours for a
particular location as determined using
the map given in Figure 1, hr.
DHR = the design heating requirement used
in determining the HSPF; refer to section
4.2 and see section 1.2, Definitions, Btu/
h.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
4.3.4 For air conditioners, the annual off
mode energy consumption, ETOTAL, is: ETOTAL
= E1 + E2.
4.3.5 For heat pumps, the annual off
mode energy consumption, ETOTAL, is E1.
69396
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
TABLE 23—REPRESENTATIVE COOLING
AND HEATING LOAD HOURS FOR
EACH GENERALIZED CLIMATIC REGION—Continued
Region
IV ..............
V ...............
CLHR
HLHR
800
400
TABLE 23—REPRESENTATIVE COOLING
AND HEATING LOAD HOURS FOR
EACH GENERALIZED CLIMATIC REGION—Continued
Region
2250
2750
CLHR
VI ..............
HLHR
200
4.5. Rounding of SEER, HSPF, and APF
for reporting purposes. After calculating
SEER according to section 4.1, HSPF
according to section 4.2, and APF according
to section 4.3, round the values off as
specified in subpart B 430.23(m) of Title 10
of the Code of Federal Regulations.
2750
Figure 2-Cooling Load Hours (CLHA) for the United States
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Figure !-Heating Load Hours (HLHA) for the United States
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
4.6 Calculations of the SHR, which
should be computed for different equipment
69397
configurations and test conditions specified
in Table 24.
TABLE 24—APPLICABLE TEST CONDITIONS FOR CALCULATION OF THE SENSIBLE HEAT RATIO
Reference
Table No. of
Appendix M
Equipment configuration
Units Having a Single-Speed Compressor and a Fixed-Speed Indoor
blower, a Constant Air Volume Rate Indoor blower, or No Indoor blower.
Units Having a Single-Speed Compressor That Meet the Section 3.2.2.1
Indoor Unit Requirements.
Units Having a Two-Capacity Compressor ................................................
Units Having a Variable-Speed Compressor .............................................
SHR computation with
results from
Computed values
4
B Test .............................
SHR(B).
5
B2 and B1 Tests ............
SHR(B1), SHR(B2).
6
7
B2 and B1 Tests ............
B2 and B1 Tests ............
SHR(B1), SHR(B2).
SHR(B1), SHR(B2).
The SHR is defined and calculated as
follows:
collected over the same 30-minute data
collection interval.
4.7 calculations of the Energy Efficiency
Ratio (EER). Calculate the energy efficiency
ratio using,
˙
˙
Where Qck(T) and Eck(T) are the space
cooling capacity and electrical power
consumption determined from the 30-minute
data collection interval of the same steadystate wet coil cooling mode test and
calculated as specified in section 3.3. Add
the letter identification for each steady-state
test as a subscript (e.g., EERA2) to
differentiate among the resulting EER values.
the 10 CFR parts 200 to 499 edition revised
as of January 1, 2015. Any representations
made with respect to the energy use or
efficiency of such central air conditioners
and central air conditioning heat pumps
must be in accordance with whichever
version is selected.
On or after May 9, 2016 and prior to the
compliance date for any amended energy
conservation standards, any representations,
including compliance certifications, made
with respect to the energy use, power, or
efficiency of central air conditioners and
central air conditioning heat pumps must be
based on the results of testing pursuant to
Appendix M.
On or after the compliance date for any
amended energy conservation standards, any
representations, including compliance
certifications, made with respect to the
energy use, power, or efficiency of central air
conditioners and central air conditioning
heat pumps must be based on the results of
testing pursuant to this appendix (Appendix
M1).
This test procedure provides a method of
determining SEER, EER, HSPF and PW,OFF for
central air conditioners and central air
conditioning heat pumps including the
following categories:
(a) Split-system air conditioners; and singlezone-multiple-coil, multi-split (including
VRF), and multi-circuit systems
(b) Split-system heat pumps and single-zonemultiple-coil, multi-split (including VRF),
and multi-circuit systems
(c) Single-package air conditioners
(d) Single-package heat pumps
(e) Small-duct, high-velocity systems
(including VRF)
(f) Space-constrained products—air
conditioners
(g) Space-constrained products—heat pumps
For purposes of this appendix, the
Department of Energy incorporates by
reference specific sections of several industry
standards, as listed in § 430.3. In cases where
there is a conflict, the language of the test
procedure in this appendix takes precedence
over the incorporated standards.
All section references refer to sections
within this appendix unless otherwise stated.
11. Add appendix M1 to subpart B of
part 430 to read as follows:
■
tkelley on DSK3SPTVN1PROD with PROPOSALS2
APPENDIX M1 TO SUBPART B OF
PART 430—UNIFORM TEST METHOD
FOR MEASURING THE ENERGY
CONSUMPTION OF CENTRAL AIR
CONDITIONERS AND HEAT PUMPS
Note: Prior to May 9, 2016, any
representations, including compliance
certifications, made with respect to the
energy use, power, or efficiency of central air
conditioners and central air conditioning
heat pumps must be based on the results of
testing pursuant to either Appendix M or the
procedures in Appendix M as it appeared at
10 CFR part 430, subpart B, Appendix M, in
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1. Scope and Definitions
1.1 Scope.
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Where both the total and sensible cooling
capacities are determined from the same
cooling mode test and calculated from data
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
1.2. Definitions
Airflow-control settings are programmed or
wired control system configurations that
control a fan to achieve discrete, differing
ranges of airflow—often designated for
performing a specific function (e.g., cooling,
heating, or constant circulation)—without
manual adjustment other than interaction
with a user-operable control (i.e., a
thermostat) that meets the manufacturer
specifications for installed-use. For the
purposes of this appendix, manufacturer
specifications for installed-use are those
found in the product literature shipped with
the unit.
Airflow prevention device denotes a
device(s) that prevents airflow via natural
convection by mechanical means, such as an
air damper box, or by means of changes in
duct height, such as an upturned duct.
Annual performance factor means the total
heating and cooling done by a heat pump in
a particular region in one year divided by the
total electric energy used in one year.
Blower coil indoor unit means the indoor
unit of a split-system central air conditioner
or heat pump that includes a refrigerant-toair heat exchanger coil, may include a
cooling-mode expansion device, and
includes either an indoor blower housed
with the coil or a separate designated air
mover such as a furnace or a modular blower
(as defined in Appendix AA). Blower coil
system refers to a split-system that includes
one or more blower coil indoor units.
CFR means Code of Federal Regulations.
Coefficient of Performance (COP) means
the ratio of the average rate of space heating
delivered to the average rate of electrical
energy consumed by the heat pump. These
rate quantities must be determined from a
single test or, if derived via interpolation,
must be determined at a single set of
operating conditions. COP is a dimensionless
quantity. When determined for a ducted unit
tested without an indoor blower installed,
COP must include the section 3.7and 3.9.1
default values for the heat output and power
input of a fan motor.
Coil-only indoor unit means the indoor
unit of a split-system central air conditioner
or heat pump that includes a refrigerant-toair heat exchanger coil and may include a
cooling-mode expansion device, but does not
include an indoor blower housed with the
coil, and does not include a separate
designated air mover such as a furnace or a
modular blower (as defined in Appendix
AA). A coil-only indoor unit is designed to
use a separately-installed furnace or a
modular blower for indoor air movement.
Coil-only system refers to a system that
includes one or more coil-only indoor units.
Condensing unit removes the heat absorbed
by the refrigerant to transfer it to the outside
environment, and which consists of an
outdoor coil, compressor(s), and air moving
device.
Constant-air-volume-rate indoor blower
means a fan that varies its operating speed to
provide a fixed air-volume-rate from a ducted
system.
Continuously recorded, when referring to a
dry bulb measurement, dry bulb temperature
used for test room control, wet bulb
temperature, dew point temperature, or
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relative humidity measurements, means that
the specified value must be sampled at
regular intervals that are equal to or less than
5 seconds.
Cooling load factor (CLF) means the ratio
having as its numerator the total cooling
delivered during a cyclic operating interval
consisting of one ON period and one OFF
period. The denominator is the total cooling
that would be delivered, given the same
ambient conditions, had the unit operated
continuously at its steady-state, spacecooling capacity for the same total time (ON
+ OFF) interval.
Crankcase heater means any electrically
powered device or mechanism for
intentionally generating heat within and/or
around the compressor sump volume often
done to minimize the dilution of the
compressor’s refrigerant oil by condensed
refrigerant. Crankcase heater control may be
achieved using a timer or may be based on
a change in temperature or some other
measurable parameter, such that the
crankcase heater is not required to operate
continuously. A crankcase heater without
controls operates continuously when the
compressor is not operating.
Cyclic Test means a test where the unit’s
compressor is cycled on and off for specific
time intervals. A cyclic test provides half the
information needed to calculate a
degradation coefficient.
Damper box means a short section of duct
having an air damper that meets the
performance requirements of section 2.5.7.
Degradation coefficient (CD) means a
parameter used in calculating the part load
factor. The degradation coefficient for cooling
is denoted by CDc. The degradation
coefficient for heating is denoted by CDh.
Demand-defrost control system means a
system that defrosts the heat pump outdoor
coil only when measuring a predetermined
degradation of performance. The heat pump’s
controls monitor one or more parameters that
always vary with the amount of frost
accumulated on the outdoor coil (e.g., coil to
air differential temperature, coil differential
air pressure, outdoor fan power or current,
optical sensors) at least once for every ten
minutes of compressor ON-time when space
heating. One acceptable alternative to the
criterion given in the prior sentence is a
feedback system that measures the length of
the defrost period and adjusts defrost
frequency accordingly. In all cases, when the
frost parameter(s) reaches a predetermined
value, the system initiates a defrost. In a
demand-defrost control system, defrosts are
terminated based on monitoring a
parameter(s) that indicates that frost has been
eliminated from the coil. (Note: Systems that
vary defrost intervals according to outdoor
dry-bulb temperature are not demand-defrost
systems.) A demand-defrost control system,
which otherwise meets the above
requirements, may allow time-initiated
defrosts if, and only if, such defrosts occur
after 6 hours of compressor operating time.
Design heating requirement (DHR) predicts
the space heating load of a residence when
subjected to outdoor design conditions.
Estimates for the DHR are provided for six
generalized U.S. climatic regions in section
4.2.
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Dry-coil tests are cooling mode tests where
the wet-bulb temperature of the air supplied
to the indoor coil is maintained low enough
that no condensate forms on this coil.
Ducted system means an air conditioner or
heat pump that is designed to be
permanently installed equipment and
delivers conditioned air to the indoor space
through a duct(s). The air conditioner or heat
pump may be either a split-system or a
single-package unit.
Energy efficiency ratio (EER) means the
ratio of the average rate of space cooling
delivered to the average rate of electrical
energy consumed by the air conditioner or
heat pump. These rate quantities must be
determined from a single test or, if derived
via interpolation, must be determined at a
single set of operating conditions. EER is
expressed in units of
When determined for a ducted unit tested
without an indoor blower installed, EER
must include the section 3.3 and 3.5.1 default
values for the heat output and power input
of a fan motor.
Evaporator coil absorbs heat from an
enclosed space and transfers the heat to a
refrigerant.
Heat pump means a kind of central air
conditioner, which consists of one or more
assemblies, utilizing an indoor conditioning
coil, compressor, and refrigerant-to-outdoor
air heat exchanger to provide air heating, and
may also provide air cooling, air
dehumidifying, air humidifying, air
circulating, and air cleaning.
Heat pump having a heat comfort
controller means equipment that regulates
the operation of the electric resistance
elements to assure that the air temperature
leaving the indoor section does not fall below
a specified temperature. This specified
temperature is usually field adjustable. Heat
pumps that actively regulate the rate of
electric resistance heating when operating
below the balance point (as the result of a
second stage call from the thermostat) but do
not operate to maintain a minimum delivery
temperature are not considered as having a
heat comfort controller.
Heating load factor (HLF) means the ratio
having as its numerator the total heating
delivered during a cyclic operating interval
consisting of one ON period and one OFF
period. The denominator is the total heating
that would be delivered, given the same
ambient conditions, if the unit operated
continuously at its steady-state space heating
capacity for the same total time (ON plus
OFF) interval.
Heating season means the months of the
year that require heating, e.g., typically, and
roughly, October through April.
Heating seasonal performance factor
(HSPF) means the total space heating
required during the space heating season,
expressed in Btu’s, divided by the total
electrical energy consumed by the heat pump
system during the same season, expressed in
watt-hours. The HSPF used to evaluate
compliance with the Energy Conservation
Standards (see 10 CFR 430.32(c)) is based on
Region IV, the design heating requirement,
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and the sampling plan stated in 10 CFR
429.16(a).
Independent coil manufacturer (ICM)
means a manufacturer that manufactures
indoor units but does not manufacture singlepackage units or outdoor units.
Indoor unit transfers heat between the
refrigerant and the indoor air and consists of
an indoor coil and casing and may include
a cooling mode expansion device and/or an
air moving device.
Multiple-circuit (or multi-circuit) system
means a split system that has one outdoor
unit and that has two or more indoor units
installed on two or more refrigeration circuits
such that each refrigeration circuit serves a
compressor and one and only one indoor
unit, and refrigerant is not shared from
circuit to circuit.
Multiple-split (or multi-split) system means
a split system that has one outdoor unit and
two or more indoor coil-only or indoor
blower coil units connected to its other
component(s) with a single refrigerant
circuit. The indoor units operate
independently and can condition multiple
zones in response to at least two indoor
thermostats or temperature sensors. The
outdoor unit operates in response to
independent operation of the indoor units
based on control input of multiple indoor
thermostats or temperature sensors, and/or
based on refrigeration circuit sensor input
(e.g., suction pressure).
Nominal capacity means the capacity that
is claimed by the manufacturer in the
product name plate. Nominal cooling
capacity is approximate to the air conditioner
cooling capacity tested at A or A2 condition.
Nominal heating capacity is approximate to
the heat pump heating capacity tested in H12
test (or the optional H1N test).
Non-ducted system means a split-system
central air conditioner or heat pump that is
designed to be permanently installed and
that directly heats or cools air within the
conditioned space using one or more indoor
units that are mounted on room walls and/
or ceilings. The system may be of a modular
design that allows for combining multiple
outdoor coils and compressors to create one
overall system.
Normalized Gross Indoor Fin Surface
(NGIFS) means the gross fin surface area of
the indoor unit coil divided by the cooling
capacity measured for the A or A2 Test
whichever applies.
Off-mode power consumption means the
power consumption when the unit is
connected to its main power source but is
neither providing cooling nor heating to the
building it serves.
Off-mode season means, for central air
conditioners, the shoulder season and the
entire heating season; and for heat pumps,
the shoulder season only.
Outdoor unit transfers heat between the
refrigerant and the outdoor air, and consists
of an outdoor coil, compressor(s), an air
moving device, and in addition for heat
pumps, could include a heating mode
expansion device, reversing valve, and
defrost controls.
Outdoor unit manufacturer (OUM) means
a manufacturer of single-package units,
outdoor units, and/or both indoor units and
outdoor units.
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Part-load factor (PLF) means the ratio of
the cyclic energy efficiency ratio (coefficient
of performance) to the steady-state energy
efficiency ratio (coefficient of performance),
where both energy efficiency ratios
(coefficients of performance) are determined
based on operation at the same ambient
conditions.
Seasonal energy efficiency ratio (SEER)
means the total heat removed from the
conditioned space during the annual cooling
season, expressed in Btu’s, divided by the
total electrical energy consumed by the
central air conditioner or heat pump during
the same season, expressed in watt-hours.
Short ducted system means a ducted split
system whose one or more indoor sections
produce greater than zero but no greater than
0.1 inches (of water) of external static
pressure when operated at the full-load air
volume not exceeding 450 cfm per rated ton
of cooling.
Shoulder season means the months of the
year in between those months that require
cooling and those months that require
heating, e.g., typically, and roughly, April
through May, and September through
October.
Single-package unit means any central air
conditioner or heat pump that has all major
assemblies enclosed in one cabinet.
Single-split-system means a split system
that has one outdoor unit and that has one
indoor coil-only or indoor blower coil unit
connected to its other component(s) with a
single refrigeration circuit.
Single-zone-multiple-coil split system
means a split system that has one outdoor
unit and that has two or more indoor units
connected with a single refrigeration circuit.
The indoor units operate in unison in
response to a single indoor thermostat.
Small-duct, high-velocity system means a
system that contains a blower and indoor coil
combination that is designed for, and
produces, at least 1.2 inches (of water) of
external static pressure when operated at the
full-load air volume rate of 220–350 cfm per
rated ton of cooling. When applied in the
field, uses high-velocity room outlets (i.e.,
generally greater than 1000 fpm) having less
than 6.0 square inches of free area.
Split system means any air conditioner or
heat pump that has one or more of the major
assemblies separated from the others. Splitsystems may be either blower coil systems or
coil-only systems.
Standard Air means dry air having a mass
density of 0.075 lb/ft 3.
Steady-state test means a test where the
test conditions are regulated to remain as
constant as possible while the unit operates
continuously in the same mode.
Temperature bin means the 5 °F
increments that are used to partition the
outdoor dry-bulb temperature ranges of the
cooling (≥65 °F) and heating (<65 °F) seasons.
Test condition tolerance means the
maximum permissible difference between the
average value of the measured test parameter
and the specified test condition.
Test operating tolerance means the
maximum permissible range that a
measurement may vary over the specified test
interval. The difference between the
maximum and minimum sampled values
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must be less than or equal to the specified
test operating tolerance.
Tested combination means a single-zonemultiple-coil, multi-split, or multi-circuit
system having the following features:
(1) The system consists of one outdoor unit
with one or more compressors matched with
between two and five indoor units;
(2) The indoor units shall:
(i) Collectively, have a nominal cooling
capacity greater than or equal to 95 percent
and less than or equal to 105 percent of the
nominal cooling capacity of the outdoor unit;
(ii) Represent the highest sales volume
model family that can meet the 95 percent
nominal cooling capacity of the outdoor unit
[Note: another indoor model family may be
used if five indoor units from the highest
sales volume model family do not provide
sufficient capacity to meet the 95 percent
threshold level].
(iii) Individually not have a nominal
cooling capacity greater than 50 percent of
the nominal cooling capacity of the outdoor
unit, unless the nominal cooling capacity of
the outdoor unit is 24,000 Btu/h or less;
(iv) Operate at fan speeds consistent with
manufacturer’s specifications; and
(v) All be subject to the same minimum
external static pressure requirement while
able to produce the same external static
pressure at the exit of each outlet plenum
when connected in a manifold configuration
as required by the test procedure.
(vi) Where referenced, ‘‘nominal cooling
capacity’’ is to be interpreted for indoor units
as the highest cooling capacity listed in
published product literature for 95 °F outdoor
dry bulb temperature and 80 °F dry bulb,
67 °F wet bulb indoor conditions, and for
outdoor units as the lowest cooling capacity
listed in published product literature for
these conditions. If incomplete or no
operating conditions are reported, the highest
(for indoor units) or lowest (for outdoor
units) such cooing capacity shall be used.
Time-adaptive defrost control system is a
demand-defrost control system that measures
the length of the prior defrost period(s) and
uses that information to automatically
determine when to initiate the next defrost
cycle.
Time-temperature defrost control systems
initiate or evaluate initiating a defrost cycle
only when a predetermined cumulative
compressor ON-time is obtained. This
predetermined ON-time is generally a fixed
value (e.g., 30, 45, 90 minutes) although it
may vary based on the measured outdoor
dry-bulb temperature. The ON-time counter
accumulates if controller measurements (e.g.,
outdoor temperature, evaporator
temperature) indicate that frost formation
conditions are present, and it is reset/remains
at zero at all other times. In one application
of the control scheme, a defrost is initiated
whenever the counter time equals the
predetermined ON-time. The counter is reset
when the defrost cycle is completed.
In a second application of the control
scheme, one or more parameters are
measured (e.g., air and/or refrigerant
temperatures) at the predetermined,
cumulative, compressor ON-time. A defrost
is initiated only if the measured parameter(s)
falls within a predetermined range. The ON-
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time counter is reset regardless of whether or
not a defrost is initiated. If systems of this
second type use cumulative ON-time
intervals of 10 minutes or less, then the heat
pump may qualify as having a demand
defrost control system (see definition).
Triple-capacity, northern heat pump
means a heat pump that provides two stages
of cooling and three stages of heating. The
two common stages for both the cooling and
heating modes are the low capacity stage and
the high capacity stage. The additional
heating mode stage is the booster capacity
stage, which offers the highest heating
capacity output for a given set of ambient
operating conditions.
Triple-split system means a central air
conditioner or heat pump that is composed
of three separate components: An outdoor fan
coil section, an indoor blower coil section,
and an indoor compressor section.
Two-capacity (or two-stage) compressor
system means a central air conditioner or
heat pump that has a compressor or a group
of compressors operating with only two
stages of capacity.
For such systems, low capacity means the
compressor(s) operating at low stage, or at
low load test conditions. The low compressor
stage for heating mode tests may be the same
or different from the cooling mode value.
For such systems, high capacity means the
compressor(s) operating at low stage, or at
full load test conditions.
Two-capacity, northern heat pump means
a heat pump that has a factory or fieldselectable lock-out feature to prevent space
cooling at high-capacity. Two-capacity heat
pumps having this feature will typically have
two sets of ratings, one with the feature
disabled and one with the feature enabled.
The certified indoor coil model number
should reflect whether the ratings pertain to
the lockout enabled option via the inclusion
of an extra identifier, such as ‘‘+LO’’. When
testing as a two-capacity, northern heat
pump, the lockout feature must remain
enabled for all tests.
Variable refrigerant flow (VRF) system
means a multi-split system with at least three
compressor capacity stages, distributing
refrigerant through a piping network to
multiple indoor blower coil units each
capable of individual zone temperature
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control, through proprietary zone
temperature control devices and a common
communications network. Single-phase VRF
systems less than 65,000 Btu/h are a kind of
central air conditioners and central air
conditioning heat pumps.
Variable-speed compressor system means a
central air conditioner or heat pump that has
a compressor that uses a variable-speed drive
to vary the compressor speed to achieve
variable capacities.
For such a system, maximum speed means
the maximum operating speed, measured by
RPM or frequency (Hz), that the unit is
designed to operate in cooling mode or
heating mode. Maximum speed does not
change with ambient temperature, and it can
be different from cooling mode to heating
mode. Maximum speed does not necessarily
mean maximum capacity.
For such systems, minimum speed means
the minimum speed, measured by RPM or
frequency (Hz), that the unit is designed to
operate in cooling mode or heating mode.
Minimum speed does not change with
ambient temperature, and it can be different
from cooling mode to heating mode.
Minimum speed does not necessarily mean
minimum capacity.
Wet-coil test means a test conducted at test
conditions that typically cause water vapor to
condense on the test unit evaporator coil.
2. Testing Overview and Conditions
(A) Test VRF systems using ANSI/AHRI
Standard 1230–2010 sections 3 (except 3.8,
3.9, 3.13, 3.14, 3.15, 3.16, 3.23, 3.24, 3.26,
3.27, 3.28, 3.29, 3.30, and 3.31), 5.1.3, 5.1.4,
6.1.5 (except Table 8), 6.1.6, and 6.2
(incorporated by reference, see § 430.3) and
Appendix M. Where ANSI/AHRI Standard
1230–2010 refers to the Appendix C therein
substitute the provisions of this appendix. In
cases where there is a conflict, the language
of the test procedure in this appendix takes
precedence over ANSI/AHRI Standard 1230–
2010.
For definitions use section 1 of Appendix
M and section 3 of ANSI/AHRI Standard
1230–2010, excluding sections 3.8, 3.9, 3.13,
3.14, 3.15, 3.16, 3.23, 3.24, 3.26, 3.27, 3.28,
3.29, 3.30, and 3.31. For rounding
requirements refer to § 430.23 (m). For
determination of certified rating
requirements refer to § 429.16.
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For test room requirements, refer to section
2.1 from Appendix M. For test unit
installation requirements refer to sections
2.2.a, 2.2.b, 2.2.c, 2.2.1, 2.2.2, 2.2.3(a),
2.2.3(c), 2.2.4, 2.2.5, and 2.4 to 2.12 from
Appendix M, and sections 5.1.3 and 5.1.4 of
ANSI/AHRI Standard 1230–2010.
For general requirements for the test
procedure refer to section 3.1 of Appendix M,
except for sections 3.1.3 and 3.1.4, which are
requirements for indoor air volume and
outdoor air volume. For indoor air volume
and outdoor air volume requirements, refer
instead to section 6.1.5 (except Table 8) and
6.1.6 of ANSI/AHRI Standard 1230–2010. For
external static pressure requirements, refer to
Table 3 in Appendix M.
For the test procedure, refer to sections 3.3
to 3.5 and 3.7 to 3.13 in Appendix M. For
cooling mode and heating mode test
conditions, refer to section 6.2 of ANSI/AHRI
Standard 1230–2010. For calculations of
seasonal performance descriptors use section
4 of Appendix M.
(B) For systems other than VRF, only a
subset of the sections listed in this test
procedure apply when testing and rating a
particular unit. Table 1 shows the sections of
the test procedure that apply to each system.
This table is meant to assist manufacturers in
finding the appropriate sections of the test
procedure; the appendix sections rather than
the table provide the specific requirements
for testing, and given the varied nature of
available units, manufacturers are
responsible for determining which sections
apply to each unit tested. To use this table,
first refer to the sections listed under ‘‘all
units’’. Then refer to additional requirements
based on:
(1) System configuration(s),
(2) The compressor staging or modulation
capability, and
(3) Any special features.
Testing requirements for space-constrained
products do not differ from similar
equipment that is not space-constrained and
thus are not listed separately in this table. Air
conditioners and heat pumps are not listed
separately in this table, but heating
procedures and calculations apply only to
heat pumps.
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Testing conditions
Testing procedures
Calculations
Gen-
General
Cooling'
General
Heating "
Cool-
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era!
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.
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2.1; 2.2a-c; 22.1; 2.2.4; 2.2.4.1;
2.2.4.1 (1); 2.2.4.2; 2.2.5.1-5;
3.1; 3.1.1-3;
4.4;
3.1.4.7; 3.1.10; 3.7a,h,d;
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Requirements for All units (except VRF)
22.5.7-g; 2.3; 2.3.1; 2.3.2; 2.4;
3.1.5-9; 3.11;
I
3 3; 3.4; 3.5a-i
4.5;
3.8a,d; 3.8.1; 3.9; 3.10
2.4.la,d; 2.5a-c; 2.5.1; 2.5.2-
I 3.12
4.6
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2.5.4.2; 2.5.5- 2.13
3.1.4.4.1; 3.1.4.4.2;
3.1.4.1.1; 3.1.4.l.la,b;
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3.1.4.5.2a-c; 3.1.4.6a-b
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142
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
04:57 Nov 07, 2015
Table 1 Informative Guidance for Using A 1
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69401
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tkelley on DSK3SPTVN1PROD with PROPOSALS2
69402
VerDate Sep<11>2014
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Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
04:57 Nov 07, 2015
3.1.4.4.3
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EP09NO15.144</GPH>
3.1.4.1.1 Table 4
tkelley on DSK3SPTVN1PROD with PROPOSALS2
2.1
VerDate Sep<11>2014
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09NOP2
tuse ANSI/AHRI Standard 1230-2010 with Addendum 2, with the sections referenced in section 2(A) of this Appendix, in conjunction with the sections set forth
in the table to perform test setup, testing, and calculations for rating VRF multiple-split and VRF SDHV systems.
NOTE: For all units, use section 3.13 for off mode testing procedures and section 4.3 for off mode calculations. For all units subject to an EER standard, use
section4.7 to determine the energy efficiency ratio.
69403
For multiple-split, single-zone-multi-coil or
multi-circuit air conditioners and heat
E:\FR\FM\09NOP2.SGM
a. Test using two side-by-side rooms, an
indoor test room and an outdoor test room.
PO 00000
**Applies only to heat pumps; not to air conditioners.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
Test room requirements.
04:57 Nov 07, 2015
EP09NO15.145</GPH>
*Does not apply to heating-only heat pumps.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
69404
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
pumps, however, use as many available
indoor test rooms as needed to accommodate
the total number of indoor units. These
rooms must comply with the requirements
specified in sections 8.1.2 and 8.1.3 of
ASHRAE Standard 37–2009 (incorporated by
reference, see § 430.3).
b. Inside these test rooms, use artificial
loads during cyclic tests and Frost
Accumulation tests, if needed, to produce
stabilized room air temperatures. For one
room, select an electric resistance heater(s)
having a heating capacity that is
approximately equal to the heating capacity
of the test unit’s condenser. For the second
room, select a heater(s) having a capacity that
is close to the sensible cooling capacity of the
test unit’s evaporator. When applied, cycle
the heater located in the same room as the
test unit evaporator coil ON and OFF when
the test unit cycles ON and OFF. Cycle the
heater located in the same room as the test
unit condensing coil ON and OFF when the
test unit cycles OFF and ON.
2.2 Test unit installation requirements.
a. Install the unit according to section 8.2
of ASHRAE Standard 37–2009 (incorporated
by reference, see § 430.3), subject to the
following additional requirements:
(1) When testing split systems, follow the
requirements given in section 6.1.3.5 of AHRI
210/240–2008 (incorporated by reference, see
§ 430.3) with Addendum 1 and 2. For the
vapor refrigerant line(s), use the insulation
included with the unit; if no insulation is
provided, refer to the specifications for the
insulation in the installation instructions
included with the unit by the manufacturer;
if no insulation is included with the unit and
the installation instructions do not contain
provisions for insulating the line(s), fully
insulate the vapor refrigerant line(s) with
vapor proof insulation having an inside
diameter that matches the refrigerant tubing
and a nominal thickness of at least 0.5
inches. For the liquid refrigerant line(s), use
the insulation included with the unit; if no
insulation is provided, refer to the
specifications for the insulation in the
installation instructions included with the
unit by the manufacturer; if no insulation is
included with the unit and the installation
instructions do not contain provisions for
insulating the line(s), leave the liquid
refrigerant line(s) exposed to the air for air
conditioners and heat pumps that heat and
cool; or, for heating-only heat pumps,
insulate the liquid refrigerant line(s) with
insulation having an inside diameter that
matches the refrigerant tubing and a nominal
thickness of at least 0.5 inches;
(2) When testing split systems, if the
indoor unit does not ship with a cooling
mode expansion device, test the system using
the device as specified in the installation
instructions provided with the indoor unit. If
none is specified, test the system using a
thermostatic expansion valve with internal
pressure equalization that the valve
manufacturer’s product literature indicates is
appropriate for the system.
(3) When testing triple-split systems (see
section 1.2, Definitions), use the tubing
length specified in section 6.1.3.5 of AHRI
210/240–2008 (incorporated by reference, see
§ 430.3) with Addendum 1 and 2 to connect
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the outdoor coil, indoor compressor section,
and indoor coil while still meeting the
requirement of exposing 10 feet of the tubing
to outside conditions; or
(4) When testing split systems having
multiple indoor coils, connect each indoor
blower-coil to the outdoor unit using:
(a) 25 feet of tubing, or
(b) Tubing furnished by the manufacturer,
whichever is longer.
If they are needed to make a secondary
measurement of capacity, install refrigerant
pressure measuring instruments as described
in section 8.2.5 of ASHRAE Standard 37–
2009(incorporated by reference, see § 430.3).
Refer to section 2.10 of this appendix to learn
which secondary methods require refrigerant
pressure measurements. At a minimum,
insulate the low-pressure line(s) of a split
system with insulation having an inside
diameter that matches the refrigerant tubing
and a nominal thickness of 0.5 inch.
b. For units designed for both horizontal
and vertical installation or for both up-flow
and down-flow vertical installations, the
manufacturer must use the orientation for
testing specified in the certification report.
Conduct testing with the following installed:
(1) The most restrictive filter(s);
(2) Supplementary heating coils; and
(3) Other equipment specified as part of the
unit, including all hardware used by a heat
comfort controller if so equipped (see section
1, Definitions). For small-duct, high-velocity
systems, configure all balance dampers or
restrictor devices on or inside the unit to
fully open or lowest restriction.
c. Testing a ducted unit without having an
indoor air filter installed is permissible as
long as the minimum external static pressure
requirement is adjusted as stated in Table 3,
note 3 (see section 3.1.4). Except as noted in
section 3.1.10, prevent the indoor air
supplementary heating coils from operating
during all tests. For coil-only indoor units
that are supplied without an enclosure,
create an enclosure using 1 inch fiberglass
ductboard having a nominal density of 6
pounds per cubic foot. Or alternatively, use
some other insulating material having a
thermal resistance (‘‘R’’ value) between 4 and
6 hr·ft2· °F/Btu. For units where the coil is
housed within an enclosure or cabinet, no
extra insulating or sealing is allowed.
d. When testing oil-only central air
conditioners and heat pumps, install a
toroidal-type transformer to power the
system’s low-voltage components, complying
with any additional requirements for this
transformer mentioned in the installation
manuals included with the unit by the
manufacturer. If the installation manuals do
not provide specifications for the
transformer, use a transformer having the
following features:
(1) A nominal volt-amp rating that results
in the transformer being loaded at a level that
is between 25 and 90 percent based on the
highest power value expected and then
confirmed during the off mode test;
(2) Designed to operate with a primary
input of 230 V, single phase, 60 Hz; and
(3) That provides an output voltage that is
within the specified range for each lowvoltage component. The power consumption
of the components connected to the
PO 00000
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transformer must be included as part of the
total system power consumption during the
off mode tests, less if included the power
consumed by the transformer when no load
is connected to it.
e. An outdoor unit with no match (i.e., that
is not sold with indoor units) shall be tested
without an indoor blower installed, with a
single cooling air volume rate, using an
indoor unit whose coil has (1) round tubes
of outer diameter no less than 0.375 inches,
and (2) a normalized gross indoor fin surface
(NGIFS) no greater than 1.15 square inches
per British thermal unit per hour (sq. in./Btu/
hr). NGIFS is calculated as follows:
˙
NGIFS = 2 × Lf × Wf × Nf ÷ Qc(95)
Where,
Lf = Indoor coil fin length in inches, also
height of the coil transverse to the tubes.
Wf = Indoor coil fin width in inches, also
depth of the coil.
Nf = Number of fins.
˙
Qc(95) = the measured space cooling
capacity of the tested outdoor unit/indoor
unit combination as determined from the A2
or A Test whichever applies, Btu/h.
2.2.1 Defrost control settings.
Set heat pump defrost controls at the
normal settings which most typify those
encountered in generalized climatic region
IV. (Refer to Figure 1 and Table 19 of section
4.2 for information on region IV.) For heat
pumps that use a time-adaptive defrost
control system (see section 1.2, Definitions),
the manufacturer must specify the frosting
interval to be used during Frost
Accumulation tests and provide the
procedure for manually initiating the defrost
at the specified time. To ease testing of any
unit, the manufacturer should provide
information and any necessary hardware to
manually initiate a defrost cycle.
2.2.2 Special requirements for units
having a multiple-speed outdoor fan.
Configure the multiple-speed outdoor fan
according to the installation manual included
with the unit by the manufacturer, and
thereafter, leave it unchanged for all tests.
The controls of the unit must regulate the
operation of the outdoor fan during all lab
tests except dry coil cooling mode tests. For
dry coil cooling mode tests, the outdoor fan
must operate at the same speed used during
the required wet coil test conducted at the
same outdoor test conditions.
2.2.3 Special requirements for multi-split
air conditioners and heat pumps, systems
composed of multiple single-zone-multiplecoil split-system units (having multiple
outdoor units located side-by-side), and
ducted systems using a single indoor section
containing multiple blowers that would
normally operate using two or more indoor
thermostats.
Because these systems will have more than
one indoor blower and possibly multiple
outdoor fans and compressor systems,
references in this test procedure to a singular
indoor blower, outdoor fan, and compressor
means all indoor blowers, all outdoor fans,
and all compressor systems that are
energized during the test.
a. Additional requirements for multi-split
air conditioners and heat pumps and systems
composed of multiple single-zone-multiple-
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09NOP2
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
coil split-system units. For any test where the
system is operated at part load (i.e., one or
more compressors ‘‘off’’, operating at the
intermediate or minimum compressor speed,
or at low compressor capacity), the
manufacturer shall designate the indoor
coil(s) that are not providing heating or
cooling during the test such that the sum of
the nominal heating or cooling capacity of
the operational indoor units is within 5
percent of the intended part load heating or
cooling capacity. For variable-speed systems,
the manufacturer must designate at least one
indoor unit that is not providing heating or
cooling for all tests conducted at minimum
compressor speed. For all other part-load
tests, the manufacturer shall choose to turn
off zero, one, two, or more indoor units. The
chosen configuration shall remain unchanged
for all tests conducted at the same
compressor speed/capacity. For any indoor
coil that is not providing heating or cooling
during a test, cease forced airflow through
this indoor coil and block its outlet duct.
b. Additional requirements for ducted
systems with a single indoor section
containing multiple blowers where the
blowers are designed to cycle on and off
independently of one another and are not
controlled such that all blowers are
modulated to always operate at the same air
volume rate or speed. This Appendix covers
systems with a single-speed compressor or
systems offering two fixed stages of
compressor capacity (e.g., a two-speed
compressor, two single-speed compressors).
For any test where the system is operated at
its lowest capacity—i.e., the lowest total air
volume rate allowed when operating the
single-speed compressor or when operating
at low compressor capacity—blowers
accounting for at least one-third of the fullload air volume rate must be turned off
unless prevented by the controls of the unit.
In such cases, turn off as many blowers as
permitted by the unit’s controls. Where more
than one option exists for meeting this ‘‘off’’
blower requirement, the manufacturer shall
include in its installation manuals included
with the unit which blower(s) are turned off.
The chosen configuration shall remain
unchanged for all tests conducted at the same
lowest capacity configuration. For any indoor
coil turned off during a test, cease forced
airflow through any outlet duct connected to
an ‘‘off’’ blower.
c. For test setups where it is physically
impossible for the laboratory to use the
required line length listed in Table 3 of
ANSI/AHRI Standard 1230–2010
(incorporated by reference, see § 430.3) with
Addendum 2, then the actual refrigerant line
length used by the laboratory may exceed the
required length and the refrigerant line
length correction factors in Table 4 of ANSI/
AHRI Standard 1230–2010 with Addendum
2 are applied.
2.2.4 Wet-bulb temperature requirements
for the air entering the indoor and outdoor
coils.
2.2.4.1 Cooling mode tests.
For wet-coil cooling mode tests, regulate
the water vapor content of the air entering
the indoor unit to the applicable wet-bulb
temperature listed in Tables 4 to 7. As noted
in these same tables, achieve a wet-bulb
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Jkt 238001
temperature during dry-coil cooling mode
tests that results in no condensate forming on
the indoor coil. Controlling the water vapor
content of the air entering the outdoor side
of the unit is not required for cooling mode
tests except when testing:
(1) Units that reject condensate to the
outdoor coil during wet coil tests. Tables 4–
7 list the applicable wet-bulb temperatures.
(2) Single-package units where all or part
of the indoor section is located in the outdoor
test room. The average dew point
temperature of the air entering the outdoor
coil during wet coil tests must be within
±3.0 °F of the average dew point temperature
of the air entering the indoor coil over the 30minute data collection interval described in
section 3.3. For dry coil tests on such units,
it may be necessary to limit the moisture
content of the air entering the outdoor side
of the unit to meet the requirements of
section 3.4.
2.2.4.2 Heating mode tests.
For heating mode tests, regulate the water
vapor content of the air entering the outdoor
unit to the applicable wet-bulb temperature
listed in Tables 11 to 14. The wet-bulb
temperature entering the indoor side of the
heat pump must not exceed 60 °F.
Additionally, if the Outdoor Air Enthalpy
test method is used while testing a singlepackage heat pump where all or part of the
outdoor section is located in the indoor test
room, adjust the wet-bulb temperature for the
air entering the indoor side to yield an
indoor-side dew point temperature that is as
close as reasonably possible to the dew point
temperature of the outdoor-side entering air.
2.2.5 Additional refrigerant charging
requirements.
2.2.5.1 The ‘‘manufacturer’s published
instructions,’’ as stated in section 8.2 of
ASHRAE Standard 37–2009 (incorporated by
reference, see § 430.3) and ‘‘manufacturer’s
installation instructions’’ discussed in this
Appendix mean the manufacturer’s
installation instructions that come packaged
with or appear in the labels applied to the
unit. This does not include online manuals.
Installation instructions that are shipped
with the unit shall take precedence over
installation instructions that appear in the
labels applied to the unit.
2.2.5.2 Instructions to Use for Charging
a. Where the manufacturer’s installation
instructions contain two sets of refrigerant
charging criteria, one for field installations
and one for lab testing, use the field
installation criteria.
b. For systems consisting of an outdoor
unit manufacturer’s outdoor section and
indoor section with differing charging
procedures the refrigerant charge shall be
adjusted per the outdoor installation
instructions.
c. For systems consisting of an outdoor
unit manufacturer’s outdoor section and an
independent coil manufacturer’s indoor
section with differing charging procedures
the refrigerant charge shall be adjusted per
the indoor installation instructions.
2.2.5.3 Test(s) to Use for Charging
a. Use the tests or operating conditions
specified in the manufacturer’s installation
instructions for charging.
b. If the manufacturer’s installation
instructions do not specify a test or operating
PO 00000
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69405
conditions for charging or there are no
manufacturer’s instructions, use the
following test(s):
(1) For air conditioners or cooling and
heating heat pumps, use the A or A2 test.
(2) For cooling and heating heat pumps
that do not function in the H1 or H12 test
with the charge set for the A or A2 test and
for heating-only heat pumps, use the H1 or
H12 test.
2.2.5.4 Parameters to Set and Their Target
Values
a. Consult the manufacturer’s installation
instructions regarding which parameters to
set and their target values. If the instructions
provide ranges of values, select target values
equal to the midpoints of the provided
ranges.
b. In the event of conflicting information
between charging instructions (defined as
multiple conditions given for charge
adjustment where all conditions specified
cannot be met), follow the following
hierarchy.
(1) For fixed orifice systems:
(i) Superheat
(ii) High side pressure or corresponding
saturation or dew-point temperature
(iii) Low side pressure or corresponding
saturation or dew-point temperature
(iv) Low side temperature
(v) High side temperature
(vi) Charge weight
(2) For expansion valve systems:
(i) Subcooling
(ii) High side pressure or corresponding
saturation or dew-point temperature
(iii) Low side pressure or corresponding
saturation or dew-point temperature
(iv) Approach temperature (difference
between temperature of liquid leaving
condenser and condenser average inlet
air temperature)
(v) Charge weight
c. If there are no installation instructions
and/or they do not provide parameters and
target values, set superheat to a target value
of 12 °F for fixed orifice systems or set
subcooling to a target value of 10 °F for
expansion valve systems.
2.2.5.5 Charging Tolerances
a. If the manufacturer’s installation
instructions specify tolerances on target
values for the charging parameters, set the
values using these tolerances.
b. Otherwise, use the following tolerances
for the different charging parameters:
1. Superheat: ±2.0 °F
2. Subcooling: ±0.6 °F
3. High side pressure or corresponding
saturation or dew point temperature:
±4.0 psi or ±1.0 °F
4. Low side pressure or corresponding
saturation or dew point temperature:
±2.0 psi or ±0.8 °F
5. High side temperature: ±2.0 °F
6. Low side temperature: ±2.0 °F
7. Approach temperature: ±1.0 °F
8. Charge weight: ±2.0 ounce
2.2.5.6 Special Charging Instructions
a. Cooling and Heating Heat Pumps
If, using the initial charge set in the A or
A2 test, the conditions are not within the
range specified in manufacturer’s
instructions for the H1 or H12 test, make as
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Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
small as possible an adjustment to obtain
conditions for this test in the specified range.
After this adjustment, recheck conditions in
the A or A2 test to confirm that they are still
within the specified range for this test.
b. Single-Package Systems
Unless otherwise directed by the
manufacturer’s installation instructions,
install one or more refrigerant line pressure
gauges during the setup of the unit if setting
of refrigerant charge is based on certain
operating parameters:
(1) Install a pressure gauge on the liquid
line if charging is on the basis of subcooling,
or high side pressure or corresponding
saturation or dew point temperature;
(2) Install a pressure gauge on the suction
line if charging is on the basis of superheat,
or low side pressure or corresponding
saturation or dew point temperature. If
manufacturer’s installation instructions
indicate that pressure gauges are not to be
installed, setting of charge shall not be based
on any of the parameters listed in b.(1) and
(2) of this section.
2.2.5.7 Near-azeotropic and zeotropic
refrigerants.
Charging of near-azeotropic and zeotropic
refrigerants shall only be performed with
refrigerant in the liquid state.
2.2.5.8 Adjustment of charge between
tests.
After charging the system as described in
this test procedure, use the set refrigerant
charge for all tests used to determine
performance. Do not adjust the refrigerant
charge at any point during testing.
2.3 Indoor air volume rates.
If a unit’s controls allow for overspeeding
the indoor blower (usually on a temporary
basis), take the necessary steps to prevent
overspeeding during all tests.
2.3.1 Cooling tests.
a. Set indoor blower airflow-control
settings (e.g., fan motor pin settings, fan
motor speed) according to the installation
instructions that are provided with the
equipment while meeting the airflow
requirements that are specified in section
3.1.4. If the manufacturer installation
instructions do not provide guidance on the
airflow-control settings for a system tested
with the indoor blower installed, select the
lowest speed that will satisfy the minimum
external static pressure specified in section
3.1.4.1.1 with an air volume rate at or higher
than the rated full-load cooling air volume
rate while meeting the maximum air flow
requirement.
b. Express the Cooling Full-load Air
Volume Rate, the Cooling Minimum Air
Volume Rate, and the Cooling Intermediate
Air Volume Rate in terms of standard air.
2.3.2 Heating tests.
a. If needed, set the indoor blower airflowcontrol settings (e.g., fan motor pin settings,
fan motor speed) according to the installation
instructions that are provided with the
equipment. Do this set-up while meeting all
applicable airflow requirements specified in
sections 3.1.4. For a cooling and heating heat
pump tested with an indoor blower installed,
if the manufacturer installation instructions
do not provide guidance on the fan airflowcontrol settings, use the same airflow-control
settings used for the cooling test. If the
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04:57 Nov 07, 2015
Jkt 238001
manufacturer installation instructions do not
provide guidance on the airflow-control
settings for a heating-only heat pump tested
with the indoor blower installed, select the
lowest speed that will satisfy the minimum
external static pressure specified in section
3.1.4.4.3 with an air volume rate at or higher
than the rated heating full-load air volume
rate.
b. Express the Heating Full-Load Air
Volume Rate, the Heating Minimum Air
Volume Rate, the Heating Intermediate Air
Volume Rate, and the Heating Nominal Air
Volume Rate in terms of standard air.
2.4 Indoor coil inlet and outlet duct
connections.
Insulate and/or construct the outlet
plenum described in section 2.4.1 and, if
installed, the inlet plenum described in
section 2.4.2 with thermal insulation having
a nominal overall resistance (R-value) of at
least 19 hr·ft2· °F/Btu.
2.4.1 Outlet plenum for the indoor unit.
a. Attach a plenum to the outlet of the
indoor coil. (NOTE: for some packaged
systems, the indoor coil may be located in
the outdoor test room.)
b. For systems having multiple indoor
coils, or multiple indoor blowers within a
single indoor section, attach a plenum to
each indoor coil or blower outlet. Connect
two or more outlet plenums to a single
common duct so that each indoor coil
ultimately connects to an airflow measuring
apparatus (section 2.6). If using more than
one indoor test room, do likewise, creating
one or more common ducts within each test
room that contains multiple indoor coils. At
the plane where each plenum enters a
common duct, install an adjustable airflow
damper and use it to equalize the static
pressure in each plenum. Each outlet air
temperature grid (section 2.5.4) and airflow
measuring apparatus are located downstream
of the inlet(s) to the common duct.
c. For small-duct, high-velocity systems,
install an outlet plenum that has a diameter
that is equal to or less than the value listed
below. The limit depends only on the
Cooling Full-Load Air Volume Rate (see
section 3.1.4.1.1) and is effective regardless
of the flange dimensions on the outlet of the
unit (or an air supply plenum adapter
accessory, if installed in accordance with the
manufacturer’s installation instructions).
d. Add a static pressure tap to each face of
the (each) outlet plenum, if rectangular, or at
four evenly distributed locations along the
circumference of an oval or round plenum.
Create a manifold that connects the four
static pressure taps. Figures 7a, 7b, 7c of
ASHRAE Standard 37–2009 (incorporated by
reference, see § 430.3) shows two of the three
options allowed for the manifold
configuration; the third option is the brokenring, four-to-one manifold configuration that
is shown in Figure 7a of ASHRAE Standard
37–2009. See Figures 7a, 7b, 7c, and 8 of
ASHRAE Standard 37–2009 for the crosssectional dimensions and minimum length of
the (each) plenum and the locations for
adding the static pressure taps for units
tested with and without an indoor blower
installed.
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TABLE 2—SIZE OF OUTLET PLENUM
Cooling full-load air volume
rate
(scfm)
≤500 ......................................
501 to 700 ............................
701 to 900 ............................
901 to 1100 ..........................
1101 to 1400 ........................
1401 to 1750 ........................
Maximum diameter * of
outlet plenum
(inches)
6
7
8
9
10
11
* If the outlet plenum is rectangular, calculate its equivalent diameter using (4A/P,)
where A is the cross-sectional area and P is
the perimeter of the rectangular plenum, and
compare it to the listed maximum diameter.
2.4.2 Inlet plenum for the indoor unit.
Install an inlet plenum when testing a coilonly indoor unit or a packaged system where
the indoor coil is located in the outdoor test
room. Add static pressure taps at the center
of each face of this plenum, if rectangular, or
at four evenly distributed locations along the
circumference of an oval or round plenum.
Make a manifold that connects the four
static-pressure taps using one of the three
configurations specified in section 2.4.1. See
Figures 7b, 7c, and Figure 8 of ASHRAE
Standard 37–2009 (incorporated by reference,
see § 430.3) for cross-sectional dimensions,
the minimum length of the inlet plenum, and
the locations of the static-pressure taps.
When testing a ducted unit having an indoor
blower (and the indoor coil is in the indoor
test room), test with an inlet plenum
installed unless physically prohibited by
space limitations within the test room. If
used, construct the inlet plenum and add the
four static-pressure taps as shown in Figure
8 of ASHRAE Standard 37–2009. If used, the
inlet duct size shall equal the size of the inlet
opening of the air-handling (blower coil) unit
or furnace, with a minimum length of 6
inches. Manifold the four static-pressure taps
using one of the three configurations
specified in section 2.4.1.d. Never use an
inlet plenum when testing a non-ducted
system.
2.5 Indoor coil air property
measurements and air damper box
applications.
Follow instructions for indoor coil air
property measurements as described in AHRI
210/240-Draft, appendix E, section E4, unless
otherwise instructed in this section.
a. Measure the dry-bulb temperature and
water vapor content of the air entering and
leaving the indoor coil. If needed, use an air
sampling device to divert air to a sensor(s)
that measures the water vapor content of the
air. See Section 5.3 of ASHRAE Standard
41.1–2013 (incorporated by reference, see
§ 430.3) for guidance on constructing an air
sampling device. No part of the air sampling
device or the tubing transferring the sampled
air to the sensor shall be within two inches
of the test chamber floor, and the transfer
tubing shall be insulated. The sampling
device may also divert air to a remotely
located sensor(s) that measures dry bulb
temperature. The air sampling device and the
remotely located temperature sensor(s) may
be used to determine the entering air dry
bulb temperature during any test. The air
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sampling device and the remotely located
leaving air dry bulb temperature sensor(s)
may be used for all tests except:
(1) Cyclic tests; and
(2) Frost accumulation tests.
b. An acceptable alternative in all cases,
including the two special cases noted above,
is to install a grid of dry bulb temperature
sensors within the outlet and inlet ducts. Use
a temperature grid to get the average dry bulb
temperature at one location, leaving or
entering, or when two grids are applied as a
thermopile, to directly obtain the
temperature difference. A grid of temperature
sensors (which may also be used for
determining average leaving air dry bulb
temperature) is required to measure the
temperature distribution within a crosssection of the leaving airstream.
c. Use an inlet and outlet air damper box,
an inlet upturned duct, or any combination
thereof when conducting one or both of the
cyclic tests listed in sections 3.2 and 3.6 on
ducted systems. Otherwise if not conducting
one or both of said cyclic tests, install an
outlet air damper box when testing ducted
and non-ducted heat pumps that cycle off the
indoor blower during defrost cycles if no
other means is available for preventing
natural or forced convection through the
indoor unit when the indoor blower is off.
Never use an inlet damper box or an inlet
upturned duct when testing a non-ducted
system. An inlet upturned duct is a length of
ductwork so installed upstream from the
inlet such that the indoor duct inlet opening,
facing upwards, is sufficiently high to
prevent natural convection transfer out of the
duct. If an inlet upturned duct is used, install
a dry bulb temperature sensor near the inlet
opening of the indoor duct at a centerline
location not higher than the lowest elevation
of the duct edges at the inlet, and ensure that
the variation of the dry bulb temperature at
this location, measured at least every minute
during the compressor OFF period of the
cyclic test, does not exceed 1.0 °F.
2.5.1 Test set-up on the inlet side of the
indoor coil: For cases where the inlet airflow
prevention device is installed.
a. Install an airflow prevention device as
specified in section 2.5.1.1 or 2.5.1.2,
whichever applies.
b. For an inlet damper box, locate the grid
of entering air dry-bulb temperature sensors,
if used, and the air sampling device, or the
sensor used to measure the water vapor
content of the inlet air, at a location
immediately upstream of the damper box
inlet. For an inlet upturned duct, locate the
grid of entering air dry-bulb temperature
sensors, if used, and the air sampling device,
or the sensor used to measure the water
vapor content of the inlet air, at a location
at least one foot downstream from the
beginning of the insulated portion of the duct
but before the static pressure measurement;
install a dry-bulb temperature sensor at a
centerline location not higher than the lowest
elevation of the duct edges at the device
inlet.
2.5.1.1 If the section 2.4.2 inlet plenum is
installed.
Construct the airflow prevention device
having a cross-sectional flow area equal to or
greater than the flow area of the inlet
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plenum. Install the airflow prevention device
upstream of the inlet plenum and construct
ductwork connecting it to the inlet plenum.
If needed, use an adaptor plate or a transition
duct section to connect the airflow
prevention device with the inlet plenum.
Insulate the ductwork and inlet plenum with
thermal insulation that has a nominal overall
resistance (R-value) of at least 19 hr · ft2
· °F/Btu.
2.5.1.2 If the section 2.4.2 inlet plenum is
not installed.
Construct the airflow prevention device
having a cross-sectional flow area equal to or
greater than the flow area of the air inlet of
the indoor unit. Install the airflow prevention
device immediately upstream of the inlet of
the indoor unit. If needed, use an adaptor
plate or a short transition duct section to
connect the airflow prevention device with
the unit’s air inlet. Add static pressure taps
at the center of each face of a rectangular
airflow prevention device, or at four evenly
distributed locations along the circumference
of an oval or round airflow prevention
device. Locate the pressure taps between the
airflow prevention device and the inlet of the
indoor unit. Make a manifold that connects
the four static pressure taps. Insulate the
ductwork with thermal insulation that has a
nominal overall resistance (R-value) of at
least 19 hr·ft2 · °F/Btu.
2.5.2 Test set-up on the inlet side of the
indoor unit: For cases where no airflow
prevention device is installed.
If using the section 2.4.2 inlet plenum and
a grid of dry bulb temperature sensors, mount
the grid at a location upstream of the static
pressure taps described in section 2.4.2,
preferably at the entrance plane of the inlet
plenum. If the section 2.4.2 inlet plenum is
not used, but a grid of dry bulb temperature
sensors is used, locate the grid approximately
6 inches upstream from the inlet of the
indoor coil. Or, in the case of non-ducted
units having multiple indoor coils, locate a
grid approximately 6 inches upstream from
the inlet of each indoor coil. Position an air
sampling device, or the sensor used to
measure the water vapor content of the inlet
air, immediately upstream of the (each)
entering air dry-bulb temperature sensor grid.
If a grid of sensors is not used, position the
entering air sampling device (or the sensor
used to measure the water vapor content of
the inlet air) as if the grid were present.
2.5.3 Indoor coil static pressure
difference measurement.
Section 6.5.2 of ASHRAE Standard 37–
2009 describes the method for fabricating
static-pressure taps. Also refer to Figure 2A
of ASHRAE Standard 51–07/AMCA Standard
210–07 (incorporated by reference, see
§ 430.3). Use a differential pressure
measuring instrument that is accurate to
within ±0.01 inches of water and has a
resolution of at least 0.01 inches of water to
measure the static pressure difference
between the indoor coil air inlet and outlet.
Connect one side of the differential pressure
instrument to the manifolded pressure taps
installed in the outlet plenum. Connect the
other side of the instrument to the
manifolded pressure taps located in either
the inlet plenum or incorporated within the
airflow prevention device. If an inlet plenum
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or inlet airflow prevention device is not used,
leave the inlet side of the differential
pressure instrument open to the surrounding
atmosphere. For non-ducted systems that are
tested with multiple outlet plenums, measure
the static pressure within each outlet plenum
relative to the surrounding atmosphere.
2.5.4 Test set-up on the outlet side of the
indoor coil.
a. Install an interconnecting duct between
the outlet plenum described in section 2.4.1
and the airflow measuring apparatus
described below in section 2.6. The crosssectional flow area of the interconnecting
duct must be equal to or greater than the flow
area of the outlet plenum or the common
duct used when testing non-ducted units
having multiple indoor coils. If needed, use
adaptor plates or transition duct sections to
allow the connections. To minimize leakage,
tape joints within the interconnecting duct
(and the outlet plenum). Construct or
insulate the entire flow section with thermal
insulation having a nominal overall
resistance (R-value) of at least 19 hr·ft2· °F/
Btu.
b. Install a grid(s) of dry-bulb temperature
sensors inside the interconnecting duct. Also,
install an air sampling device, or the
sensor(s) used to measure the water vapor
content of the outlet air, inside the
interconnecting duct. Locate the dry-bulb
temperature grid(s) upstream of the air
sampling device (or the in-duct sensor(s)
used to measure the water vapor content of
the outlet air). Air that circulates through an
air sampling device and past a remote watervapor-content sensor(s) must be returned to
the interconnecting duct at a location:
(1) Downstream of the air sampling device;
(2) Upstream of the outlet air damper box,
if installed; and
(3) Upstream of the section 2.6 airflow
measuring apparatus.
2.5.4.1 Outlet air damper box placement
and requirements.
If using an outlet air damper box (see
section 2.5), install it within the
interconnecting duct at a location
downstream of the location where air from
the sampling device is reintroduced or
downstream of the in-duct sensor that
measures water vapor content of the outlet
air. The leakage rate from the combination of
the outlet plenum, the closed damper, and
the duct section that connects these two
components must not exceed 20 cubic feet
per minute when a negative pressure of 1
inch of water column is maintained at the
plenum’s inlet.
2.5.4.2 Procedures to minimize
temperature maldistribution.
Use these procedures if necessary to
correct temperature maldistributions. Install
a mixing device(s) upstream of the outlet air,
dry-bulb temperature grid (but downstream
of the outlet plenum static pressure taps).
Use a perforated screen located between the
mixing device and the dry-bulb temperature
grid, with a maximum open area of 40
percent. One or both items should help to
meet the maximum outlet air temperature
distribution specified in section 3.1.8. Mixing
devices are described in sections 5.3.2 and
5.3.3 of ASHRAE Standard 41.1–2013
(incorporated by reference, see § 430.3) and
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section 5.2.2 of ASHRAE Standard 41.2–87
(RA 92) (incorporated by reference, see
§ 430.3).
2.5.4.3 Minimizing air leakage.
For small-duct, high-velocity systems,
install an air damper near the end of the
interconnecting duct, just prior to the
transition to the airflow measuring apparatus
of section 2.6. To minimize air leakage,
adjust this damper such that the pressure in
the receiving chamber of the airflow
measuring apparatus is no more than 0.5 inch
of water higher than the surrounding test
room ambient. If applicable, in lieu of
installing a separate damper, use the outlet
air damper box of sections 2.5 and 2.5.4.1 if
it allows variable positioning. Also apply
these steps to any conventional indoor
blower unit that creates a static pressure
within the receiving chamber of the airflow
measuring apparatus that exceeds the test
room ambient pressure by more than 0.5
inches of water column.
2.5.5 Dry bulb temperature measurement.
a. Measure dry bulb temperatures as
specified in sections 4, 5.3, 6, 7.2, and 7.3 of
ASHRAE Standard 41.1–2013 (incorporated
by reference, see § 430.3).
b. Distribute the sensors of a dry-bulb
temperature grid over the entire flow area.
The required minimum is 9 sensors per grid.
2.5.6 Water vapor content measurement.
Determine water vapor content by
measuring dry-bulb temperature combined
with the air wet-bulb temperature, dew point
temperature, or relative humidity. If used,
construct and apply wet-bulb temperature
sensors as specified in sections 4, 5, 6, 7.2,
7.3, 7.4, and 7.5 of ASHRAE Standard 41.6–
2014 (incorporated by reference, see § 430.3).
The temperature sensor (wick removed) must
be accurate to within ±0.2 °F. If used, apply
dew point hygrometers as specified in
sections 4, 5, 6, and 7.1 of ASHRAE Standard
41.6–2014. The dew point hygrometers must
be accurate to within ±0.4 °F when operated
at conditions that result in the evaluation of
dew points above 35 °F. If used, a relative
humidity (RH) meter must be accurate to
within ±0.7% RH. Other means to determine
the psychrometric state of air may be used as
long as the measurement accuracy is
equivalent to or better than the accuracy
achieved from using a wet-bulb temperature
sensor that meets the above specifications.
2.5.7 Air damper box performance
requirements.
If used (see section 2.5), the air damper
box(es) must be capable of being completely
opened or completely closed within 10
seconds for each action.
2.6 Airflow measuring apparatus.
a. Fabricate and operate an Air Flow
Measuring Apparatus as specified in section
6.2 and 6.3 of ASHRAE Standard 37–2009.
Refer to Figure 12 of ASHRAE Standard 51–
07/AMCA Standard 210–07 or Figure 14 of
ASHRAE Standard 41.2–87 (RA 92)
(incorporated by reference, see § 430.3) for
guidance on placing the static pressure taps
and positioning the diffusion baffle (settling
means) relative to the chamber inlet. When
measuring the static pressure difference
across nozzles and/or velocity pressure at
nozzle throats using electronic pressure
transducers and a data acquisition system, if
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high frequency fluctuations cause
measurement variations to exceed the test
tolerance limits specified in section 9.2 and
Table 2 of ASHRAE Standard 37–2009,
dampen the measurement system such that
the time constant associated with response to
a step change in measurement (time for the
response to change 63% of the way from the
initial output to the final output) is no longer
than five seconds.
b. Connect the airflow measuring apparatus
to the interconnecting duct section described
in section 2.5.4. See sections 6.1.1, 6.1.2, and
6.1.4, and Figures 1, 2, and 4 of ASHRAE
Standard 37–2009; and Figures D1, D2, and
D4 of AHRI 210/240–2008 (incorporated by
reference, see § 430.3) with Addendum 1 and
2 for illustrative examples of how the test
apparatus may be applied within a complete
laboratory set-up. Instead of following one of
these examples, an alternative set-up may be
used to handle the air leaving the airflow
measuring apparatus and to supply properly
conditioned air to the test unit’s inlet. The
alternative set-up, however, must not
interfere with the prescribed means for
measuring airflow rate, inlet and outlet air
temperatures, inlet and outlet water vapor
contents, and external static pressures, nor
create abnormal conditions surrounding the
test unit. (Note: Do not use an enclosure as
described in section 6.1.3 of ASHRAE
Standard 37–2009 when testing triple-split
units.)
2.7 Electrical voltage supply.
Perform all tests at the voltage specified in
section 6.1.3.2 of AHRI 210/240–2008 with
Addendum 1 and 2 for ‘‘Standard Rating
Tests.’’ If the voltage on the nameplate of
indoor and outdoor units differs, the voltage
supply on the outdoor unit shall be selected
for testing. Measure the supply voltage at the
terminals on the test unit using a volt meter
that provides a reading that is accurate to
within ±1.0 percent of the measured quantity.
2.8 Electrical power and energy
measurements.
a. Use an integrating power (watt-hour)
measuring system to determine the electrical
energy or average electrical power supplied
to all components of the air conditioner or
heat pump (including auxiliary components
such as controls, transformers, crankcase
heater, integral condensate pump on nonducted indoor units, etc.). The watt-hour
measuring system must give readings that are
accurate to within ±0.5 percent. For cyclic
tests, this accuracy is required during both
the ON and OFF cycles. Use either two
different scales on the same watt-hour meter
or two separate watt-hour meters. Activate
the scale or meter having the lower power
rating within 15 seconds after beginning an
OFF cycle. Activate the scale or meter having
the higher power rating active within 15
seconds prior to beginning an ON cycle. For
ducted units tested with a fan installed, the
ON cycle lasts from compressor ON to indoor
blower OFF. For ducted units tested without
an indoor blower installed, the ON cycle lasts
from compressor ON to compressor OFF. For
non-ducted units, the ON cycle lasts from
indoor blower ON to indoor blower OFF.
When testing air conditioners and heat
pumps having a variable-speed compressor,
avoid using an induction watt/watt-hour
meter.
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b. When performing section 3.5 and/or 3.8
cyclic tests on non-ducted units, provide
instrumentation to determine the average
electrical power consumption of the indoor
blower motor to within ±1.0 percent. If
required according to sections 3.3, 3.4, 3.7,
3.9.1, and/or 3.10, this same instrumentation
requirement applies when testing air
conditioners and heat pumps having a
variable-speed constant-air-volume-rate
indoor blower or a variable-speed, variableair-volume-rate indoor blower.
2.9 Time measurements.
Make elapsed time measurements using an
instrument that yields readings accurate to
within ±0.2 percent.
2.10 Test apparatus for the secondary
space conditioning capacity measurement.
For all tests, use the Indoor Air Enthalpy
Method to measure the unit’s capacity. This
method uses the test set-up specified in
sections 2.4 to 2.6. In addition, for all steadystate tests, conduct a second, independent
measurement of capacity as described in
section 3.1.1. For split systems, use one of
the following secondary measurement
methods: Outdoor Air Enthalpy Method,
Compressor Calibration Method, or
Refrigerant Enthalpy Method. For singlepackage units, use either the Outdoor Air
Enthalpy Method or the Compressor
Calibration Method as the secondary
measurement.
2.10.1 Outdoor Air Enthalpy Method.
a. To make a secondary measurement of
indoor space conditioning capacity using the
Outdoor Air Enthalpy Method, do the
following:
(1) Measure the electrical power
consumption of the test unit;
(2) Measure the air-side capacity at the
outdoor coil; and
(3) Apply a heat balance on the refrigerant
cycle.
b. The test apparatus required for the
Outdoor Air Enthalpy Method is a subset of
the apparatus used for the Indoor Air
Enthalpy Method. Required apparatus
includes the following:
(1) On the outlet side, an outlet plenum
containing static pressure taps (sections 2.4,
2.4.1, and 2.5.3),
(2) An airflow measuring apparatus
(section 2.6),
(3) A duct section that connects these two
components and itself contains the
instrumentation for measuring the dry-bulb
temperature and water vapor content of the
air leaving the outdoor coil (sections 2.5.4,
2.5.5, and 2.5.6), and
(4) On the inlet side, a sampling device and
temperature grid (section 2.11b.).
c. During the preliminary tests described in
sections 3.11.1 and 3.11.1.1, measure the
evaporator and condenser temperatures or
pressures. On both the outdoor coil and the
indoor coil, solder a thermocouple onto a
return bend located at or near the midpoint
of each coil or at points not affected by vapor
superheat or liquid subcooling. Alternatively,
if the test unit is not sensitive to the
refrigerant charge, install pressure gages to
the access valves or to ports created from
tapping into the suction and discharge lines
according to sections 7.4.2 and 8.2.5 of
ASHRAE Standard 37–2009. Use this
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alternative approach when testing a unit
charged with a zeotropic refrigerant having a
temperature glide in excess of 1 °F at the
specified test conditions.
2.10.2 Compressor Calibration Method.
Measure refrigerant pressures and
temperatures to determine the evaporator
superheat and the enthalpy of the refrigerant
that enters and exits the indoor coil.
Determine refrigerant flow rate or, when the
superheat of the refrigerant leaving the
evaporator is less than 5 °F, total capacity
from separate calibration tests conducted
under identical operating conditions. When
using this method, install instrumentation,
measure refrigerant properties, and adjust the
refrigerant charge according to section 7.4.2
and 8.2.5 of ASHRAE Standard 37–2009
(incorporated by reference, see § 430.3). Use
refrigerant temperature and pressure
measuring instruments that meet the
specifications given in sections 5.1.1 and 5.2
of ASHRAE Standard 37–2009.
2.10.3 Refrigerant Enthalpy Method.
For this method, calculate space
conditioning capacity by determining the
refrigerant enthalpy change for the indoor
coil and directly measuring the refrigerant
flow rate. Use section 7.5.2 of ASHRAE
Standard 37–2009 for the requirements for
this method, including the additional
instrumentation requirements, and
information on placing the flow meter and a
sight glass. Use refrigerant temperature,
pressure, and flow measuring instruments
that meet the specifications given in sections
5.1.1, 5.2, and 5.5.1 of ASHRAE Standard 37–
2009. Refrigerant flow measurement
device(s), if used, must be elevated at least
two feet from the test chamber floor or placed
upon insulating material having a total
thermal resistance of at least R–12 and
extending at least one foot laterally beyond
each side of the device(s)’ exposed surfaces,
unless the device(s) are elevated at least two
feet from the floor.
2.11 Measurement of test room ambient
conditions.
Follow instructions for measurement of
test room ambient conditions as described in
AHRI 210/240-Draft, appendix E, section E4,
(incorporated by reference, see § 430.3)
unless otherwise instructed in this section.
a. If using a test set-up where air is ducted
directly from the conditioning apparatus to
the indoor coil inlet (see Figure 2, Loop AirEnthalpy Test Method Arrangement, of
ASHRAE Standard 37–2009), add
instrumentation to permit measurement of
the indoor test room dry-bulb temperature.
b. For the outdoor side, install a grid of
evenly-distributed sensors on every airpermitting face on the inlet of the outdoor
unit, such that each measurement represents
an air-inlet area of no more than one square
foot. This grid must be constructed and
applied as per section 5.3 of ASHRAE
Standard 41.1–2013 (incorporated by
reference, see § 430.3). The maximum and
minimum temperatures measured by these
sensors may differ by no more than 1.5 °F—
otherwise adjustments to the test room must
be made to improve temperature uniformity.
The outdoor conditions shall be verified with
the air collected by air sampling device. Air
collected by an air sampling device at the air
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inlet of the outdoor unit for transfer to
sensors for measurement of temperature and/
or humidity shall be protected from
temperature change as follows: Any surface
of the air conveying tubing in contact with
surrounding air at a different temperature
than the sampled air shall be insulated with
thermal insulation with a nominal thermal
resistance (R-value) of at least 19 hr · ft2
· °F/Btu, no part of the air sampling device
or the tubing conducting the sampled air to
the sensors shall be within two inches of the
test chamber floor, and pairs of
measurements (e.g. dry bulb temperature and
wet bulb temperature) used to determine
water vapor content of sampled air shall be
measured in the same location. Take steps
(e.g., add or re-position a lab circulating fan),
as needed, to maximize temperature
uniformity within the outdoor test room.
However, ensure that any fan used for this
purpose does not cause air velocities in the
vicinity of the test unit to exceed 500 feet per
minute.
c. Measure dry bulb temperatures as
specified in sections 4, 5, 7.2, 6, and 7.3 of
ASHRAE Standard 41.1–2013. Measure water
vapor content as stated above in section
2.5.6.
2.12 Measurement of indoor blower
speed.
When required, measure fan speed using a
revolution counter, tachometer, or
stroboscope that gives readings accurate to
within ±1.0 percent.
2.13 Measurement of barometric pressure.
Determine the average barometric pressure
during each test. Use an instrument that
meets the requirements specified in section
5.2 of ASHRAE Standard 37–2009.
3. Testing Procedures.
3.1 General Requirements.
If, during the testing process, an equipment
set-up adjustment is made that would have
altered the performance of the unit during
any already completed test, then repeat all
tests affected by the adjustment. For cyclic
tests, instead of maintaining an air volume
rate, for each airflow nozzle, maintain the
static pressure difference or velocity pressure
during an ON period at the same pressure
difference or velocity pressure as measured
during the steady-state test conducted at the
same test conditions.
Use the testing procedures in this section
to collect the data used for calculating
(1) Performance metrics for central air
conditioners and heat pumps during the
cooling season;
(2) Performance metrics for heat pumps
during the heating season; and
(3) Power consumption metric(s) for
central air conditioners and heat pumps
during the off mode season(s).
3.1.1 Primary and secondary test
methods.
For all tests, use the Indoor Air Enthalpy
Method test apparatus to determine the unit’s
space conditioning capacity. The procedure
and data collected, however, differ slightly
depending upon whether the test is a steadystate test, a cyclic test, or a Frost
Accumulation test. The following sections
described these differences. For all steadystate tests (i.e., the A, A2, A1, B, B2, B1, C,
C1, EV, F1, G1, H01, H1, H12, H11, HIN, H3,
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H32, and H31 Tests), in addition, use one of
the acceptable secondary methods specified
in section 2.10 to determine indoor space
conditioning capacity. Calculate this
secondary check of capacity according to
section 3.11. The two capacity measurements
must agree to within 6 percent to constitute
a valid test. For this capacity comparison, use
the Indoor Air Enthalpy Method capacity that
is calculated in section 7.3 of ASHRAE
Standard 37–2009 (and, if testing a coil-only
system, do not make the after-test fan heat
adjustments described in section 3.3, 3.4, 3.7,
and 3.10 of this appendix). However, include
the appropriate section 3.3 to 3.5 and 3.7 to
3.10 fan heat adjustments within the Indoor
Air Enthalpy Method capacities used for the
section 4 seasonal calculations.
3.1.2 Manufacturer-provided equipment
overrides.
Where needed, the manufacturer must
provide a means for overriding the controls
of the test unit so that the compressor(s)
operates at the specified speed or capacity
and the indoor blower operates at the
specified speed or delivers the specified air
volume rate.
3.1.3 Airflow through the outdoor coil.
For all tests, meet the requirements given
in section 6.1.3.4 of AHRI 210/240–2008
(incorporated by reference, see § 430.3) with
Addendum 1 and 2 when obtaining the
airflow through the outdoor coil.
3.1.3.1 Double-ducted.
For products intended to be installed with
the outdoor airflow ducted, the unit shall be
installed with outdoor coil ductwork
installed per manufacturer installation
instructions and shall operate between 0.10
and 0.15 in H2O external static pressure.
External static pressure measurements shall
be made in accordance with ASHRAE
Standard 37–2009 Section 6.4 and 6.5.
3.1.4 Airflow through the indoor coil.
Airflow setting(s) shall be determined
before testing begins. Unless otherwise
specified within this or its subsections, no
changes shall be made to the airflow
setting(s) after initiation of testing.
3.1.4.1 Cooling Full-load Air Volume
Rate.
3.1.4.1.1 Cooling Full-Load Air Volume
Rate for Ducted Units.
The manufacturer must specify the cooling
full-load air volume rate and the instructions
for setting fan speed or controls. Adjust the
cooling full-load air volume rate if needed to
satisfy the additional requirements of this
section. First, when conducting the A or A2
Test (exclusively), the measured air volume
rate, when divided by the measured indoor
air-side total cooling capacity must not
exceed 37.5 cubic feet per minute of standard
air (scfm) per 1000 Btu/h. If this ratio is
exceeded, reduce the air volume rate until
this ratio is equaled. Use this reduced air
volume rate for all tests that call for using the
Cooling Full-load Air Volume Rate. Pressure
requirements are as follows:
a. For all ducted units tested with an
indoor blower installed, except those having
a constant-air-volume-rate indoor blower:
1. Achieve the Cooling Full-load Air
Volume Rate, determined in accordance with
the previous paragraph;
2. Measure the external static pressure;
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3. If this pressure is equal to or greater than
the applicable minimum external static
pressure cited in Table 3, the pressure
requirement is satisfied. Use the current air
volume rate for all tests that require the
Cooling Full-load Air Volume Rate.
4. If the Table 3 minimum is not equaled
or exceeded,
4a. reduce the air volume rate and increase
the external static pressure by adjusting the
exhaust fan of the airflow measuring
apparatus until the applicable Table 3
minimum is equaled or
4b. until the measured air volume rate
equals 90 percent of the air volume rate from
step 1, whichever occurs first.
5. If the conditions of step 4a occur first,
the pressure requirement is satisfied. Use the
step 4a reduced air volume rate for all tests
that require the Cooling Full-load Air
Volume Rate.
6. If the conditions of step 4b occur first,
make an incremental change to the set-up of
the indoor blower (e.g., next highest fan
motor pin setting, next highest fan motor
speed) and repeat the evaluation process
beginning at above step 1. If the indoor
blower set-up cannot be further changed,
reduce the air volume rate and increase the
external static pressure by adjusting the
exhaust fan of the airflow measuring
apparatus until the applicable Table 3
minimum is equaled. Use this reduced air
volume rate for all tests that require the
Cooling Full-load Air Volume Rate.
b. For ducted units that are tested with a
constant-air-volume-rate indoor blower
installed. For all tests that specify the
Cooling Full-load Air Volume Rate, obtain an
external static pressure as close to (but not
less than) the applicable Table 3 value that
does not cause automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined as follows, greater than 10
percent.
Where,
Qmax = maximum measured airflow value
Qmin = minimum measured airflow value
QVar = airflow variance, percent
Additional test steps as described in
section 3.3.(e) of this appendix are required
if the measured external static pressure
exceeds the target value by more than 0.03
inches of water.
c. For ducted units that are tested without
an indoor blower installed. For the A or A2
Test, (exclusively), the pressure drop across
the indoor coil assembly must not exceed
0.30 inches of water. If this pressure drop is
exceeded, reduce the air volume rate until
the measured pressure drop equals the
specified maximum. Use this reduced air
volume rate for all tests that require the
Cooling Full-load Air Volume Rate.
TABLE 3—MINIMUM EXTERNAL STATIC PRESSURE FOR DUCTED SYSTEMS TESTED WITH AN INDOOR BLOWER INSTALLED
Minimum external static pressure 3
(Inches of water)
Rated Cooling 1 or heating 2 capacity
(Btu/h)
Short ducted
systems 6
≤28,800 ........................................................................................................................................
≥29,000 and ≤42,500 ...................................................................................................................
≥43,000 ........................................................................................................................................
0.03
0.05
0.07
Small-duct,
high-velocity
systems 4 5
1.10
1.15
1.20
All other
systems
0.45
0.50
0.55
d. For ducted systems having multiple
indoor blowers within a single indoor
section, obtain the full-load air volume rate
with all blowers operating unless prevented
by the controls of the unit. In such cases, turn
on the maximum number of blowers
permitted by the unit’s controls. Where more
than one option exists for meeting this ‘‘on’’
blower requirement, which blower(s) are
turned on must match that specified by the
manufacturer in the installation manuals
included with the unit. Conduct section
3.1.4.1.1 setup steps for each blower
separately. If two or more indoor blowers are
connected to a common duct as per section
2.4.1, either turn off the other indoor blowers
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connected to the same common duct or
temporarily divert their air volume to the test
room when confirming or adjusting the setup
configuration of individual blowers. If the
indoor blowers are all the same size or
model, the target air volume rate for each
blower plenum equals the full-load air
volume rate divided by the number of ‘‘on’’
blowers. If different size blowers are used
within the indoor section, the allocation of
the system’s full-load air volume rate
assigned to each ‘‘on’’ blower must match
that specified by the manufacturer in the
installation manuals included with the unit.
3.1.4.1.2 Cooling Full-load Air Volume
Rate for Non-ducted Units.
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For non-ducted units, the Cooling Fullload Air Volume Rate is the air volume rate
that results during each test when the unit is
operated at an external static pressure of zero
inches of water.
3.1.4.2 Cooling Minimum Air Volume
Rate.
The manufacturer must specify the cooling
minimum air volume rate and the
instructions for setting fan speed or controls.
The target external static pressure, DPst_i, for
any test ‘‘i’’ with a specified air volume rate
not equal to the cooling full-load air volume
rate is determined as follows.
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1 For air conditioners and heat pumps, the value cited by the manufacturer in published literature for the unit’s capacity when operated at the A
or A2 Test conditions.
2 For heating-only heat pumps, the value the manufacturer cites in published literature for the unit’s capacity when operated at the H1 or H1
2
Test conditions.
3 For ducted units tested without an air filter installed, increase the applicable tabular value by 0.08 inches of water. For ducted units for which
the indoor blower installed for testing is the fan of a condensing gas furnace, decrease the applicable tabular value by 0.10 inches of water
(make both adjustments if they both apply). If the adjusted value is less than zero, readjust it to zero.
4 See section 1.2, Definitions, to determine if the equipment qualifies as a small-duct, high-velocity system.
5 If a closed-loop, air-enthalpy test apparatus is used on the indoor side, limit the resistance to airflow on the inlet side of the indoor blower coil
to a maximum value of 0.1 inch of water. Impose the balance of the airflow resistance on the outlet side of the indoor blower.
6 See section 1.2. Definitions.
Where:
DPst_i = target minimum external static
pressure for test i;
DPst_full = minimum external static pressure
for test A or A2 (Table 3);
Qi = air volume rate for test i; and
Qfull = cooling full-load air volume rate as
measured after setting and/or adjustment
as described in section 3.1.4.1.1.
a. For ducted units tested with an indoor
blower installed that is not a constant-airvolume indoor blower, adjust for external
static pressure as follows.
1. Achieve the manufacturer-specified
cooling minimum air volume rate;
2. Measure the external static pressure;
3. If this pressure is equal to or greater than
the target minimum external static pressure
calculated as described above, use the
current air volume rate for all tests that
require the cooling minimum air volume rate.
4. If the target minimum is not equaled or
exceeded,
4a. reduce the air volume rate and increase
the external static pressure by adjusting the
exhaust fan of the airflow measuring
apparatus until the applicable target
minimum is equaled or
4b. until the measured air volume rate
equals 90 percent of the air volume rate from
step 1, whichever occurs first.
5. If the conditions of step 4a occur first,
use the step 4a reduced air volume rate for
all tests that require the cooling minimum air
volume rate.
6. If the conditions of step 4b occur first,
make an incremental change to the set-up of
the indoor fan (e.g., next highest fan motor
pin setting, next highest fan motor speed)
and repeat the evaluation process beginning
at above step 1. If the indoor fan set-up
cannot be further changed, reduce the air
volume rate and increase the external static
pressure by adjusting the exhaust fan of the
airflow measuring apparatus until the
applicable target minimum is equaled. Use
this reduced air volume rate for all tests that
require the cooling minimum air volume rate.
b. For ducted units with constant-airvolume indoor blowers, conduct all tests that
specify the cooling minimum air volume
rate—(i.e., the A1, B1, C1, F1, and G1 Tests)—
at an external static pressure that does not
cause an automatic shutdown of the indoor
blower or air volume rate variation QVar,
defined in section 3.1.4.1.1.b, greater than 10
percent, while being as close to, but not less
than the target minimum external static
pressure. Additional test steps as described
in section 3.3(e) of this appendix are required
if the measured external static pressure
exceeds the target value by more than 0.03
inches of water.
c. For ducted two-capacity units that are
tested without an indoor blower installed,
the Cooling Minimum Air Volume Rate is the
higher of (1) the rate specified by the
installation instructions included with the
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unit by the manufacturer or (2) 75 percent of
the Cooling Full-load Air Volume Rate.
During the laboratory tests on a coil-only
(fanless) unit, obtain this Cooling Minimum
Air Volume Rate regardless of the pressure
drop across the indoor coil assembly.
d. For non-ducted units, the Cooling
Minimum Air Volume Rate is the air volume
rate that results during each test when the
unit operates at an external static pressure of
zero inches of water and at the indoor fan
setting used at low compressor capacity (twocapacity system) or minimum compressor
speed (variable-speed system). For units
having a single-speed compressor and a
variable-speed variable-air-volume-rate
indoor fan, use the lowest fan setting allowed
for cooling.
e. For ducted systems having multiple
indoor blowers within a single indoor
section, operate the indoor blowers such that
the lowest air volume rate allowed by the
unit’s controls is obtained when operating
the lone single-speed compressor or when
operating at low compressor capacity while
meeting the requirements of section 2.2.3.2
for the minimum number of blowers that
must be turned off. Adjust for external static
pressure and if necessary adjust air volume
rates as described in section 3.1.4.2.a if the
indoor fan is not a constant-air-volume
indoor fan or as described in section 3.1.4.2.b
if the indoor fan is a constant-air-volume
indoor fan. The sum of the individual ‘‘on’’
blowers’ air volume rates is the cooling
minimum air volume rate for the system.
3.1.4.3 Cooling Intermediate Air Volume
Rate.
The manufacturer must specify the cooling
intermediate air volume rate and the
instructions for setting fan speed or controls.
Calculate target minimum external static
pressure as described in section 3.1.4.2.
a. For ducted units tested with an indoor
blower, installed that is not a constant-airvolume indoor blower, adjust for external
static pressure as described in section
3.1.4.2.a for cooling minimum air volume
rate.
b. For ducted units tested with constantair-volume indoor blowers installed, conduct
the EV Test at an external static pressure that
does not cause an automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but
not less than the target minimum external
static pressure. Additional test steps as
described in section 3.3(e) of this appendix
are required if the measured external static
pressure exceeds the target value by more
than 0.03 inches of water.
c. For non-ducted units, the Cooling
Intermediate Air Volume Rate is the air
volume rate that results when the unit
operates at an external static pressure of zero
inches of water and at the fan speed selected
by the controls of the unit for the EV Test
conditions.
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3.1.4.4 Heating Full-load Air Volume
Rate.
3.1.4.4.1 Ducted heat pumps where the
Heating and Cooling Full-load Air Volume
Rates are the same.
a. Use the Cooling Full-load Air Volume
Rate as the Heating Full-load Air Volume
Rate for:
1. Ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower that operates at the
same airflow-control setting during both the
A (or A2) and the H1 (or H12) Tests;
2. Ducted heat pumps tested with constantair-flow indoor blowers installed that provide
the same air flow for the A (or A2) and the
H1 (or H12) Tests; and
3. Ducted heat pumps that are tested
without an indoor blower installed (except
two-capacity northern heat pumps that are
tested only at low capacity cooling—see
3.1.4.4.2).
b. For heat pumps that meet the above
criteria ‘‘1’’ and ‘‘3,’’ no minimum
requirements apply to the measured external
or internal, respectively, static pressure. For
heat pumps that meet the above criterion
‘‘2,’’ test at an external static pressure that
does not cause an automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but
not less than, the same Table 3 minimum
external static pressure as was specified for
the A (or A2) cooling mode test. Additional
test steps as described in section 3.9.1(c) of
this appendix are required if the measured
external static pressure exceeds the target
value by more than 0.03 inches of water.
3.1.4.4.2 Ducted heat pumps where the
Heating and Cooling Full-load Air Volume
Rates are different due to indoor blower
operation.
The manufacturer must specify the heating
full-load air volume rate and the instructions
for setting fan speed or controls. Calculate
target minimum external static pressure as
described in section 3.1.4.2.
a. For ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower, adjust for external
static pressure as described in section
3.1.4.2.a for cooling minimum air volume
rate.
b. For ducted heat pumps tested with
constant-air-volume indoor blowers installed,
conduct all tests that specify the heating fullload air volume rate at an external static
pressure that does not cause an automatic
shutdown of the indoor blower or air volume
rate variation QVar, defined in section
3.1.4.1.1.b, greater than 10 percent, while
being as close to, but not less than the target
minimum external static pressure. Additional
test steps as described in section 3.9.1(c) of
this appendix are required if the measured
external static pressure exceeds the target
value by more than 0.03 inches of water.
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c. When testing ducted, two-capacity
northern heat pumps (see section 1.2,
Definitions), use the appropriate approach of
the above two cases for units that are tested
with an indoor blower installed. For coilonly northern heat pumps, the Heating Fullload Air Volume Rate is the lesser of the rate
specified by the manufacturer in the
installation instructions included with the
unit or 133 percent of the Cooling Full-load
Air Volume Rate. For this latter case, obtain
the Heating Full-load Air Volume Rate
regardless of the pressure drop across the
indoor coil assembly.
d. For ducted systems having multiple
indoor blowers within a single indoor
section, obtain the heating full-load air
volume rate using the same ‘‘on’’ blowers as
used for the cooling full-load air volume rate.
For systems where individual blowers
regulate the speed (as opposed to the cfm) of
the indoor blower, use the first section
3.1.4.2 equation for each blower individually.
Sum the individual blower air volume rates
to obtain the heating full-load air volume rate
for the system.
3.1.4.4.3 Ducted heating-only heat
pumps.
The manufacturer must specify the Heating
Full-load Air Volume Rate.
a. For all ducted heating-only heat pumps
tested with an indoor blower installed,
except those having a constant-air-volumerate indoor blower. Conduct the following
steps only during the first test, the H1 or H12
Test.
1. Achieve the Heating Full-load Air
Volume Rate.
2. Measure the external static pressure.
3. If this pressure is equal to or greater than
the Table 3 minimum external static pressure
that applies given the heating-only heat
pump’s rated heating capacity, use the
current air volume rate for all tests that
require the Heating Full-load Air Volume
Rate.
4. If the Table 3 minimum is not equaled
or exceeded,
4a. reduce the air volume rate and increase
the external static pressure by adjusting the
exhaust fan of the airflow measuring
apparatus until the applicable Table 3
minimum is equaled or
4b. until the measured air volume rate
equals 90 percent of the manufacturerspecified Full-load Air Volume Rate,
whichever occurs first.
5. If the conditions of step 4a occurs first,
use the step 4a reduced air volume rate for
all tests that require the Heating Full-load Air
Volume Rate.
6. If the conditions of step 4b occur first,
make an incremental change to the set-up of
the indoor blower (e.g., next highest fan
motor pin setting, next highest fan motor
speed) and repeat the evaluation process
beginning at above step 1. If the indoor
blower set-up cannot be further changed,
reduce the air volume rate until the
applicable Table 3 minimum is equaled. Use
this reduced air volume rate for all tests that
require the Heating Full-load Air Volume
Rate.
b. For ducted heating-only heat pumps that
are tested with a constant-air-volume-rate
indoor blower installed. For all tests that
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specify the Heating Full-load Air Volume
Rate, obtain an external static pressure that
does not cause an automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but
not less than, the applicable Table 3
minimum. Additional test steps as described
in section 3.9.1(c) of this appendix are
required if the measured external static
pressure exceeds the target value by more
than 0.03 inches of water.
c. For ducted heating-only heat pumps that
are tested without an indoor blower installed.
For the H1 or H12 Test, (exclusively), the
pressure drop across the indoor coil assembly
must not exceed 0.30 inches of water. If this
pressure drop is exceeded, reduce the air
volume rate until the measured pressure drop
equals the specified maximum. Use this
reduced air volume rate for all tests that
require the Heating Full-load Air Volume
Rate.
3.1.4.4.4 Non-ducted heat pumps,
including non-ducted heating-only heat
pumps.
For non-ducted heat pumps, the Heating
Full-load Air Volume Rate is the air volume
rate that results during each test when the
unit operates at an external static pressure of
zero inches of water.
3.1.4.5 Heating Minimum Air Volume
Rate.
3.1.4.5.1 Ducted heat pumps where the
Heating and Cooling Minimum Air Volume
Rates are the same.
a. Use the Cooling Minimum Air Volume
Rate as the Heating Minimum Air Volume
Rate for:
1. Ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower that operates at the
same airflow-control setting during both the
A1 and the H11 tests; 2. Ducted heat pumps
tested with constant-air-flow indoor blowers
installed that provide the same air flow for
the A1 and the H11 Tests; and
3. Ducted heat pumps that are tested
without an indoor blower installed (except
two-capacity northern heat pumps that are
tested only at low capacity cooling—see
3.1.4.4.2).
b. For heat pumps that meet the above
criteria ‘‘1’’ and ‘‘3,’’ no minimum
requirements apply to the measured external
or internal, respectively, static pressure. For
heat pumps that meet the above criterion
‘‘2,’’ test at an external static pressure that
does not cause an automatic shutdown of the
indoor blower or air volume rate variation
QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but
not less than, the same target minimum
external static pressure as was specified for
the A1 cooling mode test. Additional test
steps as described in section 3.9.1(c) of this
appendix are required if the measured
external static pressure exceeds the target
value by more than 0.03 inches of water.
3.1.4.5.2 Ducted heat pumps where the
Heating and Cooling Minimum Air Volume
Rates are different due to indoor blower
operation.
The manufacturer must specify the heating
minimum volume rate and the instructions
for setting fan speed or controls. Calculate
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target minimum external static pressure as
described in section 3.1.4.2.
a. For ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower, adjust for external
static pressure as described in section
3.1.4.2.a for cooling minimum air volume
rate.
b. For ducted heat pumps tested with
constant-air-volume indoor blowers installed,
conduct all tests that specify the Heating
Minimum Air Volume Rate—(i.e., the H01,
H11, H21, and H31 Tests)—at an external
static pressure that does not cause an
automatic shutdown of the indoor blower
while being as close to, but not less thanor
air volume rate variation QVar, defined in
section 3.1.4.1.1.b, greater than 10 percent,
while being as close to, but not less than the
target minimum external static pressure.
Additional test steps as described in section
3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the
target value by more than 0.03 inches of
water.
c. For ducted two-capacity northern heat
pumps that are tested with an indoor blower
installed, use the appropriate approach of the
above two cases.
d. For ducted two-capacity heat pumps
that are tested without an indoor blower
installed, use the Cooling Minimum Air
Volume Rate as the Heating Minimum Air
Volume Rate. For ducted two-capacity
northern heat pumps that are tested without
an indoor blower installed, use the Cooling
Full-load Air Volume Rate as the Heating
Minimum Air Volume Rate. For ducted twocapacity heating-only heat pumps that are
tested without an indoor blower installed,
the Heating Minimum Air Volume Rate is the
higher of the rate specified by the
manufacturer in the test setup instructions
included with the unit or 75 percent of the
Heating Full-load Air Volume Rate. During
the laboratory tests on a coil-only system,
obtain the Heating Minimum Air Volume
Rate without regard to the pressure drop
across the indoor coil assembly.
e. For non-ducted heat pumps, the Heating
Minimum Air Volume Rate is the air volume
rate that results during each test when the
unit operates at an external static pressure of
zero inches of water and at the indoor blower
setting used at low compressor capacity (twocapacity system) or minimum compressor
speed (variable-speed system). For units
having a single-speed compressor and a
variable-speed, variable-air-volume-rate
indoor blower, use the lowest fan setting
allowed for heating.
f. For ducted systems with multiple indoor
blowers within a single indoor section,
obtain the heating minimum air volume rate
using the same ‘‘on’’ blowers as used for the
cooling minimum air volume rate. For
systems where individual blowers regulate
the speed (as opposed to the cfm) of the
indoor blower, use the first section 3.1.4.5
equation for each blower individually. Sum
the individual blower air volume rates to
obtain the heating minimum air volume rate
for the system.
3.1.4.6 Heating Intermediate Air Volume
Rate.
The manufacturer must specify the heating
intermediate air volume rate and the
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If using a test set-up where air is ducted
directly from the air reconditioning
apparatus to the indoor coil inlet (see Figure
2, Loop Air-Enthalpy Test Method
Arrangement, of ASHRAE Standard 37–
2009), maintain the dry bulb temperature
within the test room within ±5.0 °F of the
applicable sections 3.2 and 3.6 dry bulb
temperature test condition for the air entering
the indoor unit. Dew point shall be within 2
°F of the required inlet conditions.
3.1.6 Air volume rate calculations.
For all steady-state tests and for Frost
Accumulation (H2, H21, H22, H2V) tests,
calculate the air volume rate through the
indoor coil as specified in sections 7.7.2.1
and 7.7.2.2 of ASHRAE Standard 37–2009.
When using the Outdoor Air Enthalpy
Method, follow sections 7.7.2.1 and 7.7.2.2 to
calculate the air volume rate through the
outdoor coil. To express air volume rates in
terms of standard air, use:
vn′ = specific volume of air-water vapor
mixture at the nozzle, ft3 per lbm of the
air-water vapor mixture
Wn = humidity ratio at the nozzle, lbm of
water vapor per lbm of dry air
0.075 = the density associated with standard
(dry) air, (lbm/ft3)
vn = specific volume of the dry air portion
of the mixture evaluated at the dry-bulb
temperature, vapor content, and
barometric pressure existing at the
nozzle, ft3 per lbm of dry air.
3.1.7 Test sequence.
Manufacturers may optionally operate the
equipment under test for a ‘‘break-in’’ period,
not to exceed 20 hours, prior to conducting
the test method specified in this section. A
manufacturer who elects to use this optional
compressor break-in period in its
certification testing should record this
information (including the duration) in the
test data underlying the certified ratings that
are required to be maintained under 10 CFR
429.71. When testing a ducted unit (except if
a heating-only heat pump), conduct the A or
A2 Test first to establish the Cooling Fullload Air Volume Rate. For ducted heat
pumps where the Heating and Cooling Fullload Air Volume Rates are different, make the
first heating mode test one that requires the
Heating Full-load Air Volume Rate. For
ducted heating-only heat pumps, conduct the
H1 or H12 Test first to establish the Heating
Full-load Air Volume Rate. When conducting
an cyclic test, always conduct it immediately
after the steady-state test that requires the
same test conditions. For variable-speed
systems, the first test using the Cooling
Minimum Air Volume Rate should precede
the EV Test, and the first test using the
Heating Minimum Air Volume Rate must
precede the H2V Test. The test laboratory
makes all other decisions on the test
sequence.
3.1.8 Requirement for the air temperature
distribution leaving the indoor coil.
For at least the first cooling mode test and
the first heating mode test, monitor the
temperature distribution of the air leaving the
indoor coil using the grid of individual
sensors described in sections 2.5 and 2.5.4.
For the 30-minute data collection interval
used to determine capacity, the maximum
spread among the outlet dry bulb
temperatures from any data sampling must
not exceed 1.5 °F. Install the mixing devices
described in section 2.5.4.2 to minimize the
temperature spread.
3.1.9 Requirement for the air temperature
distribution entering the outdoor coil.
Monitor the temperatures of the air
entering the outdoor coil using the grid of
temperature sensors described in section
2.11. For the 30-minute data collection
interval used to determine capacity, the
maximum difference between dry bulb
temperatures measured at any of these
locations must not exceed 1.5 °F.
3.1.10 Control of auxiliary resistive
heating elements.
Except as noted, disable heat pump
resistance elements used for heating indoor
air at all times, including during defrost
cycles and if they are normally regulated by
a heat comfort controller. For heat pumps
equipped with a heat comfort controller,
enable the heat pump resistance elements
only during the below-described, short test.
For single-speed heat pumps covered under
section 3.6.1, the short test follows the H1 or,
if conducted, the H1C Test. For two-capacity
heat pumps and heat pumps covered under
section 3.6.2, the short test follows the H12
Test. Set the heat comfort controller to
provide the maximum supply air
temperature. With the heat pump operating
and while maintaining the Heating Full-load
Air Volume Rate, measure the temperature of
the air leaving the indoor-side beginning 5
minutes after activating the heat comfort
controller. Sample the outlet dry-bulb
temperature at regular intervals that span 5
minutes or less. Collect data for 10 minutes,
obtaining at least 3 samples. Calculate the
average outlet temperature over the 10minute interval, TCC.
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c. For non-ducted heat pumps, the Heating
Intermediate Air Volume Rate is the air
volume rate that results when the heat pump
operates at an external static pressure of zero
inches of water and at the fan speed selected
by the controls of the unit for the H2V Test
conditions.
3.1.4.7 Heating Nominal Air Volume
Rate.
The manufacturer must specify the heating
nominal air volume rate and the instructions
for setting fan speed or controls. Calculate
target minimum external static pressure as
described in section 3.1.4.2. Make
adjustments as described in section 3.14.6 for
heating intermediate air volume rate so that
the target minimum external static pressure
is met or exceeded.
3.1.5 Indoor test room requirement when
the air surrounding the indoor unit is not
supplied from the same source as the air
entering the indoor unit.
where,
Ô
Vs = air volume rate of standard (dry) air, (ft3/
min)da
Ô
Vmx = air volume rate of the air-water vapor
mixture, (ft3/min)mx
tkelley on DSK3SPTVN1PROD with PROPOSALS2
instructions for setting fan speed or controls.
Calculate target minimum external static
pressure as described in section 3.1.4.2.
a. For ducted heat pumps tested with an
indoor blower installed that is not a constantair-volume indoor blower, adjust for external
static pressure as described in section
3.1.4.2.a for cooling minimum air volume
rate.
b. For ducted heat pumps tested with
constant-air-volume indoor blowers installed,
conduct the H2V Test at an external static
pressure that does not cause an automatic
shutdown of the indoor blower or air volume
rate variation QVar, defined in section
3.1.4.1.1.b, greater than 10 percent, while
being as close to, but not less than the target
minimum external static pressure. Additional
test steps as described in section 3.9.1(c) of
this appendix are required if the measured
external static pressure exceeds the target
value by more than 0.03 inches of water.
69414
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
3.2 Cooling mode tests for different types
of air conditioners and heat pumps.
3.2.1 Tests for a unit having a singlespeed compressor, or a system comprised of
independently circuited single-speed
compressors, that is tested with a fixed-speed
indoor blower installed, with a constant-air-
volume-rate indoor blower installed, or with
no indoor blower installed.
Conduct two steady-state wet coil tests, the
A and B Tests. Use the two dry-coil tests, the
steady-state C Test and the cyclic D Test, to
determine the cooling mode cyclic
degradation coefficient, CDc. If testing
outdoor units of central air conditioners or
heat pumps that are not sold with indoor
units, assign CDc the default value of 0.2.
Table 4 specifies test conditions for these
four tests.
TABLE 4—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A FIXED-SPEED
INDOOR BLOWER, A CONSTANT AIR VOLUME RATE INDOOR BLOWER, OR NO INDOOR BLOWER
Air entering indoor unit
temperature (°F)
Test description
Dry bulb
A Test—required (steady, wet coil) ..
B Test—required (steady, wet coil) ..
C Test—required (steady, dry coil) ...
D Test—required (cyclic, dry coil) ....
Air entering outdoor unit
temperature (°F)
Wet bulb
80
80
80
80
Dry bulb
67
67
(3)
(3)
Cooling air volume rate
Wet bulb
95
82
82
82
1 75
Cooling full-load.2
Cooling full-load.2
Cooling full-load.2
(4).
1 65
........................
........................
1 The
specified test condition only applies if the unit rejects condensate to the outdoor coil.
in section 3.1.4.1.
3 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wetbulb temperature of 57 °F or less be used.)
4 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C Test.
2 Defined
3.2.2 Tests for a unit having a singlespeed compressor where the indoor section
uses a single variable-speed variable-airvolume rate indoor blower or multiple
blowers.
3.2.2.1 Indoor blower capacity
modulation that correlates with the outdoor
dry bulb temperature or systems with a single
indoor coil but multiple blowers.
Conduct four steady-state wet coil tests:
The A2, A1, B2, and B1 Tests. Use the two drycoil tests, the steady-state C1 Test and the
cyclic D1 Test, to determine the cooling mode
cyclic degradation coefficient, C.
3.2.2.2 Indoor blower capacity
modulation based on adjusting the sensible
to total (S/T) cooling capacity ratio.
The testing requirements are the same as
specified in section 3.2.1 and Table 4. Use a
Cooling Full-load Air Volume Rate that
represents a normal installation. If
performed, conduct the steady-state C Test
and the cyclic D Test with the unit operating
in the same S/T capacity control mode as
used for the B Test.
TABLE 5—COOLING MODE TEST CONDITIONS FOR UNITS WITH A SINGLE-SPEED COMPRESSOR THAT MEET THE SECTION
3.2.2.1 INDOOR UNIT REQUIREMENTS
Air entering indoor unit
temperature (°F)
Test description
Dry bulb
A2 Test—required (steady, wet coil) ........
A1 Test—required (steady, wet coil) ........
B2 Test—required (steady, wet coil) ........
B1 Test—required (steady, wet coil) ........
C1 Test4—required (steady, dry coil) .......
D1 Test4—required (cyclic, dry coil) .........
Air entering outdoor unit
temperature (°F)
Wet bulb
80
80
80
80
80
80
Dry bulb
67
67
67
67
(4)
(4)
Cooling air volume rate
Wet bulb
95
95
82
82
82
82
1 75
1 75
165
165
........................
(5)
Cooling
Cooling
Cooling
Cooling
Cooling
full-load.2
minimum.3
full-load.2
minimum.3
minimum.3
1 The
specified test condition only applies if the unit rejects condensate to the outdoor coil.
in section 3.1.4.1.
in section 3.1.4.2.
4 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wetbulb temperature of 57 °F or less be used.)
5 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C1 Test.
2 Defined
tkelley on DSK3SPTVN1PROD with PROPOSALS2
3 Defined
3.2.3 Tests for a unit having a twocapacity compressor. (see section 1.2,
Definitions)
a. Conduct four steady-state wet coil tests:
The A2, B2, B1, and F1 Tests. Use the two drycoil tests, the steady-state C1 Test and the
cyclic D1 Test, to determine the cooling-mode
cyclic-degradation coefficient, C. Table 6
specifies test conditions for these six tests.
b. For units having a variable speed indoor
blower that is modulated to adjust the
sensible to total (S/T) cooling capacity ratio,
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use Cooling Full-load and Cooling Minimum
Air Volume Rates that represent a normal
installation. Additionally, if conducting the
dry-coil tests, operate the unit in the same S/
T capacity control mode as used for the B1
Test.
c. Test two-capacity, northern heat pumps
(see section 1.2, Definitions) in the same way
as a single speed heat pump with the unit
operating exclusively at low compressor
capacity (see section 3.2.1 and Table 4).
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d. If a two-capacity air conditioner or heat
pump locks out low-capacity operation at
higher outdoor temperatures, then use the
two dry-coil tests, the steady-state C2 Test
and the cyclic D2 Test, to determine the
cooling-mode cyclic-degradation coefficient
that only applies to on/off cycling from high
capacity, C(k=2). The default COc(k=2) is the
same value as determined or assigned for the
low-capacity cyclic-degradation coefficient,
C [or equivalently, C(k=1)].
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69415
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
TABLE 6—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR
Air entering indoor unit
temperature (°F)
Air entering outdoor unit
temperature (°F)
Dry bulb
Dry bulb
Test description
A2 Test—required (steady, wet coil) .......
B2 Test—required (steady, wet coil) .......
B1 Test—required (steady, wet coil) .......
C2 Test—required (steady, dry-coil) .......
D2 Test—required (cyclic, dry-coil) .........
C1 Test—required (steady, dry-coil) .......
D1 Test—required (cyclic, dry-coil) .........
F1 Test—required (steady, wet coil) .......
Wet bulb
80
80
80
80
80
80
80
80
67
67
67
(4)
(4)
(4)
(4)
67
Compressor
capacity
Cooling air volume
rate
High .......................
High .......................
Low ........................
Cooling Full-Load.2
(5) ...........................
Cooling Minimum.3
(6) ...........................
Low ........................
Cooling Full-Load.2
Cooling Full-Load.2
Cooling Minimum.3
Wet bulb
1 75
95
82
82
82
82
82
82
67
1 65
1 65
High
High
Low
Low
1 53.5
Cooling Minimum.3
1 The
specified test condition only applies if the unit rejects condensate to the outdoor coil.
in section 3.1.4.1.
in section 3.1.4.2.
4 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air
wet-bulb temperature of 57 °F or less.
5 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the C2 Test.
6 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the C1 Test.
2 Defined
3 Defined
3.2.4 Tests for a unit having a variablespeed compressor.
a. Conduct five steady-state wet coil tests:
The A2, EV, B2, B1, and F1 Tests. Use the two
dry-coil tests, the steady-state G1 Test and the
cyclic I1 Test, to determine the cooling mode
cyclic degradation coefficient, CDc..-Table-7
specifies test conditions for these seven tests.
Determine the intermediate compressor
speed cited in Table 7 using:
where a tolerance of plus 5 percent or the
next higher inverter frequency step from that
calculated is allowed.
b. For units that modulate the indoor
blower speed to adjust the sensible to total
(S/T) cooling capacity ratio, use Cooling Fullload, Cooling Intermediate, and Cooling
Minimum Air Volume Rates that represent a
normal installation. Additionally, if
conducting the dry-coil tests, operate the unit
in the same S/T capacity control mode as
used for the F1 Test.
c. For multiple-split air conditioners and
heat pumps (except where noted), the
following procedures supersede the above
requirements: For all Table 7 tests specified
for a minimum compressor speed, at least
one indoor unit must be turned off. The
manufacturer shall designate the particular
indoor unit(s) that is turned off. The
manufacturer must also specify the
compressor speed used for the Table 7 EV
Test, a cooling-mode intermediate
compressor speed that falls within 1⁄4 and 3⁄4
of the difference between the maximum and
minimum cooling-mode speeds. The
manufacturer should prescribe an
intermediate speed that is expected to yield
the highest EER for the given EV Test
conditions and bracketed compressor speed
range. The manufacturer can designate that
one or more indoor units are turned off for
the EV Test.
TABLE 7—COOLING MODE TEST CONDITION FOR UNITS HAVING A VARIABLE-SPEED COMPRESSOR
Air entering indoor unit
temperature (°F)
Air entering outdoor unit
temperature (°F)
Dry bulb
Test description
Dry bulb
Wet bulb
Compressor speed
Cooling air volume
rate
Maximum ...............
Maximum ...............
Intermediate ...........
Cooling Full-Load.2
Cooling Full-Load.2
Cooling Intermediate.3
Cooling Minimum.4
Cooling Minimum.4
Wet bulb
A2 Test—required (steady, wet coil) .......
B2 Test—required (steady, wet coil) .......
EV Test—required (steady, wet coil) .......
80
80
80
67
67
67
B1 Test—required (steady, wet coil) .......
F1 Test—required (steady, wet coil) .......
G1 Test 5—required (steady, dry-coil) .....
I1 Test 5—required (cyclic, dry-coil) .........
80
80
80
80
67
67
(6)
(6)
82
67
67
67
1 75
95
82
87
1 65
1 69
1 65
1 53.5
Minimum
Minimum
Minimum ................
Minimum ................
Cooling Minimum.4.
(6).
1 The
specified test condition only applies if the unit rejects condensate to the outdoor coil.
in section 3.1.4.1.
3 Defined in section 3.1.4.3.
4 Defined in section 3.1.4.2.
5 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air
wet bulb temperature of 57 °F or less.
6 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the G1 Test.
3.2.5 Cooling mode tests for northern heat
pumps with triple-capacity compressors.
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for the cooling mode in the same way as
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specified in section 3.2.3 for units having a
two-capacity compressor.
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2 Defined
69416
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
3.2.6 Tests for an air conditioner or heat
pump having a single indoor unit having
multiple blowers and offering two stages of
compressor modulation.
Conduct the cooling mode tests specified
in section 3.2.3.
3.3 Test procedures for steady-state wet
coil cooling mode tests (the A, A2, A1, B, B2,
B1, EV, and F1 Tests).
a. For the pretest interval, operate the test
room reconditioning apparatus and the unit
to be tested until maintaining equilibrium
conditions for at least 30 minutes at the
specified section 3.2 test conditions. Use the
exhaust fan of the airflow measuring
apparatus and, if installed, the indoor blower
of the test unit to obtain and then maintain
the indoor air volume rate and/or external
static pressure specified for the particular
test. Continuously record (see section 1.2,
Definitions):
(1) The dry-bulb temperature of the air
entering the indoor coil,
(2) The water vapor content of the air
entering the indoor coil,
(3) The dry-bulb temperature of the air
entering the outdoor coil, and
(4) For the section 2.2.4 cases where its
control is required, the water vapor content
of the air entering the outdoor coil.
Refer to section 3.11 for additional
requirements that depend on the selected
secondary test method.
b. After satisfying the pretest equilibrium
requirements, make the measurements
specified in Table 3 of ASHRAE Standard
37–2009 (incorporated by reference, see
§ 430.3) for the Indoor Air Enthalpy method
and the user-selected secondary method.
Make said Table 3 measurements at equal
intervals that span 5 minutes or less.
Continue data sampling until reaching a 30minute period (e.g., four consecutive 10minute samples) where the test tolerances
specified in Table 8 are satisfied. For those
continuously recorded parameters, use the
entire data set from the 30-minute interval to
evaluate Table 8 compliance. Determine the
average electrical power consumption of the
air conditioner or heat pump over the same
30-minute interval.
c. Calculate indoor-side total cooling
capacity and sensible cooling capacity as
specified in sections 7.3.3.1 and 7.3.3.3 of
ASHRAE Standard 37–2009. Do not adjust
the parameters used in calculating capacity
for the permitted variations in test
conditions. Evaluate air enthalpies based on
the measured barometric pressure. Use the
values of the specific heat of air given in
section 7.3.3.1 for calculation of the sensible
cooling capacities. Assign the average total
space cooling capacity, average sensible
cooling capacity, and electrical power
consumption over the 30-minute data
˙
collection interval to the variables Qck(T),
˙
˙
Qsck(T) and Eck(T), respectively. For these
three variables, replace the ‘‘T’’ with the
nominal outdoor temperature at which the
test was conducted. The superscript k is used
only when testing multi-capacity units. Use
the superscript k=2 to denote a test with the
unit operating at high capacity or maximum
speed, k=1 to denote low capacity or
minimum speed, and k=v to denote the
intermediate speed.
d. For units tested without an indoor
˙
blower installed, decrease Qck(T) by
Ô
where Vs is the average measured indoor air
volume rate expressed in units of cubic feet
per minute of standard air (scfm).
TABLE 8—TEST OPERATING AND TEST CONDITION TOLERANCES FOR SECTION 3.3 STEADY-STATE WET COIL COOLING
MODE TESTS AND SECTION 3.4 DRY COIL COOLING MODE TESTS
Test operating
tolerance 1
Indoor dry-bulb, °F:
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
Indoor wet-bulb, °F:
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
Outdoor dry-bulb, °F:
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
Outdoor wet-bulb, °F:
Entering temperature ........................................................................................................................................
Leaving temperature .........................................................................................................................................
External resistance to airflow, inches of water ........................................................................................................
Electrical voltage, % of rdg. .....................................................................................................................................
Nozzle pressure drop, % of rdg. .............................................................................................................................
Test condition
tolerance 1
2.0
2.0
0.5
1.0
2 0.3
2 1.0
2.0
0.5
3 2.0
1.0
4 0.3
3 1.0
0.12
2.0
8.0
5 0.02
1.5
section 1.2, Definitions.
applies during wet coil tests; does not apply during steady-state, dry coil cooling mode tests.
applies when using the Outdoor Air Enthalpy Method.
4 Only applies during wet coil cooling mode tests where the unit rejects condensate to the outdoor coil.
5 Only applies when testing non-ducted units.
2 Only
3 Only
e. For air conditioners and heat pumps
having a constant-air-volume-rate indoor
blower, the five additional steps listed below
are required if the average of the measured
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external static pressures exceeds the
applicable sections 3.1.4 minimum (or target)
external static pressure (DPmin) by 0.03 inches
of water or more.
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1. Measure the average power consumption
˙
of the indoor blower motor (Efan,1) and record
the corresponding external static pressure
(DP1) during or immediately following the 30-
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Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69417
static pressure (DP2) by making
measurements over a 5-minute interval.
4. Approximate the average power
consumption of the indoor blower motor at
DPmin using linear extrapolation:
˙
a section 3.3 deviation, do not adjust Qss,dry
for duct losses (i.e., do not apply section
7.3.3.3 of ASHRAE Standard 37–2009). In
preparing for the section 3.5 cyclic tests,
record the average indoor-side air volume
Ô
rate, V, specific heat of the air, Cp,a
(expressed on dry air basis), specific volume
of the air at the nozzles, v′n, humidity ratio
at the nozzles, Wn, and either pressure
difference or velocity pressure for the flow
nozzles. For units having a variable-speed
indoor fan (that provides either a constant or
variable air volume rate) that will or may be
tested during the cyclic dry coil cooling
mode test with the indoor fan turned off (see
section 3.5), include the electrical power
used by the indoor fan motor among the
recorded parameters from the 30-minute test.
c. If the temperature sensors used to
provide the primary measurement of the
indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the
subsequent cyclic dry- coil test are different,
include measurements of the latter sensors
among the regularly sampled data. Beginning
at the start of the 30-minute data collection
period, measure and compute the indoor-side
air dry-bulb temperature difference using
both sets of instrumentation, DT (Set SS) and
DT (Set CYC), for each equally spaced data
sample. If using a consistent data sampling
rate that is less than 1 minute, calculate and
record minutely averages for the two
temperature differences. If using a consistent
sampling rate of one minute or more,
calculate and record the two temperature
differences from each data sample. After
having recorded the seventh (i=7) set of
temperature differences, calculate the
following ratio using the first seven sets of
values:
Each time a subsequent set of temperature
differences is recorded (if sampling more
frequently than every 5 minutes), calculate
FCD using the most recent seven sets of
values. Continue these calculations until the
30-minute period is completed or until a
value for FCD is calculated that falls outside
the allowable range of 0.94–1.06. If the latter
occurs, immediately suspend the test and
identify the cause for the disparity in the two
temperature difference measurements.
Recalibration of one or both sets of
instrumentation may be required. If all the
values for FCD are within the allowable range,
save the final value of the ratio from the 30minute test as FCD*. If the temperature
sensors used to provide the primary
measurement of the indoor-side dry bulb
temperature difference during the steadystate dry- coil test and the subsequent cyclic
dry-coil test are the same, set FCD*= 1.
3.5 Test procedures for the cyclic dry-coil
cooling-mode tests (the D, D1, D2, and I1
Tests).
a. After completing the steady-state drycoil test, remove the Outdoor Air Enthalpy
method test apparatus, if connected, and
begin manual OFF/ON cycling of the unit’s
compressor. The test set-up should otherwise
be identical to the set-up used during the
steady-state dry coil test. When testing heat
pumps, leave the reversing valve during the
compressor OFF cycles in the same position
as used for the compressor ON cycles, unless
automatically changed by the controls of the
unit. For units having a variable-speed
indoor blower, the manufacturer has the
option of electing at the outset whether to
conduct the cyclic test with the indoor
blower enabled or disabled. Always revert to
testing with the indoor blower disabled if
cyclic testing with the fan enabled is
unsuccessful.
b. For units having a single-speed or twocapacity compressor, cycle the compressor
OFF for 24 minutes and then ON for 6
minutes (Dtcyc,dry = 0.5 hours). For units
having a variable-speed compressor, cycle
the compressor OFF for 48 minutes and then
ON for 12 minutes (Dtcyc,dry = 1.0 hours).
Repeat the OFF/ON compressor cycling
pattern until the test is completed. Allow the
controls of the unit to regulate cycling of the
outdoor fan. If an upturned duct is used,
measure the dry-bulb temperature at the inlet
of the device at least once every minute and
ensure that its test operating tolerance is
within 1.0 °F for each compressor OFF
period.
c. Sections 3.5.1 and 3.5.2 specify airflow
requirements through the indoor coil of
ducted and non-ducted systems, respectively.
In all cases, use the exhaust fan of the airflow
measuring apparatus (covered under section
2.6) along with the indoor blower of the unit,
if installed and operating, to approximate a
step response in the indoor coil airflow.
Regulate the exhaust fan to quickly obtain
and then maintain the flow nozzle static
pressure difference or velocity pressure at the
same value as was measured during the
steady-state dry coil test. The pressure
difference or velocity pressure should be
within 2 percent of the value from the steadystate dry coil test within 15 seconds after
airflow initiation. For units having a variablespeed indoor blower that ramps when
cycling on and/or off, use the exhaust fan of
the airflow measuring apparatus to impose a
step response that begins at the initiation of
ramp up and ends at the termination of ramp
down.
d. For units having a variable-speed indoor
blower, conduct the cyclic dry coil test using
the pull-thru approach described below if
any of the following occur when testing with
the fan operating:
(1) The test unit automatically cycles off;
(2) Its blower motor reverses; or
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external static pressure increases to
approximately DP1 + (DP1 ¥ DPmin).
3. After re-establishing steady readings of
the fan motor power and external static
pressure, determine average values for the
˙
indoor blower power (Efan,2) and the external
5. Increase the total space cooling capacity,
˙
˙
˙
Qck(T), by the quantity (Efan,1 ¥ Efan,min),
when expressed on a Btu/h basis. Decrease
˙
the total electrical power, Eck(T), by the same
fan power difference, now expressed in
watts.
3.4 Test procedures for the steady-state
dry-coil cooling-mode tests (the C, C1, C2, and
G1 Tests).
a. Except for the modifications noted in
this section, conduct the steady-state dry coil
cooling mode tests as specified in section 3.3
for wet coil tests. Prior to recording data
during the steady-state dry coil test, operate
the unit at least one hour after achieving dry
coil conditions. Drain the drain pan and plug
the drain opening. Thereafter, the drain pan
should remain completely dry.
b. Denote the resulting total space cooling
capacity and electrical power derived from
˙
˙
the test as Qss,dry and Ess,dry. With regard to
tkelley on DSK3SPTVN1PROD with PROPOSALS2
minute interval used for determining
capacity.
2. After completing the 30-minute interval
and while maintaining the same test
conditions, adjust the exhaust fan of the
airflow measuring apparatus until the
69418
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
(3) The unit operates for more than 30
seconds at an external static pressure that is
0.1 inches of water or more higher than the
value measured during the prior steady-state
test.
For the pull-thru approach, disable the
indoor blower and use the exhaust fan of the
airflow measuring apparatus to generate the
specified flow nozzles static pressure
difference or velocity pressure. If the exhaust
fan cannot deliver the required pressure
difference because of resistance created by
the unpowered blower, temporarily remove
the blower.
e. Conduct a minimum of six complete
compressor OFF/ON cycles for a unit with a
single-speed or two-speed compressor, and a
minimum of five complete compressor OFF/
ON cycles for a unit with a variable speed
compressor. The first three cycles for a unit
with a single-speed compressor or two-speed
compressor and the first two cycles for a unit
with a unit with a variable speed compressor
are the warm-up period—the later cycles are
called the active cycles. Calculate the
degradation coefficient CD for each complete
active cycle if the test tolerances given in
Table 9 are satisfied. If the average CD for the
first three active cycles is within 0.02 of the
average CD for the first two active cycles, use
the average CD of the three active cycles as
the final result. If these averages differ by
more than 0.02, continue the test to get CD
for the fourth cycle. If the average CD of the
last three cycles is lower than or no more
than 0.02 greater than the average CD of the
first three cycles, use the average CD of all
four active cycles as the final result.
Otherwise, continue the test with a fifth
cycle. If the average CD of the last three
cycles is 0.02 higher than the average for the
previous three cycles, use the default CD,
otherwise use the average CD of all five active
cycles. If the test tolerances given in Table 9
are not satisfied, use default CD value. The
default CD value for cooling is 0.2.
f. With regard to the Table 9 parameters,
continuously record the dry-bulb
temperature of the air entering the indoor
and outdoor coils during periods when air
flows through the respective coils. Sample
the water vapor content of the indoor coil
inlet air at least every 2 minutes during
periods when air flows through the coil.
Record external static pressure and the air
volume rate indicator (either nozzle pressure
difference or velocity pressure) at least every
minute during the interval that air flows
through the indoor coil. (These regular
measurements of the airflow rate indicator
are in addition to the required measurement
at 15 seconds after flow initiation.) Sample
the electrical voltage at least every 2 minutes
beginning 30 seconds after compressor startup. Continue until the compressor, the
outdoor fan, and the indoor blower (if it is
installed and operating) cycle off.
g. For ducted units, continuously record
the dry-bulb temperature of the air entering
(as noted above) and leaving the indoor coil.
Or if using a thermopile, continuously record
the difference between these two
temperatures during the interval that air
flows through the indoor coil. For nonducted units, make the same dry-bulb
temperature measurements beginning when
the compressor cycles on and ending when
indoor coil airflow ceases.
h. Integrate the electrical power over
complete cycles of length Dtcyc,dry. For ducted
units tested with an indoor blower installed
and operating, integrate electrical power from
indoor blower OFF to indoor blower OFF.
For all other ducted units and for non-ducted
units, integrate electrical power from
compressor OFF to compressor OFF. (Some
cyclic tests will use the same data collection
intervals to determine the electrical energy
and the total space cooling. For other units,
terminate data collection used to determine
the electrical energy before terminating data
collection used to determine total space
cooling.)
TABLE 9—TEST OPERATING AND TEST CONDITION TOLERANCES FOR CYCLIC DRY COIL COOLING MODE TESTS
Test
operating
tolerance 1
Indoor entering dry-bulb temperature,2 °F ..............................................................................................................
Indoor entering wet-bulb temperature, °F ...............................................................................................................
Outdoor entering dry-bulb temperature,2 °F ............................................................................................................
External resistance to airflow,2 inches of water ......................................................................................................
Airflow nozzle pressure difference or velocity pressure,2 % of reading .................................................................
Electrical voltage,5% of rdg .....................................................................................................................................
Test
condition
tolerance 1
2.0
........................
2.0
0.12
8.0
2.0
0.5
(3)
0.5
........................
4 2.0
1.5
1 See
section 1.2, Definitions.
during the interval that air flows through the indoor (outdoor) coil except for the first 30 seconds after flow initiation. For units having a
variable-speed indoor blower that ramps, the tolerances listed for the external resistance to airflow apply from 30 seconds after achieving full
speed until ramp down begins.
3 Shall at no time exceed a wet-bulb temperature that results in condensate forming on the indoor coil.
4 The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state dry coil test.
5 Applies during the interval when at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are operating except for the first 30 seconds after compressor start-up.
2 Applies
electrical energy consumption as ecyc,dry and
express it in units of watt-hours. Calculate
the total space cooling delivered, qcyc,dry, in
units of Btu using,
Ô
where V, Cp,a, vn′ (or vn), Wn, and FCD* are
the values recorded during the section 3.4
dry coil steady-state test and
Tal(t) = dry bulb temperature of the air
entering the indoor coil at time t, °F.
Ta2(t) = dry bulb temperature of the air
leaving the indoor coil at time t, °F.
t1 = for ducted units, the elapsed time when
airflow is initiated through the indoor
coil; for non-ducted units, the elapsed
time when the compressor is cycled on,
hr.
t2 = the elapsed time when indoor coil
airflow ceases, hr.
3.5.1 Procedures when testing ducted
systems.
The automatic controls that are normally
installed with the test unit must govern the
OFF/ON cycling of the air moving equipment
on the indoor side (exhaust fan of the airflow
measuring apparatus and, if installed, the
indoor blower of the test unit). For example,
for ducted units tested without an indoor
blower installed but rated based on using a
fan time delay relay, control the indoor coil
airflow according to the rated ON and/or OFF
delays provided by the relay. For ducted
units having a variable-speed indoor blower
that has been disabled (and possibly
removed), start and stop the indoor airflow
at the same instances as if the fan were
enabled. For all other ducted units tested
without an indoor blower installed, cycle the
indoor coil airflow in unison with the cycling
of the compressor. If air damper boxes are
used, close them on the inlet and outlet side
during the OFF period. Airflow through the
indoor coil should stop within 3 seconds
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i. If the Table 9 tolerances are satisfied over
the complete cycle, record the measured
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
after the automatic controls of the test unit
(act to) de-energize the indoor blower. For
ducted units tested without an indoor blower
installed (excluding the special case where a
variable-speed fan is temporarily removed),
increase ecyc,dry by the quantity,
Ô
Equation 3.5–2
(441W÷1000scfm) * V *
[t2¥t1]
and decrease qcyc,dry by,
Ô
Equation 3.5–3 (1505 Btu/h÷1000scfm) * V
* [t2¥t1]
Ô
where Vs is the average indoor air volume
rate from the section 3.4 dry coil steady-state
test and is expressed in units of cubic feet per
minute of standard air (scfm). For units
having a variable-speed indoor blower that is
disabled during the cyclic test, increase
ecyc,dry and decrease qcyc,dry based on:
a. The product of [t2¥t1] and the indoor
blower power measured during or following
the dry coil steady-state test; or,
b. The following algorithm if the indoor
blower ramps its speed when cycling.
1. Measure the electrical power consumed
by the variable-speed indoor blower at a
minimum of three operating conditions: At
the speed/air volume rate/external static
pressure that was measured during the
steady-state test, at operating conditions
69419
associated with the midpoint of the ramp-up
interval, and at conditions associated with
the midpoint of the ramp-down interval. For
these measurements, the tolerances on the
airflow volume or the external static pressure
are the same as required for the section 3.4
steady-state test.
2. For each case, determine the fan power
from measurements made over a minimum of
5 minutes.
3. Approximate the electrical energy
consumption of the indoor blower if it had
operated during the cyclic test using all three
power measurements. Assume a linear
profile during the ramp intervals. The
manufacturer must provide the durations of
the ramp-up and ramp-down intervals. If the
test setup instructions included with the unit
by the manufacturer specifies a ramp interval
that exceeds 45 seconds, use a 45-second
ramp interval nonetheless when estimating
the fan energy.
3.5.2 Procedures when testing nonducted systems.
Do not use airflow prevention devices
when conducting cyclic tests on non-ducted
units. Until the last OFF/ON compressor
cycle, airflow through the indoor coil must
cycle off and on in unison with the
compressor. For the last OFF/ON compressor
cycle—the one used to determine ecyc,dry and
qcyc,dry—use the exhaust fan of the airflow
measuring apparatus and the indoor blower
of the test unit to have indoor airflow start
3 minutes prior to compressor cut-on and
end three minutes after compressor cutoff.
Subtract the electrical energy used by the
indoor blower during the 3 minutes prior to
compressor cut-on from the integrated
electrical energy, ecyc,dry. Add the electrical
energy used by the indoor blower during the
3 minutes after compressor cutoff to the
integrated cooling capacity, qcyc,dry. For the
case where the non-ducted unit uses a
variable-speed indoor blower which is
disabled during the cyclic test, correct ecyc,dry
and qcyc,dry using the same approach as
prescribed in section 3.5.1 for ducted units
having a disabled variable-speed indoor
blower.
3.5.3 Cooling-mode cyclic-degradation
coefficient calculation.
Use the two dry-coil tests to determine the
cooling-mode cyclic-degradation coefficient,
CDc. Append ‘‘(k=2)’’ to the coefficient if it
corresponds to a two-capacity unit cycling at
high capacity. Evaluate CDc using the above
results and those from the section 3.4 drycoil steady-state test.
3.6.1 Tests for a heat pump having a
single-speed compressor that is tested with a
fixed speed indoor blower installed, with a
constant-air-volume-rate indoor blower
installed, or with no indoor blower installed.
Conduct the High Temperature Cyclic
(H1C) Test to determine the heating mode
cyclic-degradation coefficient, CDh. Test
conditions for the four tests are specified in
Table 10.
the average energy efficiency ratio during the
cyclic dry coil cooling mode test, Btu/W·h
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Round the calculated value for CDc to the
nearest 0.01. If CDc is negative, then set it
equal to zero.
3.6 Heating mode tests for different types
of heat pumps, including heating-only heat
pumps.
EP09NO15.230</GPH> EP09NO15.231</GPH>
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the average energy efficiency ratio during the
steady-state dry coil cooling mode test, Btu/
W·h
69420
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
TABLE 10—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A FIXED-SPEED
INDOOR BLOWER, A CONSTANT AIR VOLUME RATE INDOOR BLOWER, OR NO INDOOR BLOWER
Air entering indoor unit
temperature
(°F)
Dry bulb
Test description
Air entering outdoor unit
temperature
(°F)
Dry bulb
H1 Test (required, steady) ..............................................
H1C Test (required, cyclic) .............................................
H2 Test (required) ...........................................................
H3 Test (required, steady) ..............................................
70
70
70
70
Wet bulb
60(max)
60(max)
60(max)
60(max)
Heating air volume rate
Wet bulb
47
47
35
17
43
43
33
15
Heating Full-load.1
(2).
Heating Full-load.1
Heating Full-load.1
1 Defined
in section 3.1.4.4.
the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the H1 Test.
2 Maintain
3.6.2 Tests for a heat pump having a
single-speed compressor and a single indoor
unit having either (1) a variable speed,
variable-air-rate indoor blower whose
capacity modulation correlates with outdoor
dry bulb temperature or (2) multiple blowers.
Conduct five tests: Two High Temperature
Tests (H12 and H11), one Frost Accumulation
Test (H22), and two Low Temperature Tests
(H32 and H31). Conducting an additional
Frost Accumulation Test (H21) is optional.
Conduct the High Temperature Cyclic (H1C1)
Test to determine the heating mode cyclic-
degradation coefficient, CDh. Test conditions
for the seven tests are specified in Table 11.
If the optional H21 Test is not performed, use
the following equations to approximate the
capacity and electrical power of the heat
pump at the H21 test conditions:
˙
˙
The quantities Qhk=2(47), Ehk=2(47),
˙
˙
Qhk=1(47), and Ehk=1(47) are determined from
the H12 and H11 Tests and evaluated as
specified in section 3.7; the quantities
˙
˙
Qhk=2(35) and Ehk=2(35) are determined from
the H22 Test and evaluated as specified in
˙
section 3.9; and the quantities Qhk=2(17),
˙
˙
˙
Ehk=2(17), Qhk=1(17), and Ehk=1(17), are
determined from the H32 and H31 Tests and
evaluated as specified in section 3.10.
TABLE 11—HEATING MODE TEST CONDITIONS FOR UNITS WITH A SINGLE-SPEED COMPRESSOR THAT MEET THE SECTION
3.6.2 INDOOR UNIT REQUIREMENTS
Air entering indoor unit
temperature
(°F)
Dry bulb
Dry bulb
H12 Test (required, steady) ......................
H11 Test (required, steady) ......................
H1C1 Test (required, cyclic) ......................
H22 Test (required) ...................................
H21 Test (optional) ....................................
H32 Test (required, steady) ......................
H31 Test (required, steady) ......................
Wet bulb
70
70
70
70
70
70
70
60(max)
60(max)
60(max)
60(max)
60(max)
60(max)
60(max)
Heating air volume rate
Wet bulb
47
47
47
35
35
17
17
43
43
43
33
33
15
15
Heating
Heating
(3).
Heating
Heating
Heating
Heating
Full-load.1
Minimum.2
Full-load.1
Minimum.2
Full-load.1
Minimum.2
1 Defined
in section 3.1.4.4.
in section 3.1.4.5.
the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the H11 Test.
2 Defined
3 Maintain
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Test description
Air entering outdoor unit
temperature
(°F)
69421
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
3.6.3 Tests for a heat pump having a twocapacity compressor (see section 1.2,
Definitions), including two-capacity,
northern heat pumps (see section 1.2,
Definitions).
a. Conduct one Maximum Temperature
Test (H01), two High Temperature Tests
(H12and H11), one Frost Accumulation Test
(H22), and one Low Temperature Test (H32).
Conduct an additional Frost Accumulation
Test (H21) and Low Temperature Test (H31)
if both of the following conditions exist:
1. Knowledge of the heat pump’s capacity
and electrical power at low compressor
capacity for outdoor temperatures of 37 °F
and less is needed to complete the section
4.2.3 seasonal performance calculations; and
2. The heat pump’s controls allow lowcapacity operation at outdoor temperatures of
37 °F and less.
If the above two conditions are met, an
alternative to conducting the H21 Frost
Accumulation is to use the following
equations to approximate the capacity and
electrical power:
˙
Determine the quantities Qhk=1 (47) and
˙
Ehk=1 (47) from the H11 Test and evaluate
them according to Section 3.7. Determine the
˙
˙
quantities Qhk=1 (17) and Ehk=1 (17) from the
H31 Test and evaluate them according to
Section 3.10.
b. Conduct the High Temperature Cyclic
Test (H1C1) to determine the heating mode
cyclic-degradation coefficient, CDh. If a twocapacity heat pump locks out low capacity
operation at lower outdoor temperatures,
conduct the High Temperature Cyclic Test
(H1C2) to determine the high-capacity
heating mode cyclic-degradation coefficient,
CDh (k=2). Table 12 specifies test conditions
for these nine tests.
TABLE 12—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR
Air entering indoor unit
temperature (°F)
Air entering outdoor unit
temperature (°F)
Dry bulb
Test description
Dry bulb
H01 Test (required, steady) ....................
H12 Test (required, steady) ....................
H1C2 Test (required,7 cyclic) ..................
H11 Test (required) .................................
H1C1 Test (required, cyclic) ....................
H22 Test (required) .................................
H21 Test 5 6 (required) .............................
H32 Test (required, steady) ....................
H31 Test 5 (required, steady) ..................
Wet bulb
70
70
70
70
70
70
70
70
70
60 (max)
60 (max)
60 (max)
60 (max)
60 (max)
60 (max)
60 (max)
60 (max)
60 (max)
Compressor capacity
Heating air volume
rate
Low
High
High
Low
Low
High
Low
High
Low
Heating
Heating
(3)
Heating
( 4)
Heating
Heating
Heating
Heating
Wet bulb
62
47
47
47
47
35
35
17
17
56.5
43
43
43
43
33
33
15
15
........................
.......................
.......................
........................
........................
.......................
........................
.......................
........................
Minimum.1
Full-Load.2
Minimum.1
Full-Load.2
Minimum.1
Full-Load.2
Minimum.1
1 Defined
in section 3.1.4.5.
in section 3.1.4.4.
the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H12 Test.
4 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H11 Test.
5 Required only if the heat pump’s performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is needed to complete the section 4.2.3 HSPF calculations.
6 If table note #5 applies, the section 3.6.3 equations for Q k=1 (35) and E k=1 (17) may be used in lieu of conducting the H2 Test.
˙h
˙h
1
7 Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.
2 Defined
3 Maintain
Temperature Cyclic (H1C1) Test to determine
the heating mode cyclic-degradation
coefficient, CDh. (2) The optional low
ambient temperature test (H42) may be
conducted in place of H12 to allow
representation of heating performance below
17 °F ambient temperature using the results
of H42 and H32 rather than the results of H32
and H12. This option may not be used for
units which have a cutoff temperature
preventing compressor operation below 12
°F. If H42 is conducted, it is optional to
conduct the H12 test for heating capacity
rating purposes—H1N can be conducted for
heating capacity rating purposes. If H12 is not
conducted, H22 must be conducted.
Test conditions for the nine tests are
specified in Table 13. Determine the
intermediate compressor speed cited in Table
13 using the heating mode maximum and
minimum compressors speeds and:
Where a tolerance of plus 5 percent or the
next higher inverter frequency step from that
calculated is allowed. If the H22Test is not
done, use the following equations to
approximate the capacity and electrical
power at the H22 test conditions:
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3.6.4 Tests for a heat pump having a
variable-speed compressor.
a. (1) Conduct one Maximum Temperature
Test (H01), two High Temperature Tests (H12
and H11), one Frost Accumulation Test
(H2V), and one Low Temperature Test (H32).
Conducting one or all of the following tests
is optional: An additional High Temperature
Test (H1N), an additional Frost Accumulation
Test (H22), and an additional Low
Temperature Test (H42). Conduct the High
69422
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
˙
˙
the quantities Qhk=2(TL) and Ehk=2(TL) from
the H42 Test and evaluate them according to
section 3.10. For heat pumps where the
heating mode maximum compressor speed
exceeds its cooling mode maximum
compressor speed, conduct the H1N Test if
˙
b. Determine the quantities Qhk=2(47) and
˙
from Ehk=2(47) from the H12 Test and
evaluate them according to section 3.7.
˙
Determine the quantities Qhk=2(17) and
˙
Ehk=2(17) from the H32 Test and evaluate
them according to section 3.10. Determine
the manufacturer requests it. If the H1N Test
is done, operate the heat pump’s compressor
at the same speed as the speed used for the
cooling mode A2 Test.
TABLE 13—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A VARIABLE-SPEED COMPRESSOR
Air entering indoor unit
temperature (°F)
Air entering outdoor unit
temperature (°F)
Dry bulb
Test description
Dry bulb
Wet bulb
60 (max)
Compressor speed
Heating air volume
rate
Minimum ................
Minimum ................
Maximum ...............
Minimum ................
Cooling Mode Maximum.
Maximum ...............
Intermediate ...........
Heating
(2).
Heating
Heating
Heating
Wet bulb
H01 Test (required, steady) .....................
H1C1 Test (required, cyclic) ....................
H12 Test (required, steady) .....................
H11 Test (required, steady) .....................
H1N Test (optional, steady) .....................
70
70
70
70
70
60 (max)
60 (max)
60 (max)
60 (max)
62
47
47
47
47
56.5
43
43
43
43
H22 Test (optional) ..................................
H2V Test (required) .................................
70
70
60 (max)
60 (max)
35
35
33
33
H32 Test (required, steady) .....................
H42 Test (optional, steady) 6 ...................
70
70
60 (max)
60 (max)
17
15
72
71
Maximum ...............
Maximum 8 .............
Minimum.1
Full-Load.3
Minimum.1
Nominal.4
Heating Full-Load.3
Heating Intermediate.5
Heating Full-Load.3
Heating Full-Load.3
1 Defined
in section 3.1.4.5.
the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H01 Test.
3 Defined in section 3.1.4.4.
4 Defined in section 3.1.4.7.
5 Defined in section 3.1.4.6.
6 If the maximum speed is limited below 17 °F, this test becomes required.
7 If the cutoff temperature is higher than 2 °F, run at the cutoff temperature.
8 If maximum speed is limited by unit control, this test should run at the maximum speed allowed by the control, in such case, the speed is different from the maximum speed defined in the definition section.
2 Maintain
3.6.5 Additional test for a heat pump
having a heat comfort controller.
Test any heat pump that has a heat comfort
controller (see section 1.2, Definitions)
according to section 3.6.1, 3.6.2, or 3.6.3,
whichever applies, with the heat comfort
controller disabled. Additionally, conduct
the abbreviated test described in section 3.1.9
with the heat comfort controller active to
determine the system’s maximum supply air
temperature. (Note: Heat pumps having a
variable speed compressor and a heat comfort
controller are not covered in the test
procedure at this time.)
3.6.6 Heating mode tests northern heat
pumps with triple-capacity compressors.
Test triple-capacity, northern heat pumps
for the heating mode as follows:
a. Conduct one maximum-temperature test
(H01), two high-temperature tests (H12 and
H11), one Frost Accumulation test (H22), two
low-temperature tests (H32, H33), and one
minimum-temperature test (H43). Conduct an
additional Frost Accumulation test (H21) and
low-temperature test (H31) if both of the
following conditions exist: (1) Knowledge of
the heat pump’s capacity and electrical
power at low compressor capacity for
outdoor temperatures of 37 °F and less is
needed to complete the section 4.2.6 seasonal
performance calculations; and (2) the heat
pump’s controls allow low-capacity
operation at outdoor temperatures of 37 °F
and less. If the above two conditions are met,
an alternative to conducting the H21 Frost
˙
Accumulation Test to determine Qhk=1(35)
˙
and Ehk=1(35) is to use the following
equations to approximate this capacity and
electrical power:
In evaluating the above equations, determine
˙
the quantities Qhk=1(47) from the H11 Test
and evaluate them according to section 3.7.
˙
Determine the quantities Qhk=1(17) and
˙
Ehk=1(17) from the H31 Test and evaluate
them according to section 3.10. Use the
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c. For multiple-split heat pumps (only), the
following procedures supersede the above
requirements. For all Table 13 tests specified
for a minimum compressor speed, at least
one indoor unit must be turned off. The
manufacturer shall designate the particular
indoor unit(s) that is turned off. The
manufacturer must also specify the
compressor speed used for the Table 13 H2V
Test, a heating mode intermediate
compressor speed that falls within 1⁄4 and 3⁄4
of the difference between the maximum and
minimum heating mode speeds. The
manufacturer should prescribe an
intermediate speed that is expected to yield
the highest COP for the given H2V Test
conditions and bracketed compressor speed
range. The manufacturer can designate that
one or more specific indoor units are turned
off for the H2V Test.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69423
˙
˙
paired values of Qhk=1(35) and Ehk=1(35)
derived from conducting the H21 Frost
Accumulation Test and evaluated as
specified in section 3.9.1 or use the paired
values calculated using the above default
equations, whichever contribute to a higher
Region IV HSPF based on the DHR.
b. Conducting a Frost Accumulation Test
(H23) with the heat pump operating at its
booster capacity is optional. If this optional
˙
test is not conducted, determine Qhk=3(35)
˙
and Ehk=3(35) using the following equations
to approximate this capacity and electrical
power:
˙
Determine the quantities Qhk=2(47) and
˙
Ehk=2(47) from the H12 Test and evaluate
them according to section 3.7. Determine the
˙
˙
quantities Qhk=2(35) and Ehk=2(35) from the
H22Test and evaluate them according to
section 3.9.1. Determine the quantities
˙
˙
Qhk=2(17) and Ehk=2(17) from the H32Test,
˙
determine the quantities Qhk=3(17) and
˙
Ehk=3(17) from the H33Test, and determine
˙
˙
the quantities Qhk=3(2) and Ehk=3(2) from the
H43Test. Evaluate all six quantities according
to section 3.10. Use the paired values of
˙
˙
Qhk=3(35) and Ehk=3(35) derived from
conducting the H23Frost Accumulation Test
and calculated as specified in section 3.9.1 or
use the paired values calculated using the
above default equations, whichever
contribute to a higher Region IV HSPF based
on the DHR.
c. Conduct the high-temperature cyclic test
(H1C1) to determine the heating mode cyclicdegradation coefficient, CDh. If a triplecapacity heat pump locks out low capacity
operation at lower outdoor temperatures,
conduct the high-temperature cyclic test
(H1C2) to determine the high-capacity
heating mode cyclic-degradation coefficient,
CDh (k=2). The default CDh (k=2) is the same
value as determined or assigned for the lowcapacity cyclic-degradation coefficient, CDh
[or equivalently, CDh (k=1)]. Finally, if a
triple-capacity heat pump locks out both low
and high capacity operation at the lowest
outdoor temperatures, conduct the lowtemperature cyclic test (H3C3) to determine
the booster-capacity heating mode cyclicdegradation coefficient, CDh (k=3). The
default CDh (k=3) is the same value as
determined or assigned for the high-capacity
cyclic-degradation coefficient, CDh [or
equivalently, CDh (k=2)]. Table 14 specifies
test conditions for all 13 tests.
TABLE 14— HEATING MODE TEST CONDITIONS FOR UNITS WITH A TRIPLE-CAPACITY COMPRESSOR
Test description
Air entering indoor unit temperature
°F
H01 Test (required,
steady).
H12 Test (required,
steady).
H1C2 Test (required,
cyclic).
H11 Test (required) ......
H1C1 Test (required,
cyclic).
H23 Test (optional,
steady).
H22 Test (required) ......
H21 Test (required) ......
H33 Test (required,
steady).
H3C3 Test (max)5 6 (required, cyclic).
H32 Test (required,
steady).
H31 Test5 (required,
steady).
H43 Test (required,
steady).
Wet bulb
Dry bulb
Compressor capacity
Heating air volume
rate
Wet bulb
70
60(max)
62
56.5
Low .............................
Heating Minimum.1
70
60 (max)
47
43
High ............................
Heating Full-Load.2
70
60 (max)
47
43
High ............................
( 3)
70
70
60 (max)
60 (max)
47
47
43
43
Low .............................
Low .............................
Heating Minimum.1
( 4)
70
60 (max)
35
33
Booster .......................
Heating Full-Load.2
70
70
70
60 (max)
60 (max)
60 (max)
35
35
17
33
33
15
High ............................
Low .............................
Booster .......................
Heating Full-Load.2
Heating Minimum.1
Heating Full-Load.2
70
60 (max)
17
15
Booster .......................
( 7)
70
60 (max)
17
15
High ............................
Heating Full-Load.2
70
60 (max)
17
15
Low .............................
Heating Minimum.1
70
60 (max)
2
1
Booster .......................
Heating Full-Load.2
1 Defined
in section 3.1.4.5.
in section 3.1.4.4.
3 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H12 Test.
4 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H11Test.
5 Required only if the heat pump’s performance when operating at low compressor capacity and outdoor temperatures less than 37°F is needed to complete the section 4.2.6 HSPF calculations.
2 Defined
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Dry bulb
Air entering outdoor unit temperature
°F
69424
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
˙
˙
table note 5 applies, the section 3.6.6 equations for Qhk=1(35) and Ehk=1(17) may be used in lieu of conducting the H21 Test.
the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H33 Test.
6 If
7 Maintain
3.7 Test procedures for steady-state
Maximum Temperature and High
Temperature heating mode tests (the H01, H1,
H12, H11, and H1N Tests).
a. For the pretest interval, operate the test
room reconditioning apparatus and the heat
pump until equilibrium conditions are
maintained for at least 30 minutes at the
specified section 3.6 test conditions. Use the
exhaust fan of the airflow measuring
apparatus and, if installed, the indoor blower
of the heat pump to obtain and then maintain
the indoor air volume rate and/or the
external static pressure specified for the
particular test. Continuously record the drybulb temperature of the air entering the
indoor coil, and the dry-bulb temperature
and water vapor content of the air entering
the outdoor coil. Refer to section 3.11 for
additional requirements that depend on the
selected secondary test method. After
satisfying the pretest equilibrium
requirements, make the measurements
specified in Table 3 of ASHRAE Standard
37–2009 for the Indoor Air Enthalpy method
and the user-selected secondary method.
Make said Table 3 measurements at equal
intervals that span 5 minutes or less.
Continue data sampling until a 30-minute
period (e.g., four consecutive 10-minute
samples) is reached where the test tolerances
specified in Table 15 are satisfied. For those
continuously recorded parameters, use the
entire data set for the 30-minute interval
when evaluating Table 15 compliance.
Determine the average electrical power
consumption of the heat pump over the same
30-minute interval.
TABLE 15—TEST OPERATING AND TEST CONDITION TOLERANCES FOR SECTION 3.7 AND SECTION 3.10 STEADY-STATE
HEATING MODE TESTS
Test
operating tolerance 1
Test
condition tolerance 1
2.0
2.0
0.5
..........................
1.0
1.0
..........................
..........................
2.0
0.5
..........................
Indoor dry-bulb, °F:
Entering temperature ....................................................................................................................................
Leaving temperature .....................................................................................................................................
Indoor wet-bulb, °F:
Entering temperature ....................................................................................................................................
Leaving temperature .....................................................................................................................................
Outdoor dry-bulb, °F:
Entering temperature ....................................................................................................................................
Leaving temperature .....................................................................................................................................
Outdoor wet-bulb, °F:
Entering temperature ....................................................................................................................................
Leaving temperature .....................................................................................................................................
External resistance to airflow, inches of water ....................................................................................................
Electrical voltage, % of rdg ..................................................................................................................................
Nozzle pressure drop, % of rdg ..........................................................................................................................
22.0
1.0
21.0
0.12
2.0
8.0
0.3
..........................
30.02
1.5
..........................
1 See
section 1.2, Definitions.
applies when the Outdoor Air Enthalpy Method is used.
3 Only applies when testing non-ducted units.
2 Only
capacity and electrical power over the 30minute data collection interval to the
˙
˙
variables Qhk and Ehk(T) respectively. The
‘‘T’’ and superscripted ‘‘k’’ are the same as
described in section 3.3. Additionally, for the
heating mode, use the superscript to denote
results from the optional H1N Test, if
conducted.c. For heat pumps tested without
˙
an indoor blower installed, increase Qhk(T)
by
˙
and increase Ehk(T) by,
Ô
where Vs is the average measured indoor air
volume rate expressed in units of cubic feet
per minute of standard air (scfm). During the
30-minute data collection interval of a High
Temperature Test, pay attention to
preventing a defrost cycle. Prior to this time,
allow the heat pump to perform a defrost
cycle if automatically initiated by its own
controls. As in all cases, wait for the heat
pump’s defrost controls to automatically
terminate the defrost cycle. Heat pumps that
undergo a defrost should operate in the
heating mode for at least 10 minutes after
defrost termination prior to beginning the 30minute data collection interval. For some
heat pumps, frost may accumulate on the
outdoor coil during a High Temperature test.
If the indoor coil leaving air temperature or
the difference between the leaving and
entering air temperatures decreases by more
than 1.5 °F over the 30-minute data
collection interval, then do not use the
collected data to determine capacity. Instead,
initiate a defrost cycle. Begin collecting data
no sooner than 10 minutes after defrost
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b. Calculate indoor-side total heating
capacity as specified in sections 7.3.4.1 and
7.3.4.3 of ASHRAE Standard 37–2009. Do not
adjust the parameters used in calculating
capacity for the permitted variations in test
conditions. Assign the average space heating
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69425
c. For heat pumps tested without an indoor
˙
blower installed, increase Qhk(T) by
no sooner than 10 minutes after defrost
termination. Collect 30 minutes of new data
during which the Table 15 test tolerances are
satisfied. In this case, use only the results
from the second 30-minute data collection
˙
˙
interval to evaluate Qhk(47) and Ehk(47).
d. If conducting the cyclic heating mode
test, which is described in section 3.8, record
Ô
the average indoor-side air volume rate, V,
specific heat of the air, Cp,a (expressed on dry
air basis), specific volume of the air at the
nozzles, vn′ (or vn), humidity ratio at the
nozzles, Wn, and either pressure difference or
velocity pressure for the flow nozzles. If
either or both of the below criteria apply,
determine the average, steady-state, electrical
power consumption of the indoor blower
˙
motor (Efan,1):
1. The section 3.8 cyclic test will be
conducted and the heat pump has a variablespeed indoor blower that is expected to be
disabled during the cyclic test; or
2. The heat pump has a (variable-speed)
constant-air volume-rate indoor blower and
during the steady-state test the average
external static pressure (DP1) exceeds the
applicable section 3.1.4.4 minimum (or
targeted) external static pressure (DPmin) by
0.03 inches of water or more.
˙
Determine Efan,1 by making measurements
during the 30-minute data collection interval,
or immediately following the test and prior
to changing the test conditions. When the
above ‘‘2’’ criteria applies, conduct the
˙
following four steps after determining Efan,1
(which corresponds to DP1):
i. While maintaining the same test
conditions, adjust the exhaust fan of the
airflow measuring apparatus until the
external static pressure increases to
approximately DP1 + (DP1 ¥ DPmin).
ii. After re-establishing steady readings for
fan motor power and external static pressure,
determine average values for the indoor
˙
blower power (Efan,2) and the external static
pressure (DP2) by making measurements over
a 5-minute interval.
iii. Approximate the average power
consumption of the indoor blower motor if
the 30-minute test had been conducted at
DPmin using linear extrapolation:
iv. Decrease the total space heating
˙
˙
capacity, Qhk(T), by the quantity (Efan,1 ¥
˙
Efan,min), when expressed on a Btu/h basis.
˙
Decrease the total electrical power, Ehk(T) by
the same fan power difference, now
expressed in watts.
e. If the temperature sensors used to
provide the primary measurement of the
indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the
subsequent cyclic dry-coil test are different,
include measurements of the latter sensors
among the regularly sampled data. Beginning
at the start of the 30-minute data collection
period, measure and compute the indoor-side
air dry-bulb temperature difference using
both sets of instrumentation, DT (Set SS) and
DT (Set CYC), for each equally spaced data
sample. If using a consistent data sampling
rate that is less than 1 minute, calculate and
record minutely averages for the two
temperature differences. If using a consistent
sampling rate of one minute or more,
calculate and record the two temperature
differences from each data sample. After
having recorded the seventh (i=7) set of
temperature differences, calculate the
following ratio using the first seven sets of
values:
Each time a subsequent set of temperature
differences is recorded (if sampling more
frequently than every 5 minutes), calculate
FCD using the most recent seven sets of
values. Continue these calculations until the
30-minute period is completed or until a
value for FCD is calculated that falls outside
the allowable range of 0.94–1.06. If the latter
occurs, immediately suspend the test and
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from the second 30-minute data collection
˙
˙
interval to evaluate Qhk(47) and Ehk(47).
˙
and increase Ehk(T) by,
Ô
where Vs is the average measured indoor air
volume rate expressed in units of cubic feet
per minute of standard air (scfm). During the
30-minute data collection interval of a High
Temperature Test, pay attention to
preventing a defrost cycle. Prior to this time,
allow the heat pump to perform a defrost
cycle if automatically initiated by its own
controls. As in all cases, wait for the heat
pump’s defrost controls to automatically
terminate the defrost cycle. Heat pumps that
undergo a defrost should operate in the
heating mode for at least 10 minutes after
defrost termination prior to beginning the 30minute data collection interval. For some
heat pumps, frost may accumulate on the
outdoor coil during a High Temperature test.
If the indoor coil leaving air temperature or
the difference between the leaving and
entering air temperatures decreases by more
than 1.5 °F over the 30-minute data
collection interval, then do not use the
collected data to determine capacity. Instead,
initiate a defrost cycle. Begin collecting data
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termination. Collect 30 minutes of new data
during which the Table 15 test tolerances are
satisfied. In this case, use only the results
69426
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
identify the cause for the disparity in the two
temperature difference measurements.
Recalibration of one or both sets of
instrumentation may be required. If all the
values for FCD are within the allowable range,
save the final value of the ratio from the 30minute test as FCD*. If the temperature
sensors used to provide the primary
measurement of the indoor-side dry bulb
temperature difference during the steadystate dry-coil test and the subsequent cyclic
dry-coil test are the same, set FCD*= 1.
3.8 Test procedures for the cyclic heating
mode tests (the H0C1, H1C, H1C1 and H1C2
Tests).
a. Except as noted below, conduct the
cyclic heating mode test as specified in
section 3.5. As adapted to the heating mode,
replace section 3.5 references to ‘‘the steadystate dry coil test’’ with ‘‘the heating mode
steady-state test conducted at the same test
conditions as the cyclic heating mode test.’’
Use the test tolerances in Table 16 rather
than Table 9. Record the outdoor coil
entering wet-bulb temperature according to
the requirements given in section 3.5 for the
outdoor coil entering dry-bulb temperature.
Drop the subscript ‘‘dry’’ used in variables
cited in section 3.5 when referring to
quantities from the cyclic heating mode test.
The default CD value for heating is 0.25. If
available, use electric resistance heaters (see
section 2.1) to minimize the variation in the
inlet air temperature. Determine the total
space heating delivered during the cyclic
heating test, qcyc, as specified in section 3.5
except for making the following changes:
(1) When evaluating Equation 3.5–1, use
Ô
the values of V, Cp,a,vn′, (or vn), and Wn that
were recorded during the section 3.7 steadystate test conducted at the same test
conditions.
where FCD* is the value recorded during the
section 3.7 steady-state test conducted at the
same test condition.
b. For ducted heat pumps tested without
an indoor blower installed (excluding the
special case where a variable-speed fan is
temporarily removed), increase qcyc by the
amount calculated using Equation 3.5–3.
Additionally, increase ecyc by the amount
calculated using Equation 3.5–2. In making
these calculations, use the average indoor air
Ô
volume rate (Vs) determined from the section
3.7 steady-state heating mode test conducted
at the same test conditions.
c. For non-ducted heat pumps, subtract the
electrical energy used by the indoor blower
during the 3 minutes after compressor cutoff
from the non-ducted heat pump’s integrated
heating capacity, qcyc.
d. If a heat pump defrost cycle is manually
or automatically initiated immediately prior
to or during the OFF/ON cycling, operate the
heat pump continuously until 10 minutes
after defrost termination. After that, begin
cycling the heat pump immediately or delay
until the specified test conditions have been
re-established. Pay attention to preventing
defrosts after beginning the cycling process.
For heat pumps that cycle off the indoor
blower during a defrost cycle, make no effort
here to restrict the air movement through the
indoor coil while the fan is off. Resume the
OFF/ON cycling while conducting a
minimum of two complete compressor OFF/
ON cycles before determining qcyc and ecyc.
3.8.1 Heating mode cyclic-degradation
coefficient calculation.
Use the results from the cyclic test and the
required steady-state test that were
conducted at the same test conditions to
determine the heating mode cyclicdegradation coefficient CDh. Add ‘‘(k=2)’’ to
the coefficient if it corresponds to a twocapacity unit cycling at high capacity. For the
below calculation of the heating mode cyclic
degradation coefficient, do not include the
duct loss correction from section 7.3.3.3 of
ASHRAE Standard 37–2009 in determining
˙
Qhk(Tcyc) (or qcyc). The tested CDh is
calculated as follows:
outdoor dry bulb temperature, Tcyc, and
speed/capacity, k, if applicable—as specified
for the cyclic heating mode test,
dimensionless.
where,
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the average coefficient of performance during
the steady-state heating mode test conducted
at the same test conditions—i.e., same
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the average coefficient of performance during
the cyclic heating mode test, dimensionless.
69427
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
Dtcyc, the duration of the OFF/ON intervals;
0.5 hours when testing a heat pump having
a single-speed or two-capacity compressor
and 1.0 hour when testing a heat pump
having a variable-speed compressor.
the heating load factor, dimensionless.
Tcyc, the nominal outdoor temperature at
which the cyclic heating mode test is
conducted, 62 or 47 °F.
Round the calculated value for CDh to the
nearest 0.01. If CDh is negative, then set it
equal to zero.
TABLE 16—TEST OPERATING AND TEST CONDITION TOLERANCES FOR CYCLIC HEATING MODE TESTS
Test
operating
tolerance 1
Indoor entering dry-bulb temperature,2 °F ..............................................................................................................
Indoor entering wet-bulb temperature,2 °F ..............................................................................................................
Outdoor entering dry-bulb temperature,2 °F ............................................................................................................
Outdoor entering wet-bulb temperature,2 °F ...........................................................................................................
External resistance to air-flow,2 inches of water .....................................................................................................
Airflow nozzle pressure difference or velocity pressure,2% of reading ..................................................................
Electrical voltage,4% of rdg .....................................................................................................................................
2.0
1.0
2.0
2.0
0.12
2.0
8.0
Test
condition
tolerance 1
0.5
........................
0.5
1.0
........................
3 2.0
1.5
1 See
section 1.2, Definitions.
during the interval that air flows through the indoor (outdoor) coil except for the first 30 seconds after flow initiation. For units having a
variable-speed indoor blower that ramps, the tolerances listed for the external resistance to airflow shall apply from 30 seconds after achieving
full speed until ramp down begins.
3 The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state test conducted at
the same test conditions.
4 Applies during the interval that at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are operating, except for the first 30 seconds after compressor start-up.
3.9 Test procedures for Frost
Accumulation heating mode tests (the H2,
H22, H2V, and H21 Tests).
a. Confirm that the defrost controls of the
heat pump are set as specified in section
2.2.1. Operate the test room reconditioning
apparatus and the heat pump for at least 30
minutes at the specified section 3.6 test
conditions before starting the ‘‘preliminary’’
test period. The preliminary test period must
immediately precede the ‘‘official’’ test
period, which is the heating and defrost
interval over which data are collected for
evaluating average space heating capacity
and average electrical power consumption.
b. For heat pumps containing defrost
controls which are likely to cause defrosts at
intervals less than one hour, the preliminary
test period starts at the termination of an
automatic defrost cycle and ends at the
termination of the next occurring automatic
defrost cycle. For heat pumps containing
defrost controls which are likely to cause
defrosts at intervals exceeding one hour, the
preliminary test period must consist of a
heating interval lasting at least one hour
followed by a defrost cycle that is either
manually or automatically initiated. In all
cases, the heat pump’s own controls must
govern when a defrost cycle terminates.
c. The official test period begins when the
preliminary test period ends, at defrost
termination. The official test period ends at
the termination of the next occurring
automatic defrost cycle. When testing a heat
pump that uses a time-adaptive defrost
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control system (see section 1.2, Definitions),
however, manually initiate the defrost cycle
that ends the official test period at the instant
indicated by instructions provided by the
manufacturer. If the heat pump has not
undergone a defrost after 6 hours,
immediately conclude the test and use the
results from the full 6-hour period to
calculate the average space heating capacity
and average electrical power consumption.
For heat pumps that turn the indoor blower
off during the defrost cycle, take steps to
cease forced airflow through the indoor coil
and block the outlet duct whenever the heat
pump’s controls cycle off the indoor blower.
If it is installed, use the outlet damper box
described in section 2.5.4.1 to affect the
blocked outlet duct.
d. Defrost termination occurs when the
controls of the heat pump actuate the first
change in converting from defrost operation
to normal heating operation. Defrost
initiation occurs when the controls of the
heat pump first alter its normal heating
operation in order to eliminate possible
accumulations of frost on the outdoor coil.
e. To constitute a valid Frost Accumulation
test, satisfy the test tolerances specified in
Table 17 during both the preliminary and
official test periods. As noted in Table 17,
test operating tolerances are specified for two
sub-intervals: (1) When heating, except for
the first 10 minutes after the termination of
a defrost cycle (Sub-interval H, as described
in Table 17) and (2) when defrosting, plus
these same first 10 minutes after defrost
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termination (Sub-interval D, as described in
Table 17). Evaluate compliance with Table 17
test condition tolerances and the majority of
the test operating tolerances using the
averages from measurements recorded only
during Sub-interval H. Continuously record
the dry bulb temperature of the air entering
the indoor coil, and the dry bulb temperature
and water vapor content of the air entering
the outdoor coil. Sample the remaining
parameters listed in Table 17 at equal
intervals that span 5 minutes or less.
f. For the official test period, collect and
use the following data to calculate average
space heating capacity and electrical power.
During heating and defrosting intervals when
the controls of the heat pump have the
indoor blower on, continuously record the
dry-bulb temperature of the air entering (as
noted above) and leaving the indoor coil. If
using a thermopile, continuously record the
difference between the leaving and entering
dry-bulb temperatures during the interval(s)
that air flows through the indoor coil. For
heat pumps tested without an indoor blower
installed, determine the corresponding
cumulative time (in hours) of indoor coil
airflow, Dta. Sample measurements used in
calculating the air volume rate (refer to
sections 7.7.2.1 and 7.7.2.2 of ASHRAE
Standard 37–2009) at equal intervals that
span 10 minutes or less. (Note: In the first
printing of ASHRAE Standard 37–2009, the
second IP equation for Qmi should read:
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2 Applies
69428
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Record the electrical energy consumed,
expressed in watt-hours, from defrost
termination to defrost termination, eDEFk(35),
as well as the corresponding elapsed time in
hours, DtFR.
TABLE 17—TEST OPERATING AND TEST CONDITION TOLERANCES FOR FROST ACCUMULATION HEATING MODE TESTS
Test operating tolerance 1
Sub-interval
D3
Test condition
tolerance 1
Sub-interval
H2
4 4.0
........................
10.0
........................
........................
........................
0.5
........................
1.0
0.5
5 0.02
1.5
Sub-interval
H2
Indoor entering dry-bulb temperature, °F ....................................................................................
Indoor entering wet-bulb temperature, °F ...................................................................................
Outdoor entering dry-bulb temperature, °F .................................................................................
Outdoor entering wet-bulb temperature, °F .................................................................................
External resistance to airflow, inches of water ............................................................................
Electrical voltage, % of rdg ..........................................................................................................
2.0
1.0
2.0
1.5
0.12
2.0
1 See
section 1.2, Definitions.
when the heat pump is in the heating mode, except for the first 10 minutes after termination of a defrost cycle.
3 Applies during a defrost cycle and during the first 10 minutes after the termination of a defrost cycle when the heat pump is operating in the
heating mode.
4 For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies during the 10 minute interval that follows defrost termination.
5 Only applies when testing non-ducted heat pumps.
2 Applies
Wn = humidity ratio of the air-water vapor
mixture at the nozzle, lbm of water vapor
per lbm of dry air.
DtFR = t2 ¥ t1, the elapsed time from defrost
termination to defrost termination, hr.
Tal(t) = dry bulb temperature of the air
entering the indoor coil at elapsed time
t, °F; only recorded when indoor coil
airflow occurs; assigned the value of zero
during periods (if any) where the indoor
blower cycles off.
Ta2(t) = dry bulb temperature of the air
leaving the indoor coil at elapsed time t,
°F; only recorded when indoor coil
airflow occurs; assigned the value of zero
during periods (if any) where the indoor
blower cycles off.
t1 = the elapsed time when the defrost
termination occurs that begins the
official test period, hr.
t2 = the elapsed time when the next
automatically occurring defrost
termination occurs, thus ending the
official test period, hr.
vn = specific volume of the dry air portion
of the mixture evaluated at the dry-bulb
temperature, vapor content, and
barometric pressure existing at the
nozzle, ft3 per lbm of dry air.
To account for the effect of duct losses
between the outlet of the indoor unit and the
section 2.5.4 dry-bulb temperature grid,
˙
adjust Qhk(35) in accordance with section
7.3.4.3 of ASHRAE Standard 37–2009.
b. Evaluate average electrical power,
˙
Ehk(35), when expressed in units of watts,
using:
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mixture that flows through the indoor
coil and is expressed on a dry air basis,
Btu/lbmda · °F.
vn′ = specific volume of the air-water vapor
mixture at the nozzle, ft3/lbmmx.
EP09NO15.251</GPH>
a. Evaluate average space heating capacity,
˙
Qhk(35), when expressed in units of Btu per
hour, using:
Where,
Ô
V = the average indoor air volume rate
measured during Sub-interval H, cfm.
Cp,a = 0.24 + 0.444 · Wn, the constant pressure
specific heat of the air-water vapor
tkelley on DSK3SPTVN1PROD with PROPOSALS2
3.9.1 Average space heating capacity and
electrical power calculations.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69429
For heat pumps tested without an indoor
˙
blower installed, increase Qhk(35) by,
1. Measure the average power consumption
˙
of the indoor blower motor (Efan,1) and record
the corresponding external static pressure
(DP1) during or immediately following the
Frost Accumulation heating mode test. Make
the measurement at a time when the heat
pump is heating, except for the first 10
minutes after the termination of a defrost
cycle.
2. After the Frost Accumulation heating
mode test is completed and while
maintaining the same test conditions, adjust
the exhaust fan of the airflow measuring
apparatus until the external static pressure
increases to approximately DP1 + (DP1 ¥
DPmin).
3. After re-establishing steady readings for
the fan motor power and external static
pressure, determine average values for the
˙
indoor blower power (Efan,2) and the external
static pressure (DP2) by making
measurements over a 5-minute interval.
4. Approximate the average power
consumption of the indoor blower motor had
the Frost Accumulation heating mode test
been conducted at DPmin using linear
extrapolation:
5. Decrease the total heating capacity,
˙
˙
˙
Qhk(35), by the quantity [(Efan,1 ¥ Efan,min)· (Dt
a/DtFR], when expressed on a Btu/h basis.
Decrease the total electrical power, Ehk(35),
by the same quantity, now expressed in
watts.
3.9.2 Demand defrost credit.
a. Assign the demand defrost credit, Fdef,
that is used in section 4.2 to the value of 1
in all cases except for heat pumps having a
demand-defrost control system (see section
1.2, Definitions). For such qualifying heat
pumps, evaluate Fdef using,
Where,
Dtdef = the time between defrost terminations
(in hours) or 1.5, whichever is greater. A
value of 6 must be assigned to Dtdef if
this limit is reached during a Frost
Accumulation test and the heat pump
has not completed a defrost cycle.
Dtmax = maximum time between defrosts as
allowed by the controls (in hours) or 12,
whichever is less, as provided in the
installation manuals included with the
unit by the manufacturer.
b. For two-capacity heat pumps and for
section 3.6.2 units, evaluate the above
equation using the Dtdef that applies based on
the Frost Accumulation Test conducted at
high capacity and/or at the Heating Full-load
Air Volume Rate. For variable-speed heat
pumps, evaluate Dtdef based on the required
Frost Accumulation Test conducted at the
intermediate compressor speed.
3.10 Test procedures for steady-state Low
Temperature heating mode tests (the H3, H32,
H31 and H42 Tests).
Except for the modifications noted in this
section, conduct the Low Temperature
heating mode test using the same approach
as specified in section 3.7 for the Maximum
and High Temperature tests. After satisfying
the section 3.7 requirements for the pretest
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Ô
where Vs is the average indoor air volume
rate measured during the Frost Accumulation
heating mode test and is expressed in units
of cubic feet per minute of standard air
(scfm).
c. For heat pumps having a constant-airvolume-rate indoor blower, the five
additional steps listed below are required if
the average of the external static pressures
measured during sub-Interval H exceeds the
applicable section 3.1.4.4, 3.1.4.5, or 3.1.4.6
minimum (or targeted) external static
pressure (DPmin) by 0.03 inches of water or
more:
tkelley on DSK3SPTVN1PROD with PROPOSALS2
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interval but before beginning to collect data
˙
˙
to determine Qhk(17) and Ehk(17), conduct a
defrost cycle. This defrost cycle may be
manually or automatically initiated. The
defrost sequence must be terminated by the
action of the heat pump’s defrost controls.
Begin the 30-minute data collection interval
˙
described in section 3.7, from which Qhk(17)
˙
and Ehk(17) are determined, no sooner than
10 minutes after defrost termination. Defrosts
should be prevented over the 30-minute data
collection interval. Defrost cycle is not
required for H42 Test.
3.11 Additional requirements for the
secondary test methods.
3.11.1 If using the Outdoor Air Enthalpy
Method as the secondary test method.
During the ‘‘official’’ test, the outdoor airside test apparatus described in section
2.10.1 is connected to the outdoor unit. To
help compensate for any effect that the
addition of this test apparatus may have on
the unit’s performance, conduct a
‘‘preliminary’’ test where the outdoor air-side
test apparatus is disconnected. Conduct a
preliminary test prior to the first section 3.2
steady-state cooling mode test and prior to
the first section 3.6 steady-state heating mode
test. No other preliminary tests are required
so long as the unit operates the outdoor fan
during all cooling mode steady-state tests at
the same speed and all heating mode steadystate tests at the same speed. If using more
than one outdoor fan speed for the cooling
mode steady-state tests, however, conduct a
preliminary test prior to each cooling mode
test where a different fan speed is first used.
This same requirement applies for the
heating mode tests.
3.11.1.1 If a preliminary test precedes the
official test.
a. The test conditions for the preliminary
test are the same as specified for the official
test. Connect the indoor air-side test
apparatus to the indoor coil; disconnect the
outdoor air-side test apparatus. Allow the test
room reconditioning apparatus and the unit
being tested to operate for at least one hour.
After attaining equilibrium conditions,
measure the following quantities at equal
intervals that span 5 minutes or less:
1. The section 2.10.1 evaporator and
condenser temperatures or pressures;
2. Parameters required according to the
Indoor Air Enthalpy Method.
Continue these measurements until a 30minute period (e.g., four consecutive 10minute samples) is obtained where the Table
8 or Table 15, whichever applies, test
tolerances are satisfied.
b. After collecting 30 minutes of steadystate data, reconnect the outdoor air-side test
apparatus to the unit. Adjust the exhaust fan
of the outdoor airflow measuring apparatus
until averages for the evaporator and
condenser temperatures, or the saturated
temperatures corresponding to the measured
pressures, agree within ±0.5 °F of the
averages achieved when the outdoor air-side
test apparatus was disconnected. Calculate
the averages for the reconnected case using
five or more consecutive readings taken at
one minute intervals. Make these consecutive
readings after re-establishing equilibrium
conditions and before initiating the official
test.
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3.11.1.2 If a preliminary test does not
precede the official test.
Connect the outdoor-side test apparatus to
the unit. Adjust the exhaust fan of the
outdoor airflow measuring apparatus to
achieve the same external static pressure as
measured during the prior preliminary test
conducted with the unit operating in the
same cooling or heating mode at the same
outdoor fan speed.
3.11.1.3 Official test.
a. Continue (preliminary test was
conducted) or begin (no preliminary test) the
official test by making measurements for both
the Indoor and Outdoor Air Enthalpy
Methods at equal intervals that span 5
minutes or less. Discontinue these
measurements only after obtaining a 30minute period where the specified test
condition and test operating tolerances are
satisfied. To constitute a valid official test:
(1) Achieve the energy balance specified in
section 3.1.1; and,
(2) For cases where a preliminary test is
conducted, the capacities determined using
the Indoor Air Enthalpy Method from the
official and preliminary test periods must
agree within 2.0 percent.
b. For space cooling tests, calculate
capacity from the outdoor air-enthalpy
measurements as specified in sections 7.3.3.2
and 7.3.3.3 of ASHRAE Standard 37–2009.
Calculate heating capacity based on outdoor
air-enthalpy measurements as specified in
sections 7.3.4.2 and 7.3.3.4.3 of the same
ASHRAE Standard. Adjust the outdoor-side
capacity according to section 7.3.3.4 of
ASHRAE Standard 37–2009 to account for
line losses when testing split systems. Use
the outdoor unit fan power as measured
during the official test and not the value
measured during the preliminary test, as
described in section 8.6.2 of ASHRAE
Standard 37–2009, when calculating the
capacity.
3.11.2 If using the Compressor
Calibration Method as the secondary test
method.
a. Conduct separate calibration tests using
a calorimeter to determine the refrigerant
flow rate. Or for cases where the superheat
of the refrigerant leaving the evaporator is
less than 5 °F, use the calorimeter to measure
total capacity rather than refrigerant flow
rate. Conduct these calibration tests at the
same test conditions as specified for the tests
in this appendix. Operate the unit for at least
one hour or until obtaining equilibrium
conditions before collecting data that will be
used in determining the average refrigerant
flow rate or total capacity. Sample the data
at equal intervals that span 5 minutes or less.
Determine average flow rate or average
capacity from data sampled over a 30-minute
period where the Table 8 (cooling) or the
Table 15 (heating) tolerances are satisfied.
Otherwise, conduct the calibration tests
according to sections 5, 6, 7, and 8 of
ASHRAE Standard 23.1–2010; sections 5, 6,
7, 8, 9, and 11 of ASHRAE Standard 41.9–
2011; and section 7.4 of ASHRAE Standard
37–2009 (incorporated by reference, see
§ 430.3).
b. Calculate space cooling and space
heating capacities using the compressor
calibration method measurements as
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specified in section 7.4.5 and 7.4.6
respectively, of ASHRAE Standard 37–2009.
3.11.3 If using the Refrigerant-Enthalpy
Method as the secondary test method.
Conduct this secondary method according
to section 7.5 of ASHRAE Standard 37–2009.
Calculate space cooling and heating
capacities using the refrigerant-enthalpy
method measurements as specified in
sections 7.5.4 and 7.5.5, respectively, of the
same ASHRAE Standard.
3.12 Rounding of space conditioning
capacities for reporting purposes.
a. When reporting rated capacities, round
them off as specified in 10 CFR 430.23 (for
a single unit) and in 10 CFR 429.16 (for a
sample).
b. For the capacities used to perform the
section 4 calculations, however, round only
to the nearest integer.
3.13 Laboratory testing to determine off
mode average power ratings.
Conduct one of the following tests after the
completion of the B, B1, or B2 Test,
whichever comes last: If the central air
conditioner or heat pump lacks a compressor
crankcase heater, perform the test in section
3.13.1; if the central air conditioner or heat
pump has compressor crankcase heater that
lacks controls, perform the test in section
3.13.1; if the central air conditioner or heat
pump has a compressor crankcase heater
equipped with controls, perform the test in
section 3.13.2.
3.13.1 This test determines the off mode
average power rating for central air
conditioners and heat pumps that lack a
compressor crankcase heater, or have a
compressor crankcase heater that lacks
controls.
a. Configure Controls: Configure the
controls of the central air conditioner or heat
pump so that it operates as if connected to
a building thermostat that is set to the OFF
position. This particular test contains no
requirements as to ambient conditions within
the test rooms, and room conditions are
allowed to change during the test. Ensure
that the low-voltage transformer and lowvoltage components are connected.
b. Measure P1x: Determine the average
power from non-zero value data measured
over a 5-minute interval of the non-operating
central air conditioner or heat pump and
designate the average power as P1x, the
shoulder season total off mode power.
c. Measure Px for coil-only split systems
(that would be installed in the field with a
furnace having a dedicated board for indoor
controls) and for blower-coil split systems for
which a furnace is the designated air mover:
Disconnect all low-voltage wiring for the
outdoor components and outdoor controls
from the low-voltage transformer. Determine
the average power from non-zero value data
measured over a 5-minute interval of the
power supplied to the (remaining) lowvoltage components of the central air
conditioner or heat pump, or low-voltage
power, Px.
d. Calculate P1:
Single-package systems and blower coil
split systems for which the designated air
mover is not a furnace: Divide the shoulder
season total off mode power (P1x) by the
number of compressors to calculate P1, the
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69431
and record as both P1 and P2, the latter of
which is the heating season per-compressor
off mode power. The expression for
calculating P1 is as follows:
3.13.2 This test determines the off mode
average power rating for central air
conditioners and heat pumps that have a
compressor crankcase heater equipped with
controls.
a. Configure Controls: Position a
temperature sensor to measure the outdoor
dry-bulb temperature in the air between 2
and 6 inches from the crankcase heater
temperature sensor or, if no such temperature
sensor exists, position it in the air between
2 and 6 inches from the crankcase heater.
Utilize the temperature measurements from
this sensor for this portion of the test
procedure. Configure the controls of the
central air conditioner or heat pump so that
it operates as if connected to a building
thermostat that is set to the OFF position.
Ensure that the low-voltage transformer and
low-voltage components are connected.
Adjust the outdoor temperature at a rate of
change of no more than 20 °F per hour and
achieve an outdoor dry-bulb temperature of
72 °F. Maintain this temperature within ±2 °F
for at least 5 minutes, while maintaining an
indoor dry-bulb temperature of between 75
°F and 85 °F.
b. Measure P1x: Determine the average
power from non-zero value data measured
over a 5-minute interval of the non-operating
central air conditioner or heat pump and
designate the average power as P1x, the
shoulder season total off mode power.
c. Reconfigure Controls: In the process of
reaching the target outdoor dry-bulb
temperature, adjust the outdoor temperature
at a rate of change of no more than 20 °F per
hour. This target temperature is the
temperature specified by the manufacturer in
the DOE Compliance Certification Database
at which the crankcase heater turns on,
minus five degrees Fahrenheit. Maintain this
temperature within ±2 °F for at least 5
minutes, while maintaining an indoor drybulb temperature of between 75 °F and 85 °F.
d. Measure P2x: Determine the average nonzero power of the non-operating central air
conditioner or heat pump over a 5-minute
interval and designate it as P2x, the heating
season total off mode power.
e. Measure Px for coil-only split systems
(that would be installed in the field with a
furnace having a dedicated board for indoor
controls) and for blower-coil split systems for
which a furnace is the designated air mover:
Disconnect all low-voltage wiring for the
outdoor components and outdoor controls
from the low-voltage transformer. Determine
the average power from non-zero value data
measured over a 5-minute interval of the
power supplied to the (remaining) lowvoltage components of the central air
conditioner or heat pump, or low-voltage
power, Px
f. Calculate P1:
Single-package systems and blower coil
split systems for which the air mover is not
a furnace: Divide the shoulder season total
off mode power (P1x) by the number of
compressors to calculate P1, the shoulder
season per-compressor off mode power.
Round to the nearest watt. If the compressor
is a modulating-type, assign a value of 1.5 for
the number of compressors. The expression
for calculating P1 is as follows:
Coil-only split systems (that would be
installed in the field with a furnace having
a dedicated board for indoor controls) and
blower-coil split systems for which a furnace
is the designated air mover: Subtract the low-
voltage power (Px) from the shoulder season
total off mode power (P1x) and divide by the
number of compressors to calculate P1, the
shoulder season per-compressor off mode
power. Round to the nearest watt. If the
compressor is a modulating-type, assign a
value of 1.5 for the number of compressors.
The expression for calculating P1 is as
follows:
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total off mode power (P1x) and divide by the
number of compressors to calculate P1, the
shoulder season per-compressor off mode
power. If the compressor is a modulatingtype, assign a value of 1.5 for the number of
compressors. Round P1 to the nearest watt
EP09NO15.259</GPH>
off mode power. The expression for
calculating P1 is as follows:
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compressors. Round P1 to the nearest watt
and record as both P1 and P2, the latter of
which is the heating season per-compressor
Coil-only split systems (that would be
installed in the field with a furnace having
a dedicated board for indoor controls) and
blower-coil split systems for which a furnace
is the designated air mover: Subtract the lowvoltage power (Px) from the shoulder season
tkelley on DSK3SPTVN1PROD with PROPOSALS2
shoulder season per-compressor off mode
power. If the compressor is a modulatingtype, assign a value of 1.5 for the number of
69432
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
is a modulating-type, assign a value of 1.5 for
the number of compressors. The expression
for calculating P2 is as follows:
voltage power (Px) from the heating season
total off mode power (P2x) and divide by the
number of compressors to calculate P2, the
heating season per-compressor off mode
power. Round to the nearest watt. If the
compressor is a modulating-type, assign a
value of 1.5 for the number of compressors.
The expression for calculating P2 is as
follows:
4. Calculations of Seasonal Performance
Descriptors
4.1 Seasonal Energy Efficiency Ratio
(SEER) Calculations. SEER must be
calculated as follows: For equipment covered
under sections 4.1.2, 4.1.3, and 4.1.4,
evaluate the seasonal energy efficiency ratio,
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mode power (P2x) by the number of
compressors to calculate P2, the heating
season per-compressor off mode power.
Round to the nearest watt. If the compressor
Coil-only split systems (that would be
installed in the field with a furnace having
a dedicated board for indoor controls) and
blower-coil split systems for which a furnace
is the designated air mover: Subtract the low-
tkelley on DSK3SPTVN1PROD with PROPOSALS2
h. Calculate P2:
Single-package systems and blower coil
split systems for which the air mover is not
a furnace: Divide the heating season total off
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The temperatures 95 °F and 65 °F in the
building load equation represent the selected
outdoor design temperature and the zero-load
base temperature, respectively.
4.1.1 SEER calculations for an air
conditioner or heat pump having a singlespeed compressor that was tested with a
fixed-speed indoor blower installed, a
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constant-air-volume-rate indoor blower
installed, or with no indoor blower installed.
a. Evaluate the seasonal energy efficiency
ratio, expressed in units of Btu/watt-hour,
using:
SEER = PLF (0.5) * EERB
Where,
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tkelley on DSK3SPTVN1PROD with PROPOSALS2
where,
˙
Qck=2(95) = the space cooling capacity
determined from the A2 Test and
calculated as specified in section 3.3,
Btu/h.
1.1 = sizing factor, dimensionless.
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PLF(0.5) = 1 ¥ 0.5 · CDc, the part-load
performance factor evaluated at a cooling
load factor of 0.5, dimensionless.
b. Refer to section 3.3 regarding the
˙
definition and calculation of Qc(82) and
˙
Ec(82).
4.1.2 SEER calculations for an air
conditioner or heat pump having a singlespeed compressor and a variable-speed
variable-air-volume-rate indoor blower.
4.1.2.1 Units covered by section 3.2.2.1
where indoor blower capacity modulation
correlates with the outdoor dry bulb
˙
Qc(Tj) = the space cooling capacity of the test
unit when operating at outdoor
temperature, Tj, Btu/h.
nj/N = fractional bin hours for the cooling
season; the ratio of the number of hours
during the cooling season when the
outdoor temperature fell within the
range represented by bin temperature Tj
to the total number of hours in the
cooling season, dimensionless.
temperature. The manufacturer must provide
information on how the indoor air volume
rate or the indoor blower speed varies over
the outdoor temperature range of 67 °F to 102
°F. Calculate SEER using Equation 4.1–1.
Evaluate the quantity qc(Tj)/N in Equation
4.1–1 using,
a. For the space cooling season, assign nj/
N as specified in Table 18. Use Equation 4.1–
2 to calculate the building load, BL(Tj).
˙
Evaluate Qc(Tj) using,
of air volume rates rather than fan speeds.
Refer to sections 3.2.2.1, 3.1.4 to 3.1.4.2, and
3.3 regarding the definitions and calculations
˙
˙
˙
of Qck=1(82), Qck=1(95), Qc k=2(82), and
˙
Qck=2(95).
Where,
PLFj = 1 ¥ CDc · [1 ¥ X(Tj)], the part load
factor, dimensionless.
˙
Ec(Tj) = the electrical power consumption of
the test unit when operating at outdoor
temperature Tj, W.
c. The quantities X(Tj) and nj/N are the
same quantities as used in Equation 4.1.2–1.
˙
d. Evaluate Ec(Tj) using,
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09NOP2
EP09NO15.266</GPH>
denotes the fan speed used during the
required A2 and B2 Tests, and FPc(Tj) denotes
the fan speed used by the unit when the
outdoor temperature equals Tj. For units
where indoor air volume rate is the primary
control variable, the three FPc’s are similarly
defined only now being expressed in terms
EP09NO15.264</GPH> EP09NO15.265</GPH>
tkelley on DSK3SPTVN1PROD with PROPOSALS2
the space cooling capacity of the test unit at
outdoor temperature Tj if operated at the
Cooling Full-load Air Volume Rate, Btu/h.
b. For units where indoor blower speed is
the primary control variable, FPck=1 denotes
the fan speed used during the required A1
and B1 Tests (see section 3.2.2.1), FPck=2
EP09NO15.267</GPH>
the space cooling capacity of the test unit at
outdoor temperature Tj if operated at the
Cooling Minimum Air Volume Rate, Btu/h.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69435
˙
consumption, Eck=2(Tj), of the test unit when
operating at high compressor capacity and
outdoor temperature Tj using,
˙
˙
where Qck=2(95) and Eck=2(95) are determined
˙
˙
from the A2 Test, Qck=2(82), and Eck=2(82), are
determined from the B2Test, and all are
calculated as specified in section 3.3.
The calculation of Equation 4.1–1
quantities qc(Tj)/N and ec(Tj)/N differs
depending on whether the test unit would
operate at low capacity (section 4.1.3.1),
cycle between low and high capacity (section
4.1.3.2), or operate at high capacity (sections
4.1.3.3 and 4.1.3.4) in responding to the
building load. For units that lock out low
capacity operation at higher outdoor
temperatures, the manufacturer must supply
information regarding this temperature so
that the appropriate equations are used. Use
Equation 4.1–2 to calculate the building load,
BL(Tj), for each temperature bin.
4.1.3.1 Steady-state space cooling
capacity at low compressor capacity is
greater than or equal to the building cooling
˙
load at temperature Tj, Qck=1(Tj) ≥BL(Tj).
Where,
˙
Xk=1(Tj) = BL(Tj)/Qck=1(Tj), the cooling mode
low capacity load factor for temperature
bin j, dimensionless.
PLFj = 1 ¥ CDc · [1 ¥ Xk=1(Tj)], the part load
factor, dimensionless.
nj/N, the fractional bin hours for the cooling
season; the ratio of the number of hours
during the cooling season when the
outdoor temperature fell within the
range represented by bin temperature Tj
to the total number of hours in the
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cooling season, dimensionless. Obtain
the fractional bin hours for the cooling
season, nj/N, from Table 18. Use
Equations 4.1.3–1 and 4.1.3–2,
˙
respectively, to evaluate Qck=1(Tj) and
˙
Eck=1(Tj).
E:\FR\FM\09NOP2.SGM
09NOP2
EP09NO15.501</GPH>
quantities are calculated as specified in
section 3.3. Evaluate the space cooling
˙
capacity, Qck=2(Tj), and electrical power
EP09NO15.270</GPH>
4.1.3 SEER calculations for an air
conditioner or heat pump having a twocapacity compressor. Calculate SEER using
Equation 4.1–1. Evaluate the space cooling
˙
capacity, Qck=1(Tj), and electrical power
˙
consumption, Eck=1(Tj), of the test unit when
operating at low compressor capacity and
outdoor temperature Tj using,
EP09NO15.268</GPH> EP09NO15.269</GPH>
regarding the definitions and calculations of
˙
˙
˙
˙
Eck=1(82), Eck=1(95), Eck=2(82), and Eck=2(95).
4.1.2.2 Units covered by section 3.2.2.2
where indoor blower capacity modulation is
used to adjust the sensible to total cooling
capacity ratio. Calculate SEER as specified in
section 4.1.1.
˙
˙
where Qck=1(82) and Eck=1(82) are determined
˙
˙
from the B1 Test, Qck=1(67) and Eck=1(67) are
determined from the F1Test, and all four
tkelley on DSK3SPTVN1PROD with PROPOSALS2
the electrical power consumption of the test
unit at outdoor temperature Tj if operated at
the Cooling Full-load Air Volume Rate, W.
e. The parameters FPck=1, and FPck=2, and
FPc(Tj) are the same quantities that are used
when evaluating Equation 4.1.2–2. Refer to
sections 3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3
69436
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
TABLE 18—DISTRIBUTION OF FRACTIONAL HOURS WITHIN COOLING SEASON TEMPERATURE BINS
Bin temperature range °F
Bin number, j
1
2
3
4
5
6
7
8
...................................................................................................................................................
...................................................................................................................................................
...................................................................................................................................................
...................................................................................................................................................
...................................................................................................................................................
...................................................................................................................................................
...................................................................................................................................................
...................................................................................................................................................
Representative
temperature
for bin °F
Fraction of of
total temperature bin hours,
nj/N
67
72
77
82
87
92
97
102
0.214
0.231
0.216
0.161
0.104
0.052
0.018
0.004
65–69
70–74
75–79
80–84
85–89
90–94
95–99
100–104
the building cooling load at temperature Tj,
˙
˙
Qck=1(Tj) <BL(Tj) <Qck=2(Tj).
Xk=2(Tj) = 1 ¥ Xk=1(Tj), the cooling mode,
high capacity load factor for temperature
bin j, dimensionless.
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 18. Use
Equations 4.1.3–1 and 4.1.3–2, respectively,
˙
˙
to evaluate Qck=1(Tj) and Eck=1(Tj). Use
Equations 4.1.3–3 and 4.1.3–4, respectively,
˙
˙
to evaluate Qck=2(Tj) and Eck=2(Tj).
4.1.3.3 Unit only operates at high (k=2)
compressor capacity at temperature Tj and its
capacity is greater than the building cooling
˙
load, BL(Tj) <Qck=2(Tj). This section applies
to units that lock out low compressor
capacity operation at higher outdoor
temperatures.
where,
˙
Xk=2(Tj) = BL(Tj)/Qck=2(Tj), the cooling mode
high capacity load factor for temperature
bin j, dimensionless.
˙
PLFj = 1¥CD(k=2) * [1¥Xk=2(Tj)], the part
load factor, dimensionless.
EP09NO15.273</GPH>
4.1.3.4 Unit must operate continuously at
high (k=2) compressor capacity at
˙
temperature Tj, BL(Tj) ≥Qck=2(Tj).
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09NOP2
EP09NO15.271</GPH> EP09NO15.272</GPH>
tkelley on DSK3SPTVN1PROD with PROPOSALS2
EP09NO15.274</GPH>
4.1.3.2 Unit alternates between high (k=2)
and low (k=1) compressor capacity to satisfy
˙
capacity, Qck=1(Tj), and electrical power
˙
consumption, Eck=1(Tj), of the test unit when
operating at minimum compressor speed and
outdoor temperature Tj. Use,
operating at maximum compressor speed and
outdoor temperature Tj. Use Equations 4.1.3–
˙
3 and 4.1.3–4, respectively, where Qck=2(95)
˙
and Eck=2(95) are determined from the A2
˙
˙
Test, Qck=2(82) and Eck=2(82) are determined
from the B2 Test, and all four quantities are
calculated as specified in section 3.3.
Calculate the space cooling capacity,
˙
Qck=v(Tj), and electrical power consumption,
˙
Eck=v(Tj), of the test unit when operating at
outdoor temperature Tj and the intermediate
compressor speed used during the section
3.2.4 (and Table 7) EV Test using,
4.1.4.1 Steady-state space cooling
capacity when operating at minimum
compressor speed is greater than or equal to
the building cooling load at temperature Tj,
˙
Qck=1(Tj) ≥BL(Tj).
where,
˙
Xk=1(Tj) = BL(Tj)/Qck=1(Tj), the cooling mode
minimum speed load factor for
temperature bin j, dimensionless.
PLFj = 1 ¥ CDc · [1 ¥ Xk=1(Tj)], the part load
factor, dimensionless.
nj/N, the fractional bin hours for the cooling
season; the ratio of the number of hours
during the cooling season when the
outdoor temperature fell within the
range represented by bin temperature Tj
to the total number of hours in the
cooling season, dimensionless.
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 18. Use
Equations 4.1.3–1 and 4.1.3–2, respectively,
˙
˙
to evaluate Qck=l (Tj) and Eck=l (Tj).
4.1.4.2 Unit operates at an intermediate
compressor speed (k=i) in order to match the
building cooling load at temperature
˙
˙
Tj,Qck=1(Tj) <BL(Tj) <Qck=2(Tj).
where,
˙
Qck=i(Tj) = BL(Tj), the space cooling capacity
delivered by the unit in matching the
building load at temperature Tj, Btu/h.
The matching occurs with the unit
operating at compressor speed k = i.
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 18. For each
EP09NO15.276</GPH>
EP09NO15.278</GPH>
4.1.4 SEER calculations for an air
conditioner or heat pump having a variablespeed compressor. Calculate SEER using
Equation 4.1–1. Evaluate the space cooling
˙
˙
where Qck=1(82) and Eck=1(82) are determined
˙
˙
from the B1 Test, Qck=1(67) and Eck=1(67) are
determined from the F1 Test, and all four
quantities are calculated as specified in
section 3.3. Evaluate the space cooling
˙
capacity, Qck=2(Tj), and electrical power
˙
consumption, Eck=2(Tj), of the test unit when
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 18. Use
Equations 4.1.3–3 and 4.1.3–4, respectively,
˙
˙
to evaluate Qck=2(Tj) and Eck=2(Tj).
EP09NO15.277</GPH>
69437
EP09NO15.502</GPH> EP09NO15.275</GPH>
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
EERk=i(Tj) = the steady-state energy efficiency
ratio of the test unit when operating at
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a compressor speed of k = i and
temperature Tj, Btu/h per W.
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09NOP2
69438
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
Tv = the outdoor temperature at which the
unit, when operating at the intermediate
compressor speed used during the
section 3.2.4 EV Test, provides a space
cooling capacity that is equal to the
˙
building load (Qck=v (Tv) = BL(Tv)), °F.
Determine Tv by equating Equations
4.1.4–1 and 4.1–2 and solving for
outdoor temperature.
T2 = the outdoor temperature at which the
unit, when operating at maximum
compressor speed, provides a space
cooling capacity that is equal to the
˙
building load (Qck=2 (T2) = BL(T2)), °F.
Determine T2 by equating Equations
4.1.3–3 and 4.1–2 and solving for
outdoor temperature.
4.1.4.3 Unit must operate continuously at
maximum (k=2) compressor speed at
˙
temperature Tj, BL(Tj) ≥Qck=2(Tj). Evaluate
the Equation 4.1–1 quantities
as specified in section 4.1.3.4 with the
˙
˙
understanding that Qck=2(Tj) and Eck=2(Tj)
correspond to maximum compressor speed
operation and are derived from the results of
the tests specified in section 3.2.4.
4.1.5 SEER calculations for an air
conditioner or heat pump having a single
indoor unit with multiple blowers. Calculate
SEER using Eq. 4.1–1, where qc(Tj)/N and
ec(Tj)/N are evaluated as specified in
applicable below subsection.
4.1.5.1 For multiple blower systems that
are connected to a lone, single-speed outdoor
unit. a. Calculate the space cooling capacity,
˙
Qck=1 (Tj), and electrical power consumption,
˙
Eck=1 (Tj), of the test unit when operating at
the cooling minimum air volume rate and
outdoor temperature Tj using the equations
given in section 4.1.2.1. Calculate the space
˙
cooling capacity, Qck=2 (Tj), and electrical
˙
power consumption, Eck=2 (Tj), of the test unit
when operating at the cooling full-load air
volume rate and outdoor temperature Tj
using the equations given in section 4.1.2.1.
In evaluating the section 4.1.2.1 equations,
˙
˙
determine the quantities Qck=1 (82) and Eck=1
˙
˙
(82) from the B1 Test, Qck=1 (95) and Eck=1
˙
˙
(95) from the Al Test, Qck=2 (82) and Eck=2
˙
(82) from the B2 Test, and Qck=2 (95) and
˙
Eck=2 (95) from the A2 Test. Evaluate all eight
quantities as specified in section 3.3. Refer to
section 3.2.2.1 and Table 5 for additional
information on the four referenced laboratory
tests. b. Determine the cooling mode cyclic
degradation coefficient, CDc, as per sections
3.2.2.1 and 3.5 to 3.5.3. Assign this same
value to CDc(K=2). c. Except for using the
˙
˙
˙
above values of Qck=1 (Tj), Eck=1 (Tj), Eck=2 (Tj),
˙
Qck=2 (Tj), CDc, and CDc (K=2), calculate the
quantities qc(Tj)/N and ec(Tj)/N as specified
˙
in section 4.1.3.1 for cases where Qck=1 (Tj)
≥ BL(Tj). For all other outdoor bin
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temperatures, Tj, calculate qc(Tj)/N and
˙
ec(Tj)/N as specified in section 4.1.3.3 if Qck=2
(Tj) > BL (Tj) or as specified in section 4.1.3.4
˙
if Qck=2 (Tj) ≤ BL(Tj).
4.1.5.2 For multiple blower systems that
are connected to either a lone outdoor unit
having a two-capacity compressor or to two
separate but identical model single-speed
outdoor units. Calculate the quantities qc(Tj)/
N and ec(Tj)/N as specified in section 4.1.3.
4.2 Heating Seasonal Performance Factor
(HSPF) Calculations.
Unless an approved alternative efficiency
determination method is used, as set forth in
10 CFR 429.70(e), HSPF must be calculated
as follows: Six generalized climatic regions
are depicted in Figure 1 and otherwise
defined in Table 19. For each of these regions
and for each applicable standardized design
heating requirement, evaluate the heating
seasonal performance factor using,
E:\FR\FM\09NOP2.SGM
09NOP2
EP09NO15.281</GPH>
For each unit, determine the coefficients A,
B, and C by conducting the following
calculations once:
EP09NO15.279</GPH> EP09NO15.280</GPH>
EERk=i(Tj) = A + B · Tj + C · Tj2.
where,
T1 = the outdoor temperature at which the
unit, when operating at minimum
compressor speed, provides a space
cooling capacity that is equal to the
˙
building load (Qck=l (Tl) = BL(T1)), °F.
Determine T1 by equating Equations
4.1.3–1 and 4.1–2 and solving for
outdoor temperature.
tkelley on DSK3SPTVN1PROD with PROPOSALS2
temperature bin where the unit operates at an
intermediate compressor speed, determine
the energy efficiency ratio EERk=i(Tj) using,
69439
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
Where,
eh(Tj)/N, the ratio of the electrical energy
consumed by the heat pump during
periods of the space heating season when
the outdoor temperature fell within the
range represented by bin temperature Tj
to the total number of hours in the
heating season (N), W. For heat pumps
having a heat comfort controller, this
ratio may also include electrical energy
used by resistive elements to maintain a
minimum air delivery temperature (see
4.2.5).
RH(Tj)/N, the ratio of the electrical energy
used for resistive space heating during
periods when the outdoor temperature
fell within the range represented by bin
temperature Tj to the total number of
hours in the heating season (N), W.
Except as noted in section 4.2.5, resistive
space heating is modeled as being used
to meet that portion of the building load
that the heat pump does not meet
because of insufficient capacity or
because the heat pump automatically
turns off at the lowest outdoor
temperatures. For heat pumps having a
heat comfort controller, all or part of the
electrical energy used by resistive
heaters at a particular bin temperature
may be reflected in eh(Tj)/N (see 4.2.5).
Tj, the outdoor bin temperature, °F. Outdoor
temperatures are ‘‘binned’’ such that
calculations are only performed based
one temperature within the bin. Bins of
5 °F are used.
nj/N, the fractional bin hours for the heating
season; the ratio of the number of hours
during the heating season when the
outdoor temperature fell within the
range represented by bin temperature Tj
to the total number of hours in the
heating season, dimensionless.
Obtain nj/N values from Table 19.
j, the bin number, dimensionless.
J, for each generalized climatic region, the
total number of temperature bins,
dimensionless. Referring to Table 19, J is
the highest bin number (j) having a
nonzero entry for the fractional bin hours
for the generalized climatic region of
interest.
Fdef, the demand defrost credit described in
section 3.9.2, dimensionless.
BL(Tj), the building space conditioning load
corresponding to an outdoor temperature
of
Tj; the heating season building load also
depends on the generalized climatic
region’s outdoor design temperature and
the design heating requirement, Btu/h.
TABLE 19—GENERALIZED CLIMATIC REGION INFORMATION
Region number
I
II
III
Heating Load Hours .........................................................
Outdoor Design Temperature, TOD ..................................
Zero Load Temperature, TZL ...........................................
j Tj (°F) ...........................................................................
562
37
60
909
27
58
1
2
3
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
.291
.239
.194
.129
.081
.041
.019
.005
.001
0
0
0
0
0
0
0
0
0
.215
.189
.163
.143
.112
.088
.056
.024
.008
.002
0
0
0
0
0
0
0
0
62 ................................................................................
57 ................................................................................
52 ................................................................................
47 ................................................................................
42 ................................................................................
37 ................................................................................
32 ................................................................................
27 ................................................................................
22 ................................................................................
17 ..............................................................................
12 ..............................................................................
7 ................................................................................
2 ................................................................................
¥3 ............................................................................
¥8 ............................................................................
¥13 ..........................................................................
¥18 ..........................................................................
¥23 ..........................................................................
IV
V
1,363
1,701
17
5
57
55
Fractional Bin Hours, nj/N
.153
.142
.138
.137
.135
.118
.092
.047
.021
.009
.005
.002
.001
0
0
0
0
0
.132
.111
.103
.093
.100
.109
.126
.087
.055
.036
.026
.013
.006
.002
.001
0
0
0
VI
2,202
¥10
55
1,974 *
30
58
.106
.092
.086
.076
.078
.087
.102
.094
.074
.055
.047
.038
.029
.018
.010
.005
.002
.001
.113
.206
.215
.204
.141
.076
.034
.008
.003
0
0
0
0
0
0
0
0
0
* Pacific Coast Region.
where,
TOD, the outdoor design temperature, °F. An
outdoor design temperature is specified
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for each generalized climatic region in
Table 19.
DHR, the design heating requirement (see
section 1.2, Definitions), Btu/h.
Tzl, the zero load temperature, °F
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Calculate the design heating requirements
for each generalized climatic region as
follows:
For a heat pump that delivers both cooling
and heating,
E:\FR\FM\09NOP2.SGM
09NOP2
EP09NO15.282</GPH> EP09NO15.283</GPH>
tkelley on DSK3SPTVN1PROD with PROPOSALS2
Evaluate the building heating load using
69440
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
Tzl, the zero load temperature, °F
˙
Qck=2(95), the space cooling capacity of the
unit as determined from the A or A2
Test, whichever applies, Btu/h.
where,
C = 1.3, a multiplier to provide the
appropriate slope for the heating load
line, dimensionless.
Tzl, the zero load temperature, °F
˙
Qhk(47), expressed in units of Btu/h and
otherwise defined as follows:
1. For a single-speed heating only heat
˙
pump tested as per section 3.6.1, Qhk(47) =
˙
Qh(47), the space heating capacity
determined from the H1 Test.
2. For a variable-speed heating only heat
pump, a section 3.6.2 single-speed heating
only heat pump, or a two-capacity heating
˙
˙
only heat pump, Qnk(47) = Qnk=2(47), the
space heating capacity determined from the
H12 Test.
For all heat pumps, HSPF accounts for the
heating delivered and the energy consumed
by auxiliary resistive elements when
operating below the balance point. This
condition occurs when the building load
exceeds the space heating capacity of the
heat pump condenser. For HSPF calculations
for all heat pumps, see either section 4.2.1,
4.2.2, 4.2.3, or 4.2.4, whichever applies.
For heat pumps with heat comfort
controllers (see section 1.2, Definitions),
HSPF also accounts for resistive heating
contributed when operating above the heatpump-plus-comfort-controller balance point
as a result of maintaining a minimum supply
temperature. For heat pumps having a heat
comfort controller, see section 4.2.5 for the
additional steps required for calculating the
HSPF.
4.2.1 Additional steps for calculating the
HSPF of a heat pump having a single-speed
compressor that was tested with a fixedspeed indoor blower installed, a constant-airvolume-rate indoor blower installed, or with
no indoor blower installed.
whichever is less; the heating mode load
factor for temperature bin j, dimensionless.
˙
Qh(Tj), the space heating capacity of the heat
pump when operating at outdoor
temperature Tj, Btu/h.
˙
Eh(Tj), the electrical power consumption of
the heat pump when operating at
outdoor temperature Tj, W.
d(Tj), the heat pump low temperature cut-out
factor, dimensionless.
˙
PLFj = 1 ¥ CDh · [1 ¥ X(Tj)], the part load
factor, dimensionless.
Use Equation 4.2–2 to determine BL(Tj).
Obtain fractional bin hours for the heating
season, nj/N, from Table 19.
Determine the low temperature cut-out
factor using
EP09NO15.286</GPH>
EP09NO15.287</GPH>
For a heating-only heat pump,
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where,
C = 1.3, a multiplier to provide the
appropriate slope for the heating load
line, dimensionless.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69441
(If no such temperature exists, Tj is
always greater than Toff and Ton).
Ton, the outdoor temperature when the
compressor is automatically turned back
on, if applicable, following an automatic
shut-off, °F.
˙
˙
Calculate Qh(Tj) and Eh(Tj) using,
where,
˙
˙
Qh(47) and Eh(47) are determined from the H1
Test and calculated as specified in
section 3.7
˙
˙
Qh(35) and Eh(35) are determined from the H2
Test and calculated as specified in
section 3.9.1
˙
˙
Qh(17) and Eh(17) are determined from the H3
Test and calculated as specified in
section 3.10.
4.2.2 Additional steps for calculating the
HSPF of a heat pump having a single-speed
compressor and a variable-speed, variableair-volume-rate indoor blower. The
manufacturer must provide information
about how the indoor air volume rate or the
indoor blower speed varies over the outdoor
temperature range of 65 °F to ¥23 °F.
Calculate the quantities
in Equation 4.2–1 as specified in section
4.2.1 with the exception of replacing
references to the H1C Test and section 3.6.1
with the H1C1 Test and section 3.6.2. In
addition, evaluate the space heating capacity
and electrical power consumption of the heat
˙
˙
pump Qh(Tj) and Eh(Tj) using
where the space heating capacity and
electrical power consumption at both low
capacity
(k=1) and high capacity (k=2) at outdoor
temperature Tj are determined using
For units where indoor blower speed is the
primary control variable, FPhk=1 denotes the
fan speed used during the required H11 and
H31 Tests (see Table 11), FPhk=2 denotes the
fan speed used during the required H12, H22,
and H32 Tests, and FPh(Tj) denotes the fan
speed used by the unit when the outdoor
temperature equals Tj. For units where indoor
air volume rate is the primary control
variable, the three FPh’s are similarly defined
only now being expressed in terms of air
volume rates rather than fan speeds.
˙
˙
Determine Qhk=1(47) and Ehk=1(47) from the
˙
˙
H11 Test, and Qhk=2(47) and Ehk=2(47) from
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the H12 Test. Calculate all four quantities as
˙
specified in section 3.7. Determine Qhk=1(35)
˙
and Ehk=1(35) as specified in section 3.6.2;
˙
˙
determine Qhk=2(35) and Ehk=2(35) and from
the H22 Test and the calculation specified in
˙
˙
section 3.9. Determine Qhk=1(17) and Ehk=1(17
˙
from the H31 Test, and Qhk=2(17) and
EP09NO15.288</GPH> EP09NO15.289</GPH>
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where,
Toff, the outdoor temperature when the
compressor is automatically shut off, °F.
69442
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
whether the heat pump would operate at low
capacity (section 4.2.3.1), cycle between low
and high capacity (Section 4.2.3.2), or
operate at high capacity (sections 4.2.3.3 and
4.2.3.4) in responding to the building load.
For heat pumps that lock out low capacity
a. Evaluate the space heating capacity and
electrical power consumption of the heat
pump when operating at low compressor
capacity and outdoor temperature Tj using
b. Evaluate the space heating capacity and
˙
electrical power consumption (Qhk=2(Tj) and
˙
Ehk=2 (Tj)) of the heat pump when operating
at high compressor capacity and outdoor
temperature Tj by solving Equations 4.2.2–3
and 4.2.2–4, respectively, for k=2. Determine
˙
˙
Qhk=1(62) and Ehk=1(62) from the H01 Test,
˙
˙
Qhk=1(47) and Ehk=1(47) from the H11 Test,
˙
˙
and Qhk=2(47) and Ehk=2(47) from the H12
Test. Calculate all six quantities as specified
˙
in section 3.7. Determine Qhk=2(35) and
˙
Ehk=2(35) from the H22 Test and, if required
as described in section 3.6.3, determine
˙
˙
Qhk=1(35) and Ehk=1(35) from the H21 Test.
Calculate the required 35 °F quantities as
˙
specified in section 3.9. Determine Qhk=2(17)
˙
and Ehk=2(17) from the H32 Test and, if
required as described in section 3.6.3,
˙
˙
determine Qhk=1(17) and Ehk=1(17) from the
H31 Test. Calculate the required 17 °F
quantities as specified in section 3.10.
4.2.3.1 Steady-state space heating
capacity when operating at low compressor
capacity is greater than or equal to the
building heating load at temperature Tj,
˙
Qhk=1(Tj) ≥BL(Tj).
Where,
˙
Xk=1(Tj) = BL(Tj)/Qhk=1(Tj), the heating mode
low capacity load factor for temperature
bin j, dimensionless.
PLFj = 1 ¥ CDh · [ 1 ¥ Xk=1(Tj) ], the part
load factor, dimensionless.
d′(Tj), the low temperature cutoff factor,
dimensionless.
Determine the low temperature cut-out
factor using
Where,
Toff and Ton are defined in section 4.2.1. Use
the calculations given in section 4.2.3.3,
and not the above, if:
(a) The heat pump locks out low capacity
operation at low outdoor temperatures
and
(b) Tj is below this lockout threshold
temperature.
4.2.3.2 Heat pump alternates between
high (k=2) and low (k=1) compressor
capacity to satisfy the building heating load
˙
at a temperature Tj, Qhk=1(Tj) < BL(Tj) <
˙
Qhk=2(Tj).
EP09NO15.295</GPH>
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operation at low outdoor temperatures, the
manufacturer must supply information
regarding the cutoff temperature(s) so that the
appropriate equations can be selected.
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˙
Ehk=2(17) from the H32 Test. Calculate all four
quantities as specified in section 3.10.
4.2.3 Additional steps for calculating the
HSPF of a heat pump having a two-capacity
compressor. The calculation of the Equation
4.2–1 quantities differ depending upon
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69443
Where,
Determine the low temperature cut-out
factor, d′(Tj), using Equation 4.2.3–3.
4.2.3.3 Heat pump only operates at high
(k=2) compressor capacity at temperature Tj
and its capacity is greater than the building
˙
heating load, BL(Tj) < Qhk=2(Tj). This section
applies to units that lock out low compressor
capacity operation at low outdoor
temperatures.
Where,
˙
Xk=2(Tj)= BL(Tj)/Qhk=2(Tj).
PLFj = 1 ¥ C(k = 2) * [1 ¥ Xk=2(Tj)]
Determine the low temperature cut-out
factor, d(Tj), using Equation 4.2.3–3.
4.2.3.4 Heat pump must operate
continuously at high (k=2) compressor
˙
capacity at temperature Tj, BL(Tj) ≥ Qhk=2(Tj).
4.2.4 Additional steps for calculating the
HSPF of a heat pump having a variable-speed
compressor. Calculate HSPF using Equation
4.2–1. Evaluate the space heating capacity,
˙
Qhk=1(Tj), and electrical power consumption,
˙
Ehk=1(Tj), of the heat pump when operating
at minimum compressor speed and outdoor
temperature Tj using
Where,
˙
˙
Qhk=1(62) and Ehk=1(62) are determined from
the H01 Test
˙
˙
Qhk=1(47) and Ehk=1(47) are determined from
the H11Test,
and all four quantities are calculated as
specified in section 3.7.
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Xk=2(Tj) = 1 ¥ Xk=1(Tj) the heating mode,
high capacity load factor for temperature
bin j, dimensionless.
69444
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
˙
˙
Determine Qhk=2(35) and Ehk=2(35) from the
H22 Test and the calculations specified in
section 3.9 or, if the H22 Test is not
conducted, by conducting the calculations
specified in section 3.6.4. Determine
˙
˙
Qhk=2(17) and Ehk=2(17) from the H32 Test
and the calculations specified in section 3.10.
If H42 test is conducted, evaluate the space
˙
heating capacity, Qhk=2(Tj), and electrical
˙
power consumption, Ehk=2(Tj), of the heat
pump when operating at maximum
compressor speed and outdoor temperature
Tj by using the following equation instead of
Equations 4.2.2–3 and 4.2.2–4. Determine the
˙
˙
quantities Qhk=2(Tl) and Ehk=2(Tl) from the
H42 Test and the calculations specified in
section 3.7.
Where Tl is the outdoor temperature where
the H42 test is conducted.
Calculate the space heating capacity,
˙
Qhk=v(Tj), and electrical power consumption,
˙
Ehk=v(Tj), of the heat pump when operating
at outdoor temperature Tj and the
intermediate compressor speed used during
the section 3.6.4 H2V Test using
Where,
˙
˙
Qhk=v(35) and Ehk=v(35) are determined from
the H2V Test and calculated as specified
in section 3.9. Approximate the slopes of
the k=v intermediate speed heating
capacity and electrical power input
curves, MQ and ME, as follows:
Use Equations 4.2.4–1 and 4.2.4–2,
˙
respectively, to calculate Qhk=1(35) and
˙
Ehk=1(35). The calculation of Equation 4.2–1
quantities eh(Tj)/N and RH(Tj)/N differs
depending upon whether the heat pump
would operate at minimum speed (section
4.2.4.1), operate at an intermediate speed
(section 4.2.4.2), or operate at maximum
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speed (section 4.2.4.3) in responding to the
building load.
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Evaluate the space heating capacity,
˙
Qhk=2(Tj), and electrical power consumption,
˙
Ehk=2(Tj), of the heat pump when operating
at maximum compressor speed and outdoor
temperature Tj by solving Equations 4.2.2–3
and 4.2.2–4, respectively, for k=2. Determine
the Equation 4.2.2–3 and 4.2.2–4 quantities
˙
˙
Qhk=2(47) and Ehk=2(47) from the H12 Test
and the calculations specified in section 3.7.
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
compressor speed, provides a space
heating capacity that is equal to the
˙
building load (Qhk=1(T3) = BL(T3)), °F.
Tvh, the outdoor temperature at which the
heat pump, when operating at the
intermediate compressor speed used
during the section 3.6.4 H2V Test,
provides a space heating capacity that is
˙
equal to the building load (Qhk=v(Tvh) =
BL(Tvh)), °F. Determine Tvh by equating
Equations 4.2.4–3 and 4.2–2 and solving
for outdoor temperature.
COPk=i(Tj) = A + B · Tj + C · Tj2.
For each heat pump, determine the
coefficients A, B, and C by conducting the
following calculations once:
Determine T3 by equating Equations
4.2.4–1 and 4.2–2 and solving for
outdoor temperature:
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T4, the outdoor temperature at which the heat
pump, when operating at maximum
compressor speed, provides a space
heating capacity that is equal to the
˙
building load (Qhk=2(T4) = BL(T4)), °F.
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COPk=i(Tj), the steady-state coefficient of
performance of the heat pump when
operating at compressor speed k=i and
temperature Tj, dimensionless.
For each temperature bin where the heat
pump operates at an intermediate compressor
speed, determine COPk=i(Tj) using,
Where,
T3, the outdoor temperature at which the heat
pump, when operating at minimum
tkelley on DSK3SPTVN1PROD with PROPOSALS2
and d(Tj) is evaluated using Equation 4.2.3–
3 while,
˙
Qhk=i(Tj) = BL(Tj), the space heating capacity
delivered by the unit in matching the
building load at temperature (Tj), Btu/h.
The matching occurs with the heat pump
operating at compressor speed k=i.
69445
69446
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
Determine T4 by equating Equations 4.2.2–
3 (k=2) and 4.2–2 and solving for outdoor
temperature.
requirements for calculating COPhk=i(Tj). For
each temperature bin where T3 >Tj >Tvh,
4.2.4.3 Heat pump must operate
continuously at maximum (k=2) compressor
˙
speed at temperature Tj, BL(Tj) ≥Qhk=2(Tj).
Evaluate the Equation 4.2–1 quantities
as specified in section 4.2.3.4 with the
˙
˙
understanding that Qhk=2(Tj) and Ehk=2(Tj)
correspond to maximum compressor speed
operation and are derived from the results of
the specified section 3.6.4 tests. If H42 test is
˙
conducted in place of H12, evaluate Qhk=2(Tj)
˙
and Ehk=2(Tj) using the following equation
instead of equations 4.2.2–3 and 4.2.2–4.
Where, TL is the ambient dry bulb
temperature where H42 test is conducted.
4.2.5 Heat pumps having a heat comfort
controller. Heat pumps having heat comfort
controllers, when set to maintain a typical
minimum air delivery temperature, will
cause the heat pump condenser to operate
less because of a greater contribution from
the resistive elements. With a conventional
heat pump, resistive heating is only initiated
if the heat pump condenser cannot meet the
building load (i.e., is delayed until a second
stage call from the indoor thermostat). With
a heat comfort controller, resistive heating
can occur even though the heat pump
condenser has adequate capacity to meet the
building load (i.e., both on during a first stage
call from the indoor thermostat). As a result,
the outdoor temperature where the heat
pump compressor no longer cycles (i.e., starts
to run continuously), will be lower than if
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For multiple-split heat pumps (only), the
following procedures supersede the above
Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules
69447
the heat pump did not have the heat comfort
controller.
4.2.5.1 Heat pump having a heat comfort
controller: additional steps for calculating the
HSPF of a heat pump having a single-speed
compressor that was tested with a fixedspeed indoor blower installed, a constant-air-
volume-rate indoor blower installed, or with
no indoor blower installed. Calculate the
space heating capacity and electrical power
of the heat pump without the heat comfort
controller being active as specified in section
4.2.1 (Equations 4.2.1–4 and 4.2.1–5) for each
outdoor bin temperature, Tj, that is listed in
Table 19. Denote these capacities and
electrical powers by using the subscript ‘‘hp’’
instead of ‘‘h.’’ Calculate the mass flow rate
(expressed in pounds-mass of dry air per
hour) and the specific heat of the indoor air
(expressed in Btu/lbmda · °F) from the results
of the H1 Test using:
Ô Ô
Where Vs, Vmx, v′n (or vn), and Wn are defined
following Equation 3–1. For each
outdoor bin temperature listed in Table
19, calculate the nominal temperature of
the air leaving the heat pump condenser
coil using,
Case 1. For outdoor bin temperatures
where To(Tj) is equal to or greater than TCC
(the maximum supply temperature
determined according to section 3.1.9),
˙
˙
determine Qh(Tj) and Eh(Tj) as specified in
˙
˙
˙
section 4.2.1 (i.e., Qh(Tj) = Qhp(Tj) and Ehp(Tj)
˙
= Ehp(Tj)). Note: Even though To(Tj) ≥Tcc,
resistive heating may be required; evaluate
Equation 4.2.1–2 for all bins.
Case 2. For outdoor bin temperatures
˙
˙
where To(Tj) >Tcc, determine Qh(Tj) and Eh(Tj)
using,
NOTE: Even though To(Tj) <Tcc, additional
resistive heating may be required; evaluate
Equation 4.2.1–2 for all bins.
4.2.5.2 Heat pump having a heat comfort
controller: Additional steps for calculating
the HSPF of a heat pump having a singlespeed compressor and a variable-speed,
variable-air-volume-rate indoor blower.
Calculate the space heating capacity and
electrical power of the heat pump without
the heat comfort controller being active as
specified in section 4.2.2 (Equations 4.2.2–1
and 4.2.2–2) for each outdoor bin
temperature, Tj, that is listed in Table 19.
Denote these capacities and electrical powers
by using the subscript ‘‘hp’’ instead of ‘‘h.’’
Calculate the mass flow rate (expressed in
pounds-mass of dry air per hour) and the
specific heat of the indoor air (expressed in
Btu/lbmda · °F) from the results of the H12
Test using:
Ô Ô
Where VS, Vmx, v′n (or vn), and Wn are defined
following Equation 3–1. For each
outdoor bin temperature listed in Table
19, calculate the nominal temperature of
the air leaving the heat pump condenser
coil using,
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and electrical power from Case 1 or Case 2,
whichever applies.
Case 1. For outdoor bin temperatures
where To(Tj) is equal to or greater than TCC
(the maximum supply temperature
determined according to section 3.1.9),
˙
˙
determine Qh(Tj) and Eh(Tj) as specified in
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˙
˙
˙
section 4.2.2 (i.e. Qh(Tj) = Qhp(Tj) and Eh(Tj)
˙
=
