Energy Conservation Program for Consumer Products: Test Procedure for Residential Central Air Conditioners and Heat Pumps, 59122-59180 [05-15601]
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Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
10 CFR Part 430
Thomas B. DePriest, Esq., U.S.
Department of Energy, Office of General
Counsel, GC–72, 1000 Independence
Avenue, SW., Washington, DC 20585–
0121, (202) 586–9507, e-mail:
thomas.depriest@hq.doe.gov.
[Docket No. EE–RM/TP–97–440]
SUPPLEMENTARY INFORMATION:
The final
rule incorporates, by reference, into
Subpart B of Part 430 seven test-method
standards published by the American
Society of Heating, Refrigerating, and
Air-Conditioning Engineers, Inc.
(ASHRAE), as follows:
• Standard 23–1993, ‘‘Methods of
Testing for Rating Positive Displacement
Refrigerant Compressors and
Condensing Units;’’
• Standard 37–1988, ‘‘Methods of
Testing for Rating Unitary AirConditioning and Heat Pump
Equipment;’’
• Standard 41.1–1986 (Reaffirmed
2001), ‘‘Standard Method for
Temperature Measurement;’’
• Standard 41.2–1987 (Reaffirmed
1992), ‘‘Standard Methods for
Laboratory Airflow Measurement;’’
• Standard 41.6–1994 (Reaffirmed
2001), ‘‘Standard Method for
Measurement of Moist Air Properties;’’
• Standard 41.9–2000, ‘‘Calorimeter
Test Methods for Mass Flow
Measurements of Volatile Refrigerants;’’
and
• Standard 116–1995, ‘‘Methods of
Testing for Rating for Seasonal
Efficiency of Unitary Air Conditioners
and Heat Pumps.’’
The following joint test-method
standard of ASHRAE and the Air
Movement and Control Association
International, Inc. (ASHRAE/AMCA) is
incorporated by reference into subpart B
of Part 430:
• Standard 51–1999/210–1999,
‘‘Laboratory Methods of Testing Fans for
Aerodynamic Performance Rating.’’
The following test-and-rating standard
of the Air-Conditioning and
Refrigeration Institute (ARI) is
incorporated by reference into Subpart
B of Part 430:
• Standard 210/240–2003, ‘‘Unitary
Air-Conditioning and Air-Source Heat
Pump Equipment.’’
Copies of these standards are
available for public review at the
Department of Energy’s Building
Technologies Program Resource Room
described above. Copies of the
ASHRAE, ASHRAE/AMCA and ARI
Standards are available from the
American Society of Heating,
Refrigerating, and Air-Conditioning
Engineers, Inc., 1971 Tullie Circle, NE.,
Atlanta, GA 30329, https://
www.ashrae.org; the Air Movement and
Control Association International, Inc.,
30 West University Drive, Arlington
Heights, IL 60004–1893, https://
www.amca.org; and the AirConditioning and Refrigeration Institute,
4100 North Fairfax Drive, Suite 200,
Arlington, VA 22203–1629, https://
www.ari.org.
I. Introduction
A. Authority
B. Background
II. Discussion of Comments
A. General Discussion
1. Adopting References Updated Since
Public Hearing
2. Small-Duct, High-Velocity (SDHV)
Systems
3. Non-Defrost Heat Pumps
4. Two-Capacity, Northern Heat Pumps
5. Heat Pumps Having a Heat Comfort
Controller
B. Definitions
C. Testing Conditions
1. Section 2.2.4 Wet-Bulb Temperature
Requirements for Air Entering the Indoor
and Outdoor Coils
2. Section 2.2.5 Additional Refrigerant
Charging Requirements
D. Testing Procedures
1. Section 3.1.4 Airflow Through the
Indoor Coil: Systems Having a VariableSpeed, Constant Airflow Blower
2. Sections 3.1.4.2, 3.1.4.5, 3.3, 3.5.1, 3.7,
and 3.9.1. Testing a Two-Capacity
Compressor System: Coil-Only Units
Tested at Low Capacity and Differences
in High/Low Cycling
III. Summary of Other Additions and
Changes to the DOE Residential Central
Air Conditioner and Heat Pump Test
Procedure
A. Update and Add References for
ASHRAE and ARI Standards
B. Air Volume Rates
C. Cyclic Testing
D. Fanless (Coil-Only) Units
E. Frost Accumulation Test
F. Test Tolerance Tables
G. Pretest Intervals
1. Wet Coil Tests
2. Dry Coil Steady-State Test
3. Dry Coil Cyclic Test
4. Maximum and High Temperature
Heating Mode Tests
5. Heating Mode Cyclic Test
6. Frost Accumulation Test
7. Low Temperature Test
H. Multi-Capacity Systems
1. Two-Capacity Heat Pumps That Lock
Out Low Capacity at Higher Outdoor
Temperatures
2. Systems Having a Single-Speed
Compressor and a Variable-Speed Indoor
Fan Where Fan Speed or Air Volume
Rate Depends on Outdoor Temperature
I. Triple-Split Systems
J. Time-Adaptive Defrost Control Systems
K. Test Unit Installation
L. Test Apparatus and Measurement/
Sampling Frequency
1. Inlet Plenum for Blower Coils
2. Manifolded Static Pressure Taps
3. Temperature Measurement Intervals
4. Temperature Measurement Accuracies
5. Grid of Individual Temperature Sensors
Within the Indoor-Side Outlet Plenum
DEPARTMENT OF ENERGY
Office of Energy Efficiency and
Renewable Energy
RIN 1904–AA46
Energy Conservation Program for
Consumer Products: Test Procedure
for Residential Central Air
Conditioners and Heat Pumps
Office of Energy Efficiency and
Renewable Energy, Department of
Energy.
ACTION: Final rule.
AGENCY:
SUMMARY: The Department of Energy
(DOE, or the Department) amends its
test procedures for residential central air
conditioners and heat pumps. This final
rule adds new sections and revises
several sections of the test procedure to
bring it up-to-date by eliminating the
need for several test procedure waivers
and making it more complete. The
Department also re-organized the test
procedure to be more chronological in
its progression. The revisions to the test
procedure do not alter the minimum
energy conservation standards currently
in effect for central air conditioners and
heat pumps.
DATES: This rule is effective April 10,
2006. The incorporation by reference of
certain publications listed in this rule is
approved by the Director of the Federal
Register as of April 10, 2006.
ADDRESSES: You may review copies of
all materials related to this rulemaking
at the U.S. Department of Energy,
Forrestal Building, Room 1J–018
(Resource Room of the Building
Technologies Program), 1000
Independence Avenue, SW.,
Washington, DC, (202) 586–9127,
between 9 a.m. and 4 p.m., Monday
through Friday, except Federal holidays.
Please call Ms. Brenda Edwards-Jones at
the above telephone number for
additional information regarding
visiting the Resource Room. Please note:
The Department’s Freedom of
Information Reading Room (formerly
Room 1E–190 at the Forrestal Building)
is no longer housing rulemaking
materials.
FOR FURTHER INFORMATION CONTACT:
Michael G. Raymond, U.S. Department
of Energy, Office of Energy Efficiency
and Renewable Energy, EE–2J, 1000
Independence Avenue, SW.,
Washington, DC 20585–0121, (202) 586–
9611, e-mail:
michael.raymond@ee.doe.gov; or
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Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
6. Duct Loss Correction
7. Water Vapor Measurements Using a
Dew-Point Hygrometer, a Relative
Humidity Meter, or Any Other
Alternative Instrument
8. Voltmeter Accuracy
9. Electrical Power Measurement
M. Different Compressor Speeds and
Indoor Fan Capacities Between Cooling
and Heating
N. Secondary Test Requirements
O. Calculations
P. Effect of Test Procedure Revisions on
SEER and HSPF
IV. Procedural Requirements
A. Review Under Executive Order 12866
B. Review Under the Regulatory Flexibility
Act
C. Review Under the Paperwork Reduction
Act
D. Review Under the National
Environmental Policy Act
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 of 1999
I. Review Under Executive Order 12630
J. Review Under the Treasury and General
Government Appropriations Act of 2001
K. Review Under Executive Order 13211
L. Review Under Section 32 of the Federal
Energy Administration Act of 1974
M. Congressional Notification
N. Approval of the Office of the Secretary
procedure. (42 U.S.C. 6293(e)(1)) If DOE
determines that an amended test
procedure would alter the measured
energy efficiency of a covered product,
DOE is required to amend the applicable
energy conservation standard with
respect to such test procedure. In
determining any such amended energy
conservation standard, DOE is required
to measure the energy efficiency or
energy use of a representative sample of
covered products that minimally
comply with the existing standard. The
average efficiency or energy use of these
representative samples, tested using the
amended test procedure, constitutes the
amended standard. (42 U.S.C.
6293(e)(2)) The Department has
determined that today’s amended test
procedure does not alter the measured
efficiency or measured energy use of
central air conditioners and heat pumps.
Beginning 180 days after a test
procedure for a covered product is
prescribed, no manufacturer,
distributor, retailer, or private labeler
may make representations with respect
to the energy use, efficiency, or cost of
energy consumed by such product,
except as reflected in tests conducted
according to the DOE procedure. (42
U.S.C. 6293(c)(2))
I. Introduction
B. Background
On January 22, 2001, the Department
published a Notice of Proposed
Rulemaking (hereafter referred to as the
January 22, 2001, proposed rule) that
proposed a revised test procedure for
central air conditioners and heat pumps.
(66 FR 6768) As summarized in the
January 22, 2001, proposed rule, the
Department initiated several
interactions, including a DOE
workshop, phone conferences, and the
release of multiple drafts for review and
comment between DOE and
stakeholders prior to preparing the
revised test procedure.
Most of the existing test procedure
dates back to its original publication in
the Federal Register on December 27,
1979. (44 FR 76700) The Department
modified the test procedure on March
14, 1988, to cover variable-speed air
conditioners and heat pumps, to address
testing of split-type non-ducted units,
and to change the method used for
crediting heat pumps that provide a
demand defrost capability. (53 FR 8304)
The January 22, 2001, proposed rule
specified dates for holding a public
hearing and for submitting written
comments. At the request of ARI, the
Department changed these specified
dates. (66 FR 15203, March 16, 2001)
Prior to the public hearing and at the
invitation of ARI, a NIST representative
attended a meeting of the ARI Unitary
A. Authority
Part B of Title III of the Energy Policy
and Conservation Act (EPCA or Act) (42
U.S.C. 6291 et seq.), established the
Energy Conservation Program for
Consumer Products Other Than
Automobiles (Program). The products
currently subject to this Program
(‘‘covered products’’) include central air
conditioners and heat pumps, the
subject of today’s final rule.
Under the Act, the Program consists
of three parts: Testing, labeling, and the
Federal energy conservation standards.
The Department, in consultation with
the National Institute of Standards and
Technology (NIST), is authorized to
establish or amend test procedures as
appropriate for each of the covered
products. (42 U.S.C. 6293) The purpose
of the test procedures is to measure
energy efficiency, energy use, or
estimated annual operating cost of a
covered product during a representative,
average use cycle or period of use. The
test procedure must not be unduly
burdensome to conduct. (42 U.S.C.
6293(b)(3))
If a test procedure is amended, DOE
is required to determine to what extent,
if any, the proposed new test procedure
would alter the measured energy
efficiency of any covered product as
determined under the existing test
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Small Equipment Engineering
Committee on February 27, 2001, at ARI
headquarters. The public hearing was
held on March 29, 2001, at DOE
headquarters.1 At the public hearing,
the participants spent the majority of
the time discussing the list of items
from the proposed rulemaking for which
the Department solicited stakeholder
comment. One manufacturer, the Carrier
Corporation, presented a prepared oral
statement. On May 1, 2001, DOE and
NIST personnel met with
representatives of the Carrier
Corporation at DOE headquarters.
During the comment period,
stakeholders, DOE, and NIST held
several phone and e-mail discussions
about issues associated with the
proposed test procedure (a revision of
10 CFR part 430, Subpart B, Appendix
M) and about rating untested splitsystem combinations (a separate test
procedure issue not covered in
Appendix M, but in 10 CFR 430.24(m)).
The issue of rating untested split-system
combinations is not part of this
rulemaking and will be the subject of a
future rulemaking.
II. Discussion of Comments
A. General Discussion
Nine different stakeholders submitted
a total of fourteen comments on the
January 22, 2001, proposed rule.
Concurrent with this rulemaking, the
Department also conducted a
rulemaking to issue new energy
conservation standards for central air
conditioners and heat pumps. Both
rulemakings covered, among other
consumer products, small-duct, highvelocity (SDHV) systems. In the
standards rulemaking (66 FR 7197),
DOE stated that concerns for SDHV
systems had been addressed by
modifying the test procedure for SDHV
products. This test procedure
modification would have given SDHV
systems a higher tested value of the
Seasonal Energy Efficiency Ratio
(SEER). (DOE later rejected this test
procedure modification for reasons
discussed in section II.A.2 of this
preamble). As a result, the Department
considered comments received on
October 18, 2001, from SDHV
manufacturers SpacePak and Unico, Inc.
(Unico) as part of the energy
conservation standards rulemaking in
today’s final rule on the test procedure.
1 The Department held a public workshop on
issues that would not be considered for the current
revision to the test procedure (i.e., alternative rating
method for untested combinations, promoting
devices that compensate for installation problems,
metrification of the DOE test procedure) on the day
immediately following the close of the public
hearing.
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Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
(SpacePak, No. 21, Unico, No. 22) 2 The
Department also considered during this
rulemaking amended comments from
ARI, dated October 30, 2001, that
addressed the SDHV issue. (ARI, No. 20)
A discussion of the comments and the
actions taken in response to them
follows.
1. Adopting References Updated Since
Public Hearing
The January 22, 2001, proposed rule
referenced seven ASHRAE standards, as
well as ASHRAE Standard 51–99/
AMCA Standard 210–99, and ARI
standard 210/240. Since the publication
of the proposed rule, however, two of
these standards have been reaffirmed
and two have been revised. The two
reaffirmed standards are ASHRAE
Standard 41.1–1986 (Reaffirmed 2001)
and ASHRAE Standard 41.6–1994
(Reaffirmed 2001). When a standard is
reaffirmed within ASHRAE, no
substantive changes are permitted to the
document. In the ASHRAE Project
Committee Manual of Procedures,
substantive change is defined as
a change that involves an important (has
value, weight or consequences),
fundamental (is the foundation, without
which it would collapse), or essential
(belongs to the very nature of a thing)
part or changes the meaning of the
material or that directly and materially
affects the use of the standard.
Following are example changes that
may be found substantive when
examined in context;
• ‘‘shall’’ to ‘‘should’’ or ‘‘should’’ to
‘‘shall;’
• addition, deletion or revision of
mandatory requirements, regardless of
the number of changes;
• or addition of mandatory
compliance with referenced standards.
Thus, today’s final rule references
ASHRAE Standards 41.1–1986
(Reaffirmed 2001) and 41.6–1994
(Reaffirmed 2001), whereas the January
22, 2001, proposed rule had referenced
ASHRAE Standards 41.1–1986
(Reaffirmed 1991) and 41.6–1994. These
changes have no effect on the test
procedure itself nor on the reported
energy efficiency ratings of the tested
equipment.
The two revised standards are
ASHRAE Standard 41.9–2000 and ARI
Standard 210/240–2003. A revision of
ASHRAE Standard 41.9, ‘‘Calorimeter
Test Methods for Mass Flow
Measurements of Volatile Refrigerants,’’
2 These comments were received in the course of
the standards rulemaking, Docket Number EE–RM–
98–440, but are relevant to this test procedure
rulemaking. SpacePak’s comments are item 267 in
that docket; Unico’s comments are item 251.
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was published in 2000. The previous
version, Standard 41.9–1988, was
referenced in the proposed rulemaking.
This particular standard is only
referenced in section 3.11.2 of the test
procedure. Section 3.11.2 pertains to
one of three allowed secondary test
methods, the Compressor Calibration
Method. These secondary test methods
do not affect the reported performance
ratings. Instead, these secondary test
methods are used to provide a check of
the primary method, i.e., the Indoor Air
Enthalpy Method. Specifically, the
cooling or heating capacity determined
using the approved primary method and
the user selected secondary test method
must agree within six percent to
constitute a valid test set-up. The
revised version of ASHRAE Standard
41.9 is referenced in today’s test
procedure both because it does not
affect the reported ratings and because
it provides the most current methods for
making refrigerant calorimeter
measurements.
The other revised standard is ARI
Standard 210/240–2003. The main
impetus behind the 2003 revision of ARI
Standard 210/240 was a desire to
narrow the scope of the equipment
covered by the standard. Whereas the
1994 version of Standard 210/240
covered equipment up to 135,000 Btu/
h, the 2003 version is limited to
equipment having rated capacities less
than 65,000 Btu/h. With regard to the
DOE test procedure, the January 22,
2001, proposed rule referenced four
sections within ARI Standard 210/240–
1994. In the 2003 version of the
standard, no substantive changes were
made to these four sections. The
numbering/lettering of the sections,
however, did change slightly. For
example, section 5.1.3.5 in the 1994
document became section 6.1.3.5 in the
2003 document. Today’s test procedure
maintains the approach taken in the
proposed rule of only referencing the
four particular sections of 210/240.
Because of this consistency, the DOE
test procedure is unaffected by
referencing ARI Standard 210/240–2003
rather than Standard 210/240–1994. The
reported energy efficiency ratings of the
tested equipment are unaffected as well.
2. Small-Duct, High-Velocity (SDHV)
Systems
As discussed in the January 22, 2001,
proposed rule, Unico, a manufacturer of
SDHV systems, argued for creating a
separate SDHV product class that was
subject to a lower future energy
conservation standard than the level
established for conventional units. (66
FR 6768) However, in the energy
standards rulemaking, a majority of
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industry members opposed the separateproduct-class option. DOE did not
include a separate SDHV class in the
January 22, 2001, proposed rule.
Instead, DOE proposed testing SDHV
systems as coil-only units. Testing as
coil-only units would give SDHV units
an immediate SEER and Heating
Seasonal Performance Factor (HSPF)
boost, as long as the default fan power
was less than the actual blower wattage.
The SEER and HSPF boost eliminated
the need for a separate product class.
Both Unico and ARI at first endorsed
this approach. (Unico, No. 10; ARI, No.
19 at p. 3) But SpacePak, Trane, and
ultimately ARI, disagreed with the coilonly testing approach. (SpacePak, No.
15; Trane, No. 12 at p. 1, ARI, No. 20)
These comments noted that SDHV
systems would be tested in a manner
that would never occur in real
applications and, as a result, give energy
efficiency and cost-of-operation results
that are not representative of the unit’s
true energy performance. Furthermore,
SDHV manufacturers would have no
incentive to use high-efficiency blowers
if systems were tested without the
indoor blower. Finally, there is no
technical basis for setting the default
fan-power level. For these reasons, DOE
has determined that its proposal to test
SDHV systems as coil-only units is
unacceptable. As a result, today’s final
rule does not amend the test procedures
to test SDHV systems as coil-only units.
DOE considered another alternative
for SDHV systems which it also
ultimately rejected. This alternative was
to make no changes at all. In other
words, test SDHV systems as they are
currently tested and require them to
meet the same future energy
conservation standards as conventional
units. The Department rejected this
option because it risked the continued
existence of SDHV systems. The
Department explained its position at the
public hearing on March 29, 2001: The
Department cannot set standards in a
way that removes from the market a
product which offers special utility.
(Public Hearing Tr., p. 44)
Because today’s final rule does not
amend the test procedures for SDHV
units, DOE recognizes, as it did in the
January 22, 2001, energy standards final
rule, that SDHV units will have
difficulty in meeting the 13 SEER
standard. In the May 23, 2002, final rule
on central air conditioner and heat
pump standards, DOE further discussed
how the special characteristics of SDHV
systems would make it unlikely such
systems could even meet the 12 SEER/
7.4 HSPF standard established for space
constrained products. (67 FR 36396)
However, because of the ruling by the
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3. Non-Defrost Heat Pumps
The January 22, 2001, proposed rule
included steps for calculating the HSPF
of a non-defrost heat pump. This
proposal addressed the test procedure
waiver granted to Enviromaster
International (EMI). In 1992, the
Department granted EMI a waiver for its
line of non-defrost, multi-split heat
pumps. Under the waiver, the
Department did not require EMI to
report an HSPF and instead required
EMI to include in its printed materials
for the product the following sentence,
‘‘No HSPF value has been measured
since the heat pump cannot be operated
at temperatures below 35°F.’’ EMI
finally applied to the Department’s
Office of Hearing and Appeals (OHA) on
January 23, 2003, for exception relief
from the HSPF efficiency standards.
OHA granted the exception relief on
April 1, 2003. Thus, EMI has never
calculated HSPF because of its waiver,
and will not do so in the future because
of OHA exception relief.
Since there are no manufacturers of
products on the market which would
actually use the proposed procedure for
calculating the HSPF of a non-defrost
heat pump, the Department has
removed from the test procedure all
references to non-defrost heat pumps
and the special caveats for calculating
an HSPF for such units.
4. Two-Capacity, Northern Heat Pumps
The January 22, 2001, proposed rule
applied to a two-capacity heat pump
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configured to use only low capacity
when cooling, while using both low and
high capacities when heating. (66 FR
6768) The proposed test procedure
identified such units as ‘‘two-capacity
heat pumps that lock out high capacity
when cooling.’’ At the March 29, 2001,
public hearing, York expressed concern
regarding the use of the term ‘‘lockout.’’
(Public Hearing Tr., p. 54) York felt the
term was too restrictive, since it could
be interpreted to mean that the lockout
feature must be hard-wired, whereas
DOE intended the meaning to include
factory or field-selectable lockout.
At the March 29, 2001, public
hearing, ARI commented that such units
would typically have two different
indoor coil identifiers and, as a result,
two different sets of ratings. (Public
Hearing Tr., p. 53) The ARI comment
was supported by many of the other
participants at the public hearing. ARI
and York submitted written comments
that supported the consensus reached at
the public hearing. (ARI, No. 19 at p. 2;
York, No. 9 at p. 2) The Department
chose to adopt the public comment
consensus and now defines these types
of systems as ‘‘two-capacity, northern
heat pumps.’’ The Department included
a requirement in the definition of ‘‘twocapacity, northern heat pump’’ that the
manufacturer must clearly state that the
feature is factory or field-selectable and
that manufacturers must publish two
sets of ratings. Finally, the definition
indicates that the lockout feature is to
remain enabled for all tests. The
northern heat pump is allowed to
operate at high capacity during its
defrost cycle, an issue that arose at the
public hearing. (Public Hearing Tr., p.
55)
5. Heat Pumps Having a Heat Comfort
Controller
The January 22, 2001, proposed rule
included an algorithm for calculating
the HSPF for most single-speed heat
pumps having a heat comfort controller.
(66 FR 6768) At the March 29, 2001,
public hearing, Trane commented that
the wording in the test procedure on the
calculation of the energy consumed for
resistive heating by a heat comfort
controller needed clarification. Trane
suggested that one use the higher of: (1)
The resistive heating based on meeting
the heat comfort controller’s
temperature setting; or (2) the resistive
heating based on meeting the building
load deficit (when operating below the
balance point). (Public Hearing Tr., p.
30) Later, Trane submitted written
comments that the algorithm, as
interpreted, would overstate the HSPF
at heat-comfort-controller set points
beginning around 90°F and get
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progressively worse as the set point was
reduced. (Trane, No. 12)
Battelle offered three general
recommendations. The first
recommendation was to emphasize that
comfort controllers operate both above
and below the normal balance point
temperature. The second
recommendation was to account for the
fact that conventional heat pumps and,
to a lesser extent, heat pumps with
comfort controllers, will cycle below the
system balance point. The third
recommendation was that DOE perform
a parametric calculation to determine
‘‘HSPF deficits’’ due to the operation of
a comfort controller. (Battelle, No. 11)
The end product could potentially be a
table listing the reduction in HSPF that
results from operating the comfort
controller at different temperature
settings.
The American Gas Association (AGA)
comments paralleled those from
Battelle. Both AGA and Battelle
recommended that the definition of
HSPF specify that for heat pumps with
heat comfort controllers, HSPF accounts
for resistive heating contributed when
operating either above or below the
balance point as a result of maintaining
a minimum supply temperature. Both
also recommended that the equation for
the heating load factor in section 4.2.1
be changed to the following:
( )
X Tj =
( )
BL Tj
( )
˙
Q h Tj + n( RH b )
where,
X(Tj) = the heating mode load factor for
temperature bin j, dimensionless
BL(Tj) = the building space conditioning
load corresponding to an outdoor
temperature of Tj
˙
Qh(Tj) = the space heating capacity of
the heat pump when operating at
outdoor temperature Tj, Btu/h
RHb = the size of each resistance heat
bank
n = the number of banks needed to
exceed the building load at each bin
temperature.
Finally, in a slight variation from
Battelle, AGA recommended that ‘‘DOE
provide direction in the test procedure
for evaluating performance of heat
pumps retrofitted with heat comfort
controllers in the field, including a
parametric table of HSPF by DOE region
for various delivered air temperatures.’’
(AGA, No. 18, Battelle, No. 11)
Given the general support for covering
those heat pumps having heat comfort
controllers, today’s test procedure
covers all heat pumps having heat
comfort controllers, except when a heat
comfort controller is used with a heat
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U.S. Court of Appeals for the Second
Circuit in January, 2004, 355 F.3d 179
(2d Cir. 2004), that bars DOE from
adopting a standard of less than 13
SEER for SDHV systems, the 13 SEER
standard applies to SDHV systems,
despite DOE’s later conclusion that it is
unlikely such systems can meet that
standard or even the lower 12 SEER
standard for space constrained systems.
(69 FR 50997) Nonetheless, the inability
of SDHV systems to meet the applicable
energy efficiency standards is not a new
problem created by the amendments to
the test procedure in today’s
rulemaking. Instead, these products
were unable to meet the standard under
the old test procedures. As a result, DOE
need not amend the applicable test
procedure or standard to mitigate this
noncompliance. DOE has advised the
two manufacturers of these systems of
the procedure available to affected
persons under section 504 of the
Department of Energy Organization Act
(42 U.S.C. 7194), which allows them to
request relief from hardship or inequity
caused by a regulation issued under
EPCA.
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pump having a variable-speed
compressor. Test procedure section
4.2.5.4 is reserved for a variable-speed
heat pump having a heat comfort
controller.
The algorithm for calculating the
HSPF of a heat pump having a heat
comfort controller is covered in sections
4.2.5.1 to 4.2.5.3 of today’s final rule.
The algorithm captures the fact that the
balance point temperature (i.e., where
the compressor first runs continuously)
for a heat pump with a heat comfort
controller will be less than, or equal to,
the balance point temperature of that
same heat pump without the heat
comfort controller. In response to
Trane’s comments (Public Hearing Tr.,
p. 30; Trane, No. 12), today’s test
procedure includes editorial additions
that alert the user to evaluate Equation
4.2.1–2 for all temperature bins. The test
procedure then accounts for the
resistive heating needed to satisfy the
minimum air delivery temperature of
the heat comfort controller and the
(additional) resistive heating needed to
give an overall heating capacity that
matches the building load.3
In considering AGA and Battelle’s
recommended definition change, the
key point is to emphasize the downward
shift in the balance point and the
associated lower contribution by the
heat pump. The Department doesn’t
believe that a single sentence referenced
to heat comfort controllers within the
HSPF definition, even when modified as
recommended, is sufficient. Therefore,
the definition of ‘‘Heat pumps having a
heat comfort controller,’’ emphasizes
the downward shift in the balance point
and the associated lower contribution
by the heat pump.
The Department is amending the
definition of HSPF by moving the
following language from the definition
text in the proposed rule to the main
3 When calculating the HSPF for a conventional
˙
˙
heat pump, the section 4.2 variable Eh(Tj) and Qh(Tj)
represent the electrical power and heating capacity
provided exclusively by the heat pump, while the
variable RH(Tj) applies exclusively to any resistive
heating contribution. When calculating the HSPF of
a heat pump having a heat comfort controller, by
˙
˙
comparison, the variables Eh(Tj) and Qh(Tj)
represent the electrical power and heating capacity
provided by the heat pump and any supplemental
resistive heating needed to provide the comfortcontroller-set-point air delivery temperature. The
variable RH(Tj), in this case, reflects any additional
resistive heating if the combined capacity of heat
pump and the resistive heating associated with
achieving the set-point air delivery temperature is
nonetheless insufficient to meet the building load.
Electrical resistive heating for a heat pump having
a heat comfort controller is thus allocated among
˙
two variables (Eh(Tj) and RH(Tj)) rather than one
(RH(Tj)). This redefining allows the calculation
procedure to capture the reduced heat pump
contribution, the shift to a lower balance point, and
the negative impact on HSPF.
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text of the test procedure, specifically,
to the end of Section 4.2, ‘‘Heating
Seasonal Performance Factor (HSPF)
Calculations.’’
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 heat pumps with
heat comfort controllers (see Definition 1.26),
in addition, HSPF also accounts for resistive
heating contributed when operating above
the balance point as a result of maintaining
a minimum supply temperature.
This moved text includes the one
sentence from the HSPF definition in
the proposed rule that specifically
addressed heat comfort controllers. This
sentence is the same one that both AGA
and Battelle recommended changing.
Coupled with the additional paragraph
in Section 4.2.5, ‘‘Heat pumps having a
heat comfort controller,’’ the
Department believes the revisions more
accurately convey the operating changes
caused by adding a heat comfort
controller.
The Department did not adopt AGA
and Battelle’s recommendation for
changing the calculation of the heatingmode-load factor. (AGA, No. 18,
Battelle, No. 11) The Department agrees
with AGA and Battelle that resistive
heating initiated as the result of a
second stage call of the indoor
thermostat can, under the right
conditions, cause a conventional heat
pump to cycle below its balance point.
Even though a conventional heat pump
terminates resistive heating once the
second stage setpoint is met, the
concentrated burst of resistive heating
coupled with the capacity of the
continuously operating heat pump may
cause the first stage of the thermostat to
be met shortly after the second stage is
met. An overshoot occurs and the heat
pump cycles off. The overshoot is more
likely to occur near the balance point
where only a small amount of resistive
heating is needed.
The existing test procedure makes the
implicit assumption that an overshoot
never occurs. AGA and Battelle’s
proposed change assumes that an
overshoot always occurs. The frequency
of this overshoot is unknown. Until data
become available showing that
overshoot occurs more often than the
case where the heat pump runs
continuously and the resistive elements
cycle on and off at the second stage, the
Department will leave the heating-loadfactor calculation unchanged. The AGA
and Battelle recommendation would be
more appropriate if resistive heating,
once initiated as the result of a second-
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stage call, stayed on until the first stage
setpoint was met. The Department is not
aware of conventional heat pumps that
use this strategy, so it did not change
the calculation of the heating-mode-load
factor.
Heat pumps with heat comfort
controllers operate differently from
conventional heat pumps following a
second-stage-thermostat call for resistive
heating. When the second-stage setpoint
is satisfied, heat comfort controllers
reduce the resistive heating rather than
cycling it off. In this manner, the heat
comfort controller attempts to modulate
the resistive heating so that additional
second-stage calls are reduced while
also avoiding satisfying the first-stage
setpoint. The goal is for the heat pump
to operate continuously below the
balance point while having the resistive
heating regulated to provide a more
uniform delivery temperature than that
provided by a conventional heat pump.
The heat comfort controller’s operation
when responding to a second-stagethermostat call is believed to provide a
more comfortable environment for the
homeowner, while not causing an
energy penalty. The one field study
cited by both AGA and Battelle 4
supports this assertion. Therefore, as
was decided for conventional heat
pumps, the Department did not adopt
the AGA and Battelle recommended
heating-load-factor equation within the
section 4.2.5 calculations that only
apply to heat pumps having a heat
comfort controller.
Finally, with regard to the Battelle
and AGA recommendations that the test
procedure contain information on the
impact of heat comfort controllers for
different temperature setpoints and/or
quantify the impact from an after-market
retro-fit installation of a heat comfort
controller, the Department agrees that
such information is probably warranted
but judges it inappropriate for inclusion
in the test procedure. The scope of the
test procedure is to test and rate new,
factory-supplied equipment. Addressing
the impact of after-market products on
the performance of covered products is
not within the purview of EPCA.
However, as pointed out at the March
29, 2001, pubic hearing, the test
procedure may provide a framework for
building code officials’ consideration
when deciding how to handle the aftermarket sale of heat comfort controllers.
(Public Hearing Tr., p. 32)
4 ‘‘Improving Occupant Comfort Without an
Energy Penalty in Homes Heated by Electric Heat
Pumps,’’ Yuill, G.K., and Musser, A., ASHRAE
Paper 4162, ASHRAE Transactions 1998 V. 104, Pt.
1.
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B. Definitions
In addition to the amendments to the
definitions discussed above in section
II.A.1 of this preamble, today’s final rule
modifies definitions and references as
described below.
An editorial correction was made to
the citation for ASHRAE Standard 51–
99/AMCA Standard 210–99. In the
proposed rule the words ‘‘AMCA
Standard’’ were wrongly omitted.
The definitions of ‘‘heating seasonal
performance factor (HSPF),’’ and
‘‘seasonal energy efficiency ratio
(SEER)’’ have been modified to move
some text to later sections of the test
procedure. The moved text provided
complementary information that was
better placed in the main text of the test
procedure rather than in a definition.
Sentences from the definition of HSPF
were moved to Section 4.2, ‘‘Heating
Seasonal Performance Factor (HSPF)
Calculations.’’ Similarly, one sentence
from the definition of SEER became the
first sentence in Section 4.1, ‘‘Seasonal
Energy Efficiency Ratio (SEER)
Calculations.’’
C. Testing Conditions
1. Section 2.2.4 Wet-Bulb Temperature
Requirements for Air Entering the
Indoor and Outdoor Coils
The January 22, 2001, proposed rule
included a requirement that applied to
wet-coil cooling tests of single-packaged
units where all or part of the indoor
section is located in the outdoor test
room. The requirement was that the
average dew point temperature of the air
entering the outdoor coil must be within
±3.0°F of the average dew point
temperature of the air entering the
indoor coil. This requirement was
added to address concerns about
equipment leakage affecting capacity
measurements. The water vapor content
of the outdoor air could affect the
repeatability of the measurements.
Similarly, leakage could present a
problem when using the Outdoor Air
Enthalpy test method for testing a
single-packaged heat pump where all or
part of its outdoor section is located in
the indoor test room.
In comments made at the March 29,
2001, public hearing and in written
comments received thereafter, York and
ARI agreed with the proposed
requirements. ( Public Hearing Tr., p.
79; York, No. 9 at p. 4; ARI, No. 19 at
p. 2) The Department has adopted the
proposed test requirement in today’s
final rule without alteration.
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2. Section 2.2.5 Additional Refrigerant
Charging Requirements
Existing testing procedures require
that the unit be installed in accordance
with the manufacturer’s installation
instructions. The ARI, as part of its
certification program, occasionally
makes decisions on what is and is not
within the spirit of the requirement.
Thus, a policy has evolved wherein ARI
certification testing allows procedures
such as break-in times for compressors
and washing the oil residue from the
coils prior to testing. ARI does not allow
disconnecting an electrical component,
such as a crankcase heater. For the most
part, the Department chose to defer to
ARI to maintain consistency in the test
set-ups. However, the Department
proposed additional limits on the
specific issue of the refrigerant-charging
procedure. In the section 2.2.5 of the
January 22, 2001, proposed rule, the
Department proposed two additional
requirements. First, the Department
sought to avoid a gray area of defining
when an independent test laboratory
should consult with the manufacturer
on how to charge a unit. The proposed
section included the sentence: ‘‘For
third party testing, for example, do not
consult the manufacturer about how to
charge the unit.’’ This requirement was
thought to place extra responsibility on
the manufacturer to publish accurate
and clear charging instructions.
The second requirement was to
promote the ideal of testing the unit in
a manner that is similar to its actual
installation in the field. The Department
proposed amendments to section 2.2.5
to include the following sentence:
‘‘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.’’
At the March 29, 2001, public
hearing, ARI, ITS, and ACEEE spoke in
favor of allowing the independent test
laboratory to contact the manufacturer if
it had any charging questions. (Public
Hearing Tr., pages 101 to 112) This
discussion noted the value of feedback
in assisting the manufacturer to identify
mistakes or incompleteness in its
published instructions. Such feedback,
if acted upon by the manufacturer,
could benefit the eventual field
installer. At the public hearing,
attendees also came to the realization
that the attempt to prevent special labonly charging criteria could likely be
circumvented by having a single criteria
that listed wide ranges for such charging
parameters as the targeted superheat or
subcooling level(s).
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The Department considered deleting
the proposed section 2.2.5. However,
today’s final rule contains a revised
version of the January 22, 2001,
proposed rule language. (66 FR 6792) In
the proposed rule, for third-party
testing, the test laboratory was not to
consult with the manufacturer about
how to charge a unit. Based on the
public hearing comments discussed
above, today’s final rule has modified
this requirement. The test laboratory
may consult with the manufacturer
about the refrigerant-charging procedure
and make changes that do not contradict
the published installation instructions.
The manufacturer may specify an
alternative charging criteria to the thirdparty laboratory if the manufacturer
then revises the published installation
instructions accordingly. DOE decided
to keep the section in an effort to convey
the side benefit of the allowed feedback
mechanism and to emphasize that the
goal is a lab set-up as consistent as
possible with a field installation.
D. Testing Procedures
1. Section 3.1.4 Airflow Through the
Indoor Coil: Systems Having a VariableSpeed, Constant Airflow Blower
The January 22, 2001, proposed rule
included additions to the test procedure
for systems having a variable-speed,
constant airflow (often called constant
CFM (cubic foot per minute)) blower.
These additions included:
(1) Controlling the exhaust fan of the
airflow measuring apparatus to obtain a
specified external static pressure. DOE
received no comments on this addition.
(2) Specifying an additional test and
algorithm to correct the fan power in cases
where the specified external static pressure
cannot be achieved during testing due to
blower instabilities. ITS and York
commented in favor of this addition. (Public
Hearing Tr., ITS, p. 72–73, York, p. 73)
(3) Making use of the fan laws if a unit
must be tested at an air volume rate other
than the (cooling or heating) Certified Air
Volume Rate. DOE received no comments on
this addition.
(4) Allowing cyclic tests to be conducted
with or without the indoor fan enabled and
using a step profile for the air volume rate
during cyclic tests. DOE received no
comments on this addition.
(5) Imposing an 8-percent tolerance for the
difference between the lab-measured and
manufacturer-Certified Air Volume Rates.
At the March 29, 2001, public
hearing, ARI, Trane, and York spoke in
favor of making a change to eliminate
the eight percent tolerance. (Public
Hearing Tr., ARI, p. 69, Trane, p. 70,
and York, p. 70) ARI and York
submitted written comments to the
same effect. (ARI, No. 19 at p. 2; York,
No. 9 at p. 2) Opposition to the eight
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percent tolerance was based on the
industry’s not wanting another certified
parameter. ARI recommended that DOE
limit its focus to rated capacity and
seasonal performance, SEER and HSPF,
and not include parameters that affect
those values. (ARI, No. 19 at p. 2)
DOE proposed the tolerance to
provide manufacturers with assurance
that any third-party testing would
employ a representative air volume rate.
However, these blowers have a level of
variability which may occasionally
exceed the proposed eight percent
tolerance. The eight-percent tolerance
could cause several unnecessary
stoppages in testing where the impact
on rated capacity and seasonal
performance would be negligible. Given
the foreseeable unfavorable trade-off
from imposing the tolerance, the
Department has eliminated the eightpercent tolerance in today’s final rule.
2. Sections 3.1.4.2, 3.1.4.5, 3.3, 3.5.1,
3.7, and 3.9.1. Testing a Two-Capacity
Compressor System: Coil-Only Units
Tested at Low Capacity and Differences
in High/Low Cycling
The proposed test procedure sections
3.1.4.2 and 3.1.4.5 specified that the air
volume rate used when testing twocapacity, coil-only units at low capacity
(i.e., at the Minimum Air Volume Rate)
is the higher of:
(1) The rate specified by the
manufacturer, or
(2) 75 percent of the air volume rate
used for the high capacity tests.
At both the public hearing and in its
written comments, York opposed the
proposed 75-percent limit. (Public
Hearing Tr., pp. 81–86; York, No. 9 at
p. 3) York argued that the limit was
‘‘arbitrarily derived, is unnecessary, and
restrictive towards applying existing
and future technologies in motor speed
controls. * * *’’ (York, No. 9 at p. 3)
Conversely, at both the public hearing
and in their written comments, both
Copeland Corporation and ARI
supported the defining of a lower limit.
Their written comments specifically
endorsed assigning the limit at 75
percent. (Public Hearing Tr., pp 86–90;
Copeland Corporation, No. 13 at p. 2;
ARI, No. 19 at p. 2)
This 75-percent value is based on the
assumption that the two-capacity coilonly unit would most often be used
with an existing multi-tap furnace
blower. The low range offered from
typical multi-tap motors can vary
considerably. Nonetheless, the limited
data collected by NIST and by industry
supports the proposed 75-percent value,
and DOE has included it in today’s final
rule.
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The proposed test procedure sections
3.3, 3.5.1, 3.7 and 3.9.1 did not
differentiate between the default fan
power values for high capacity and low
capacity. The value of 365 watts per
1000 standard cubic feet per minute
(SCFM) was used in all cases. Only York
commented on this issue, and York’s
comment supported the proposed test
procedure. (Public Hearing Tr., p. 94,
York, No. 9 at p. 3) York commented
that the proposed low capacity default
causes a conservative prediction of fan
power, with a resulting error too
insignificant to warrant a change. (York,
No. 9 at p. 3) Today’s final rule
maintains the changes on this subject
incorporated into the proposed test
procedure.
The final two-capacity, compressorsystem issue was whether there is a
significant performance difference
between compressors (systems) that can
switch between low and high stages
over a very short time interval versus
those having to turn off for a short
period and take longer overall to make
the transition. (This issue is included
because DOE received comments about
it. It does not appear in the proposed
rule, nor in today’s final rule.) Copeland
Corporation noted that it has experience
manufacturing both types of
compressors and that it has ‘‘observed
that shutting a system down for greater
than one minute has nearly the same
cyclic loss impact as a typical on/off CD
penalty, since the evaporator warms up
almost completely.’’ Copeland
encouraged the Department to study the
issue further and stated that an
appropriate action may be to conduct a
test program at Intertek Testing Services
(ITS). (Copeland Corporation, No. 13 at
p. 1) York, on the other hand, expressed
its opinion that the difference in
technology was not significant enough
to warrant a change in the test
procedure. (York, No. 9 at p. 3) The
Department has been unable to identify
test procedure changes that could
capture a performance difference,
assuming that its overall impact
significantly alters the SEER and HSPF
ratings. The Department would have to
make assumptions about the frequency
of high/low transitions as a function of
the magnitudes of the low and high
stage capacities relative to each
temperature bin building load. Also,
data are needed to determine whether
the cooling and heating mode on/off
degradation coefficients could act as
substitutes for the high/low transition
degradation or whether a separate
optional test and/or separate transition
default values are warranted. In general,
the Department is willing to consider
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future changes to the test procedure but
asks that interested industry members
take the lead in quantifying the impact
on SEER and HSPF before making
specific recommendations on how to
alter the test procedure calculations.
III. Summary of Other Additions and
Changes to the DOE Residential Central
Air Conditioner and Heat Pump Test
Procedure
Today’s final rule contains numerous
changes that were proposed in the
January 22, 2001, proposed rule, for
which the Department received no
adverse comments.
A. Update and Add References for
ASHRAE and ARI Standards
The current test procedure references
ASHRAE Standard 37–78 and ASHRAE
Standard 41.1 (no year), ARI Standard
210–79, ARI Standard 240–77, and ARI
Standard 320–76. Today’s final rule also
includes references to ARI Standard
210/240–03, ASHRAE Standard 23–93,
ASHRAE Standard 37–88, ASHRAE
Standard 41.1–86 (RA 01), ASHRAE
Standard 41.2–87 (RA 92), ASHRAE
Standard 41.6–94 (RA 01), ASHRAE
Standard 41.9–00, ASHRAE Standard
51–99/AMCA Standard 210–99, and
ASHRAE Standard 116–95. The
additional commercial standards are
necessary to more completely inform
manufacturers and testers about the
multiple test options, especially for the
secondary test method, and to address
as many of the small details of lab
testing as possible. The additional
commercial standards were all included
in the January 22, 2001, proposed rule.
(66 FR 6768) Some of the commercial
standards have been updated since the
publication of the proposed rule as
discussed in section II.A.1 of this
preamble.
B. Air Volume Rates
The current test procedure references
ARI Standard 240–77. Now, rather than
referencing ARI Standard 210/240–03,
which replaced ARI Standard 240–77,
the Department has added its own
sections to the test procedure. The main
reason for no longer referencing ARI
Standard 210/240 is that it does not
cover variable-speed and constant CFM
blowers. In addition, ARI Standard 210/
240 does not directly address twocapacity and variable-speed systems.
The Department believes it is preferable
to have the overall issue of air volume
rates covered in one place rather than in
two.
The test procedure set forth in this
final rule no longer references ASHRAE
Standard 37–78 (or ASHRAE Standard
37–88, its replacement) for the equation
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used to calculate the air volume rate of
standard air, because the referenced
equation is incorrect. The factor ‘‘1
+Wn’’ is missing from the denominator
of the pertinent equation in both
versions of ASHRAE Standard 37.
Today’s test procedure includes what
DOE believes to be the correct version
of the equation.
Today’s test procedure also adopts the
approach used in the ISO Standard 5151
of conducting each test at zero external
static pressure when testing a nonducted unit.
All of these ‘‘air volume rate’’
substantive changes were originally
published in the proposed rulemaking
(66 FR 6778) and are included in today’s
final rule.
C. Cyclic Testing
The Department is today adopting
standard industry practice and the
method described in ASHRAE Standard
116. Sections 4.1.1.2, 4.1.2, 4.2.2.2, and
5.1 of the current (1988) test procedure
require measurement of the air volume
rate during cyclic tests and use of this
measurement in determining the total
cooling (heating) delivered. Standard
laboratory practice, by comparison, is to
achieve and maintain the same velocity
pressure or nozzle static pressure drop
that was obtained during the
comparable steady-state test. The total
cooling (heating) delivered during a
cyclic test, in addition, is calculated
using the air volume rate measured
during the comparable steady-state test.
Changes to adopt this industry practice
and become consistent with ASHRAE
Standard 116 were introduced in the
proposed rulemaking and are included
in today’s final rule in section 3.1.
When testing split-type non-ducted
(ductless) systems, section 4.1.1.5 of the
current test procedure provides, ‘‘The
integration time for capacity and power
shall be from compressor cut-on time to
indoor fan cutoff time.’’ The indoor fan
is operated for three minutes prior to
compressor cut-on and for three minutes
after compressor cutoff during the final
OFF/ON interval. In sections 3.5 and
3.5.2, today’s final rule adopts industry
practice and integrates power from
compressor OFF to compressor OFF and
subtracts the electrical energy associated
with operating the indoor fan during the
initial three-minute fan-only period.
Space cooling capacity is integrated
from compressor ON to indoor fan OFF.
As with the current test procedure, fan
energy for the three minutes after
compressor cutoff is added to the
integrated cooling capacity.
The current test procedure does not
contain specific information regarding
the air dampers: where to install them,
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how well they should seal, and how
quickly they should respond. Appendix
D of ARI Standard 210/240–03 contains
much of this information. Today’s final
rule incorporates the required
information in sections 2.5.4.1 and 2.5.7
rather than make specific references to
each pertinent section of Appendix D of
the ARI Standard.
For dry coil tests, today’s test
procedure final rule adopts, in section
3.4, the language in ARI Standard 210/
240–03 Appendix D with regard to the
requirements that the drain pan be
plugged and completely dry.
Today’s final rule clarifies in section
2.8 that the requirement of making
electrical energy measurements using an
instrument having an accuracy of ±0.5
percent of reading applies during both
the ON and OFF intervals of cyclic tests.
Today’s final rule deletes the current
section 4.1.3.1, ‘‘The indoor and
outdoor average dry-bulb temperature
for the cyclic dry coil test D shall both
be within 1.0 °F of the indoor and
outdoor average dry bulb temperature
for the steady-state dry coil test C,
respectively.’’ This requirement is
automatically met given the 0.5 °F test
condition tolerance associated with
each test. (Today’s amended test
procedure is substantially re-organized;
the section 4.1.3.1 in today’s final rule
has no relation to the deleted section
4.1.3.1.)
For units having a variable-speed
indoor fan, the manufacturer will have
the option of conducting the cyclic tests
with the indoor fan either enabled or
disabled, the latter being the default
option if an attempt at testing with the
fan enabled is unsuccessful. See section
3.5 of today’s final rule. Specifically, if
the test is performed with the indoor fan
operating, and the fan automatically
reverses, shuts down, or operates at an
uncharacteristically high external static
pressure, then the test must be repeated
using a pull-thru method, with the fan
disabled.
Although a unit having a variablespeed indoor fan may be designed to
ramp its fan speed when cycling on
and/or off, a step response in air volume
rate is nonetheless required during
cyclic tests. See section 3.5 of today’s
final rule. The work associated with
moving the additional air during the
ramp periods is performed by the
exhaust fan of the air flow measuring
apparatus. The step response begins at
the initiation of ramp up and ends at the
termination of ramp down. The
rationale for imposing the step change is
mainly due to the difficulty in obtaining
the ramp response and then making an
accurate measurement of the space
conditioning delivered. Systems having
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indoor fans that ramp are expected to
have low cyclic degradation coefficients
(CD) regardless of whether the ramp
feature is used, thus the absolute
improvement in CD is expected to be
minor.
D. Fanless (Coil-Only) Units
Section 4.1 of the current test
procedure calls for corrections to
capacity and power based on air flow
measured in cubic feet per minute
(CFM). Section 4.2 of the current test
procedure calls for corrections to
capacity and power based on air flow
measured in cubic feet per minute
under standard conditions (SCFM). To
avoid confusion, the test procedure
should base corrections on either CFM
or SCFM, but not both. ITS, which tests
for both the industry and ARI, uses
SCFM in all cases. Therefore, in
consideration of the above, today’s test
procedure adopts, in sections 3.3, 3.5.1,
and 3.7, the practice of specifying all
corrections in terms of SCFM.
The test procedure also adopts in
section 2.2 the requirement in ARI
Standard 210/240–03, Appendix D, that
an enclosure be constructed using oneinch ductboard for testing a coil-only
unit that does not employ an enclosure.
E. Frost Accumulation Test
Today’s final rule adopts the
convention in ASHRAE Standard 116–
95 and ARI 210/240–03 of specifying
the outdoor wet bulb temperature (33
°F) in place of the presently specified
dew point temperature (30 °F). Sections
3.6.1, 3.6.2, 3.6.3, and 3.6.4.
F. Test Tolerance Tables
The current test procedure contains
tables covering all tests except steadystate cooling-mode tests, for which
Table III in ASHRAE Standard 37–78 is
referenced. Since the test procedure
includes all other tables, the Department
chose to add the needed parts of Table
III (Table 7 of this document).
The test condition tolerance for
external resistance to air flow now
applies only when testing non-ducted
units. (See Table 7). Also, DOE has
added in Table 7 a test condition
tolerance for electrical supply voltage
(previously, only a test operating
tolerance was specified). The existing
test procedure lacked a clarification that
the test condition tolerance for the
indoor inlet wet bulb temperature in
Table III of ASHRAE Standard 37–78
does not apply for dry coil tests.
Therefore, today’s final rule includes a
footnote to Table 7 that makes this
clarification. In a similar attempt to
clarify when particular tolerances apply,
today’s final rule also includes a
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footnote to tables stating that the test
tolerances given for the outdoor outlet
dry and wet bulb temperatures only
apply when using the Outdoor Air
Enthalpy Method to provide the
secondary capacity measurement.
For the Frost Accumulation Test, DOE
modified slightly the intervals
considered to be heating versus
defrosting. Specifically, in the current
test procedure in section 4.2.3.3, the
first five minutes after a defrost
termination was included in the defrost
interval. In today’s final rule, the time
interval has been increased to ten
minutes in section 3.7. This is a better
approximation of the time needed for
temperatures to reach equilibrium after
defrost termination. Also, in making the
test condition conversion of 30 °F dew
point to 33 °F wet bulb, the test
operating tolerance and test condition
tolerance convert to wet bulb
temperature tolerances of 0.6 °F and 0.3
°F, respectively. This 0.6 °F test
operating tolerance on outdoor wet bulb
temperature is more stringent than the
value allowed for the steady-state tests.
The 0.3 °F test condition tolerance is the
same as required for steady-state tests.
Because these tolerances should be less
stringent that those required of a steadystate test, the test procedure adopts in
Table 15 the values given in ASHRAE
Standard 37: 1.5 °F and 0.5 °F.
G. Pretest Intervals
1. Wet Coil Tests
The following change makes the test
conditions more specific than they are
in the current test procedure:
Current: ‘‘The test room
reconditioning apparatus and the
equipment under test shall be operated
until equilibrium conditions are
attained.’’ (Section 4.1.1.1)
Today’s final rule: ‘‘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.’’
(Section 3.3)
2. Dry Coil Steady-State Test
The following change also makes the
test conditions more specific than they
are in the current test procedure. The
industry realized the merits of this
improved wording several years ago.
The added text is taken from a
prescriptive methodology that appears
within an appendix of ARI Standard
210/240–2003.
Current: ‘‘The test room
reconditioning apparatus and the
equipment under test shall be operated
until equilibrium conditions are
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attained, but not for less than one hour
before data for test C are recorded.’’
(Section 4.1.1.2)
Today’s final rule: Same as proposed
for section 3.3 wet coil tests with the
additional requirement to ‘‘operate the
unit at least one hour after achieving dry
coil conditions.’’ (Section 3.4)
3. Dry Coil Cyclic Test
The following change makes the test
conditions more specific than they are
in the current test procedure. The
existing language is weaker because the
phrase ‘‘until steadily repeating ambient
conditions are again achieved’’ is
comparatively subjective.
Current: ‘‘[T]est unit shall be
manually cycled ‘off’ and ‘on’* * *
until steadily repeating ambient
conditions are again achieved in both
the indoor and outdoor test chambers,
but for not less than two complete ‘off/
on’ cycles.’’ (Section 4.1.1.2)
Today’s final rule: ‘‘After completing
a minimum of two complete compressor
OFF/ON cycles, determine the overall
cooling delivered and total electrical
energy consumption during any
subsequent data collection interval
where the test tolerances given in Table
8 are satisfied.’’ (Section 3.5)
4. Maximum and High Temperature
Heating Mode Tests
The requirement for the test apparatus
and the test unit to operate for at least
one hour was dropped based on
industry comments that it had no
bearing on the outcome of the testing—
the key is to have steady operation at
the specified test conditions for an
interval (30 minutes) prior to starting
the test.
Current: ‘‘The test room apparatus
and test units must be operated for at
least one hour with at least one-half
hour at equilibrium and at the specified
test conditions prior to starting the test.’’
(Section 4.2.1.1)
Today’s final rule: ‘‘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.’’
(Section 3.7)
5. Heating Mode Cyclic Test
The new language is more definitive
and easier for a test laboratory to
understand and implement. The
existing language is weaker because the
phrase ‘‘until steadily repeating ambient
conditions are again achieved’’ is
comparatively subjective.
Current: ‘‘[A]nd be cycled ‘on’ and
‘off’ as specified in 3.2.1.2 until steadily
repeating ambient conditions are
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achieved for both the indoor and
outdoor test chambers, but for not less
than two complete ‘off’/‘on’ cycles.’’
(Section 4.2.1.2)
Today’s final rule: ‘‘After completing
a minimum of two complete compressor
OFF/ON cycles, determine the overall
cooling delivered and total electrical
energy consumption during any
subsequent data collection interval
where the test tolerances given in Table
8 are satisfied.’’ (Section 3.5)
6. Frost Accumulation Test
The new wording is clearer about the
goal of getting the test room to achieve
and maintain the specified test
conditions. It clarifies the 30-minute
requirement as a period that starts after
the test conditions are first achieved.
Current: ‘‘The test room
reconditioning equipment and the unit
under test shall be operated for at least
one-half hour prior to the start of a
‘preliminary’ test period.’’ (Section
4.2.1.3)
Today’s final rule: ‘‘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.’’ (Section 3.9)
7. Low Temperature Test
The existing language can be
interpreted to mean that one only needs
to achieve the test conditions
immediately prior to starting the test as
opposed to maintaining the test
conditions for at least 30 minutes prior
to starting the test. The new wording is
clearer. The new wording also clarifies
the sequential process for having the
heat pump conduct a defrost.
Current: ‘‘The test room
reconditioning equipment shall first be
operated in a steady-state manner for at
least one-half hour at equilibrium and at
the specified test conditions. The unit
shall then undergo a defrost, either
automatic or manually induced.’’
(Section 4.2.1.4)
Today’s final rule: ‘‘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.’’
(Section 3.7) ‘‘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.’’ (Section 3.10)
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H. Multi-Capacity Systems
1. Two-Capacity Heat Pumps That Lock
Out Low Capacity at Higher Outdoor
Temperatures
The current test procedure in section
2.2.2 covers two-capacity units that
operate exclusively at high capacity
when the building load exceeds the
unit’s low capacity. The Department is
unaware of any two-capacity units that
implement such a control strategy, and
so DOE is not including coverage of
them in today’s final rule. However, the
Department is adding coverage in
section 3.2.3 to address units that lock
out low capacity operation at low
(heating) or high (cooling) outdoor
temperatures. Today’s test procedure
uses the CD determined based on
cycling at low capacity (or the
appropriate default) in all cases.
2. Systems Having a Single-Speed
Compressor and a Variable-Speed
Indoor Fan Where Fan Speed or Air
Volume Rate Depends on Outdoor
Temperature
Today’s final rule requires two
additional steady-state tests for the
cooling mode (see section 3.2.2.1 and
Table 4) and two additional steady-state
tests for the heating mode (see section
3.6.2 and Table 10). The additional
tests, at a different air volume rate, are
required to calculate the effect of the
variable-speed indoor fan. An additional
frost accumulation test is optional.
I. Triple-Split Systems
The current DOE test procedure, in
sections 4.1 and 4.2.1, refers to ASHRAE
Standard 37–78 on the issue of
laboratory set up procedures. Section
3.1.3 of ASHRAE Standard 37–78
requires using the calorimeter airenthalpy method arrangement when
testing units where the compressor is in
the indoor section and separately
ventilated. For this arrangement, an
enclosure must be built around the
equipment within the indoor chamber.
The present requirement is burdensome,
and DOE has learned no one uses it
when testing triple-splits. Furthermore,
the heat loss from the indoor
compressor section should be reflected,
if at all, in an adjusted output capacity
and not by a raised entering-air
temperature because the lost heat is
transferred to the surrounding ambient,
not dissipated within the return air
duct. The surrounding ambient, in this
case, may or may not be part of the
conditioned space.
The amount of heat dissipated to the
ambient by the indoor compressor
section of such units is usually
minimized as a result of the insulated
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enclosure of the third section (mainly in
an effort to reduce the operating noise).
Based on the limited information
currently available, DOE believes that
the amount of heat lost from the indoor
compressor section is on the order of
two percent or less of the unit’s space
conditioning capacity.
Today’s final rule reflects the
assumption that the heat loss from the
indoor compressor section contributes
nothing to the unit’s overall delivered
capacity if the compressor section is
located in an unconditioned space. If
the compressor section is located in the
conditioned space, it still contributes
only a negligible amount. Today’s final
rule specifies that triple-split systems
are not to be tested using the calorimeter
air-enthalpy method arrangement (see
note in section 2.6 of the test procedure
in today’s final rule). The final rule does
not provide for any adjustment to
capacity, or any algorithm or method for
assigning/determining the heat loss
from the indoor compressor section. If
triple-split systems become more
popular and if information becomes
available indicating the heat loss from
the indoor compressor section exceeds
two percent of the air-side capacity,
then DOE will revisit the option of
having a capacity adjustment.
J. Time-Adaptive Defrost Control
Systems
When conducting a frost
accumulation test on a heat pump
having a time-adaptive defrost control
system, repeatable frosting and
defrosting intervals typically require (if
obtainable at all) an excessive number of
cycles. The tester must manually initiate
defrosts during the ‘‘preliminary’’ test
and the ‘‘official’’ test. Under today’s
final rule, the manufacturer must
provide information as to how long the
unit would optimally frost before it
initiates a defrost, and on how to initiate
a defrost cycle at the appropriate
elapsed time. See section 2.2.1.
However, the controls of the unit will
still control the duration of the defrost
cycle after its initiation.
K. Test Unit Installation
For the most part, equipment
installation requirements under today’s
final rule will continue according to the
manufacturer’s field installation
instructions. However, today’s final rule
adopts the lab and field practice of
insulating the low pressure line(s) of a
split system. See section 2.2.
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59131
L. Test Apparatus and Measurement/
Sampling Frequency
1. Inlet Plenum for Blower Coils
The current DOE test procedure does
not require an inlet plenum when
testing blower coil units. (Lab ceiling
height on vertical installation is a
limitation.) In today’s final rule, the
manufacturer has the option to test with
or without an inlet plenum installed
when testing a ducted unit having an
indoor fan. Space limitations within the
test room may dictate that the
manufacturer choose the latter option.
(Section 2.4.2)
2. Manifolded Static Pressure Taps
The current (1988) test procedure
does not discuss methods of
manifolding static pressure taps.
Today’s final rule allows three
configurations: The triple-T
configuration; the complete ring, fourto-one manifold configuration; and the
broken-ring, four-to-one manifold
configuration. (Section 2.4.1) A 1976
study found the triple-T configuration to
be the preferred method for manifolding
static pressure taps.5 The broken-ring,
four-to-one manifold configuration is
generally considered to be the least
accurate of the three methods.
3. Temperature Measurement Intervals
Today’s final rule (Definition 1.15)
specifies dry-bulb temperature
measurements at the intervals specified
in ASHRAE Standard 41.1–86 (RA01).
The tester must measure wet bulb
temperature, dew point temperature, or
relative humidity at the minimum
sampling interval specified in the
definition of the term ‘‘Continuously
recorded.’’
4. Temperature Measurement
Accuracies
Today’s final rule (sections 2.5.5,
2.5.6, 2.11) incorporates the accuracy
and precision requirements of
temperature measurement from
ASHRAE Standard 41.1–86 (RA 01).
5. Grid of Individual Temperature
Sensors Within the Indoor-Side Outlet
Plenum
Today’s final rule adopts the
requirements in ARI Standard 210/240–
03, Appendix D, that a temperature
spread of 1.5 °F or less be obtained, and
that a minimum of 9 sensors compose
the outlet temperature grid. (Section
2.5.5.) The January 22, 2001, proposed
rule contained these DOE
recommendations (66 FR 6796):
5 ‘‘The Design of Piezometer Rings’’ by K. A.
Blake, Journal of Fluid Mechanics, Vol. 78, 1976,
part 2, pp. 415–428.
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DOE recommends using 16
temperature sensors within each
temperature grid. DOE recommends
installing redundant inlet and outlet dry
bulb temperature sensors and
particularly a thermopile. If using
thermocouples, DOE recommends the
following:
(1) Use 24 gauge wire;
(2) Remove approximately 1 inch of
insulation from each lead when
preparing to make a junction; and
(3) Use no more than two bonded
turns per junction.
The Department believes these
recommendations to be sound, but
today’s final rule omits them because
recommendations are not appropriate in
a regulatory test procedure.
M. Different Compressor Speeds and
Indoor Fan Capacities Between Cooling
and Heating
The existing test procedure covers
variable-speed systems that operate at
higher speeds when heating than when
cooling. Today’s final rule extrapolates
this allowance to coverage of twocapacity, northern heat pumps (see
section 4.2). Today’s rule covers any
case where the heat pump uses different
fan speeds or air volume rates for
cooling versus when heating. (Section
3.1.4.4.2)
N. Secondary Test Requirements
Today’s final rule explicitly permits
alternatives to using wet bulb
temperature sensors. To ease
instrumentation selection, the rule
specifies required instrument accuracies
for dew point hygrometers and relative
humidity meters. (Section 2.5.6)
When using the Outdoor Air Enthalpy
test method, the tester must conduct a
preliminary test to compensate, if
necessary, for any performance impact
resulting from the outdoor air-side test
apparatus. (Section 3.11.1) In the
existing test procedure, a preliminary
test is conducted prior to all steady-state
tests (i.e., those tests that require a
secondary measurement of capacity).
Today’s final rule relaxes this
requirement. Section 3.11.1 indicates
that the number of preliminary tests can
be reduced in most cases to one (for air
conditioners or heating-only heat
pumps) or two (for heat pumps): One for
the first cooling mode steady-state test
and one for the first heating mode
steady-state test. The above ‘‘test
apparatus and measurement/sampling
frequency’’ substantive changes were
introduced in the proposed rulemaking
and are maintained in today’s final rule.
(Section 3.11.1)
8. Voltmeter Accuracy
O. HSPF Calculations
The required accuracy of voltage
measurements has been changed from
±2 percent to ±1 percent. (Section 2.7)
Today’s final rule does not include
the final paragraph of sections 5.2.1 and
5.2.2 of the current test procedure. The
paragraph in question reads ‘‘Once the
maximum and minimum HSPF and
operating cost values have been
obtained for each region, the HSPF and
operating cost shall be determined for
each standardized design heating
requirement (see section 6.2.6) between
the maximum and minimum design
heating requirements by means of
interpolation.’’ The number of required
HSPF calculations is covered in 10 CFR
Subpart B, 430.23(m)(3)(ii). In today’s
final rule, this section of the CFR is
noted in the Definition (1.27) for HSPF.
Because of the relative ease of
automating the calculation process, and
the nonlinearity of the HSPF-versusdesign-heating-requirement
relationship, today’s final rule makes no
reference to obtaining HSPF or
operating cost via interpolation.
6. Duct Loss Correction
Today’s final rule includes a
correction for the heat transfer between
the test room and an outlet duct
sandwiched between the coil and the
outlet temperature grid. (Section 3.11)
This correction is already an industry
practice.
7. Water Vapor Measurements Using a
Dew-Point Hygrometer, a Relative
Humidity Meter, or Any Other
Alternative Instrument
9. Electrical Power Measurement
Adjustable-speed-driven motors, as
used in a variable-speed compressor,
distort the input current and, to a lesser
degree, voltage waveforms. For reasons
that were outlined in the preamble of
the January 22, 2001, proposed rule (66
FR 6779), today’s final rule (Section 2.8)
eschews the use of induction type
meters for measuring such nonsinusoidal power. The January 22, 2001,
proposed rule included a
recommendation to use a meter capable
of sampling up to the 50th harmonic.
Sampling up to the 50th harmonic
reduces the chances for measurement
errors, but the extra expense for such a
piece of equipment may not be justified,
so today’s final rule does not require its
use.
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P. Effect of Test Procedure Revisions on
SEER and HSPF
The most significant revisions to the
test procedure in this final rule adopt
industry practices and clear up gray
areas with more precise instructions. No
existing requirements are changed, but
new requirements are added. Based on
its development, review and analysis of
the test procedure revisions being
published today, the Department
believes that these test procedure
revisions will have no material impact
on the measured values of SEER and
HSPF, and thus it has satisfied the
requirement of 42 U.S.C. 6293(e)(1): ‘‘In
the case of any amended test procedure
which is prescribed pursuant to this
section, the Secretary shall determine,
in the rulemaking carried out with
respect to prescribing such procedure,
to what extent, if any, the proposed test
procedure would alter the measured
energy efficiency, measured energy use,
or measured water use of any covered
product as determined under the
existing test procedure.’’ In the January
22, 2001, proposed rule, the Department
asked for comments on this issue (66 FR
6782), and received no comments
contending that these revisions would
impact measured values of SEER and
HSPF.
IV. Procedural Requirements
A. Review Under Executive Order 12866
It has been determined that today’s
regulatory action is not a ‘‘significant
regulatory action’’ under Executive
Order 12866, ‘‘Regulatory Planning and
Review,’’ 58 FR 51735 (October 4, 1993).
Accordingly, this action was not subject
to review under the Executive Order by
the Office of Information and Regulatory
Affairs (OIRA) of the Office of
Management and Budget (OMB) .
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 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
rulemaking process. (68 FR 7990) DOE
has made its procedures and policies
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available on the Office of General
Counsel’s Web site: https://
www.gc.doe.gov.
DOE reviewed today’s rule under the
provisions of the Regulatory Flexibility
Act and the procedures and policies
published on February 19, 2003. DOE
certified in the January 22, 2001,
proposed rule that the proposed rule
would not impose a significant
economic impact on a substantial
number of small entities. (66 FR 6780)
DOE received no comments on this
issue, and after considering the
potential small entity impact of this
final rule, DOE affirms the certification
that this rule will not have a significant
economic impact on a substantial
number of small entities.
C. Review Under the Paperwork
Reduction Act
This rulemaking imposes no new
information or record keeping
requirements under the Paperwork
Reduction Act. (44 U.S.C. 3501 et seq.)
D. Review Under the National
Environmental Policy Act
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 the Department’s
implementing regulations at 10 CFR part
1021. This rule amends an existing rule
without changing its environmental
effect, and, therefore, is covered by the
Categorical Exclusion in paragraph A5
to subpart D, 10 CFR part 1021.
Accordingly, neither an environmental
assessment nor an environmental
impact statement is required.
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
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 today’s rule
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and has determined that it does not
preempt State law and does 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. No further action
is required by Executive Order 13132.
F. Review Under Executive Order 12988
With respect to the review of existing
regulations and the promulgation of
new regulations, section 3(a) of
Executive Order 12988, ‘‘Civil Justice
Reform’’ (61 FR 4729, February 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; and
(3) provide a clear legal standard for
affected conduct rather than a general
standard and 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
review regulations in light of applicable
standards in section 3(a) and section
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, this 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 (Pub. L. 104–4)
(UMRA) requires each Federal agency to
assess the effects of Federal regulatory
actions on State, local, and Tribal
governments and the private sector. For
a proposed regulatory action that may
result in the expenditure by State, local
and Tribal governments, in the
aggregate, or by the private sector of
$100 million or more (adjusted annually
for inflation), section 202 of UMRA
requires a Federal agency to publish
estimates of the resulting costs, benefits,
and other effects on the national
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59133
economy. (2 U.S.C. 1532(a), (b)) 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://
www.gc.doe.gov). The rule published
today contains neither an
intergovernmental mandate, nor a
mandate that may result in an
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 of 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
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 which
might require compensation under the
Fifth Amendment to the United States
Constitution.
J. Review Under the Treasury and
General Government Appropriations
Act of 2001
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 (February 22, 2002), and
DOE’s guidelines were published at 67
FR 62446 (October 7, 2002). DOE has
reviewed today’s notice under the OMB
and DOE guidelines and has concluded
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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 OIRA, 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.
Today’s regulatory action would not
have a significant adverse effect on the
supply, distribution, or use of energy
and, therefore, is not a significant
energy action. Accordingly, DOE has not
prepared a Statement of Energy Effects.
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), the Department of Energy must
comply with section 32 of the Federal
Energy Administration Act of 1974
(FEAA), as amended by the Federal
Energy Administration Authorization
Act of 1977. (15 U.S.C. 788) Section 32
provides in essence that, where a
proposed rule contains or involves use
of commercial standards, the notice of
proposed rulemaking must inform the
public of the use and background of
such standards. This final rule
incorporates nine commercial standards
as discussed in section II.A.1 of this
preamble.
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 which fully provides for
public participation, comment and
review. As required by Section 32(c) of
the FEAA, the Department has
consulted with the Attorney General
and the Chairman of the Federal Trade
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Commission concerning the impact of
these two standards on competition, and
neither recommended against
incorporation of these standards.
M. Congressional Notification
As required by 5 U.S.C. 801, DOE will
report to Congress on the promulgation
of today’s rule prior to its effective date.
The report will state that it has been
determined that the rule is not a ‘‘major
rule’’ as defined by 5 U.S.C. 804(2).
N. Approval of the Office of the
Secretary
The Secretary of Energy has approved
publication of today’s rule.
List of Subjects in 10 CFR Part 430
Administrative practice and
procedure, Energy conservation,
Household appliances, Incorporation by
reference.
Issued in Washington, DC, on July 21,
2005.
Douglas L. Faulkner,
Acting Assistant Secretary, Energy Efficiency
and Renewable Energy.
For the reasons set forth in the
preamble, Part 430 of Chapter II of Title
10, Code of Federal Regulations is
amended as set forth below.
I
PART 430—ENERGY CONSERVATION
PROGRAM FOR CONSUMER
PRODUCTS
1. The authority citation for Part 430
continues to read as follows:
I
Authority: 42 U.S.C. 6291–6309; 28 U.S.C.
2461 note.
2. Section 430.22 is amended:
a. In paragraph (b)(1) by adding
paragraph (b)(1)8.
I b. In paragraph (b)(5) by removing
paragraph (b)(5)2., and adding new
paragraphs (b)(5)2. through (b)(5)9.
I c. By adding paragraph (b)(8).
The additions specified above read as
follows:
I
I
§ 430.22
*
Reference Sources.
*
*
(b) * * *
(1) * * *
*
*
8. ANSI Standard Z21.56–1994, ‘‘Gas-Fired
Pool Heaters,’’ section 2.9.
*
*
*
(5) * * *
*
*
2. American Society of Heating,
Refrigerating, and Air-Conditioning
Engineers Standard 23–1993, ‘‘Methods of
Testing for Rating Positive Displacement
Refrigerant Compressors and Condensing
Units.’’
3. American Society of Heating,
Refrigerating, and Air-Conditioning
Engineers Standard 37–1988, ‘‘Methods of
Testing for Rating Unitary Air-Conditioning
and Heat Pump Equipment.’’
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4. American Society of Heating,
Refrigerating, and Air-Conditioning
Engineers Standard 41.1–1986 (Reaffirmed
2001), ‘‘Standard Method for Temperature
Measurement.’’
5. American Society of Heating,
Refrigerating, and Air-Conditioning
Engineers Standard 41.2–1987 (Reaffirmed
1992), ‘‘Standard Methods for Laboratory
Airflow Measurement.’’
6. American Society of Heating,
Refrigerating, and Air-Conditioning
Engineers Standard 41.6–1994 (Reaffirmed
2001), ‘‘Standard Method for Measurement of
Moist Air Properties.’’
7. American Society of Heating,
Refrigerating, and Air-Conditioning
Engineers Standard 41.9–2000, ‘‘Calorimeter
Test Methods for Mass Flow Measurements
of Volatile Refrigerants.’’
8. American Society of Heating,
Refrigerating, and Air-Conditioning
Engineers Standard 116–1995, ‘‘Methods of
Testing for Rating for Seasonal Efficiency of
Unitary Air Conditioners and Heat Pumps.’’
9. American Society of Heating,
Refrigerating, and Air-Conditioning
Engineers/Air Movement and Control
Association International, Inc. Standard 51–
1999/210–1999, ‘‘Laboratory Methods of
Testing Fans for Aerodynamic Performance
Rating.’’
*
*
*
*
*
(8) Air-Conditioning and Refrigeration
Institute (ARI), 4100 North Fairfax
Drive, Suite 200, Arlington, Virginia
22203–1629, (703) 524–8800, ARI
Standard 210/240–2003, ‘‘Unitary AirConditioning and Air-Source Heat
Pump Equipment.’’
*
*
*
*
*
I 3. Section 430.23 of subpart B is
amended by revising the section
heading, paragraph (m) introductory
heading and paragraph (m)(1), (2), and
(3) to read as follows:
§ 430.23 Test procedure for measures of
energy consumption.
*
*
*
*
*
(m) Central air conditioners and heat
pumps. (1) The estimated annual
operating cost for cooling-only units and
air-source heat pumps shall be one of
the following:
(i) For cooling-only units or the
cooling portion of the estimated annual
operating cost for air-source heat pumps
which provide both heating and cooling,
the product of:
(A) The quotient of the cooling
capacity, in Btu’s per hour, determined
from the steady-state wet-coil test (A or
A2 Test), as described in section 3.2 of
appendix M to this subpart, divided by
the seasonal energy efficiency ratio
(SEER), in Btu’s per watt-hour,
determined from section 4.1 of
appendix M to this subpart;
(B) The representative average use
cycle for cooling of 1,000 hours per
year;
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(C) A conversion factor of 0.001
kilowatt per watt; and
(D) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act, the
resulting product then being rounded
off to the nearest dollar per year.
(ii) For air-source heat pumps which
provide only heating or the heating
portion of the estimated annual
operating cost for air-source heat pumps
which provide both heating and cooling,
the product of:
(A) The quotient of the standardized
design heating requirement, in Btu’s per
hour, nearest to the heating Region IV
minimum design heating requirement,
determined in section 4.2 of appendix
M to this subpart, divided by the
heating seasonal performance factor
(HSPF), in Btu’s per watt-hour,
calculated for heating Region IV
corresponding to the above-mentioned
standardized design heating
requirement and determined in section
4.2 of appendix M to this subpart;
(B) The representative average use
cycle for heating of 2,080 hours per
year;
(C) 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;
(D) A conversion factor of 0.001
kilowatt per watt; and
(E) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act, the
resulting product then being rounded
off to the nearest dollar per year.
(iii) For air-source heat pumps which
provide both heating and cooling, the
estimated annual operating cost is the
sum of the quantity determined in
paragraph (m)(1)(i) of this section added
to the quantity determined in paragraph
(m)(1)(ii) of this section.
(2) The estimated regional annual
operating cost for cooling-only units and
for air-source heat pumps shall be one
of the following:
(i) For cooling-only units or the
cooling portion of the estimated regional
annual operating cost for air-source heat
pumps which provide both heating and
cooling, the product of:
(A) The quotient of the cooling
capacity, in Btu’s per hour, determined
from the steady-state wet-coil test (A or
A2 Test), as described in section 3.2 of
appendix M to this subpart, divided by
the seasonal energy efficiency ratio
(SEER), in Btu’s per watt-hour,
determined from section 4.1 of
appendix M to this subpart;
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(B) The estimated number of regional
cooling load hours per year determined
from Figure 3 in section 4.3 of appendix
M to this subpart;
(C) A conversion factor of 0.001
kilowatts per watt; and
(D) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act, the
resulting product then being rounded
off to the nearest dollar per year.
(ii) For air-source heat pumps which
provide only heating or the heating
portion of the estimated regional annual
operating cost for air-source heat pumps
which provide both heating and cooling,
the product of:
(A) The estimated number of regional
heating load hours per year determined
from Figure 2 in section 4.3 of appendix
M to this subpart;
(B) The quotient of the standardized
design heating requirement, 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 in
section 4.2 of appendix M to this
subpart, divided by the heating seasonal
performance factor (HSPF), in Btu’s per
watt-hour, calculated for the appropriate
generalized climatic region of interest
and corresponding to the abovementioned standardized design heating
requirement while being determined in
section 4.2 of appendix M to this
subpart;
(C) 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;
(D) A conversion factor of 0.001
kilowatts per watt; and
(E) The representative average unit
cost of electricity in dollars per
kilowatt-hour as provided pursuant to
section 323(b)(2) of the Act, the
resulting product then being rounded
off to the nearest dollar per year.
(iii) For air-source heat pumps which
provide both heating and cooling, the
estimated regional annual operating cost
is the sum of the quantity determined in
paragraph (m)(3)(i) of this section added
to the quantity determined in paragraph
(m)(3)(ii) of this section.
(3) The measure(s) of efficiency of
performance for cooling-only units and
air-source heat pumps shall be one or
more of the following:
(i) The cooling mode efficiency
measure for cooling-only units and airsource heat pumps which provide
cooling shall be the seasonal energy
efficiency ratio (SEER), in Btu’s per
watt-hour, determined according to
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59135
section 4.1 of appendix M to this
subpart, rounded off to the nearest 0.05.
(ii) The heating mode efficiency
measure for air-source heat pumps shall
be the heating seasonal performance
factors (HSPF), in Btu’s per watt-hour,
determined according to section 4.2 of
appendix M to this subpart for each
applicable standardized design heating
requirement within each climatic
region, rounded off to the nearest 0.05.
(iii) The annual efficiency measure for
air-source heat pumps which provide
heating and cooling, shall be the annual
performance factors (APF), in Btu’s per
watt-hour, determined according to
section 4.3 of appendix M to this
subpart for each standardized design
heating requirement within each
climatic region, rounded off to the
nearest 0.05.
*
*
*
*
*
I 4. Section 430.24 of subpart B is
amended by revising the introductory
text for paragraph (m)(1) to read as
follows:
§ 430.24
Units to be tested.
*
*
*
*
*
(m)(1) For central air conditioners and
heat pumps, each condensing unit
(outdoor unit) shall have a condenserevaporator (outdoor coil-indoor coil)
combination selected and a sample of
sufficient size tested in accordance with
applicable provisions of this subpart
such that
*
*
*
*
*
I 5. Appendix M to Subpart B is revised
to read as follows:
Appendix M to Subpart B of Part 430—
Uniform Test Method for Measuring the
Energy Consumption of Central Air
Conditioners and Heat Pumps
1. DEFINITIONS
2. TESTING CONDITIONS
2.1 Test room requirements.
2.2 Test unit installation requirements.
2.2.1 Defrost control settings.
2.2.2 Special requirements for units
having a multiple-speed outdoor fan.
2.2.3 Special requirements for multi-split
air conditioners and heat pumps, and
systems composed of multiple mini-split
units (outdoor units located side-by-side) that
would normally operate using two or more
indoor thermostats.
2.2.4 Wet-bulb temperature requirements
for the air entering the indoor and outdoor
coils.
2.2.4.1 Cooling mode tests.
2.2.4.2 Heating mode tests.
2.2.5 Additional refrigerant charging
requirements.
2.3 Indoor air volume rates.
2.3.1 Cooling tests.
2.3.2 Heating tests.
2.4 Indoor coil inlet and outlet duct
connections.
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2.4.1 Outlet plenum for the indoor unit.
2.4.2 Inlet plenum for the indoor unit.
2.5 Indoor coil air property
measurements and air damper box
applications.
2.5.1 Test set-up on the inlet side of the
indoor coil: For cases where the inlet damper
box is installed.
2.5.1.1 If the section 2.4.2 inlet plenum is
installed.
2.5.1.2 If the section 2.4.2 inlet plenum is
not installed.
2.5.2 Test set-up on the inlet side of the
indoor unit: For cases where no inlet damper
box is installed.
2.5.3 Indoor coil static pressure
difference measurement.
2.5.4 Test set-up on the outlet side of the
indoor coil.
2.5.4.1 Outlet air damper box placement
and requirements.
2.5.4.2 Procedures to minimize
temperature maldistribution.
2.5.5 Dry bulb temperature measurement.
2.5.6 Water vapor content measurement.
2.5.7 Air damper box performance
requirements.
2.6 Airflow measuring apparatus.
2.7 Electrical voltage supply.
2.8 Electrical power and energy
measurements.
2.9 Time measurements.
2.10 Test apparatus for the secondary
space conditioning capacity measurement.
2.10.1 Outdoor Air Enthalpy Method.
2.10.2 Compressor Calibration Method.
2.10.3 Refrigerant Enthalpy Method.
2.11 Measurement of test room ambient
conditions.
2.12 Measurement of indoor fan speed.
2.13 Measurement of barometric pressure.
3. TESTING PROCEDURES
3.1 General Requirements.
3.1.1 Primary and secondary test
methods.
3.1.2 Manufacturer-provided equipment
overrides.
3.1.3 Airflow through the outdoor coil.
3.1.4 Airflow through the indoor coil.
3.1.4.1 Cooling Certified Air Volume
Rate.
3.1.4.1.1 Cooling Certified Air Volume
Rate for Ducted Units.
3.1.4.1.2 Cooling Certified Air Volume
Rate for Non-ducted Units.
3.1.4.2 Cooling Minimum Air Volume
Rate.
3.1.4.3 Cooling Intermediate Air Volume
Rate.
3.1.4.4 Heating Certified Air Volume
Rate.
3.1.4.4.1 Ducted heat pumps where the
Heating and Cooling Certified Air Volume
Rates are the same.
3.1.4.4.2 Ducted heat pumps where the
Heating and Cooling Certified Air Volume
Rates are different due to indoor fan
operation.
3.1.4.4.3 Ducted heating-only heat
pumps.
3.1.4.4.4 Non-ducted heat pumps,
including non-ducted heating-only heat
pumps.
3.1.4.5 Heating Minimum Air Volume
Rate.
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3.1.4.6 Heating Intermediate Air Volume
Rate.
3.1.4.7 Heating Nominal Air Volume
Rate.
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.
3.1.6 Air volume rate calculations.
3.1.7 Test sequence.
3.1.8 Requirement for the air temperature
distribution leaving the indoor coil.
3.1.9 Control of auxiliary resistive heating
elements.
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 that is tested with a fixedspeed indoor fan installed, with a constantair-volume-rate indoor fan installed, or with
no indoor fan installed.
3.2.2 Tests for a unit having a singlespeed compressor and a variable-speed
variable-air-volume-rate indoor fan installed.
3.2.2.1 Indoor fan capacity modulation
that correlates with the outdoor dry bulb
temperature.
3.2.2.2 Indoor fan capacity modulation
based on adjusting the sensible to total (S/T)
cooling capacity ratio.
3.2.3 Tests for a unit having a twocapacity compressor.
3.2.4 Tests for a unit having a variablespeed compressor.
3.3 Test procedures for steady-state wet
coil cooling mode tests (the A, A2, A1, B, B2,
B1, EV, and F1 Tests).
3.4 Test procedures for the optional
steady-state dry coil cooling mode tests (the
C, C1, and G1 Tests).
3.5 Test procedures for the optional
cyclic dry coil cooling mode tests (the D, D1,
and I1 Tests).
3.5.1 Procedures when testing ducted
systems.
3.5.2 Procedures when testing nonducted systems.
3.5.3 Cooling mode cyclic degradation
coefficient calculation.
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 fan installed, with a
constant-air-volume-rate indoor fan installed,
or with no indoor fan installed.
3.6.2 Tests for a heat pump having a
single-speed compressor and a variablespeed, variable-air-volume-rate indoor fan:
capacity modulation correlates with outdoor
dry bulb temperature.
3.6.3 Tests for a heat pump having a twocapacity compressor (see Definition 1.45),
including two-capacity, northern heat pumps
(see Definition 1.46).
3.6.4 Tests for a heat pump having a
variable-speed compressor.
3.6.5 Additional test for a heat pump
having a heat comfort controller.
3.7 Test procedures for steady-state
Maximum Temperature and High
Temperature heating mode tests (the H01, H1,
H12, H11, and H1N Tests).
3.8 Test procedures for the optional
cyclic heating mode tests (the H0C1, H1C,
and H1C1 Tests).
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3.8.1 Heating mode cyclic degradation
coefficient calculation.
3.9 Test procedures for Frost
Accumulation heating mode tests (the H2,
H22, H2V, and H21 Tests).
3.9.1 Average space heating capacity and
electrical power calculations.
3.9.2 Demand defrost credit.
3.10 Test procedures for steady-state Low
Temperature heating mode tests (the H3, H32,
and H31 Tests).
3.11 Additional requirements for the
secondary test methods.
3.11.1 If using the Outdoor Air Enthalpy
Method as the secondary test method.
3.11.1.1 If a preliminary test precedes the
official test
3.11.1.2 If a preliminary test does not
precede the official test.
3.11.1.3 Official test.
3.11.2 If using the Compressor
Calibration Method as the secondary test
method.
3.11.3 If using the Refrigerant Enthalpy
Method as the secondary test method.
3.12 Rounding of space conditioning
capacities for reporting purposes.
4. CALCULATIONS OF SEASONAL
PERFORMANCE DESCRIPTORS
4.1 Seasonal Energy Efficiency Ratio
(SEER) Calculations.
4.1.1 SEER calculations for an air
conditioner or heat pump having a singlespeed compressor that was tested with a
fixed-speed indoor fan installed, a constantair-volume-rate indoor fan installed, or with
no indoor fan installed.
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 fan.
4.1.2.1 Units covered by section 3.2.2.1
where indoor fan capacity modulation
correlates with the outdoor dry bulb
temperature.
4.1.2.2 Units covered by section 3.2.2.2
where indoor fan capacity modulation is
used to adjust the sensible to total cooling
capacity ratio.
4.1.3 SEER calculations for an air
conditioner or heat pump having a twocapacity compressor.
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).
4.1.3.2 Unit alternates between high (k=2)
and low (k=1) compressor capacity to satisfy
the building cooling load at temperature Tj,
˙
˙
Qck=1(Tj) < BL(Tj) < Qck=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).
4.1.3.4 Unit must operate continuously at
high (k=2) compressor capacity at
˙
temperature Tj, BL(Tj) ≥ Qck=2(Tj).
4.1.4 SEER calculations for an air
conditioner or heat pump having a variablespeed compressor.
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).
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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).
4.1.4.3 Unit must operate continuously at
maximum (k=2) compressor speed at
˙
temperature Tj, BL(Tj) ≥ Qck=2(Tj).
4.2 Heating Seasonal Performance Factor
(HSPF) Calculations.
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 fan installed, a constant-airvolume-rate indoor fan installed, or with no
indoor fan installed.
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 fan.
4.2.3 Additional steps for calculating the
HSPF of a heat pump having a two-capacity
compressor.
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).
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).
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).
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.
4.2.4.1 Steady-state space heating
capacity when operating at minimum
compressor speed is greater than or equal to
the building heating load at temperature Tj,
˙
Qhk=1(Tj) ≥ BL(Tj).
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).
4.2.4.3 Heat pump must operate
continuously at maximum (k=2) compressor
˙
speed at temperature Tj, BL(Tj) ≥ Qhk=2(Tj).
4.2.5 Heat pumps having a 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 singlespeed compressor that was tested with a
fixed-speed indoor fan installed, a constantair-volume-rate indoor fan installed, or with
no indoor fan installed.
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 fan.
4.2.5.3 Heat pumps having a heat comfort
controller: Additional steps for calculating
the HSPF of a heat pump having a twocapacity compressor.
4.2.5.4 Heat pumps having a heat comfort
controller: Additional steps for calculating
the HSPF of a heat pump having a variablespeed compressor. [Reserved]
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4.3 Calculations of the Actual and
Representative Regional Annual Performance
Factors for Heat Pumps.
4.3.1 Calculation of actual regional
annual performance factors (APFA) for a
particular location and for each standardized
design heating requirement.
4.3.2 Calculation of representative
regional annual performance factors (APFR)
for each generalized climatic region and for
each standardized design heating
requirement.
4.4 Rounding of SEER, HSPF, and APF
for reporting purposes.
1. Definitions
1.1 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. Paragraph (m)(3)(iii) of § 430.23 of
the Code of Federal Regulations states the
calculation requirements for this rating
descriptor.
1.2 ARI means Air-Conditioning and
Refrigeration Institute.
1.3 ARI Standard 210/240–2003 means
the test standard ‘‘Unitary Air-Conditioning
and Air-Source Heat Pump Equipment’’
published in 2003 by ARI.
1.4 ASHRAE means the American Society
of Heating, Refrigerating and AirConditioning Engineers, Inc.
1.5 ASHRAE Standard 23–93 means the
test standard ‘‘Methods of Testing for Rating
Positive Displacement Refrigerant
Compressors and Condensing Units’’
published in 1993 by ASHRAE.
1.6 ASHRAE Standard 37–88 means the
test standard ‘‘Methods of Testing for Rating
Unitary Air-Conditioning and Heat Pump
Equipment’’ published in 1988 by ASHRAE.
1.7 ASHRAE Standard 41.1–86 (RA 01)
means the test standard ‘‘Standard Method
for Temperature Measurement’’ published in
1986 and reaffirmed in 2001 by ASHRAE.
1.8 ASHRAE Standard 41.2–87 (RA 92)
means the test standard ‘‘Standard Methods
for Laboratory Airflow Measurement’’
published in 1987 and reaffirmed in 1992 by
ASHRAE.
1.9 ASHRAE Standard 41.6–94 (RA 01)
means the test standard ‘‘Method for
Measurement of Moist Air Properties’’
published in 1994 and reaffirmed in 2001 by
ASHRAE.
1.10 ASHRAE Standard 41.9–00 means
the test standard ‘‘Calorimeter Test Methods
for Mass Flow Measurements of Volatile
Refrigerants’’ published in 2000 by ASHRAE.
1.11 ASHRAE Standard 51–99/AMCA
Standard 210–1999 means the test standard
‘‘Laboratory Methods of Testing Fans for
Aerodynamic Performance Rating’’ published
in 1999 by ASHRAE and the Air Movement
and Control Association International, Inc.
1.12 ASHRAE Standard 116–95 means
the test standard ‘‘Methods of Testing for
Rating for Seasonal Efficiency of Unitary Air
Conditioners and Heat Pumps’’ published in
1995 by ASHRAE.
1.13 CFR means Code of Federal
Regulations.
1.14 Constant-air-volume-rate indoor fan
means a fan that varies its operating speed to
provide a fixed air-volume-rate from a ducted
system.
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1.15 Continuously recorded, when
referring to a dry bulb measurement, means
that the specified temperature must be
sampled at regular intervals that are equal to
or less than the maximum intervals specified
in section 4.3 part ‘‘a’’ of ASHRAE Standard
41.1–86 (RA 01). If such dry bulb
temperatures are used only for test room
control, it means that one samples at regular
intervals equal to or less than the maximum
intervals specified in section 4.3 part ‘‘b’’ of
the same ASHRAE Standard. Regarding wet
bulb temperature, dew point temperature, or
relative humidity measurements,
continuously recorded means that the
measurements must be made at regular
intervals that are equal to or less than 1
minute.
1.16 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 space cooling
capacity for the same total time (ON + OFF)
interval.
1.17 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 tied to a single set
of operating conditions. COP is a
dimensionless quantity. When determined
for a ducted unit tested without an indoor fan
installed, COP must include the section 3.7,
3.8, and 3.9.1 default values for the heat
output and power input of a fan motor.
1.18 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.
1.19 Damper box means a short section of
duct having an air damper that meets the
performance requirements of section 2.5.7.
1.20 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.
1.21 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, etc.) 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.1 In all cases, when the frost
parameter(s) reaches a predetermined value,
1 Systems that vary defrost intervals according to
outdoor dry-bulb temperature are not demand
defrost systems.
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the system initiates a defrost. In a demanddefrost control system, defrosts are
terminated based on monitoring a
parameter(s) that indicates that frost has been
eliminated from the coil.
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.
1.22 Design heating requirement (DHR)
predicts the space heating load of a residence
when subjected to outdoor design conditions.
Estimates for the minimum and maximum
DHR are provided for six generalized U.S.
climatic regions in section 4.2.
1.23 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.
1.24 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-packaged unit.
1.25 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 tied to a single set
of operating conditions. EER is expressed in
units of
Btu / h
.
W
When determined for a ducted unit tested
without an indoor fan 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.
1.26 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.
1.27 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), Subpart C)
is based on Region IV, the minimum
standardized design heating requirement,
and the sampling plan stated in 10 CFR
430.24(m), Subpart B.
1.28 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
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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.
1.29 Mini-split air conditioners and heat
pumps means systems that have a single
outdoor section and one or more indoor
sections. The indoor sections cycle on and off
in unison in response to a single indoor
thermostat.
1.30 Multiple-split air conditioners and
heat pumps means systems that have two or
more indoor sections. The indoor sections
operate independently and can be used to
condition multiple zones in response to
multiple indoor thermostats.
1.31 Non-ducted system means an air
conditioner or heat pump that is designed to
be permanently installed equipment and
directly heats or cools air within the
conditioned space using one or more indoor
coils that are mounted on room walls and/
or ceilings. The unit may be of a modular
design that allows for combining multiple
outdoor coils and compressors to create one
overall system. Non-ducted systems covered
by this test procedure are all split systems.
1.32 Part-load factor (PLF) means the
ratio of the cyclic energy efficiency ratio
(coefficient of performance) to the steadystate energy efficiency ratio (coefficient of
performance). Evaluate both energy
efficiency ratios (coefficients of performance)
based on operation at the same ambient
conditions.
1.33 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 air conditioner or heat pump during the
same season, expressed in watt-hours. The
SEER calculation in section 4.1 of this
Appendix and the sampling plan stated in 10
CFR Subpart B, 430.24(m) are used to
evaluate compliance with the Energy
Conservation Standards. (See 10 CFR
430.32(c), Subpart C.)
1.34 Single-packaged unit means any
central air conditioner or heat pump that has
all major assemblies enclosed in one cabinet.
1.35 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 certified 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.
1.36 Split system means any air
conditioner or heat pump that has one or
more of the major assemblies separated from
the others.
1.37 Standard Air means dry air at 70 °F
and 14.696 psia. Under these conditions, dry
air has a mass density of 0.075 lb/ft3.
1.38 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.
1.39 Temperature bin means the 5 °F
increments that are used to partition the
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outdoor dry-bulb temperature ranges of the
cooling (≥ 65 °F) and heating (< 65 °F)
seasons.
1.40 Test condition tolerance means the
maximum permissible difference between the
average value of the measured test parameter
and the specified test condition.
1.41 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
must be less than or equal to the specified
test operating tolerance.
1.42 Time adaptive defrost control system
is a demand-defrost control system (see
definition 1.21) that measures the length of
the prior defrost period(s) and uses that
information to automatically determine when
to initiate the next defrost cycle.
1.43 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 ONtime counter is reset regardless of whether 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 1.21).
1.44 Triple-split system means an air
conditioner or heat pump that is composed
of three separate components: An outdoor fan
coil section, an indoor fan coil section, and
an indoor compressor section.
1.45 Two-capacity (or two-stage)
compressor means an air conditioner or heat
pump that has one of the following:
(1) A two-speed compressor,
(2) Two compressors where only one
compressor ever operates at a time,
(3) Two compressors where one
compressor (Compressor #1) operates at low
loads and both compressors (Compressors #1
and #2) operate at high loads but Compressor
#2 never operates alone, or
(4) A compressor that is capable of cylinder
or scroll unloading.
For such systems, low capacity means:
(1) Operating at low compressor speed,
(2) Operating the lower capacity
compressor,
(3) Operating Compressor #1, or
(4) Operating with the compressor
unloaded (e.g., operating one piston of a twopiston reciprocating compressor, using a
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fixed fractional volume of the full scroll,
etc.).
For such systems, high capacity means:
(1) Operating at high compressor speed,
(2) Operating the higher capacity
compressor,
(3) Operating Compressors #1 and #2, or
(4) Operating with the compressor loaded
(e.g., operating both pistons of a two-piston
reciprocating compressor, using the full
volume of the scroll).
1.46 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 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.
1.47 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 Conditions
This test procedure covers split-type and
single-packaged ducted units and split-type
non-ducted units. Except for units having a
variable-speed compressor, ducted units
tested without an indoor fan installed are
covered.
a. Only a subset of the sections listed in
this test procedure apply when testing and
rating a particular unit. Tables 1–A through
1–C show which sections of the test
procedure apply to each type of equipment.
In each table, look at all four of the Roman
numeral categories to see what test sections
apply to the equipment being tested.
1. The first category, Rows I–1 through I–
4 of the Tables, pertains to the compressor
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and indoor fan features of the equipment.
After identifying the correct ‘‘I’’ row, find the
table cells in the same row that list the type
of equipment being tested: Air conditioner
(AC), heat pump (HP), or heating-only heat
pump (HH). Use the test section(s) listed
above each noted table cell for testing and
rating the unit.
2. The second category, Rows II–1 and II–
2, pertains to the presence or absence of
ducts. Row II–1 shows the test procedure
sections that apply to ducted systems, and
Row II–2 shows those that apply to nonducted systems.
3. The third category is for special features
that may be present in the equipment. When
testing units that have one or more of the
three (special) equipment features described
by the Table legend for Category III, use Row
III to find test sections that apply.
4. The fourth category is for the secondary
test method to be used. If the secondary
method for determining the unit’s cooling
and/or heating capacity is known, use Row
IV to find the appropriate test sections.
Otherwise, include all of the test sections
referenced by Row IV cell entries—i.e.,
sections 2.10 to 2.10.3 and 3.11 to 3.11.3—
among those sections consulted for testing
and rating information.
b. Obtain a complete listing of all pertinent
test sections by recording those sections
identified from the four categories above.
c. The user should note that, for many
sections, only part of a section applies to the
unit being tested. In a few cases, the entire
section may not apply. For example, sections
3.4 to 3.5.3 (which describe optional dry coil
tests), are not relevant if the allowed default
value for the cooling mode cyclic degradation
coefficient is used rather than determining it
by testing.
Example for Using Tables 1–A to 1–C
Equipment Description: A ducted air
conditioner having a single-speed
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compressor, a fixed-speed indoor fan, and a
multi-speed outdoor fan.
Secondary Test Method: Refrigerant
Enthalpy Method
Step 1. Determine which of four listed Row
‘‘I’’ options applies ==> Row I–2
Table 1–A: ‘‘AC’’ in Row I–2 is found in
the columns for sections 1.1 to 1.47, 2.1 to
2.2, 2.2.4 to 2.2.4.1, 2.2.5, 2.3 to 2.3.1, 2.4 to
2.4.1, 2.5, 2.5.2 to 2.10, and 2.11 to 2.13.
Table 1–B: ‘‘AC’’ is listed in Row I–2 for
sections 3 to 3.1.4, 3.1.5 to 3.1.8, 3.2.1, 3.3
to 3.5, 3.5.3, 3.11 and 3.12.
Table 1–C: ‘‘AC’’ is listed in Row I–2 for
sections 4.1.1 and 4.4.
Step 2. Equipment is ducted ==> Row II–
1
Table 1–A: ‘‘AC’’ is listed in Row II–1 for
sections 2.4.2 and 2.5.1 to 2.5.1.2.
Table 1–B: ‘‘AC’’ is listed in Row II–1 for
sections 3.1.4.1 to 3.1.4.1.1 and 3.5.1.
Table 1–C: no ‘‘AC’’ listings in Row II–1.
Step 3. Equipment Special Features
include multi-speed outdoor fan ==> Row III,
M
Table 1–A: ‘‘M’’ is listed in Row III for
section 2.2.2
Tables 1–B and 1–C: no ‘‘M’’ listings in
Row III.
Step 4. Secondary Test Method is
Refrigerant Enthalpy Method ==> Row IV, R
Table 1–A: ‘‘R’’ is listed in Row IV for
section 2.10.3
Table 1–B: ‘‘R’’ is listed in Row IV for
section 3.11.3
Table 1–C: no ‘‘R’’ listings in Row IV.
Step 5. Cumulative listing of applicable
test procedure sections 1.1 to 1.47, 2.1 to 2.2,
2.2.2, 2.2.4 to 2.4.1, 2.2.5, 2.3 to 2.3.1, 2.4 to
2.4.1, 2.4.2, 2.5, 2.5.1 to 2.5.1.2, 2.5.2 to 2.10,
2.10.3, 2.11 to 2.13, 3. to 3.1.4, 3.1.4.1 to
3.1.4.1.1, 3.1.5 to 3.1.8, 3.2.1, 3.3 to 3.5, 3.5.1,
3.5.3, 3.11, 3.11.3, 3.12, 4.1.1, and 4.4.
BILLING CODE 6450–01–U
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2.1 Test room requirements. a. Test using
two side-by-side rooms, an indoor test room
and an outdoor test room. These rooms must
comply with the requirements specified in
sections 8.1.2 and 8.1.3 of ASHRAE Standard
37–88 (incorporated by reference, see
§ 430.22).
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 8.6 of
ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22). With respect to
interconnecting tubing used when testing
split systems, however, follow the
requirements given in section 6.1.3.5 of ARI
Standard 210/240–2003 (incorporated by
reference, see § 430.22). When testing triplesplit systems (see Definition 1.44), use the
tubing length specified in section 6.1.3.5 of
ARI Standard 210/240–2003 (incorporated by
reference, see § 430.22) 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. When testing nonducted systems having multiple indoor coils,
connect each indoor fan-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 8.6.5 of ASHRAE
Standard 37–88 (incorporated by reference,
see § 430.22). 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 foam insulation
having an inside diameter that matches the
refrigerant tubing and a nominal thickness of
1⁄2 inch.
b. For units designed for both horizontal
and vertical installation or for both up-flow
and down-flow vertical installations, the
manufacturer must specify the orientation
used for testing. 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
Definition 1.28).
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 2,
note 3 (see section 3.1.4). Except as noted in
section 3.1.9, prevent the indoor air
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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.
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 2 and Table 17 of section 4.2 for
information on region IV.) For heat pumps
that use a time-adaptive defrost control
system (see Definition 1.42), 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 manufacturer’s
specifications, 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, and
systems composed of multiple mini-split
units (outdoor units located side-by-side) that
would normally operate using two or more
indoor thermostats. During the steady-state
tests, shunt all thermostats to make all indoor
fan-coil units operate simultaneously. To
ease the testing burden of cyclic tests,
consider creating a single control circuit that
allows simultaneous cycling of all
compressor systems. For these systems, the
test procedure references to a single indoor
fan, outdoor fan, and compressor means all
indoor fans, all outdoor fans, and all
compressor systems.
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 3 to 6. 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 3–
6 list the applicable wet-bulb temperatures.
(2) Single-packaged units where all or part
of the indoor section is located in the outdoor
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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 9 to 12. 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 single-packaged 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. Charging according to the
‘‘manufacturer’s instructions,’’ as stated in
section 8.6 of ASHRAE Standard 37–88
(incorporated by reference, see § 430.22),
means the manufacturer’s installation
instructions that come packaged with the
unit. If a unit requires charging but the
installation instructions do not specify a
charging procedure, then evacuate the unit
and add the nameplate refrigerant charge.
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. 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
manufacturer may specify an alternative
charging criteria to the third-party laboratory
so long as the manufacturer thereafter revises
the published installation instructions
accordingly.
2.3 Indoor air volume rates. If a unit’s
controls allow for overspeeding the indoor
fan (usually on a temporary basis), take the
necessary steps to prevent overspeeding
during all tests.
2.3.1 Cooling tests. a. Set indoor fan
control options (e.g., fan motor pin settings,
fan motor speed) according to the published
installation instructions that are provided
with the equipment while meeting the
airflow requirements that are specified in
sections 3.1.4.1 to 3.1.4.3.
b. Express the Cooling Certified 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 fan control options (e.g., fan motor
pin settings, fan motor speed) according to
the published installation instructions that
are provided with the equipment. Do this setup while meeting all applicable airflow
requirements specified in sections 3.1.4.4 to
3.1.4.7.
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b. Express the Heating Certified 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 sistance (R-value) of at
least 19 hr·ft2·°F/Btu.
2.4.1 Outlet plenum for the indoor unit.
Attach a plenum to the outlet of the indoor
coil. (Note: for some packaged systems, the
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indoor coil may be located in the outdoor test
room.) For non-ducted systems having
multiple indoor coils, attach a plenum to
each indoor coil outlet. 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. Figure
1 shows two of the three options allowed for
the manifold configuration; the third option
is the broken-ring, four-to-one manifold
configuration that is shown in Figure 7 of
ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22). See Figures 7 and 8
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of ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22) for the cross-sectional
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 fan installed. For a
non-ducted system having multiple indoor
coils, have all outlet plenums discharge air
into a single common duct. At the plane
where each plenum enters the common duct,
install an adjustable airflow damper and use
it to equalize the static pressure in each
plenum.
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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
Figure 8 of ASHRAE Standard 37–88
(incorporated by reference, see § 430.22) 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 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. If used, construct the inlet plenum
and add the four static pressure taps as
shown in Figure 8 of ASHRAE Standard 37–
88 (incorporated by reference, see § 430.22).
Manifold the four static pressure taps using
one of the three configurations specified in
section 2.4.1. Never use an inlet plenum
when testing a non-ducted system.
2.5 Indoor coil air property
measurements and air damper box
applications. 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 Figure 2 of
ASHRAE Standard 41.1–86 (RA 01)
(incorporated by reference, see § 430.22) for
guidance on constructing an air sampling
device. 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
when testing ducted systems if conducting
one or both of the cyclic tests listed in
sections 3.2 and 3.6. Otherwise, install an
outlet air damper box when testing heat
pumps, both ducted and non-ducted, that
cycle off the indoor fan during defrost cycles
if no other means is available for preventing
natural or forced convection through the
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indoor unit when the indoor fan is off. Never
use an inlet damper box when testing a nonducted system.
2.5.1 Test set-up on the inlet side of the
indoor coil: for cases where the inlet damper
box is installed. a. Install the inlet side
damper box as specified in section 2.5.1.1 or
2.5.1.2, whichever applies. Insulate or
construct the ductwork between the point
where the air damper is installed and where
the connection is made to either the inlet
plenum (section 2.5.1.1 units) or the indoor
unit (section 2.5.1.2 units) with thermal
insulation that has a nominal overall
resistance (R-value) of at least 19 hr·ft2·°F/
Btu.
b. Locate the grid of entering air dry-bulb
temperature sensors, if used, at the inlet of
the damper box. Locate 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.
2.5.1.1 If the section 2.4.2 inlet plenum is
installed. Install the inlet damper box
upstream of the inlet plenum. The crosssectional flow area of the damper box must
be equal to or greater than the flow area of
the inlet plenum. If needed, use an adaptor
plate or a transition duct section to connect
the damper box with the inlet plenum.
2.5.1.2 If the section 2.4.2 inlet plenum is
not installed. Install the damper box
immediately upstream of the air inlet of the
indoor unit. The cross-sectional dimensions
of the damper box must be equal to or greater
than the dimensions of the indoor unit inlet.
If needed, use an adaptor plate or a short
transition duct section to connect the damper
box with the unit’s air inlet. Add static
pressure taps at the center of each face of the
damper box, if rectangular, or at four evenly
distributed locations along the
circumference, if oval or round. Locate the
pressure taps between the inlet damper and
the inlet of the indoor unit. Make a manifold
that connects the four static pressure taps.
2.5.2 Test set-up on the inlet side of the
indoor unit: for cases where no inlet damper
box 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 6.4.4.1 of
ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22) describes the method
for fabricating static pressure taps. Also refer
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to Figure 2A of ASHRAE Standard 51–99/
AMCA Standard 210–99 (incorporated by
reference, see § 430.22). 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 air damper box. If an
inlet plenum or inlet damper box are 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 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 point:
(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
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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 6.3—6.5 of
ASHRAE Standard 41.1–86 (RA 01)
(incorporated by reference, see § 430.22) and
section 5.2.2 of ASHRAE Standard 41.2–87
(RA 92) (incorporated by reference, see
§ 430.22).
2.5.5 Dry bulb temperature measurement.
a. Measure dry bulb temperatures as
specified in sections 4, 5, 6.1–6.10, 9, 10, and
11 of ASHRAE Standard 41.1–86 (RA 01)
(incorporated by reference, see § 430.22). The
transient testing requirements cited in
section 4.3 of ASHRAE Standard 41.1–86 (RA
01) (incorporated by reference, see § 430.22)
apply if conducting a cyclic or frost
accumulation test.
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, 9, 10,
and 11 of ASHRAE Standard 41.1–86 (RA 01)
(incorporated by reference, see § 430.22). As
specified in ASHRAE 41.1–86 (RA 01)
(incorporated by reference, see § 430.22), the
temperature sensor (wick removed) must be
accurate to within ±0.2 °F. If used, apply dew
point hygrometers as specified in sections 5
and 8 of ASHRAE Standard 41.6–94 (RA 01)
(incorporated by reference, see § 430.22). 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 6.6 of
ASHRAE Standard 116–95 (incorporated by
reference, see § 430.22). Refer to Figure 12 of
ASHRAE Standard 51–99/AMCA Standard
210–99 (incorporated by reference, see
§ 430.22) or Figure 14 of ASHRAE Standard
41.2–87 (RA 92) (incorporated by reference,
see § 430.22) for guidance on placing the
static pressure taps and positioning the
diffusion baffle (settling means) relative to
the chamber inlet.
b. Connect the airflow measuring apparatus
to the interconnecting duct section described
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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 37–88 (incorporated by reference,
see § 430.22), and Figures D1, D2, and D4 of
ARI Standard 210/240–2003 (incorporated by
reference, see § 430.22) 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 37–88 (incorporated by reference,
see § 430.22) when testing triple-split units.)
2.7 Electrical voltage supply. Perform all
tests at the voltage specified in section 6.1.3.2
of ARI Standard 210/240–2003 (incorporated
by reference, see § 430.22) for ‘‘Standard
Rating Tests.’’ 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 non-ducted 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 watthour 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 fan OFF. For
ducted units tested without an indoor fan
installed, the ON cycle lasts from compressor
ON to compressor OFF. For non-ducted
units, the ON cycle lasts from indoor fan ON
to indoor fan 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
fan 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 fan or a variable-speed, variable-airvolume-rate indoor fan.
2.9 Time measurements. Make elapsed
time measurements using an instrument that
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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 single
packaged 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) 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
optional temperature grid (sections 2.5 and
2.5.2).
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, connect pressure gages to
the access valves or to ports created from
tapping into the suction and discharge lines.
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
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refrigerant charge according to section 7.4.2
of ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22). Use refrigerant
temperature and pressure measuring
instruments that meet the specifications
given in sections 5.1.1 and 5.2 of ASHRAE
Standard 37–88 (incorporated by reference,
see § 430.22).
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 7.6.2 of ASHRAE Standard 37–
88 (incorporated by reference, see § 430.22)
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 37–88 (incorporated by
reference, see § 430.22).
2.11 Measurement of test room ambient
conditions. 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-Enthalpy Test Method
Arrangement, of ASHRAE Standard 37–88
(incorporated by reference, see § 430.22)),
add instrumentation to permit measurement
of the indoor test room dry-bulb temperature.
b. If the Outdoor Air Enthalpy Method is
not used, add instrumentation to measure the
dry-bulb temperature and the water vapor
content of the air entering the outdoor coil.
If an air sampling device is used, construct
and apply the device as per section 6 of
ASHRAE Standard 41.1–86 (RA 01)
(incorporated by reference, see § 430.22).
Take steps (e.g., add or re-position a lab
circulating fan), as needed, to minimize the
magnitude of the temperature distribution
non-uniformity. Position any fan in the
outdoor test room while trying to keep air
velocities in the vicinity of the test unit
below 500 feet per minute.
c. Measure dry bulb temperatures as
specified in sections 4, 5, 6.1–6.10, 9, 10, and
11 of ASHRAE Standard 41.1–86 (RA 01)
(incorporated by reference, see § 430.22).
Measure water vapor content as stated above
in section 2.5.6.
2.12 Measurement of indoor fan 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 37–88
(incorporated by reference, see § 430.22).
3. Testing Procedures
3.1 General Requirements. If, during the
testing process, an equipment set-up
adjustment is made that would alter the
performance of the unit when conducting an
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.
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 steady-state 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 37–88 (incorporated by reference,
see § 430.22) (and do not make the after-test
fan heat adjustments described in sections
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 fan 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 ARI Standard 210/240–
2003 (incorporated by reference, see § 430.22)
59149
when obtaining the airflow through the
outdoor coil.
3.1.4 Airflow through the indoor coil.
3.1.4.1 Cooling Certified Air Volume
Rate.
3.1.4.1.1 Cooling Certified Air Volume
Rate for Ducted Units. The manufacturer
must specify the Cooling Certified Air
Volume Rate. Use this value as long as the
following two requirements are satisfied.
First, when conducting the A or A2 Test
(exclusively), the measured air volume rate,
when divided by the measured indoor airside 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 Certified Air Volume Rate. The
second requirement is as follows:
a. For ducted units that are tested with a
fixed-speed, multi-speed, or variable-speed
variable-air-volume-rate indoor fan installed.
For the A or A2 Test (exclusively), the
measured external static pressure must be
equal to or greater than the applicable
minimum external static pressure cited in
Table 2. If the Table 2 minimum is not
equaled or exceeded, incrementally change
the set-up of the indoor fan (e.g., fan motor
pin settings, fan motor speed) until the Table
2 requirement is met while maintaining the
same air volume rate. If the indoor fan setup changes cannot provide the minimum
external static, then reduce the air volume
rate until the correct Table 2 minimum is
equaled. For the last scenario, use the
reduced air volume rate for all tests that
require the Cooling Certified Air Volume
Rate.
b. For ducted units that are tested with a
constant-air-volume-rate indoor fan installed.
For all tests that specify the Cooling Certified
Air Volume Rate, obtain an external static
pressure as close to (but not less than) the
applicable Table 2 value that does not cause
instability or an automatic shutdown of the
indoor blower.
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 Certified Air Volume Rate.
TABLE 2.—MINIMUM EXTERNAL STATIC PRESSURE FOR DUCTED SYSTEMS TESTED WITH AN INDOOR FAN INSTALLED
Minimum External
Resistance 3
(Inches of Water)
Rated Cooling 1 or Heating 2 Capacity
(Btu/h)
Up Thru 28,800 .............................................................................................................................................................................
29,000 to 42,500 ...........................................................................................................................................................................
43,000 and Above .........................................................................................................................................................................
0.10
0.15
0.20
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.
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59150
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
3.1.4.1.2 Cooling Certified Air Volume
Rate for Non-ducted Units. For non-ducted
units, the Cooling Certified 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. a. For ducted units that regulate the
Cooling Minimum Air Vol. Rate = Cooling Certified Air Vol. Rate ×
where ‘‘Cooling Minimum Fan Speed’’
corresponds to the fan speed used when
operating at low compressor capacity (twocapacity system), the fan speed used when
operating at the minimum compressor speed
(variable-speed system), or the lowest fan
speed used when cooling (single-speed
compressor and a variable-speed variable-air-
speed (as opposed to the cfm) of the indoor
fan,
Cooling Minimum Fan Speed
,
A 2 Test Fan Speed
volume-rate indoor fan). For such systems,
obtain the Cooling Minimum Air Volume
Rate regardless of the external static pressure.
b. For ducted units that regulate the air
volume rate provided by the indoor fan, the
manufacturer must specify the Cooling
Minimum Air Volume Rate. For such
systems, 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
instability or an automatic shutdown of the
indoor blower while being as close to, but not
less than,
2
Cooling Minimum Air Volume Rate
A1, B1, C1, F1, & G1 Test ∆Pst = ∆Pst , A 2 ×
,
Cooling Certified Air Volume Rate
where DPst,A2 is the applicable Table 2
minimum external static pressure that was
targeted during the A2 (and B2) Test.
c. For ducted two-capacity units that are
tested without an indoor fan installed, the
Cooling Minimum Air Volume Rate is the
higher of (1) the rate specified by the
manufacturer or (2) 75 percent of the Cooling
Certified 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.
3.1.4.3 Cooling Intermediate Air Volume
Rate. a. For ducted units that regulate the
speed of the indoor fan,
Cooling Intermediate Air Volume Rate = Cooling Certified Air Volume Rate ×
For such units, obtain the Cooling
Intermediate Air Volume Rate regardless of
the external static pressure.
b. For ducted units that regulate the air
volume rate provided by the indoor fan, the
manufacturer must specify the Cooling
Intermediate Air Volume Rate. For such
systems, conduct the EV Test at an external
static pressure that does not cause instability
or an automatic shutdown of the indoor
E v Test Fan Speed
.
A 2 Test Fan Speed
blower while being as close to, but not less
than,
2
Heating Certified Air Volume Rate = Cooling Certified Air Volume Rate ×
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H1 or H12 Test Fan Speed
.
A or A 2 Test Fan Speed
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11OCR2
ER11OC05.005</MATH>
ER11OC05.004</MATH>
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 instability or an automatic
shutdown of the indoor blower while being
as close to, but not less than, the same Table
2 minimum external static pressure as was
specified for the A (or A2) cooling mode test.
3.1.4.4.2 Ducted heat pumps where the
Heating and Cooling Certified Air Volume
Rates are different due to indoor fan
operation. a. For ducted heat pumps that
regulate the speed (as opposed to the cfm) of
the indoor fan,
ER11OC05.003</MATH>
Certified Air Volume Rate as the Heating
Certified Air Volume Rate for:
1. Ducted heat pumps that operate at the
same indoor fan speed during both the A (or
A2) and the H1 (or H12) Tests;
2. Ducted heat pumps that regulate fan
speed to deliver the same constant air
volume rate during both the A (or A2) and the
H1 (or H12) Tests; and
3. Ducted heat pumps that are tested
without an indoor fan installed (except twocapacity 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
ER11OC05.002</MATH>
where DPst,A2 is the applicable Table 2
minimum external static pressure that was
targeted during the A2 (and B2) Test.
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 Certified Air Volume
Rate.
3.1.4.4.1 Ducted heat pumps where the
Heating and Cooling Certified Air Volume
Rates are the same. a. Use the Cooling
ER11OC05.006</MATH>
Cooling Intermediate Air Volume Rate
E v Test ∆Pst = ∆Pst , A 2 ×
,
Cooling Certified Air Volume Rate
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
For such heat pumps, obtain the Heating
Certified Air Volume Rate without regard to
the external static pressure.
b. For ducted heat pumps that regulate the
air volume rate delivered by the indoor fan,
the manufacturer must specify the Heating
Certified Air Volume Rate. For such heat
pumps, conduct all tests that specify the
Heating Certified Air Volume Rate at an
external static pressure that does not cause
Heating Certified ∆Pst = Cooling Certified ∆Pst
where the Cooling Certified DPst is the
applicable Table 2 minimum external static
pressure that was specified for the A or A2
Test.
c. When testing ducted, two-capacity
northern heat pumps (see Definition 1.46),
use the appropriate approach of the above
two cases for units that are tested with an
indoor fan installed. For coil-only (fanless)
northern heat pumps, the Heating Certified
Air Volume Rate is the lesser of the rate
specified by the manufacturer or 133 percent
of the Cooling Certified Air Volume Rate. For
this latter case, obtain the Heating Certified
Air Volume Rate regardless of the pressure
drop across the indoor coil assembly.
3.1.4.4.3 Ducted heating-only heat
pumps. The manufacturer must specify the
Heating Certified Air Volume Rate. Use this
value when the following two requirements
are satisfied. First, when conducting the H1
or H12 Test (exclusively), the measured air
volume rate, when divided by the measured
indoor air-side total heating 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
Heating Minimum Air Volume Rate = Heating Certified Air Volume Rate ×
where ‘‘Heating Minimum Fan Speed’’
corresponds to the fan speed used when
operating at low compressor capacity (twocapacity system), the lowest fan speed used
at any time when operating at the minimum
compressor speed (variable-speed system), or
the lowest fan speed used when heating
(single-speed compressor and a variable-
instability or an automatic shutdown of the
indoor blower while being as close to, but not
less than,
Heating Certified Air Volume Rate
×
Cooling Certified Air Volume Rate
air volume rate for all tests of heating-only
heat pumps that call for the Heating Certified
Air Volume Rate. The second requirement is
as follows:
a. For heating-only heat pumps that are
tested with a fixed-speed, multi-speed, or
variable-speed variable-air-volume-rate
indoor fan installed. For the H1 or H12 Test
(exclusively), the measured external static
pressure must be equal to or greater than the
Table 2 minimum external static pressure
that applies given the heating-only heat
pump’s rated heating capacity. If the Table 2
minimum is not equaled or exceeded,
incrementally change the set-up of the indoor
fan until the Table 2 requirement is met
while maintaining the same air volume rate.
If the indoor fan set-up changes cannot
provide the necessary external static
pressure, then reduce the air volume rate
until the correct Table 2 minimum is
equaled. For the last scenario, use the
reduced air volume rate for all tests that
require the Heating Certified Air Volume
Rate.
b. For ducted heating-only heat pumps
having a constant-air-volume-rate indoor fan.
For all tests that specify the Heating Certified
speed variable-air-volume-rate indoor fan).
For such heat pumps, obtain the Heating
Minimum Air Volume Rate without regard to
the external static pressure.
b. For ducted heat pumps that regulate the
air volume rate delivered by the indoor fan,
the manufacturer must specify the Heating
Minimum Air Volume Rate. For such heat
59151
2
Air Volume Rate, obtain an external static
pressure that does not cause instability or an
automatic shutdown of the indoor blower
while being as close to, but not less than, the
applicable Table 2 minimum.
c. For ducted heating-only heat pumps that
are tested without an indoor fan 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 Certified 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 Certified 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. a. For ducted heat pumps that regulate
the speed (as opposed to the cfm) of the
indoor fan,
Heating Minimum Fan Speed
H12 Test Fan Speed
pumps, 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
instability or an automatic shutdown of the
indoor blower while being as close to, but not
less than,
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ER11OC05.009</MATH>
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 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
ER11OC05.008</MATH>
is the minimum external static pressure that
was targeted during the H12 Test.
c. For ducted two-capacity northern heat
pumps that are tested with an indoor fan
installed, use the appropriate approach of the
above two cases.
d. For ducted two-capacity heat pumps
that are tested without an indoor fan
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 fan installed, use the Cooling
Certified Air Volume Rate as the Heating
Minimum Air Volume Rate. For ducted twocapacity heating-only heat pumps that are
tested without an indoor fan installed, the
Heating Minimum Air Volume Rate is the
higher of the rate specified by the
manufacturer or 75 percent of the Heating
Certified Air Volume Rate. During the
laboratory tests on a coil-only (fanless) unit,
obtain the Heating Minimum Air Volume
ER11OC05.007</MATH>
where ∆Pst ,H12
ER11OC05.161</MATH>
2
Htg Minimum Air Vol. Rate
H01 , H11 , H21 , H31 , Test ∆Pst = ∆Pst,H12 ×
,
Htg Certified Air Vol. Rate
59152
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
indoor fan, use the lowest fan setting allowed
for heating.
3.1.4.6 Heating Intermediate Air Volume
Rate. a. For ducted heat pumps that regulate
the speed of the indoor fan,
Heating Intermediate Air Volume Rate = Heating Certified Air Volume Rate ×
For such heat pumps, obtain the Heating
Intermediate Air Volume Rate without regard
to the external static pressure.
b. For ducted heat pumps that regulate the
air volume rate delivered by the indoor fan,
the manufacturer must specify the Heating
Intermediate Air Volume Rate. For such heat
pumps, conduct the H2V Test at an external
static pressure that does not cause instability
or an automatic shutdown of the indoor
H2 V Test Fan Speed
.
H12 Test Fan Speed
blower while being as close to, but not less
than,
2
Heating Intermediate Air Volume Rate
H2 V Test ∆Pst = ∆Pst,H12 ×
,
Heating Certified Air Volume Rate
where ∆Pst ,H12
is the minimum external static pressure that
was specified for the H12 Test.
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. Except for the noted changes, determine
the Heating Nominal Air Volume Rate using
the approach described in section 3.1.4.6.
Required changes include substituting ‘‘H1N
Test’’ for H2V Test’’ within the first section
3.1.4.6 equation, substituting ‘‘H1N Test DPst’’
for ‘‘H2V Test DPst’’ in the second section
3.1.4.6 equation, substituting ‘‘H1N Test’’ for
each ‘‘H2V Test’’, and substituting ‘‘Heating
Nominal Air Volume Rate’’ for each ‘‘Heating
Intermediate Air Volume Rate.’’
Heating Nominal Air Volume Rate = Heating Certified Air Volume Rate ×
H1N Test Fan Speed
.
H12 Test Fan Speed
2
Heating Nominal Air Volume Rate
H1N Test ∆Pst = ∆Pst,H12 ×
.
Heating Certified Air Volume Rate
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3.1.7 Test sequence. When testing a
ducted unit (except if a heating-only heat
pump), conduct the A or A2 Test first to
establish the Cooling Certified Air Volume
Rate. For ducted heat pumps where the
Heating and Cooling Certified Air Volume
Rates are different, make the first heating
mode test one that requires the Heating
Certified Air Volume Rate. For ducted
heating-only heat pumps, conduct the H1 or
H12 Test first to establish the Heating
Certified Air Volume Rate. When conducting
an optional 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
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should precede the EV Test if one expects to
adjust the indoor fan control options when
preparing for the first Minimum Air Volume
Rate test. Under the same circumstances, the
first test using the Heating Minimum Air
Volume Rate should 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
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.013</MATH>
ER11OC05.012</MATH>
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.
(3-1)
ER11OC05.162</MATH>
˙
˙
Vmx
Vmx
=
lbm da '
lbm da
0.075
⋅ v n ⋅ [1 + Wn ] 0.075
⋅ vn
ft 3
ft 3
specified in sections 7.8.3.1 and 7.8.3.2 of
ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22). When using the
Outdoor Air Enthalpy Method, follow
sections 7.8.3.1 and 7.8.3.2 to calculate the
air volume rate through the outdoor coil. To
express air volume rates in terms of standard
air, use:
ER11OC05.011</MATH>
˙
Vs =
§ 430.22), 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.
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
ER11OC05.010</MATH>
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. If using a test setup 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
37–88) (incorporated by reference, see
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
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 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 Certified
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.
59153
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 that is tested with a fixedspeed indoor fan installed, with a constantair-volume-rate indoor fan installed, or with
no indoor fan installed. Conduct two steadystate wet coil tests, the A and B Tests. Use
the two optional dry-coil tests, the steadystate C Test and the cyclic D Test, to
determine the cooling mode cyclic
degradation coefficient, CDc. If the two
optional tests are not conducted, assign CDc
the default value of 0.25. Table 3 specifies
test conditions for these four tests.
TABLE 3.—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A FIXED-SPEED
INDOOR FAN, A CONSTANT AIR VOLUME RATE INDOOR FAN, OR NO INDOOR FAN
Air entering indoor unit temperature (°F)
Test description
Dry bulb
A Test—required (steady, wet coil) ..........................
B Test—required (steady, wet coil) ..........................
C Test—optional (steady, dry coil) ...........................
D Test—optional (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
1 65
......................
......................
Cooling certified 2
Cooling certified 2
Cooling certified 2
(4)
1 The
specified test condition only applies if the unit rejects condensate to the outdoor coil.
in section 3.1.4.1.
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 The
3.2.2 Tests for a unit having a singlespeed compressor and a variable-speed
variable-air-volume-rate indoor fan installed.
3.2.2.1 Indoor fan capacity modulation
that correlates with the outdoor dry bulb
temperature. Conduct four steady-state wet
coil tests: The A2, A1 , B2, and B1 Tests. Use
the two optional dry-coil tests, the steadystate C1 Test and the cyclic D1 Test, to
determine the cooling mode cyclic
degradation coefficient, CDc. If the two
optional tests are not conducted, assign CDc
the default value of 0.25. Table 4 specifies
test conditions for these six tests.
3.2.2.2 Indoor fan 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 3. Use a Cooling
Certified Air Volume Rate that represents a
normal residential 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 4.—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A VARIABLE AIR
VOLUME RATE INDOOR FAN THAT CORRELATES WITH THE OUTDOOR DRY BULB TEMPERATURE (SEC. 3.2.2.1)
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—optional (steady, dry coil) ........................
D1 Test 4—optional (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
1 65
1 65
......................
......................
Cooling
Cooling
Cooling
Cooling
Cooling
(5)
certified 2
minimum 3
certified 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 Definition 1.45.) a.
Conduct four steady-state wet coil tests: The
A2, A1, B2, and B1 Tests. Use the two optional
dry-coil tests, the steady-state C1 Test and the
cyclic D1 Test, to determine the cooling mode
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cyclic degradation coefficient, CDc. If the two
optional tests are not conducted, assign CDc
the default value of 0.25. Table 5 specifies
test conditions for these six tests.
b. For units having a variable speed indoor
fan that is modulated to adjust the sensible
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to total (S/T) cooling capacity ratio, use
Cooling Certified and Cooling Minimum Air
Volume Rates that represent a normal
residential installation. Additionally, if
conducting the optional dry-coil tests,
E:\FR\FM\11OCR2.SGM
11OCR2
59154
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
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 Definition 1.46) 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 3).
d. If a two-capacity air conditioner or heat
pump locks out low capacity operation at
outdoor temperatures that are less than 95 °F,
conduct the A1 Test using the outdoor
temperature conditions listed for the F1 Test
in Table 6 rather than using the outdoor
temperature conditions listed in Table 5 for
the A1 Test.
TABLE 5.—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR
Air entering indoor
unit
temperature (°F)
Test description
Wet
bulb
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—optional (steady, dry coil) ....................................
D1 Test 4—optional (cyclic, dry coil) ......................................
80
80
80
80
80
80
Air entering outdoor
unit
temperature (°F)
Wet
bulb
Dry bulb
67
67
67
67
(4)
(4)
95
95
82
82
82
82
Compressor
capacity
1 75
High
Low
High
Low
Low
Low
1 75
1 65
1 65
..............
..............
Cooling air volume rate
Cooling
Cooling
Cooling
Cooling
Cooling
(5)
Certified 2
Minimum 3
Certified 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
3.2.4 Tests for a unit having a variablespeed compressor. a. Conduct five steadystate wet coil tests: The A2, EV, B2, B1, and
F1 Tests. Use the two optional dry-coil tests,
the steady-state G1 Test and the cyclic I1 Test,
to determine the cooling mode cyclic
degradation coefficient,CDc. If the two
optional tests are not conducted, assign CDc
Maximum speed − Minimum speed
3
Intermediate speed = Minimum speed +
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 fan
speed to adjust the sensible to total (S/T)
the default value of 0.25. Table 6 specifies
test conditions for these seven tests.
Determine the intermediate compressor
speed cited in Table 6 using:
cooling capacity ratio, use Cooling Certified,
Cooling Intermediate, and Cooling Minimum
Air Volume Rates that represent a normal
residential installation. Additionally, if
conducting the optional dry-coil tests,
operate the unit in the same S/T capacity
control mode as used for the F1 Test.
TABLE 6.—COOLING MODE TEST CONDITIONS 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—optional (steady, dry coil) ..........................
I1 Test 5—optional (cyclic, dry coil) ..............................
Wet
bulb
80
80
80
80
80
80
80
Air entering outdoor
unit
Temperature (°F)
Dry bulb
67
67
67
67
67
(5)
(5)
95
82
87
82
67
67
67
Compressor
speed
Cooling air volume rate
Wet
bulb
1 75
Maximum
Maximum
Intermediate
Minimum
Minimum
Minimum
Minimum
1 65
1 69
1 65
1 53.5
..............
..............
Cooling
Cooling
Cooling
Cooling
Cooling
Cooling
(6)
Certified 2
Certified 2
Intermediate 3
Minimum 4
Minimum 4
Minimum 4
1 The
specified test condition only applies if the unit rejects condensate to the outdoor coil.
in section 3.1.4.1.
in section 3.1.4.3.
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. (It is recommended that an indoor wetbulb temperature of 57 °F or less be used.)
6 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 G1 Test.
2 Defined
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
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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
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airflow measuring apparatus and, if installed,
the indoor fan of the test unit to obtain and
then maintain the indoor air volume rate
and/or external static pressure specified for
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ER11OC05.014</MATH>
3 Defined
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
the particular test. Continuously record (see
Definition 1.15):
(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 5 of ASHRAE Standard
37–88 (incorporated by reference, see
§ 430.22) for the Indoor Air Enthalpy method
and the user-selected secondary method.
Except for external static pressure, make the
Table 5 measurements at equal intervals that
span 10 minutes or less. Measure external
static pressure every 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 7 are satisfied. For those
continuously recorded parameters, use the
entire data set from the 30-minute interval to
evaluate Table 7 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 as specified in section 7.3.3.1 of
ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22). 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. Assign the
average total space cooling capacity and
electrical power consumption over the 30minute data collection interval to the
˙
˙
variables Qck(T) and Eck(T), respectively. For
59155
these two 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 fan
˙
installed, decrease Qck(T) by
1250 Btu/h ˙
⋅ Vs ,
1000 scfm
˙
and increase Eck(T) by,
365 W
˙
⋅ Vs ,
1000 scfm
Ô
where Vs is the average measured indoor air
volume rate expressed in units of cubic feet
per minute of standard air (scfm).
TABLE 7.—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
Test condition tolerance 2
2.0
2.0
0.5
1.0
3 0.3
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. .....................................................................................
3 1.0
2.0
0.5
4 2.0
1.0
5 0.3
4 1.0
0.05
2.0
2.0
6 0.02
1.5
1 See
Definition 1.41.
Definition 1.40.
applies during wet coil tests; does not apply during steady-state, dry coil cooling mode tests.
4 Only applies when using the Outdoor Air Enthalpy Method.
5 Only applies during wet coil cooling mode tests where the unit rejects condensate to the outdoor coil.
6 Only applies when testing non-ducted units.
2 See
3 Only
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.
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˙
˙
E fan,2 − E fan,1
∆P2 − ∆P1
(∆Pmin
˙
− ∆P1 ) + E fan,1 ⋅
3.4 Test procedures for the optional
steady-state dry coil cooling mode tests (the
C, C1, 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.
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ER11OC05.017</MATH>
˙
E fan,min =
3. After re-establishing steady readings of
the fan motor power and external static
pressure, determine average values for the
˙
indoor fan 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 fan motor at DPmin
using linear extrapolation:
Prior to recording data during the steadystate 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.
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11OCR2
ER11OC05.016</MATH>
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).
ER11OC05.015</MATH>
d. For air conditioners and heat pumps
having a constant-air-volume-rate indoor fan,
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 fan motor (Efan,1) and record the
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
b. Denote the resulting total space cooling
capacity and electrical power derived from
˙
˙
the test as Qss,dry and Ess,dry(T). In preparing
for the section 3.5 cyclic test, 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, 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.
3.5 Test procedures for the optional
cyclic dry coil cooling mode tests (the D, D1,
and I1 Tests). a. After completing the steadystate dry-coil test, remove the Outdoor Air
Enthalpy method test apparatus, if
connected, and begin manual OFF/ON
cycling of the unit’s compressor. The test setup should otherwise be identical to the setup 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 fan, the manufacturer
has the option of electing at the outset
whether to conduct the cyclic test with the
indoor fan enabled or disabled. Always revert
to testing with the indoor fan 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.
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 fan 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 fan 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
fan, conduct the cyclic dry coil test using the
pull-thru approach described below if any of
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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 fan 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. After completing a minimum of two
complete compressor OFF/ON cycles,
determine the overall cooling delivered and
total electrical energy consumption during
any subsequent data collection interval
where the test tolerances given in Table 8 are
satisfied. If available, use electric resistance
heaters (see section 2.1) to minimize the
variation in the inlet air temperature.
f. With regard to the Table 8 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 fan (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 fan installed and
operating, integrate electrical power from
indoor fan OFF to indoor fan 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.)
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TABLE 8.—TEST OPERATING AND TEST
CONDITION TOLERANCES FOR CYCLIC DRY COIL COOLING MODE
TESTS
Test Operating Tolerance 1
Indoor entering dry-bulb
temperature 3, °F ....
Indoor entering wet-bulb
temperature, °F ......
Outdoor entering drybulb temperature 3,
°F ...............
External resistance to
airflow 3,
inches of
water .........
Airflow nozzle
pressure
difference
or velocity
pressure 3,
% of reading .............
Electrical voltage 6, % of
rdg. ............
Test Condition Tolerance 2
2.0
......................
0.5
(4)
2.0
0.05
0.5
......................
2.0
5 2.0
2.0
1.5
1 See
Definition 1.41.
Definition 1.40.
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 fan that ramps,
the tolerances listed for the external resistance
to airflow apply from 30 seconds after achieving full speed until ramp down begins.
4 Shall at no time exceed a wet-bulb temperature that results in condensate forming on
the indoor coil.
5 The test condition shall be the average
nozzle pressure difference or velocity pressure
measured during the steady-state dry coil test.
6 Applies during the interval when at least
one of the following—the compressor, the outdoor fan, or, if applicable, the indoor fan—are
operating except for the first 30 seconds after
compressor start-up.
2 See
3 Applies
i. If the Table 8 tolerances are satisfied over
the complete cycle, record the measured
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,
q cyc,dry =
=
˙
60 ⋅ V ⋅ C p,a ⋅ Γ
v ' ⋅ (1 + W )
n
n
˙
60 ⋅ V ⋅ C p,a ⋅ Γ
vn
(3.5 -1)
Ô
where V, Cp,a, vn′ (or vn), and Wn are the
values recorded during the section 3.4
dry coil steady-state test and,
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ER11OC05.018</MATH>
59156
59157
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
(3.5 - 3)
where Vs is the average indoor air volume
rate from the section 3.4 dry coil steadystate test and is expressed in units of
cubic feet per minute of standard air
(scfm). For units having a variable-speed
indoor fan that is disabled during the
cyclic test, increase ecyc,dry and decrease
qcyc,dry based on:
1 − CLF
where,
EER cyc,dry =
q cyc,dry
e cyc,dry
,
the average energy efficiency ratio during the
cyclic dry coil cooling mode
test, Btu/W·h
˙
Q ss,dry
EER ss,dry = ˙
,
E ss,dry
the average energy efficiency ratio during the
steady-state dry coil cooling mode test, Btu/
W·h
q cyc,dry
Q ss,dry ⋅ ∆τ cyc,dry
,
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 fan installed, with a
constant-air-volume-rate indoor fan installed,
or with no indoor fan installed. Conduct
three tests: The High Temperature (H1) Test,
the Frost Accumulation (H2) Test, and the
Low Temperature (H3) Test. Conduct the
optional High Temperature Cyclic (H1C) Test
to determine the heating mode cyclic
degradation coefficient, CDh. If this optional
test is not conducted, assign CDh the default
value of 0.25. Test conditions for these four
tests are specified in Table 9.
TABLE 9.—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A FIXED-SPEED
INDOOR FAN, A CONSTANT AIR VOLUME RATE INDOOR FAN, OR NO INDOOR FAN
Air entering indoor unit
Temperature (°F)
Air entering outdoor unit
Temperature (°F)
Dry bulb
Test description
Dry bulb
H1 Test (required, steady) ................................................
H1C Test (optional, 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
1 Defined
Heating Certified 1
(2)
Heating Certified 1
Heating Certified 1
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
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11OCR2
ER11OC05.025</MATH>
CLF =
ER11OC05.024</MATH>
1250 Btu/ h ˙
⋅ Vs ⋅ [ τ 2 − τ1 ],
1000 scfm
Ô
EER ss,dry
ER11OC05.023</MATH>
and decrease qcyc,dry by,
Cc =
D
EER cyc,dry
ER11OC05.022</MATH>
(3.5 - 2)
1−
ER11OC05.021</MATH>
365 W
˙
⋅ Vs ⋅ [ τ 2 − τ1 ],
1000 scfm
in section 3.5.1 for ducted units having a
disabled variable-speed indoor fan.
3.5.3 Cooling mode cyclic degradation
coefficient calculation. Use two optional drycoil tests to determine the cooling mode
cyclic degradation coefficient, CDc. If the two
optional tests are not conducted, assign CDc
the default value of 0.25. Evaluate CDc using
the above results and those from the section
3.4 dry coil steady-state test.
ER11OC05.020</MATH>
τ1
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 fan of the test unit). For
example, for ducted units tested without an
indoor fan 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 fan 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
fan installed, cycle the indoor coil airflow in
unison with the cycling of the compressor.
Close air dampers on the inlet (section 2.5.1)
and outlet side (sections 2.5 and 2.5.4) during
the OFF period. Airflow through the indoor
coil should stop within 3 seconds after the
automatic controls of the test unit (act to) deenergize the indoor fan. For ducted units
tested without an indoor fan installed
(excluding the special case where a variablespeed fan is temporarily removed), increase
ecyc,dry by the quantity,
a. The product of [t2 ¥ t1] and the indoor
fan power measured during or following the
dry coil steady-state test; or,
b. The following algorithm if the indoor fan
ramps its speed when cycling.
1. Measure the electrical power consumed
by the variable-speed indoor fan 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 fan 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 a
manufacturer-supplied ramp interval exceeds
45 seconds, use a 45-second ramp interval
nonetheless when estimating the fan energy.
The manufacturer is allowed to choose
option a, and forego the extra testing burden
of option b, even if the unit ramps indoor fan
speed when cycling.
3.5.2 Procedures when testing nonducted systems. Do not use air dampers
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 fan 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 fan during the 3 minutes prior to
compressor cut-on from the integrated
electrical energy, ecyc,dry. Add the electrical
energy used by the indoor fan 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 fan which is disabled
during the cyclic test, correct ecyc,dry and
qcyc,dry using the same approach as prescribed
ER11OC05.019</MATH>
τ2
Γ = ∫ [Tal ( τ) − Ta 2 ( τ)]dτ , hr ⋅ ° F.
59158
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
3.6.2 Tests for a heat pump having a
single-speed compressor and a variablespeed, variable-air-volume-rate indoor fan:
capacity modulation correlates with outdoor
dry bulb temperature. 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 optional High Temperature
Cyclic (H1C1) Test to determine the heating
mode cyclic degradation coefficient, CDh. If
this optional test is not conducted, assign CDh
{
˙
(35) ⋅ {E
[
˙
(17) + 0.6 ⋅ [E
the default value of 0.25. Table 10 specifies
test conditions for these seven tests. If the
optional H21 Test is not done, use the
following equations to approximate the
capacity and electrical power of the heat
pump at the H21 test conditions:
]}
k
˙k
˙k
˙k
˙k
Q h =1 (35) = QR h = 2 (35) ⋅ Q h =1 (17) + 0.6 ⋅ Q h =1 ( 47) − Q h =1 (17)
k
˙k
E h =1 (35) = PR h = 2
k =1
h
k =1
h
}
˙k
(47) − E h =1 (17)]
where,
˙ k
QR h = 2 (35) =
˙k
Q h = 2 (35)
˙
˙k
˙k
Q k = 2 (17) + 0.6 ⋅ Q h = 2 ( 47) − Q h = 2 (17)
k
PR h = 2 (35) =
˙k
E h = 2 (35)
⋅
˙k
˙k
˙k
E h = 2 (17) + 0.6 ⋅ E h = 2 ( 47) − E h = 2 (17)
˙
˙
˙
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 10.—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A VARIABLE AIR
VOLUME RATE INDOOR FAN
Air entering indoor unit
temperature (°F)
Air entering outdoor unit
temperature (°F)
Dry bulb
Test description
Dry bulb
H12 Test (required, steady) .................................................
H11 Test (required, steady) .................................................
H1C1 Test (optional, cyclic) ................................................
H22 Test (required) .............................................................
H21 Test (optional) ..............................................................
H32 Test (required, steady) .................................................
H31 Test (required, steady) .................................................
70
70
70
70
70
70
70
Wet 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
Certified.1
Minimum.2
Certified.1
Minimum.2
Certified.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 Definition 1.45),
including two-capacity, northern heat pumps
(see Definition 1.46). a. Conduct one
Maximum Temperature Test (H01), two High
Temperature Tests (H12 and 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 low
capacity operation at outdoor temperatures of
37°F and less.
b. Conduct the optional Maximum
Temperature Cyclic Test (H0C1) to determine
the heating mode cyclic degradation
coefficient, CDh. If this optional test is not
conducted, assign CDh the default value of
0.25. Table 11 specifies test conditions for
these eight tests.
Air entering outdoor unit
Temperature (°F)
Dry Bulb
Dry Bulb
H01 Test (required, steady) .........................
H0C1 Test (optional, cyclic) ........................
H12 Test (required, steady) .........................
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Wet Bulb
70
70
70
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60(max)
60(max)
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62
62
47
Sfmt 4700
Wet Bulb
56.5
56.5
43
E:\FR\FM\11OCR2.SGM
Compressor capacity
Low ..........
Low ..........
High .........
11OCR2
Heating air volume rate
Heating Minimum 1
(2)
Heating Certified 3
ER11OC05.026</GPH>
Air entering indoor unit
Temperature (°F)
Test description
ER11OC05.027</GPH>
TABLE 11.—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR
59159
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
TABLE 11.—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR—Continued
Air entering indoor unit
Temperature (°F)
H11
H22
H21
H32
H31
Air entering outdoor unit
Temperature (°F)
Dry Bulb
Test description
Dry Bulb
Test (required, steady) .........................
Test (required) .....................................
Test 4 (required) ...................................
Test (required, steady) .........................
Test 4 (required, steady) .......................
Wet Bulb
60(max)
60(max)
60(max)
60(max)
60(max)
70
70
70
70
70
Wet Bulb
47
35
35
17
17
43
33
33
15
15
Compressor capacity
Low ..........
High .........
Low ..........
High .........
Low ..........
Heating air volume rate
Heating
Heating
Heating
Heating
Heating
Minimum 1
Certified 3
Minimum 1
Certified 3
Minimum 1
1 Defined
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 H01 Test.
3 Defined in section 3.1.4.4.
4 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.
2 Maintain
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 optional Maximum Temperature
Cyclic (H0C1) Test to determine the heating
mode cyclic degradation coefficient, CDh. If
this optional test is not conducted, assign CDh
the default value of 0.25. Table 12 specifies
Intermediate speed = Minimum speed +
where a tolerance of plus 5 percent or the
next higher inverter frequency step from that
Maximum speed − Minimum speed
3
calculated is allowed. If the H22 Test is not
done, use the following equations to
{
˙
(35) = 0.985 ⋅ {E
test conditions for these eight tests.
Determine the intermediate compressor
speed cited in Table 12 using the heating
mode maximum and minimum compressors
speeds and:
[
˙
(17) + 0.6 ⋅ [E
approximate the capacity and electrical
power at the H22 test conditions:
]}
(17)]} ⋅
˙k
˙k
˙k
˙k
Q h = 2 (35) = 0.90 ⋅ Q h = 2 (17) + 0.6 ⋅ Q h = 2 ( 47) − Q h = 2 (17)
˙k
E h =2
˙
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
k =2
h
k =2
h
˙k
(47) − E h =2
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 12.—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
Heating air volume
rate
Wet bulb
...............
...............
...............
...............
...............
70
70
70
70
70
60(max)
60(max)
60(max)
60(max)
60(max)
.....
.....
.....
.....
.....
62
62
47
47
47
56.5
56.5
43
43
43
H22 Test (optional) .............................
H2V Test (required) ............................
H32 Test (required, steady) ...............
70
70
70
60(max) .....
60(max) .....
60(max) .....
35
35
17
33
33
15
H01 Test (required, steady)
H0C1 Test (optional, cyclic)
H12 Test (required, steady)
H11 Test (required, steady)
H1N Test (optional, steady)
Compressor speed
Minimum ....................
Minimum ....................
Maximum ...................
Minimum ....................
Cooling Mode Maximum.
Maximum ...................
Intermediate ..............
Maximum ...................
Heating
(2)
Heating
Heating
Heating
Minimum.1
Certified.3
Minimum.1
Nominal.4
Heating Certified.3
Heating Intermediate.5
Heating Certified.3
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E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.028</MATH>
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 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.
2 Maintain
ER11OC05.029</MATH>
1 Defined
59160
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
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 Definition 1.28) 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.)
3.7 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 fan 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 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. 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 5 of ASHRAE Standard
37–88 (incorporated by reference, see
§ 430.22) for the Indoor Air Enthalpy method
and the user-selected secondary method.
Except for external static pressure, make the
Table 5 measurements at equal intervals that
span 10 minutes or less. Measure external
static pressure every 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 13 are satisfied. For those
continuously recorded parameters, use the
entire data set for the 30-minute interval
when evaluating Table 13 compliance.
Determine the average electrical power
consumption of the heat pump over the same
30-minute interval.
TABLE 13.—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:
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 ..................................................................................................................................................
2.0
2.0
Test
condition tolerance 2
0.5
1.0
1.0
2.0
0.5
2 2.0
1.0
0.3
3 1.0
0.05
2.0
2.0
4 0.02
1.5
1 See
Definition 1.41.
Definition 1.40.
applies when the Outdoor Air Enthalpy Method is used.
4 Only applies when testing non-ducted units.
2 See
1250 Btu / h ˙
⋅ Vs ,
1000 scfm
˙
and increase Ehk(T) by,
365 W
˙
⋅ Vs ,
1000 scfm
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
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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 13 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).
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d. If conducting the optional cyclic heating
mode test, which is described in section 3.8,
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, 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
˙
fan motor (Efan,1):
1. The section 3.8 cyclic test will be
conducted and the heat pump has a variablespeed indoor fan that is expected to be
disabled during the cyclic test; or
2. The heat pump has a (variable-speed)
constant-air volume-rate indoor fan 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
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.030</GPH>
b. Calculate indoor-side total heating
capacity as specified in section 7.3.4.1 of
ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22). 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 30-minute 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
˙
fan installed, increase Qhk(T) by
ER11OC05.031</GPH>
3 Only
59161
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
∫ [Ta 2 (τ) − Ta1(τ)]δτ, hr ⋅ ° F.
τ1
b. For ducted heat pumps tested without
an indoor fan 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 fan
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
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1 − HLF
where,
COPcyc =
q cyc
,
Btu / h
3.413
⋅ e cyc
W
the average coefficient of performance during
the cyclic heating mode test, dimensionless.
( )
COPss Tcyc =
( )
˙k
Q h Tcyc
,
Btu / h ˙ k
3.413
⋅ E h Tcyc
W
( )
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 applicable—as specified
for the cyclic heating mode test,
dimensionless.
HLF =
q cyc
,
˙k
Q h Tcyc ⋅ ∆τ cyc
( )
the heating load factor, dimensionless.
Tcyc = the nominal outdoor temperature at
which the cyclic heating mode test is
conducted, 62 or 47 °F.
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.
Round the calculated value for CDh to the
nearest 0.01. If CDh is negative, then set it
equal to zero.
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0.5
1.0
2.0
0.5
2.0
1.0
0.05
2.0
4 2.0
2.0
1.5
1 See
Definition 1.41.
Definition 1.40.
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 fan that ramps,
the tolerances listed for the external resistance
to airflow shall apply from 30 seconds after
achieving full speed until ramp down begins.
4 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.
5 Applies during the interval that at least one
of the following—the compressor, the outdoor
fan, or, if applicable, the indoor fan—are operating, except for the first 30 seconds after
compressor start-up.
2 See
3 Applies
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
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.037</MATH>
( )
COPss Tcyc
2.0
ER11OC05.036</MATH>
Γ=
=
Indoor entering drybulb temperature,3
°F ...........................
Indoor entering wetbulb temperature,3
°F ...........................
Outdoor entering drybulb temperature,3
°F ...........................
Outdoor entering wetbulb temperature,3
°F ...........................
External resistance to
air-flow,3 inches of
water .....................
Airflow nozzle pressure difference or
velocity pressure,3
% of reading ..........
Electrical voltage,5 %
of rdg .....................
Test
condition
tolerance 2
ER11OC05.035</MATH>
τ2
1−
h
CD
COPcyc
Test
operating
tolerance 1
ER11OC05.034</MATH>
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.
3.8 Test procedures for the optional cyclic
heating mode tests (the H0C1, H1C, and H1C1
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 14 rather
than Table 8. 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.
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,
TABLE 14.—TEST OPERATING AND
TEST CONDITION TOLERANCES FOR
CYCLIC HEATING MODE TESTS.
ER11OC05.033</MATH>
˙
˙
E
− E fan,1
˙
˙
E fan,min = fan,2
(∆Pmin − ∆P1 ) + E fan,1.
∆P2 − ∆P1
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 fan
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 optional cyclic test and the required
steady-state test that were conducted at the
same test conditions to determine the heating
mode cyclic degradation coefficient, CDh. If
the optional test is not conducted, assign CDh
the default value of 0.25.
ER11OC05.032</MATH>
˙
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 fan
˙
power (Efan,2) and the external static pressure
(DP2) by making measurements over a 5minute interval.
iii. Approximate the average power
consumption of the indoor fan motor if the
30-minute test had been conducted at DPmin
using linear extrapolation:
59162
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
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 Definition 1.42),
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 12 hours,
immediately conclude the test and use the
results from the full 12-hour period to
calculate the average space heating capacity
and average electrical power consumption.
For heat pumps that turn the indoor fan 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 fan. 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 15 during both the preliminary and
official test periods. As noted in Table 15,
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 15) and (2) when defrosting, plus
these same first 10 minutes after defrost
termination (Sub-interval D, as described in
Table 15). Evaluate compliance with Table 15
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 15 at equal
intervals that span 10 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 fan on, continuously record the drybulb 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 fan
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 7.8.3.1 and 7.8.3.2 of ASHRAE
Standard 37–88 (incorporated by reference,
see § 430.22)) at equal intervals that span 10
minutes or less. 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 15.—TEST OPERATING AND TEST CONDITION TOLERANCES FOR FROST ACCUMULATION HEATING MODE TESTS.
Test operating tolerance 1
Sub-interval
H3
Sub-interval
D4
2.0
1.0
2.0
1.5
0.05
2.0
5 4.0
....................
10.0
....................
....................
....................
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 ......................................................................................................................
Test condition tolerance 2
Sub-interval
H3
0.5
....................
1.0
0.5
0.02 6
1.5
1 See
Definition 1.41.
Definition 1.40.
3 Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a defrost cycle.
4 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.
5 For heat pumps that turn off the indoor fan during the defrost cycle, the noted tolerance only applies during the 10 minute interval that follows
defrost termination.
6 Only applies when testing non-ducted heat pumps.
2 See
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.
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12:34 Oct 07, 2005
Jkt 208001
˙
60 ⋅ V ⋅ C p,a ⋅ Γ
[
]
∆τ FR v'n ⋅ (1 + Wn )
=
˙
60 ⋅ V ⋅ C p,a ⋅ Γ
∆τ FR ⋅ v n
DtFR = t2 ¥ t1, the elapsed time from defrost
termination to defrost termination, hr.
τ2
Γ=
∫ [Ta 2 (τ) − Ta1 (τ)] dτ, hr ⋅ ° F.
τ1
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
fan cycles off.
PO 00000
Frm 00042
Fmt 4701
Sfmt 4700
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
fan 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.
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.039</MATH>
˙k
Q h (35) =
ER11OC05.038</MATH>
3.9.1 Average space heating capacity and
electrical power calculations. a. Evaluate
˙
average space heating capacity, Qhk(35),
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
˙
E fan,min =
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),
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 demanddefrost control system (Definition 1.21). For
such qualifying heat pumps, evaluate Fdef
using,
∆τ def − 1.5
Fdef = 1 + 0.03 ⋅ 1 −
,
∆τ max − 1.5
where,
Dtdef = the time between defrost terminations
(in hours) or 1.5, whichever is greater.
Dtmax = maximum time between defrosts as
allowed by the controls (in hours) or 12,
whichever is less.
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 Certified
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
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12:34 Oct 07, 2005
Jkt 208001
˙
˙
E fan,2 − E fan,1
∆P2 − ∆P1
(∆Pmin
˙
− ∆P1 ) + E fan,1 ⋅
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. Prior to evaluating if
the energy balance specified in section 3.1.1
is obtained, make an adjustment to account
for the energy loss within the air duct that
connects the indoor coil and the location
where the outlet dry-bulb temperature is
measured. If using the Outdoor Air Enthalpy
Method, make an adjustment to account for
the energy loss within the air duct that
connects the outdoor coil and the location
where the outlet temperature is measured. In
all cases, apply the correction to the indoor
space conditioning capacity that is
determined using the secondary test method.
3.11.1 If using the Outdoor Air Enthalpy
Method as the secondary test method. During
the ‘‘official’’ test, the outdoor air-side 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 steady-state
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
PO 00000
Frm 00043
Fmt 4701
Sfmt 4700
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 10 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
7 or Table 13, 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 outdoorside 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 10 minutes or less.
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.044</MATH>
˙
and increase Ehk(35) by,
ER11OC05.043</MATH>
1250 Btu/h ˙
∆τ a
⋅ Vs ⋅
,
1000 scfm
∆τ FR
ER11OC05.042</MATH>
For heat pumps tested without an indoor
˙
fan installed, increase Qhk(35) by,
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 fan, 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:
1. Measure the average power consumption
˙
of the indoor fan 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 fan 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 fan motor had the
Frost Accumulation heating mode test been
conducted at DPmin using linear
extrapolation:
ER11OC05.041</MATH>
e (35)
˙k
E h (35) = def
.
∆τ FR
365 W
∆τ a
˙
⋅ Vs ⋅
,
1000 scfm
∆τ FR
ER11OC05.040</MATH>
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.
b. Evaluate average electrical power,
˙
Ehk(35), when expressed in units of watts,
using:
59163
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
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 10 minutes or
less. Determine average flow rate or average
capacity from data sampled over a 30-minute
period where the Table 7 (cooling) or the
Table 13 (heating) tolerances are satisfied.
Otherwise, conduct the calibration tests
according to ASHRAE Standard 23–93
(incorporated by reference, see § 430.22),
ASHRAE Standard 41.9–00 (incorporated by
reference, see § 430.22), and section 7.5 of
ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22).
b. Calculate space cooling and space
heating capacities using the compressor
calibration method measurements as
specified in sections 7.5.7 and 7.5.8,
respectively, of ASHRAE Standard 37–88
(incorporated by reference, see § 430.22).
8
e c Tj
N
∑
j =1
( )
(4.1-1)
( )=
where,
e c Tj
( )=
q c Tj
N
N
the electrical energy consumed by the test
unit during periods of the space 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 (N), W.
the ratio of the total space cooling provided
during periods of the space 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 (N), Btu/h.
( )
BL T j
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 single-
VerDate Aug<31>2005
12:34 Oct 07, 2005
Jkt 208001
(T
=
˙
)⋅Q
− 65
j
95 − 65
k =2
c
(95)
.
11
( 4.1- 2)
speed compressor that was tested with a
fixed-speed indoor fan installed, a constantair-volume-rate indoor fan installed, or with
no indoor fan installed. a. Evaluate the
seasonal energy efficiency ratio, expressed in
units of Btu/watt-hour, using:
SEER = PLF(0.5) · EERB
where,
PO 00000
EER B =
˙
Q c (82)
,
˙
E (82)
c
Frm 00044
Fmt 4701
Tj = the outdoor bin temperature, °F.
Outdoor temperatures are grouped or
‘‘binned.’’ Use bins of 5 °F with the 8 cooling
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,
Sfmt 4700
ER11OC05.050</MATH>
∑ e c (T j )
N
ER11OC05.049</MATH>
=
j =1
j =1
j =1
8
q c Tj
∑
the energy efficiency ratio determined from
the B Test described in sections 3.2.1, 3.1.4.1,
and 3.3, Btu/h per watt.
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). If the optional tests described in
section 3.2.1 are not conducted, set the
cooling mode cyclic degradation coefficient,
CDc, to the default value specified in section
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.047</MATH>
SEER =
( )
8
8
∑ q c (T j )
3.11.3 If using the Refrigerant Enthalpy
Method as the secondary test method.
Conduct this secondary method according to
section 7.6 of ASHRAE Standard 37–88
(incorporated by reference, see § 430.22).
Calculate space cooling and space heating
capacities using the refrigerant enthalpy
method measurements as specified in
sections 7.6.4 and 7.6.5, 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 follows:
1. For capacities less than 20,000 Btu/h,
round to the nearest 100 Btu/h.
2. For capacities between 20,000 and
37,999 Btu/h, round to the nearest 200 Btu/
h.
3. For capacities between 38,000 and
64,999 Btu/h, round to the nearest 500 Btu/
h.
b. For the capacities used to perform the
section 4 calculations, however, round only
to the nearest integer.
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,
ER11OC05.046</MATH>
Discontinue these measurement only after
obtaining a 30-minute 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 section 7.3.3.2
of ASHRAE Standard 37–88 (incorporated by
reference, see § 430.22). Calculate heating
capacity based on outdoor air enthalpy
measurements as specified in section 7.3.4.2
of the same ASHRAE Standard. Adjust
outdoor side capacities according to section
7.3.3.3 of ASHRAE Standard 37–88
(incorporated by reference, see § 430.22) to
account for line losses when testing split
systems. Do not correct the average electrical
power measurement as described in section
8.5.3 of ASHRAE Standard 37–88
(incorporated by reference, see § 430.22).
3.11.2 If using the Compressor
Calibration Method as the secondary test
method.
ER11OC05.045</MATH>
59164
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
3.5.3. If these optional tests are conducted,
set CDc to the lower of:
1. The value calculated as per section 3.5.3;
or
2. The section 3.5.3 default value of 0.25.
4.1.2 SEER calculations for an air
conditioner or heat pump having a single-
speed compressor and a variable-speed
variable-air-volume-rate indoor fan.
4.1.2.1 Units covered by section 3.2.2.1
where indoor fan capacity modulation
correlates with the outdoor dry bulb
temperature. The manufacturer must provide
information on how the indoor air volume
( )=X T ⋅ Q T ⋅
( ) ˙ ( )
N
q c Tj
j
where,
c
j
nj
rate or the indoor fan 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,
(4.1.2 -1)
N
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 16. Use Equation
4.1–2 to calculate the building load, BL(Tj).
˙
Evaluate Qc(Tj) using,
whichever is less; the cooling mode load
factor for temperature bin j, dimensionless.
˙
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
˙
BL( Tj ) Q c ( Tj )
X Tj =
or
;
1
( )
( )
( )
˙
˙k
Q c T j = Q c =1 T j +
( )
( )⋅
˙k
˙k
Q c = 2 T j − Q c =1 T j
FPck = 2
−
FPck =1
59165
[FP (T ) − FP ]
c
k =1
c
j
(4.1.2-2)
where,
˙
˙k
Q k =1 (95) − Q c =1 (82)
˙k
˙k
Q c =1 Tj = Q c =1 (82) + c
⋅ Tj − 82 ,
95 − 82
( )
(
)
(
N
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.
( )
12:34 Oct 07, 2005
Jkt 208001
j
nj
PLF j
( 4.1.2-3)
N
c. The quantities X(Tj) and nj /N are the
same quantities as used in Equation 4.1.2–1.
If the optional tests described in section
3.2.2.1 and Table 4 are not conducted, set the
cooling mode cyclic degradation coefficient,
CDc, to the default value specified in section
( )
˙
˙k
E c T j = E c =1 T j +
VerDate Aug<31>2005
c
PO 00000
( )
( )⋅
˙k
˙k
E c = 2 T j − E c =1 T j
FPck = 2
Frm 00045
−
FPck =1
Fmt 4701
ER11OC05.057</MATH>
j
3.5.3. If these optional tests are conducted,
set CDc to the lower of:
1. The value calculated as per section 3.5.3;
or
2.The section 3.5.3 default value of 0.25.
˙
d. Evaluate Ec(Tj) using,
[FP (T ) − FP ]
Sfmt 4725
c
j
k =1
c
E:\FR\FM\11OCR2.SGM
( 4.1.2-4)
11OCR2
ER11OC05.056</MATH>
˙
( ) = X( T ) ⋅ E ( T ) ⋅
e c Tj
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).
Calculate ec(Tj)/N in Equation 4.1–1 using,
ER11OC05.053</MATH>
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
the space cooling capacity of the test unit at
outdoor temperature Tj if operated at the
Cooling Certified Air Volume Rate, Btu/h.
b. For units where indoor fan 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
)
ER11OC05.052</MATH>
( )
ER11OC05.058</MATH>
˙
˙k
Q k = 2 (95) − Q c = 2 (82)
˙k
˙k
Q c = 2 Tj = Q c = 2 (82) + c
⋅ Tj − 82 ,
95 − 82
ER11OC05.059</MATH>
ER11OC05.060</MATH>
the space cooling capacity of the test unit at
outdoor temperature Tj if operated at the
Cooling Minimum Air Volume Rate, Btu/h.
59166
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
where
˙
˙k
E k =1 (95) − E c =1 (82)
˙k
˙k
⋅ Tj − 82 ,
E c =1 Tj = E c =1 (82) + c
95 − 82
( )
(
)
the electrical power consumption of the test
unit at outdoor temperature Tj if operated at
the Cooling Minimum Air Volume Rate, W.
˙
˙k
E k = 2 (95) − E c = 2 (82)
˙k
˙k
E c = 2 Tj = E c = 2 (82) + c
⋅ Tj − 82 ,
95 − 82
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,
˙
˙k
Q k =1 (95) − Q c =1 (82)
˙k
˙k
Q c =1 T j = Q c =1 (82) + c
⋅ T j − 82
95 − 82
˙
˙
where Qck=1(95) and Eck=1(95) are determined
˙
˙
from the A1 Test, Qck=1(82) and Eck=1(82) are
determined from the B1 Test, and all are
calculated as specified in section 3.3. For
two-capacity units that lock out low capacity
operation at outdoor temperatures less than
95 °F (but greater than 82 °F), use Equations
4.1.4–1 and 4.1.4–2 rather than Equations
4.1.3–1 and 4.1.3–2 for estimating
performance at low compressor capacity.
˙
˙k
Q k = 2 (95) − Q c = 2 (82)
˙k
˙k
Q c = 2 Tj = Q c = 2 (82) + c
⋅ Tj − 82
95 − 82
)
˙
˙k
E k = 2 (95) − E c = 2 (82)
˙k
˙k
E c = 2 Tj = E c = 2 (82) + c
⋅ Tj − 82
95 − 82
)
( )
(
( )
˙
˙
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 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.
VerDate Aug<31>2005
12:34 Oct 07, 2005
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(
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).
( )=X
q c Tj
N
k =1
( )=X
e c Tj
N
˙
(T ) ⋅ Q (T ) ⋅ N
˙
(T ) ⋅ E (T ) ⋅ n
k =1
nj
j
k =1
c
j
j
k =1
c
j
PLFj
j
N
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.
PO 00000
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)
( 4.1.3-2)
˙
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,
( 4.1.3-3)
( 4.1.3-4)
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 16. Use
Equations 4.1.3–1 and 4.1.3–2, respectively,
˙
˙
to evaluate Qck=1(Tj) and Eck=1(Tj). If the
optional tests described in section 3.2.3 and
Table 5 are not conducted, set the cooling
mode cyclic degradation coefficient, CDc, to
the default value specified in section 3.5.3.
If these optional tests are conducted, set CDc
to the lower of:
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.068</MATH>
(
ER11OC05.067</MATH>
( )
( 4.1.3-1)
ER11OC05.066</MATH>
˙
˙k
E k =1 (95) − E c =1 (82)
˙k
˙k
E c =1 T j = E c =1 (82) + c
⋅ T j − 82
95 − 82
)
ER11OC05.065</MATH>
(
ER11OC05.064</MATH>
( )
ER11OC05.063</MATH>
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 fan capacity modulation is
used to adjust the sensible to total cooling
capacity ratio. Calculate SEER as specified in
section 4.1.1.
)
ER11OC05.062</MATH>
the electrical power consumption of the test
unit at outdoor temperature Tj if operated at
the Cooling Certified 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
(
ER11OC05.061</MATH>
( )
59167
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
a. The value calculated according to
section 3.5.3; or
b. The section 3.5.3 default value of 0.25.
TABLE 16.—DISTRIBUTION OF FRACTIONAL HOURS WITHIN COOLING SEASON TEMPERATURE BINS
.............................................................................................................
.............................................................................................................
.............................................................................................................
.............................................................................................................
.............................................................................................................
.............................................................................................................
.............................................................................................................
.............................................................................................................
( )
c
j
c
k =1
j
k =1
c
k =2
q c Tj
( )
( )
˙k
Q c = 2 Tj − BL Tj
Tj = k = 2
,
˙
˙
Q
T − Q k =1 T
N
( )=X
e c Tj
j
the cooling mode, low capacity load factor
for temperature bin j, dimensionless.
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 16. 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.
k =2
c
j
j
j
N
k =2
j
( )
( )
k =2
k =2
c
j
j
j
4.1.3.4 Unit must operate continuously at
high (k=2) compressor capacity at
˙
temperature Tj, BL(Tj) ≥ Qck=2(Tj).
( )
( )
nj
˙k
Tj ⋅ Q c = 2 Tj ⋅
N
˙ k =2 T n
Tj ⋅ E c
j
j
⋅
PLFj
N
( ) =Q
˙
q c Tj
N
where,
˙
Xk=2(Tj) = BL(Tj)/Qck=2(Tj), the cooling mode
high capacity load factor for temperature
bin j, dimensionless.
PLFj = 1 ¥ CDc · [1 ¥ Xk=2(Tj)], the part load
factor, dimensionless.
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 16. Use
Equations 4.1.3–3 and 4.1.3–4, respectively,
˙
˙
to evaluate Qck=2(Tj) and Eck=2(Tj). When
evaluating the above equation for part load
factor at high capacity, use the same value of
CDc as used in the section 4.1.3.1
calculations.
( )=E
˙
e c Tj
N
)
nj
j
(T ) ⋅ N ⋅
nj
j
( 4.1.4 -1)
˙
˙k
E k =1 (82) − E c =1 (67)
˙k
˙k
⋅ Tj − 67
E c =1 Tj = E c =1 (67) + c
82 − 67
)
( 4.1.4 -2)
( )
(
( )
˙
˙
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
12:34 Oct 07, 2005
k =2
c
(T ) ⋅ N
Obtain the fractional bin hours for the
cooling season, nj/N, from Table 16. Use
Equations 4.1.3–3 and 4.1.3–4, respectively,
˙
˙
to evaluate Qck=2(Tj) and Eck=2(Tj).
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,
˙
˙k
Q k =1 (82) − Q c =1 (67)
˙k
˙k
Q c =1 Tj = Q c =1 (67) + c
⋅ Tj − 67
82 − 67
VerDate Aug<31>2005
k =2
c
Jkt 208001
(
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.
PO 00000
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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 6) EV Test using,
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.077</MATH>
where,
k =2
j
n
˙
˙
[X (T ) ⋅ E (T ) + X (T ) ⋅ E (T )] ⋅ N
( )=X
N
X
k =1
c
j
ER11OC05.076</MATH>
( )=
e c Tj
k =1
ER11OC05.074</MATH>
N
n
˙
˙
[X (T ) ⋅ Q (T ) + X (T ) ⋅ Q (T )] ⋅ N
ER11OC05.072</MATH>
( )=
( )
( )
0.214
0.231
0.216
0.161
0.104
0.052
0.018
0.004
the building cooling load at temperature Tj,
˙
˙
Qck=1(Tj) < BL(Tj) < Qck=2(Tj).
q c Tj
k =1
67
72
77
82
87
92
97
102
ER11OC05.070</MATH>
4.1.3.2 Unit alternates between high (k=2)
and low (k=1) compressor capacity to satisfy
65–69
70–74
75–79
80–84
85–89
90–94
95–99
100–104
Fraction of of total temperature
bin hours, nj/N
ER11OC05.069</MATH>
1
2
3
4
5
6
7
8
Representative
temperature for
bin °F
Bin temperature
range °F
Bin number, j
59168
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
( )
(
)
( 4.1.4 -3)
( )
(
)
( 4.1.4 - 4)
˙k
˙k
Q c = v Tj = Q c = v (87) + M Q ⋅ Tj − 87
˙k
˙k
E c = v Tj = E c = v (87) + M E ⋅ Tj − 87
˙
˙
where Qck=v(87) and Eck=v(87) are determined
from the EV Test and calculated as specified
in section 3.3. Approximate the slopes of the
k = v intermediate speed cooling capacity
and electrical power input curves, MQ and
ME, as follows:
˙
˙k
˙
˙k
Q k =1 (82) − Q c =1 (67)
Q k = 2 (95) − Q c = 2 (82)
⋅ 1 − N Q + N Q ⋅ c
MQ = c
82 − 67
95 − 82
k =2
k =2
k =1
k =1
˙
˙
˙
˙
E (82) − E c (67)
E (95) − E c (82)
⋅ (1 − N E ) + N E ⋅ c
ME = c
95 − 82
82 − 67
differs depending upon whether the test unit
would operate at minimum speed (section
4.1.4.1), operate at an intermediate speed
(section 4.1.4.2), or operate at maximum
speed (section 4.1.4.3) in responding to the
building load. Use Equation 4.1–2 to
calculate the building load, BL(Tj), for each
temperature bin.
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).
( )=X
q c Tj
k =1
N
( )=X
e c Tj
N
k =1
˙
(T ) ⋅ Q (T ) ⋅ N
˙
(T ) ⋅ E (T ) ⋅ n
nj
j
k =1
c
j
j
k =1
c
j
PLFJ
j
N
D=
B=
C=
2
T2 − T12
2
Tv − T12
nj
j
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.
( )
˙k
E c = i Tj =
( ) ,
( )
˙k
Q c = i Tj
EER k = i Tj
the electrical power input required by the
test unit when operating at a compressor
speed of k = i and temperature Tj, W.
EER k=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 16. For each
temperature bin where the unit operates at an
intermediate compressor speed, determine
the energy efficiency ratio EER k=i(Tj) using,
EER k=i(Tj) = A + B · Tj + C · Tj2.
For each unit, determine the coefficients A,
B, and C by conducting the following
calculations once:
[
]
EER k =1 (T1 ) − EER k = 2 (T2 ) − D ⋅ EER k =1 (T1 ) − EER k = v (Tv )
T1 − T2 − D ⋅ (T1 − Tv )
EER k =1 (T1 ) − EER k = 2 (T2 ) − B ⋅ (T1 − T2 )
2
T12 − T2
2
A = EER k = 2 (T2 ) − B ⋅ T2 − C ⋅ T2
where,
VerDate Aug<31>2005
Tl = the outdoor temperature at which the
unit, when operating at minimum
12:34 Oct 07, 2005
Jkt 208001
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Fmt 4701
Sfmt 4700
compressor speed, provides a space
cooling capacity that is equal to the
E:\FR\FM\11OCR2.SGM
ER11OC05.088</MATH>
j
N
(T ) ⋅ N
ER11OC05.086</MATH>
c
N
k=i
c
nj
j
ER11OC05.085</MATH>
( ) and e (T )
q c Tj
N
(T ) ⋅ N
ER11OC05.083</MATH>
Calculating Equation 4.1–1 quantities
( )=E
˙
e c Tj
k=i
c
ER11OC05.082</MATH>
˙k
˙k
E c = v (87) − E c =1 (87)
⋅
k =2
˙
˙k
E c (87) − E c =1 (87)
N
ER11OC05.080</MATH>
NE =
( ) =Q
˙
q c Tj
ER11OC05.081</MATH>
˙
˙k
Q k = v (87) − Q c =1 (87)
N Q = ˙ c =2
, and
k
˙k
Q c (87) − Q c =1 (87)
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 16. Use
Equations 4.1.4–1 and 4.1.4–2, respectively,
˙
˙
to evaluate Qck=1(Tj) and Eck=1(Tj). If the
optional tests described in section 3.2.4 and
Table 6 are not conducted, set the cooling
mode cyclic degradation coefficient, CDc, to
the default value specified in section 3.5.3.
If these optional tests are conducted, set CDc
to the lower of:
a. The value calculated according to
section 3.5.3; or
b. The section 3.5.3 default value of 0.25.
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).
11OCR2
ER11OC05.079</MATH>
where,
)
ER11OC05.078</MATH>
(
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
˙
building load (Qck=1(T1) = BL(T1)), °F.
Determine T1 by equating Equations
4.1.4–1 and 4.1–2 and solving for
outdoor temperature.
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
4.1.4–3 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.
]
]
EER k =1 (T1 ) =
˙k
Q c =1 (T1 ) Eqn. 4.1.4-1, substituting T1 for Tj
, Btu/ h per W.
˙k
E c =1 (T1 ) Eqn. 4.1.4-2, substituting T1 for Tj
EER k = v (Tv ) =
˙k
Q c = v (Tv ) Eqn. 4.1.4-3, substituting Tv for Tj
, Btu/ h per W.
˙k
E c = v (Tv ) Eqn. 4.1.4-4, substituting Tv for Tj
c
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
( ) and e (T )
N
c
j
N
2
j
2
2
j
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.
4.2 Heating Seasonal Performance Factor
(HSPF) Calculations. Unless an approved
alternative rating method is used, as set forth
J
HSPF =
2
( )
∑ n j ⋅ BL Tj
j
J
J
j
J
⋅ Fdef =
j
∑ e h (Tj ) + ∑ RH(Tj )
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
nj
j
in 10 CFR 430.24(m), Subpart B, HSPF must
be calculated as follows: Six generalized
climatic regions are depicted in Figure 2 and
otherwise defined in Table 17. For each of
these regions and for each applicable
standardized design heating requirement,
evaluate the heating seasonal performance
factor using,
∑ N ⋅ BL(Tj )
( )+
J
e h Tj
j
N
∑
( )
J
RH Tj
j
(4.2-1)
⋅ Fdef
N
∑
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=
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 17.
j = the bin number, dimensionless.
J = for each generalized climatic region, the
total number of temperature bins,
dimensionless. Referring to Table 17, 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 17.—GENERALIZED CLIMATIC REGION INFORMATION
Region Number ........................................................................................
Heating Load Hours, HLH .......................................................................
Outdoor Design Temperature, TOD ..........................................................
j
62 ..................................................................................................
57 ..................................................................................................
52 ..................................................................................................
750
37
II
1250
27
Tj (°F) .............................................................................................
1
2
3
I
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III
1750
17
IV
2250
5
V
2750
¥10
VI
*2750
30
.106
.092
.086
.113
.206
.215
Fractional Bin Hours, nj/N
.291
.239
.194
Sfmt 4700
.215
.189
.163
.153
.142
.138
E:\FR\FM\11OCR2.SGM
11OCR2
.132
.111
.103
ER11OC05.091</MATH>
˙k
Qc =2
(T2 ) = ˙ k = 2
E
ER11OC05.090</MATH>
k =2
[
]
[
]
(T ) [Eqn. 4.1.3-3, substituting T for T ]
, Btu/ h per W.
(T ) [Eqn. 4.1.3-4, substituting T for T ]
ER11OC05.089</MATH>
EER
q c Tj
59169
59170
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
TABLE 17.—GENERALIZED CLIMATIC REGION INFORMATION—Continued
4
5
6
7
8
9
10
11
12
13
14
15
16
17
18
47 ..................................................................................................
42 ..................................................................................................
37 ..................................................................................................
32 ..................................................................................................
27 ..................................................................................................
22 ..................................................................................................
17 ..................................................................................................
12 ..................................................................................................
7 ....................................................................................................
2 ....................................................................................................
¥3 ................................................................................................
¥8 ................................................................................................
¥13 ..............................................................................................
¥18 ..............................................................................................
¥23 ..............................................................................................
.129
.081
.041
.019
.005
.001
0
0
0
0
0
0
0
0
0
.143
.112
.088
.056
.024
.008
.002
0
0
0
0
0
0
0
0
.137
.135
.118
.092
.047
.021
.009
.005
.002
.001
0
0
0
0
0
.093
.100
.109
.126
.087
.055
.036
.026
.013
.006
.002
.001
0
0
0
.076
.078
.087
.102
.094
.074
.055
.047
.038
.029
.018
.010
.005
.002
.001
.204
.141
.076
.034
.008
.003
0
0
0
0
0
0
0
0
0
* Pacific Coast Region.
Evaluate the building heating load using
( )
BL Tj =
where,
TOD = the outdoor design temperature, °F. An
outdoor design temperature is specified
for each generalized climatic region in
Table 17.
DHR min
(65 − T ) ⋅ C ⋅ DHR
j
65 − TOD
( 4.2-2)
C = 0.77, a correction factor which tends to
improve the agreement between
calculated and measured building loads,
dimensionless.
DHR = the design heating requirement (see
Definition 1.22), Btu/h.
Calculate the minimum and maximum
design heating requirements for each
generalized climatic region as follows:
˙ k
65 − TOD
Q h ( 47) ⋅ 60 , for Regions I, II, III, IV, & VI
Rounded to the nearest
=
standardized DHR
˙ k
given in Table 18.
for Region V
Q h ( 47),
and
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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 Definition 1.28), HSPF also
accounts for resistive heating contributed
when operating above the heat-pump-pluscomfort-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.
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.098</MATH>
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
ER11OC05.097</MATH>
˙
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 Definition 1.46), Qkh(47) = Qk=1h(47), the
ER11OC05.096</MATH>
DHR max
65 − TOD
˙k
2 ⋅ Q h ( 47) ⋅ 60 , for Regions I, II, III, IV, & VI
Rounded to the nearest
=
standardized DHR
given in Table 18.
k
˙
for Region V
2.2 ⋅ Q h ( 47),
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
40,000
80,000
˙
( ) = X( T ) ⋅ E ( T ) ⋅ δ ( T ) ⋅ n
e h Tj
j
h
N
j
j
PLFj
130,000
j
( 4.2.1-1)
N
˙
( ) = BL(T ) − [X(T ) ⋅ Q (T ) ⋅ δ(T )] ⋅ n
RH Tj
j
h
j
j
Btu / h
3.413
W
N
j
N
(4.2.1-2)
˙
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 cutout 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
where,
( )
˙
BL(TJ ) Q h Tj
X Tj =
or
1
( )
j
whichever is less; the heating mode load
factor for temperature bin j, dimensionless.
season, nj/N, from Table 17. If the optional
H1C Test described in section 3.6.1 is not
conducted, set the heating mode cyclic
degradation coefficient, CDh, to the default
value specified in section 3.8.1. If this
˙
optional test is conducted, set CDh to the
lower of:
a. The value calculated according to
section 3.8.1 or
b. The section 3.8.1 default value of 0.25.
Determine the low temperature cut-out
factor using
( )
( )
( )
( )
( )
( )
˙
Q h Tj
0, if Tj ≤ Toff or
<1
˙
3.413 ⋅ E h Tj
˙
Q h Tj
δ Tj = 1/ 2, if Toff < Tj ≤ Ton and
≥1
˙
3.413 ⋅ E h Tj
˙
Q h Tj
1, if T > T and
≥1
on
j
˙
3.413 ⋅ E h Tj
( )
where,
Toff = the outdoor temperature when the
compressor is automatically shut off, °F.
( 4.2.1-3)
(If no such temperature exists, Tj is
always greater than Toff and Ton).
Ton = the outdoor temperature when the
compressor is automatically turned back
˙
Q h (17) +
˙
Q h Tj =
˙
Q h (17) +
( )
on, if applicable, following an automatic
shut-off, °F.
˙
˙
Calculate Qh(Tj) and Eh(Tj) using,
˙
˙
[Q (47) − Q (17)] ⋅ (T − 17) , if T ≥ 45 ° F or T ≤ 17 ° F
h
h
j
j
47 -17
[
](
j
) , if 17 ° F < T < 45 ° F
(4.2.1- 4)
˙
˙
Q h (35) − Q h (17) ⋅ Tj − 17
j
35 -17
[
](
)
[
](
)
˙
˙
E h ( 47) − E h (17) ⋅ Tj − 17
˙
E h (17) +
, if Tj ≥ 45 ° F or Tj ≤ 17 ° F
47 -17
˙
E h Tj =
˙
˙
E (35) − E h (17) ⋅ Tj − 17
˙
E (17) + h
, if 17 ° F < Tj < 45 ° F
h
35 -17
( )
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ER11OC05.104</MATH>
20,000 ...
ER11OC05.103</MATH>
90,000
100,000
110,000
ER11OC05.102</MATH>
50,000
60,000
70,000
ER11OC05.101</MATH>
25,000
30,000
35,000
( 4.2.1 - 5)
11OCR2
ER11OC05.100</MATH>
5,000 .....
10,000 ...
15,000 ...
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 fan installed, a constant-airvolume-rate indoor fan installed, or with no
indoor fan installed.
TABLE 18.—STANDARDIZED DESIGN
HEATING REQUIREMENTS (BTU/H)—
Continued
ER11OC05.099</MATH>
TABLE 18.—STANDARDIZED DESIGN
HEATING REQUIREMENTS (BTU/H)
59171
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
˙
˙
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
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, variable-
air-volume-rate indoor fan. The manufacturer
must provide information about how the
indoor air volume rate or the indoor fan
speed varies over the outdoor temperature
range of 65 °F to ¥23 °F. Calculate the
quantities
( ) and RH(T )
e h Tj
j
N
( )
N
( ) ⋅ FP
j
( ) ⋅ FP
j
( )
( )
( )
˙k
˙k
Q h = 2 Tj − Q h =1 Tj
˙k
˙k
E h = 2 Tj − E h =1 Tj
˙
˙k
Q h Tj = Q h =1 Tj +
( )
˙
˙k
E h Tj = E h =1 Tj +
( )
k
FPh = 2
[ (T ) − FP ]
k =1
h
( 4.2.2-1)
[ (T ) − FP ]
k
− FPh =1
( 4.2.2-2)
h
k
− FPh =1
h
k =1
h
capacity (k=1) and high capacity (k=2) at
outdoor temperature Tj are determined using
)
( )
[
](
[
](
)
)
˙k
˙k
E h ( 47) − E h (17) ⋅ Tj − 17
k
E h (17) +
, if Tj ≥ 45 ° F or Tj ≤ 17 ° F
47 − 17
˙k
E h Tj =
˙
˙k
E k 35 − E h (17) ⋅ Tj − 17
E k (17) + h ( )
˙
, if 17 ° F < Tj < 45 ° F
h
35 − 17
( )
[
)
˙
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
˙
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
( ) and RH(T )
e h Tj
N
j
N
( 4.2.2 - 4)
differs depending upon 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 operation at low outdoor
temperatures, the manufacturer must supply
information regarding the cutoff
temperature(s) so that the appropriate
equations can be selected.
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
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11OCR2
ER11OC05.105</MATH>
ER11OC05.106</MATH>
For units where indoor fan speed is the
primary control variable, FPhk=1 denotes the
fan speed used during the required H11 and
H31 Tests (see Table 10), 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)
](
( 4.2.2- 3)
ER11OC05.110</MATH>
](
ER11OC05.109</MATH>
[
˙k
˙k
Q h ( 47) − Q h (17) ⋅ Tj − 17
˙k
Q h (17) +
, if Tj ≥ 45 ° F or Tj ≤ 17 ° F
47 − 17
˙k
Q h Tj =
˙
˙k
Q k 35 − Q h (17) ⋅ Tj − 17
Q k (17) + h ( )
˙
, if 17 ° F < Tj < 45 ° F
h
35 − 17
ER11OC05.108</MATH>
where the space heating capacity and
electrical power consumption at both low
k
FPh = 2
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
ER11OC05.107</MATH>
59172
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
[
](
)
[
[
k =1
h
˙k
(62) − E h =1 (47)] ⋅ (Tj − 47)
62 − 47
˙k
˙k
E h =1 (35) − E h =1 (17) ⋅ Tj − 17
](
[
) , if 17 °F ≤ T < 40 °F
](
) , if T < 17 °F
47 − 17
j
˙
( ) = X (T ) ⋅ E (T ) ⋅ δ' (T ) ⋅ n
k =1
e h Tj
k =1
h
j
N
j
j
PLFj
j
( )
Jkt 208001
N
( 4.2.3 -1)
( 4.2.3 - 2)
d′(Tj) = the low temperature cutoff factor,
dimensionless.
If the optional H0C1 Test described in
section 3.6.3 is not conducted, set the heating
mode cyclic degradation coefficient, CDh, to
the default value specified in section 3.8.1.
0,
1/ 2,
δ' Tj =
1,
12:34 Oct 07, 2005
j
Frm 00053
If this optional test is conducted, set CDh to
the lower of:
a. The value calculated according to
section 3.8.1; or
b. The section 3.8.1 default value of 0.25.
Determine the low temperature cut-out
factor using
if Tj ≤ Toff
if Toff < Tj ≤ Ton
( 4.2.3 - 3)
if Tj > Ton
(a) The heat pump locks out low capacity
operation at low outdoor temperatures and
(b) Tj is below this lockout threshold
temperature.
PO 00000
˙
˙
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).
ER11OC05.113</MATH>
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.
j
Btu / h
3.413
W
N
j
N
( ) = BL(T ) ⋅ [1 − δ' (T )] ⋅ n
RH Tj
VerDate Aug<31>2005
j
35 − 17
˙k
˙k
E h =1 ( 47) − E h =1 (17) ⋅ Tj − 17
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,
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
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:
, if Tj ≥ 40 ° F
Fmt 4701
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ER11OC05.115</MATH>
( )
˙
[E
)
ER11OC05.114</MATH>
˙k
E h =1 ( 47) +
˙ k
Tj = E h =1 (17) +
˙ k =1
E h (17) +
](
4.2.3.2 Heat pump alternates between
high (k=2) and low (k=1) compressor
capacity to satisfy the building heating load
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.112</MATH>
[
( )
˙k
E h =1
)
˙
˙k
Q k =1 (62) − Q h =1 ( 47) ⋅ Tj − 47
˙ k =1 ( 47) + h
Qh
, if Tj ≥ 40 ° F
62 − 47
˙k
˙k
Q h =1 (35) − Q h =1 (17) ⋅ Tj − 17
˙ k
Tj = Q h =1 (17) +
, if 17 ° F ≤ Tj < 40 ° F
35 − 17
˙k
˙k
Q h =1 ( 47) − Q h =1 (17) ⋅ Tj − 17
˙k
Q h =1 (17) +
, if Tj < 17 ° F
47 − 17
ER11OC05.111</MATH>
˙k
Q h =1
](
59173
59174
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
˙
at a temperature Tj, Qhk=1(Tj) < BL(Tj) <
˙
Qhk=2(Tj).
Calculate
using Equation 4.2.3–2. Evaluate
( )
e h Tj
( )
N
RH Tj
using
N
n
˙
˙
[X (T ) ⋅ E (T ) + X (T ) ⋅ E (T )] ⋅ δ' (T ) ⋅ N
( )
e h Tj
N
using
( )=
( ) ( )⋅
˙k
X k = 2 Tj ⋅ E h = 2 Tj ⋅ δ' Tj
nj
N
PLFj
N
where,
˙
Xk=2(Tj)= BL(Tj)/Qhk=2(Tj).
˙
PLFj = 1 ¥ CDh [ 1 ¥ Xk=2(Tj) ].
0,
δ' ' Tj = 1/ 2,
1,
( )
4.2.4 Additional steps for calculating the
HSPF of a heat pump having a variable-speed
compressor. Calculate HSPF using Equation
( )
if Tj ≤ Toff or
( )=E
˙
e h Tj
e h Tj
(T ) ⋅ δ' ' (T ) ⋅ N
˙
RH(T ) BL(T ) − [Q (T ) ⋅ δ' ' (T )] n
=
⋅
N
k =2
h
j
j
Btu/ h
3.413
W
N
j
N
Where
( )
( )
˙ k=2
Q h Tj
<1
˙k
3.413 ⋅ E h = 2 Tj
if Toff < Tj ≤ Ton and
if Tj > Ton and
( )
( )
˙ k=2
Q h Tj
≥1
˙k
3.413 ⋅ E h = 2 Tj
( )
( )
˙ k=2
Q h Tj
≥1
˙k
3.413 ⋅ E h = 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
)
( 4.2.4 -1)
˙
˙k
E k =1 (62) − E h =1 ( 47)
˙k
˙k
⋅ Tj − 47
E h =1 Tj = E h =1 ( 47) + h
62 − 47
)
( 4.2.4 -2)
( )
(
( )
˙
˙
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 H11 Test, 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 solving
12:34 Oct 07, 2005
j
j
j
j
˙
˙k
Q k =1 (62) − Q h =1 ( 47)
˙k
˙k
⋅ Tj − 47
Q h =1 Tj = Q h =1 ( 47) + h
62 − 47
VerDate Aug<31>2005
nj
k =2
h
Jkt 208001
(
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.
PO 00000
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Fmt 4701
Sfmt 4700
˙
˙
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
E:\FR\FM\11OCR2.SGM
ER11OC05.126</MATH>
j
ER11OC05.125</MATH>
h
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. Calculate
ER11OC05.124</MATH>
j
N
using Equation 4.2.3–2. Evaluate
ER11OC05.123</MATH>
( )
( )
ER11OC05.122</MATH>
h
When evaluating the above equation for
part load factor at high capacity, use the same
value of CDh as used in the section 4.2.3.1
calculations. 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).
RH Tj
˙k
Q h = 2 Tj − BL Tj
˙
˙
Q k = 2 T − Q k =1 T
j
11OCR2
ER11OC05.121</MATH>
( )
( )
j
j
ER11OC05.120</MATH>
( )
k =2
h
j
( )
where,
X k =1 Tj =
k =2
j
ER11OC05.119</MATH>
k =1
h
j
ER11OC05.118</MATH>
k =1
ER11OC05.117</MATH>
N
ER11OC05.116</MATH>
( )=
e h Tj
59175
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
( )
(
)
( 4.2.4 - 3)
( )
(
)
( 4.2.4 - 4)
electrical power input curves, MQ and ME, as
follows:
˙k
˙k
˙k
˙k
Q h =1 (62) − Q h =1 ( 47)
N Q ⋅ Q h = 2 (35) − Q h = 2 (17)
⋅ 1 − NQ +
MQ =
62 − 47
35 − 17
˙k
˙k
˙
˙k
E k =1 (62) − E h =1 ( 47)
N ⋅ E h = 2 (35) − E h = 2 (17)
⋅ (1 − N E ) + E
ME = h
62 − 47
35 − 17
N
˙
˙k
E k = v (35) − E h =1 (35)
N E = h =2
.
˙
˙
E k (35) − E k =1 (35)
h
( )
h
N
and
( )
RH T j
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 speed (section 4.2.4.3) in
responding to the building load.
4.2.4.1 Steady-state space heating
capacity when operating at minimum
compressor speed is greater than or equal to
( )
N
using Equation 4.2.3–2 while evaluating
( )
e h Tj
N
using,
12:34 Oct 07, 2005
ER11OC05.138</MATH>
'
j
j
nj
N
where,
( )
˙k
E h = i Tj =
( )
˙k
Q h = i Tj
Btu / h
3.413
⋅ COP k = i Tj
W
( )
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:
2
2
T3 − T4
2
2
Tvh − T4
[
]
T4 − T3 − D ⋅ (T4 − Tvh )
Jkt 208001
PO 00000
compressor speed, provides a space
heating capacity that is equal to the
˙
building load (Qhk=1(T3) = BL(T3)), °F.
Frm 00055
Fmt 4701
Sfmt 4700
Determine T3 by equating Equations
4.2.4–1 and 4.2–2 and solving for:
E:\FR\FM\11OCR2.SGM
ER11OC05.137</MATH>
(T ) ⋅ δ (T ) ⋅
COP k = 2 (T4 ) − COP k =1 (T3 ) − D ⋅ COP k = 2 (T4 ) − COP k = v (Tvh )
where,
T3 = the outdoor temperature at which the
heat pump, when operating at minimum
VerDate Aug<31>2005
N
RH T j
D=
B=
( )
RH T j
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
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
e h Tj
and
N
k =1
h
ER11OC05.136</MATH>
( )
e h Tj
( )=E
˙
ER11OC05.135</MATH>
(35)
, and
(35)
e h Tj
ER11OC05.134</MATH>
(35)
(35)
˙k
− Q h =1
˙k
− Q h =1
ER11OC05.128</MATH>
NQ =
˙k
Q h =v
˙k
Q h =2
the building heating load at temperature Tj,
˙
Qhk=1(Tj ≥ BL(Tj). Evaluate the Equation 4.2–
1 quantities
ER11OC05.133</MATH>
where,
)
ER11OC05.132</MATH>
(
ER11OC05.131</MATH>
in section 3.9. Approximate the slopes of the
k=v intermediate speed heating capacity and
ER11OC05.130</MATH>
˙
˙
where Qhk=v(35) and Ehk=v(35) are determined
from the H2V Test and calculated as specified
ER11OC05.129</MATH>
˙k
˙k
E h = v Tj = E h = v (35) + M E ⋅ Tj − 35
11OCR2
ER11OC05.127</MATH>
˙k
˙k
Q h = v Tj = Q h = v (35) + M Q ⋅ Tj − 35
59176
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
C=
( )
COP k = 2 T 4 − COP k =1 (T3 ) − B ⋅ (T4 − T3 )
2
2
T4 − T3
2
A = COP k = 2 (T4 ) − B ⋅ T4 − C ⋅ T4 .
]
˙k
Q h = v (Tvh ) Eqn. 4.2.4 - 3, substituting Tvh for Tj
Btu / h ˙ k = v
3.413
⋅ E h (Tvh ) Eqn. 4.2.4 - 4, substituting Tvh for Tj
W
˙
Q k = 2 (T ) Eqn. 4.2.2 - 3, substituting T for T
4
[
4
j
[
]
( ) and RH(T )
j
N
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 fixedspeed indoor fan installed, a constant-airvolume-rate indoor fan installed, or with no
indoor fan 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 17. 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:
ER11OC05.142</MATH>
˙
˙
1bm da 60 min
Vmx
60 min Vmx 60 min
˙
˙
m da = Vs ⋅ 0.075
⋅
=
⋅
=
⋅
3
hr
v′ ⋅ [1 + Wn ]
hr
vn
hr
ft
n
C p, da = 0.24 + 0.444 ⋅ Wn
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 17, calculate the
nominal temperature of the air leaving the
heat pump condenser coil using,
( )
To Tj = 70 ° F +
( )
˙
Q hp Tj
˙
m da ⋅ C p, da
.
Evaluate eh(Tj/N), RH(Tj)/N, X(Tj), PLFj,
and d(Tj) as specified in section 4.2.1. For
VerDate Aug<31>2005
12:34 Oct 07, 2005
Jkt 208001
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.
PO 00000
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Fmt 4701
Sfmt 4700
Case 2. For outdoor bin temperatures
˙
where To(Tj) > Tcc, determine Qh(Tj) and
˙
Eh(Tj) using,
( ) ( )
( )
˙
˙
˙
E (T ) = E (T ) + E (T )
˙
˙
˙
Q h Tj = Q hp Tj + Q CC Tj
h
where,
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.145</MATH>
h
[
Btu / h ˙ k = 2
3.413
⋅ E h (T4 ) Eqn. 4.2.2 - 4, substituting T4 for Tj
W
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
N
[
]
ER11OC05.144</MATH>
COP k = 2 (T4 ) =
[
ER11OC05.143</MATH>
COP k = v (Tvh ) =
e h Tj
]
˙k
Q h =1 (T3 ) Eqn. 4.2.4 -1, substituting T3 for Tj
(T3 ) =
Btu/ h ˙ k =1
3.413
⋅ E h (T3 ) Eqn. 4.2.4 - 2, substituting T3 for Tj
W
j
hp
j
CC
j
ER11OC05.141</MATH>
[
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.
ER11OC05.140</MATH>
COP
k =1
˙
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
ER11OC05.139</MATH>
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
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
[
( )
( )]
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 fan. Calculate the
space heating capacity and electrical power
of the heat pump without the heat comfort
˙
˙
Q CC Tj = m da ⋅ C p, da ⋅ TCC − To Tj
( )
˙
E CC Tj =
( )
˙
Q CC Tj
Btu
3.413
W⋅h
59177
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 17. 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:
˙
˙
Vmx
60 min Vmx 60 min
1bm da 60 min
˙
˙
m da = Vs ⋅ 0.075
⋅
=
⋅
=
⋅
3
v′ ⋅ [1 + Wn ]
vn
hr
hr
hr
ft
n
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.
Case 1. For outdoor bin temperatures
where To(Tj) is equal to or greater than TCC
(the maximum supply temperature
( )
( )
˙
Q CC T j
˙
E CC T j =
3.413
Btu
W ⋅ h
.
˙
˙
1bm da 60 min
Vmx
60 min Vmx 60 min
˙
˙ k=
m da 1 = Vs ⋅ 0.075
⋅
=
⋅
=
⋅
hr
v ′ ⋅ [1 + Wn ]
vn
hr
ft 3
n
hr
C k,=1 = 0.24 + 0.444 ⋅ Wn
p da
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 17, calculate the
nominal temperature of the air leaving the
heat pump condenser coil when operating at
low capacity using,
k
To =1
( )
˙ k=1
Q hp Tj
(T ) = 70 ºF + m
˙
j
k =1
k =1
da ⋅ C p,da
⋅
( )
k
To = 2 Tj = 70 ºF +
( )
˙ k=2
Q hp Tj
˙ k=
m da 2
⋅ C k,= 2
p da
⋅
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
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
˙
˙
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,
˙
˙
˙
Qhk=1(Tj) = Qhpk=1(Tj) + QCCk=1(Tj)
˙
˙
˙
Ehk=1(Tj) = Ehpk=1(Tj) + ECCk=1(Tj)
where,
VerDate Aug<31>2005
12:34 Oct 07, 2005
Jkt 208001
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Frm 00057
Fmt 4701
Sfmt 4700
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.146</MATH>
ER11OC05.147</MATH>
Repeat the above calculations to determine
˙
the mass flow rate (mdak=2) and the specific
heat of the indoor air (Cp,dak=2) when
operating at high capacity by using the
results of the H12 Test. For each outdoor bin
temperature listed in Table 17, calculate the
nominal temperature of the air leaving the
heat pump condenser coil when operating at
high capacity using,
ER11OC05.152</MATH>
.
ER11OC05.151</MATH>
˙
m da ⋅ C p,da
ER11OC05.150</MATH>
( )
˙
Q hp T j
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 17. 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:
ER11OC05.149</MATH>
( )
To T j = 70 ºF +
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,
˙
˙
QCC(Tj) = mda · Cp,da · [TCC ¥ To(Tj)]
ER11OC05.148</MATH>
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 17, calculate the
nominal temperature of the air leaving the
heat pump condenser coil using,
ER11OC05.153</MATH>
C p, da = 0.24 + 0.444 ⋅ Wn
59178
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
[
( )
( )]
k
˙ k=
˙ k=
Q CC1 T j = m da 1 ⋅ C k,=1 ⋅ TCC − To =1 T j
p da
( )
( )
˙ k=
Q CC1 T j
˙ k=
E CC1 T j =
3.413
Btu
W ⋅ h
.
˙
˙
TCC, determine Qhk=2(Tj) and Ehk=2(Tj) as
˙
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
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
( )
( )
( )
( )
( )
may be required; evaluate RH(Tj)/N for all
bins.
Case 4. For outdoor bin temperatures
˙
where Tok=2(Tj) < TCC, determine Qhk=2(Tj)
˙
and Ehk=2(Tj) using,
( )
˙k
˙ k=
˙ k=
Q h = 2 T j = Q hp 2 T j + Q CC2 T j
˙k
˙ k=
˙ k=
E h = 2 T j = E hp 2 T j + E CC2 T j
where,
[
( )
( )]
k
˙ k=
˙ k=
Q CC2 T j = m da 2 ⋅ C k,= 2 ⋅ TCC − To = 2 T j
p da
VerDate Aug<31>2005
12:34 Oct 07, 2005
Jkt 208001
.
APFR =
˙k
CLH R ⋅ Q c (95) + HLH R ⋅ DHR ⋅ C
˙k
CLH R ⋅ Q c (95) HLH R ⋅ DHR ⋅ C
+
SEER
HSPF
where,
Frm 00058
Fmt 4701
Sfmt 4700
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.158</MATH>
CLHR = the representative cooling hours for
each generalized climatic region, Table
19, hr.
HLHR = the representative heating hours for
each generalized climatic region, Table
19, 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 2 shows the generalized climatic
regions. Table 18 lists standardized design
heating requirements.
ER11OC05.157</MATH>
˙k
CLH A ⋅ Q c (95) + HLH A ⋅ DHR ⋅ C
˙k
CLH A ⋅ Q c (95) HLH A ⋅ DHR ⋅ C
+
SEER
HSPF
that includes the particular location of
interest (see Figure 2), 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.
4.3.2 Calculation of representative
regional annual performance factors (APFR)
for each generalized climatic region and for
each standardized design heating
requirement.
PO 00000
4.3.1 Calculation of actual regional
annual performance factors (APFA) for a
particular location and for each standardized
design heating requirement.
ER11OC05.156</MATH>
Btu
W⋅ h
HSPF of a heat pump having a variable-speed
compressor. [Reserved]
4.3 Calculations of the Actual and
Representative Regional Annual Performance
Factors for Heat Pumps.
APFA =
where,
CLHA = the actual cooling hours for a
particular location as determined using
the map given in Figure 3, 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 2, hr.
DHR = the design heating requirement used
in determining the HSPF; refer to section
4.2 and Definition 1.22, Btu/h.
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
3.413
ER11OC05.155</MATH>
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
( )
˙ k=
Q CC2 T j
ER11OC05.154</MATH>
( )
˙ k=
E CC2 T j =
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
GION
Region
CLHR
I .................................
II ................................
III ...............................
VerDate Aug<31>2005
Region
HLHR
2400
1800
1200
12:34 Oct 07, 2005
TABLE 19.—REPRESENTATIVE COOLING AND HEATING LOAD HOURS FOR
EACH GENERALIZED CLIMATIC REGION—Continued
Jkt 208001
750
1250
1750
CLHR
IV ..............................
V ...............................
VI ..............................
PO 00000
Frm 00059
Fmt 4701
800
400
200
Sfmt 4725
HLHR
2250
2750
2750
4.4. Rounding of SEER, HSPF, and APF
for reporting purposes. After calculating
SEER according to section 4.1, round it off as
specified in subpart B 430.23(m)(3)(i) of Title
10 of the Code of Federal Regulations. Round
section 4.2 HSPF values and section 4.3 APF
values as per § 430.23(m)(3)(ii) and (iii) of
Title 10 of the Code of Federal Regulations.
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.172</GPH>
TABLE 19.—REPRESENTATIVE COOLING AND HEATING LOAD HOURS FOR
EACH GENERALIZED CLIMATIC RE-
59179
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 / Rules and Regulations
6. Section 430.32 of subpart C is
amended by revising the section
heading and adding introductory text to
paragraph (c) to read as follows:
I
VerDate Aug<31>2005
15:33 Oct 07, 2005
Jkt 208001
§ 430.32 Energy conservation standards
and effective dates.
*
*
*
*
*
(c) Central air conditioners and heat
pumps. The energy conservation
standards defined in terms of the
heating seasonal performance factor are
PO 00000
Frm 00060
Fmt 4701
Sfmt 4700
based on Region IV, the minimum
standardized design heating
requirement, and the sampling plan
stated in § 430.24(m).
*
*
*
*
*
[FR Doc. 05–15601 Filed 10–7–05; 8:45 am]
BILLING CODE 6450–01–U
E:\FR\FM\11OCR2.SGM
11OCR2
ER11OC05.173</GPH>
59180
]]>Agencies
[Federal Register Volume 70, Number 195 (Tuesday, October 11, 2005)]
[Rules and Regulations]
[Pages 59122-59180]
From the Federal Register Online via the Government Printing Office [www.gpo.gov]
[FR Doc No: 05-15601]
[[Page 59121]]
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Part II
Department of Energy
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Office of Energy Efficiency and Renewable Energy
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10 CFR Part 430
Energy Conservation Program for Consumer Products: Test Procedure for
Residential Central Air Conditioners and Heat Pumps; Final Rule
Federal Register / Vol. 70, No. 195 / Tuesday, October 11, 2005 /
Rules and Regulations
[[Page 59122]]
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DEPARTMENT OF ENERGY
Office of Energy Efficiency and Renewable Energy
10 CFR Part 430
[Docket No. EE-RM/TP-97-440]
RIN 1904-AA46
Energy Conservation Program for Consumer Products: Test Procedure
for Residential Central Air Conditioners and Heat Pumps
AGENCY: Office of Energy Efficiency and Renewable Energy, Department of
Energy.
ACTION: Final rule.
-----------------------------------------------------------------------
SUMMARY: The Department of Energy (DOE, or the Department) amends its
test procedures for residential central air conditioners and heat
pumps. This final rule adds new sections and revises several sections
of the test procedure to bring it up-to-date by eliminating the need
for several test procedure waivers and making it more complete. The
Department also re-organized the test procedure to be more
chronological in its progression. The revisions to the test procedure
do not alter the minimum energy conservation standards currently in
effect for central air conditioners and heat pumps.
DATES: This rule is effective April 10, 2006. The incorporation by
reference of certain publications listed in this rule is approved by
the Director of the Federal Register as of April 10, 2006.
ADDRESSES: You may review copies of all materials related to this
rulemaking at the U.S. Department of Energy, Forrestal Building, Room
1J-018 (Resource Room of the Building Technologies Program), 1000
Independence Avenue, SW., Washington, DC, (202) 586-9127, between 9
a.m. and 4 p.m., Monday through Friday, except Federal holidays. Please
call Ms. Brenda Edwards-Jones at the above telephone number for
additional information regarding visiting the Resource Room. Please
note: The Department's Freedom of Information Reading Room (formerly
Room 1E-190 at the Forrestal Building) is no longer housing rulemaking
materials.
FOR FURTHER INFORMATION CONTACT: Michael G. Raymond, U.S. Department of
Energy, Office of Energy Efficiency and Renewable Energy, EE-2J, 1000
Independence Avenue, SW., Washington, DC 20585-0121, (202) 586-9611, e-
mail: michael.raymond@ee.doe.gov; or Thomas B. DePriest, Esq., U.S.
Department of Energy, Office of General Counsel, GC-72, 1000
Independence Avenue, SW., Washington, DC 20585-0121, (202) 586-9507, e-
mail: thomas.depriest@hq.doe.gov.
SUPPLEMENTARY INFORMATION: The final rule incorporates, by reference,
into Subpart B of Part 430 seven test-method standards published by the
American Society of Heating, Refrigerating, and Air-Conditioning
Engineers, Inc. (ASHRAE), as follows:
Standard 23-1993, ``Methods of Testing for Rating Positive
Displacement Refrigerant Compressors and Condensing Units;''
Standard 37-1988, ``Methods of Testing for Rating Unitary
Air-Conditioning and Heat Pump Equipment;''
Standard 41.1-1986 (Reaffirmed 2001), ``Standard Method
for Temperature Measurement;''
Standard 41.2-1987 (Reaffirmed 1992), ``Standard Methods
for Laboratory Airflow Measurement;''
Standard 41.6-1994 (Reaffirmed 2001), ``Standard Method
for Measurement of Moist Air Properties;''
Standard 41.9-2000, ``Calorimeter Test Methods for Mass
Flow Measurements of Volatile Refrigerants;'' and
Standard 116-1995, ``Methods of Testing for Rating for
Seasonal Efficiency of Unitary Air Conditioners and Heat Pumps.''
The following joint test-method standard of ASHRAE and the Air
Movement and Control Association International, Inc. (ASHRAE/AMCA) is
incorporated by reference into subpart B of Part 430:
Standard 51-1999/210-1999, ``Laboratory Methods of Testing
Fans for Aerodynamic Performance Rating.''
The following test-and-rating standard of the Air-Conditioning and
Refrigeration Institute (ARI) is incorporated by reference into Subpart
B of Part 430:
Standard 210/240-2003, ``Unitary Air-Conditioning and Air-
Source Heat Pump Equipment.''
Copies of these standards are available for public review at the
Department of Energy's Building Technologies Program Resource Room
described above. Copies of the ASHRAE, ASHRAE/AMCA and ARI Standards
are available from the American Society of Heating, Refrigerating, and
Air-Conditioning Engineers, Inc., 1971 Tullie Circle, NE., Atlanta, GA
30329, https://www.ashrae.org; the Air Movement and Control Association
International, Inc., 30 West University Drive, Arlington Heights, IL
60004-1893, https://www.amca.org; and the Air-Conditioning and
Refrigeration Institute, 4100 North Fairfax Drive, Suite 200,
Arlington, VA 22203-1629, https://www.ari.org.
I. Introduction
A. Authority
B. Background
II. Discussion of Comments
A. General Discussion
1. Adopting References Updated Since Public Hearing
2. Small-Duct, High-Velocity (SDHV) Systems
3. Non-Defrost Heat Pumps
4. Two-Capacity, Northern Heat Pumps
5. Heat Pumps Having a Heat Comfort Controller
B. Definitions
C. Testing Conditions
1. Section 2.2.4 Wet-Bulb Temperature Requirements for Air
Entering the Indoor and Outdoor Coils
2. Section 2.2.5 Additional Refrigerant Charging Requirements
D. Testing Procedures
1. Section 3.1.4 Airflow Through the Indoor Coil: Systems Having
a Variable-Speed, Constant Airflow Blower
2. Sections 3.1.4.2, 3.1.4.5, 3.3, 3.5.1, 3.7, and 3.9.1.
Testing a Two-Capacity Compressor System: Coil-Only Units Tested at
Low Capacity and Differences in High/Low Cycling
III. Summary of Other Additions and Changes to the DOE Residential
Central Air Conditioner and Heat Pump Test Procedure
A. Update and Add References for ASHRAE and ARI Standards
B. Air Volume Rates
C. Cyclic Testing
D. Fanless (Coil-Only) Units
E. Frost Accumulation Test
F. Test Tolerance Tables
G. Pretest Intervals
1. Wet Coil Tests
2. Dry Coil Steady-State Test
3. Dry Coil Cyclic Test
4. Maximum and High Temperature Heating Mode Tests
5. Heating Mode Cyclic Test
6. Frost Accumulation Test
7. Low Temperature Test
H. Multi-Capacity Systems
1. Two-Capacity Heat Pumps That Lock Out Low Capacity at Higher
Outdoor Temperatures
2. Systems Having a Single-Speed Compressor and a Variable-Speed
Indoor Fan Where Fan Speed or Air Volume Rate Depends on Outdoor
Temperature
I. Triple-Split Systems
J. Time-Adaptive Defrost Control Systems
K. Test Unit Installation
L. Test Apparatus and Measurement/Sampling Frequency
1. Inlet Plenum for Blower Coils
2. Manifolded Static Pressure Taps
3. Temperature Measurement Intervals
4. Temperature Measurement Accuracies
5. Grid of Individual Temperature Sensors Within the Indoor-Side
Outlet Plenum
[[Page 59123]]
6. Duct Loss Correction
7. Water Vapor Measurements Using a Dew-Point Hygrometer, a
Relative Humidity Meter, or Any Other Alternative Instrument
8. Voltmeter Accuracy
9. Electrical Power Measurement
M. Different Compressor Speeds and Indoor Fan Capacities Between
Cooling and Heating
N. Secondary Test Requirements
O. Calculations
P. Effect of Test Procedure Revisions on SEER and HSPF
IV. Procedural Requirements
A. Review Under Executive Order 12866
B. Review Under the Regulatory Flexibility Act
C. Review Under the Paperwork Reduction Act
D. Review Under the National Environmental Policy Act
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 of 1999
I. Review Under Executive Order 12630
J. Review Under the Treasury and General Government
Appropriations Act of 2001
K. Review Under Executive Order 13211
L. Review Under Section 32 of the Federal Energy Administration
Act of 1974
M. Congressional Notification
N. Approval of the Office of the Secretary
I. Introduction
A. Authority
Part B of Title III of the Energy Policy and Conservation Act (EPCA
or Act) (42 U.S.C. 6291 et seq.), established the Energy Conservation
Program for Consumer Products Other Than Automobiles (Program). The
products currently subject to this Program (``covered products'')
include central air conditioners and heat pumps, the subject of today's
final rule.
Under the Act, the Program consists of three parts: Testing,
labeling, and the Federal energy conservation standards. The
Department, in consultation with the National Institute of Standards
and Technology (NIST), is authorized to establish or amend test
procedures as appropriate for each of the covered products. (42 U.S.C.
6293) The purpose of the test procedures is to measure energy
efficiency, energy use, or estimated annual operating cost of a covered
product during a representative, average use cycle or period of use.
The test procedure must not be unduly burdensome to conduct. (42 U.S.C.
6293(b)(3))
If a test procedure is amended, DOE is required to determine to
what extent, if any, the proposed new test procedure would alter the
measured energy efficiency of any covered product as determined under
the existing test procedure. (42 U.S.C. 6293(e)(1)) If DOE determines
that an amended test procedure would alter the measured energy
efficiency of a covered product, DOE is required to amend the
applicable energy conservation standard with respect to such test
procedure. In determining any such amended energy conservation
standard, DOE is required to measure the energy efficiency or energy
use of a representative sample of covered products that minimally
comply with the existing standard. The average efficiency or energy use
of these representative samples, tested using the amended test
procedure, constitutes the amended standard. (42 U.S.C. 6293(e)(2)) The
Department has determined that today's amended test procedure does not
alter the measured efficiency or measured energy use of central air
conditioners and heat pumps.
Beginning 180 days after a test procedure for a covered product is
prescribed, no manufacturer, distributor, retailer, or private labeler
may make representations with respect to the energy use, efficiency, or
cost of energy consumed by such product, except as reflected in tests
conducted according to the DOE procedure. (42 U.S.C. 6293(c)(2))
B. Background
On January 22, 2001, the Department published a Notice of Proposed
Rulemaking (hereafter referred to as the January 22, 2001, proposed
rule) that proposed a revised test procedure for central air
conditioners and heat pumps. (66 FR 6768) As summarized in the January
22, 2001, proposed rule, the Department initiated several interactions,
including a DOE workshop, phone conferences, and the release of
multiple drafts for review and comment between DOE and stakeholders
prior to preparing the revised test procedure.
Most of the existing test procedure dates back to its original
publication in the Federal Register on December 27, 1979. (44 FR 76700)
The Department modified the test procedure on March 14, 1988, to cover
variable-speed air conditioners and heat pumps, to address testing of
split-type non-ducted units, and to change the method used for
crediting heat pumps that provide a demand defrost capability. (53 FR
8304)
The January 22, 2001, proposed rule specified dates for holding a
public hearing and for submitting written comments. At the request of
ARI, the Department changed these specified dates. (66 FR 15203, March
16, 2001) Prior to the public hearing and at the invitation of ARI, a
NIST representative attended a meeting of the ARI Unitary Small
Equipment Engineering Committee on February 27, 2001, at ARI
headquarters. The public hearing was held on March 29, 2001, at DOE
headquarters.\1\ At the public hearing, the participants spent the
majority of the time discussing the list of items from the proposed
rulemaking for which the Department solicited stakeholder comment. One
manufacturer, the Carrier Corporation, presented a prepared oral
statement. On May 1, 2001, DOE and NIST personnel met with
representatives of the Carrier Corporation at DOE headquarters.
---------------------------------------------------------------------------
\1\ The Department held a public workshop on issues that would
not be considered for the current revision to the test procedure
(i.e., alternative rating method for untested combinations,
promoting devices that compensate for installation problems,
metrification of the DOE test procedure) on the day immediately
following the close of the public hearing.
---------------------------------------------------------------------------
During the comment period, stakeholders, DOE, and NIST held several
phone and e-mail discussions about issues associated with the proposed
test procedure (a revision of 10 CFR part 430, Subpart B, Appendix M)
and about rating untested split-system combinations (a separate test
procedure issue not covered in Appendix M, but in 10 CFR 430.24(m)).
The issue of rating untested split-system combinations is not part of
this rulemaking and will be the subject of a future rulemaking.
II. Discussion of Comments
A. General Discussion
Nine different stakeholders submitted a total of fourteen comments
on the January 22, 2001, proposed rule. Concurrent with this
rulemaking, the Department also conducted a rulemaking to issue new
energy conservation standards for central air conditioners and heat
pumps. Both rulemakings covered, among other consumer products, small-
duct, high-velocity (SDHV) systems. In the standards rulemaking (66 FR
7197), DOE stated that concerns for SDHV systems had been addressed by
modifying the test procedure for SDHV products. This test procedure
modification would have given SDHV systems a higher tested value of the
Seasonal Energy Efficiency Ratio (SEER). (DOE later rejected this test
procedure modification for reasons discussed in section II.A.2 of this
preamble). As a result, the Department considered comments received on
October 18, 2001, from SDHV manufacturers SpacePak and Unico, Inc.
(Unico) as part of the energy conservation standards rulemaking in
today's final rule on the test procedure.
[[Page 59124]]
(SpacePak, No. 21, Unico, No. 22) \2\ The Department also considered
during this rulemaking amended comments from ARI, dated October 30,
2001, that addressed the SDHV issue. (ARI, No. 20) A discussion of the
comments and the actions taken in response to them follows.
---------------------------------------------------------------------------
\2\ These comments were received in the course of the standards
rulemaking, Docket Number EE-RM-98-440, but are relevant to this
test procedure rulemaking. SpacePak's comments are item 267 in that
docket; Unico's comments are item 251.
---------------------------------------------------------------------------
1. Adopting References Updated Since Public Hearing
The January 22, 2001, proposed rule referenced seven ASHRAE
standards, as well as ASHRAE Standard 51-99/AMCA Standard 210-99, and
ARI standard 210/240. Since the publication of the proposed rule,
however, two of these standards have been reaffirmed and two have been
revised. The two reaffirmed standards are ASHRAE Standard 41.1-1986
(Reaffirmed 2001) and ASHRAE Standard 41.6-1994 (Reaffirmed 2001). When
a standard is reaffirmed within ASHRAE, no substantive changes are
permitted to the document. In the ASHRAE Project Committee Manual of
Procedures, substantive change is defined as
a change that involves an important (has value, weight or
consequences), fundamental (is the foundation, without which it would
collapse), or essential (belongs to the very nature of a thing) part or
changes the meaning of the material or that directly and materially
affects the use of the standard. Following are example changes that may
be found substantive when examined in context;
``shall'' to ``should'' or ``should'' to ``shall;'
addition, deletion or revision of mandatory requirements,
regardless of the number of changes;
or addition of mandatory compliance with referenced
standards.
Thus, today's final rule references ASHRAE Standards 41.1-1986
(Reaffirmed 2001) and 41.6-1994 (Reaffirmed 2001), whereas the January
22, 2001, proposed rule had referenced ASHRAE Standards 41.1-1986
(Reaffirmed 1991) and 41.6-1994. These changes have no effect on the
test procedure itself nor on the reported energy efficiency ratings of
the tested equipment.
The two revised standards are ASHRAE Standard 41.9-2000 and ARI
Standard 210/240-2003. A revision of ASHRAE Standard 41.9,
``Calorimeter Test Methods for Mass Flow Measurements of Volatile
Refrigerants,'' was published in 2000. The previous version, Standard
41.9-1988, was referenced in the proposed rulemaking. This particular
standard is only referenced in section 3.11.2 of the test procedure.
Section 3.11.2 pertains to one of three allowed secondary test methods,
the Compressor Calibration Method. These secondary test methods do not
affect the reported performance ratings. Instead, these secondary test
methods are used to provide a check of the primary method, i.e., the
Indoor Air Enthalpy Method. Specifically, the cooling or heating
capacity determined using the approved primary method and the user
selected secondary test method must agree within six percent to
constitute a valid test set-up. The revised version of ASHRAE Standard
41.9 is referenced in today's test procedure both because it does not
affect the reported ratings and because it provides the most current
methods for making refrigerant calorimeter measurements.
The other revised standard is ARI Standard 210/240-2003. The main
impetus behind the 2003 revision of ARI Standard 210/240 was a desire
to narrow the scope of the equipment covered by the standard. Whereas
the 1994 version of Standard 210/240 covered equipment up to 135,000
Btu/h, the 2003 version is limited to equipment having rated capacities
less than 65,000 Btu/h. With regard to the DOE test procedure, the
January 22, 2001, proposed rule referenced four sections within ARI
Standard 210/240-1994. In the 2003 version of the standard, no
substantive changes were made to these four sections. The numbering/
lettering of the sections, however, did change slightly. For example,
section 5.1.3.5 in the 1994 document became section 6.1.3.5 in the 2003
document. Today's test procedure maintains the approach taken in the
proposed rule of only referencing the four particular sections of 210/
240. Because of this consistency, the DOE test procedure is unaffected
by referencing ARI Standard 210/240-2003 rather than Standard 210/240-
1994. The reported energy efficiency ratings of the tested equipment
are unaffected as well.
2. Small-Duct, High-Velocity (SDHV) Systems
As discussed in the January 22, 2001, proposed rule, Unico, a
manufacturer of SDHV systems, argued for creating a separate SDHV
product class that was subject to a lower future energy conservation
standard than the level established for conventional units. (66 FR
6768) However, in the energy standards rulemaking, a majority of
industry members opposed the separate-product-class option. DOE did not
include a separate SDHV class in the January 22, 2001, proposed rule.
Instead, DOE proposed testing SDHV systems as coil-only units. Testing
as coil-only units would give SDHV units an immediate SEER and Heating
Seasonal Performance Factor (HSPF) boost, as long as the default fan
power was less than the actual blower wattage. The SEER and HSPF boost
eliminated the need for a separate product class. Both Unico and ARI at
first endorsed this approach. (Unico, No. 10; ARI, No. 19 at p. 3) But
SpacePak, Trane, and ultimately ARI, disagreed with the coil-only
testing approach. (SpacePak, No. 15; Trane, No. 12 at p. 1, ARI, No.
20) These comments noted that SDHV systems would be tested in a manner
that would never occur in real applications and, as a result, give
energy efficiency and cost-of-operation results that are not
representative of the unit's true energy performance. Furthermore, SDHV
manufacturers would have no incentive to use high-efficiency blowers if
systems were tested without the indoor blower. Finally, there is no
technical basis for setting the default fan-power level. For these
reasons, DOE has determined that its proposal to test SDHV systems as
coil-only units is unacceptable. As a result, today's final rule does
not amend the test procedures to test SDHV systems as coil-only units.
DOE considered another alternative for SDHV systems which it also
ultimately rejected. This alternative was to make no changes at all. In
other words, test SDHV systems as they are currently tested and require
them to meet the same future energy conservation standards as
conventional units. The Department rejected this option because it
risked the continued existence of SDHV systems. The Department
explained its position at the public hearing on March 29, 2001: The
Department cannot set standards in a way that removes from the market a
product which offers special utility. (Public Hearing Tr., p. 44)
Because today's final rule does not amend the test procedures for
SDHV units, DOE recognizes, as it did in the January 22, 2001, energy
standards final rule, that SDHV units will have difficulty in meeting
the 13 SEER standard. In the May 23, 2002, final rule on central air
conditioner and heat pump standards, DOE further discussed how the
special characteristics of SDHV systems would make it unlikely such
systems could even meet the 12 SEER/7.4 HSPF standard established for
space constrained products. (67 FR 36396) However, because of the
ruling by the
[[Page 59125]]
U.S. Court of Appeals for the Second Circuit in January, 2004, 355 F.3d
179 (2d Cir. 2004), that bars DOE from adopting a standard of less than
13 SEER for SDHV systems, the 13 SEER standard applies to SDHV systems,
despite DOE's later conclusion that it is unlikely such systems can
meet that standard or even the lower 12 SEER standard for space
constrained systems. (69 FR 50997) Nonetheless, the inability of SDHV
systems to meet the applicable energy efficiency standards is not a new
problem created by the amendments to the test procedure in today's
rulemaking. Instead, these products were unable to meet the standard
under the old test procedures. As a result, DOE need not amend the
applicable test procedure or standard to mitigate this noncompliance.
DOE has advised the two manufacturers of these systems of the procedure
available to affected persons under section 504 of the Department of
Energy Organization Act (42 U.S.C. 7194), which allows them to request
relief from hardship or inequity caused by a regulation issued under
EPCA.
3. Non-Defrost Heat Pumps
The January 22, 2001, proposed rule included steps for calculating
the HSPF of a non-defrost heat pump. This proposal addressed the test
procedure waiver granted to Enviromaster International (EMI). In 1992,
the Department granted EMI a waiver for its line of non-defrost, multi-
split heat pumps. Under the waiver, the Department did not require EMI
to report an HSPF and instead required EMI to include in its printed
materials for the product the following sentence, ``No HSPF value has
been measured since the heat pump cannot be operated at temperatures
below 35[deg]F.'' EMI finally applied to the Department's Office of
Hearing and Appeals (OHA) on January 23, 2003, for exception relief
from the HSPF efficiency standards. OHA granted the exception relief on
April 1, 2003. Thus, EMI has never calculated HSPF because of its
waiver, and will not do so in the future because of OHA exception
relief.
Since there are no manufacturers of products on the market which
would actually use the proposed procedure for calculating the HSPF of a
non-defrost heat pump, the Department has removed from the test
procedure all references to non-defrost heat pumps and the special
caveats for calculating an HSPF for such units.
4. Two-Capacity, Northern Heat Pumps
The January 22, 2001, proposed rule applied to a two-capacity heat
pump configured to use only low capacity when cooling, while using both
low and high capacities when heating. (66 FR 6768) The proposed test
procedure identified such units as ``two-capacity heat pumps that lock
out high capacity when cooling.'' At the March 29, 2001, public
hearing, York expressed concern regarding the use of the term
``lockout.'' (Public Hearing Tr., p. 54) York felt the term was too
restrictive, since it could be interpreted to mean that the lockout
feature must be hard-wired, whereas DOE intended the meaning to include
factory or field-selectable lockout.
At the March 29, 2001, public hearing, ARI commented that such
units would typically have two different indoor coil identifiers and,
as a result, two different sets of ratings. (Public Hearing Tr., p. 53)
The ARI comment was supported by many of the other participants at the
public hearing. ARI and York submitted written comments that supported
the consensus reached at the public hearing. (ARI, No. 19 at p. 2;
York, No. 9 at p. 2) The Department chose to adopt the public comment
consensus and now defines these types of systems as ``two-capacity,
northern heat pumps.'' The Department included a requirement in the
definition of ``two-capacity, northern heat pump'' that the
manufacturer must clearly state that the feature is factory or field-
selectable and that manufacturers must publish two sets of ratings.
Finally, the definition indicates that the lockout feature is to remain
enabled for all tests. The northern heat pump is allowed to operate at
high capacity during its defrost cycle, an issue that arose at the
public hearing. (Public Hearing Tr., p. 55)
5. Heat Pumps Having a Heat Comfort Controller
The January 22, 2001, proposed rule included an algorithm for
calculating the HSPF for most single-speed heat pumps having a heat
comfort controller. (66 FR 6768) At the March 29, 2001, public hearing,
Trane commented that the wording in the test procedure on the
calculation of the energy consumed for resistive heating by a heat
comfort controller needed clarification. Trane suggested that one use
the higher of: (1) The resistive heating based on meeting the heat
comfort controller's temperature setting; or (2) the resistive heating
based on meeting the building load deficit (when operating below the
balance point). (Public Hearing Tr., p. 30) Later, Trane submitted
written comments that the algorithm, as interpreted, would overstate
the HSPF at heat-comfort-controller set points beginning around
90[deg]F and get progressively worse as the set point was reduced.
(Trane, No. 12)
Battelle offered three general recommendations. The first
recommendation was to emphasize that comfort controllers operate both
above and below the normal balance point temperature. The second
recommendation was to account for the fact that conventional heat pumps
and, to a lesser extent, heat pumps with comfort controllers, will
cycle below the system balance point. The third recommendation was that
DOE perform a parametric calculation to determine ``HSPF deficits'' due
to the operation of a comfort controller. (Battelle, No. 11) The end
product could potentially be a table listing the reduction in HSPF that
results from operating the comfort controller at different temperature
settings.
The American Gas Association (AGA) comments paralleled those from
Battelle. Both AGA and Battelle recommended that the definition of HSPF
specify that for heat pumps with heat comfort controllers, HSPF
accounts for resistive heating contributed when operating either above
or below the balance point as a result of maintaining a minimum supply
temperature. Both also recommended that the equation for the heating
load factor in section 4.2.1 be changed to the following:
[GRAPHIC] [TIFF OMITTED] TR11OC05.000
where,
X(Tj) = the heating mode load factor for temperature bin j,
dimensionless
BL(Tj) = the building space conditioning load corresponding
to an outdoor temperature of Tj
Qh(Tj) = the space heating capacity of the heat
pump when operating at outdoor temperature Tj, Btu/h
RHb = the size of each resistance heat bank
n = the number of banks needed to exceed the building load at each bin
temperature.
Finally, in a slight variation from Battelle, AGA recommended that
``DOE provide direction in the test procedure for evaluating
performance of heat pumps retrofitted with heat comfort controllers in
the field, including a parametric table of HSPF by DOE region for
various delivered air temperatures.'' (AGA, No. 18, Battelle, No. 11)
Given the general support for covering those heat pumps having heat
comfort controllers, today's test procedure covers all heat pumps
having heat comfort controllers, except when a heat comfort controller
is used with a heat
[[Page 59126]]
pump having a variable-speed compressor. Test procedure section 4.2.5.4
is reserved for a variable-speed heat pump having a heat comfort
controller.
The algorithm for calculating the HSPF of a heat pump having a heat
comfort controller is covered in sections 4.2.5.1 to 4.2.5.3 of today's
final rule. The algorithm captures the fact that the balance point
temperature (i.e., where the compressor first runs continuously) for a
heat pump with a heat comfort controller will be less than, or equal
to, the balance point temperature of that same heat pump without the
heat comfort controller. In response to Trane's comments (Public
Hearing Tr., p. 30; Trane, No. 12), today's test procedure includes
editorial additions that alert the user to evaluate Equation 4.2.1-2
for all temperature bins. The test procedure then accounts for the
resistive heating needed to satisfy the minimum air delivery
temperature of the heat comfort controller and the (additional)
resistive heating needed to give an overall heating capacity that
matches the building load.\3\
---------------------------------------------------------------------------
\3\ When calculating the HSPF for a conventional heat pump, the
section 4.2 variable Eh(Tj) and
Qh(Tj) represent the electrical power and
heating capacity provided exclusively by the heat pump, while the
variable RH(Tj) applies exclusively to any resistive
heating contribution. When calculating the HSPF of a heat pump
having a heat comfort controller, by comparison, the variables
Eh(Tj) and Qh(Tj)
represent the electrical power and heating capacity provided by the
heat pump and any supplemental resistive heating needed to provide
the comfort-controller-set-point air delivery temperature. The
variable RH(Tj), in this case, reflects any additional
resistive heating if the combined capacity of heat pump and the
resistive heating associated with achieving the set-point air
delivery temperature is nonetheless insufficient to meet the
building load. Electrical resistive heating for a heat pump having a
heat comfort controller is thus allocated among two variables
(Eh(Tj) and RH(Tj)) rather than one
(RH(Tj)). This redefining allows the calculation
procedure to capture the reduced heat pump contribution, the shift
to a lower balance point, and the negative impact on HSPF.
---------------------------------------------------------------------------
In considering AGA and Battelle's recommended definition change,
the key point is to emphasize the downward shift in the balance point
and the associated lower contribution by the heat pump. The Department
doesn't believe that a single sentence referenced to heat comfort
controllers within the HSPF definition, even when modified as
recommended, is sufficient. Therefore, the definition of ``Heat pumps
having a heat comfort controller,'' emphasizes the downward shift in
the balance point and the associated lower contribution by the heat
pump.
The Department is amending the definition of HSPF by moving the
following language from the definition text in the proposed rule to the
main text of the test procedure, specifically, to the end of Section
4.2, ``Heating Seasonal Performance Factor (HSPF) Calculations.''
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 heat pumps with heat comfort controllers (see Definition 1.26),
in addition, HSPF also accounts for resistive heating contributed
when operating above the balance point as a result of maintaining a
minimum supply temperature.
This moved text includes the one sentence from the HSPF definition
in the proposed rule that specifically addressed heat comfort
controllers. This sentence is the same one that both AGA and Battelle
recommended changing. Coupled with the additional paragraph in Section
4.2.5, ``Heat pumps having a heat comfort controller,'' the Department
believes the revisions more accurately convey the operating changes
caused by adding a heat comfort controller.
The Department did not adopt AGA and Battelle's recommendation for
changing the calculation of the heating-mode-load factor. (AGA, No. 18,
Battelle, No. 11) The Department agrees with AGA and Battelle that
resistive heating initiated as the result of a second stage call of the
indoor thermostat can, under the right conditions, cause a conventional
heat pump to cycle below its balance point. Even though a conventional
heat pump terminates resistive heating once the second stage setpoint
is met, the concentrated burst of resistive heating coupled with the
capacity of the continuously operating heat pump may cause the first
stage of the thermostat to be met shortly after the second stage is
met. An overshoot occurs and the heat pump cycles off. The overshoot is
more likely to occur near the balance point where only a small amount
of resistive heating is needed.
The existing test procedure makes the implicit assumption that an
overshoot never occurs. AGA and Battelle's proposed change assumes that
an overshoot always occurs. The frequency of this overshoot is unknown.
Until data become available showing that overshoot occurs more often
than the case where the heat pump runs continuously and the resistive
elements cycle on and off at the second stage, the Department will
leave the heating-load-factor calculation unchanged. The AGA and
Battelle recommendation would be more appropriate if resistive heating,
once initiated as the result of a second-stage call, stayed on until
the first stage setpoint was met. The Department is not aware of
conventional heat pumps that use this strategy, so it did not change
the calculation of the heating-mode-load factor.
Heat pumps with heat comfort controllers operate differently from
conventional heat pumps following a second-stage-thermostat call for
resistive heating. When the second-stage setpoint is satisfied, heat
comfort controllers reduce the resistive heating rather than cycling it
off. In this manner, the heat comfort controller attempts to modulate
the resistive heating so that additional second-stage calls are reduced
while also avoiding satisfying the first-stage setpoint. The goal is
for the heat pump to operate continuously below the balance point while
having the resistive heating regulated to provide a more uniform
delivery temperature than that provided by a conventional heat pump.
The heat comfort controller's operation when responding to a second-
stage-thermostat call is believed to provide a more comfortable
environment for the homeowner, while not causing an energy penalty. The
one field study cited by both AGA and Battelle \4\ supports this
assertion. Therefore, as was decided for conventional heat pumps, the
Department did not adopt the AGA and Battelle recommended heating-load-
factor equation within the section 4.2.5 calculations that only apply
to heat pumps having a heat comfort controller.
---------------------------------------------------------------------------
\4\ ``Improving Occupant Comfort Without an Energy Penalty in
Homes Heated by Electric Heat Pumps,'' Yuill, G.K., and Musser, A.,
ASHRAE Paper 4162, ASHRAE Transactions 1998 V. 104, Pt. 1.
---------------------------------------------------------------------------
Finally, with regard to the Battelle and AGA recommendations that
the test procedure contain information on the impact of heat comfort
controllers for different temperature setpoints and/or quantify the
impact from an after-market retro-fit installation of a heat comfort
controller, the Department agrees that such information is probably
warranted but judges it inappropriate for inclusion in the test
procedure. The scope of the test procedure is to test and rate new,
factory-supplied equipment. Addressing the impact of after-market
products on the performance of covered products is not within the
purview of EPCA. However, as pointed out at the March 29, 2001, pubic
hearing, the test procedure may provide a framework for building code
officials' consideration when deciding how to handle the after-market
sale of heat comfort controllers. (Public Hearing Tr., p. 32)
[[Page 59127]]
B. Definitions
In addition to the amendments to the definitions discussed above in
section II.A.1 of this preamble, today's final rule modifies
definitions and references as described below.
An editorial correction was made to the citation for ASHRAE
Standard 51-99/AMCA Standard 210-99. In the proposed rule the words
``AMCA Standard'' were wrongly omitted.
The definitions of ``heating seasonal performance factor (HSPF),''
and ``seasonal energy efficiency ratio (SEER)'' have been modified to
move some text to later sections of the test procedure. The moved text
provided complementary information that was better placed in the main
text of the test procedure rather than in a definition. Sentences from
the definition of HSPF were moved to Section 4.2, ``Heating Seasonal
Performance Factor (HSPF) Calculations.'' Similarly, one sentence from
the definition of SEER became the first sentence in Section 4.1,
``Seasonal Energy Efficiency Ratio (SEER) Calculations.''
C. Testing Conditions
1. Section 2.2.4 Wet-Bulb Temperature Requirements for Air Entering the
Indoor and Outdoor Coils
The January 22, 2001, proposed rule included a requirement that
applied to wet-coil cooling tests of single-packaged units where all or
part of the indoor section is located in the outdoor test room. The
requirement was that the average dew point temperature of the air
entering the outdoor coil must be within 3.0[deg]F of the
average dew point temperature of the air entering the indoor coil. This
requirement was added to address concerns about equipment leakage
affecting capacity measurements. The water vapor content of the outdoor
air could affect the repeatability of the measurements. Similarly,
leakage could present a problem when using the Outdoor Air Enthalpy
test method for testing a single-packaged heat pump where all or part
of its outdoor section is located in the indoor test room.
In comments made at the March 29, 2001, public hearing and in
written comments received thereafter, York and ARI agreed with the
proposed requirements. ( Public Hearing Tr., p. 79; York, No. 9 at p.
4; ARI, No. 19 at p. 2) The Department has adopted the proposed test
requirement in today's final rule without alteration.
2. Section 2.2.5 Additional Refrigerant Charging Requirements
Existing testing procedures require that the unit be installed in
accordance with the manufacturer's installation instructions. The ARI,
as part of its certification program, occasionally makes decisions on
what is and is not within the spirit of the requirement. Thus, a policy
has evolved wherein ARI certification testing allows procedures such as
break-in times for compressors and washing the oil residue from the
coils prior to testing. ARI does not allow disconnecting an electrical
component, such as a crankcase heater. For the most part, the
Department chose to defer to ARI to maintain consistency in the test
set-ups. However, the Department proposed additional limits on the
specific issue of the refrigerant-charging procedure. In the section
2.2.5 of the January 22, 2001, proposed rule, the Department proposed
two additional requirements. First, the Department sought to avoid a
gray area of defining when an independent test laboratory should
consult with the manufacturer on how to charge a unit. The proposed
section included the sentence: ``For third party testing, for example,
do not consult the manufacturer about how to charge the unit.'' This
requirement was thought to place extra responsibility on the
manufacturer to publish accurate and clear charging instructions.
The second requirement was to promote the ideal of testing the unit
in a manner that is similar to its actual installation in the field.
The Department proposed amendments to section 2.2.5 to include the
following sentence: ``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.''
At the March 29, 2001, public hearing, ARI, ITS, and ACEEE spoke in
favor of allowing the independent test laboratory to contact the
manufacturer if it had any charging questions. (Public Hearing Tr.,
pages 101 to 112) This discussion noted the value of feedback in
assisting the manufacturer to identify mistakes or incompleteness in
its published instructions. Such feedback, if acted upon by the
manufacturer, could benefit the eventual field installer. At the public
hearing, attendees also came to the realization that the attempt to
prevent special lab-only charging criteria could likely be circumvented
by having a single criteria that listed wide ranges for such charging
parameters as the targeted superheat or subcooling level(s).
The Department considered deleting the proposed section 2.2.5.
However, today's final rule contains a revised version of the January
22, 2001, proposed rule language. (66 FR 6792) In the proposed rule,
for third-party testing, the test laboratory was not to consult with
the manufacturer about how to charge a unit. Based on the public
hearing comments discussed above, today's final rule has modified this
requirement. The test laboratory may consult with the manufacturer
about the refrigerant-charging procedure and make changes that do not
contradict the published installation instructions. The manufacturer
may specify an alternative charging criteria to the third-party
laboratory if the manufacturer then revises the published installation
instructions accordingly. DOE decided to keep the section in an effort
to convey the side benefit of the allowed feedback mechanism and to
emphasize that the goal is a lab set-up as consistent as possible with
a field installation.
D. Testing Procedures
1. Section 3.1.4 Airflow Through the Indoor Coil: Systems Having a
Variable-Speed, Constant Airflow Blower
The January 22, 2001, proposed rule included additions to the test
procedure for systems having a variable-speed, constant airflow (often
called constant CFM (cubic foot per minute)) blower. These additions
included:
(1) Controlling the exhaust fan of the airflow measuring
apparatus to obtain a specified external static pressure. DOE
received no comments on this addition.
(2) Specifying an additional test and algorithm to correct the
fan power in cases where the specified external static pressure
cannot be achieved during testing due to blower instabilities. ITS
and York commented in favor of this addition. (Public Hearing Tr.,
ITS, p. 72-73, York, p. 73)
(3) Making use of the fan laws if a unit must be tested at an
air volume rate other than the (cooling or heating) Certified Air
Volume Rate. DOE received no comments on this addition.
(4) Allowing cyclic tests to be conducted with or without the
indoor fan enabled and using a step profile for the air volume rate
during cyclic tests. DOE received no comments on this addition.
(5) Imposing an 8-percent tolerance for the difference between
the lab-measured and manufacturer-Certified Air Volume Rates.
At the March 29, 2001, public hearing, ARI, Trane, and York spoke
in favor of making a change to eliminate the eight percent tolerance.
(Public Hearing Tr., ARI, p. 69, Trane, p. 70, and York, p. 70) ARI and
York submitted written comments to the same effect. (ARI, No. 19 at p.
2; York, No. 9 at p. 2) Opposition to the eight
[[Page 59128]]
percent tolerance was based on the industry's not wanting another
certified parameter. ARI recommended that DOE limit its focus to rated
capacity and seasonal performance, SEER and HSPF, and not include
parameters that affect those values. (ARI, No. 19 at p. 2)
DOE proposed the tolerance to provide manufacturers with assurance
that any third-party testing would employ a representative air volume
rate. However, these blowers have a level of variability which may
occasionally exceed the proposed eight percent tolerance. The eight-
percent tolerance could cause several unnecessary stoppages in testing
where the impact on rated capacity and seasonal performance would be
negligible. Given the foreseeable unfavorable trade-off from imposing
the tolerance, the Department has eliminated the eight-percent
tolerance in today's final rule.
2. Sections 3.1.4.2, 3.1.4.5, 3.3, 3.5.1, 3.7, and 3.9.1. Testing a
Two-Capacity Compressor System: Coil-Only Units Tested at Low Capacity
and Differences in High/Low Cycling
The proposed test procedure sections 3.1.4.2 and 3.1.4.5 specified
that the air volume rate used when testing two-capacity, coil-only
units at low capacity (i.e., at the Minimum Air Volume Rate) is the
higher of:
(1) The rate specified by the manufacturer, or
(2) 75 percent of the air volume rate used for the high capacity
tests.
At both the public hearing and in its written comments, York
opposed the proposed 75-percent limit. (Public Hearing Tr., pp. 81-86;
York, No. 9 at p. 3) York argued that the limit was ``arbitrarily
derived, is unnecessary, and restrictive towards applying existing and
future technologies in motor speed controls. * * *'' (York, No. 9 at p.
3) Conversely, at both the public hearing and in their written
comments, both Copeland Corporation and ARI supported the defining of a
lower limit. Their written comments specifically endorsed assigning the
limit at 75 percent. (Public Hearing Tr., pp 86-90; Copeland
Corporation, No. 13 at p. 2; ARI, No. 19 at p. 2)
This 75-percent value is based on the assumption that the two-
capacity coil-only unit would most often be used with an existing
multi-tap furnace blower. The low range offered from typical multi-tap
motors can vary considerably. Nonetheless, the limited data collected
by NIST and by industry supports the proposed 75-percent value, and DOE
has included it in today's final rule.
The proposed test procedure sections 3.3, 3.5.1, 3.7 and 3.9.1 did
not differentiate between the default fan power values for high
capacity and low capacity. The value of 365 watts per 1000 standard
cubic feet per minute (SCFM) was used in all cases. Only York commented
on this issue, and York's comment supported the proposed test
procedure. (Public Hearing Tr., p. 94, York, No. 9 at p. 3) York
commented that the proposed low capacity default causes a conservative
prediction of fan power, with a resulting error too insignificant to
warrant a change. (York, No. 9 at p. 3) Today's final rule maintains
the changes on this subject incorporated into the proposed test
procedure.
The final two-capacity, compressor-system issue was whether there
is a significant performance difference between compressors (systems)
that can switch between low and high stages over a very short time
interval versus those having to turn off for a short period and take
longer overall to make the transition. (This issue is included because
DOE received comments about it. It does not appear in the proposed
rule, nor in today's final rule.) Copeland Corporation noted that it
has experience manufacturing both types of compressors and that it has
``observed that shutting a system down for greater than one minute has
nearly the same cyclic loss impact as a typical on/off CD
penalty, since the evaporator warms up almost completely.'' Copeland
encouraged the Department to study the issue further and stated that an
appropriate action may be to conduct a test program at Intertek Testing
Services (ITS). (Copeland Corporation, No. 13 at p. 1) York, on the
other hand, expressed its opinion that the difference in technology was
not significant enough to warrant a change in the test procedure.
(York, No. 9 at p. 3) The Department has been unable to identify test
procedure changes that could capture a performance difference, assuming
that its overall impact significantly alters the SEER and HSPF ratings.
The Department would have to make assumptions about the frequency of
high/low transitions as a function of the magnitudes of the low and
high stage capacities relative to each temperature bin building load.
Also, data are needed to determine whether the cooling and heating mode
on/off degradation coefficients could act as substitutes for the high/
low transition degradation or whether a separate optional test and/or
separate transition default values are warranted. In general, the
Department is willing to consider future changes to the test procedure
but asks that interested industry members take the lead in quantifying
the impact on SEER and HSPF before making specific recommendations on
how to alter the test procedure calculations.
III. Summary of Other Additions and Changes to the DOE Residential
Central Air Conditioner and Heat Pump Test Procedure
Today's final rule contains numerous changes that were proposed in
the January 22, 2001, proposed rule, for which the Department received
no adverse comments.
A. Update and Add References for ASHRAE and ARI Standards
The current test procedure references ASHRAE Standard 37-78 and
ASHRAE Standard 41.1 (no year), ARI Standard 210-79, ARI Standard 240-
77, and ARI Standard 320-76. Today's final rule also includes
references to ARI Standard 210/240-03, ASHRAE Standard 23-93, ASHRAE
Standard 37-88, ASHRAE Standard 41.1-86 (RA 01), ASHRAE Standard 41.2-
87 (RA 92), ASHRAE Standard 41.6-94 (RA 01), ASHRAE Standard 41.9-00,
ASHRAE Standard 51-99/AMCA Standard 210-99, and ASHRAE Standard 116-95.
The additional commercial standards are necessary to more completely
inform manufacturers and testers about the multiple test options,
especially for the secondary test method, and to address as many of the
small details of lab testing as possible. The additional commercial
standards were all included in the January 22, 2001, proposed rule. (66
FR 6768) Some of the commercial standards have been updated since the
publication of the proposed rule as discussed in section II.A.1 of this
preamble.
B. Air Volume Rates
The current test procedure references ARI Standard 240-77. Now,
rather than referencing ARI Standard 210/240-03, which replaced ARI
Standard 240-77, the Department has added its own sections to the test
procedure. The main reason for no longer referencing ARI Standard 210/
240 is that it does not cover variable-speed and constant CFM blowers.
In addition, ARI Standard 210/240 does not directly address two-
capacity and variable-speed systems. The Department believes it is
preferable to have the overall issue of air volume rates covered in one
place rather than in two.
The test procedure set forth in this final rule no longer
references ASHRAE Standard 37-78 (or ASHRAE Standard 37-88, its
replacement) for the equation
[[Page 59129]]
used to calculate the air volume rate of standard air, because the
referenced equation is incorrect. The factor ``1 +Wn'' is
missing from the denominator of the pertinent equation in both versions
of ASHRAE Standard 37. Today's test procedure includes what DOE
believes to be the correct version of the equation.
Today's test procedure also adopts the approach used in the ISO
Standard 5151 of conducting each test at zero external static pressure
when testing a non-ducted unit.
All of these ``air volume rate'' substantive changes were
originally published in the proposed rulemaking (66 FR 6778) and are
included in today's final rule.
C. Cyclic Testing
The Department is today adopting standard industry practice and the
method described in ASHRAE Standard 116. Sections 4.1.1.2, 4.1.2,
4.2.2.2, and 5.1 of the current (1988) test procedure require
measurement of the air volume rate during cyclic tests and use of this
measurement in determining the total cooling (heating) delivered.
Standard laboratory practice, by comparison, is to achieve and maintain
the same velocity pressure or nozzle static pressure drop that was
obtained during the comparable steady-state test. The total cooling
(heating) delivered during a cyclic test, in addition, is calculated
using the air volume rate measured during the comparable steady-state
test. Changes to adopt this industry practice and become consistent
with ASHRAE Standard 116 were introduced in the proposed rulemaking and
are included in today's final rule in section 3.1.
When testing split-type non-ducted (ductless) systems, section
4.1.1.5 of the current test procedure provides, ``The integration time
for capacity and power shall be from compressor cut-on time to indoor
fan cutoff time.'' The indoor fan is operated for three minutes prior
to compressor cut-on and for three minutes after compressor cutoff
during the final OFF/ON interval. In sections 3.5 and 3.5.2, today's
final rule adopts industry practice and integrates power from
compressor OFF to compressor OFF and subtracts the electrical energy
associated with operating the indoor fan during the initial three-
minute fan-only period. Space cooling capacity is integrated from
compressor ON to indoor fan OFF. As with the current test procedure,
fan energy for the three minutes after compressor cutoff is added to
the integrated cooling capacity.
The current test procedure does not contain specific information
regarding the air dampers: where to install them, how well they should
seal, and how quickly they should respond. Appendix D of ARI Standard
210/240-03 contains much of this information. Today's final rule
incorporates the required information in sections 2.5.4.1 and 2.5.7
rather than make specific references to each pertinent section of
Appendix D of the ARI Standard.
For dry coil tests, today's test procedure final rule adopts, in
section 3.4, the language in ARI Standard 210/240-03 Appendix D with
regard to the requirements that the drain pan be plugged and completely
dry.
Today's final rule clarifies in section 2.8 that the requirement of
making electrical energy measurements using an instrument having an
accuracy of 0.5 percent of reading applies during both the
ON and OFF intervals of cyclic tests.
Today's final rule deletes the current section 4.1.3.1, ``The
indoor and outdoor average dry-bulb temperature for the cyclic dry coil
test D shall both be within 1.0 [deg]F of the indoor and outdoor
average dry bulb temperature for the steady-state dry coil test C,
respectively.'' This requirement is automatically met given the 0.5
[deg]F test condition tolerance associated with each test. (Today's
amended test procedure is substantially re-organized; the section
4.1.3.1 in today's final rule has no relation to the deleted section
4.1.3.1.)
For units having a variable-speed indoor fan, the manufacturer will
have the option of conducting the cyclic tests with the indoor fan
either enabled or disabled, the latter being the default option if an
attempt at testing with the fan enabled is unsuccessful. See section
3.5 of today's final rule. Specifically, if the test is performed with
the indoor fan operating, and the fan automatically reverses, shuts
down, or operates at an uncharacteristically high external static
pressure, then the test must be repeated using a pull-thru method, with
the fan disabled.
Although a unit having a variable-speed indoor fan may be designed
to ramp its fan speed when cycling on and/or off, a step response in
air volume rate is nonetheless required during cyclic tests. See
section 3.5 of today's final rule. The work associated with moving the
additional air during the ramp periods is performed by the exhaust fan
of the air flow measuring apparatus. The step response begins at the
initiation of ramp up and ends at the termination of ramp down. The
rationale for imposing the step change is mainly due to the difficulty
in obtaining the ramp response and then making an accurate measurement
of the space conditioning delivered. Systems having indoor fans that
ramp are expected to have low cyclic degradation coefficients
(CD) regardless of whether the ramp feature is used, thus
the absolute improvement in CD is expected to be minor.
D. Fanless (Coil-Only) Units
Section 4.1 of the current test procedure calls for corrections to
capacity and power based on air flow measured in cubic feet per minute
(CFM). Section 4.2 of the current test procedure calls for corrections
to capacity and power based on air flow measured in cubic feet per
minute under standard conditions (SCFM). To avoid confusion, the test
procedure should base corrections on either CFM or SCFM, but not both.
ITS, which tests for both the industry and ARI, uses SCFM in all cases.
Therefore, in consideration of the above, today's test procedure
adopts, in sections 3.3, 3.5.1, and 3.7, the practice of specifying all
corrections in terms of SCFM.
The test procedure also adopts in section 2.2 the requirement in
ARI Standard 210/240-03, Appendix D, that an enclosure be constructed
using one-inch ductboard for testing a coil-only unit that does not
employ an enclosure.
E. Frost Accumulation Test
Today's final rule adopts the convention in ASHRAE Standard 116-95
and ARI 210/240-03 of specifying the outdoor wet bulb temperature (33
[deg]F) in place of the presently specified dew point temperature (30
[deg]F). Sections 3.6.1, 3.6.2, 3.6.3, and 3.6.4.
F. Test Tolerance Tables
The current test procedure contains tables covering all tests
except steady-state cooling-mode tests, for which Table III in ASHRAE
Standard 37-78 is referenced. Since the test procedure includes all
other tables, the Department chose to add the needed parts of Table III
(Table 7 of this document).
The test condition tolerance for external resistance to air flow
now applies only when testing non-ducted units. (See Table 7). Also,
DOE has added in Table 7 a test condition tolerance for electrical
supply voltage (previously, only a test operating tolerance was
specified). The existing test procedure lacked a clarification that the
test condition tolerance for the indoor inlet wet bulb temperature in
Table III of ASHRAE Standard 37-78 does not apply for dry coil tests.
Therefore, today's final rule includes a footnote to Table 7 that makes
this clarification. In a similar attempt to clarify when particular
tolerances apply, today's final rule also includes a
[[Page 59130]]
footnote to tables stating that the test tolerances given for the
outdoor outlet dry and wet bulb temperatures only apply when using the
Outdoor Air Enthalpy Method to provide the secondary capacity
measurement.
For the Frost Accumulation Test, DOE modified slightly the
intervals considered to be heating versus defrosting. Specifically, in
the current test procedure in section 4.2.3.3, the first five minutes
after a defrost termination was included in the defrost interval. In
today's final rule, the time interval has been increased to ten minutes
in section 3.7. This is a better approximation of the time needed for
temperatures to reach equilibrium after defrost termination. Also, in
making the test condition conversion of 30 [deg]F dew point to 33
[deg]F wet bulb, the test operating tolerance and test condition
tolerance convert to wet bulb temperature tolerances of 0.6 [deg]F and
0.3 [deg]F, respectively. This 0.6 [deg]F test operating tolerance on
outdoor wet bulb temperature is more stringent than the value allowed
for the steady-state tests. The 0.3 [deg]F test condition tolerance is
the same as required for steady-state tests. Because these tolerances
should be less stringent that those required of a steady-state test,
the test procedure adopts in Table 15 the values given in ASHRAE
Standard 37: 1.5 [deg]F and 0.5 [deg]F.
G. Pretest Intervals
1. Wet Coil Tests
The following change makes the test conditions more specific than
they are in the current test procedure:
Current: ``The test room reconditioning apparatus and the equipment
under test shall be operated until equilibrium conditions are
attained.'' (Section 4.1.1.1)
Today's final rule: ``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.'' (Section 3.3)
2. Dry Coil Steady-State Test
The following change also makes the test conditions more specific
than they are in the current test procedure. The industry realized the
merits of this improved wording several years ago. The added text is
taken from a prescriptive methodology that appears within an appendix
of ARI Standard 210/240-2003.
Current: ``The test room reconditioning apparatus and the equipment
under test shall be operated until equilibrium conditions are attained,
but not for less than one hour before data for test C are recorded.''
(Section 4.1.1.2)
Today's final rule: Same as proposed for section 3.3 wet coil tests
with the additional requirement to ``operate the unit at least one hour
after achieving dry coil conditions.'' (Section 3.4)
3. Dry Coil Cyclic Test
The following change makes the test conditions more specific than
they are in the current test procedure. The existing language is weaker
because the phrase ``until steadily repeating ambient conditions are
again achieved'' is comparatively subjective.
Current: ``[T]est unit shall be manually cycled `off' and `on'* * *
until steadily repeating ambient conditions are again achieved in both
the indoor and outdoor test chambers, but for not less than two
complete `off/on' cycles.'' (Section 4.1.1.2)
Today's final rule: ``After completing a minimum of two complete
compressor OFF/ON cycles, determine the overall cooling delivered and
total electrical energy consumption during any subsequent data
collection interval where the test tolerances given in Table 8 are
satisfied.'' (Section 3.5)
4. Maximum and High Temperature Heating Mode Tests
The requirement for the test apparatus and the test unit to operate
for at least one hour was dropped based on industry comments that it
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