[Federal Register Volume 75, Number 105 (Wednesday, June 2, 2010)]
[Proposed Rules]
[Pages 31224-31271]
From the Federal Register Online via the Government Publishing Office [www.gpo.gov]
[FR Doc No: 2010-12271]
[[Page 31223]]
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Part III
Department of 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; Proposed Rule
Federal Register / Vol. 75, No. 105 / Wednesday, June 2, 2010 /
Proposed Rules
[[Page 31224]]
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DEPARTMENT OF ENERGY
10 CFR Part 430
[Docket No. EERE-2009-BT-TP-0004]
RIN 1904-AB94
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: Notice of proposed rulemaking and public meeting.
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SUMMARY: The U.S. Department of Energy (DOE) proposes amendments to its
test procedure for residential central air conditioners and heat pumps.
The proposed amendments would add requirements for the calculation of
sensible heat ratio, incorporate a method to evaluate off mode power
consumption, and add parameters for establishing regional measures of
energy efficiency. DOE will hold a public meeting to receive and
discuss comments on the proposal.
DATES: DOE will hold a public meeting in Washington, DC on Friday, June
11, 2010 from 9 a.m. to 4 p.m. The purpose of the meeting is to receive
comments and to help DOE understand potential issues associated with
this proposed rulemaking. DOE must receive requests to speak at the
meeting before 4 p.m. Friday, June 4, 2010. DOE must receive a signed
original and an electronic copy of statements to be given at the public
meeting before 4 p.m. Friday, June 4, 2010.
DOE will accept comments, data, and other information regarding
this notice of proposed rulemaking (NOPR) before or after the public
meeting, but no later than August 16, 2010. See section V., ``Public
Participation,'' of this NOPR for details.
ADDRESSES: The public meeting will be held at the U.S. Department of
Energy, Forrestal Building, Room 8E-089. You may submit comments,
identified by docket number EERE-2009-BT-TP-0004 and/or Regulation
Identifier Number (RIN) 1904-AB94, by any of the following methods:
Federal eRulemaking Portal http://www.regulations.gov.:
Follow the instructions for submitting comments.
E-mail: [email protected]. Include the
docket number EERE-2009-BT-TP-0004 and/or RIN number 1904-AB94 in the
subject line of the message.
Postal Mail: Ms. Brenda Edwards, U.S. Department of
Energy, Building Technologies Program, Mailstop EE-2J, 1000
Independence Avenue, SW., Washington, DC 20585-0121. Please submit one
signed paper original.
Hand Delivery/Courier: Ms. Brenda Edwards, U.S. Department
of Energy, Building Technologies Program, 6th Floor, 950 L'Enfant
Plaza, SW., Washington, DC 20024. Telephone: (202) 586-2945. Please
submit one signed paper original.
Instructions: All submissions must include the agency name and
docket number or RIN for this rulemaking. For detailed instructions on
submitting comments and additional information on the rulemaking
process, see section V., ``Public Participation,'' of this document.
Docket: For access to the docket to read background documents or
comments received, visit the U.S. Department of Energy, 6th Floor, 950
L'Enfant Plaza, SW., Washington, DC 20024, (202) 586-2945, between 9
a.m. and 4 p.m., Monday through Friday, except Federal holidays. Please
call Ms. Brenda Edwards at (202) 586-2945 for additional information
regarding visiting the Resource Room. Please note: DOE's Freedom of
Information Reading Room (Forrestal Building, Room 1E-190) no longer
houses rulemaking materials.
FOR FURTHER INFORMATION CONTACT: Mr. Wes Anderson, U.S. Department of
Energy, Office of Energy Efficiency and Renewable Energy, Building
Technologies Program, EE-2J, 1000 Independence Avenue, SW., Washington,
DC 20585-0121. Telephone: (202) 586-7335. E-mail:
[email protected].
Ms. Francine Pinto, U.S. Department of Energy, Office of the
General Counsel, GC-71, 1000 Independence Avenue, SW., Washington, DC
20585. Telephone: (202) 586-7432. E-mail: [email protected].
SUPPLEMENTARY INFORMATION:
I. Authority and Background
A. Authority
B. Background
II. Summary of the Proposed Rule
III. Discussion
A. Framework Comment Summary and DOE Responses
1. Test Procedure Schedule
2. Bench Testing of Third-Party Coils
3. Defaults for Fan Power
4. Changes to External Static Pressure Values
5. Fan Time Delay Relays
6. Inverter-Driven Compressors
7. Addition of Calculation for Sensible Heat Ratio
8. Regional Rating Procedure
9. Address Testing Inconsistencies for Ductless Mini- and Multi-
Splits
10. Standby Power Consumption and Measurement
B. Summary of the Test Procedure Revisions
1. Modify the Definition of ``Tested Combination'' for
Residential Multi-Split Systems
2. Add Alternative Minimum External Static Pressure Requirements
for Testing Ducted Multi-Split Systems
3. Clarify That Optional Tests May Be Conducted Without
Forfeiting Use of the Default Value(s)
4. Allow a Wider Tolerance on Air Volume Rate To Yield More
Repeatable Laboratory Setups
5. Change the Magnitude of the Test Operating Tolerance
Specified for the External Resistance to Airflow and the Nozzle
Pressure Drop
6. Modify Third-Party Testing Requirements When Charging the
Test Unit
7. Clarify Unit Testing Installation Instruction and Address
Manufacturer and Third-Party Testing Laboratory Interactions
8. When Determining the Cyclic Degradation Coefficient
CD, Correct the Indoor-Side Temperature Sensors Used
During the Cyclic Test To Align With the Temperature Sensors Used
During the Companion Steady-State Test, If Applicable
9. Clarify Inputs for the Demand Defrost Credit Equation
10. Add Calculations for Sensible Heat Ratio
11. Incorporate Changes To Cover Testing and Rating of Ducted
Systems Having More Than One Indoor Blower
12. Add Changes To Cover Triple-Capacity, Northern Heat Pumps
13. Specify Requirements for the Low-Voltage Transformer Used
When Testing Only Air Conditioners and Heat Pumps and Require
Metering of All Sources of Energy Consumption During All Tests
14. Add Testing Procedures and Calculations for Off Mode Energy
Consumption
15. Add Parameters for Establishing Regional Standards
a. Use a Bin Method for Single-Speed SEER Calculations for the
Hot-Dry Region and National Rating
b. Add New Hot-Dry Region Bin Data
c. Add Optional Testing at the A and B Test Conditions With the
Unit in a Hot-Dry Region Setup
d. Add a New Equation for Building Load Line in the Hot-Dry
Region
16. Add References to ASHRAE 116-1995 (RA 2005) for Equations
That Calculate SEER and HSPF for Variable Speed Systems
17. Update Test Procedure References to the Current Standards of
AHRI and ASHRAE
IV. Regulatory Review
A. Review Under Executive Order 12866
B. Review Under the National Environmental Policy Act
C. Review Under the Regulatory Flexibility Act
D. Review Under the Paperwork Reduction Act
[[Page 31225]]
E. Review Under the Unfunded Mandates Reform Act of 1995
F. Review Under the Treasury and General Government
Appropriations Act, 1999
G. Review Under Executive Order 13132
H. Review Under Executive Order 12988
I. Review Under the Treasury and General Government
Appropriations Act, 2001
J. Review Under Executive Order 13211
K. Review Under Executive Order 12630
L. Review Under Section 32 of the Federal Energy Administration
(FEA) Act of 1974
V. Public Participation
A. Attendance at Public Meeting
B. Procedure for Submitting Requests To Speak
C. Conduct of Public Meeting
D. Submission of Comments
E. Issues on Which DOE Seeks Comment
VI. Approval of the Office of the Secretary
I. Authority and Background
A. Authority
Title III of the Energy Policy and Conservation Act (42 U.S.C. 6291
et seq.; EPCA or the Act) sets forth a variety of provisions designed
to improve energy efficiency. Part A of Title III (42 U.S.C. 6291-6309)
establishes the ``Energy Conservation Program for Consumer Products
Other Than Automobiles.'' (This part was originally titled Part B;
however, it was redesignated Part A in the United States Code for
editorial reasons.) The program covers consumer products and certain
commercial products (collectively ``covered products''), including
residential central air conditioners and heat pumps having rated
cooling capacities less than 65,000 British thermal units/hour (Btu/h).
(42 U.S.C. 6291(1)-(2), (21) and 6292(a)(3))
Under the Act, the overall program consists of testing, labeling,
and Federal energy conservation standards. Manufacturers of covered
products must use the test procedures prescribed under EPCA to measure
energy efficiency, to certify to DOE that products comply with EPCA's
energy conservation standards, and for representing the energy
efficiency of their products. Similarly, DOE must use these test
procedures when determining whether the equipment complies with energy
conservation standards adopted pursuant to EPCA.
Section 323 of EPCA (42 U.S.C. 6293) sets forth generally
applicable criteria and procedures for DOE's adoption and amendment of
such test procedures. For example, the Act states that ``[a]ny test
procedures prescribed or amended under this section shall be reasonably
designed to produce test results which measure energy efficiency,
energy use * * * or estimated annual operating cost of a covered
product during a representative average use cycle or period of use, as
determined by the Secretary [of Energy], and shall not be unduly
burdensome to conduct.'' (42 U.S.C. 6293(b)(3)) DOE's existing test
procedures for central air conditioners and heat pumps adopted pursuant
to these provisions appear under Title 10 of the Code of Federal
Regulations (CFR) part 430, subpart B, appendix M (``Uniform Test
Method for Measuring the Energy Consumption of Central Air Conditioners
and Heat Pumps'').
Further, if any rulemaking amends a test procedure, DOE must
determine ``to what extent, if any, the proposed 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 it determines that the amended test procedure would alter the
measured efficiency of a covered product, DOE must amend the applicable
energy conservation standard accordingly. (42 U.S.C. 6293(e)(2)) The
amendments proposed in today's rulemaking will not alter the measured
efficiency, as represented in the regulating metrics of SEER and HSPF.
Thus, today's proposed test procedure changes can be adopted without
amending the standards for SEER and HSPF.
On December 19, 2007, the President signed the Energy Independence
and Security Act of 2007 (EISA 2007; Pub. L. 110-140), which contains
numerous amendments to EPCA. Section 310 of EISA 2007 established that
the Department's test procedures for all covered products must account
for standby and off mode energy consumption. (42 U.S.C. 6295(gg)(2)(A))
DOE must modify the test procedures to integrate such energy
consumption into the energy descriptor(s) for each product, unless the
Secretary determines that ``(i) the current test procedures for a
covered product already fully account for and incorporate the standby
mode and off mode energy consumption of the covered product; or (ii)
such an integrated test procedure is technically infeasible * * * in
which case the Secretary shall prescribe a separate standby mode and
off mode energy use test for the covered product, if technically
feasible. (42 U.S.C. 6295 (gg)(2)(A)) In addition, section 306(a) of
EISA 2007 amended EPCA section 325(o)(6) to consider one or two
regional standards for central air conditioners and heat pumps (among
other products) in addition to a base national standard. (42 U.S.C.
6295(o)(6)(B)) EPCA 325(o)(6)(C)(i) requires that DOE consider only
regions made up of contiguous States. (42 U.S.C. 6295(o)(6)(C)(i))
Accordingly, today's proposed test procedure rulemaking includes
additions that specifically address sections 306 and 310 of EISA 2007.
B. Background
Most portions of the existing test procedure for central air
conditioners and heat pumps were originally published as a final rule
in the Federal Register on December 27, 1979. 44 FR 76700. DOE modified
the test procedure on March 14, 1988, to expand coverage to variable-
speed central air conditioners and heat pumps, to address testing of
split non-ducted units, and to change the method for crediting heat
pumps that provide a demand defrost capability. 53 FR 8304.
The next revision of the central air conditioners and heat pumps
test procedure was published as a final rule on October 11, 2005, and
became effective on April 10, 2006. 70 FR 59122. The October 2005 final
rule provided a much needed updating to reference current standards,
adopted improved measurement capabilities, and presented more detail on
how to conduct the laboratory testing. The 2005 final rule also
expanded coverage for equipment features previously not covered (e.g.,
two-capacity northern heat pumps, heat comfort controllers, triple-
split systems, etc.). During this revision process, the test procedure
was significantly reorganized in an effort to improve its readability.
On July 20, 2006, DOE published a proposed rule to consider
additional changes to the test procedure in response to issues
interested parties submitted before the October 2005 publication of the
final rule. 71 FR 41320. DOE determined that it was appropriate to
consider additional modifications to the test procedure for the
following reasons: (1) To implement test procedure revisions for new
energy conservation standards for small-duct, high-velocity (SDHV)
systems; (2) to address test procedure waivers for multi-split systems;
and (3) to address interested parties' concerns about sampling and
rating after new energy conservation standards became effective on
January 23, 2006. (10 CFR 432.32(c)(2)) DOE issued a final rule
adopting relevant amendments to the central air conditioner and heat
pump test procedures on October 22, 2007, which became effective on
April 21, 2008. 72 FR 59906. This latter final rule was published
before EISA's implementation on December 19, 2007; therefore, the test
procedures did not incorporate the requirements in sections 306 and 310
of EISA 2007.
[[Page 31226]]
While making changes necessary to comply with the amendments in
EISA 2007, DOE is considering additional changes to the test procedure
that were identified after finalizing the prior rulemaking.
II. Summary of the Proposed Rule
DOE proposes amendments to its test procedure for residential
central air conditioners and heat pumps. The amendments would add
calculations for determination of sensible heat ratio (SHR), would
incorporate a method to evaluate off mode power consumption, and would
add parameters for establishing regional measures of energy efficiency.
In addition to statutory requirements for amended test procedures,
EISA 2007 has three separate provisions regarding the inclusion of
standby mode and off mode energy use in any energy conservation
standard that have bearing on the current test procedure rulemaking.
First, test procedure amendments to include standby mode and off mode
energy consumption shall not be used to determine compliance with
standards established prior to the adoption of such test procedure
amendments. (42 U.S.C. 6295(gg)(2)(C)) Second, standby mode and off
mode energy use must be included into a single amended or new standard
for a covered product adopted in a final rule after July 1, 2010.
Finally, a separate standard for standby mode and off mode energy
consumption is required if a single amended or new standard is not
feasible. (42 U.S.C. 6295(gg)(3)(B))
In order to accommodate the above-mentioned first provision, DOE
clarifies that today's proposed amended test procedure would not alter
the measure of energy efficiency used in existing energy conservation
standards; therefore, this proposal would neither affect a
manufacturer's ability to demonstrate compliance with previously
established standards nor require retesting and rerating of existing
units that are already certified. These amended test procedures would
become effective, in terms of adoption into the CFR, 30 days after the
date of publication in the Federal Register of the final rule in this
test procedure rulemaking. However, DOE is proposing added language to
the regulations codified in the CFR that would state that any added
procedures and calculations for determining off mode energy consumption
and regional cooling mode performance being proposed in order to
satisfy the relevant provisions of EISA 2007 need not be performed at
this time to determine compliance with the current energy conservation
standards. Subsequently, and consistent with the second provision
above, manufacturers would be required to use the amended test
procedures' off mode and regional cooling mode provisions to
demonstrate compliance with DOE's energy conservation standards on the
effective date of a final rule establishing amended energy conservation
standards for these products that address off mode energy consumption
and/or regional cooling mode performance, at which time the limiting
statement in the DOE test procedure would be revised or removed.
Further clarification would also be provided that as of 180 days after
publication of a test procedure final rule, any representations as to
the off mode energy consumption and regional cooling mode performance
of the products that are the subject of this rulemaking would need to
be based upon results generated under the applicable provisions of this
test procedure. (42 U.S.C. 6293(c)(2)) A separate standard for off-mode
energy consumption is required if a single amended or new standard is
not feasible. (42 U.S.C. 6295(gg)(3)(B))
III. Discussion
The current standards rulemaking preliminary analysis for
residential central air conditioners and heat pumps is ready for
stakeholder review and comment. This preliminary analysis follows the
first step in the standards rulemaking process, the release of the
framework document (http://www1.eere.energy.gov/buildings/appliance_standards/residential/pdfs/cac_framework.pdf) and the subsequent June
12, 2008 public meeting. At and following this latter meeting,
stakeholder comments were received, some of which apply to today's
proposed test procedure.
In formulating today's notice of proposed rulemaking (NOPR), DOE
considered these test procedure related comments and, where
appropriate, proposed changes to the test procedure. Moreover, DOE
responses to stakeholder comments are provided in the following subject
areas:
1. Test Procedure Schedule
2. Bench Testing of Third Party coils
3. Defaults for Fan Power
4. Changes to External Static Pressure Values
5. Fan Time Delay Relays
6. Inverter-Driven Compressors
7. Addition of Calculation for Sensible Heat Ratio
8. Regional Rating Procedure
9. Address Testing Inconsistencies for Ductless Mini- and Multi-
Splits
10. Standby Power Consumption and Measurement
Section III. A. provides a more in-depth discussion on those
comments that questioned or disagreed with DOE's positions in the
framework document.
Section III. B. provides a summary of the proposed changes to the
test procedure, including
1. Modify the definition of ``tested combination'' for residential
multi-split systems
2. Add Alternative Minimum External Static Pressure Requirements
for Testing Ducted Multi-Split Systems
3. Clarify that Optional Tests May Be Conducted Without Forfeiting
Use of the Default Value(s)
4. Allow a Wider Tolerance on Air Volume Rate to Yield More
Repeatable Laboratory Setups
5. Change the Magnitude of the Test Operating Tolerance Specified
for the External Resistance to Airflow and the Nozzle Pressure Drop
6. Modify Third-Party Testing Requirements when Charging the Test
Unit
7. Clarify Unit Testing Installation Instruction and Address
Manufacturer and Third-Party Testing Laboratory Interactions
8. When Determining the Cyclic Degradation Coefficient
CD, Correct the Indoor-Side Temperature Sensors Used During
the Cyclic Test to Align with the Temperature Sensors Used During the
Companion Steady-State Test, If Applicable
9. Clarify Inputs for the Demand Defrost Credit Equation
10. Add Calculations for Sensible Heat Ratio
11. Incorporate Changes to Cover Testing and Rating of Ducted
Systems Having More than One Indoor Blower
12. Add Changes To Cover Triple-Capacity, Northern Heat Pumps.
13. Specify Requirements for the Low-Voltage Transformer Used when
Testing Coil-Only Air Conditioners and Heat Pumps and Require Metering
of All Sources of Energy Consumption During All Tests
14. Add Testing Procedures and Calculations for Off Mode Energy
Consumption
15. Add Parameters for Establishing Regional Standards
As part of today's rulemaking, DOE provides the specific proposed
changes to 10 CFR part 430, subpart B, appendix M, ``Uniform Test
Method for Measuring the Energy Consumption of Central Air Conditioners
and Heat Pumps.''
A. Framework Comment Summary and DOE Responses
A notation in the form ``Southern Company Systems (SCS), No. 13 at
p. 105'' identifies a written comment DOE
[[Page 31227]]
has received and has included in the docket of this rulemaking. This
particular notation refers to a comment (1) by the Southern Company
Systems (SCS); (2) in document number 13 in the docket of this
rulemaking; and (3) appearing on page 105 of document number 13.
1. Test Procedure Schedule
Several interested parties commented that DOE should consider the
timeline necessary when modifying this test procedure, and how the
publication of the test procedure coincides with publication of the
revised standard. (Southern Company Systems (SCS), No. 13 at p. 105;
Air-Conditioning, Heating and Refrigeration Institute (AHRI), No. 13 at
p. 116; the American Council for an Energy Efficient Economy (ACEEE),
No. 13 at p. 117; Trane, No. 13 at p. 123)
DOE is coordinating the publication timelines of both the test
procedure and the amended standard. The test procedure NOPR will be
open for public comments. DOE will then address those comments and
publish a final test procedure rule. The associated standard will
proceed concurrently with the test procedure rulemaking to maximize the
time interval between the test procedure final rule and the revised
energy standards final rule.
2. Bench Testing of Third-Party Coils
The Northeast Energy Efficiency Partnerships (NEEP) comment stated
that test procedures should require laboratory/bench testing for
independent coil manufacturers' (ICM) indoor units. (NEEP, No. 37 at p.
3) NEEP includes representatives from the Connecticut Office of Policy
and Management, New Hampshire Office of Energy and Planning, Efficiency
Maine, and Department of Energy Resources for the Commonwealth of
Massachusetts.
As amended, EPCA makes all residential central air conditioners and
heat pumps sold in the United States subject to specific testing,
rating, minimum efficiency, and labeling requirements. These
requirements apply to complete systems, including those split systems
where the outdoor components are provided by one manufacturer, while
the indoor components are provided by a separate manufacturer. The
typical two-manufacturer split system is where the indoor unit is
provided by an ICM and the outdoor unit is provided by an original
equipment manufacturer (OEM). Because the ICM wants to advertise the
performance of its indoor coils with various OEM outdoor units, the ICM
is responsible for obtaining the system seasonal energy efficiency
ratio (SEER) and heating seasonal performance factor (HSPF) ratings
according to DOE requirements. In obtaining these ratings, the ICM can
either test complete systems or use a DOE-approved alternative rating
method (ARM) to calculate the rating. Approval of the ARM requires
laboratory test results for complete systems, but inputs to the ARM may
or may not require testing of just the indoor unit. (10 CFR 430.24)
Although DOE does not have the authority to regulate a component of
an air conditioner or heat pump system, it does regulate the complete
systems. The system ratings published by ICMs must be obtained in
accordance with DOE requirements summarized above.
3. Defaults for Fan Power
A Joint Comment stated that the present rating method does not
credit advanced air handler designs adequately because the default
value is much lower than the average air handler energy use observed in
the field. (Joint Comment, No. 25 at pp. 4, 6-7) According to the Joint
Comment, a low default value for fan power reduces the incentive to
improve fan efficiency. The Joint Comment includes representatives from
ACEEE, Appliance Standards Awareness Project (ASAP), the California
Energy Commission (CEC), the Northwest Power and Conservation Council
(NPCC), and the Western Cooling Efficiency Center (WCEC).
Proctor Engineering Group (Proctor) stated that the inside coil fan
energy needs to represent the median values from actual installations,
and also provided input on the methodology for evaluating fan power
based on air volume rate and equipment tonnage. (Proctor, No. 38 at p.
1)
NEEP stated that testing should be required for motors in actual
operation and that the procedure should include provisions for testing
while air handler fans are running. (NEEP, No. 37 at p. 3)
Split-system ducted air conditioners and heat pumps are primarily
designed for two different applications. These applications depend on
whether the air conditioner or heat pump is installed with a hot-air
furnace and share a common duct system. Air conditioners and heat pumps
not designed for installation with a hot-air furnace must contain a
blower to circulate air through the indoor coil and ductwork. Systems
that include the integral or modular indoor blower are typically
referred to as blower-coil units. Coil-only units--air conditioners and
heat pumps designed for installation with a hot-air furnace--rely on
the furnace blower to circulate air through the indoor coil, ductwork,
and the furnace section when the compressor and outdoor fan are
operating.
The Joint Comment pertains to coil-only units, so discussion in the
following paragraphs is limited to those products. This comment does
not apply to blower-coil units within the test procedure because there
is no required default assumption for the average air handler. With
regard to the NEEP comment, the ratings for blower coil units already
reflect the performance of the system's particular indoor blower. When
blower coils are tested, the indoor blower operates, and its
performance is accounted for in the measured system capacity and power
consumption values and ultimately in SEER and HSPF.
A coil-only air conditioner or heat pump can be installed with a
multitude of new and existing furnaces. The key considerations for
matching a coil-only unit with a furnace are (1) the furnace blower's
ability to provide the necessary air volume rate for the system; and
(2) whether the outlet flange dimensions of the furnace are compatible
with the inlet flanges on the indoor coil-only section of the air
conditioner or heat pump. Another factor for field application is
whether the overall height (length) of the furnace and coil-only indoor
section will fit into the available building space.
The SEER and HSPF ratings represent the seasonal efficiencies of a
complete, functioning air conditioner or heat pump system. However,
coil-only split systems in laboratory testing are incomplete because a
hot-air furnace is not part of the setup. Instead of the furnace
blower, the exhaust fan in the test facility pulls air through the
indoor unit of the coil-only system. The exhaust fan is located
downstream of the test unit's indoor section, outlet instrumentation,
and air volume measurement station. When the hot-air furnace and blower
are removed from testing, the associated power consumption and measured
cooling or heating capacity are adjusted to account for the
hypothetical hot-air furnace blower. The Joint Comment asserted that
the test procedure default value is too low and should require
additional real-time blower testing. Proctor Engineering Group agreed
and offered an alternative default equation based on data collected
from actual installations.
Given the variety of furnaces within which a coil-only unit may be
installed, the range of blower sizes and associated efficiency of a
complete installed system are unknown. As a result, there are several
options for calculating the assumed power and heat contributions for
the hypothetical hot-air furnace
[[Page 31228]]
blower. To obtain a SEER (and for heat pumps, an HSPF) rating for each
coil-only split system, the hot-air furnace blower receives a default
value. According to the DOE test procedure, the hypothetical hot-air
furnace blower contribution is expressed in terms of power (watts) and
heat (Btu/h) per unit of air volume rate (in this case, 1,000 standard
cubic feet per minute [scfm]).
Since it was issued in 1979, the DOE test procedure for central air
conditioners and heat pumps has used the same default fan power and
heat for rating coil-only air conditioners and heat pumps: 365 watts
per 1,000 scfm and 1,250 Btu/h per 1,000 scfm. These default values
result in the adjustment range from approximately 220 watts (750 Btu/h)
for a 1.5-ton unit to approximately 730 watts (2,500 Btu/h) for a 5-ton
unit.
The default value does not indicate the efficiency of blowers in
furnaces; it simply provides a means of comparing products on a
complete system basis. The long-standing default values represent a
typical furnace blower while not being overly conservative. Changing
the default values would shift the SEER and HSPF ratings, but the
ranking among most comparably sized equipment would change minimally,
if at all. DOE evaluated the worst-case scenario: multiple units with
the same SEER calculated using the existing fan power and heat
defaults, but with degradation coefficients (CD) varying from 0.01 and
0.25, and capacities differing up to 10 percent. If the SEER
calculation uses a higher default like 500 watts per 1,000 scfm (1,700
Btu/h per 1,000 scfm), the new SEER ratings would all decrease but lie
within a range that spans less than 0.20 points (on the SEER rating
scale). The minimal impact on the ranking lessens the need for better
defaults. To determine whether higher default values better represent
actual installations, DOE must address three questions:
What data can accurately represent the typical
installation?
What coordination will ensure that blower coils and coil-
only units are evaluated on a common basis?
Should poor duct systems affect equipment ratings?
DOE expects that addressing these questions will require additional
data collection, analysis, and input from interested parties. With
minimal impact on altering the relative ranking among competing
products combined with the need to answer the above questions, DOE
chose not to propose alternative default values for the power and heat
contribution of the hypothetical furnace blower used when calculating
the SEER and HSPF for coil-only air conditioners and heat pumps.
4. Changes to External Static Pressure Values
A Joint Comment stated that the current assumed inches of water
column (in wc) values are lower than those typically found in the field
and unrealistically deemphasize the importance of fan efficiency as a
part of overall system effectiveness. (Joint Comment, No. 25 at pp. 4,
6) The discrepancy often leads to less airflow in a field application,
which generally improves latent (at the expense of sensible) capacity.
The Joint Utility Comment suggested that new test conditions for
external static pressure and default fan power should be consistent
with current field research findings. (Joint Utility Comment, No. 30 at
pp. 1, 21) The Joint Utility Comment includes representatives from
Pacific Gas and Electric Company (PG&E), Southern California Edison,
Sempra Energy Utilities (Southern California Gas Company and San Diego
Gas and Electric Company; hereafter ``Sempra''), Sacramento Municipal
Utility District, the Nevada Power Company, and Sierra Pacific Power.
DOE received a number of comments requesting that the minimum
external static pressure levels be increased. (Florida Solar Energy
Center (FSEC), No. 31 at p. 4; Sempra, No. 13 at p. 121; SCS, No. 39 at
p. 2) Additionally, Proctor Engineering Group (Proctor) provided a
formula for estimating the static pressure based on the rated cfm/ton
(Proctor, No. 38 at p. 2).
Some split system and all single-package system air conditioners
and heat pumps are sold with integral indoor blowers. Split systems
with integral indoor blowers (i.e., blower-coil units) may be designed
for ducted or non-ducted installation. The integral indoor blower may
be located either upstream (push-through configuration) or downstream
(draw-through configuration) of the indoor refrigerant-to-air heat
coil.
To mimic a field installation, single-package and blower-coil split
air conditioners and heat pumps are laboratory tested with installed
components to include the most restrictive filter(s), supplementary
heating coils, and other equipment specified as part of the unit. The
DOE test procedure allows testing of a ducted unit without an indoor
air filter but requires a compensatory increase of 0.08 in wc for the
minimum external static pressure requirement. Otherwise, the test
procedure requires that the unit be installed and configured in
accordance with the manufacturer's instructions.
The DOE test procedure requires that a minimum external static
pressure be equaled or exceeded during the wet-coil cooling mode test.
If this requirement is not met initially, the configuration of the
indoor unit is incrementally changed (e.g., switched to the next
highest speed tap), and the wet-coil test is repeated until the
measured external static pressure meets or surpasses the applicable DOE
test procedure minimum value.
Since its issuance in 1980, the DOE test procedure for central air
conditioners and heat pumps has used the same set of minimum external
static pressure values (except for SDHV systems): 0.10 in wc for
systems with a rated cooling capacity less than or equal to 28,800 Btu/
h, 0.15 in wc for 29,000 to 42,500 Btu/h, and 0.20 in wc for 43,000 to
64,500 Btu/h. The laboratory static pressure measurement tries to
account for the supply and return home or building duct system unit
flow resistance.
Limited field testing reports and the general decline in the
quality of installed duct systems (in part from the proliferation of
the flexible duct) would support an increase in the minimum external
static pressure. Efforts by building trades and code compliance
communities to improve the quality of installed duct systems would
support smaller increases in the minimum statics prescribed in the DOE
test procedure. More field data would be helpful but would likely never
be acquired to the level needed to provide a definitive basis for
selecting new minimums. The greater impact of higher minimum external
static pressures will be on lowering the SEER and HSPF of all units
equally. Lacking a basis to propose new values or reference a consensus
standard where alternatives to the current minimums are established,
DOE chose not to propose an alternative to the existing minimum values
as part of today's NOPR.
5. Fan Time Delay Relays
FSEC and SCS commented that the fan time delay relays should be
disabled for the SEER test procedure. (FSEC, No. 31 at p. 3; SCS, No.
39 at p. 2)
Many air conditioners and heat pumps employ a fan-off delay feature
on the indoor blower. This delay, which is usually active for both the
cooling and heating modes, is used to extract stored energy from the
indoor coil immediately after the compressor has cycled off. The indoor
blower typically continues to operate for 45 to 90 seconds after the
compressor cycles off.
[[Page 31229]]
The DOE test procedure seeks to evaluate the performance of central
air conditioners and heat pumps without making the process overly
burdensome or expensive. The test procedure includes optional cyclic
tests used to quantify the degradation in performance from the system
cycling (predominantly in field installation) compared with operating
continuously (as in most laboratory tests). During these cyclic tests,
the fan-off delay feature is not disabled. The evaluation thus accounts
for an incremental increase in total delivered capacity at the expense
of increased electrical energy consumption in extending the indoor
blower operation.
Disabling the fan time delay from central air conditioners and heat
pumps during the cooling season will prevent re-evaporation of moisture
on the indoor coil and in the condensation pan. Substantial re-
evaporation can occur if the indoor blower continues for an extended
period after compressor shutoff. Because of this evaporative mechanism,
continuous fan operation is discouraged during the cooling season.
However, DOE is not aware of definitive data that show significant re-
evaporation during short fan-off delays. Part of the data void is due
to the challenge of measuring rapidly changing values (humidity and
temperature) during the relatively short fan-off delay period. Because
of this difficulty, the cyclic cooling mode test, used in establishing
the SEER, is conducted at an indoor wet bulb (wb) temperature that
results in a dry coil. This also explains why this test cannot be used
to address the concern about re-evaporation.
In a related comment, Proctor recommended conducting the cooling
mode cyclic tests with the indoor conditions set to the same values
used for the steady-state tests, 80 degrees Fahrenheit ([deg]F) dry
bulb (db)/67 [deg]F wb (Proctor, No. 38 at p. 2). Proctor stated that
such a change to wet-coil cooling mode cyclic tests is well within the
reach of today's measurement technologies.
DOE needs additional information to quantify the potential benefits
of converting from dry-coil to wet-coil cyclic testing. DOE must
evaluate any potential benefits relative to any laboratory upgrades
that would be needed to achieve acceptably accurate and repeatable
results across the industry, and the impact of changing the time
required to run a cyclic test. DOE seeks data and information that
would aid efforts to quantify the relative performance impact and
associated expense of laboratory upgrades in combination with
achievable measurement uncertainty. Until more is known about the
impact of changing from the long-standing dry-coil tests to a wet-coil
cyclic test, DOE has tentatively decided not to modify this test
procedure to convert to wet-coil cyclic testing.
6. Inverter-Driven Compressors
Mitsubishi Electric and Electronics USA, Inc. (MEUS) commented that
new systems incorporating inverter-driven compressor technology require
a modification to the test procedure. (MEUS, No. 13 at p. 19)
Since 1988, the DOE test procedure has covered air conditioners and
heat pumps with variable-speed compressors, single indoor units, and
single outdoor units. The October 2007 final rule extended coverage to
variable-speed multi-split systems. 72 FR 59906. Before DOE can offer a
more substantive evaluation of the comment, DOE will need specific
examples, including laboratory data, of how the test procedure fails to
capture the performance characteristics of an air conditioner or heat
pump that uses ``new inverter-driven compressor technology.''
7. Addition of Calculation for Sensible Heat Ratio
The Joint Comment contended that the latent heat removal capability
of CAC equipment should be measured under typical operating conditions,
as opposed to high temperature conditions, and should be certified for
all models sold in hot and humid climates. (Joint Comment, No. 25 at p.
4) FSEC expressed similar views and suggested that the latent heat
ratio should be measured under different test conditions for single
speed and multi-speed equipment. (FSEC, No. 31 at p. 2) Ice Energy
suggested that the dehumidification capability of CAC equipment under
hot and humid conditions be included in the standard, and any regional
standard for the Southeast region should address this issue. (Ice
Energy, No. 33 at p. 3) On the other hand, the Edison Electric
Institute (EEI) wants dehumidification capability to be included in the
standards for all regions. (EEI, No. 20 at p. 4) SCS stated that for
hot and humid climates, a higher dehumidification capacity should be
incorporated in the standard. (SCS, No. 13 at p. 42) SCS also stated
that any regional air conditioning standard should provide for minimum
dehumidification performance that should be measured at normal
operating conditions and not at a higher temperature like 95 [deg]F.
(SCS, No. 39 at p. 1) The Joint Utilities Comment stated that DOE
should require that all units be certified and rated for SHR at 82
[deg]F ambient db temperature. (Joint Comment, No. 30 at pp. 1, 21)
Proctor stated that the rating for humid climates should include
information about what portion of the capacity is latent. (Proctor, No.
38 at p. 2)
DOE proposes including the calculation for the SHR within the
revised DOE test procedure. (10 CFR part 430, subpart B, appendix M,
revised section 3.3c and proposed section 4.5) The Federal Trade
Commission (FTC) could then consider incorporating this information in
labels for these products.
8. Regional Rating Procedure
DOE received some comments that were supportive and others that
were neutral on the development of regional ratings. The Joint Comment
noted that DOE already applies regional rating methods in the current
test procedure for residential central air conditioners and heat pumps.
(Joint Comment, No. 25 at pp. 3-4) It further noted that adoption of
regional rating methods might allow DOE to set standards of comparable
stringency, but using different rating conditions. (Joint Comment, No.
25 at p. 8) Ice Energy stated that the test protocol should be
comprehensive and should span outdoor ambient conditions over the
complete range of expected operating conditions. (Ice Energy, No. 33 at
p. 3) FSEC stated that DOE should develop new cooling season bin
temperature profiles using 2008 typical meteorological year (TMY) data
from the National Renewable Energy Laboratory (NREL). (FSEC, No. 31 at
pp. 3-4) The National Rural Electric Cooperative Association (NRECA)
commented that DOE should evaluate whether its test procedures account
for the vast differences in ambient humidity levels in different
regions. The air conditioner and heat pump standards should also take
into account the effects of humidity on different regional standards.
(NRECA, No. 35 at p. 1)
A second Joint Comment (Joint Comment 2) from the National
Resources Defense Council, National Consumer Law Center, Inc., and
Enterprise stated that DOE should strengthen the SEER test procedure to
provide a more robust measure of actual performance in varying
conditions in different regions. (Joint Comment 2, No. 36 at p. 2) PG&E
noted that DOE needs to reevaluate test procedures to determine the
performance of this equipment in the various climate zones. (PG&E, No.
13 at p. 116) EEI suggested
[[Page 31230]]
that the test procedure be updated to account for ambient conditions in
hot-dry and hot-humid climates. (EEI, No. 20 at p. 3) Proctor commented
that the temperature bins used for the rating calculation are not
representative of the hotter portions of the United States and provided
data representative of specific hot climates. Proctor also commented
that the ratings for dry climates should be based only on the sensible
capacities measured in the test, and suggested that the sensible
capacities and latent capacities, as well as the appropriate watt
draws, be measured in the existing 115 [deg]F test. Further, the
results of that test should be used in conjunction with any
intermediate tests to establish the relationship between the energy
efficiency ratio (EER) and outdoor temperature. Proctor also suggested
that in defining regions, DOE start with examination of the existing
DOE climate map (currently used in the DOE Building Energy Codes
Program), which defines dry and humid regions of the United States.
(Proctor, No. 38 at pp. 1, 2) SCS also commented that measuring
performance at 115 [deg]F would allow the design of temperature bin
profiles that better reflect the actual climate of the desert
Southwest. SCS supports the concept of a regional rating that reflects
actual weather conditions, stating that for a ``hot-dry'' regional
standard, setting the performance rating at 115 [deg]F would be of
great value to consumers and would not put an unreasonable burden on
manufacturers. (SCS, No. 39 at p. 2) SCS stated, however, that it is
neutral at this time on whether a hot-humid regional standard should be
established, due to uncertainties about changes in test procedures,
future design options manufacturers could use to reach higher
efficiency, of the ability of local jurisdictions to limit use of
equipment with poor dehumidification performance, and changes in
consumer repair versus replacement or substitute behavior due to higher
standards. (SCS, No. 39 at pp. 2, 3, 4)
Regarding the comments that favor region-specific cooling mode
performance evaluations, DOE proposes changes that will allow the
calculation of a region-specific SEER. (10 CFR 430, subpart B, appendix
M, proposed section 2.2e and revised sections 3.2.1, 3.2.2.1, 3.2.3,
and 3.2.4) The calculation parameters that permit this proposed region-
specific SEER are the fractional bin hour distribution and the outdoor
design temperature. DOE proposes modifying the indoor wet bulb
temperature as part of additional required and optional testing. (10
CFR part 430, subpart B, appendix M, revised sections 3.2.1 (table 3A),
3.2.2.1 (table 4A), and 3.2.2 (table 5A)) These test procedure proposed
changes will complement efforts to evaluate the merit of a regional
standard for a cooling-dominated region with dry climate. DOE believes
that similar changes are not needed for cooling-dominated States with
humid climates. The current indoor side entering wet-bulb test
condition of 67 [deg]F, fractional bin-hour distribution, and outdoor
design temperature sufficiently represent the conditions for a humid
climate. Calculation of the SHR from such existing tests, however, is
proposed in today's NOPR to quantify the product's dehumidification
capabilities.
Section 306(a) of EISA amended section 325(o) of EPCA to require
that regions defined for the purposes of regional standards are
required to be composed of contiguous States. (42 U.S.C.
6295(o)(6)(C)(i)) In addition, individual States shall be placed only
into a single region. (42 U.S.C. 6295(o)(6)(C)(iii)) DOE is proposing
an alternative regional efficiency metric, a region-specific SEER
(SEER-HD) for a four-State region consisting of Arizona, California,
Nevada, and New Mexico. The proposed SEER-HD reflects equipment
performance in this region.
DOE does not endorse the recommendation to add testing at 115
[deg]F outdoor temperature. A linear fit of data collected from the
cooling mode tests at 82 [deg]F and 95 [deg]F can sufficiently estimate
capacity and power consumption at 105 [deg]F, 110 [deg]F, and even 115
[deg]F. Interested parties have not provided, and DOE has not
identified, examples where a SEER rating or the proposed region-
specific SEER was statistically different as a result of being
evaluated based on laboratory data at 115 [deg]F as opposed to 95
[deg]F.
In other related comments, ACEEE asked how DOE would capture and
evaluate the efficiency of continuous ventilation for regional
standards, as it is provided and used in a reasonable fraction of
houses. (ACEEE, No. 13 at p. 138) Sempra indicated that the test
protocols should be able to accommodate technologies other than air-
cooled expansion unitary equipment. Sempra also commented that DOE
should consider using the time value of energy in the new test
procedures. (Sempra, No. 13 at p. 121) WCEC contended that certain
changes in the test procedures could result in energy savings: (1) A
24-hour test protocol that can measure and characterize the energy and
peak demand implications of control and thermal storage technologies;
(2) a test protocol that provides different types of evaporative-cooled
equipment with directly comparable SEER ratings; and (3) a test
protocol that seriously addresses installation and performance-
longevity issues. (WCEC, No. 41 at p. 2) ACEEE stated that DOE could
use an alternative rating route to deal with enhanced dehumidification
products. (ACEEE, No. 13 at p. 154)
Regarding installation and performance longevity issues, DOE does
not have the authority to implement new performance metrics for
characterizing such features at this time. Presently, the only metrics
available for representing performance are SEER and HSPF. These are
seasonal performance metrics and are not useful for characterizing
installation issues, performance longevity, or quantifying performance
at peak demand.
DOE notes that while there may be value in defining a test
procedure that can provide consistent, comparable rating of alternative
cooling systems, including evaporative cooling technologies and
technologies incorporating thermal storage, such expansion of the test
procedure is beyond the scope of this rulemaking. This rulemaking seeks
to address changes mandated in EISA and otherwise improve upon coverage
of comparatively conventional air conditioners and heat pumps.
Determining additions and changes needed to allow testing and rating of
thermal storage technologies, for example, is a formidable task, one
that requires significant investigation. Such an investigation is
difficult to pursue until such equipment is readily available as a
commercial product.
9. Address Testing Inconsistencies for Ductless Mini- and Multi-Splits
Two interested parties commented that there are inconsistencies
within the central air conditioning test procedure for mini- and multi-
split systems. (MEUS, No. 13 at p. 21 and 22; Daikin, No. 28 at p. 6)
The proposed changes to items 1 through 3 of Appendix M, cover test
procedure changes addressing inconsistencies for ductless mini- and
multi-splits. In response to the comments, DOE proposes three changes
to the test procedure to address these inconsistencies: (1) Modify the
definition of tested combination for multi-split systems. DOE proposes
to use the term ``nominal cooling capacity'' within the definition of
``tested combination'' (proposed change to 10 CFR 430, subpart A,
section 430.2, Definitions, Tested Combination) and to simplify the
requirements for multi-split systems with cooling capacities of
[[Page 31231]]
24,000 Btu/h or lower; (2) add an alternative minimum static pressure
requirement for use when testing ducted multi-split systems (10 CFR
430, subpart B, appendix M, proposed table 2); (3) clarify within the
test procedure that optional testing may be conducted without
forfeiting the use of default values (10 CFR 430, subpart B, appendix
M, proposed section 3.6.4d).
10. Standby Power Consumption and Measurement
Interested parties submitted comments refuting the need to revise
the test procedure to consider standby power consumption when EISA does
not explicitly call for its revision, and noting that standby power
consumption is already addressed in the standard. (AHRI, No. 13 at p.
105; Sempra, No. 13 at p. 133; Energy Solutions, No. 13 at p. 108;
Emerson, No. 13 at p. 111) Some contended that the test procedure's
accounting of standby power consumption is adequate and does not
require modification. (Trane, No. 16 at p. 3; Carrier Corporation
(Carrier), No. 18 at p. 1; ASAP, No. 13 at p. 114; MEUS, No. 19 at p.
1; AHRI, No. 24 at p. 2). Trane and Carrier representatives both stated
that the standby power consumption calculation is already captured in
the degradation coefficient, CD calculation. (Trane, No. 16
at p. 3; Carrier, No. 18 at p. 1)
SEER reflects all modes of climate control energy consumption that
occur during the cooling season, as HSPF does for the heating season.
SEER does not capture the time that an air conditioner could be
energized but idle during the non-cooling season. Similarly, the
current test procedure does not capture energy consumed by a heat pump
during the non-cooling and non-heating seasons. These are the shoulder
seasons that occur between the cooling and heating seasons and can be
quantified by converting the cooling and heating load hours for any
location into actual hours. In each case, the actual site or region-
specific cooling and heating season hours always sum to less than
8,760. To calculate annual energy consumption or annual operating cost,
all 8,760 hours of the year must be accounted for. Until now, these
annual quantities have been based on energy consumption of fewer than
8,760 hours. The DOE test procedure must account for the idle mode
energy consumption of the air conditioner and heat pump during the
shoulder seasons and the idle mode energy consumption of an air
conditioner during the heating season.
Several interested parties commented that although the current
standard does address standby power consumption, standby and off mode
power need to be better defined. (Joint Comment, No. 25 at p. 6; CFM
Equipment Distributors, No. 13 at p. 129; Lennox, No. 13 at pp. 113,
134; Carrier, No. 13 at p. 113; the Unico System, No. 13 at p. 129;
Trane, No. 13 at pp. 130, 131, 136; PG&E, No. 13 at pp. 132, 137;
General Electric, No. 13 at p. 135; EEI, No. 20 at p. 5; ASAP, No. 13
at p. 132)
DOE concurs with the commenters. The definitions of standby and off
mode as provided in EPCA section 325(gg) were amended by section 310 of
EISA and are purposely generic so that they can apply to all covered
products. (42 U.S.C. 6295(gg)(1)(A)(iii), (42 U.S.C.
6295(gg)(1)(A)(ii), respectively) EPCA section 325 allows DOE to
redefine these definitions, including off mode, as part of this
rulemaking. (42 U.S.C. 6295(gg)(1)(B)) The proposed definition is as
follows:
The term ``off mode'' means:
(1) For air conditioners, all times during the non-cooling
season of an air conditioner. This mode includes the ``shoulder
seasons'' between the cooling and heating seasons when the unit
provides no cooling to the building and the entire heating season,
when the unit is idle. The air conditioner is assumed to be
connected to its main power source at all times during the off mode;
and
(2) For heat pumps, all times during the non-cooling and non-
heating seasons of a heat pump. This mode includes the ``shoulder
seasons'' between the cooling and heating seasons when the unit
provides neither heating nor cooling to the building. The heat pump
is assumed to be connected to its main power source at all times
during the off mode.
DOE requests comments on this proposed definition (10 CFR,
subpart B, appendix M, proposed section 1.48).
B. Summary of the Test Procedure Revisions
Today's proposed rule contains the following proposed changes to
the test procedure in 10 CFR part 430, subpart B, appendix M.
1. Modify the Definition of ``Tested Combination'' for Residential
Multi-Split Systems
DOE procedures require testing a complete system, not just its
components. For multi-split systems, each model of outdoor unit may be
installed with numerous indoor unit combinations. Systems may differ in
the number of connected indoor units, their physical type (e.g., wall-
mounted versus ceiling cassette, ducted versus non-ducted), and
individual capacities.
As part of the October 2007 final rule, multi-split units with
rated cooling capacities less than 65,000 Btu/h were newly covered in
the DOE central air conditioner and heat pump test procedure. As part
of this coverage, manufacturers are required to test each model of a
multi-split outdoor unit with at least one set of non-ducted (and at
least one set of ducted, if applicable) indoor units. DOE placed limits
on the set of indoor units selected to meet this testing requirement
for each multi-split outdoor unit. These limits are prescribed in 10
CFR 430.2 definition for ``tested combination.'' During the previous
test procedure rulemaking, DOE refined the ``tested combination''
definition from the version published in the July 20, 2006 NOPR to the
version published in the October 2007 final rule. After implementing
the new test procedures, manufacturers of multi-split systems requested
additional changes.
In its May 27, 2008 letter to DOE, the Air-Conditioning, Heating,
and Refrigeration Institute (AHRI) recommended three changes to the
``tested combination'' definition. First, AHRI supported changing
specific references to ``capacity'' and ``nominal capacity'' to
``nominal cooling capacity.'' AHRI argued that ``this correction is
necessary to clarify that the test procedures are based on the cooling
(rather than heating) capacity of the equipment and to recognize that
the nominal means the cooling capacity of the system at 95 [deg]F
ambient, 80/67 [deg]F indoor conditions.''
Second, AHRI requested that the requirement preventing the use of
an indoor unit having a nominal cooling capacity that exceeds 50
percent of the nominal cooling capacity of the outdoor unit be waived
for outdoor units with a nominal cooling capacity of 24,000 Btu/h or
lower. AHRI noted that it is not always possible to meet this
requirement, especially because of the additional DOE requirement that
the nominal cooling capacities of the indoor units, when summed, must
fall between 95 and 105 percent of the outdoor unit's nominal capacity.
AHRI gave the example of an outdoor unit rated for 20,000 Btu/h that is
designed to be used with indoor units having nominal capacities of
9,000 and 12,000 Btu/h. In this case, the only combination that meets
the 95 to 105 percent indoor-outdoor capacity criteria is where two
indoor units are used, one having a capacity of 12,000 Btu/h and one
having a capacity of 9,000 Btu/h. The current definition for tested
combination, however, does not allow this combination because the
12,000 Btu/h indoor unit exceeds the 50 percent limit on the capacity
of the indoor unit to the capacity of the outdoor unit.
AHRI's final suggested change pertains to multi-split systems with
nominal capacities greater than 150,000
[[Page 31232]]
Btu/h. The current limit of five indoor units to complete the system is
often insufficient for the required 95 to 105 percent match with the
outdoor unit. As AHRI stated in its letter, AHRI recognizes that ``this
capacity is beyond the cooling capacity limit of 65,000 Btu/h * * * but
many manufacturers have been granted waivers in which this tested
combination definition applies.''
DOE concurs with two of the three changes AHRI requested. DOE
proposes to adopt the wording ``nominal cooling capacity'' within the
definition of ``tested combination.'' (10 CFR 430.2) DOE will also
waive the restriction that no indoor unit shall have a nominal cooling
capacity exceeding 50 percent of the outdoor unit's nominal cooling
capacity for multi-split systems having a nominal cooling capacity of
24,000 Btu/h or less. (10 CFR 430.2(2)(iii)) Additionally, DOE proposes
to modify the definition for ``tested combination'' to indicate that
the allowed range for the indoor to outdoor capacity percentages is 95
to 105 percent, inclusive. (10 CFR 430.2(2)(ii) The current wording
calls for the match to be ``between'' (i.e., not ``including'') these
bounds. Especially with the above switch to using ``nominal cooling
capacity,'' specifying a set of indoor units that yields an indoor to
outdoor capacity percentage of either 95 or 105 percent increases
should be allowed.
With regard to the third change requested by AHRI, DOE will not
establish a different limit on the number of indoor units used when
testing multi-split systems with nominal capacities greater than
150,000 Btu/h because these systems are outside the scope of this
residential test procedure rulemaking.
2. Add Alternative Minimum External Static Pressure Requirements for
Testing Ducted Multi-Split Systems
Since the inception of DOE central air conditioner and heat pump
test procedures, the majority of covered products have used a single
indoor unit designed to work with a multi-branch duct system to
distribute air within a building. This system imposes an additional
load (quantified as external static pressure (ESP)) on the indoor
blower as it distributes and returns air to and from the conditioned
space.
When a system is laboratory tested according to the DOE test
procedure, airflow resistance imposed on the blower by external
attachments is measured when the indoor blower and the laboratory's
airflow measurement apparatus maintain the manufacturer-specified air
volume rate. To constitute a valid setup for ducted indoor units, this
external resistance measurement must equal or exceed a value--the
minimum ESP expressed in wc--specified in the DOE test procedure. The
minimum ESP value depends on one of three minimum rated cooling
capacities of the tested system: 0.1 in wc for units up to 28,800 Btu/
h, 0.15 in wc for units between 29,000 and 42,500 Btu/h, and 0.2 in wc
for units 43,000 Btu/h and above. These minimums were adopted from
industry standards that were in place when the test procedure was
developed and that have remained unchanged.
The majority of multi-split systems use non-ducted indoor units. In
laboratory testing following the DOE test procedure, these free
discharge units are tested with an ESP of 0 in wc. Multi-splits are
also offered where one or more of the indoor units is ducted. Compared
with conventional ducted units, indoor unit ducting for multi-splits is
shorter and used on the return or supply, or both.
In its May 27, 2008 letter, AHRI stated that ``many ductless
manufacturers have `ducted' indoor units that are intended for a
minimum (less than a few feet) or no duct runs and as a result have a
rated external static pressure capability of less than 0.1 ESP and
usually around 0.02 ESP.'' AHRI recommended a mechanism and language
for addressing this issue in the DOE test procedure. Specifically, AHRI
suggested that DOE amend its test procedure by adding the following
footnote to Table 2 of Appendix M (shown as Table III.1 below): ``If
the manufacturer's rated external static pressure is less than 0.10 in
wc (25 Pascals (Pa)), then the indoor unit should be tested at that
rated external static pressure.''
Table III.1--Minimum External Static Pressure for Ducted Systems Tested With an Indoor Fan Installed *
----------------------------------------------------------------------------------------------------------------
Minimum External Resistance [dagger] in wc
-------------------------------------------------
Rated cooling or heating capacity ** Btu/h SDHV Systems
[dagger][dagger] All other systems
----------------------------------------------------------------------------------------------------------------
<= 28,800..................................................... 1.10 0.10
29,000 to 42,500.............................................. 1.15 0.15
43,000 >=..................................................... 1.20 0.20
----------------------------------------------------------------------------------------------------------------
* Source: Table 2 from 10 CFR 430, modified for today's NOPR.
** For air conditioners and heat pumps, this is the value the manufacturer cites in published literature for the
unit's capacity when operated at the A or A2 test conditions. For heating-only heat pumps, this is the value
the manufacturer cites in published literature for the unit's capacity when operated at the H1 or H12 test
conditions.
[dagger] For ducted units tested without an air filter installed, increase the applicable tabular value by 0.08
in wc.
[dagger][dagger] See definition 1.35 to determine if equipment qualifies as an SDHV system. If a closed-loop air-
enthalpy test apparatus is used on the indoor side, limit the resistance to airflow on the inlet side of the
indoor blower coil to a maximum of 0.1 in wc. Impose the balance of airflow resistance on the outlet side of
the indoor blower.
In the field, ducted multi-split systems are installed using lower
pressure duct systems than are typically used to install a conventional
ducted central air conditioner or heat pump. Consequently, DOE
recognizes that ducted multi-split systems should not be subject to the
same minimum ESP requirements as conventional central systems.
Specifying appropriate minimums, however, is difficult.
One problem with the language AHRI proposed is that a manufacturer
could choose an unrealistically low value for the rated external static
pressure. Because this would likely be a secondary concern (if not
completely overlooked) when a system is selected, the manufacturer
lacks an incentive to choose a representative rating. Additionally,
because the manufacturer is not allowed to select the minimum external
static pressure when testing a conventional unit, allowing the
manufacturer to select the minimum when testing a ducted multi-split
systems would create an unjustifiable inconsistency.
DOE considered three related factors before formulating an
alternative to the AHRI proposal. First, the following approach appears
in the Draft International Standard (DIS) ballot of
[[Page 31233]]
ISO Standard 15402, ``Multi-Split System Air Conditioners and Air-to-
Air Heat Pumps: Testing and Rating for Performance.''
This ESP shall be greater than the minimum value given in Table
1 but not greater than 80% of the maximum external static pressure
specified by the manufacturer. * * * If the maximum ESP of the unit
is lower than the minimum ESP given in Table 1, then the airflow
rate is lowered to achieve an ESP equal to 80% of the maximum ESP of
the manufacturer. In case this ESP is lower than 25 Pa, the unit can
be considered as a free delivery unit.
Where the ISO approach ties the tested minimum external static
pressure to a manufacturer published maximum value while approximating
the smallest indoor units as non-ducted, the two other inputs suggest
that the current test procedure requirements are manageable.
Specifically, manufacturers of single indoor blower coil units that use
short ducts --sometimes referred to as ``furred down or ceiling mounted
air handling units''--have never requested that DOE lower the minimum
static pressure requirements. Further, DOE has received no evidence
showing that any multi-split indoor unit could not achieve the
applicable DOE minimum external static pressure when delivering its air
volume rate.
DOE proposes an approach that does not require publication of the
maximum external static pressure. For the systems meeting the
definition of ``multiple-split air conditioner and heat pumps'' in the
test procedure (10 CFR part 430, subpart B, appendix M, section 1.30),
DOE proposes a new set of minimum external static pressures. The
proposed minimums will be listed in table 2 of appendix M of the test
procedure, along with the current values for SDHV and all other
systems. The proposed values are 0.03 in wc for units through 28,800
Btu/h, 0.05 in wc for units between 29,000 and 42,500 Btu/h, and 0.07
in wc for units 43,000 Btu/h and above. The proposed minimums seek to
capture the relative differences between a conventional central ducted
system and one with the shorter ducts of a typical multi-split system
installation. Because ducts add resistance, DOE will not adopt the ISO
approach of testing the smallest systems at zero static pressure. For
multi-split systems, the applicable minimum external static pressure
will be assigned based on the nominal/rated cooling capacity of the
outdoor unit. A static pressure equal to or higher that this minimum
will be achieved in each outlet duct upstream of the point where they
connect to the common plenum that leads to the test room's airflow
measuring apparatus. In addition to ducted multi-split systems, DOE
proposes applying this new set of minimum external static pressures to
ducted mini-splits or 1-to-1 systems where the indoor air handler is a
ducted furred down/ceiling-mounted unit. To limit the 1-to-1 products
that qualify for the lower minimum static pressures, the single indoor
unit must not exceed specified dimensions (e.g., no more than 11 in
high and less than 24 in deep), the indoor unit must use a single slab
coil that is perpendicular to the flow stream, and the system's rated
capacity must not exceed 39,000 Btu/h.
DOE requests comment from interested parties on the proposed lower
external static pressure levels for certain equipment as described
above and on the proposed language for ensuring that these levels are
used only for testing the intended products: ducted multi-splits,
ducted mini-splits, and ducted furred down/ceiling mounted one-to-one
units.
3. Clarify That Optional Tests May Be Conducted Without Forfeiting Use
of the Default Value(s)
In the DOE test procedure, the manufacturer has two options for
obtaining a required parameter within the SEER or HSPF calculation
algorithm: (1) Run one or two additional tests to obtain the necessary
data; or (2) use a ``default value,'' which may be fixed or derived
from an approximating equation. For certain frost accumulation tests,
the DOE test procedure gives the manufacturer the option of conducting
the test or using default equations to determine the pump's power
consumption and space heating capacity at 35 [deg]F outdoor temperature
and at the designated compressor capacity. The test procedure is not
clear whether defaults are forfeited if the manufacturer conducts the
optional laboratory test. This matter is clarified here.
As stated in the DOE test procedure (10 CFR part 430, subpart B,
appendix M, sections 3.2.1, 3.2.2.1, and 3.2.3), the manufacturer may
run the optional test(s) for determining a cyclic degradation
coefficient but still use the default if it is lower than the tested
value. DOE proposes allowing manufacturers to run the optional test(s),
with the understanding that they can still use the default value if it
is more favorable for optional frost accumulation tests. Specifically,
the manufacturer may use the power consumption and heating capacity
values derived from conducting the optional frost accumulation test or
the values calculated using the default equations, whichever set
contributes to a higher Region IV HSPF based on the minimum design
heating requirement.
4. Allow a Wider Tolerance on Air Volume Rate To Yield More Repeatable
Laboratory Setups
A goal of the DOE test procedure is specifying a consistent
equipment configuration to obtain repeatable laboratory test results.
For example, the indoor blower of a particular model should be
consistently set to the same blower speed setting for a given test
configuration. More generally, the blower speed setting should be the
same when performing the same test on all units of the same equipment
model.
As part of the equipment setup requirements for most blower-coil
units, the testing entity (e.g., manufacturer or third party) turns on
both the indoor unit blower and the test facility exhaust fan. The
exhaust fan and/or an airflow damper are adjusted until the
manufacturer-specified indoor air volume rate is obtained. If the
measured external static pressure equals or exceeds the test procedure
specified minimum value, testing proceeds without adjustment to the
indoor unit configuration.
If the measured external static pressure is below the DOE minimum,
the setup requires additional effort. The first step is to reduce the
air volume rate until the measured external static pressure equals the
DOE minimum. As currently specified in the test procedure, if the
measured external static pressure does not equal the DOE minimum by the
time the air volume rate has been reduced to 95 percent of the rated
value, then the indoor unit blower is turned off, and the indoor unit's
setup is adjusted to the next highest speed setting.
The above setup procedure will typically result in the indoor
blower-coil set to the same speed setting for testing all units of the
same model. In essence, the procedure handles the inherent variability
in the external static pressure and air volume rate produced and
measured for multiple equipment setups. This variability is due to
manufacturing tolerances and lab measurement uncertainties.
In its May 27, 2008 letter, AHRI requested that the 5-percent
tolerance on air volume rate be increased to 10 percent. In addition,
AHRI recommended that the language for the indoor blower coil setup
procedure be refined to recognize that some incremental setting changes
may affect more than fan speed. AHRI gives the example that ``some
speed tap settings may equate to a specific duration of fan delay
whereas other settings may translate to no fan delay.'' To address this
issue, AHRI recommends that DOE
[[Page 31234]]
make incremental changes to the indoor blower setting among settings
that provide similar operating features.
AHRI offers two reasons in its May 27, 2008 letter for supporting a
greater tolerance on air volume rate during the initial setup process:
The expanding use of constant torque motors for central air
conditioners and heat pumps blower coils, and the effect of barometric
pressure. AHRI states that ``for a given speed tap, the air volume rate
achieved using a constant torque motor is comparatively more variable;
also the change in power draw as a function of an incremental change in
the speed tap is also comparatively greater so the impact on efficiency
will be more pronounced.'' Barometric pressure affects air density and
the water vapor content for a given db/wb combination. Thus, barometric
pressure affects capacity through both the air volume rate and the
enthalpy change of the air. As referenced in the AHRI letter,
barometric pressure effects are especially important, as most
manufacturers' in-house testing is conducted at a lower elevation and
typically higher barometric pressure than at the industry's primary
independent certification testing facility.
In response to AHRI's May 27, 2008 letter, DOE proposes to increase
the tolerance on air volume rate from 5 to 10 percent. In addition, DOE
proposes to adopt AHRI's recommendation to refine the indoor blower
coil setup procedure to recognize that some incremental changes to the
setting may affect more than the fan speed. DOE used computer modeling
and laboratory data to determine that a 10 percent difference in air
volume rate will cause total capacity to decrease between 1.3 to 2
percent, while having the total system power consumption fall between 1
to 1.8 percent for a minimally compliant system. Because capacity and
power impacts are similar, the EER and SEER impacts are less. SEER is
projected to decrease between 0.2 and 0.4 percent. Thus, this proposed
change has the potential to affect the measured capacity such that it
may make it more difficult to meet the industry certification program's
95 percent capacity tolerance. The impact on the DOE regulated
descriptor of SEER, however, is well within the measurement
uncertainty, even for the limiting case of a 10-percent departure.
DOE requests data and comments from interested parties on the
impact of the change from 5 to 10 percent tolerance on air volume rate.
5. Change the Magnitude of the Test Operating Tolerance Specified for
the External Resistance to Airflow and the Nozzle Pressure Drop
The DOE test procedure specifies both test operating and condition
tolerances. Test operating tolerances indicate the maximum range that a
parameter may vary during the data collection interval. For any given
test, operating tolerances are specified for a few different
parameters. For each parameter, the difference between the highest and
lowest instantaneous measurement for the data collection interval must
not exceed the specified operating tolerance in order to constitute a
valid test.
The test operating tolerance for external resistance to airflow is
0.05 in wc. The test operating tolerance for nozzle pressure drop is
2.0 percent. Both tolerances, which apply for all cooling and heating
tests were included in industry standards (e.g., ASHRAE Standard 37)
that pre-date the first publication of the DOE central air conditioner
and heat pump test procedure. The DOE test procedure adopted the two
tolerances at its inception and has not changed it. For current
industry standards, the tolerances appear in the 2009 version of ASHRAE
Standard 37.
The two test operating tolerances are often exceeded when an
electronic pressure transducer is used to measure differential pressure
instantaneously. The likelihood of exceeding the tolerance increases
with higher sampling rates and when testing indoor blowers whose
controls actively regulate operation of the blower's motor. One example
is a blower with a variable-speed motor designed to maintain the air
volume rate regardless of the airflow resistance. In contrast, these
test operating tolerances are usually satisfied if the differential
pressures are measured using liquid manometers. The fluid provides
mechanical damping that tends to stabilize readings.
DOE proposes to loosen the existing tolerances from 0.05 to 0.12 in
wc for the test operating tolerance assigned to the external resistance
to airflow and from 2.0 percent to 8.0 percent for the nozzle pressure
drop tolerance because the pressure fluctuations are real (10 CFR,
subpart B, appendix M, revised tables 7, 8, 13, 14 and 15). The
proposed changes in the magnitude of the tolerances are based on
limited data obtained from laboratory testing of a variable-speed,
constant air-volume-rate blower using electronic pressure transducers
with a 5-second sampling rate. This data indicated that the current
tolerances could rarely be achieved when using and electronic pressure
transducer instead of a liquid manometer. Matching or remaining within
the proposed tolerances, by comparison, was far more achievable.
At this stage, DOE proposes amended values for the two tolerances
rather than their complete elimination because they still help assure
data is taken during a period of relatively steady operation.
Additional steps, however, may be warranted. For example, a prescribed
algorithm for identifying outliers and/or establishing minimum
intervals over which all instantaneous measurements are averaged (e.g.,
minutely averages) may also be needed to strike the necessary balance
between defining test tolerances that promote repeatable test results
while not extending test times. Another option may be to introduce a
mechanical means for damping the high frequency pressure fluctuations
that are fed to the electronic pressure transducer to mimic a liquid
manometer. Such damping would be acceptable because the measurements
would still reveal whether the flow was steady or trending higher or
lower.
DOE seeks comments from interested parties about the proposal to
increase the test operating tolerance for the external resistance to
airflow from 0.05 to 0.12 in wc and increase the test operating
tolerance for the nozzle pressure drop from 2.0 percent to 8.0 percent.
In addition, comments on alternative or additional steps to assure the
capacity and electrical power data are collected over a 30-minute
period of consistent operation are encouraged.
6. Modify Third-Party Testing Requirements When Charging the Test Unit
DOE proposes to revise section 2.2.5, ``Additional refrigerant
charging requirements,'' of the test procedure. Most of the proposed
revisions originate from the requirements listed in section 9.8.1.1 of
the 2008 ARI General Operations Manual for AHRI Certification Programs.
DOE adopted the current language in section 2.2.5 of the DOE test
procedure in the October 2005 final rule. The section 2.2.5 text covers
details not addressed in the test procedure prior to the October 2005
rule, such as charging instructions that differ for field installations
versus laboratory testing and the procedure for manufacturers and
third-party testing entities to resolve questions on charging a
particular system. In the months following publication of that rule,
AHRI members reconsidered refrigerant charging, mainly within the
context of implementing its third-party certification program. During
the August
[[Page 31235]]
23, 2006 public meeting, Rheem Manufacturing Company shared AHRI's view
of key shortcomings. These include provisions in section 2.2.5
regarding available options when a unit is charged and tested by a
third party. These provisions failed to disallow charge manipulation
during the testing process (e.g., different charging criteria for the
cooling mode tests versus the heating mode tests).
AHRI provided language from the current version of the AHRI General
Operations Manual so that all or part of it may be considered for
incorporation into the DOE test procedure. The specific AHRI text of
interest is as follows:
9.8.1.1 Test Sample Refrigerant Charge. All test samples will be
charged in accordance with the following instructions and those
provided in the manufacturers' Installation and Operational (I/O)
Manuals.
Determine refrigerant charge at the Standard Rating Condition in
accordance with instructions from I/O Manual. For a given specified
range for superheat, sub-cooling, or refrigerant pressure, the
average of the range shall be used to determine the refrigerant
charge. If multiple instructions are given, the manufacturer will be
asked to sign off on the preferred method.
The testing laboratory will then add or subtract the correct
amount of refrigerant to achieve the pre-determined superheat, sub-
cooling, or refrigerant pressure. This single charge will then be
used to conduct all cooling cycle and heating cycle tests.
Once the correct refrigerant charge is determined, the test will
run until completion without interruption.
DOE proposes to adopt selected elements of the above AHRI
procedures. (10 CFR part 430, subpart B, appendix M, section 2.2.5) The
proposed changes promote consistency with current AHRI certification
practices, including explicitly disallowing charge manipulation once
the initial charging procedure is completed, while differing on the
approach of addressing cases where a manufacturer either provides no
instructions or provides more than one set of charging instructions. In
particular, DOE chose not to implement a ``sign off'' option as AHRI
uses because the proposed approach of specifically addressing the setup
procedure in these two special cases is effective and less burdensome.
7. Clarify Unit Testing Installation Instruction and Address
Manufacturer and Third-Party Testing Laboratory Interactions
DOE proposes to add language to section 2.2 of the test procedure.
The additions seek to clarify installation instructions and, when
third-party testing is conducted, to clarify that interaction with the
manufacturer is allowed.
The AHRI Certification Program and the DOE test procedure focus on
different aspects of the rating process. The AHRI program conducts
verification testing of full production of randomly sampled units taken
from the manufacturer's inventory. By comparison, the DOE test
procedure is typically conducted before a new model of air conditioner
or heat pump is introduced into the market. Therefore, testing is
usually performed on first production or pre-production units, each of
which meets the requirement in 10 CFR 430.24 that testing be done on
``units which are production units, or are representative of production
units.'' When testing pre-production units, the installation
instructions are not packaged with the unit or perhaps not even
finalized. DOE proposes adding language on how to handle such cases.
(appendix M, revised section 2.2) Some of the restrictions on
interactions between third-party testing laboratories and
manufacturers, imposed as part of the AHRI Certification Program, do
not apply to the DOE test procedure. One example is AHRI's General
Operations Manual requirement that ``only laboratory personnel shall
install test units.'' The policy is useful to AHRI because
certification testing checks DOE ratings. AHRI does not want individual
manufacturers to slow the testing process or reveal information about a
competitor. On the other hand, DOE will not prohibit a manufacturer
from interacting with a third-party testing laboratory if the latter is
contracted to perform work similar to in-house manufacturers. (10 CFR
part 430, subpart B, appendix M, revised section 2.2a) In the event of
a DOE enforcement action, DOE places no restrictions on manufacturer
involvement as long as the test unit installation and laboratory
testing are conducted in complete compliance with all other
requirements in the DOE test procedure. The highest order of these
other requirements is to install the unit according ``the
manufacturer's installation instructions,'' as stated in section 8.2 of
ASHRAE Standard 37, where the first source for those instructions is
the published literature that comes packaged with the unit.
This second issue on the allowed interactions between third-party
testing laboratory and the manufacturer was addressed in a previous
rulemaking (70 FR 59122) but only as it pertained to the specific
installation step of refrigerant charging (section 2.2.5 of the test
procedure). Because the interaction applies to the entire installation
process, DOE proposes to address the issue in section 2.2 and, as a
result, existing section 2.2.5 language on this topic is proposed for
deletion.
8. When Determining the Cyclic Degradation Coefficient CD,
Correct the Indoor-Side Temperature Sensors Used During the Cyclic Test
to Align With the Temperature Sensors Used During the Companion Steady-
State Test, If Applicable
In the DOE test procedure, the results from two optional dry-coil
cooling mode tests--one steady-state, one cyclic--provide the inputs to
calculate cooling mode cyclic degradation coefficient(s), CcD. For the
heating mode, the results from one of the required steady-state tests
plus the results from an optional cyclic test are used to calculate the
heating mode cyclic degradation coefficient, ChD. In all cases, the two
tests for calculating a cyclic degradation coefficient are conducted
consecutively, with the steady-state test conducted first.
Both the steady-state (10 CFR part 430, subpart B, appendix M,
sections 3.4 and 3.7) and cyclic (10 CFR part 430, subpart B, appendix
M, sections 3.5 and 3.8) CD tests require calculating the change in the
db temperature on the indoor side. To complete these measurements, the
laboratory test setup includes redundant sets of temperature sensors
and associated instrumentation. In many cases, one set of temperature
sensors provides the primary measurement of the change in db
temperature for all steady-state tests, while the second set provides
the same primary measurement for all transient tests, including the
cyclic CD test. Using two sets of temperature sensors allows highly
accurate measurements during the steady-state test; comparatively less
accurate but necessarily faster-responding measurements are achieved
during the transient tests. The DOE test procedure refers to ASHRAE
Standard 41.1-1986 (RA 2001) for recommendations and requirements on
making these temperature measurements.
Cyclic degradation coefficients are used to obtain a relationship
between part-load factor (PLF) and the percent on-time of the unit. PLF
is a ratio of the cyclic to the steady-state EER. The consecutive CD
tests are used to obtain one point on the PLF versus percent on-time
plot. Because the results of the consecutive CD tests define a ratio,
the preferred testing approach is to limit differences between the two
tests. Using one set of instrumentation to measure the change in the db
air temperature entering and leaving the indoor unit
[[Page 31236]]
during the steady-state CD test and a different set for the companion
cyclic CD test is a source of potential bias.
To avoid conflict, DOE may require that the same temperature
measurement instrumentation be used for both consecutive CD tests. The
Standards Project Committee revising ASHRAE Standard 116, ``Methods of
Testing for Rating Seasonal Efficiency of Unitary Air Conditioners and
Heat Pumps,'' considered this alternative but chose to make it a
recommendation, not a requirement (see clause 5.1.4 of ASHRAE Standard
116-1995R, ``Method of Testing for Rating Seasonal Efficiency of
Unitary Air Conditioners and Heat Pumps,'' First Public Review draft).
A second option is to correlate the instrumentation used for the
primary measurement of the temperature difference of the cyclic CD test
to that used for the primary measurement during the steady-state CD
test. Some industry members have implemented this correlation approach
and found that it improves repeatability.
DOE proposes to require a correlation step for testing laboratories
that use different instrumentation to measure the change in the db
temperature of the air entering and leaving the indoor unit during the
steady-state CD test versus the cyclic CD test. This correlation step
is conducted during the steady-state CD test. During the test, both
sets of instrumentation--those sensors providing the primary
measurement during the steady-state (set SS) and during the cyclic (set
CYC) tests--measure the indoor-side air db temperature difference. For
both sets of instrumentation, measurements made at equal intervals that
span 5 minutes or less determine the temperature difference. Once the
30-minute data collection period begins for the steady-state CD test,
an average temperature difference is calculated based on the sets SS
and CYC instrumentation after a minimum of 7 data samples and 6 minutes
or more. The average temperature differences are then used to calculate
the CD correlation factor, FCD:
[GRAPHIC] [TIFF OMITTED] TP02JN10.304
An updated FCD value shall be recalculated every minute or after
each data sample, whichever occurs later. In addition, each
recalculated ratio shall be based on the same number of data samples
and same elapsed time as used for the first FCD. For the example case
of a sampling rate of 1 minute or less, the first FCD shall be based on
data collected from elapsed time of 0 to 6 minutes, the second from 1
to 7 minutes, the third from 2 to 8 minutes, and so on.
Upper and lower limits are proposed for FCD to provide a uniform
basis as to how much the two temperature measurements may deviate. The
proposed allowable range of FCD is 0.94 to 1.06. Laboratories that
sample at a rate of every minute or less can evaluate the first FCD as
soon as 6 minutes after the start of the normal 30-minute data
collection period. If this first or any subsequent value of FCD is
outside the proposed application range of 0.94 to 1.06, then the
testing laboratory can make a decision to abort the test in advance of
completing the 30-minute data collection period. By comparison, if a 5-
minute sample rate is used, FCD falling within the allowed range will
remain unknown until the 30-minute data collection period is completed.
In this case, up to 24 minutes of laboratory testing time may be lost
from a longer wait to evaluate compliance.
If the value of FCD at the conclusion of the 30-minute period
(saved FCD) falls outside the range of 1.0 0.6, then the
test sequence must be terminated, and steps taken to improve the
agreement between the sets SS and CYC instrumentation. Calibration of
one or both sets of instrumentation in accordance with ASHRAE Standard
41.1 may be necessary. Once the remedial steps are complete, the
steady-state CD test shall be repeated. For cases within the accepted
range, the saved FCD shall thereafter be used during the cyclic CD test
to adjust the indoor-side temperature difference or a time-integrated
value of the same determined using the set CYC instrumentation. For
example, with respect to section 3.5 of Appendix M, the equation for
the integrated, indoor-side air temperature difference will be written
as follows:
[GRAPHIC] [TIFF OMITTED] TP02JN10.303
The value of FCD shall be used only to adjust the set CYC
temperature difference measurement from the cyclic CD test that
immediately follows the steady-state CD test that yields the
correlation factor. The FCD determined and applied for one set of
consecutive CD tests shall not be used to adjust the set CYC
temperature difference measured during a second cyclic CD test or
during a frost accumulation test.
DOE proposes to decrease the minimum sampling rate of the db
temperature difference from the current value of every 10 minutes to
every 5 minutes to obtain a more representative value of FCD. As an
extension of this modification, DOE proposes to change the long-
standing minimum sampling rate for all steady-state tests from 10 to 5
minutes. The 10-minute sampling interval rate allows time for some
measurements to be hand-recorded. Improved test quality and results,
advances in electronic instrumentation, and the low cost of computer-
based versus manual recording justify the minimum sampling rate change.
DOE seeks comments from interested parties on the introduction and
calculation of the cyclic degradation correlation factor. DOE also
seeks comments on the change in sampling rate from 10 to 5 minutes.
9. Clarify Inputs for the Demand Defrost Credit Equation
The demand defrost credit (Fdef) is a direct multiplier within the
HSPF calculation Eq. 4.2-1 in the DOE test procedure. The factor
provides nominal credit for heat pumps with a demand defrost control
system. Systems that meet DOE requirements in test procedure definition
1.21, ``demand defrost control system,'' qualify for this credit. The
multiplier has a value between 1.00 and 1.03, which is a 0 to 3 percent
increase in the HSPF rating. The credit is evaluated using the
following equation from section 3.9.2 of the DOE test procedure:
[GRAPHIC] [TIFF OMITTED] TP02JN10.239
Where:
[Delta][tau]def = time between defrost terminations (in hours) or
1.5, whichever is greater, and
[Delta][tau]max = maximum time between defrosts as allowed by the
controls (in hours) or 12, whichever is less.
The demand defrost credit was incorporated into the test procedure
during the rulemaking completed in March 1988 and has remained
unchanged. 53 FR 8319. DOE mistakenly overlooked inputs to this
equation during the most recent test procedure final rulemaking, in
which DOE shortened the maximum duration of all frost accumulation
tests from 12 to 6 hours. DOE has since considered two options for
calculating the credit: (1) Update the evaluation of [Delta][tau]max to
read ``maximum time between defrosts as allowed by the controls (in
hours) or 6 hours, whichever is less;'' and (2) reinforce that the
current form of the equation still applies and, when a defrost cycle is
not completed before the maximum time, assign [Delta][tau]def the value
of 6 hours. DOE proposes to adopt this second option in today's notice.
As discussed in the October 2007 final rule, the change from a
maximum
[[Page 31237]]
test duration of 12 to 6 hours rarely affected testing; when it did,
there was a negligible impact on the calculation of the average heating
capacity and power consumption at a 35 [deg]F outdoor temperature. The
main reason for changing the maximum limit to 6 hours was to reduce the
test burden when frost did not build on the outdoor coil. The frost
accumulation tests at low-capacity for two-capacity heat pumps and at
the intermediate compressor speed for variable-speed units are the two
leading cases where this revision may help reduce that burden. Since
the institution of this change, DOE has not received any comments or
information about the effects on heating capacity or power.
Shortening the maximum duration of the frost accumulation test
affects heat pumps that would otherwise conduct a defrost after 6 but
before 12 hours in two ways. First, as recognized during the October
2007 final rule process, such heat pumps benefit slightly from not
having a defrost cycle factored into their average heating capacity
calculation. Second, they earn a higher demand defrost credit than they
would have earned previously. As a worst case (e.g., unit's demand
defrost controls actuate at 11.999 hours while the unit's maximum
duration is 12 hours or more), the approximated demand defrost credit
is now 1.017 compared to the ``true'' value of 1.000.
In summary, the proposed rule includes additional language
clarifying that manufacturers must assign [Delta][tau]def the value of
6 hours if this limit is reached during a frost accumulation test and
the heat pump has not completed a defrost cycle. A sentence is also
added to indicate that the manufacturer must provide the value of
[Delta][tau]max.
DOE seeks comments from interested parties on this proposal for
calculating the demand defrost credit (Fdef) for cases where the Frost
Accumulation Test is terminated because the heat pump does not initiate
a defrost within the maximum allowed 6-hour heating interval.
10. Add Calculations for Sensible Heat Ratio
SHR is a parameter that indicates the relative contributions of the
air conditioner's or heat pump's cooling output that reduces the db
temperature of the air (i.e., sensible cooling) to the cooling output
that reduces the moisture content in the air (i.e., latent cooling).
The parameter is calculated by dividing the sensible cooling capacity
by the total cooling capacity. Total cooling capacity is the sum of the
sensible and latent cooling capacities. For example, an SHR of 0.75
indicates that 75 percent of the cooling is sensible and 25 percent is
latent.
The DOE test procedure considers total building cooling loads and
total cooling equipment capacities as part of the SEER calculation. The
cooling load and capacity are not divided into their sensible and
latent components. Based on historical data, equipment SHRs have
remained relatively unchanged as equipment SEER ratings have increased.
In addition, cooling equipment has historically provided a reasonable
match to the sensible and latent loads of the building or residence.
However, better insulation of homes and small commercial buildings has
helped reduce sensible building loads. Particularly in more humid
climates, this reduction in the sensible building load can make the
latent building load more prominent.
SHR differences among equipment having approximately the same SEER
have always existed. For example, 2001 Amrane, Hourahan, and Potts data
reported in the January 2003 ASHRAE Journal (pp. 28-31) show SHR values
that vary by at least 0.10 for a given SEER value. When humidity
control is a concern, consumers and their contractors may wish to know
the SHRs of different units to make a more informed decision.
The measurements required to calculate the SHR from a DOE wet-coil
cooling mode test are taken as part of the DOE test procedure. In fact,
manufacturers and independent testing laboratories routinely determine
SHR. DOE proposes to add the SHR calculation to its test procedure to
endorse the calculation and its continued use explicitly. (10 CFR part
430, subpart B, appendix M, revised section 3.3c and proposed section
4.5)
11. Incorporate Changes to Cover Testing and Rating of Ducted Systems
Having More Than One Indoor Blower
The majority of residential central air conditioners and heat pumps
employ a single blower and a single refrigerant-to-air coil. Typical
multi- and some mini-splits use more than one indoor unit, with the
indoor units using one blower and one coil. However, a newer type of
residential central system that uses more indoor blowers than indoor
coils does not follow this one-to-one blower-to-coil ratio.
The multi-blower design facilitates zoning when the system responds
to more than one thermostat. Associated with the zoning feature are
capacity modulation and variations in electrical power consumption. The
first and more limited means of affecting capacity and power use is
controlling the number of indoor blowers that are turned on and, where
applicable, altering the blower's speed (if equipped with a multi-stage
or variable-speed motor). The second and broader means of affecting
power consumption occurs in systems that use a single outdoor unit
equipped with a two-stage compressor or in systems consisting of two
outdoor units, each having single-speed compressors.
DOE proposes modifications to cover the testing and rating of
systems using a multi-blower indoor unit. These systems will be treated
as if all zones depend on outdoor temperature such that they respond to
the same load profile as a single-zone system. DOE test procedure
algorithms for covering two-capacity units and systems having a single-
speed compressor with a variable-air-volume rate indoor blower would
provide the basis for the algorithms that address systems with a multi-
blower indoor unit (10 CFR 430, subpart B, appendix M, revised sections
2.2.3, 2.4.1, 3.1.4.1.1, 3.1.4.2, 3.1.4.4.2, 3.1.4.5, 3.2.2, 3.2.2.1,
and 3.6.2; proposed sections 3.2.6, 3.6.7, 4.1.5, and 4.2.7; and
revised tables 4 and 10).
On August 28, 2008, DOE published a decision and order granting a
waiver from the DOE Residential Central Air Conditioner and Heat Pump
Test Procedure for a line of multi-blower indoor units that may be
combined with one single-speed heat pump outdoor unit, one two-capacity
heat pump outdoor unit, or two separate single-speed heat pump outdoor
units. 73 FR 50787-50797. For the two separate single-speed outdoor
units, the chosen indoor coil contains two independent refrigeration
circuits, each fed by one of the outdoor units.
The above-referenced waiver covers products that use two to eight
indoor blowers with a single- or dual-circuit indoor coil. To simplify
the testing and rating algorithm, DOE structured the waiver so that
each system was evaluated with all and with half of the indoor blowers
operating. DOE did not consider any other potential blower
combinations. For systems offering compressor modulation, a high-stage
compressor operation was evaluated only when all blowers were on, and
the low-stage was evaluated with half the blowers on.
DOE proposes to amend the test procedure to allow the coverage of
systems that use a multi-blower indoor unit to address the same type of
equipment covered by the test procedure waiver granted to Cascade
Group, LLC.
[[Page 31238]]
12. Add Changes To Cover Triple-Capacity, Northern Heat Pumps
On February 5, 2010, DOE granted Hallowell International a waiver
from the DOE test procedure on how to test and rate its line of boosted
compression heat pumps. (24 FR 6014-6018) These heat pumps offer three
stages of compressor capacity when heating, with the third stage being
designed to provide greater heating capacity at the lowest outdoor
temperatures. The approved waiver contained additional laboratory tests
and calculations steps that were specific to obtaining an HSPF rating
for the Hallowell heat pumps. No changes to the DOE test procedure were
required to evaluate the SEER for these heat pumps. The test procedure
sections covering two-capacity systems when operating in a cooling mode
are applicable for the Hallowell heat pumps.
Proposed test procedure amendments are offered as part of this
rulemaking to cover heat pumps that provide three levels or stages of
heating capacity like the Hallowell units. The proposals seek to cover
the more generic case of such technology.. The proposal includes,
additional laboratory testing to capture the effect on both capacity
and power of the additional stage of heating operations.. The proposed
building load assigned by HSPF calculations requires evaluation based
on the application in which high-stage compressor capacity for heating
exceeds that for cooling. Finally, the proposed coverage accounts for
controls that lock out one or two heating mode capacity levels at any
given outdoor temperature. Once these proposals are incorporated into
the test procedure, the need for a waiver will be eliminated and the
requirements will apply to all manufacturers who offer equipment with
this technology.
DOE proposes adding two required steady-state tests to quantify the
heating capacity and power consumption characteristics of the third
stage of heating. One test would be conducted at the existing outdoor
temperature test condition of 17 [deg]F db/15 [deg]F wb temperature
(H33). The second test would be at a new outdoor test condition (H43),
2 [deg]F db/1 [deg]F wb. This proposed outdoor temperature condition is
slightly higher than the 0 [deg]F db/-2 [deg]F wb condition proposed by
Hallowell and cited in the approved waiver. The alternative condition
is proposed with the intent of specifying a test condition that is
marginally more achievable for testing laboratories. Finally, two
optional tests are proposed, a Frost Accumulation Test and a cyclic
test with the heat pump operating at its third or boosted compression
stage (10 CFR part 430, subpart B, appendix M, proposed section 3.6.6).
DOE is proposing equations for calculating the capacity and
electrical power consumption of the heat pump as a function of the
outdoor temperature when operating at its highest stage of compressor
capacity. As part of the proposal, the heating building load used in
the HSPF calculation, would also be based on the capacity measured
during the H1 test condition (47 [deg]F db/43 [deg]F wb outdoor
temperatures). The compressor would operate at the same speed or stage
as in the (A2) cooling mode test at 95 [deg]F outdoor db. The HSPF
calculation algorithm would be an extension of the approach currently
used in the DOE test procedure for two-capacity heat pumps. The active
stages of heating capacity available for each bin temperature
calculation would be based on the control logic of the unit (10 CFR
part 430, subpart B, appendix M, proposed section 4.2.6).
DOE seeks comments from interested parties on the inclusion of test
procedure amendments to cover heat pumps that offer three stages of
compressor capacity when heating.
13. Specify Requirements for the Low-Voltage Transformer Used when
Testing Coil-Only Air Conditioners and Heat Pumps and Require Metering
of All Sources of Energy Consumption During All Tests
The transformer that powers the low-voltage components of a field-
installed hot-air furnace and add-on (coil-only) air conditioner or
heat pump resides in the furnace. A coil-only air conditioner or heat
pump with a hot-air furnace is not typically laboratory tested. As a
result, the DOE test procedure does not specify the low-voltage source
of power for the compressor contactor, control boards, and most heat
pump reversing valves. Because the test procedure does not stipulate
metering requirements, the associated power consumption is typically
unmetered, which makes the choice of the transformer used
inconsequential. A 100 volt amp (VA) transformer powered by a 230 V
input works as well as a 40 VA model powered by a 115 V input.
Because coil-only equipment mainly competes against like equipment,
not accounting for low-voltage components' power consumption in the
past was not a glaring deficiency as the comparable impact on SEER and
HSPF ratings. However, in seeking to account for all modes and sources
of energy consumption as per section 310 of EISA 2007, DOE proposes
that the energy consumption of low-voltage components of coil-only
systems be measured and included in the applicable rating descriptors.
DOE anticipates needing to specify a VA rating for the transformer used
for laboratory testing, while requiring that the input voltage be the
same as that provided to the outdoor unit (e.g., 230 V).
An indoor wall thermostat is not typically used for laboratory
testing of a central air conditioner or heat pump. For this rulemaking,
DOE considered but decided against assigning a default power value to
account for the absence of the wall thermostat. Some thermostats use no
power or are battery powered. If a low-voltage-powered electronic
thermostat is used, its power consumption is often low, usually less
than a watt or two. In most cases, an air conditioner or heat pump can
be installed in a system that includes a variety of wall thermostats.
It is not possible to know the type of thermostat that will be used or
its power consumption.
For testing coil-only air conditioners and heat pumps, DOE proposes
that the power consumption of the low-voltage system components be
metered. Additionally, the transformer would be rated to provide 24 V,
have a load rating of either 40 or 50 VA, and would be designed to
operate with a primary input of 230 V, single phase, 60 hertz. The
transformer may be powered by the same source as the outdoor unit or a
separate 230 V source. The key requirement is that the instrument
measuring the transformer's power consumption during the off mode power
or any other test must do so within the prescribed measurement
accuracy.
14. Add Testing Procedures and Calculations for Off Mode Energy
Consumption
SEER is a seasonal descriptor that accounts for all (modes of)
energy consumption that occurs during the cooling season, including
times when the air conditioner or heat pump is cycled off because the
building thermostat is satisfied. HSPF is a seasonal descriptor for
heat pumps that accounts for all (modes of) energy consumption during
the heating season. The current test procedure does not cover the
energy consumption of an air conditioner during the heating season when
the unit is typically turned off at the thermostat but its controls and
protective devices remain energized. The current test procedure also
does not account for a complete 8,760-hour year as part of the annual
cost calculation. As documented in appendix A of ASHRAE Standard 137-
2009, ``Method of Testing
[[Page 31239]]
for Efficiency of Space-Conditioning/Water Heating Appliances that
Include a Desuperheater Water Heater,'' the combination of the
location-specific cooling and heating load hours used in the annual
cost calculation is less than 8,760. The missing hours correspond to
the intervals during which space conditioning is not required because
the outdoor temperature is moderate, as during the shoulder seasons
that occur between the cooling and heating seasons. Neither SEER nor
HSPF account for energy consumed during the shoulder seasons.
To provide a means for more clearly accounting for the energy
consumption during the shoulder seasons and, for air conditioners, the
energy consumption during the heating season, DOE proposes to define
that such times occur when the air conditioner or heat pump is in an
``off mode.'' DOE proposes the following definition.
The term ``off mode'' means:
(1) For air conditioners, all times during the non-cooling
season of an air conditioner. This mode includes the ``shoulder
seasons'' between the cooling and heating seasons when the unit
provides neither heating nor cooling to the building plus the entire
heating season, when the unit is idle. The air conditioner is
assumed to remain connected to its main power source at all times
during the off mode; and
(2) For heat pumps, all times during the non-cooling and non-
heating seasons of a heat pump. This mode includes the ``shoulder
seasons'' between the cooling and heating seasons when the unit
provides neither heating nor cooling to the building. The heat pump
is assumed to remain connected to its main power source at all times
during the off mode.
Notably, the above proposed definition differs from the one
provided in section 310 of EISA 2007, which amended section
325(gg)(1)(A) of EPCA. (42 U.S.C. 6295(gg)(1)(A)) This section of EPCA
applies to a wide range of covered products, and as a result, the
definitions for off-mode, active mode, and standby mode are relatively
general in order to address all possible energy consuming modes. Rather
than introduce alternative definitions for all of these modes within
the central air conditioner and heat pump test procedure, DOE proposes
modifying only the definition for off-mode as part of this rulemaking.
DOE proposes new laboratory tests and a separate calculation
algorithm for estimating the energy consumption during the off-mode
season. The new tests and calculations are used to determine an average
power consumption for the collective shoulder seasons and, for air
conditioners, an average power consumption during the heating season.
The shoulder season's off-mode power consumption will be designated as
P1, which affects both air conditioner and heat pump energy usage. The
heating season off-mode power consumption will be designated as P2,
which only affects air conditioner energy usage.
(10 CFR part 430, subpart B, appendix M, proposed section 3.13)
DOE has determined that it is not technically feasible to integrate
off-mode energy use into the SEER and HSPF metrics because they are
both seasonal descriptors. These seasonal descriptors should not be
used to account for the out-of-season of off-mode energy consumption--
i.e., the energy consumed during the shoulder seasons and during the
heating season. To do so would alter the basis of SEER and HSPF. The
basis for the integrated SEER for an air conditioner would be annual
performance, while the basis for the integrated SEER and HSPF for a
heat pump would be part-year performance. Annual and part-year bases
for SEER and HSPF are inconsistent with the definitions of these
regulating metrics. Moreover, the difference in bases, annual for the
air conditioner versus part-year for the heat pump, disallows the use
of the integrated SEER for comparing an air conditioner to a heat pump.
Therefore, to maintain the technical integrity of SEER and HSPF and to
account for off-mode (off season) energy consumption, DOE has developed
a separate algorithm to calculate the off-mode (off season) energy
consumption.
The proposed P1 and P2 parameters are used to evaluate the off-mode
energy consumption for any generalized climatic region or specific
location.
The shoulder season average off-mode power P1 (for air conditioners
and heat pumps) would be multiplied by the appropriate shoulder season
hours to obtain the energy consumed during the collective shoulder
seasons. For air conditioners during the heating season, the average
off-mode power P2 would be multiplied by the applicable heating season
hours to obtain the energy consumed. The calculation of an air
conditioner's annual energy consumption and annual operating cost would
include both the shoulder season energy consumption and the energy
consumed during the heating season. For heat pumps, the energy
consumption during the shoulder seasons would be included in the
calculation of the annual energy consumption and annual operating cost.
As part of today's notice, DOE provides the actual hours associated
with cooling, heating, and the collective shoulder seasons for six
generalized climatic regions currently defined in the test procedure.
DOE also includes actual hours that correspond to the 1,000 cooling
load and the 2,080 heating load hours referenced in 10 CFR 430.23(m),
``Test procedures for the measurement of energy and water consumption--
central air conditioners and heat pumps,'' as the representative
average use cycles. Additionally, DOE provides equations for
calculating the actual hours for the cooling, heating, and collective
shoulder seasons corresponding to any cooling and heating load hour
combination.
As noted above, it is not technically feasible to use SEER and HSPF
to account for the off-mode energy use. SEER and HSPF are the seasonal
performance descriptors for the cooling and heating seasons,
respectively. Moreover, such changes would have a deleterious impact on
the manufacturer and confuse the consumer. Air conditioners and heat
pumps would no longer be comparable and their energy efficiency values
would only apply to similar climactic regions (i.e. one specific
combination of cooling season hours, heating season hours, and shoulder
season hours). If these energy efficiency values were integrated, SEER
would be different in Maine than in Florida for similar air conditioner
design. Therefore, additional precautions would be required to make
sure the manufacturer only labels the units with a ``locally
integrated'' SEER when selling a unit. This new complexity would
require the consumer to have a technically pertinent knowledge to make
an informed purchasing decision.
DOE seeks comments from interested parties about off-mode power
consumption, its definition, and how DOE proposes to add it to the test
procedure.
15. Add Parameters for Establishing Regional Standards
Implementation of regional standards for central air conditioners
and heat pumps is allowed if justified. (42 U.S.C. 6295(o)(6)(D)(i))
Before DOE can establish regional standards it must fulfill two
statutory requirements: (1) That the establishment of additional
regional standards will produce significant energy savings in
comparison to establishing only a single national standard; and (2)
that the additional regional standards are economically justified. DOE
has considered regional standards from two perspectives: (1) Using the
existing SEER and/or HSPF rating but setting the regional standard
higher than the national standard; and (2) evaluating the
[[Page 31240]]
regional SEER and/or HSPF using a different algorithm and establishing
a standard based on this region-specific SEER and/or HSPF. As part of
its standards rulemaking, DOE is considering the merits of both
alternatives. Notably, DOE does not have authority to use a performance
metric other than SEER and HSPF to quantify performance, either as part
of a national rating or as part of a regional rating. EER and COP, for
example, cannot be used.
To consider a standard based on a region-specific SEER and/or HSPF,
DOE must implement changes to the test procedure. Proposed test
procedure changes are itemized below. These proposed changes were
formulated based on the framework specified in EISA 2007 and from the
results of the preliminary analysis conducted as part of the standards
rulemaking. For that framework, section 306 of EISA 2007 permits DOE to
establish up to two regional standards for cooling products in addition
to the national standard. (42 U.S.C. 6295(o)(6)(B)) Further, individual
States shall be placed only into a single region. (42 U.S.C.
6295(o)(6)(C)(iii)) In response, DOE has tentatively decided to limit
its consideration of regional standards to cooling-dominated contiguous
States and, in addition, to focus only on a region-specific SEER, not
HSPF. The natural division of the cooling-dominated region is an east-
west partitioning where the eastern region generically qualifies as
having a hot, humid climate, where the western region may be
generically categorized as hot and dry.
SEER, which has and will continue to be used to establish the
national standard, is evaluated based on indoor test conditions of 80
[deg]F db/67 [deg]F wb. These conditions would be suitable to evaluate
performance when the equipment is applied in the proposed hot-humid
region. As a result, test procedure changes are not necessary to
complement a potential hot-humid regional standard. As currently
planned, any hot-humid regional standard would be based on the current
SEER algorithm. The final SEER assigned to the hot-humid regional
standard, however, could be higher than the value assigned for the
national standard.
As for the proposed hot-dry region, DOE identified States that
could be included in this region. These States and the basis for their
selection is described in the technical support document (TSD) prepared
as part of the development of the residential central air conditioners
and heat pumps standards. For this region, DOE is considering the
option of establishing a regional SEER standard based on a region-
specific SEER rating (i.e., SEER or SEER Hot-Dry (SEER-HD)). The
subsections that follow discuss test procedure elements that offer
mechanisms for capturing equipment performance in a climate that
differs from the average climate represented in the national SEER
rating. Until DOE finalizes the list of States in the targeted region,
some numbers and inputs are subject to change.
a. Use a Bin Method for Single-Speed SEER Calculations for the Hot-Dry
Region and National Rating
The bin calculation structure currently used in the DOE test
procedure for calculating the SEER of two-capacity and variable-speed
systems accounts for the effects of outdoor db temperature (including a
shift in the frequency of occurrence), the equipment sizing criteria,
and an alternative building load profile. The bin calculation method
allows a mechanism to evaluate the relative impact of installing an air
conditioner or heat pump in different climates, including a hot
climate.
The simple short-cut equation provided in the DOE test procedure
for rating most single-speed systems typically yields a SEER value that
is close to the SEER value obtained using the temperature bin method;
i.e., if the fractional bin hour distribution, the sizing criteria, and
the building load line algorithm are the national average values. As
deviations to this specific case are introduced, however, the bin
calculated SEER will change accordingly while the short-cut SEER will
remain unchanged and equal to the value that results from the
calculations in 10 CFR part 430, subpart B, appendix M, section 4.1.1.
Thus, the current short-cut SEER method cannot be used if any
calculation parameter changes.
Three potentially differentiating parameters of the proposed hot-
dry region are the addition of operating hours at bin temperatures
above the current maximum of 102 [deg]F, an appreciable redistribution
in the percentage of hours occurring in each 5 [deg]F outdoor
temperature bin, and a different outdoor design temperature. To account
for the dryness of the region, in addition, cooling capacity and
electrical power can be based on performance achieved when operating
with comparatively drier indoor conditions. Because of these projected
departures, DOE proposes a bin calculation method for evaluating the
region-specific SEER for all types of systems, including those units
having a single-speed compressor.
The proposed SEER-HD temperature bin method will use a single set
of new fractional bin hours representative of the applicable contiguous
States. A revised outdoor design temperature would be used in defining
the building load for each temperature bin. The zero-load balance point
will remain at 65 [deg]F, and the assumed oversizing would remain at 10
percent. The assumed linear relationship between outdoor db temperature
and building load would also remain. The performance of the air
conditioner or heat pump as a function of outdoor db temperature would
be based on operating at indoor ambient conditions comparatively drier
than those used for the national rating.
With the planned institution of a bin calculation method for all
systems when determining the SEER-HD, DOE proposes to eliminate the use
of the short-cut method for all single-speed systems when determining
the national SEER, replacing it with the bin calculation algorithm on
which the short-cut method is based. The benefits of this proposed
transition include consistency between rating fixed speed and
modulating systems, an increase in the potential impact of the A Test
relative to the B Test, avoidance of potential confusion about the
validity and basis of the short-cut method, elimination of concerns
that the short-cut method often yields a slightly higher SEER than the
bin method for current equipment, and consistency between the
calculation of the national SEER and regional SEER-HD (10 CFR part 430,
subpart B, appendix M, revised sections 4.1 and 4.1.1).
b. Add New Hot-Dry Region Bin Data
An important component for implementing a new SEER-HD rating is
defining a representative set of outdoor temperature data for the
cooling season. This data set is the fractional bin hours assigned to
each 5 [deg]F temperature bin. Using TMY2 weather data combined with
the calculated building load for each temperature bin (based on using
the ASHRAE 1 percent design dry-bulb temperature for specific location
in place of the 95 [deg]F used in the DOE test procedure), DOE
generated cooling load profiles for cities within those States being
considered as part of the hot-dry region. Using population-based
weighting factors for each TMY location, DOE calculated a population-
averaged annual cooling load profile and a corresponding fractional bin
hour distribution.
Table III.2 lists the proposed cooling season fractional bin hour
distribution for the hot-dry region under the column heading SEER-HD
(for basis of this
[[Page 31241]]
table, see chapter 7 of the preliminary TSD of the central air
conditioner standards rulemaking). For comparison, the current DOE test
procedure cooling season fractional bin hour distribution is shown
along with the cooling load profiles calculated from each bin hour
distribution. To three decimal places, the cooling season fractional
bin hours for the SEER-HD in the 110 to 114 [deg]F temperature bin is
shown as 0.000; however, the actual bin hour fraction, 0.0002, resulted
in a 0.001 annual cooling load fraction as shown in the rightmost
column. DOE requests comments on the chart below.
Table III.2--Proposed Four-State Hot-Dry Region: Arizona, California, New Mexico, Nevada
----------------------------------------------------------------------------------------------------------------
Cooling season fractional bin Resulting cooling load profile
hours -------------------------------
Temperature [deg]F --------------------------------
DOE PT.430 SEER-HD DOE PT.430 SEER-HD
----------------------------------------------------------------------------------------------------------------
65-69........................................... 0.214 0.477 0.036 0.115
70-74........................................... 0.231 0.208 0.137 0.175
75-79........................................... 0.216 0.119 0.220 0.172
80-84........................................... 0.161 0.086 0.232 0.176
85-89........................................... 0.104 0.047 0.194 0.124
90-94........................................... 0.052 0.027 0.119 0.088
95-99........................................... 0.018 0.021 0.049 0.082
100-104......................................... 0.004 0.011 0.013 0.050
105-109......................................... 0.000 0.004 0.000 0.018
110-114......................................... 0.000 0.000 0.000 0.001
----------------------------------------------------------------------------------------------------------------
c. Add Optional Testing at the A and B Test Conditions With the Unit in
a Hot-Dry Region Setup
Bin calculations account for how the air conditioner or heat pump's
total cooling capacity and electrical power consumption change with
outdoor temperature (and, for modulating systems, with the compressor's
capacity or speed). During the cooling season for the proposed hot-dry
region, the air conditioner or heat pump will operate mostly when
comparatively less latent cooling is needed. By comparison, the
performance data from the currently required laboratory tests (Tests A
and B for single-speed systems) correspond to indoor test conditions
that result in a fully wetted coil and a significant amount of latent
cooling (typically 20 to 30 percent of the total capacity). The
electrical power consumption and EER of a system operating with a fully
wetted coil also differ slightly from the values obtained from
operating with a partially wetted or dry coil.
In addition to evaluating the SEER-HD using the same performance
data used to calculate the national SEER, at least two other options
are available: specify hot-dry, steady-state cooling mode tests (where
indoor conditions are representative of such an installation), or test
at the same indoor conditions currently specified for the dry-coil
tests used to determine the cooling mode cyclic degradation
coefficient(s).
To determine the potential impact that the indoor conditions (wb
temperature) may have on the new SEER-HD rating, DOE conducted sample
calculations for the bracketing cases. A unit with a tested national
SEER of 13.6 would earn a SEER-HD of 13 using the 80 [deg]F/67 [deg]F
data and a SEER-HD of 11 using the dry-coil data. The first drop
reflects the effects of the fractional bin hour distribution and a
different outdoor design temperature for the hot-dry region. The second
drop captures the impact of using dry- instead of wet-coil data. The
magnitude of the latter drop persuaded DOE to explore a different
option. Acknowledging the greater test burden, DOE seeks to specify
conditions more representative of a hot-dry region installation.
Lacking any contrary data or comments supporting an indoor db
temperature for the hot-dry region tests greater than the 80 [deg]F db
temperature used for standard SEER tests, DOE proposes to use the 80
[deg]F db temperature to minimize the increased test burden. For the
companion wb test condition, DOE considered four values: 63 [deg]F, 64
[deg]F, 64.5 [deg]F, and 65 [deg]F. These candidate wb temperatures
were selected based upon published reports of field data collected in
California drier climate zones, a review of indoor test conditions
selected for hot-dry testing by private and university researchers, and
the practical aspect of differentiating from the current test condition
of 67 [deg]F wb temperature (Proctor Engineering Group, Ltd., ``Hot Dry
Climate Air Conditioner [HDAC] Proof of Concept [POC]--Final 3-Ton
Laboratory Test Analysis Report,'' Draft Report, July 13, 2006 and
Southern California Edison, Proctor Engineering Group Ltd., and
Bevilacqua-Knight, Inc., ``Energy Performance of Hot, Dry Optimized
Air-Conditioning Systems,'' PIER Final Project Report, CEC-500-2008-
056, July 2008). DOE today proposes to use an indoor wb temperature of
64 [deg]F because it lies at the midpoint of the considered range.
The effect of outdoor temperature on cooling capacity and power
consumption can be approximated by a linear fit when calculating the
national SEER using a bin method. As such, DOE prefers testing at two
different outdoor temperatures, with all other operating parameters
constant. Ideally, the two temperatures should provide a range of
application to maximize interpolation values and minimize
extrapolation. The national SEER test pair of 82 [deg]F and 95 [deg]F
approach the specified criterion for singlespeed units, for the high
capacity of two-capacity units, and for the maximum speed of variable-
speed systems. The test pair of 67 [deg]F and 82 [deg]F for the low
capacity performance of two-capacity units and for the minimum speed
performance of variable-speed systems provide the same utility.
Because of the availability of the national SEER wet-coil test
data, the need to minimize the test burden, and the fact that the
performance ratings only apply to the hot-dry regional climate, DOE
seeks to minimize the number of new required tests. Therefore, DOE
proposes a combination of required and optional tests. Instead of
conducting optional tests, DOE proposes using simplified approximating
equations to capture the change in performance as the outdoor
temperature changes.
As proposed, single-speed systems will have a single required SEER-
HD test, which will occur at an outdoor temperature of 95 [deg]F and be
designated ``the AD Test.'' Systems having a modulating capability will
have two
[[Page 31242]]
required tests: one (AD2) occurring at a 95 [deg]F outdoor temperature
with the unit operating at high capacity or maximum speed, and the
other (BD1) occurring at a 82 [deg]F outdoor temperature with the unit
operating at low capacity or minimum compressor speed. Before
conducting the first SEER-HD tests, the system shall be (re)configured,
as applicable, in accordance with any published instructions from the
manufacturer that pertain to installations in a hot-dry region.
As proposed, single-speed systems will have a single optional SEER-
HD test (BD) that would occur at an outdoor temperature of 82 [deg]F.
Systems with a modulating capability would have two optional tests: one
(BD2) occurring at a 82 [deg]F outdoor temperature with the unit
operating at high capacity or maximum compressor speed, and the other
(FD1) occurring at a 67 [deg]F outdoor temperature with the unit
operating at low capacity or minimum compressor speed. These optional
tests provide the additional data necessary to determine how the
cooling capacity and power consumption change with outdoor temperature.
Instead of conducting the optional test(s), manufacturers can use
the capacity and power data collected from the national SEER cooling
mode tests conducted using 80 [deg]F db/67 [deg]F wb as the indoor
entering air conditions to approximate how the hot-dry region capacity
and power consumption change with outdoor temperature for a given
compressor capacity. Specifically, the slope of the capacity (or power
consumption) versus outdoor temperature relationship for the comparable
80 [deg]F db/67 [deg]F wb tests will be scaled by multiplying the ratio
of the capacity (or power consumption) determined from the SEER-HD test
by the capacity (power consumption) determined from the national SEER
test conducted at the same outdoor temperature. Using a single-speed
system as an example, the slope based on the A and B Tests is
multiplied by the ratio of the AD Test capacity (or power consumption)
to the A Test capacity (or power consumption).
For approximating the capacity and power consumption dependency
with outdoor temperature, DOE proposes global adjustment factors to
assist in obtaining a conservative SEER-HD. Applying the approximated
slope, estimated capacities for temperatures above the single-test
temperature point will be over-predicted, while capacities for
temperatures below will be under-predicted. Given the proposed required
tests for the hot-dry region, the calculated weighted energy
consumption for temperature bins below the required test temperature
(e.g., 95 [deg]F) should be higher than the bin-weighted total energy
consumed for temperature bins above the test temperature. Conversely,
the total bin-weighted cooling delivered for temperature bins less than
the test temperature should exceed the cooling contribution from
temperature bins above the test temperature. As a result, a
conservative rating would be achieved if the capacity at the lower
temperatures is under-predicted and the power consumption at these
temperatures is over-predicted. To determine the under-prediction of
capacity, the magnitude of the negative slope for the approximated
capacity versus temperature relationship should be reduced slightly.
DOE proposes a capacity slope adjustment factor of 0.95. Similarly, the
magnitude of the positive slope for the approximated power consumption
versus temperature relationship should be reduced slightly. DOE
proposes a power consumption slope adjustment factor of 0.95. These
adjustment factors are assigned based on the goal of safeguarding
against the default equations yielding a higher SEER-HD than the tested
values. DOE specifically requests data showing whether the magnitudes
of these adjustment factors should be changed.
Collectively, the approximation approach that includes the proposed
adjustment factors should yield a SEER-HD equal to or slightly less
than the SEER-HD determined from the optional test(s). DOE wants the
approximation to provide a conservative rating, which will avoid over-
predicting the actual value. When the optional testing is conducted but
yields a poorer outcome, a manufacturer shall not be penalized for
having conducted the optional SEER tests. If the SEER-HD determined
using the approximations defined above is higher than the SEER-HD
determined using the data from the optional test(s), the manufacturer
may use the higher value. (10 CFR part 430, subpart B, appendix M,
revised sections 3.6.2, 3.6.3, and 3.6.4)
DOE considered additional options for modifying the laboratory
testing to differentiate equipment installed in a hot-dry region. For
example, DOE considered setting higher minimum external static pressure
requirements for the required and optional SEER-HD laboratory tests, as
some interested parties have advocated increasing the current minimums.
DOE elected not to change these minimums as part of the SEER-HD tests
to maximize consistency between the SEER-HD and national SEER tests.
This consistency is necessary given the above-described method for
approximating the relationship between cooling capacity (power
consumption) and outdoor temperature for the hot-dry condition. DOE
also considered ways to account for an extended indoor fan time delay
mode designed to re-evaporate condensate trapped on the coil or lying
in the pan. Because the current CD tests are dry-coil tests, DOE was
unable to conceive of a change that would permit measurement of such an
evaporative cooling (latent recovery) mechanism if employed in the
field.
d. Add a New Equation for Building Load Line in the Hot-Dry Region
As part of the evaluation of the newly proposed region-specific
performance rating, SEER-HD, DOE must establish a building load line
for the SEER-HD (just as used for evaluating the national SEER):
[GRAPHIC] [TIFF OMITTED] TP02JN10.240
Where:
Tj = the bin temperature,
TZB = the zero load balance point,
TOD = the outdoor design temperature,
Qkc,HD (TOD) = the unit's capacity at the
design outdoor temperature, and
FOS = the oversizing factor.
As with the calculation of the national SEER, the building load is
assumed to vary linearly with outdoor temperature. Other parameters
common to the two building load calculations are the zero load balance
point, the outdoor design temperature, and the oversizing factor: 65
[deg]F, 95 [deg]F and 10 percent (i.e., FOS = 1.1),
respectively. As for the 95 [deg]F outdoor design temperature, DOE
arrived at it by calculating the population-weighted average of the
ASHRAE Handbook 1 percent design dry-bulb temperature for multiple
cities located within the proposed hot-dry region. DOE recognizes that
across the hot-dry region there are significant differences in cooling
design conditions by location but has proposed 95 [deg]F for
establishing the load line.
DOE requests comments from interested parties on the introduction
of regional standards, the use of the bin method for determining
regional and national SEER, the proposed hot-dry regional bin data, and
the addition of required and optional testing in a hot-dry region
setup.
[[Page 31243]]
16. Add References to ASHRAE 116-1995 (RA 2005) for Equations That
Calculate SEER and HSPF for Variable-Speed Systems
DOE proposes to reference specific language and equations within
ASHRAE Standard 116-1995 (RA 2005) that provide greater detail in
determining the three balance point temperatures needed when
calculating the SEER of an air conditioner or heat pump having a
variable-speed compressor. DOE proposes to do the same for the HSPF
variable-speed algorithm.
The DOE test procedure does not include the equations used for
calculating the outdoor temperatures at which the unit's cooling or
heating capacity matches the building's cooling or heating load when
operating at minimum, intermediate, or maximum compressor speeds.
(Intermediate speed is used for laboratory testing.) The DOE test
procedure defines these three outdoor temperatures and how they are
evaluated. ASHRAE Standard 116-1995 (RA 2005) provides explicit
equations for calculating the three outdoor temperatures for cooling
and the three outdoor temperatures for heating. Referencing this
standard within the DOE test procedure is worthwhile, as it may be
especially helpful for those new to either test procedures or testing
and rating variable-speed products.
DOE proposes adding a sentence within test procedure sections
4.1.4.2 and 4.2.4.2 to reference the applicable sections of the ASHRAE
Standard that provide the exact equations, along with explanatory text
and figures.
DOE seeks comments on this proposal.
17. Update Test Procedure References to the Current Standards of AHRI
and ASHRAE
Since the October 2007 final rule, ARI has merged with the Gas
Appliance Manufacturers Association to become AHRI. References to ARI
within Appendix M need to be updated accordingly, as documented below.
IV. Regulatory Review
A. Review Under Executive Order 12866
Today's regulatory action is not a ``significant regulatory
action'' under Executive Order (E.O.) 12866, ``Regulatory Planning and
Review.'' 58 FR 51735 (October 4, 1993). Accordingly, this action was
not subject to review by the Office of Management and Budget under the
Executive Order.
B. Review Under the National Environmental Policy Act of 1969
In this proposed rule, DOE proposes amendments to test procedures
that may be used to implement future energy conservation standards for
central air conditioners. These amendments will not affect the quality
or distribution of energy usage and, therefore, will not result in any
environmental impacts. 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 (NEPA) (42 U.S.C. 4321 et
seq.) and the Department's implementing regulations at 10 CFR part
1021. More specifically, this rule 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.
C. 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 (IRFA) 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 E.O. 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 available on the Office of the General
Counsel's Web site (http://www.gc.doe.gov).
DOE reviewed today's proposed rule, which would amend the test
procedures for residential central air conditioners and heat pumps,
under the provisions of the Regulatory Flexibility Act and the
procedures and policies published on February 19, 2003. DOE tentatively
concludes and certifies that the proposed rule, if adopted, would not
result in a significant impact on a substantial number of small
entities. The factual basis for this certification is set forth below.
As defined by the Small Business Administration (SBA) for the Air-
Conditioning and Warm Air Heating Equipment manufacturing industry,
small businesses are manufacturing enterprises with 750 employees or
fewer. DOE used the small business size standards published on January
31, 1996, as amended, by the SBA to determine whether any small
entities would be required to comply with the rule. 61 FR 3286, January
31, 1996, as amended at 67 FR 3045, January 23, 2002 and at 69 FR
29203, May 21, 2004; see also 65 FR 30836, 30850 (May 15, 2000), as
amended at 65 FR 53533, 53545 (September 5, 2000). The size standards
are codified at 13 CFR part 121. The standards are listed by North
American Industry Classification System (NAICS) code and industry
description and are available at http://www.sba.gov/idc/groups/public/documents/sba_homepage/serv_sstd_tablepdf.pdf.
Residential central air conditioner and heat pump equipment
manufacturing is classified under NAICS 333415, ``Air-Conditioning and
Warm Air Heating Equipment and Commercial and Industrial Refrigeration
Equipment Manufacturing.'' 70 FR 12395 (March 11, 2005). DOE reviewed
AHRI's listing of residential central air conditioner and heat pump
equipment manufacturer members and surveyed the industry to develop a
list of domestic manufacturers. As a result of this review, DOE
identified 22 manufacturers of residential central air conditioners and
heat pumps, of which 15 would be considered small manufacturers with a
total of approximately 3 percent of the market sales. DOE seeks comment
on its estimate of the number of small entities that may be impacted by
the proposed test procedure.
Potential impacts of the proposed test procedures on all
manufacturers, including small businesses, come from impacts associated
with the cost of proposed additional testing. DOE estimates the
incremental cost of the proposed additional tests described in 10 CFR
part 430, subpart B, appendix M (revised sections 3.1, 4.3.1, and
4.3.2; and proposed sections 3.13 and 4.2.7) to be an increase of
$1,000 to $1,500 per unit tested. This estimate is based on private
testing services quoted on behalf of DOE in the last two years for
central air conditioners and heat pumps. Typical costs for running the
cooling tests appear to be approximately $5,000. DOE estimated that the
additional activities required by the revised test procedure would
introduce a 20 to 30 percent increase in testing time resulting in
approximately $1,000 to $1,500 additional cost. The largest additional
cost would be associated with conducting steady-state cooling mode
tests and the dry climate tests (for SEER-HD).
[[Page 31244]]
Because the incremental cost of running the extra tests is the same
for all manufacturers, DOE believes that all manufacturers would incur
comparable costs for testing of individual basic models as a result of
the proposed test procedures. DOE expects that small manufacturers will
incur less testing expense compared with larger manufacturers as a
result of the proposed testing requirements because they have fewer
basic models and thus require proportionally less testing when compared
with large manufacturers that have many basic models. DOE recognizes,
however, that smaller manufacturers may have less capital available
over which to spread the increased costs of testing.
DOE compared the cost of the testing to the total value added by
the manufacturers to determine whether the impact of the proposed test
procedure amendments is significant. The value added represents the net
economic value that a business creates when it takes manufacturing
inputs (e.g. materials) and turns them into manufacturing outputs (e.g.
manufactured goods). Specifically as defined by the U.S. Census, the
value added statistic is calculated as the total value of shipments
(products manufactured plus receipts for services rendered) minus the
cost of materials, supplies, containers, fuel, purchased electricity,
and contract work expenses.
DOE analyzed the impact on the smallest manufacturers of central
air conditioners and heat pumps because these manufacturers would
likely be the most vulnerable to cost increases. DOE calculated the
additional testing expense as a percentage of the average value added
statistic for the five individual firms in the 25 to 49 employee size
category in NAICS 333415 as reported by the U.S. Census (U.S. Bureau of
the Census, American Factfinder, 2002 Economic Census, Manufacturing,
Industry Series, Industry Statistics by Employment Size) http://factfinder.census.gov/servlet/EconSectorServlet?_lang=en&ds_name=EC0200A1&_SectorId=31&_ts=288639767147). The average
annual value for manufacturers in this size range from the census data
was 1.26 million dollars in 2001$, per the 2002 Economic Census, or
approximately 1.52 million dollars per year in 2009$ after adjusting
for inflation using the implicit price deflator for gross domestic
product (U.S. Department of Commerce Bureau of Economic Analysis http://www.bea.gov/national/nipaweb/SelectTable.asp).
DOE also examined the average value added statistic provided by
census for all manufacturers with less than 500 employees in this NAICS
classification as the most representative value from the 2002 Economic
Census data of the CAC manufacturers with less than 750 employees that
are considered small businesses by the SBA (15 manufacturers). The
average annual value added statistic for all small manufacturers with
less than 500 employees was 7.88 million dollars (2009$).
Given this data, and assuming the high-end estimate of $1,500 for
the additional testing costs, DOE concluded that the additional costs
for testing of a single basic model product under the proposed
requirements would be approximately 0.1% of annual value added for the
five smallest firms, and approximately 0.02% of the average annual
value added for all small CAC manufacturers (15 firms). DOE estimates
that testing of basic models may not have to be updated more than once
every five years, and therefore the average incremental burden of
testing one basic model may be one fifth of these values when the cost
is spread over several years.
DOE requires that only the highest sales volume split system
combinations be lab tested (10 CFR 430.24(m)). The majority of air
conditioners and heat pumps offered by a manufacturer are typically
split systems that are not required to be lab tested but can be
certified using an alternative rating method which does not require DOE
testing of these units. DOE reviewed the available data for five of the
smallest manufacturers to estimate the incremental testing cost burden
for those small firms that might experience the greatest relative
burden from the revised test procedures. These manufacturers had an
average of 10 models requiring testing (AHRI Directory of Certified
Product Performance http://www.ahridirectory.org/ahridirectory/pages/home.aspx), while large manufacturers will have well over a hundred
such models. The additional testing cost for final certification for 10
models was estimated at $15,000. Meanwhile these certifications would
be expected to last the product life, estimated to be at least five
years based on the time frame established in EPCA for DOE review of CAC
efficiency standards. This test burden is therefore estimated to be
approximately 0.2% of the estimated five-year value added for the
smallest five manufacturers. DOE believes that these costs are not
significant given other, much more significant costs that the small
manufacturers of central air conditioners and heat pumps incur in the
course of doing business. DOE seeks comment on its estimate of the
impact of the proposed test procedure amendments on small entities and
its conclusion that this impact is not significant.
Accordingly, as stated above, DOE tentatively concludes and
certifies that this proposed rule would not have a significant economic
impact on a substantial number of small entities. Accordingly, DOE has
not prepared an IRFA for this rulemaking. DOE will provide its
certification and supporting statement of factual basis to the Chief
Counsel for Advocacy of the SBA for review under 5 U.S.C. 605(b).
D. Review Under the Paperwork Reduction Act
This rule contains a collection-of-information requirement subject
to the Paperwork Reduction Act (PRA) and which has been approved by OMB
under control number 1910-1400. Public reporting burden for the
collection of test information and maintenance of records on regulated
residential central air conditioners and heat pumps based on the
certification and reporting requirements is estimated to average 30
hours per response, including the time for reviewing instructions,
searching existing data sources, gathering and maintaining the data
needed, and completing and reviewing the collection of information.
Send comments regarding this burden estimate, or any other aspect of
this data collection, including suggestions for reducing the burden, to
DOE (see ADDRESSES) and by e-mail to [email protected].
Notwithstanding any other provision of the law, no person is
required to respond to, nor shall any person be subject to a penalty
for failure to comply with, a collection of information subject to the
requirements of the PRA, unless that collection of information displays
a currently valid OMB control number.
E. Review Under the Unfunded Mandates Reform Act of 1995
Title II of the Unfunded Mandates Reform Act of 1995 (UMRA; Pub. L.
104-4, codified at 2 U.S.C. 1501 et seq.) requires each Federal agency
to assess the effects of Federal regulatory actions on State, local,
and Tribal governments and the private sector. For proposed regulatory
actions likely to result in a rule that may cause expenditures by
State, local, and Tribal governments in the aggregate or by the private
sector of $100 million or more in any one year (adjusted annually for
inflation), section 202 of UMRA requires a Federal agency
[[Page 31245]]
to publish estimates of the resulting costs, benefits, and other
effects on the national economy. (2 U.S.C. 1532(a), (b)) The UMRA also
requires a Federal agency to develop an effective process to permit
timely input by elected officers of State, local, and Tribal
governments on a proposed ``significant intergovernmental mandate'' and
requires an agency plan for giving notice and opportunity for timely
input to potentially affected small governments before establishing any
requirements that might significantly or uniquely affect small
governments. On March 18, 1997, DOE published a statement of policy on
its process for intergovernmental consultation under UMRA. 62 FR 12820.
(This policy is also available at http://www.gc.doe.gov.) Today's
proposed rule contains neither an intergovernmental mandate, nor a
mandate that may result in the expenditure of $100 million or more in
any year, so these requirements do not apply.
F. Review Under the Treasury and General Government Appropriations Act,
1999
Section 654 of the Treasury and General Government Appropriations
Act, 1999 (Pub. L. 105-277) requires Federal agencies to issue a Family
Policymaking Assessment for any proposed rule that may affect family
well-being. Today's proposed rule would not have any impact on the
autonomy or integrity of the family as an institution. Accordingly, DOE
has concluded that it is unnecessary to prepare a Family Policymaking
Assessment.
G. Review Under Executive Order 13132
Executive Order 13132, ``Federalism,'' 64 FR 43255 (August 10,
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 assess carefully 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 examined today's
proposed rule 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. EPCA governs and prescribes Federal preemption of State
regulations as to energy conservation for the products that are the
subject of today's proposed rule. States can petition DOE for a waiver
of such preemption to the extent, and based on criteria, set forth in
EPCA. (42 U.S.C. 6297) No further action is required by E.O. 13132.
H. Review Under Executive Order 12988
With respect to the review of existing regulations and the
promulgation of new regulations, section 3(a) of E.O. 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; (3) provide a clear legal standard for affected
conduct rather than a general standard; and (4) promote simplification
and burden reduction. Section 3(b) of E.O. 12988 specifically requires
that Executive agencies make every reasonable effort so 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
E.O. 12988 requires Executive agencies to review regulations in light
of applicable standards in sections 3(a) and 3(b) to determine whether
they are met or it is unreasonable to meet one or more of them. DOE has
completed the required review and determined that to the extent
permitted by law, the proposed rule meets the relevant standards of
E.O. 12988.
I. Review Under the Treasury and General Government Appropriations Act,
2001
Section 515 of the Treasury and General Government Appropriations
Act, 2001 (44 U.S.C. 3516 note) provides for agencies to review most
disseminations of information to the public under information quality
guidelines established by each agency pursuant to general OMB
guidelines. The 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 proposed rule under the OMB and DOE
guidelines and has concluded that it is consistent with applicable
policies in those guidelines.
J. 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 the
Office of Information and Regulatory Affairs (OIRA), Office of
Management and Budget, 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 E.O. 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, it is not a significant
energy action. Accordingly, DOE has not prepared a Statement of Energy
Effects.
K. Review Under Executive Order 12630
DOE has determined, under E.O. 12630, ``Governmental Actions and
Interference with Constitutionally Protected Property Rights,'' 53 FR
8859 (March 15, 1988), that this proposed regulation, if promulgated as
a final rule, would not result in any takings that might require
compensation under the Fifth Amendment to the U.S. Constitution.
L. Review Under Section 32 of the Federal Energy Administration (FEA)
Act of 1974
Under section 301 of the Department of Energy Organization Act
(Pub. L. 95-91), DOE must comply with section 32 of the Federal Energy
Administration Act of 1974, as amended by the Federal Energy
Administration Authorization Act of 1977. When a proposed rule
[[Page 31246]]
contains or involves use of commercial standards, the rulemaking must
inform the public of the use and background of such standards. 15
U.S.C. 788 Section 32.
The proposed rule incorporates testing methods contained in the
following commercial standards: (1) ASHRAE Standard 23-2005, ``Methods
of Testing for Rating Positive Displacement Refrigerant Compressors and
Condensing Units;'' (2) ASHRAE Standard 37-2005, ``Methods of Testing
for Rating Electrically Driven Unitary Air-Conditioning and Heat Pump
Equipment,'' sections 7.3.3.1, 7.3.3.3, 7.3.4.1, 7.3.4.3, 7.4, 8.2,
8.2.5, and Table 3; (3) ASHRAE Standard 41.1-1986 (RA 2006), ``Standard
Method for Temperature Measurement,'' sections 4, 5, 6, 9, 10, and 11;
(4) ASHRAE 41.6-1994 (RA 2006), ``Standard Method for Measurement of
Moist Air Properties,'' sections 5 and 8; (5) ASHRAE 41.9-2000 (RA
2006), ``Calorimeter Test Methods for Mass Flow Measurements of
Volatile Refrigerants;'' (6) ASHRAE Standard 116-1995 (RA 2005),
``Methods of Testing for Rating Seasonal Efficiency of Unitary Air
Conditioners and Heat Pumps,'' section 10.2.4; (7) ANSI/AMCA 210-07
(ANSI/ASHRAE 51-07), ``Laboratory Methods of Testing Fans for Certified
Aerodynamic Performance Rating,'' Figures 2A and 12; and (8) AHRI
Standard 210/240-2008 ``Standard for Performance Rating of Unitary Air-
Conditioning & Air-Source Heat Pump Equipment,'' sections 6.1.3.2,
6.1.3.4, and 6.1.3.5 and Figures D1, D2, and D4. DOE has evaluated
these standards and is unable to conclude whether they fully comply
with the requirements of section 323(b) of the Federal Energy
Administration Act (i.e., whether they were developed in a manner that
fully provides for public participation, comment, and review).
As required by section 32(c) of the Federal Energy Administration
Act of 1974 as amended, DOE will consult with the Attorney General and
the Chairman of the FTC before prescribing a final rule about the
impact on competition of using the methods contained in these
standards.
V. Public Participation
A. Attendance at Public Meeting
The time and date of the public meeting are listed in the DATES
section at the beginning of this NOPR. The public meeting will be held
at the U.S. Department of Energy, Forrestal Building, Room 1E-245. To
attend the public meeting, please notify Ms. Brenda Edwards at (202)
586-2945. Foreign nationals visiting DOE Headquarters are subject to
advance security screening procedures requiring a 30-day advance
notice. Any foreign national wishing to participate in the meeting
should advise DOE of this fact as soon as possible by contacting Ms.
Brenda Edwards to initiate the necessary procedures.
B. Procedure for Submitting Requests To Speak
Any person who has an interest in today's notice or who is a
representative of a group or class of persons that has an interest in
these issues may request an opportunity to make an oral presentation.
Such persons may hand-deliver requests to speak, along with a computer
diskette or CD in WordPerfect, Microsoft Word, PDF, or text (ASCII)
file format to the address shown in the ADDRESSES section at the
beginning of this NOPR between 9 a.m. and 4 p.m. Monday through Friday,
except Federal holidays. Requests may also be sent by mail or e-mail to
[email protected].
Persons requesting to speak should briefly describe the nature of
their interest in this rulemaking, provide a telephone number for
contact, and submit an advance copy of their statements at least one
week before the public meeting. At its discretion, DOE may permit any
person who cannot supply an advance copy of their statement to
participate, if that person has made advance alternative arrangements
with the Building Technologies Program. The request to give an oral
presentation should ask for such alternative arrangements.
C. Conduct of Public Meeting
DOE will designate a DOE official to preside at the public meeting
and may also employ a professional facilitator to aid discussion. The
meeting will not be a judicial or evidentiary-type public hearing, but
DOE will conduct it in accordance with section 336 of EPCA (42 U.S.C.
6306). A court reporter will record the proceedings and prepare a
transcript. DOE reserves the right to schedule the order of
presentations and to establish the procedures governing the conduct of
the public meeting. After the public meeting, interested parties may
submit further comments on the proceedings as well as on any aspect of
the rulemaking until the end of the comment period.
The public meeting will be conducted in an informal conference
style. DOE will present summaries of comments received before the
public meeting, allow time for presentations by participants, and
encourage all interested parties to share their views on issues
affecting this rulemaking. Each participant will be allowed to make a
prepared general statement (within DOE-determined time limits) prior to
the discussion of specific topics. DOE will permit other participants
to comment briefly on any general statements.
At the end of all prepared statements on a topic, DOE will permit
participants to clarify their statements briefly and comment on
statements made by others. Participants should be prepared to answer
questions from DOE and other participants concerning these issues. DOE
representatives may also ask questions of participants concerning other
matters relevant to this rulemaking. The official conducting the public
meeting will accept additional comments or questions from those
attending, as time permits. The presiding official will announce any
further procedural rules or modification of the above procedures that
may be needed for the proper conduct of the public meeting.
DOE will make the entire record of this proposed rulemaking,
including the transcript from the public meeting, available for
inspection at the U.S. Department of Energy, 6th Floor, 950 L'Enfant
Plaza, SW., Washington, DC 20024, (202) 586-2945, between 9 a.m. and 4
p.m. Monday through Friday, except Federal holidays. Any person may
purchase a copy of the transcript from the transcribing reporter.
D. Submission of Comments
DOE will accept comments, data, and other information regarding the
proposed rule before or after the public meeting, but no later than the
date provided at the beginning of this NOPR. Please submit comments,
data, and other information electronically to [email protected]. Submit electronic comments in WordPerfect, Microsoft
Word, PDF, or text (ASCII) file format and avoid the use of special
characters or any form of encryption. Comments in electronic format
should be identified by the docket number EERE-2009-BT-TP-0004 and/or
RIN number 1904-AB94 and wherever possible carry the electronic
signature of the author. No telefacsimiles (faxes) will be accepted.
According to 10 CFR 1004.11, any person submitting information that
he or she believes to be confidential and exempt by law from public
disclosure should submit two copies: one copy of the document including
all the information believed to be confidential and one copy of the
document with the information believed to be confidential deleted. DOE
will make its own
[[Page 31247]]
determination as to the confidential status of the information and
treat it according to its determination.
Factors of interest to DOE when evaluating requests to treat
submitted information as confidential include (1) a description of the
items; (2) whether and why such items are customarily treated as
confidential within the industry; (3) whether the information is
generally known by or available from other sources; (4) whether the
information has previously been made available to others without
obligation concerning its confidentiality; (5) an explanation of the
competitive injury to the submitting person which would result from
public disclosure; (6) a date upon which such information might lose
its confidential nature due to the passage of time; and (7) why
disclosure of the information would be contrary to the public interest.
E. Issues on Which DOE Seeks Comment
Although comments are welcome on all aspects of this rulemaking,
DOE is particularly interested in receiving comments on following
issues:
1. Specific examples, including laboratory data, that address a
stakeholder's comment on the failure of the test procedure to capture
the performance characteristics of an air conditioner or heat pump that
uses ``new inverter-driven compressor technology.''
2. Do the proposed definitions for off mode air conditioners and
off mode heat pumps clarify the meaning of off mode power?
3. What is the impact of proposed lower external static pressure
levels and the proposed language for making sure that these levels are
limited to testing ducted multi-split systems?
4. What is the impact of the change to the air volume rate setup
tolerance? Information on real cases where the indoor unit was
adversely affected by the current 5 percent tolerance would be
especially helpful.
5. What is the proposed magnitude of the test operating tolerance
for the external static pressure relative to its ability to provide an
indication of steady, repeatable performance?
6. Do manufacturers foresee obtaining a SEER-HD rating for all of
their products? If not, what is an approximate percentage of systems
that will likely have a SEER-HD rating?
7. Do manufacturers foresee specifying installation instructions
that would result in systems being configured differently for the hot-
dry tests than for the normal SEER tests? If so, please provide
examples of the likely differences in the setups.
8. Will the proposed hot-dry indoor test condition of 80 [deg]F db/
64 [deg]F wb create less stable or less repeatable testing because the
indoor coil will likely be only partially wetted? DOE is particularly
interested in receiving laboratory data that quantify the relative
differences in performance from testing conducted at 80 [deg]F db/64
[deg]F wb versus 80 [deg]F db/67 [deg]F wb.
9. Is it necessary for DOE to develop and incorporate a regional
hot-dry SEER rating within the test procedure?
10. Are the proposed changes to cover systems similar to Hallowell
cold-climate heat pumps adequate to address testing concerns for these
products?
11. Are modifications needed, within the test procedure, for the
laboratory set-up of through-the-wall air conditioners and heat pumps?
VI. Approval of the Office of the Secretary
The Secretary of Energy has approved publication of today's NOPR.
List of Subjects in 10 CFR Part 430
Administrative practice and procedure, Energy conservation test
procedures, Household appliances, Incorporation by reference.
Issued in Washington, DC on February 12, 2010.
Cathy Zoi,
Assistant Secretary, Energy Efficiency and Renewable Energy.
For the reasons set forth in the preamble, DOE proposes to amend
part 430 of chapter II of Title 10, Code of Federal Regulations, to
read as follows:
PART 430--ENERGY CONSERVATION PROGRAM FOR CONSUMER PRODUCTS
1. The authority citation for part 430 continues to read as
follows:
Authority: 42 U.S.C. 6291-6309; 28 U.S.C. 2461 note.
2. Section 430.2 is amended by revising the definition of ``tested
combination'' to read as follows:
Sec. 430.2 Definitions.
* * * * *
Tested combination means a multi-split system with multiple indoor
coils having the following features:
(1) The basic model of a system used as a tested combination shall
consist of one outdoor unit with one or more compressors matched with
between two and five indoor units; for the multi-split system, each
indoor unit shall be designed for individual operation.
(2) The indoor units shall:
(i) Collectively, have a nominal cooling capacity greater than or
equal to 95 percent and less than or equal to 105 percent of the
nominal cooling capacity of the outdoor unit;
(ii) Represent the highest sales volume model family [Note: another
indoor model family may be used if five indoor units from the highest
sales volume model family do not provide sufficient capacity to meet
the 95 percent threshold level specified in paragraph (2)(i) of this
section];
(iii) Individually not have a nominal cooling capacity greater than
50 percent of the nominal cooling capacity of the outdoor unit, unless
the nominal cooling capacity of the outdoor unit is 24,000 Btu/h or
less;
(iv) Operate at fan speeds consistent with manufacturer's
specifications; and
(v) All be subject to the same minimum external static pressure
requirement (i.e., 0 in wc for non-ducted; see entries in the column
labeled ``Short Duct Systems'' of Table 2 in Appendix M to subpart B of
this part for ducted indoor units) while able to produce the same
static pressure at the exit of each outlet plenum when connected in a
manifold configuration as per section 2.4.1 of Appendix M.
* * * * *
3. Section 430.3 is amended:
a. By removing, in paragraph (b)(1), ``210/240-2006'' and adding in
its place ``210/240-2008.''
b. By removing, in paragraph (e)(3), ``(Reaffirmed 2001)'' and
adding in its place ``(Reaffirmed 2006).''
c. By revising paragraph (e)(7).
The revisions read as follows:
Sec. 430.3 Materials incorporated by reference.
* * * * *
(e) * * *
(7) ANSI/AMCA 210-07 (ANSI/ASHRAE 51-07), Laboratory Methods of
Testing Fans for Certified Aerodynamic Performance Rating approved
August 17, 2007, IBR approved for Appendix M to Subpart B.
* * * * *
Appendix M [Amended]
4. Appendix M to subpart B of part 430:
(a) In section 1, Definitions by:
1. Removing, in section 1.2, ``ARI means Air-Conditioning and
Refrigeration Institute'' and adding in its place ``AHRI means Air-
Conditioning, Heating and Refrigeration Institute.''
2. Removing, in section 1.3, ``ARI'' and adding in its place
``AHRI'' in two locations.
3. Removing, in section 1.7, ``RA 01'' and adding in its place ``RA
06;'' and removing ``2001'' and adding in its place ``2006.''
[[Page 31248]]
4. Removing, in section 1.9, ``RA 01'' and adding in its place ``RA
06;'' and by removing ``2001'' and adding in its place ``2006.''
5. Adding, in section 1.10, ``(RA 06)'' after ``41.6-00'' and
adding ``and reaffirmed in 2006'' after ``2000.''
6. Removing, in section 1.11, ``51-99'' and adding in its place
``51-07;'' and by removing ``1999'' and adding in its place ``2007'' in
two locations.
7. Redesignating sections 1.32 through 1.33 as 1.33 through 1.34
respectively; 1.34 through 1.43 as 1.36 through 1.45 respectively; and
1.44 through 1.47 as 1.48 through 1.51 respectively.
8. Adding new sections 1.32, 1.35, 1.46, and 1.47.
(b) In section 2, Testing Conditions, by:
1. Removing, in section 2.1, ``430.22'' and adding in its place
``430.3.''
2. Revising, in section 2.2 paragraph a., and adding new paragraphs
d, e, and f.
3. Revising section 2.2.1.
4. Revising section 2.2.3, and adding new sections 2.2.3.1 and
2.2.3.2.
5. Revising section 2.2.5 and section 2.4.1 paragraph b., first
sentence.
6. Removing, in section 2.4.1d, ``430.22'' and adding in its place
``430.3'' in two locations.
7. Removing, in section 2.4.2, ``430.22'' and adding in its place
``430.3'' in two locations.
8. Removing, in section 2.5, ``430.22'' and adding in its place
``430.3.''
9. Removing, in section 2.5.3, ``430.22'' and adding in its place
``430.3'' in two locations. and in the second sentence by removing ``-
99'' and adding in its place ``-07'' in two locations.
10. Removing, in section 2.5.4.2, ``430.22'' and adding in its
place ``430.3'' in two locations and in the last sentence by removing
``RA 01'' and adding in its place ``RA 06.''
11. Revising section 2.5.5a.
12. Removing, in section 2.5.6, third, fourth, and fifth sentences
``RA 01'' and adding in its place ``RA 06,'' and by removing ``430.22''
and adding ``430.3'' in its place in the three locations.
13. Removing, in section 2.6, paragraph a, ``-99'' and adding in
its place ``-07'' in two locations; and by removing ``430.22'' and
adding in its place ``430.3'' in three locations.
14. Removing, in section 2.6, paragraph b. ``ARI Standard'' and
adding in its place ``AHRI Standard'' in one location; and by removing
``430.22'' and adding in its place ``430.3'' in three locations.
15. Removing, in section 2.7, ``ARI Standard'' and adding in its
place ``AHRI Standard,'' and by removing ``430.22'' and adding in its
place ``430.3.''
16. Removing, in section 2.10.2, ``430.22'' and adding in its place
``430.3'' in two locations.
17. Removing, in section 2.10.3, ``430.22'' and adding in its place
``430.3'' in two locations.
18. Removing, in section 2.11, paragraph a. ``430.22'' and adding
in its place ``430.3.''
19. Removing, in section 2.11, paragraph b. ``RA 01'' and adding in
its place ``RA 06,'' and by removing ``430.22'' and adding in its place
``430.3.''
20. Removing, in section 2.11, paragraph c. ``RA 01'' and adding in
its place ``RA 06,'' and by removing ``430.22'' and adding in its place
``430.3.''
21. Removing, in section 2.13, ``430.22'' and adding in its place
``430.3.''
(c) In section 3, Testing Procedures, by:
1. Adding three new sentences at the end of section 3.1.
2. Removing, in section 3.1.1, ``430.22'' and adding in its place
``430.3.''
3. Removing, in section 3.1.3, ``ARI Standard'' and adding in its
place ``AHRI Standard,'' and by removing ``430.22'' and adding in its
place ``430.3.''
4. Removing ``95'' and adding in its place ``90'' in section
3.1.4.1.1, paragraph a.4b.
5. Revising the first sentence of paragraph a.6 in section
3.1.4.1.1.
6. Revising Table 2 in section 3.1.4.1.1.
7. Adding new paragraphs d. and e. in section 3.1.4.1.1.
8. Adding a new paragraph e. in section 3.1.4.2 .
9. Revising in section 3.1.4.4.2 paragraph c. and adding new
paragraphs d. and e.
10. Removing, in section 3.1.4.4.3, paragraph 4b, ``95'' and adding
in its place ``90'' and revising the first sentence of paragraph a.6.
11. Adding, in section 3.1.4.5, a new paragraph f.
12. Removing, in section 3.1.5, ``430.22'' and adding in its place
``430.3.''
13. Removing, in section 3.1.6, ``430.22'' and adding in its place
``430.3.''
14. Adding, in section 3.2.1 following Table 3 footnotes,
undesignated text, a new Table 3a and additional undesignated text. .
15. Revising sections 3.2.2, 3.2.2.1, and 3.2.2.2.
16. Revising section 3.2.3 introductory sentence and paragraph c.,
and adding a new paragraph e.
17. Adding a new paragraph d. in section 3.2.4, and adding new
sections 3.2.5 and 3.2.6.
18. Revising section 3.3, paragraphs b. and c., and redesignating
the second paragraph d. as paragraph e.
19. Removing ``0.05'' in section 3.3 Table 7 column ``Test
Operating Tolerance,'' and adding in its place ``0.12.''
20. Removing ``2.0'' in section 3.3 Table 7 row ``Nozzle pressure
drop, % of rdg'', and adding in its place ``8.0.''
21. Removing ``See Definition 1.41'' in section 3.3 Table 7
footnote (1), and adding in its place ``See Definition 1.43.''
22. Removing ``See Definition 1.40'' in section 3.3 Table 7
footnote (2), and adding in its place ``See Definition 1.42.''
23. Redesignating paragraph b. as c. in section 3.4, and adding a
new paragraph b.
24. Removing ``0.05'' in section 3.3 Table 8 column ``Test
Operating Tolerance,'' and adding in its place ``0.12.''
25. Removing ``2.0'' in section 3.3 Table 8 row ``Airflow nozzle
pressure difference or velocity pressure\3\, % of reading'', and adding
in its place ``8.0.''
26. Removing ``See Definition 1.41'' in section 3.3 Table 8
footnote (1), and adding in its place ``See Definition 1.43.''
27. Removing ``See Definition 1.40'' in section 3.3 Table 8
footnote (2), and adding in its place ``See Definition 1.42.''
28. Revising, in section 3.5, the text following equation (3.5-1)
in paragraph i.
29. Revising, in section 3.6.2, the first sentence of the first
paragraph, Table 10 heading, and adding text following Table 10
footnotes.
30. Adding in section 3.6.3 paragraph a., 2 sentences at the end of
the paragraph.
31. Removing, in section 3.6.4, paragraph a last sentence and two
unnumbered equations, revising paragraphs b and c, and adding new
paragraph d.
32. Adding new sections 3.6.6 and 3.6.7.
33. Revising, in section 3.7, paragraph a., the first sentence of
paragraphs b. and d., and adding a new paragraph e.
34. Revising the introductory sentence in section 3.8 and paragraph
a.
35. Removing, in section 3.8.1, ``430.22'' and adding in its place
``430.3'', and revising Table 14.
36. Adding ``H23'' between ``H2'' and ``H22.'' in section 3.9
introductory sentence, revising the last sentence of paragraph e, and
by removing ``430.22'' and adding in its place ``430.3'' in paragraph
f.
37. Removing, in section 3.9c. ``(see Definition 1.42)'' from the
third sentence and adding in its place ``(see Definition 1.44).''
38. Removing ``0.05'' in section 3.9f Table 15 column ``Test
Operating Tolerance,'' and adding in its place ``0.12.''
39. Removing ``2.0'' in section 3.9f Table 15 row ``External
resistance to
[[Page 31249]]
airflow, inches of water'', and adding in its place ``8.0.''
40. Removing ``See Definition 1.41'' in section 3.9f. Table 15
footnote (1), and adding in its place ``See Definition 1.43.''
41. Removing ``See Definition 1.40'' in section 3.9f. Table 15
footnote (2), and adding in its place ``See Definition 1.42.''
42. Removing, in section 3.9.1a., ``430.22'' and adding in its
place ``430.3.''
43. Revising section 3.9.2 paragraph a., section 3.10, section
3.11.1.1 paragraph a., and 3.11.1.3 paragraph a.
44. Removing, in section 3.11.1.3, paragraph b., ``430.22'' and
adding in its place ``430.3'' in three locations.
45. Revising, in section 3.11.2, paragraph a.
46. Removing, in section 3.11.2, paragraph b., ``430.22'' and
adding in its place ``430.3.''
47. Removing, in section 3.11.3, ``430.22'' and adding in its place
``430.3.''
48. Adding new sections 3.13, 3.13.1, 3.13.2, 3.13.2.1, 3.13.2.2,
3.13.3, 3.13.3.1, 3.13.3.2, 3.13.3.3, 3.13.3.4, 3.13.3.5, 3.13.4,
3.13.4.1, 3.13.4.2, 3.13.4.3, 3.13.4.4.1, 3.13.4.4.2, 3.13.4.4.3,
3.13.4.4.4, 3.13.4.4.5, 3.13.4.4.6, 3.13.4.4.7, 3.13.4.4.8, 3.13.4.5,
3.13.4.6, 3.13.5, 3.13.5.1, 3.13.5.2, 3.13.5.33.13.5.4, 3.13.5.4.1,
3.13.5.4.2, 3.13.5.43, 3.13.5.4.4, 3.13.5.4.5, 3.13.5.5, 3.13.5.5.1,
3.13.5.5.2, 3.13.5.5.3, 3.13.5.6, and 3.13.5.7.
(d) In section 4, Calculations of Seasonal Performance Descriptors,
by:
1. Revising, in section 4.1, the introductory text before equation
(4.1-2), and the text following equation (4.1-2).
2. Revising section 4.1.1.
3. Adding, in section 4.1.3, at the end of the first sentence ``,
including triple-capacity northern heat pumps''.
4. Revising, in section 4.1.4.2, the definitions of T1 and T2
following equation for calculating B.
5. Adding new sections 4.1.5, 4.1.5.1, 4.1.5.2, 4.1.6, 4.1.6.1,
4.1.6.2, 4.1.6.2.1, 4.1.6.2.2, 4.1.6.3, and 4.1.6.4.
6. Adding, in section 4.2, item 4 in the numbered list following
the equation for DHRmax, and revising the sentence preceding
Table 18.
7. Revising, in section 4.2.4.2, the definition of T4 following the
equation for A.
8. Adding new sections 4.2.6, 4.2.6.1, 4.2.6.2, 4.2.6.3, 4.2.6.4,
4.2.6.5, 4.2.6.6, 4.2.6.7, 4.2.6.8, 4.2.7, 4.2.7.1, 4.2.7.2, 4.2.8,
4.2.8.1, 4.2.8.1.1, 4.2.8.1.2, 4.2.8.1.3, 4.2.8.2, 4.2.8.2.1,
4.2.8.2.2, 4.2.8.3, 4.2.8.3.1, and 4.2.8.3.2.
9. Revising, in section 4.3.1, the equation which immediately
follows the introductory text, and adding new text at the end of the
last sentence.
10. Revising sections 4.3.2 and 4.4, and adding a new section 4.5.
The additions and revisions 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
* * * * *
1.32 Off mode means:
(1) For air conditioners, all times during the non-cooling
season of an air conditioner. This mode includes the ``shoulder
seasons'' between the cooling and heating seasons when the unit
provides no cooling to the building and the entire heating season,
when the unit is idle. The air conditioner is assumed to be
connected to its main power source at all times during the off mode;
and
(2) For heat pumps, all times during the non-cooling and non-
heating seasons of a heat pump. This mode includes the ``shoulder
seasons'' between the cooling and heating seasons when the unit
provides neither heating nor cooling to the building. The heat pump
is assumed to be connected to its main power source at all times
during the off mode.
* * * * *
1.35 Seasonal Energy Efficiency Ratio--Hot Dry (SEER-HD) means
the total heat removed from the conditioned space during the annual
cooling season for the designated hot-dry climatic region, expressed
in Btus, divided by the total electrical energy consumed by the air
conditioner or heat pump during the same season, expressed in watt-
hours. Calculate SEER-HD as specified in section 4.1.6 of this
Appendix.
* * * * *
1.46 Triple-capacity (or triple-stage) compressor means an air
conditioner or heat pump with one of the following:
(1) A three-speed compressor,
(2) Two compressors where one is a two-capacity compressor--as
defined in section 1.45--and one is a single-speed compressor where
the two-capacity compressor operates at both low and high capacity
with the single-speed compressor turned off and then operates
exclusively at high capacity when the single speed compressor is
turned on, or
(3) A compressor capable of cylinder or scroll unloading to
provide a total of three levels of compressor capacity.
For such systems, low capacity means:
(1) Operating at the low compressor speed,
(2) Operating the two-capacity compressor at low capacity with
the single-speed compressor turned off, and
(3) Operating with the compressor fully unloaded.
For such systems, high capacity means:
(1) Operating at the high compressor speed,
(2) Operating the two-capacity compressor at high capacity with
the single-speed compressor turned off, and
(3) Operating with the compressor partially unloaded.
For such systems, booster capacity means:
(1) Operating at the booster compressor speed,
(2) Operating the two-capacity compressor at high capacity with
the single-speed compressor turned on, and
(3) Operating the compressor fully loaded.
1.47 Triple-capacity northern heat pump means a heat pump that
provides two stages of cooling and three stages of heating. The two
common stages for both the cooling and heating modes are the low
capacity stage and the high capacity stage. The additional heating
mode stage is called the booster capacity stage. Of the three
heating mode stages, the booster capacity stage offers the highest
heating capacity output for a given set of ambient operating
conditions.
* * * * *
2. Testing Conditions
* * * * *
2.2 Test unit installation requirements.
a. Except as noted in this appendix, install the unit according
to section 8.2 of ASHRAE Standard 37-2005 (incorporated by
reference, see Sec. 430.3) where references to ``manufacturer's
installation instructions'' shall mean the installation instructions
that come packaged with the unit. If the particular model of air
conditioner or heat pump is not yet in production, the installation
instructions used must be written and saved until they are confirmed
as being consistent with the instructions that are thereafter
packaged with the full production model. With respect to
interconnecting tubing used when testing split systems, follow the
requirements in section 6.1.3.5 of AHRI Standard 210/240-2008
(incorporated by reference, see Sec. 430.3). When testing triple-
split systems (see Definition 1.48), use the tubing length specified
in section 6.1.3.5 of AHRI Standard 210/240-2008 (incorporated by
reference, see Sec. 430.3) 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 split systems having multiple indoor coils, connect
each indoor fan-coil to the outdoor unit using 25 feet of tubing or
manufacturer-furnished tubing, whichever is longer. If needed to
make a secondary measurement of capacity, install refrigerant
pressure measuring instruments as described in section 8.2.5 of
ASHRAE Standard 37-2005 (incorporated by reference, see Sec.
430.3). Refer to section 2.10 of this Appendix to learn which
secondary methods require refrigerant pressure measurements. At a
minimum, insulate the low-pressure line(s) of a split system with
insulation having an inside diameter that matches the refrigerant
tubing and a nominal thickness of 0.5 inch.
* * * * *
d. When testing coil-only air conditioners and heat pumps,
install a nominal 24-V transformer to power the low-voltage
components of the system. The transformer must have a load rating of
either 40 or 50 V-amps and must be designed to operate with a
primary input that is 230 V, single phase, 60 Hz. The transformer
may be powered from the same source as supplies powered to the
outdoor unit or powered by a separate 230-V source. The power
consumption of the added low-voltage transformer must be measured as
part of the total system power consumption during all tests.
[[Page 31250]]
e. If the manufacturer's installation instructions include steps
that apply to a hot-dry climate different from the steps that apply
for a mixed climate, apply these differing installation steps in
advance of conducting the laboratory tests that apply for the
respective climates.
f. For third-party testing conducted to meet DOE certification
requirements, the working relationship between the test laboratory
and the manufacturer shall not be restricted as long as the test
unit installation and laboratory testing are conducted in complete
compliance with the procedures specified in this appendix.
* * * * *
2.2.1 Defrost control settings. Set heat pump defrost controls
at the normal settings which most typify those encountered in
generalized climactic 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 1.44), the
manufacturer must specify the frosting interval to be used during
the 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.
* * * * *
2.2.3 Special requirements for systems that would normally
operate using two or more indoor thermostats, including multi-split
air conditioners and heat pumps, systems composed of multiple mini-
split units (outdoor units located side-by-side), and ducted systems
using a single indoor section containing multiple blowers. Because
these types of systems will have more than one indoor fan and
possibly multiple outdoor fans and compressor systems, references in
this test procedure to a single indoor fan, outdoor fan, and
compressor mean all indoor fans, all outdoor fans, and all
compressor systems turned on during the test.
2.2.3.1 Additional requirements for multi-split air conditioners
and heat pumps and systems composed of multiple mini-split units.
For any test where the system is operated at part load (i.e., one or
more compressors ``off,'' operating at the intermediate or minimum
compressor speed or at low compressor capacity), the manufacturer
shall designate the particular indoor coils that are turned off
during the test. For variable-speed systems, the manufacturer must
designate at least one indoor unit that is turned off for all tests
conducted at minimum compressor speed. For all other part-load
tests, the manufacturer shall choose to turn off zero, one, two, or
more indoor units. The chosen configuration shall remain unchanged
for all tests conducted at the same compressor speed/capacity. For
any indoor coil turned off during a test, take steps to cease forced
airflow through this indoor coil and block its outlet duct.
2.2.3.2 Additional requirements for ducted systems with a single
indoor section containing multiple blowers where the blowers are
designed to cycle on and off independently of one another and are
not controlled such that all blowers are modulated to always operate
at the same air volume rate or speed. This Appendix covers systems
with a single-speed compressor or systems offering two fixed stages
of compressor capacity (e.g., a two-speed compressor, two single-
speed compressors). For any test where the system is operated at its
lowest capacity--i.e., the lowest total air volume rate allowed when
operating the single-speed compressor or when operating at low
compressor capacity--blowers accounting for at least one-third of
the full-load air volume rate must be turned off unless prevented by
the controls of the unit. In such cases, turn off as many blowers as
permitted by the unit's controls. Where more than one option exists
for meeting this ``off'' blower requirement, the manufacturer shall
choose which blower(s) are turned off. The chosen configuration
shall remain unchanged for all tests conducted at the same lowest
capacity configuration. For any indoor coil turned off during a
test, take steps to cease forced airflow through any outlet duct
connected to an ``off'' blower.
* * * * *
2.2.5 Additional refrigerant charging requirements. The test
unit shall be charged in accordance with both the following
instructions and the manufacturer's installation instructions
described in section 2.2.
If the manufacturer's installation instructions specify as part
of a standard installation and/or commissioning practice to either
alter or check the refrigerant charge while the unit is operating,
the testing laboratory shall do so in conjunction with establishing
the cooling full-load air volume rate (see section 3.1.4.1) and
operating entering air conditions specified in the A (or A2) Test.
For heating-only heat pumps, this refrigerant charge evaluation and
potential adjustment step shall be done in conjunction with
establishing the heating full-load air volume rate (see section
3.1.4.4) and operating entering air conditions specified for the H1
(or H12) Test. For the entering db and wb air temperature conditions
noted above, determine from the manufacturer's installation
instructions the target value(s) for the system's measurable
operating parameter(s)--e.g., suction superheat temperature, liquid
line subcooling temperature, refrigerant suction pressure, etc. If
the manufacturer's installation instructions list a range for a
particular parameter, use the midpoint value as the target value.
The testing laboratory shall add or subtract the correct amount of
refrigerant to achieve as closely as possible the target value(s).
If a unit requires charging but the manufacturer's 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 or more sets of
refrigerant charging criteria, use the set most appropriate for a
normal field installation.
Once the test unit has been properly charged with refrigerant,
all cooling mode and, if a heat pump, all heating mode-laboratory
tests shall be conducted, and the testing laboratory shall not add
or subtract any more refrigerant to or from the test unit.
* * * * *
2.4.1 * * *
* * * * *
b. For systems having multiple indoor coils or multiple indoor
blowers within a single indoor section, attach a plenum to each
indoor coil or blower outlet. * * *
* * * * *
2.5.5 * * *
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 06)
(incorporated by reference, see Sec. 430.3). The transient testing
requirements cited in section 4.3 of ASHRAE Standard 41.1-86 (RA 06)
apply if conducting a cyclic or frost accumulation test. If the
temperature sensors used to measure the indoor-side dry bulb
temperature difference are different for steady-state tests and
cyclic tests; in addition, the two sets of instrumentation must be
correlated as described in section 3.4 for cooling mode tests and
section 3.8 for heating mode tests.
* * * * *
3. Testing Procedures
3.1 * * * Use the testing procedures in this section to collect
the data used for calculating (1) the seasonal performance ratings
for air conditioners and heat pumps during the cooling season; (2)
the seasonal performance ratings for heat pumps during the heating
season; and (3) the seasonal off-mode power consumption rating(s)
for air conditioners and heat pumps during the parts of the year not
captured by the cooling and heating seasonal performance
descriptors. For air conditioners, the non-cooling seasons are the
heating season and the shoulder seasons that separate the cooling
and heating seasons. For heat pumps, the collective shoulder season
is the only time of the year where a seasonal off-mode power
consumption rating applies.
* * * * *
3.1.4.1.1 * * *
a. * * *
* * * * *
6. If the conditions of step 4b occur first, make an incremental
change to the set-up of the indoor fan that increases air volume
rate while maintaining the same operating features (e.g., next
highest fan motor pin setting that maintains the same fan delay
interval, next highest fan motor speed) and repeat the evaluation
process beginning with the above step 1. * * *
* * * * *
[[Page 31251]]
Table 2--Minimum External Static Pressure for Ducted Systems Tested With an Indoor Fan Installed
----------------------------------------------------------------------------------------------------------------
Minimum external resistance \3\ in wc
-----------------------------------------------
Rated Cooling \1\ or Heating \2\ Capacity Btu/h Multi-split All other
SDHV 4,5 systems systems
----------------------------------------------------------------------------------------------------------------
<=28,800........................................................ 1.10 0.03 0.10
29,000-42,500................................................... 1.15 0.05 0.15
>=43,000........................................................ 1.20 0.07 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 H12 Test conditions.
\3\ For ducted units tested without an air filter installed, increase the applicable tabular value by 0.08 inch
of water.
\4\ See Definition 1.37 to determine if the equipment qualifies as a small-duct, high-velocity system.
\5\ If a closed-loop, air-enthalpy test apparatus is used on the indoor side, limit the resistance to airflow on
the inlet side of the indoor blower coil to a maximum value of 0.1 inch of water. Impose the balance of the
airflow resistance on the outlet side of the indoor blower.
d. For systems having multiple blower coil indoor units, conduct
the above section 3.1.4.1.1 setup steps for each indoor unit
separately. If two or more indoor units are connected to a common
duct as per section 2.4.1, either turn off the other indoor units
connected to the same common duct or temporarily divert their air
volume to the test room when confirming or adjusting the setup
configuration of individual indoor units. If the indoor units are
all the same size or model, the target air volume rate for each
indoor unit equals the full-load air volume rate divided by the
number of indoor units. If different size indoor units are used, the
manufacturer must allocate the system's full-load air volume rate
assigned to each indoor unit during this set-up phase.
e. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the full-load air volume rate with all
blowers operating unless prevented by the controls of the unit. In
such cases, turn on the maximum number of blowers permitted by the
unit's controls. Where more than one option exists for meeting this
``on'' blower requirement, the manufacturer shall choose which
blower(s) are turned on. Conduct section 3.1.4.1.1 setup steps for
each blower separately. If two or more indoor blowers are connected
to a common duct as per section 2.4.1, either turn off the other
indoor blowers connected to the same common duct or temporarily
divert their air volume to the test room when confirming or
adjusting the setup configuration of individual blowers. If the
indoor blowers are all the same size or model, the target air volume
rate for each blower plenum equals the full-load air volume rate
divided by the number of ``on'' blowers. If different size blowers
are used within the indoor section, the manufacturer must allocate
the system's full-load air volume rate assigned to each ``on''
blower.
* * * * *
3.1.4.2 * * *
* * * * *
e. For ducted systems having multiple indoor blowers within a
single indoor section, operate the indoor blowers such that the
lowest air volume rate allowed by the unit's controls is obtained
when operating the lone single-speed compressor or when operating at
low compressor capacity while meeting the requirements of section
2.2.3.2 for the minimum number of blowers that must be turned off.
The air volume rate for each ``on'' blower must then be determined
using the first section 3.1.4.2 equation if the blower operates at
fixed fan speeds or must be specified by the manufacturer if the
blower is designed to provide a constant air volume rate. The sum of
the individual ``on'' blowers' air volume rates is the cooling
minimum air volume rate for the system.
* * * * *
3.1.4.4.2 * * *
* * * * *
c. When testing ducted, two-capacity northern heat pumps (see
Definition 1.50), use the appropriate approach of the above two
cases for units that are installed with an indoor fan installed. For
coil-only (fanless) northern heat pumps, the Heating Full-Load Air
Volume Rate is the lesser of the rate specified by the manufacturer
or 133 percent of the Cooling Full-Load Air Volume Rate. For this
latter case, obtain the Heating Full-Load Air Volume Rate regardless
of the pressure drop across the indoor coil assembly.
d. For systems having multiple indoor blower coil units where
individual blowers regulate the speed (as opposed to the cfm) of the
indoor fan, use the first section 3.1.4.4.2 equation for each blower
coil individually. Sum the individual blower coil air volume rates
to obtain the heating full-load air volume rate for the system.
e. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the heating full-load air volume rate
using the same ``on'' blowers as used for the cooling full-load air
volume rate. For systems where individual blowers regulate the speed
(as opposed to the cfm) of the indoor fan, use the first section
3.1.4.4.2 equation for each blower individually. Sum the individual
blower air volume rates to obtain the heating full-load air volume
rate for the system.
* * * * *
3.1.4.4.3 * * *
a. * * *
6. If the conditions of step 4b occur first, make an incremental
change to the set-up of the indoor fan that increases air volume
rate while maintaining the same operating features (e.g., next
highest fan motor pin setting that maintains the same fan delay
interval, next highest fan motor speed) and repeat the evaluation
process beginning with the above step 1. * * *
* * * * *
3.1.4.5 * * *
* * * * *
f. For ducted systems with multiple indoor blowers within a
single indoor section, obtain the heating minimum air volume rate
using the same ``on'' blowers as used for the cooling minimum air
volume rate. For systems where individual blowers regulate the speed
(as opposed to the cfm) of the indoor fan, use the first section
3.1.4.5 equation for each blower individually. Sum the individual
blower air volume rates to obtain the heating minimum air volume
rate for the system.
* * * * *
3.2.1 * * *
* * * * *
In order to evaluate the cooling season performance of the test
unit when applied in a hot-dry climate, conduct one steady-state
test, the AD Test. Conducting an additional steady-state, dry
climate test (the BD Test) is optional. Test conditions for the two
dry climate tests are specified in Table 3A.
[[Page 31252]]
Table 3a--Dry Climate 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 Air entering outdoor
unit temperature unit temperature
[deg]F [deg]F
Test description -------------------------------------------- Dry climate air volume rate
Wet bulb
Dry bulb Wet bulb Dry bulb \1\
----------------------------------------------------------------------------------------------------------------
AD Test--required (steady)........... 80 64 95 75 Dry-Climate Full-Load.
BD Test--optional (steady)........... 80 64 82 65 Dry-Climate Full-Load.
----------------------------------------------------------------------------------------------------------------
\1\The specified test condition only applies if the unit rejects condensate to the outdoor coil.
As an alternative to conducting the optional BD Test, use the
following equations to approximate the capacity and electrical power
of the test unit at the BD test conditions:
QHD (82) = QHD (95) + MDQ x (82 - 95)
EHD (82) = EHD (95) + MDE x (82 - 95)
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.241
In evaluating the above equations, determine the quantities QHD
(95) and EHD (95) from the AD Test. Determine the quantities Qc (82)
and Ec (82) from the B Test and the quantities Qc (95) and Ec (95)
from the A Test. Evaluate all six quantities according to section
3.3. If the manufacturer conducts the BD Test, the option of using
the above default equations is not forfeited. Use the paired values
of QHD (82) and EHD (82) derived from conducting the BD Test and
evaluated as specified in section 3.3 or use the paired values
calculated using the above default equations, whichever contribute
to a higher SEER-HD.
Determine and obtain the dry-climate full-load air volume rate
used for the AD and BD Tests as specified in section 3.1.4.1 for the
cooling full-load air volume rate, only now replacing references to
the A Test and cooling full-load with references to the AD Test and
the dry-climate full load.
3.2.2 Tests for a unit with a single-speed compressor where the
indoor section uses a single variable-speed variable-air-volume rate
indoor fan or multiple blowers.
3.2.2.1 Indoor fan capacity modulation that correlates with
outdoor dry-bulb temperature or systems with a single indoor coil
but multiple blowers. Conduct four steady-state wet-coil tests: the
A2, A1, B2, and B1 Tests. Use the two optional dry-coil tests, the
steady-state C1 Test and the cyclic D1 Test to determine the cooling
mode cyclic-degradation coefficient, CDc . If the two optional tests
are conducted but yield a tested CDc that exceeds the default CDc or
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.
Table 4--Cooling Mode Test Conditions for Air Conditioners and Heat Pumps With a Single-Speed Compressor That
Meet the Section 3.2.2.1 Indoor Unit Requirements
----------------------------------------------------------------------------------------------------------------
Air entering indoor Air entering outdoor
unit temperature unit temperature
Test description [deg]F [deg]F Cooling air volume rate
--------------------------------------------
Dry bulb Wet bulb Dry bulb Wet bulb
----------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet 80 67 95 \1\ 75 Cooling Full-Load.\2\
coil).
A1 Test--required (steady, wet 80 67 95 \1\ 75 Cooling Minimum.\3\
coil).
B2 Test--required (steady, wet 80 67 82 \1\ 65 Cooling Full-Load.\2\
coil).
B1 Test--required (steady, wet 80 67 82 \1\ 65 Cooling Minimum.\3\
coil).
C1 Test\4\--optional (steady, 80 (\4\) 82 -- Cooling Minimum.\3\
dry coil).
D1 Test\4\--optional (cyclic, 80 (\4\) 82 -- (\5\)
dry coil).
----------------------------------------------------------------------------------------------------------------
\1\The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ Defined in section 3.1.4.2.
\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 wet-bulb temperature of 57 [deg]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.
In order to evaluate the cooling season performance of the test
unit when applied in a hot-dry climate, conduct two steady-state
tests (the AD2 and the AD1). Two additional steady-state, hot-dry-
climate tests (the BD2 Test and the BD1 Test) are optional. Test
conditions for the four dry climate tests are specified in Table 4a.
As an alternative to conducting the optional BD2 and BD1 Tests, use
the following equations to approximate the capacity and electrical
power of the test unit at the BD2 (k=2) and BD1 (k=1) test
conditions:
[[Page 31253]]
[GRAPHIC] [TIFF OMITTED] TP02JN10.242
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.243
In evaluating the above equations for k=2 (dry-climate full-load
air volume rate) and k=1 (dry-climate minimum air volume rate),
determine the quantities QHDk=2 (95) and EHDk=2 (95) from the AD2
Test and the quantities QHDk=1 (95) and EHDk=1 (95) from the AD1
Test. Determine the quantities Qck=2 (95) and ECk=2 (95) from the A2
Test, the quantities Qck=1 (95) and Eck=1 (95) from the A1 Test, the
quantities Qck=2 (82) and ECk=2 (82) from the B2 Test, and the
quantities Qck=1 (82) and Eck=1 (82) from the B1 Test. Evaluate all
12 quantities according to section 3.3. If the manufacturer conducts
either or both the BD2 and BD1 Tests, the option of using the above
default equations is not forfeited. Use the paired values of QHDk=2
(82) and EHDk=2 (82) derived from conducting the BD2 Test and
evaluated as specified in section 3.3 or use the paired values
calculated using the above default equations, whichever contribute
to a higher SEER-HD. Similarly, use the paired values of QHDk=1 (82)
and EHDk=1 (82) derived from conducting the BD1 Test and evaluated
as specified in section 3.3 or use the paired values calculated
using the above default equations, whichever contribute to a higher
SEER-HD.
Determine and obtain the dry-climate full-load air volume rate
used for the AD2 and BD2 Tests as specified in section 3.1.4.1 for
the cooling full-load air volume rate, only now replacing references
to the A2 Test and cooling full-load with references to the AD2 Test
and the dry-climate full-load. Similarly, determine and obtain the
dry-climate minimum air volume rate used for the AD1 and BD1 Tests
specified in section 3.1.4.2 for the cooling minimum air volume
rate, only now replacing references to the A1 Test, B1 Test, A2
Test, B2 Test, cooling full-load, cooling minimum, and [Delta]Pst,A2
with references to the AD1 Test, BD1 Test, AD2 Test, BD2 Test, dry-
climate full-load, dry-climate minimum, and [Delta]Pst,AD2,
respectively.
Table 4a--Dry Climate Cooling Mode Test Conditions for Air Conditioners and Heat Pumps With a Single-Speed
Compressor That Meets the Section 3.2.2.1 Indoor Unit Requirements
----------------------------------------------------------------------------------------------------------------
Air entering indoor Air entering outdoor
unit temperature unit temperature
Test description [deg]F [deg]F Dry climate air volume rate
--------------------------------------------
Dry bulb Wet bulb Dry bulb Wet bulb
----------------------------------------------------------------------------------------------------------------
AD2 Test-required (steady)..... 80 64 95 75 Dry-Climate Full-Load.
AD1 Test-required (steady)..... 80 64 95 75 Dry-Climate Minimum.
BD2 Test-optional (steady)..... 80 64 82 65 Dry-Climate Full-Load.
BD1 Test-optional (steady)..... 80 64 82 65 Dry-Climate Minimum.
----------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
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 full-load 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.
3.2.3 Tests for a unit having a two-capacity compressor (see
Definition 1.49). * * *
* * * * *
c. Test two-capacity, northern heat pumps (see Definition 1.50)
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).
* * * * *
e. In order to evaluate the cooling season performance of the
test unit when applied in a hot-dry climate, conduct two steady-
state tests, the AD2 and the BD1. Conducting two additional steady-
state, dry-climate tests (the BD2 and the FD1) are optional. Test
conditions for the four dry climate tests are specified in Table 5a.
As an alternative to conducting the optional BD2 Test, use the
following equations to approximate the capacity and electrical power
of the test unit at the BD2 test conditions:
[GRAPHIC] [TIFF OMITTED] TP02JN10.244
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.245
[[Page 31254]]
In evaluating the above equations, determine the quantities QHDk=2
(95) and EHDk=2 (95) from the AD2 Test. Determine the quantities Qck=2
(95) and ECk=2 (95) from the A2 Test and the quantities Qck=2 (82) and
Eck=2 (82) from the B2 Test. Evaluate all six quantities according to
section 3.3. If the manufacturer conducts the BD2 Test, the option of
using the above default equations is not forfeited. Use the paired
values of QHDk=2 (82) and EHDk=2 (82) derived from conducting the BD2
Test and evaluated as specified in section 3.3 or use the paired values
calculated using the above default equations, whichever paired values
contribute to a higher SEER-HD.
As an alternative to conducting the optional FD1 Test, use the
following equations to approximate the capacity and electrical power of
the test unit at the FD1 Test conditions:
[GRAPHIC] [TIFF OMITTED] TP02JN10.246
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.247
In evaluating the above equations, determine the quantities QHDk=1
(82) and EHDk=1 (82) from the BD1 Test. Determine the quantities Qck=1
(82) and ECk=1 (82) from the B1 Test and the quantities Qck=1 (67) and
Eck=1 (67) from the F1 Test. Evaluate all six quantities according to
section 3.3. If the manufacturer conducts the FD1 Test, the option of
using the above default equations is not forfeited. Use the paired
values of QHDk=1 (67) and EHDk=1 (67) derived from conducting the FD1
Test and evaluated as specified in section 3.3 or use the paired values
calculated using the above default equations, whichever contribute to a
higher SEER-HD.
Determine and obtain the dry-climate full-load air volume rate used
for the AD2 and BD2 Tests as specified in section 3.1.4.1 for the
cooling full-load air volume rate, only now replacing references to the
A2 Test and cooling full-load with references to the AD2 Test and the
dry-climate full-load. Similarly, determine and obtain the dry-climate
minimum air volume rate used for the BD1 and FD1 Tests as specified in
section 3.1.4.2 for the cooling minimum air volume rate, only now
replacing references to the B1 Test, F1 Test, A2 Test, cooling full
load, cooling minimum, and [Delta]Pst,A2 with references to the BD1
Test, FD1 Test, AD2 Test, dry-climate full-load, dry-climate minimum,
and [Delta]Pst,AD2, respectively.
Table 5a--Dry Climate Cooling Mode Test Conditions for Air Conditioners and Heat Pumps Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor
temperature [deg] F unit temperature [deg]
Test description -------------------------- F Compressor capacity Dry climate air volume rate
--------------------------
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
AD2 Test--required (steady).............. 80 64 95 75 High........................ Dry-Climate Full-Load.
BD2 Test--optional (steady).............. 80 64 82 65 High........................ Dry-Climate Full-Load.
BD1 Test--required (steady).............. 80 64 82 65 Low......................... Dry-Climate Minimum.
FD1 Test--optional (steady).............. 80 64 67 53.5 Low......................... Dry-Climate Minimum.
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
3.2.4 * * *
* * * * *
d. In order to evaluate the cooling season performance of the test
unit when applied in a hot-dry climate, conduct two steady-state tests,
the AD2 Test and the BD1 Test. Conducting two additional steady-state,
dry climate tests (the BD2 and the FD1) are optional. Test conditions
for the four dry climate tests are specified in Table 5a, only now
substituting ``Maximum'' and ``Minimum'' for the Compressor Capacity
entries of ``High'' and ``Low,'' respectively. As an alternative to
conducting the optional BD2 and FD1 Tests, use the equations given in
section 3.2.3 to approximate the capacity and electrical power of the
test unit at the BD2 and FD1 test conditions.
3.2.5 Tests for a unit having a triple-capacity compressor
(Definition 1.46). With the exception of triple-capacity northern heat
pumps (Definition 1.47), no other units having a triple-capacity
compressor are currently addressed within this test procedure. Test
triple-capacity, northern heat pumps for the cooling mode in the same
way as specified in section 3.2.3 for units having a two-capacity
compressor.
3.2.6 Tests for an air conditioner or heat pump having a single
indoor unit having multiple blowers and offering two stages of
compressor modulation. Conduct the cooling mode tests specified in
section 3.2.3. Covered multiple blower systems have a single indoor
coil connected to a single outdoor unit offering two stages of capacity
modulation, and ones with a single indoor coil having two refrigerant
circuits where each circuit is connected
[[Page 31255]]
to separate but identical outdoor units, each having a single-speed
compressor.
3.3 * * *
* * * * *
b. After satisfying the pretest equilibrium requirements, make the
measurements specified in Table 3 of ASHRAE Standard 37-2005
(incorporated by reference, see Sec. 430.3) for the Indoor Air
Enthalpy method and the user-selected secondary method. Make the Table
3 measurements at equal intervals that span 5 minutes or less. Continue
data sampling until reaching a 30-minute period (e.g., seven
consecutive 5-minute 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 and sensible cooling
capacity as specified in sections 7.3.3.1 and 7.3.3.3 of ASHRAE
Standard 37-2005 (incorporated by reference, see Sec. 430.3). Do not
adjust the parameters used in calculating the capacities for the
permitted variations in test conditions. Evaluate air enthalpies based
on the measured barometric pressure for calculation of the total
cooling capacity. Use the values of the specific heat of air given in
section 7.3.3.1 for calculation of the sensible cooling capacities.
Assign the average total space cooling capacity, average sensible
cooling capacity, and average electrical power consumption over the 30-
minute data collection interval to the variables Qck(T), Qsck(T), and
Eck(T), respectively. For these three variables, replace 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.
* * * * *
3.4 * * *
* * * * *
b. If the temperature sensors used to provide the primary
measurement of the indoor-side dry bulb temperature difference during
the steady-state dry-coil test and the subsequent cyclic dry-coil test
are different, include measurements of the latter sensors among the
regularly sampled data. Beginning at the start of the 30-minute data
collection period, measure and compute the indoor-side air dry-bulb
temperature difference using both sets of instrumentation, [Delta]T
(Set SS) and [Delta]T (Set CYC), for each equally spaced data sample.
If using a consistent data sampling rate that is less than 1 minute,
calculate and record minutely averages for the two temperature
differences. If using a consistent sampling rate of one minute or more,
calculate and record the two temperature differences from each data
sample. After having recorded the seventh (i=7) set of temperature
differences, calculate the following ratio using the first seven sets
of values:
[GRAPHIC] [TIFF OMITTED] TP02JN10.248
Each time a subsequent set of temperature differences is recorded
(if sampling more frequently than every 5 minutes), calculate FCD using
the most recent seven sets of values. Continue these calculations until
the 30-minute period is completed or until a value for FCD is
calculated that falls outside the allowable range of 0.94-1.06. If the
latter occurs, immediately suspend the test and identify the cause for
the disparity in the two temperature difference measurements.
Recalibration of one or both sets of instrumentation may be required.
If all the values for FCD are within the allowable range, save the
final value of the ratio from the 30-minute test as FCD*.
If the temperature sensors used to provide the primary measurement
of the indoor-side dry bulb temperature difference during the steady-
state dry-coil test and the subsequent cyclic dry-coil test are the
same, set FCD* = 1.
* * * * *
3.5 * * *
* * * * *
i. * * *
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.249
and, V, Cp,a, Vn (or vn), Wn, and FCD* = the values
recorded during the section 3.4 dry coil steady-state tests,
and Ta1([tau]) = dry-bulb temperature of the air entering the indoor
coil at time [tau], [deg]F.
* * * * *
3.6.2 Tests for a heat pump having a single-speed compressor and a
single indoor unit having either (1) a variable-speed, variable-air-
rate indoor fan whose capacity modulation correlates with outdoor dry
bulb temperature or (2) multiple blowers. * * *
* * * * *
Table 10--Heating Mode Test Conditions for Heat Pumps With a Single-
Speed Compressor That Meet the Section 3.6.2 Indoor Unit Requirements *
* *
* * * * *
As an alternative to conducting the optional H21 Frost Accumulation
Test, use the following equations to approximate the capacity and
electrical power of the heat pump at the H21 test conditions:
[GRAPHIC] [TIFF OMITTED] TP02JN10.250
Where:
[[Page 31256]]
[GRAPHIC] [TIFF OMITTED] TP02JN10.251
In evaluating the above equations, determine the quantities
Qhk=2(47) and Ehk=2(47) from the H12 Test,
determine the quantities Qhk=1(47) and Ehk=1(47)
from the H11 Test, and evaluate all four quantities according to
section 3.7. Determine the quantities Qhk=2(35) and
Ehk=2(35) from the H22 Test and evaluate them according to
section 3.9. Determine the quantities Qhk=2(17) and
Ehk=2(17) from the H32 Test, determine the quantities
Qhk=1(17) and Ehk=1(17) from the H31 Test, and
evaluate all four quantities according to Section 3.10. If the
manufacturer conducts the H21 Test, the option of using the above
default equations is not forfeited. Use the paired values of
Qhk=1(35) and Ehk=1(35) derived from conducting
the H21 Frost Accumulation Test and evaluated as specified in section
3.9 or use the paired values calculated using the above default
equations, whichever contribute to a higher Region IV HSPF based on the
DHRmin.
* * * * *
3.6.3 * * *
a. * * * If the manufacturer conducts the H21 Test, the option of
using the above default equations is not forfeited. Use the paired
values of Qhk=1(35) and Ehk=1(35) derived from
conducting the H21 Frost Accumulation Test and calculated as specified
in section 3.9 or use the paired values calculated using the above
default equations, whichever contribute to a higher Region IV HSPF
based on the DHRmin.
* * * * *
3.6.4 * * *
a. * * *
b. As an alternative to conducting the optional H22 Frost
Accumulation Test, use the following equations to approximate the
capacity and electrical power of the heat pump at the H22 test
conditions:
[GRAPHIC] [TIFF OMITTED] TP02JN10.252
In evaluating the above equations, determine the quantities
Qhk=2(47) and Ehk=2(47) from the H12 Test and
evaluate them according to section 3.7. Determine the quantities
Qhk=2(17) and Ehk=2(17) from the H32 Test and
evaluate them according to section 3.10. If the manufacturer conducts
the H22 Test, the option of using the above default equations is not
forfeited. Use the paired values of Qhk=2(35) and
Ehk=2(35) derived from conducting the H22 Frost Accumulation
Test and evaluated as specified in section 3.9 or use the paired values
calculated using the above default equations, whichever contribute to a
higher Region IV HSPF based on the DHRmin.
c. For heat pumps where the heating mode maximum compressor speed
exceeds their 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 used for the cooling
mode A2 Test. Refer to the last sentence of section 4.2 for how the
results of the H1N Test may be used in calculating the HSPF.
d. For multiple-split heat pumps (only), the following procedures
supersede the above requirements. * * *
* * * * *
3.6.6 Tests for a heat pump having a triple-capacity compressor
(Definition 1.46). With the exception of triple-capacity northern heat
pumps (Definition 1.47), no other heat pumps having a triple-capacity
compressor are currently addressed within this test procedure. Test
triple-capacity, northern heat pumps for the heating mode as follows:
(a) Conduct one maximum-temperature test (H01), two high-
temperature tests (H12 and H11), one Frost Accumulation test (H22), two
low-temperature tests (H32, H33), and one minimum-temperature test
(H43). Conduct an additional Frost Accumulation test (H21) and low-
temperature test (H31) if both of the following conditions exist: (1)
Knowledge of the heat pump's capacity and electrical power at low
compressor capacity for outdoor temperatures of 37 [deg]F and less is
needed to complete the section 4.2.6 seasonal performance calculations;
and (2) the heat pump's controls allow low-capacity operation at
outdoor temperatures of 37 [deg]F and less.
If the above two conditions are met, an alternative to conducting
the H21 Frost Accumulation Test to determine Qhk=1(35) and
Ehk=1(35) is to use the following equations to approximate
this capacity and electrical power:
[GRAPHIC] [TIFF OMITTED] TP02JN10.253
In evaluating the above equations, determine the quantities
Qhk=1(47) and Ehk=1(47) from the H11 Test and
evaluate them according to section 3.7. Determine the quantities
Qhk=1(17) and Ehk=1(17) from the H31 Test and
evaluate them according to section 3.10. If the manufacturer conducts
the H21 Test, the option of using the above default
[[Page 31257]]
equations is not forfeited. Use the paired values of
Qhk=1(35) and Ehk=1(35) derived from conducting
the H21 Frost Accumulation Test and evaluated as specified in section
3.9.1 or use the paired values calculated using the above default
equations, whichever contribute to a higher Region IV HSPF based on the
DHRmin.
(b) Conducting a Frost Accumulation Test (H23) with the heat pump
operating at its booster capacity is optional. If this optional test is
not conducted, determine Qhk=3(35) and Ehk=3(35)
using the following equations to approximate this capacity and
electrical power:
[GRAPHIC] [TIFF OMITTED] TP02JN10.254
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.255
Determine the quantities Qhk=2(47) and
Ehk=2(47) from the H12 Test and evaluate them according to
section 3.7. Determine the quantities Qhk=2(35) and
Ehk=2(35) from the H22 Test and evaluate them according to
section 3.9.1. Determine the quantities Qhk=2(17) and
Ehk=2(17) from the H32 Test, determine the quantities
Qhk=3(17) and Ehk=3(17) from the H33 Test, and
determine the quantities Qhk=3(2) and Ehk=3(2)
from the H43 Test. Evaluate all six quantities according to section
3.10. If the manufacturer conducts the H23 Test, the option of using
the above default equations is not forfeited. Use the paired values of
Qhk=3(35) and Ehk=3(35) derived from conducting
the H23 Frost Accumulation Test and calculated as specified in section
3.9.1 or use the paired values calculated using the above default
equations, whichever contribute to a higher Region IV HSPF based on the
DHRmin.
(c) Conduct the optional high-temperature cyclic test (H1C1) to
determine the heating-mode cyclic-degradation coefficient, CDh. If this
optional test is conducted but yields a tested CDh that exceeds the
default CDh or if the optional test is not conducted, assign CDh the
default value of 0.25. If a triple-capacity heat pump locks out low
capacity operation at lower outdoor temperatures, conduct the optional
high-temperature cyclic test (H1C2) to determine the high-capacity
heating-mode cyclic-degradation coefficient, CDh(k=2). If this optional
test at high capacity is conducted but yields a tested CDh(k=2) that
exceeds the default CDh(k=2) or if the optional test is not conducted,
assign CDh(k=2) the default value. The default CDh(k=2) is the same
value as determined or assigned for the low-capacity cyclic-degradation
coefficient, CDh [or equivalently, CDh(k=1)]. Finally, if a triple-
capacity heat pump locks out both low and high capacity operation at
the lowest outdoor temperatures, conduct the optional low-temperature
cyclic test (H3C3) to determine the booster-capacity heating-mode
cyclic-degradation coefficient, CDh(k=3). If this optional test at the
booster capacity is conducted but yields a tested CDh(k=3) that exceeds
the default CDh(k=3) or if the optional test is not conducted, assign
CDh(k=3)the default value. The default CDh(k=3) is the same value as
determined or assigned for the high-capacity cyclic-degradation
coefficient, CDh [or equivalently, CDh(k=2)]. Table A specifies test
conditions for all 13 tests.
Table A--Heating Mode Test Conditions for Units With a Triple-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering Air entering
indoor unit outdoor unit
Test description temperature [deg]F temperature [deg]F Compressor capacity Heating air volume rate
-----------------------------------------
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).............. 70 60(max) 62 56.5 Low......................... Heating Minimum.\1\
H12 Test (required, steady).............. 70 60(max) 47 43 High........................ Heating Full-Load.\2\
H1C2 Test (optional, cyclic)............. 70 60(max) 47 43 High........................ \3\
H11 Test (required)...................... 70 60(max) 47 43 Low......................... Heating Minimum.\1\
H1C1 Test (optional, cyclic)............. 70 60(max) 47 43 Low......................... \4\
H23 Test (optional, steady).............. 70 60(max) 35 33 Booster..................... Heating Full-Load.\2\
H22 Test (required)...................... 70 60(max) 35 33 High........................ Heating Full-Load.\2\
H21 Test 5 6 (required).................. 70 60(max) 35 33 Low......................... Heating Minimum.\1\
H33 Test (required, steady).............. 70 60(max) 17 15 Booster..................... Heating Full-Load.\2\
H3C3 Test (optional, cyclic)............. 70 60(max) 17 15 Booster..................... \7\
H32 Test (required, steady).............. 70 60(max) 17 15 High........................ Heating Full-Load.\2\
[[Page 31258]]
H31 Test \5\ (required, steady).......... 70 60(max) 17 15 Low......................... Heating Minimum.\1\
H43 Test (required, steady).............. 70 60(max) 2 1 Booster..................... Heating Full-Load.\2\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5.
\2\ Defined in section 3.1.4.4.
\3\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H12 Test.
\4\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H11 Test.
\5\ Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 [deg]F is needed to
complete the section 4.2.6 HSPF calculations.
\6\ If table note \5\ applies, the section 3.6.6 equations for Qhk=1(35) and Ehk=1(17) may be used in lieu of conducting the H21 Test.
\7\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H33 Test.
3.6.7 Tests for a heat pump having a single indoor unit having
multiple blowers and offering two stages of compressor modulation.
Conduct the heating mode tests specified in section 3.6.3. Covered
multiple blower systems have a single indoor coil connected to a single
outdoor unit offering two stages of capacity modulation and ones having
a single indoor coil having two refrigerant circuits where each circuit
is connected to separate but identical outdoor units, each having a
single-speed compressor.
3.7 * * *
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 external static pressure specified
for the particular test. Continuously record the dry-bulb temperature
of the air entering the outdoor coil. Refer to section 3.11 for
additional requirements that depend on the selected secondary test.
After satisfying the pretest equilibrium requirements, make the
measurements specified in Table 3 of ASHRAE Standard 37-2005
(incorporated by reference, see Sec. 430.3) for the Indoor Air
Enthalpy method and the user-selected secondary method. Make the Table
3 measurements at equal intervals that span 5 minutes or less. Continue
data sampling until a 30-minute period (e.g., seven consecutive 5-
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 Test condition
tolerance \1\ tolerance \2\
------------------------------------------------------------------------
Indoor dry-bulb, [deg]F
Entering temperature...... 2.0 0.5
Leaving temperature....... 2.0 ...................
Indoor wet-bulb, [deg]F
Entering temperature...... 1.0 ...................
Leaving temperature....... 1.0 ...................
Outdoor dry-bulb, [deg]F
Entering temperature...... 2.0 0.5
Leaving temperature....... \2\ 2.0
Outdoor wet-bulb, [deg]F
Entering temperature...... 1.0 0.3
Leaving temperature....... \3\ 1.0 ...................
External resistance to 0.12 \4\ 0.02
airflow, inches of water.....
Electrical voltage, % of rdg.. 2.0 1.5
Nozzle pressure drop, % of rdg 8.0 ...................
------------------------------------------------------------------------
\1\ See Definition 1.43.
\2\ See Definition 1.42.
\3\ Only applies when the Outdoor Air Enthalpy Method is used.
\4\ Only applies when testing non-ducted units.
b. Calculate indoor-side total heating capacity as specified in
sections 7.3.4.1 and 7.3.4.3 of ASHRAE Standard 37-2005 (incorporated
by reference, see Sec. 430.3). * * *
* * * * *
d. If conducting the optional cyclic heating mode test described in
section 3.8, record the average indoor-side air volume rate, V,
specific heat of the air,
[[Page 31259]]
Cp,a (expressed on a dry air basis), specific volume of the air at the
nozzles, vn[min] (or vn), humidity ratio at the nozzles, Wn,
and either pressure difference or velocity pressure for the flow
nozzles.
If the temperature sensors used to provide the primary measurement
of the indoor-side dry bulb temperature difference during the steady-
state dry-coil test and the subsequent cyclic dry-coil test are
different, include measurements of the latter sensors among the
regularly sampled data during the steady-state test. Beginning at the
start of the 30-minute data collection period, measure and compute the
indoor-side air dry bulb temperature difference using both sets of
instrumentation, [Delta]T(Set SS) and [Delta]T(Set CYC), for each
equally spaced data sample. If using a consistent data sampling rate
that is less than 1 minute, calculate and record minutely averages for
the two temperature differences. If using a consistent sampling rate of
one minute or more, calculate and record the two temperature
differences from each data sample. After having recorded the seventh
(i=7) set of temperature differences, calculate the following ratio
using the first seven sets of values:
[GRAPHIC] [TIFF OMITTED] TP02JN10.256
Each time a subsequent set of temperature differences is recorded
(if sampling more frequently than every 5 minutes), calculate FCD using
the most recent seven sets of values. Continue these calculations until
the 30-minute period is completed or until a value for FCD is
calculated that falls outside the allowable range of 0.94-1.06. If the
latter occurs, immediately suspend the test and identify the cause for
the disparity in the two temperature difference measurements.
Recalibration of one or both sets of instrumentation may be required.
If all the values for FCD are within the allowable range, save the
final value of the ratio from the 30-minute test as FCD\*\.
If the temperature sensors used to provide the primary measurement
of the indoor-side dry bulb temperature difference during the steady-
state dry-coil test and the subsequent cyclic dry-coil test are the
same, set FCD* = 1.
e. 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 variable-speed 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 ([Delta]P1) exceeds the applicable section 3.1.4.4 minimum (or
targeted) external static pressure ([Delta]Pmin) by 0.03 in wc or more.
Determine Efan,1 by making measurements during the 30-minute
data collection interval, or immediately following the test and prior
to changing the test conditions. When the above ``2'' criteria applies,
conduct the following four steps after determining Efan,1
(which corresponds to [Delta]P1):
1. While maintaining the same test conditions, adjust the exhaust
fan of the airflow measuring apparatus until the external static
pressure increases to approximately [Delta]P1 + ([Delta]P1 -
[Delta]Pmin).
2. 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 ([Delta]P2)
by making measurements over a 5-minute interval.
3. Approximate the average power consumption of the indoor fan
motor if the 30-minute test had been conducted at [Delta]Pmin using
linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TP02JN10.257
4. 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, [Edot]hk(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, H1C1, H1C2, and H3C3 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
steady-state 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 wet-
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 Eq. 3.5-1, use the values of V, Cp,a, vn' (or
vn), and Wn that were recorded during the section 3.7 steady state test
conducted at the same test conditions.
(2) Calculate [Gamma] using
[GRAPHIC] [TIFF OMITTED] TP02JN10.258
Where:
FCD* = recorded during the section 3.7 steady state test
conducted at the same test conditions.
* * * * *
3.8.1 * * *
Table 14--Test Operating and Test Condition Tolerances for Cyclic
Heating Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \2\
------------------------------------------------------------------------
Indoor entering dry-bulb 2.0 0.5
temperature, [deg] F...............
Indoor entering wet-bulb 1.0 ................
temperature, [deg] F...............
Outdoor entering dry-bulb 2.0 0.5
temperature, [deg] F...............
Outdoor entering wet-bulb 2.0 1.0
temperature, [deg] F...............
External resistance to air-flow,\3\ 0.12 ................
inches of water....................
[[Page 31260]]
Airflow nozzle pressure difference 2.0 \4\ 2.0
or velocity pressure, \3\ % of
reading............................
Electrical voltage,\5\ % of rdg..... 8.0 1.5
------------------------------------------------------------------------
\1\ See Definition 1.43.
\2\ See Definition 1.42.
\3\ Applies 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.
* * * * *
3.9 * * *
e. * * * Sample the remaining parameters listed in Table 15 at
equal intervals that span 5 minutes or less.
* * * * *
3.9.2 * * *
a. Assign the demand defrost credit Fdef used in section 4.2 to the
value of 1 in all cases except for heat pumps having a demand-defrost
control system (Definition 1.21). For such qualifying heat pumps,
evaluate Fdef using
[GRAPHIC] [TIFF OMITTED] TP02JN10.259
Where:
[Delta]Tdef = the time between defrost terminations (in hours) or
1.5, whichever is greater. A value of 6 must be assigned to [Delta]Tdef
if this limit is reached during a frost accumulation test and the heat
pump has not completed a defrost cycle.
[Delta]Tmax = maximum time between defrosts as allowed by the
controls (in hours) or 12, whichever is less. The value of [Delta]Tmax
must be provided by the manufacturer.
* * * * *
3.10 Test procedures for steady-state low and minimum temperature
heating mode tests (the H3, H33, H32, H31, and H43 Tests). Except for
modifications noted in this section, conduct the low temperature and
minimum temperature heating mode tests 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) or Qhk (2) and
Ehk (17) or Ehk (2) ,
conduct a defrost cycle that can be initiated manually or
automatically. The defrost sequence must be terminated by the action of
the heat pump's defrost controls. Begin the 30-minute data collection
interval described in section 3.7 from which Qhk
(17) and Ehk (17) or Qhk
(2) and Ehk (2) are determined, no sooner than 10
minutes after defrost termination. Defrosts should be prevented over
the 30-minute data collection interval.
* * * * *
3.11.1.1 * * *
a. The test conditions for the preliminary test are the same as
specified for the official test. Connect the indoor air-side 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 1 hour. After attaining equilibrium conditions,
measure the following quantities at equal intervals that span 5 minutes
or less:
1. The section 2.10.1 evaporator and condenser temperatures or
pressures;
2. Parameters required according to the indoor air enthalpy method.
Continue these measurements until a 30-minute period (e.g., seven
consecutive 5-minute samples) is obtained where the Table 7 or Table
13, whichever applies, test tolerances are satisfied.
* * * * *
3.11.1.3 * * *
a. Continue (preliminary test was conducted) or begin (no
preliminary test) the official test by making measurements for both the
indoor and outdoor air enthalpy methods at equal intervals that span 5
minutes or less. Discontinue these measurements only after obtaining a
30-minute period where the specified test condition and 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 percent.
* * * * *
3.11.2 * * *
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 [deg]F, use
the calorimeter to measure total capacity rather than refrigerant flow
rate. Conduct these calibration tests at the same test conditions as
specified for the tests in this Appendix. Operate the unit for at least
one hour or until obtaining equilibrium conditions before collecting
data that will be used in determining the average refrigerant flow rate
or total capacity. Sample the data at equal intervals that span 5
minutes or less. Determine average flow rate or average capacity from
data sampled over a 30-minute period where the Table 7 (cooling) or the
Table 13 (heating) tolerances are satisfied. Otherwise, conduct the
calibration tests according to ASHRAE Standard 23-05 (incorporated by
reference, see Sec. 430.3), ASHRAE Standard 41.9-2000 (incorporated by
reference, see Sec. 430.3), and section 7.4 of ASHRAE Standard 37-2005
(incorporated by reference, see Sec. 430.3).
* * * * *
3.13 Laboratory testing to determine off-mode energy consumption.
The below laboratory testing is used to estimate the energy consumption
of an air conditioner during the non-cooling seasons, the heating and
shoulder seasons that separate the cooling and heating seasons. Testing
to estimate the energy consumption of a heat pump during the collective
shoulder seasons is also described. The extent of the testing strongly
depends on whether the test unit includes a compressor crankcase
heater, the heater is thermostatically controlled, and the heater is
provided on an air conditioner or heat pump.
3.13.1 Determine if the air conditioner or heat pump has a
compressor crankcase heater. If so equipped, turn off the power to the
outdoor unit, isolate the leads that supply power to the crankcase
heater, measure the resistance of the heater circuit, record the value
as
[[Page 31261]]
RCC, reconnect the heater's leads, and resupply power to the outdoor
unit.
Determine from the manufacturer if the compressor crankcase heater
is thermostatically controlled. If the heater is thermostatically
controlled, the manufacturer must provide:
a. A value for the outdoor temperature, T00, at which the crankcase
heater is expected to begin heating if the indoor temperature is above
75 [deg]F and no space conditioning has been needed for a long enough
time that the compressor's shell temperature equals the outdoor air
temperature; and
b. A value for the outdoor temperature, T100, at which the
crankcase heater is expected to begin continuous heating if the indoor
temperature is above 75 [deg]F and no space conditioning is needed.
3.13.2 For air conditioners not having a compressor crankcase
heater, conduct the following off-mode power test.
3.13.2.1 Conduct the test immediately following the final cooling
mode test. No requirements are placed on the ambient conditions within
the indoor and outdoor test rooms. The room conditions are allowed to
change for the duration of this particular test. Configure the controls
of the air conditioner to mimic the operating mode if connected to a
building thermostat that is set to the OFF mode.
3.13.2.2 Integrate the power consumption of the air conditioner
over a 5-minute interval. Calculate the average power consumption rate
for the interval. Round this value to the nearest even wattage value
and record it as both P1 and P2. Assign RCC=0.
3.13.3 For heat pumps not having a compressor crankcase heater,
conduct the following off-mode power test.
3.13.3.1 Conduct the test immediately following the final cooling
mode test. No requirements are placed on the ambient conditions within
the indoor and outdoor test rooms. The room conditions are allowed to
change for the duration of this particular test. Configure the controls
of the heat pump to mimic the operating mode if connected to a building
thermostat that is set to the COOL mode but whose temperature setpoint
is satisfied.
3.13.3.2 Integrate the power consumption of the heat pump over a 5-
minute interval. Calculate the average power consumption rate for the
interval. Record this value as P1C.
3.13.3.3 Re-configure the controls of the heat pump to mimic the
operating mode if connected to a building thermostat that is set to the
HEAT mode but whose temperature setpoint is satisfied.
3.13.3.4 Integrate the power consumption of the heat pump over a 5-
minute interval. Calculate the average power consumption rate for the
interval. Record this value as P1H.
3.13.3.5 Calculate P1 = (P1C + P1H)/2 and round to the nearest even
wattage. Assign RCC=0 and P2=0.
3.13.4 For air conditioners having a compressor crankcase heater,
conduct the following off-mode power test.
3.13.4.1 Conduct the test immediately following the final cooling
mode test.
3.13.4.2 If the compressor crankcase heater is not thermostatically
controlled, then (1) configure the controls of the air conditioner to
mimic the operating mode if connected to a building thermostat set to
the OFF mode; (2) assign T00 = T100 = 75 [deg]F; and (3) skip to
section 3.13.4.5.9.
3.13.4.3 If the compressor crankcase heater is thermostatically
controlled and the manufacturer-provided T100 is greater than or equal
to 75 [deg]F, then (1) T00 and T100 are deemed verified; (2) configure
the controls of the air conditioner to mimic the operating mode if
connected to a building thermostat that is set to the OFF mode; and (3)
skip to section 3.13.4.5.9.
3.13.4.4.1 Configure the controls of the air conditioner to mimic
the operating mode if connected to a building thermostat that is set to
the OFF mode. Maintain the dry bulb temperature in the indoor test room
between 75 [deg]F and 85 [deg]F.
3.13.4.4.2 Monitor the power consumption of the air conditioner and
denote two operating states: (1) Power draw is at a lower level
corresponding to no current flowing to the compressor crankcase heater
(power-low) and (2) power draw is at the higher level corresponding to
the compressor crankcase heater operating (power-high).
3.13.4.4.3 As needed, temporarily depart from the end of test
cooling rate (EOTCR) until the outdoor temperature is at least 3 [deg]F
higher than T100 for at least 15 minutes or, if the crankcase heater is
observed to cycle on (power-high) at this temperature, keep increasing
the outdoor temperature until the compressor crankcase heater remains
off (power-low) for at least 15 minutes. The compressor must have
cycled off prior to beginning either 15 minute count.
3.13.4.4.4 Re-establish cooling the outdoor test room with the
reconditioning system set to provide EOTCR. As the outdoor temperature
decreases, monitor the test unit's electrical power and record the
outdoor temperature when the first power-high reading is measured. If
this measured temperature is equal to or less than T00 + 2.5 [deg]F,
then the manufacturer-provided T00 is verified. If the measured
temperature is greater than T00 + 2.5 [deg]F, round the measured
outdoor temperature to the nearest 2.5 [deg]F increment relative to a
65 [deg]F reference (e.g., 67.5 [deg]F, 70.0 [deg]F, 72.5 [deg]F, * * *
or 65.0 [deg]F, 62.5 [deg]F, 60.0 [deg]F, * * *) and designate this
rounded value as the new T00.
3.13.4.4.5 If the manufacturer-provided T100 is greater than or
equal to T00-10 [deg]F then T100 is deemed verified. If T100 > T00,
then set T100 = T00. Skip to section 3.13.4.5.
3.13.4.4.6 As needed, depart from the EOTCR to obtain and then
maintain within 1.0 [deg]F an outdoor dry bulb temperature
that is between 10 [deg]F and 15 [deg]F less than T00. During the time
that the outdoor temperature is maintained within the 1.0
[deg]F tolerance, monitor the elapsed time of each power-high interval
([Delta][tau]PH) and the elapsed time of the power-low interval
([Delta][tau]PL) that immediately follows. Also monitor the outdoor
temperature. Start data collection at the beginning of a power-high
interval--elapsed time = 0. If one or more power-high + power-low
cycles is completed when the elapsed time equals 20 minutes,
discontinue the data collection and proceed to section 3.13.4.4.7. If a
power-high interval is completed before the elapsed time equals 30
minutes, monitor until the subsequent power-low interval is finished
before discontinuing the data collection and proceeding to section
3.13.4.4.7. If a power-low condition has not started at an elapsed time
of 30 minutes or within 45 minutes of first obtaining outdoor
conditions that meet the 1.0 [deg]F tolerance, then assign
T100 = T00-10 [deg]F and skip to section 3.13.4.5.
3.13.4.4.7 Designate the total number of completed power-high +
power-low intervals from section 3.13.4.4.6 as NCC. Calculate the
average outdoor temperature recorded over the corresponding interval of
complete cycles and designate it as TCC. Calculate the average percent
on-time of the crankcase heater, FCC, using
[GRAPHIC] [TIFF OMITTED] TP02JN10.260
Using the T00 from section 3.13.4.4.4, FCC, and TCC, estimate the
outdoor temperature at which the crankcase
[[Page 31262]]
heater would first begin to operate continuously:
[GRAPHIC] [TIFF OMITTED] TP02JN10.261
If T100(Lab) <= T100 + 2.5 [deg]F, then the manufacturer-provided
T100 is verified. If T100(Lab) > T100 + 2.5 [deg]F, round T100(Lab) to
the nearest 2.5 [deg]F increment relative to a 65 [deg]F reference
(e.g., 67.5 [deg]F, 70.0 [deg]F, 72.5 [deg]F, * * * or 65.0 [deg]F,
62.5 [deg]F, 60.0 [deg]F, * * *) and designate this rounded value as
the new T100.
3.13.4.4.8 Approximate the percent time on of the crankcase heater
at any outdoor temperatures between T00 and T100 using
[GRAPHIC] [TIFF OMITTED] TP02JN10.262
For outdoor temperatures Tj that are greater than or
equal to T00, assign FCC(Tj)=0. For outdoor temperatures that are less
than or equal to T100, assign FCC(Tj)=100 percent.
3.13.4.5 At this point in the off-mode power test, no requirements
are placed on the ambient conditions within the indoor and outdoor test
rooms. The room conditions are allowed to change for the duration of
this particular test. Temporarily turn off the power to the outdoor
unit and safely disable the compressor crankcase heater to prevent it
from consuming any electrical power. Re-energize the outdoor unit.
3.13.4.6 Integrate the power consumption of the air conditioner
over a 5-minute interval. Calculate the average power consumption rate
for the interval. Record the value as P0.
3.13.5 For heat pumps having a compressor crankcase heater, conduct
the following off-mode power test.
3.13.5.1 The test shall be conducted immediately following the
final cooling mode test. Configure the controls of the heat pump to
mimic the operating mode if connected to a building thermostat set to
the COOL mode but whose temperature setpoint is satisfied.
3.13.5.2 If the compressor crankcase heater is not thermostatically
controlled, assign FCC(65 [deg]F) = 100 percent, and skip to section
3.13.5.5.
3.13.5.3 If the compressor crankcase heater is thermostatically
controlled and the manufacturer-provided T100 is greater than or equal
to 65 [deg]F, then assign FCC(65 [deg]F) = 100 percent and skip to
section 3.13.5.5.
3.13.5.4 If the compressor crankcase heater is thermostatically
controlled and the manufacturer-provided T100 is less than 65 [deg]F,
obtain and then maintain the outdoor dry bulb temperature between 64
[deg]F and 66 [deg]F. Maintain the dry bulb temperature in the indoor
test room between 75 [deg]F and 85 [deg]F.
3.13.5.4.1 Monitor the power consumption of the heat pump and
denote the two operating states: (1) Power draw is at a lower level
corresponding to no current flowing to the compressor crankcase heater
(power-low); and (2) power draw is at the higher level corresponding to
the compressor crankcase heater operating (power-high).
3.13.5.4.2 After the compressor has been off for a minimum of 15
minutes and while the outdoor temperature is between 64 [deg]F and 66
[deg]F, monitor the elapsed time of each power-high interval
([Delta][tau]PH) and the elapsed time of the power low interval
([Delta][tau]PH) that immediately follows. Continue monitoring the
outdoor temperature.
Start the data collection at the beginning of a power-high
interval--elapsed time = 0. If one or more power-high + power-low
cycles is completed when the elapsed time equals 20 minutes,
discontinue the data collection and proceed to section 3.13.5.4.3. If a
power-high interval is completed before the elapsed time equals 30
minutes, monitor until the subsequent power-low interval is finished
before discontinuing the data collection and proceeding to section
3.13.5.4.3. If a power-low condition has not started at an elapsed time
of 30 minutes or within 45 minutes of first obtaining an outdoor
temperature between 64 [deg]F and 66 [deg]F, then assign FCC(65 [deg]F)
= 100 percent and skip to section 3.13.5.5.
3.13.5.4.3 Designate the total number of completed power-high +
power-low intervals as NCC. Calculate the average outdoor temperature
over the corresponding interval of complete cycles and designate it as
TCC. Calculate the average percent on-time of the crankcase
heater, FCC, using
[GRAPHIC] [TIFF OMITTED] TP02JN10.263
3.13.5.4.4 Using the manufacturer-provided T00 and T100, along with
lab-measured TCC, calculate the expected value of
FCC. If TCC >= T00, then FCC = 0; if
TCC <= T100, then FCC = 100 percent; and if T100
< TCC < T00, then use:
[GRAPHIC] [TIFF OMITTED] TP02JN10.264
[[Page 31263]]
3.13.5.4.5 If FCC(Lab) <= FCC + 5 percent, then solve the section
3.13.5.4.4 equation for TCC = 65 [deg]F and assign the
result as being FCC(65 [deg]F). If FCC(Lab) >
FCC + 5 percent, round FCC(Lab) to the nearest 5
percent increment (e.g., 5, 10, 15, * * * 95 percent) and designate
this rounded value as FCC(65 [deg]F).
3.13.5.5 At this point in the off-mode power test, no requirements
are placed on the ambient conditions within the indoor and outdoor test
rooms. The room conditions are allowed to change for the duration of
this particular test. Temporarily turn off the power to the outdoor
unit and safely disable the compressor crankcase heater to prevent it
from consuming any electrical power. Re-energize the outdoor unit.
3.13.5.5.1 Integrate the power consumption of the heat pump over a
5-minute interval. Calculate the average power consumption rate for the
interval. Record this value as P0C.
3.13.5.5.2 Configure the controls of the heat pump to mimic the
operating mode if connected to a building thermostat set to the HEAT
mode but whose temperature setpoint is satisfied.
3.13.5.5.3 Integrate the power consumption of the heat pump over a
5-minute interval. Calculate the average power consumption rate for the
interval. Record this value as P0H. Assign P0 = (P0C + P0H)/2.
3.13.5.6 Calculate P1 = P0 + (FCC(65 [deg]F)/100%) x
[(230 V)\2\/RCC] and round to the nearest even wattage.
Assign P2 = 0.
3.13.5.7 Re-enable the compressor crankcase heater so that it may
operate in its normal manner.
4. Calculations of Seasonal Performance Descriptors
* * * * *
4.1 * * *
When referenced, evaluate BL(Tj) for cooling using * * *
* * * Where:
Qck(95) = the space cooling capacity determined from the A or A2
Test, whichever applies, Btu/h.
1.1 = sizing factor, dimensionless.
The temperatures 95 [deg] and 65 [deg] 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-speed compressor that was tested with a fixed-speed indoor fan
installed, a constant-air-volume-rate indoor fan installed, or with no
indoor fan installed. a. Calculate the seasonal energy efficiency
ratio, SEER, using Eq. 4.1-1. Evaluate the quantity qc(Tj)/N in Eq.
4.1-1 using
[GRAPHIC] [TIFF OMITTED] TP02JN10.265
Where:
X(Tj) = the cooling mode load factor for temperature bin j,
dimensionless,
Qc(Tj) = space cooling capacity of the test unit when operating at
outdoor temperature Tj, Btu/h, and
[GRAPHIC] [TIFF OMITTED] TP02JN10.266
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.
Assign
[GRAPHIC] [TIFF OMITTED] TP02JN10.267
using the fractional bin hours listed in Table 16. Calculate the space
cooling capacity at outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TP02JN10.268
Determine Qc(82) from the B Test, Qc(95), from the A Test, and
evaluate both in accordance with section 3.3. Calculate the cooling
mode load factor using
[GRAPHIC] [TIFF OMITTED] TP02JN10.269
Use Eq. 4.1-2 to calculate the building load, BL(Tj).
b. Evaluate the quantity ec(Tj)/N in Eq. 4.1-1 using
[GRAPHIC] [TIFF OMITTED] TP02JN10.270
Where:
Ec(Tj) = the electrical power consumption of the test unit when
operating at outdoor temperature Tj, Btu/h, and
PLFf = the part load factor for temperature bin j, dimensionless.
The quantities X(Tj) and
[GRAPHIC] [TIFF OMITTED] TP02JN10.271
are the same quantities as used for calculating
[GRAPHIC] [TIFF OMITTED] TP02JN10.272
Calculate the electrical power consumption at outdoor temperature Tj
using
[GRAPHIC] [TIFF OMITTED] TP02JN10.273
[[Page 31264]]
Determine Ec (82) from the B Test, Ec (95) from the A Test, and
evaluate both in accordance with section 3.3. Calculate the part load
factor using
[GRAPHIC] [TIFF OMITTED] TP02JN10.274
c. 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 3.5.3.
* * * * *
4.1.4.2 * * *
T1 = the outdoor temperature at which the unit, when operating
at minimum compressor speed, provides a space cooling capacity that
is equal to the building load
(Qck=1(T1))=BL(T1)), [deg]F.
Determine T1 by equating Eqs. 4.1.3-1 and 4.1-2 and solving for
outdoor temperature. Alternatively, T1 may be determined as
specified in section 10.2.4 of ASHRAE Standard 116-95 (RA 05)
(incorporated by reference, see Sec. 430.3).
T2 = 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=2 (T2) = BL (T2)), [deg]F. Determine
T2 by equating Eqs. 4.1.4-1 and 4.1-2 and solving for outdoor
temperature. Alternatively, T2 may be determined as specified in
section 10.2.4 of ASHRAE Standard 116-95 (RA 05) (incorporated by
reference, see Sec. 430.3).
* * * * *
4.1.5 SEER calculations for an air conditioner or heat pump having
a single indoor unit with multiple blowers. Calculate SEER using Eq.
4.1-1, where qc (Tj)/N and ec (Tj)/N are evaluated as specified in
applicable below subsection.
4.1.5.1 For multiple blower systems that are connected to a lone,
single-speed outdoor unit.
a. Calculate the space cooling capacity, Qck=1 (Tj), and
electrical power consumption, Eck=1 (Tj), of the test unit
when operating at the cooling minimum air volume rate and outdoor
temperature Tj using the equations given in section 4.1.2.1. Calculate
the space cooling capacity, Qck=2 (Tj), and electrical power
consumption, Eck=2 (Tj), of the test unit when operating at
the cooling full-load air volume rate and outdoor temperature Tj using
the equations given in section 4.1.2.1. In evaluating the section
4.1.2.1 equations, determine the quantities Qck=1 (82) and
Eck=1 (82) from the B1 Test, Qck=1
(95) and Eck=1 (95) from the Al Test,
Qck=2 (82) and Eck=2 (82) from the B2
Test, and Qck=2 (95) and from the A2 Test. Evaluate all
eight quantities as specified in section 3.3. Refer to section 3.2.2.1
and Table 4 for additional information on the four referenced
laboratory tests.
b. Determine the cooling mode cyclic degradation coefficient, CcD,
as per sections 3.2.2.1 and 3.5 to 3.5.3. Assign this same value to
CcD(K=2).
c. Except for using the above values of Qck=1 (Tj),
Eck=1 (Tj), Qck=2 (Tj), Eck=2 (Tj),
CcD, and CcD (k = 2), calculate the quantities qc (Tj)/N and ec (Tj)/N
as specified in section 4.1.3.1 for cases where Qck=1 (Tj)
[gteqt] BL (Tj). For all other outdoor bin temperatures, Tj, calculate
qc (Tj)/N and ec (Tj)/N as specified in section 4.1.3.3 if
Qck=2 (Tj) > BL (Tj) or as specified in section 4.1.3.4 if
Qck=2 (Tj) <= BL (Tj).
4.1.5.2 For multiple blower systems that are connected to either a
lone outdoor unit having a two-capacity compressor or to two separate
but identical model single-speed outdoor units.
Calculate the quantities qc (Tj)/N and ec (Tj)/N as specified in
section 4.1.3.
* * * * *
4.1.6 Region-specific SEER calculations for a hot-dry climatic
region, SEER-HD. Calculate SEER-HD, expressed in units of Btu/Wxh,
using:
[GRAPHIC] [TIFF OMITTED] TP02JN10.275
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.276
for the hot-dry climatic region, the ratio of the total space
cooling delivered 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.
[GRAPHIC] [TIFF OMITTED] TP02JN10.277
for the hot-dry climatic region, the ratio of the total 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.
Tj = the outdoor bin temperature, [deg]F. Outdoor temperatures are
grouped or ``binned.'' Use bins of 5 [deg]F with the 10 dry climate
bin temperatures being 67, 72, 77, 82, 87, 92, 97, 102, 107, and 112
[deg]F.
j = the bin number. For dry climate seasonal calculations, j ranges
from 1 to 10.
When referenced, evaluate the dry climate building load BLHD(Tj)
using
[GRAPHIC] [TIFF OMITTED] TP02JN10.278
Where:
Q*HD (95) = the space cooling capacity determined from the AD or AD2
Test, whichever applies, Btu/h, and
1.1 = sizing factor, dimensionless.
The temperatures 95 [deg]F and 65 [deg]F in the building load
equation represent the outdoor design temperature and the zero-load
temperature, respectively, for the hot-dry climatic region.
4.1.6.1 SEER-HD calculations for an air conditioner or heat pump
having a single-speed compressor that was tested with a fixed-speed
indoor fan installed, a constant-air-volume-rate fan installed, or with
no indoor fan installed. Calculate SEER-HD using Eq. 4.1.6-1. Evaluate
the quantities qHD(Tj)/N and eHD(Tj)/N in Eq. 4.1.6-1 as specified in
section 4.1.1 for qc(Tj)/N and ec(Tj)/N, respectively, only now
replacing the
[[Page 31265]]
quantities Qc(Tj) and Ec(Tj) with QHD(Tj) and EHD(Tj). Also, use the
fractional bin hours, nj)/N, given in Table 16a rather than the values
listed in Table 16.
Calculate QHD(Tj) using the section 4.1.1 equation for Qc(Tj),
replacing Qc(95) and Qc(82) with QHD(95) and QHD(82), respectively.
Calculate EHD(Tj) using the section 4.1.1 equation for Ec(Tj),
replacing Ec(95) and Ec(82) with EHD(95) and EHD(82), respectively.
Determine QHD(95) and EHD(95) from the AD Test described in section
3.2.1 and conducted in accordance with section 3.3. Determine QHD(82)
and EHD(82) using the section 3.2.1 default equations or from the BD
Test described in section 3.2.1 and conducted in accordance with
section 3.3.
Replace section 4.1.1 references to BL(Tj) with BLHD(Tj), as
evaluated using Eq. 4.1.6-2. In evaluating Eq. 4.1.6-2, set QHD\*\(90)
equal to the value obtained from solving the equation for QHD(Tj) at Tj
= 90 [deg]F.
If it helps the user, the remaining section 4.1.1 calculation
parameters of X(Tj) and PLFj may also be designated as their dry
climate versions by adding a subscript ``HD'' when calculating SEER-HD.
Finally, use the section 4.1.1 value of CDc that was used to calculate
SEER to also calculate SEER-HD.
4.1.6.2 SEER-HD calculations for an air conditioner or heat pump
having a single-speed compressor and a variable-speed variable-air-
volume rate indoor fan.
4.1.6.2.1 Units covered by section 3.2.2.1 where the indoor fan
capacity modulation correlates with the outdoor dry bulb temperature.
The manufacturer must provide information on how the indoor air volume
rate or the indoor fan speed varies over the outdoor temperature range
of 67 [deg]F to 112 [deg]F. Calculate SEER-HD using Eq. 4.1.6-1.
Evaluate the quantities qHD(Tj)/N and eHD(Tj)/N in Eq. 4.1.6-1 as
specified in section 4.1.2.1 for qc(Tj)/N and ec(Tj)/N, respectively,
only now replacing the quantities Qc(Tj) and Ec(Tj) with QHD(Tj) and
EHD(Tj). Also, use the fractional bin hours, nj/N, given in Table 16a
rather than the values listed in Table 16.
Calculate QHD(Tj) using Eq. 4.1.2-2, where QHD(Tj),
QHDk=2(Tj), and QHDk=1(Tj) replace Qc(Tj),
Qck=2(Tj), and Qck=1(Tj), respectively. Use the
section 4.1.2.1 equations for Qck=1(Tj) and
Qck=2(Tj) to calculate QHDk=1(Tj) and
QHDk=2(Tj), respectively. In evaluating these equations, use
QHDk=1(82), QHDk=1(95), QHDk=2(82),
and QHDk=2(95). Determine QHDk=2(95), and
QHDk=1(95) from the AD2 and AD1 Tests described in section
3.2.2.1 and conducted in accordance with section 3.3. Determine
QHDk=2(82) and QHDk=1(82) using the section
3.2.2.1 default equations or from the BD2 and BD1 Tests described in
section 3.2.2.1 and conducted in accordance with section 3.3.
Calculate EHD(Tj) using Eq. 4.1.2-4, where EHD(Tj),
EHDk=2(Tj), and EHDk=1(Tj) replace Ec(Tj),
Eck=2(Tj), and Eck=1(Tj), respectively. Use the
section 4.1.2.1 equations for Eck=1(Tj) and
Eck=2(Tj) to calculate EHDk=1(Tj) and
EHDk=2(Tj), respectively. In evaluating these equations, use
EHDk=1(82), EHDk=1(95), EHDk=2(82),
and EHDk=2(95). Determine EHDk=2(95) and
EHDk=1(95) from the AD2 and AD1 Tests described in section
3.2.2.1 and conducted in accordance with section 3.3. Determine
EHDk=2(82) and EHDk=1(82) using the section
3.2.2.1 default equations or from the BD2 and BD1 Tests described in
section 3.2.2.1 and conducted in accordance with section 3.3.
Replace section 4.1.2.1 references to BL(Tj) with BLHD(Tj), as
evaluated using Eq. 4.1.6-2. In evaluating Eq. 4.1.6-2, set QHD\*\(90)
equal to the value obtained from solving the equation for
QHDk=2(Tj) at Tj = 90 [deg]F. The parameters
FPck=1, FPck=2, and FPc(Tj) denote the fan speeds
described in section 4.1.2.1, only now as applied to the dry climate
configuration and, in the case of the first two variables, as used for
the AD1 and AD2 Tests.
If it helps the user, the remaining section 4.1.2.1 calculation
parameters of X(Tj) and PLFj may also be designated as their dry
climate versions by adding a subscript ``HD'' when calculating SEER-HD.
Finally, use the section 4.1.2.1 value of cDc used to calculate SEER to
also calculate SEER-HD.
4.1.6.2.2 Units covered by section 3.2.2 where indoor fan capacity
modulation is used to adjust the sensible to total cooling capacity
ratio. Calculate SEER-HD as specified in section 4.1.6.1.
4.1.6.3 SEER-HD calculations for an air conditioner or heat pump
having a two-capacity compressor.
Calculate SEER-HD using Eq. 4.1.6-1. Evaluate the quantities
qHD(Tj)/N and eHD(Tj)/N in Eq. 4.1.6-1 as specified for qc(Tj)/N and
ec(Tj)/N, respectively, in sections 4.1.3.1, 4.1.3.2, 4.1.3.3, and
4.1.3.4, as appropriate, only now replacing the quantities Qck(Tj) and
Eck(Tj) with QHDk(Tj) and EHDk(Tj). Also, use the fractional bin hours,
nj/N, given in Table 16a rather than the values listed in Table 16.
Calculate QHDk=1(Tj) using Eq. 4.1.3-1, where
QHDk=1(Tj), QHDk=1(82), and
QHDk=1(67), replace Qck=1(Tj),
Qck=1(82), and Qck=1(67), respectively. Calculate
QHDk=2(Tj) using Eq. 4.1.3-3 where QHDk=2(Tj),
QHDk=2(95), and QHDk=2(82) replace
Qck=2(Tj), Qck=2(95), and Qck=2(82),
respectively. Determine QHDk=2(95) and QHDk=1(82)
from the AD2 and BD1 Tests described in section 3.2.3 and conducted in
accordance with section 3.3. Determine QHDk=2(82) and
QHDk=1(67) using the section 3.2.3 default equations or from
the BD2 and FD1 Tests described in section 3.2.3 and conducted in
accordance with section 3.3.
Calculate EHDk=1(Tj) using Eq. 4.1.3-2, where
EHDk=1(Tj), EHDk=1(82), and
EHDk=1(67), replace Eck=1(Tj),
Eck=1(82), and Eck=1(67), respectively. Calculate
EHDk=2(Tj) using Eq. 4.1.3-4, where EHDk=2(Tj),
EHDk=2(95), and EHDk=2(82), replace
Eck=2(Tj),Eck=2(95), and Eck=2(82),
respectively. Determine EHDk=2(95) and EHDk=1(82)
from the AD2 and BD1 Tests described in section 3.2.3 and conducted in
accordance with section 3.3. Determine EHDk=2(82) and
EHDk=1(67) using the section 3.2.3 default equations or from
the BD2 and FD1 Tests described in section 3.2.3 and conducted in
accordance with section 3.3.
Replace section 4.1.3 to 4.1.3.4 references to BL(Tj) with
BLHD(Tj), as evaluated using Eq. 4.1.6-2. In evaluating Eq. 4.1.6-2,
set Q\*\HD(90) equal to the value obtained from solving the equation
for QHDk=2(Tj) at Tj = 90 [deg]F.
If it helps the user, the remaining section 4.1.3 to 4.1.3.4
calculation parameters of Xk=1(Tj), Xk=2(Tj), and
PLFj may also be designated as their dry climate versions by adding a
subscript ``HD'' when calculating SEER-HD. Finally, use the section
4.1.3.1 value of CDc and the section 4.1.3.3 value of CDc(k = 2) that
were used to calculate SEER to also calculate SEER-HD.
4.1.6.4 SEER-HD calculations for an air conditioner or heat pump
having a variable-speed compressor.
Calculate SEER-HD using Eq. 4.1.6-1. Evaluate the quantities qHD
(Tj) / N and eHD (Tj) / N in Eq. 4.1.6-1 as specified for qc (Tj) / N,
and ec (Tj) / N, respectively, in sections 4.1.4.1, 4.1.4.2, and
4.1.4.3, as appropriate only now replacing the quantities Qkc (Tj) and
Ekc (Tj) with QkHD (Tj) and EkHD (Tj). Also, use the fractional bin
hours, nj/N, given in Table 16a rather than the values
listed in Table 16.
Calculate QHDk\=1\ (Tj) using Eq. 4.1.3-1, where QHDk\=1\ (Tj),
QHDk\=1\ (82), and QHDk\=1\ (67), replace Qck\=1\ (Tj), Qck\=1\ (82),
and Qck\=1\ (67), respectively. Calculate QHDk\=2\ (Tj) using Eq.
4.1.3-3 where QHDk\=2\ (Tj), QHDk\=2\ (82) replace Qck\=2\ (Tj),
Qck\=2\ (95), and Qck\=2\ (82), respectively. Determine QHDk\=2\ (95)
and QHDk\=1\ (82) from the AD2 and BD1 Tests described in
section 3.2.4 and conducted in accordance with section 3.3. Determine
QHDk\=2\ (82) and QHDk\=1\ (67) using the section 3.2.3 default
[[Page 31266]]
equations or from the BD2 and FD1 Tests described in section
3.2.4 and conducted in accordance with section 3.3.
Calculate EHDk\=1\ (Tj) using Eq. 4.1.3-2, where EHDk\=1\ (Tj),
EHDk\=1\ (82), and EHDk\=1\ (67), replace Eck\=1\ (Tj), Eck\=1\ (82),
and Eck\=1\ (67), respectively. Calculate EHDk\=2\ (Tj), using Eq.
4.1.3-4, where EHDk\=2\ (Tj), EHDk\=2\ (95), and EHDk\=2\ (82) replace
Eck\=2\ (Tj), Eck\=2\ (95), and Eck\=2\ (82), respectively. Determine
EHDk\=2\ (95) and EHDk\=2\ (82) from the AD2 and BD1 Tests
described in section 3.2.4 and conducted in accordance with section
3.3. Determine EHDk\=2\ (82) and EHDk\=1\ (67) using the section 3.2.3
default equations or from the BD2 and FD3 Tests
described in section 3.2.4 and conducted in accordance with section
3.3.
Approximate the performance of the air conditioner and heat pump
had it been tested for its steady-state, dry climate, intermediate
speed (k = v) performance at an outdoor dry bulb temperature of 87
[deg]F using the following equations.
[GRAPHIC] [TIFF OMITTED] TP02JN10.279
Where:
QHDk\=1\ (87) and QHDk\=2\ (87) = obtained by solving the equations
for QHDk\=1\ (Tj) and QHDk\=2\ (Tj) for Tj = 87 [deg]F,
and EHDk\=1\ (87), and
EHDk\=2\ (87) = obtained by solving the equations for EHDk\=1\ (Tj)
and EHDk\=2\ (Tj) for Tj = 87 [deg]F.
Calculate QHDk=v (Tj) using Eq. 4.1.4-1, where QHDk=v (Tj) and
QHDk=v (87) replace Qck=v (Tj) and Qck=v (87), respectively. Calculate
EHDk=v (Tj) using Eq. 4.1.4-2, where EHDk=v (Tj) and EHDk=v (87)
replace Eck=v (Tj) and Eck=v (87), respectively.
Replace section 4.1.4 to 4.1.4.3 references to BL(Tj) with BLHD
(Tj), as evaluated using Eq. 4.1.6-2. In evaluating Eq. 4.1.6-2, set
QHD (90) equal to the value obtained from solving the equation for
QHDk\=2\ (Tj) at Tj = 90 [deg]F.
If it helps the user, the remaining section 4.1.4 to 4.1.4.3
calculation parameters of MQ, ME, NQ,
NE, ERRk\=1\ (Tj), A, B, C, D, T1, Tv,
T2, EERk\=1\ (T1), EERk\=v\ (Tv),
EERk\=2\(T2), Xk=1(Tj), and PLFj may also be
designated as their dry climate versions by adding a subscript ``HD''
when calculating SEER-HD. Finally, use the section 4.1.4.1 value of CcD
used to calculate SEER to also calculate SEER-HD.
Table 16a--Distribution of Fractional Bin Hours Within the Hot-Dry Climatic Region
----------------------------------------------------------------------------------------------------------------
Representative Fraction of total
Bin No. j Bin temperature temperature for temperature bin
range [deg]F bin j [deg]F hours nj/N
----------------------------------------------------------------------------------------------------------------
1................................................... 65-69 67 0.477
2................................................... 70-74 72 0.208
3................................................... 75-79 77 0.119
4................................................... 80-84 82 0.086
5................................................... 85-89 87 0.047
6................................................... 90-94 92 0.027
7................................................... 95-99 97 0.021
8................................................... 100-104 102 0.011
9................................................... 105-109 107 0.004
10.................................................. 110-114 112 0.000
----------------------------------------------------------------------------------------------------------------
* * * * *
4.2 * * *
4. For triple-capacity, northern heat pumps (Definition 1.47), Qhk
(47) = Qhk=2 (47), the space heating capacity determined
from the H12 Test.
For HSPF calculations for all heat pumps, see either section 4.2.1,
4.2.2, 4.2.3, 4.2.4, or 4.2.6, whichever applies.
* * * * *
4.2.4.2 * * *
T4 = the outdoor temperature at which the heat pump, when operating
at maximum compressor speed, provides a space heating capacity equal to
the building load (Qh\k=2\(T4) = BL(T4)), [deg]F.
Determine T4 by equating Eqs. 4.2.2-3 (k=2) and 4.2-2 and solving for
outdoor temperature. Alternatively T4 may be determined as specified in
section 10.2.4 of ASHRAE Standard 116-95 (RA 05) (incorporated by
reference, see Sec. 430.3).
* * * * *
4.2.6 Additional steps for calculating the HSPF of a heat pump
having a triple-capacity compressor. The only triple-capacity heat
pumps covered at this time are triple-capacity, northern heat pumps as
defined in section 1.45. For such heat pumps, the calculation of the
Eq. 4.2-1 quantities
[GRAPHIC] [TIFF OMITTED] TP02JN10.280
differ depending on whether the heat pump would cycle on and off at low
capacity (section 4.2.6.1), cycle on and off at high capacity (section
4.2.6.2), cycle on and off at booster capacity (4.2.6.3), cycle between
low and high capacity (section 4.2.6.4), cycle between high and booster
capacity (section 4.2.6.5), operate continuously at low capacity
(4.2.6.6), operate continuously at high capacity (section 4.2.6.7),
operate continuously at booster capacity (4.2.6.8), or heat solely
using resistive heating (also section 4.2.6.8) in responding to the
building load. As applicable, the manufacturer must supply information
regarding the outdoor temperature range at which each stage of
compressor capacity is active. Information of the type shown in
[[Page 31267]]
the example table below is required in such cases.
------------------------------------------------------------------------
Outdoor temperature range of
Compressor capacity operation
------------------------------------------------------------------------
Low (k=1).............................. 40 [deg]F <= T <= 65 [deg]F
High (k=2)............................. 20 [deg]F <= T <= 50 [deg]F
Booster (k=3).......................... -20 [deg]F <= T <= 30 [deg]F
------------------------------------------------------------------------
a. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at low compressor capacity
and outdoor temperature Tj using the equations given in section 4.2.3
for Qhk=1 (Tj) and Ehk=1 (Tj) In evaluating the
section 4.2.3 equations, determine the inputs Qhk=1 (62) and
Ehk=1 (62) from the HO1 Test and determine Qhk=1
(47) and Ehk=1 (47) from the H11 Test. Calculate all four
quantities as specified in section 3.7. If, in accordance with section
3.6.6, the H31 Test is conducted, calculate Qhk=1 (17) and
Ehk=1 (17) as specified in section 3.10 and determine
Qhk=1 (35) and Ehk=1 (35) as specified in section
3.6.6.
b. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at high compressor capacity
and outdoor temperature Tj [Qhk=2 (Tj) and Ehk=2
(Tj)] by solving Eqs. 4.2.2-3 and 4.2.2-4, respectively, for k = 2.
Determine the equation inputs Qhk=2 (47) and
Ehk=2 (47) from the H12 Test, evaluated as specified in
section 3.7. Determine the equation inputs Qhk=2 (35) and
Ehk=2 (35) from the H22 Test, evaluated as specified in
section 3.9.1. Also, determine the equation inputs Qhk=2
(17) and Ehk=2 (17) from the H32 Test, evaluated as
specified in section 3.10.
c. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at booster compressor
capacity and outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TP02JN10.281
[GRAPHIC] [TIFF OMITTED] TP02JN10.282
Determine the inputs Qhk=3 (17) and Ehk=3
(17) from the H33 Test and determine Qhk=3 (2) and
Ehk=3 (2) from the H43 Test. Calculate all four quantities
as specified in section 3.10. Determine the inputs Qhk=3
(35) and Ehk=3 (35) as specified in section 3.6.6.
4.2.6.1 Steady-state space heating capacity when operating at low
compressor capacity is greater than or equal to the building heating
load at temperature Tj, Qhk=1 (Tj) >= BL(Tj), and the heat
pump permits low compressor capacity operation at Tj. Evaluate the
quantities
[GRAPHIC] [TIFF OMITTED] TP02JN10.283
using Eqs. 4.2.3-1 and 4.2.3-2, respectively. Determine the equation
inputs Xk=1 (Tj), PLFj, and [delta][min](Tj) as specified in
section 4.2.3.1. In calculating the part load factor, PLFj, use the
low-capacity cyclic-degradation coefficient CDh [or equivalently, CDh(k
= 1)] determined in accordance with section 3.6.6.
4.2.6.2 Heat pump only operates at high (k = 2) compressor capacity
at temperature Tj and its capacity is greater than or equal to the
building heating load, Qhk=1 (Tj) >= BL(Tj). Evaluate the
quantities
[GRAPHIC] [TIFF OMITTED] TP02JN10.284
as specified in section 4.2.3.3. Determine the equation inputs
Xk=2 (Tj), PLFj, and [delta][min](Tj) as specified in
section 4.2.3.3. In calculating the part load factor, PLFj, use the
high-capacity cyclic-degradation coefficient, CDh(k = 2)] determined in
accordance with section 3.6.6.
4.2.6.3 Heat pump only operates at booster (k = 3) capacity at
temperature Tj and its capacity is greater than or equal to the
building heating load, Qhk=3 (Tj) >= BL(Tj).
[GRAPHIC] [TIFF OMITTED] TP02JN10.285
[[Page 31268]]
[GRAPHIC] [TIFF OMITTED] TP02JN10.286
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.287
Determine the low temperature cut-out factor, [delta][min](Tj),
using Eq. 4.2.3-3. Use the booster-capacity cyclic-degradation
coefficient, CDh(k = 3), determined in accordance with section 3.6.6.
4.2.6.4 Heat pump alternates between low (k = 1) and high (k = 2)
compressor capacity to satisfy the building heating load at temperature
Tj, Qhk=1 (Tj) < BL(Tj) < Qhk=2 (Tj).
Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TP02JN10.288
as specified in section 4.2.3.2. Determine the equation inputs
Xk=1 (Tj), Xk=2 (Tj), and [delta][min](Tj) as
specified in section 4.2.3.2.
4.2.6.5 Heat pump alternates between high (k = 2) and booster (k =
3) compressor capacity to satisfy the building heating load at
temperature Tj, Qhk=2 (Tj) < BL(Tj) < Qhk=3(Tj).
[GRAPHIC] [TIFF OMITTED] TP02JN10.289
[GRAPHIC] [TIFF OMITTED] TP02JN10.290
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.291
Xk=3 (Tj) = Xk=2 (Tj) =
the heating mode, booster capacity load factor for temperature bin j,
dimensionless.
Determine the low temperature cut-out factor, [delta][min](Tj),
using Eq. 4.2.3-3.
4.2.6.6 Heat pump only operates at low (k = 1) capacity at
temperature Tj and its capacity is less than the building heating load,
BL(Tj) > Qhk=1 (Tj).
[GRAPHIC] [TIFF OMITTED] TP02JN10.292
where the low temperature cut-out factor, [delta][min](Tj), is
calculated using Eq. 4.2.3-3.
4.2.6.7 Heat pump only operates at high (k = 2) capacity at
temperature Tj and its capacity is less than the building heating load,
BL(Tj) > Qhk=2(Tj). Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TP02JN10.293
as specified in section 4.2.3.4. Calculate [delta][sec](Tj) using the
equation given in section 4.2.3.4.
4.2.6.8 Heat pump only operates at booster (k = 3) capacity at
temperature Tj and its capacity is less than the building heating load,
BL(Tj) > Qhk=3(Tj), or the system converts to using only
resistive heating.
[GRAPHIC] [TIFF OMITTED] TP02JN10.294
where [delta][sec](Tj) is calculated as specified in section 4.2.3.4 if
the heat pump is operating at its booster compressor capacity. If the
heat pump system coverts to using only resistive heating at outdoor
temperature Tj, set [delta][sec](Tj) equal to zero.
* * * * *
4.2.7 Additional steps for calculating the HSPF of a heat pump
having a single indoor unit with multiple blowers. The calculation of
the
[[Page 31269]]
Eq. 4.2-1 quantities eh(Tj) /N and RH(Tj) /N are evaluated as specified
in applicable below subsection.
4.2.7.1 For multiple blower heat pumps that are connected to a
lone, single-speed outdoor unit.
a. Calculate the space heating capacity, Qhk=1 (Tj), and
electrical power consumption, Ehk=1 (Tj), of the heat pump
when operating at the heating minimum air volume rate and outdoor
temperature Tj using Eqs. 4.2.2-3 and 4.2.2-4, respectively. Use these
same equations to calculate the space heating capacity,
Qhk=2 (Tj) and electrical power consumption,
Ehk=2 (Tj), of the test unit when operating at the heating
full-load air volume rate and outdoor temperature Tj. In evaluating
Eqs. 4.2.2-3 and 4.2.2-4, determine the quantities Qhk=1
(47) and Ehk=1 (47) from the H11 Test; determine
Qhk=2 (47) and Ehk=2 (47) from the H12 Test.
Evaluate all four quantities according to section 3.7. Determine the
quantities Qhk=1 (35) and Ehk=1 (35) as specified
in section 3.6.2. Determine Qhk=2 (35) and Ehk=2
(35) from the H22 Frost Accumulation Test as calculated according to
section 3.9.1. Determine the quantities Qhk=1 (17) and
Ehk=1 (17) from the H31 Test, and Qhk=2 (17) and
Ehk=2 (17) from the H32 Test. Evaluate all four quantities
according to section 3.10. Refer to section 3.6.2 and Table 10 for
additional information on the referenced laboratory tests.
b. Determine the heating mode cyclic degradation coefficient, CDh,
as per sections 3.6.2 and 3.8 to 3.8.1. Assign this same value to CDh(k
= 2).
c. Except for using the above values of Qhk=1 (Tj),
Ehk=1 (Tj), Qhk=2 (Tj), Ehk=2 (Tj),
CDh, and CDh(k = 2), calculate the quantities eh(Tj)/N as specified in
section 4.2.3.1 for cases where Qhk=1 (Tj) >= BL(Tj). For
all other outdoor bin temperatures, Tj, calculate eh(Tj)/N
and RHh(Tj)/N as specified in section 4.2.3.3 if Qhk=2 (Tj)
> BL(Tj) or as specified in section 4.2.3.4 if Qhk=2 (Tj) <=
BL(Tj).
4.2.7.2 For multiple blower heat pumps connected to either a lone
outdoor unit with a two-capacity compressor or to two separate but
identical model single-speed outdoor units.
Calculate the quantities eh(Tj)/N and RH(Tj)/N as specified in
section 4.2.3.
* * * * *
4.2.8 Off-mode seasonal power and energy consumption calculations.
Evaluate the off-mode seasonal power consumption for the collective
shoulders seasons, P1, which applies to air conditioners and heat
pumps. For air conditioners, determine the off-mode seasonal power
consumption for the heating season, P2. Once P1 and, for air
conditioners, P2, are evaluated, use the SSH and the HSH to calculate
the site specific seasonal energy consumption values.
4.2.8.1 Off-mode seasonal power consumption for the collective
shoulder seasons, P1. For air conditioners and heat pumps, the off-mode
power consumption for the shoulder seasons is a single value that
applies for all locations. The calculation of P1 varies for different
types of systems.
4.2.8.1.1 Air conditioners and heat pumps that do not have a
compressor crankcase heater. For air conditioners and heat pumps not
having a compressor crankcase heater, assign P1 as specified in
sections 3.13.2.2 and 3.13.3.5, respectively.
4.2.8.1.2 Air conditioners that have a compressor crankcase heater.
For air conditioners having a compressor crankcase heater, evaluate P1
using
[GRAPHIC] [TIFF OMITTED] TP02JN10.295
Where:
[GRAPHIC] [TIFF OMITTED] TP02JN10.296
Obtain RCC, the measured resistance of crankcase heater element,
and P0, the average off-mode power consumption of all other air
conditioner components except the crankcase heater, as specified in
sections 3.13.1 and 3.13.4.6, respectively. Calculate the percent time
on of the crankcase heater for outdoor bin temperatures Tj = 57, 62,
67, and 72 [deg]F as specified in section 3.13.4.4.8.
4.2.8.1.3 Heat pumps that have a compressor crankcase heater. For
heat pumps having a compressor crankcase heater, evaluate P1 using
[GRAPHIC] [TIFF OMITTED] TP02JN10.297
rounded to the nearest even wattage.
Obtain RCC, the measured resistance of crankcase heater element,
and P0, the average off-mode power consumption of all other heat pump
components except the crankcase heater, as specified in sections 3.13.1
and 3.13.5.5.3, respectively. Calculate the percent time on of the
crankcase heater at a 65 [deg]F outdoor temperature, FCC(65), as
specified in section 3.13.5.4.5.
4.2.8.2 Off-mode seasonal power consumption for air conditioners
during the heating season, P2. For air conditioners, P2 is non-zero and
evaluated as specified below. For heat pumps, P2 equals zero.
4.2.8.2.1 For air conditioners that do not have a compressor
crankcase heater. The off-mode power consumption for the heating season
is a single value that applies for all locations. Assign P2 = P1, as
determined in section 3.13.2.2.
4.2.8.2.2 For air conditioners that have compressor crankcase
heater. The off-mode power consumption for the heating season depends
on the fractional bin hour distribution, for which a different
distribution is specified for each of the six generalized climatic
regions, Figure 2. Calculate P2 using
[GRAPHIC] [TIFF OMITTED] TP02JN10.298
rounded to the nearest even wattage. Obtain RCC, the measured
resistance of crankcase heater element, and P0, the average off-mode
power consumption of all other air conditioner components except the
crankcase heater, as specified in sections 3.13.1 and 3.13.4.6,
respectively. Calculate FCC(Tj), the percent time on of the crankcase
heater for outdoor bin temperatures Tj as specified in section
3.13.4.4.8. Obtain nj/N, the heating season fractional bin hours, from
Table 17.
4.2.8.3 Off-mode seasonal energy consumption.
4.2.8.3.1 For the shoulder seasons. Calculate the off-mode energy
consumption for the collective shoulder seasons, E1, using
E1 = P1 x SSH
Where:
P1 = determined as specified in section 4.2.7.1 and the SSH are
determined from Table 19.
[[Page 31270]]
Table 19--Representative Cooling and Heating Load Hours and the Corresponding Set of Seasonal Hours for Each
Generalized Climatic Region
----------------------------------------------------------------------------------------------------------------
Cooling Heating Cooling Heating Shoulder
Climatic region load hours load hours season Season Season
CLRR HLHR hours CSHR Hours HSHR Hours SSHR
----------------------------------------------------------------------------------------------------------------
I.............................................. 2400 750 6731 1826 203
II............................................. 1800 1250 5048 3148 564
III............................................ 1200 1750 3365 4453 942
IV............................................. 800 2250 2244 5643 873
Rating Values.................................. 1000 2080 2805 5216 739
V.............................................. 400 2750 1122 6956 682
VI............................................. 200 2750 561 6258 1941
----------------------------------------------------------------------------------------------------------------
4.2.8.3.2 For the heating season--air conditioners only. Calculate
the off-mode energy consumption of an air conditioner during the
heating season, E2, using
E2 = P2 x HSH
Where:
P2 = determined as specified in section 4.2.7.2 and the HSH are
determined from Table 19.
* * * * *
4.3.1 * * *
[GRAPHIC] [TIFF OMITTED] TP02JN10.299
* * *
P1 = the off-mode seasonal power consumption for the collective
shoulders seasons, as determined in section 4.2.7.1, W, and
P2 = the off-mode seasonal power consumption for the heating
season, as determined in section 4.2.7.2, W.
Evaluate the HSH using
[GRAPHIC] [TIFF OMITTED] TP02JN10.300
Where:
TOD and nj/N = listed in Table 19 and depend on the location of
interest relative to Figure 2. For the six generalized climatic
regions, this equation simplifies to the following set of equations:
Region I HSH = 2.4348 x HLH
Region II HSH = 2.5182 x HLH
Region III HSH = 2.5444 x HLH
Region IV HSH = 2.5078 x HLH
Region V HSH = 2.5295 x HLH
Region VI HSH = 2.2757 x HLH
Evaluate the shoulder season hours using
SSH = 8760 - (CSH + HSH)
Where:
CSH = the cooling season hours calculated from CSH = 2.8045 x CLH
* * * * *
4.3.2 Calculation of representative regional annual performance
factors (APFR) for each generalized climatic region and for each
standardized design heating requirement.
[GRAPHIC] [TIFF OMITTED] TP02JN10.301
Where:
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, and
HSPF = the heating seasonal performance factor calculated as
specified in section 4.2 for each generalized climatic region and
for each standardized design heating requirement within each region,
Btu/W x h.
The SEER, Qc\k\ (95), DHR, C, P1, P2, SSH, and HSH 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.
Table 19--Representative Cooling and Heating Load Hours for Each
Generalized Climatic Region
------------------------------------------------------------------------
Region CLHR HLHR
------------------------------------------------------------------------
I............................... 2400 750
II.............................. 1800 1250
III............................. 1200 1750
IV.............................. 800 2250
V............................... 400 2750
[[Page 31271]]
VI.............................. 200 2750
------------------------------------------------------------------------
4.4 Rounding of SEER, HSPF, SHR, 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 CFR. Round
section 4.2 HSPF values and section 4.3 APF values as per Sec.
430.23(m)(3)(ii) and (iii) of Title 10 of the CFR. Round section 4.5
SHR values to 2 decimal places.
4.5 Calculations of the SHR, which should be computed for different
equipment configurations and test conditions specified in Table 20.
Table 20--Applicable Test Conditions for Calculation of the Sensible Heat Ratio
----------------------------------------------------------------------------------------------------------------
Reference
Equipment configuration Table No. of SHR computation with Computed values
Appendix M results from
----------------------------------------------------------------------------------------------------------------
Single-Speed Compressor and a Fixed- 3 B Test.................... SHR(B)
Speed Indoor Fan, a Constant Air Volume
Rate Indoor Fan, or No Indoor Fan.
Single-Speed Compressor and a Variable 4 B2 and B1 Tests........... SHR(B1), SHR(B2)
Air Volume Rate Indoor Fan.
Units Having a Two-Capacity Compressor.. 5 B2 and B1 Tests........... SHR(B1), SHR(B2)
Units Having a Variable-Speed Compressor 6 B2 and B1 Tests........... SHR(B1), SHR(B2)
----------------------------------------------------------------------------------------------------------------
The SHR is defined and calculated as follows:
[GRAPHIC] [TIFF OMITTED] TP02JN10.302
Where both the total and sensible cooling capacities are determined
from the same cooling mode test and calculated from data collected
over the same 30-minute data collection interval.
* * * * *
[FR Doc. 2010-12271 Filed 6-1-10; 8:45 am]
BILLING CODE 6450-01-P