6768 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

DEPARTMENT OF ENERGY

Office of Energy Efficiency and

Renewable Energy

10 CFR Part 430

[Docket No. EE–RM/TP–97–440]

RIN 1904–AA46

Energy Conservation Program for

Consumer Products: Test Procedures

for Central Air Conditioners and Heat

Pumps

AGENCY: Office of Energy Efficiency and

Renewable Energy, Department of

Energy.

ACTION: Proposed rule and public

hearing.

SUMMARY: The Department of Energy

(DOE) is proposing changes to its

regulations on test procedures for

central air conditioners and heat pumps.

Today’s revision of the test procedure is

not expected to alter the minimum

energy conservation standards currently

in effect. The revised test procedure is

up-to-date, more complete and better

organized than the current version. It

should yield more accurate

measurements of the energy efficiency

of central air conditioners and heat

pumps.

DATES: Comments must be received on

or before March 23, 2001. DOE is

requesting a signed original, a computer

disk (WordPerfect 8) and 10 copies of

the written comments. The Department

will also accept e-mailed comments but

you must send a signed original. Oral

views, data, and arguments may be

presented at the public workshop

(hearing) in Washington, DC, beginning

at 9 a.m. on February 7, 2001.

The Department must receive requests

to speak at the workshop and a copy of

your statements no later than 4 p.m.,

January 9, 2001, and we request that you

provide a computer diskette

(WordPerfect 8) of each statement at that

time. The DOE panel will read the

statements in advance of the hearing

and requests that speakers limit oral

presentations to a summary. Attendees

will have an opportunity to ask

questions.

ADDRESSES: Please submit written

comments, and requests to speak at the

public hearing to: Brenda EdwardsJones, U.S. Department of Energy, Office

of Energy Efficiency and Renewable

Energy, Hearings and Dockets, Test

Procedures for Central Air Conditioners

Including Heat Pumps, Docket No. EERM–97–440, EE–41, Room 1J–018,

Forrestal Building, 1000 Independence

Avenue, SW., Washington, DC 20585–

0121. You may send email to:

brenda.edwards-jones@ee.doe.gov. The

hearing will be at the U.S. Department

of Energy, Forrestal Building, Room 1E–

245, 1000 Independence Avenue, SW.,

Washington, DC. You can find more

information concerning public

participation in this rulemaking

proceeding in section VI, ‘‘Public

Comment,’’ of this notice.

You may read copies of the transcript

of the public hearing and public

comments at the Department of Energy

Freedom of Information Reading Room,

U.S. Department of Energy, Forrestal

Building, Room 1E–190, 1000

Independence Avenue, SW.,

Washington, DC 20585, (202) 586–3142,

between the hours of 9 a.m. and 4 p.m.,

Monday through Friday, except Federal

holidays.

FOR FURTHER INFORMATION CONTACT:

Michael G. Raymond, U.S. Department

of Energy, Energy Efficiency and

Renewable Energy, Mail Station EE–

41, Forrestal Building, 1000

Independence Avenue, SW,

Washington, DC 20585–0121, (202)

586–9611

Eugene Margolis, Esq., U.S. Department

of Energy, Office of General Counsel,

Mail Station GC–72, Forrestal

Building, 1000 Independence Avenue,

SW, Washington, DC 20585–0103,

(202) 586–9526

SUPPLEMENTARY INFORMATION: The

proposed rule incorporates, by

reference, seven test procedures

published by the American Society of

Heating, Refrigerating, and AirConditioning Engineers, Inc. (ASHRAE),

as follows:

• Standard 23–1993, ‘‘Methods of

Testing for Rating Positive Displacement

Refrigerant Compressors and

Condensing Units.’’

• Standard 37–1988, ‘‘Methods of

Testing for Rating Unitary AirConditioning and Heat Pump

Equipment.’’

• Standard 41.1–1986 (Reaffirmed

1991), ‘‘Standard Method for

Temperature Measurement.’’

• Standard 41.2–1987 (Reaffirmed

1992), ‘‘Standard Method for Laboratory

Airflow Measurement.’’

• Standard 41.6–1994, ‘‘Standard

Method for Measurement of Moist Air

Properties.’’

• Standard 41.9–1988, ‘‘A Standard

Calorimeter Test Method for Flow

Measurement of a Volatile Refrigerant.’’

• Standard 116–1995, ‘‘Methods of

Testing for Rating for Seasonal

Efficiency of Unitary Air Conditioners

and Heat Pumps.’’

One test procedure of the American

Society of Heating, Refrigerating, and

Air-Conditioning Engineers/Air Moving

and Conditioning Association, Inc.

(ASHRAE/AMCA) is incorporated by

reference:

• Standard 51–1999, ‘‘Laboratory

Methods of Testing Fans for Rating.’’

One test procedure of the AirConditioning and Refrigeration Institute

(ARI) is incorporated by reference:

• Standard 210/240–1994, ‘‘Unitary

Air-Conditioning and Air-Source Heat

Pump Equipment.’’

You can view copies of these

standards at the Department of Energy’s

Freedom of Information Reading Room

at the address stated above. You can

also obtain copies of the ASHRAE,

ASHRAE/AMCA and ARI Standards

from the American Society of Heating,

Refrigerating, and Air-Conditioning

Engineers, Inc., 1971 Tullie Circle, NE,

Atlanta, GA 30329, http://

www.ashrae.org; and the AirConditioning and Refrigeration Institute,

4301 North Fairfax Drive, Suite 425,

Arlington, VA 22203, http://

www.ari.org, respectively.

I. Summary of Proposed Rule

II. Introduction

A. Authority

B. Background

1. Short and Long-term Plans

2. Background for Today’s Proposed

Rulemaking

III. Discussion of Comments

A. General

1. Non-ducted split system air conditioners

and heat pumps

2. Small-duct, high-velocity systems

3. Non-defrost (limited-range) heat pumps

4. Heat pumps that incorporate a heat

comfort controller

5. Other commercially-available equipment

that should be covered in the test

procedure

B. Definitions

1. Revise definition 1.20 ‘‘Demand-defrost

control system’’.

C. Testing Conditions

1. Section 2.2.4. Wet-bulb temperature

requirements for air entering the indoor

and outdoor coils.

2. Section 2.2.5. Additional refrigerant

charging requirements

D. Testing Procedures

1. Section 3.1.4. Indoor air volume rates for

a variable-speed, constant CFM blower.

2. Section 3.1.4.1. Cooling air volume rate.

3. Section 3.1.4.1.1. External static

pressure.

4. Sections 3.2.3 and 3.5.3. Testing a twocapacity compressor system.

5. Section 3.3. Capacity adjustments for

barometric effects

6. Sections 3.5.3 and 3.8.1. Cyclic

degradation coefficients

E. Calculations of Seasonal Performance

Descriptors

1. Sections 4.1.4 and 4.2.4. Variable-speed

bin calculations

IV. Summary of Proposed Modifications to

the DOE Air Conditioner and Heat Pump

Test Procedure

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6769

1Public Law 94–163, as amended by the National

Energy Conservation Policy Act, Public Law 95–

619, the National Appliance Energy Conservation

Act of 1987, Public Law 100–12, the National

Appliance Energy Conservation Amendments of

1988, Public Law 100–357, and the Energy Policy

Act of 1992, Public Law 102–486, Part B of Title

III of Energy Policy and Conservation Act, as

amended, is referred to in this proposed rule as

‘‘EPCA’’ or the ‘‘Act.’’ Part B of Title III is codified

at 42 U.S.C. 6291–6309.

A. Update and Add References for

ASHRAE and ARI Standards

B. Air Volume Rates

C. Cyclic Testing

D. Fanless (coil-only) Units

E. Frost Accumulation Test

F. Test Tolerance Tables

G. Pretest Intervals

H. Multi-Capacity Systems

I. Triple-split Systems

J. Time-Adaptive Defrost Control Systems

K. Test Unit Installation

L. Test Apparatus and Measurement/

Sampling Frequency

M. Different Compressor Speeds and

Indoor Fan Capacities Between Cooling

and Heating

N. Secondary Test Requirements

O. HSPF Calculations

V. Procedural Requirements

A. Review Under the National

Environmental Policy Act of 1969

B. Regulatory Review

C. Regulatory Flexibility Review

D. ‘‘Takings’’ Assessment Review

E. Federalism Review

F. Paperwork Reduction Act Review

G. Review Under Unfunded Mandates

Reform Act of 1995

H. Review Under Executive Order 12988,

‘‘Civil Justice Reform’’

I. Review Under the Treasury and General

Government Appropriations Act, 1999

J. Plain Language Review

VI. Public Comment Procedures

A. Written Comment Procedures

B. Issues for Public Comment

C. Public Workshop

1. Procedures for Submitting Requests to

Speak

2. Conduct of Workshop

I. Summary of Proposed Rule

Today’s proposed rule concerns the

testing aspect for central airconditioners and central airconditioning heat pumps. The

Department develops these procedures

for manufacturers to test products to

measure energy efficiency, energy use,

or estimated annual operating cost of a

product. It will interest manufacturers,

but consumers of air conditioners will

see no changes due to this revision,

which brings the test procedure up-todate, and makes it more complete and

better organized. Nearly all the technical

content is preserved and the use of U.S.

customary (i.e., inch-pound) units is

maintained. Air conditioners and heat

pumps that presently meet the NAECA

energy conservation standards will still

meet these standards when rated using

the revised test procedure.

II. Introduction

A. Authority

The Energy Policy and Conservation

Act requires the Department of Energy

to establish the Energy Conservation

Program for Consumer Products. This

program sets test procedures, energy

consumption and efficiency labeling,

and energy conservation standards for

many household, consumer products.1

The Act requires DOE to determine to

what extent a proposed test procedure

would change the energy efficiency or

energy use of a product from the current

test procedure. If we determine that a

new test procedure would change the

efficiency or use of a covered product,

we will amend the standard. To

determine the new energy conservation

standard, we measure the energy

efficiency or energy use of a

representative sample of covered

products that minimally comply with

the existing standard. The average

efficiency of these representative

samples, tested using the amended test

procedure, constitutes the amended

standard. EPCA, Section 323(e)(2).

B. Background

1. Short and Long-Term Plans

This proposed DOE test procedure is

the first step of a planned two-step

revision process. The immediate goal is

to promulgate a revised test procedure

that is up-to-date, more complete and

better organized. Nearly all the technical

content is preserved and the use of U.S.

customary (i.e., inch-pound) units is

maintained. One especially important

goal of this first step is to have air

conditioners and heat pumps that

presently meet the NAECA energy

conservation standards to still meet

these standards when rated using the

revised test procedure.

The second step in the planned

revision process is to convert the DOE

test procedure to using Systeme

Internationale (SI) units while

maximizing compatibility with

pertinent standards of the International

Organization for Standardization (ISO).

The goal of this second step is a DOE

metric test procedure which will also

meet the requirements specified by ISO

for determining capacities, EER(s) for a

‘‘moderate’’ climate, and COP’s. For

example, DOE plans to directly

reference selected ISO indoor and

outdoor test conditions. However, the

DOE test procedure will impose

additional requirements, not found in

the ISO test standards, that allow

determination of the seasonal

performance factors SEER and HSPF.

Presently, the pertinent ISO standards

are either under revision or are being

newly developed so we can not yet fully

determine the extent of compatibility

between the DOE and ISO testing and

rating procedures. DOE, via NIST

personnel, is participating in the

development of the ISO test standards

in an effort to minimize the differences.

A proposed DOE metric test procedure

will be available for industry review

several months after the revision of ISO

standards (5151 and 13253 or, possibly

a combined standard) is completed.

This two-step test procedure revision

will not delay the concurrent revision of

the NAECA energy conservation

standards, nor will standards revision

be delayed because of the planned

conversion of the test procedure to SI

units. Until a DOE metric test procedure

has been promulgated, you will make

predictions of seasonal performance

using the I–P version of the DOE test

procedure, i.e., this revision. This

revised test procedure modifies tests for

certain configurations, but is not

expected to impact the performance

measurements. In the coming years,

when a DOE metric test procedure is

progressing through the rulemaking

process, DOE and stakeholders will

review the best time line for

implementing the metric test procedure

and instituting compatible NAECA

energy conservation standards. As far as

possible, the metric test procedure will

retain the current energy efficiency

descriptors, SEER and HSPF.

2. Background for Today’s Proposed

Rulemaking

The first DOE test procedure covering

central air conditioners and heat pumps

was published in the Federal Register

on December 27, 1979, and became

effective January 17, 1980. 44 FR 76700.

The test procedure was modified once,

in March 1988. 53 FR 8304 (March 14,

1988). Revisions made in 1988 included

expanding coverage to variable-speed

air conditioners and heat pumps,

addressing split-type non-ducted units,

and modifying the method used for

crediting heat pumps that provide a

demand defrost capability.

Five waivers to the DOE test

procedure covering central air

conditioners and heat pumps have been

granted since the 1988 final rulemaking.

Waivers have been granted to two

different brands of non-defrost heat

pumps, to two brands of combined heat

pump-water heating appliances, and for

a line of burner-assisted heat pumps.

Non-defrost heat pumps do not contain

a defrost controller and are designed to

shut the compressor off under operating

6770 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

conditions where frost accumulation on

the outdoor coil is likely. Combined

appliances use an extra condensing coil

to permit the unit to provide domestic

water heating in addition to space

conditioning. Burner-assisted heat

pumps use a gas-fired burner in the

outdoor coil while using electricity to

power the refrigerant compressor.

In revising this test procedure, we

considered whether actions could be

taken to eliminate the continued need

for any of the granted waivers. Today’s

proposed rule covers testing and

calculation of HSPF for non-defrost, allelectric heat pumps, eliminating the

first two of the five waivers discussed in

the preceding paragraph. As the market

for dual fuel heat pumps, including

burner assisted heat pumps, and

combined heat pump-water heating

appliances grows, we will pursue the

development of separate test procedures

for these devices, which will eliminate

the remaining three waivers.

We completed the first draft of this

revised test procedure for central air

conditioners and heat pumps in June

1996. The draft test procedure

addressed equipment features presently

not covered and improved upon the

completeness and readability of the

document. The June 1996 draft test

procedure was distributed to members

of the HVAC industry and academia for

comment on the proposed changes.

Several parties provided comments on

the June 1996 draft test procedures. We

determined that more input on several

issues would be beneficial, and DOE

held a workshop on September 25,

1997. The workshop focused on five

areas of concern. The first area was the

identification of commercially-available

equipment that is not adequately

addressed in the existing test procedure.

Examples include non-defrost heat

pumps, heat pumps that incorporate a

heat comfort controller, multi-split nonducted heat pumps, two-capacity heat

pumps that are sized to meet the space

cooling load while operating at low

capacity, small duct systems, and

single-speed heat pumps having a

variable-speed indoor fan that is

modulated based on outdoor

temperature. The second issue was the

appropriate way to conduct steady-state

and cyclic testing on units having a

variable-speed, constant-air-volume-rate

indoor blower. The third area of concern

dealt with appropriate adjustments in

order to credit a demand defrost

capability and to account for the effect

of barometric pressure. A group of items

that pertained to specifics on lab testing

procedures composed the fourth topic of

discussion. Examples included how to

best test packaged units having leakage,

whether to limit manufacturer-specified

special lab set-up requirements,

recommended static pressure tap

manifolding, and electrical energy

measurement requirements. The fifth

issue concerned the development of

new defaults for the cyclic degradation

coefficients, as an alternative to having

to conduct tests to determine the

coefficients.

A transcript of the discussions at the

September 25 workshop is available for

review in the DOE Freedom of

Information Reading Room. The section

below summarizes comments received

throughout the revision process. During

the workshop, several items were

introduced but left unresolved. In many

of these cases, ARI industry members

indicated that they would offer more

input and, where possible, a consensus

response in the months following the

workshop.

At the invitation of ARI, NIST

participated in a meeting and

teleconferences hosted by the ARI

Unitary Small Equipment Engineering

Committee in September and October of

1997 and February of 1998. For the

meetings/teleconferences that followed

the September 25, 1997 Workshop,

discussions on DOE test procedure

issues focused mainly on eleven issues,

namely: (1) Small duct systems, (2) nondefrost systems, (3) multiple split heat

pumps, (4) variable-speed, constant

CFM blowers, (5) heat pumps that

incorporate a heat comfort controller, (6)

two capacity heat pumps that are sized

to meet the design cooling load while

operating at low speed, (7) definition for

a demand defrost system, (8) effects of

barometric pressure, (9) testing of

packaged systems with internal leaks,

(10) special laboratory setups, and (11)

new default values for the cyclic

degradation coefficients, CD (the

measure of performance degradation

from cycling losses). Written comments

were received dated 24 November 1997

from ARI (ARI, No. 6) that addressed

these particular areas. ARI formed a task

group to provide additional input on

three items: #4, #6, and #9. ARI also

hoped to provide data and a strawman

approach for addressing item #11. These

last four items were discussed during a

February 1998 teleconference but ARI

provided no consensus by the end of

February, the cutoff date imposed by

DOE.

The 24 November 1997 written

comments from ARI are included among

the overall comment summary provided

below. With regard to unresolved issues

associated with ARI items #4, #6, and

#9, we implemented changes based on

the information gathered to date.

Today’s rulemaking proposes no

changes for the CD defaults that may be

used instead of conducting extra tests.

DOE is willing to investigate and

consider new CD defaults based on the

hardware features of the air conditioner

or heat pump. ARI and its members

have thus far provided no test data nor

made any recommendations concerning

the hardware features (e.g., type of

expansion device, with or without a

time delay relay on the indoor fan, type

of compressor, off-cycle power

consumption, refrigerant charge

quantity, rated capacity, etc.) that

should be included in a statistical

analysis to identify the primary factors

and the associated correlations.

A draft of this proposed test

procedure was posted to the Office of

Codes and Standards web site in

October 1998. This document was

revised during the summer of 1999 to

comply with the President’s

Memorandum of June 1, 1998, ‘‘Plain

Language in Government Writing.’’

Thereafter, some sections of the

proposed test procedure were

reorganized and amended in response to

comments received during the DOE

internal review process.

In the proposed central air

conditioner and heat pump standards

rule (65 FR 59590, October 5, 2000), the

Department discussed issues associated

with mandating thermostatic expansion

valves, or TXVs, to help maintain

equipment performance under improper

charge or airflow. In the standards final

rule, we decided not to adopt a TXV

requirement, but considered pursuing

modifications to this test procedure to

encourage the use of TXVs. Such

modifications will not be part of this

rulemaking, but will be considered in a

separate process. Related issues that

may be discussed in the separate

process include the alternate rating

method for mixed systems. The

alternate rating method is not a part of

this revision, which concerns only

appendix M to subpart B of 10 CFR part

430. The alternate rating method is

discussed in 10 CFR § 430.24(m). In the

last revision of this test procedure in

1988, the adoption of a standard rating

procedure for untested combinations of

split systems was proposed, but the

Department decided not to include a

standard rating procedure in the test

procedure rule. Instead, the Department

requested the National Bureau of

Standards to develop a rating method

available to any manufacturer to use in

rating untested combinations.

Manufacturers may use this method or

any other after obtaining the

Department’s approval. It may again be

time to discuss a standard mixed system

rating method included in the test

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6771

procedure. These issues will be

discussed in a workshop to be held in

the spring of 2001.

III. Discussion of Comments

Following the September 1997

workshop, we received comments from

the ARI Unitary Small Equipment

Engineering Committee and individual

ARI members, Proctor Engineering

Group, and from the Florida Solar

Energy Center. We grouped these

comments into the following categories

corresponding to sections of the test

procedure: General, Definitions, Testing

Conditions, and Testing Procedures.

(ARI, No. 6, PEG, No. 3, FSEC, No. 7)

A. General

1. Non-ducted Split System Air

Conditioners and Heat Pumps

Non-ducted units may use one or

more indoor coils. When two or more

indoor coils are used, they may operate

in response to a single or multiple room

thermostats. Standards of the

International Organization for

Standardization (ISO) differentiate nonducted units as single or multiple room

thermostat systems. We refer to

equipment having one or more indoor

coils all controlled by a single indoor

thermostat as mini-split systems. We

refer to equipment that uses two or more

indoor thermostats to regulate the

operation of two or more indoor coils as

multi-split systems.

The current DOE test procedure does

not differentiate between mini-split and

multi-split systems. Both are tested and

seasonal calculations are based on all

indoor coils operating simultaneously.

The zoning capability of multi-split

units, though not operating some indoor

coils, is not credited.

As part of its 1992 waiver petition,

EnviroMaster International (EMI) sought

‘‘to test its three and four zone MC/MH

series systems in the manner prescribed

in the DOE test for two zone systems.’’

57 FR 53736 (November 12, 1992). The

modification noted in the Decision and

Order was to change the wording of

Section 3.1.7 to the following:

‘‘Subsystems of multizone split-type ductless

systems shall be tested as a single system.

The system energy efficiency shall be based

on the sum of the measured capacities of all

of the zones in the system divided by the

total input power used by the subsystems

compressors, outdoor fans, indoor air

handlers, and any additional power used by

the system.’’

ARI commented on this issue: ‘‘Our

members do not believe any change is

necessary to the test procedures to

address multiple split heat pumps. We

are unaware of any unfair treatment of

this product in the industry by the

current test methods.’’ (ARI, No. 6 at 1).

We propose no changes in today’s test

procedure. The option of testing each

zone separately is possible. Such extra

testing should provide a more complete

description of the unit’s capabilities.

However, the benefits would have to be

weighed against the considerable

increase in the testing burden. The

Department recommends tabling this

issue until a multi-split manufacturer

deems that a different and, most likely,

more burdensome test approach is

needed.

2. Small-duct, High-velocity Systems

Unico originally requested that DOE

add a new class (or subclass) of central

air conditioners and heat pumps that

covered small-duct, high-velocity

(SDHV) systems. Unico recommended

changes to the test procedure that were

coupled with DOE issuing separate

NAECA standards for SDHV systems.

The main test procedure changes were

to impose higher minimum external

static pressures and lower maximum air

volume rates requirements on SDHV

systems. Unico also provided a

proposed definition for SDHV systems.

(Unico, No. 5 at 2).

Unico noted how small duct systems

differ from more conventional systems:

external static is typically 1.5 inches of

water, air volume rate is usually onehalf of a conventional system, duct

outlets into the room are typically two

inches in diameter, and air velocity

entering the room is in the 800 to 2000

feet per minute range. ‘‘We feel this

product is different enough that it * * *

should be considered for a different

class. We have different classes for room

air conditioners; we have different

classes for packaged terminal units and

ductless systems versus ducted

systems.’’ (Unico, No. 2HH at 42). ARI

commented: ‘‘ARI believes that no

changes to the existing test procedure

are necessary for these products. They

are currently tested and rated in

accordance with the existing procedure.

Furthermore, ARI does not believe a

different product class or category

should be created for small-duct

systems, since that would allow for a

potentially separate efficiency standard.

They should be held to the same

minimum efficiency standards as

conventional systems. There is concern

that a separate product class could open

a loophole in the regulations. Other

products might be specifically designed

to meet the criteria of the new class,

with the only intention being that they

would be subjected to a less stringent

efficiency standard, while still used in

applications for typical equipment.’’

(ARI, No. 6 at 1).

Unico later submitted an alternative

proposal to DOE. In its alternative

proposal, Unico plans to exercise the

option of testing its line of SDHV units

as coil-only units. In the Unico product

line, the blower assembly is sold

separately from the indoor coil

assembly. The only change in the test

procedure needed to implement this

alternative approach is to relax the

maximum pressure drop allowed when

testing coil-only units. Presently, the

test procedure states that the pressure

drop across the indoor coil assembly

must not exceed 0.30 inches of water.

Unico requested that the limit be

increased, preferably to 0.50 inches of

water.

Today’s proposed test procedure sets

a higher pressure drop limit of 0.5

inches of water when testing coil-only

units that meet the definition of a smallduct, high-velocity system. The

proposed definition is given in section

1.46. We welcome comments on this

action. Possible points for consideration

include whether the action is acceptable

as proposed or if incorporated in

combination with a different default fan

power and heat adjustment.

3. Non-defrost (Limited-range) Heat

Pumps

We granted the first of two waivers for

non-defrost heat pumps to Airlex in

1988. 53 FR 52216 (December 27, 1988).

The waiver called for testing at 47 °F

and 62 °F in lieu of testing at 35 °F and

17 °F. HSPF was calculated. Airlex, to

the knowledge of DOE, has since gone

out of business. We granted the second

waiver to EMI in November 1992. 57 FR

53736 (November 12, 1992). Unlike

Airlex, EMI did not seek to report HSPF

and so did not offer proposed

modifications to the DOE test

procedure. We required that EMI state

in its printed materials on its nondefrost products that ‘‘no HSPF value

has been measured since the heat pump

cannot be operated at temperatures

below 35 °F.’’

At this time, non-defrost heat pumps

appear to be limited to non-ducted,

multi-zone, multi-split heat pumps

having multiple refrigeration systems

where one refrigeration system may be

heating while another is cooling. In

such systems, having one refrigeration

system conduct a defrost while the other

refrigeration system(s) is cooling is

apparently quite difficult (see below

EMI comment). No opposition was

voiced at the workshop to a DOE

proposal to cover non-defrost heat

pumps in the test procedure. We also

6772 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

received the following comments at the

workshop:

In response to the question on why

EMI can not make its non-ducted, multirefrigeration system, multi-split heat

pumps defrost, EMI stated ‘‘we have put

preliminary designs together, but we’ve

never been able to successfully control

the defrost cycle while operating all the

circuits.’’ (EMI, No. 2HH at 23). Trane

spoke against the option of creating a

new class and a new NAECA HSPF

energy standard for non-defrost heat

pumps. (Trane, No. 2HH at 24). An ARI

representative said that presently a

multi-zone multi-split would be tested

with all refrigeration systems operating

in the same mode. (ARI, No. 2HH at 23).

In written comments received following

the workshop, ARI stated: ‘‘For the same

rationale as with small duct systems,

ARI does not believe a separate product

class or category is needed for nondefrost heat pumps. We also

recommend no change in the current

test procedure to accommodate nondefrost systems. As discussed above,

they should be held to the same

minimum efficiency standards as

conventional systems.’’ (ARI, No. 6 at 1).

Since the workshop, DOE received

information on non-ducted, multirefrigeration system, multi-split heat

pumps made by two manufacturers

other than EMI. Both of these competing

multi-split products provide a defrost

capability. The key differentiating

feature is that these units do not provide

the option of simultaneous heating and

cooling like the EMI product. EMI

apparently values this simultaneous

cooling/heating capability more than a

defrost capability while these other two

manufacturers do without the

simultaneous mode feature in return for

being able to defrost. To date, we have

found no product that provides both the

simultaneous heating/cooling feature

and a reverse defrost cycle capability.

From a test procedure standpoint,

several options are available. One

option, in line with ARI’s comment, is

to make no applicable changes to the

test procedure and allow the existing

EMI (and Airlex) waivers to remain.

This option defers the issue until we

receive another waiver request for a

non-defrost heat pump. A second option

is to make additions to the test

procedure so that the HSPF of any type

of non-defrost heat pump could be

evaluated. A third option is to exclude

heat pumps that are designed to

simultaneously heat and cool ‘‘whether

they can defrost or not’’ from the scope

of the test procedure. The rationale for

exclusion would be that such units

generally compete with commercial

applications where packaged terminal

heat pumps and air conditioners are

used and so should be tested and rated

in a manner comparable to the approach

used for packaged terminal equipment

(i.e., heating performance descriptor

becomes COP at 47 °F and the

equipment has no HSPF rating). For this

third option, the test procedure could

either be changed to cover all other nondefrost heat pumps (even though DOE

knows of only the EMI simultaneously

heat and cool, non-defrost heat pump)

or no changes could be made, again

deferring until we receive another

waiver petition.

DOE requests comment on the above

three and any other options for handling

non-defrost heat pumps. To provide an

understanding of the test procedure

changes required to cover non-defrost

heat pumps, we include in today’s

proposed test procedure (see Sections

3.6.1.1 and 4.2.1.1) the steps required to

test and rate most conceivable types of

single-speed, non-defrost heat pumps.

4. Heat Pumps That Incorporate a Heat

Comfort Controller

Heat comfort controllers modulate the

operation of the resistive elements of a

heat pump to minimize temperature

swings of the heated supply air when

operating below the heat pump’s

balance point. Frequently, they seek to

maintain a minimum delivery

temperature when operating above the

balance point. This latter application

can cause the system to use more

electrical energy than the heat pump

alone would use to meet the building

load.

At the 25 September 1997 DOE

workshop, the issue was discussed at

some length. The workshop members

noted that the item can be both an OEM

product that is an integral part of the asshipped heat pump or it can be a field

added accessory that is provided by the

heat pump manufacturer or, more

commonly, by a third party supplier.

Also, assuming that the test procedure

was modified to cover heat pumps with

a heat comfort controller, no workshop

invitee spoke in favor of new and

separate NAECA standards for such

products. The following points were

also made at the workshop:

ARI stated if the manufacturer incorporates

a heat comfort controller as an OEM feature,

it should be covered by the test procedure.

(ARI, No. 2HH at 31). Trane stated if the test

procedure is modified to cover heat comfort

controllers, the rating should be based on

operating the controller at its maximum

delivery temperature. (Trane, No. 2HH at 60).

Proctor Engineering commented: ‘‘Units

designed to operate with strip heat above the

balance temperature should not receive any

special consideration in the test process or

the [NAECA] Standard. Allowing special

consideration will open the door to lower

efficiencies in the field where installation

errors already result in excessive strip heat

use.’’ (PEG, No. 3 at 3). ARI commented: ‘‘We

request DOE to develop a rating procedure

for heat pumps that incorporate the use of

electric resistance heat above the balance

point. The procedure should be based on the

highest indoor air delivery/supply

temperature setting that the control system

allows, so that the most conservative rating

will be derived. Any heat pump that uses this

feature, and still meets the minimum HSPF

standard should be permitted. However, the

existing ICC Model Energy Code prohibits

such systems, because there is no rating

method for them.’’ (ARI, No. 6 at 2).

Today’s proposed test procedure

covers heat comfort controllers as

applied to most types of single-speed

heat pumps. With the heat comfort

controller disabled, conduct all the

same heating mode tests. Following the

normally conducted heating mode test

at 47 °F outdoor temperature, conduct

an extra abbreviated test with the

controller enabled to determine the air

delivery temperature when the

controller is set to its maximum setting

(see Section 3.1.9). We describe

proposed steps for calculating the HSPF

of a single-speed heat pump having a

heat comfort controller in Section

4.2.1.2.

5. Other Commercially-available

Equipment that Should Be Covered in

the Test Procedure

One focus of the 25 September 1997

DOE workshop was to identify

commercially-available equipment that

is not covered by the DOE test

procedure. For the majority of

equipment discussed at the workshop,

we provide separate discussions

elsewhere in this summary. Equipment

types that were discussed and thought

not to be a commercial product

included: (1) Triple-capacity heat

pumps and (2) units that use a twocapacity (two-stage) compressor and a

variable-speed indoor fan that is

modulated at each fixed stage of

compressor operation.

B. Definitions

1. Revise Definition 1.20 ‘‘Demanddefrost Control System’’

ARI commented: ‘‘We recommend

that DOE expand the current ARI

Standard 210/240 definition of a

demand defrost system to include

sampling intervals of a minimum of 10

minutes and not to have the definition

pertain to time adaptive systems.’’ (ARI,

No. 6 at 2)

DOE’s goal is to improve upon the

existing definition provided in ARI

Standard 210/240–94, Section A1.11,

and in particular, to stop allowance of

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6773

the (maximum) 3 percent HSPF credit to

units that truly do not offer a demand

defrost capability. We provide a

proposed definition for a ‘‘demanddefrost control system’’ that seeks to be

consistent with ARI’s comment as

Definition 1.20.

C. Testing Conditions

1. Section 2.2.4. Wet-bulb Temperature

Requirements for Air Entering the

Indoor and Outdoor Coils

ARI commented: ‘‘In order to provide

better repeatability when testing

packaged systems, which may be

susceptible to internal air leakage, ARI

believes it may be necessary to specify

an outdoor dew point temperature when

units are located in the outdoor chamber

(ambient). A task group has been formed

to investigate this issue and we will

provide our recommendations to DOE as

soon as they are available.’’ (ARI, No. 6

at 2).

DOE’s understanding of the impact of

a leak that could result in optimistic

results is as follows:

(1) Leak of outdoor air to a location

upstream of the indoor coil but

downstream of the test facility inlet wet

bulb temperature (dew point, relative

humidity) sensor. If the outdoor dew

point is lower than the indoor dew

point, the measured latent capacity will

be higher than the true latent capacity,

while the measured sensible capacity

will be lower than the actual sensible

capacity. The effect on total capacity

will depend on dry bulb temperature of

the outdoor air (82 °F or 95 °F) and the

depression of the outdoor dew point

relative to the indoor dew point.

(2) Leak of outdoor air to a location

downstream of the indoor coil. Results

are the same as (1) except that the

depression of the outdoor dew point

would have to be greater to overcome

the negative effect on sensible capacity.

The measured air volume rate on the

indoor side would be higher than the

actual rate at the coil and would thus

increase the perceived sensible and

latent capacity.

DOE’s understanding of the other

factors that are related to this issue are

as follows. First, psychometric rooms

have difficulty achieving and

maintaining outdoor wet bulb

temperatures in the mid 70’s °F and

higher during the A and B Tests. If the

internal leakage is significant, obtaining

a 6 percent energy balance would be

difficult to achieve. Although

potentially frustrating for a third party

tester, the lack of an energy balance

should provide impetus for the

manufacturer to reduce the leakage. You

can avoid the difficulty in maintaining

the outdoor wet bulb temperature

during the C and D dry coil tests by

meeting the requirements of achieving a

dry indoor coil, and by using the

equation for determining sensible

cooling capacity, as opposed to total

cooling capacity.

In an effort to avoid potential cases

where the leakage causes an optimistic

result while still providing an energy

balance of 6 percent or less, DOE

recommends operating at an outdoor

dew point temperature that is the same

as the indoor dew point temperature

during wet-coil tests where the unit

does not reject condensate to the

outdoor coil. DOE proposes a test

tolerance of ±3.0 °F in the agreement of

the average outdoor dew point

temperature with the average indoor

dew point temperature. In nominal

terms, the target outdoor wet bulb

temperatures will be 71.7 °F and 67.7 °F

for the A and B Tests, respectively.

During heating mode tests, leaks

could cause problems if the Outdoor Air

Enthalpy Method is used to provide a

secondary check of capacity. The

proposed test procedure includes a

recommendation for regulating the

indoor side wet bulb temperature in an

effort to minimize the difference

between the indoor and outdoor-side

dew point temperatures.

2. Section 2.2.5. Additional Refrigerant

Charging Requirements

ARI stated: ‘‘We believe the test

procedure, as currently written,

reasonably addresses the issue of special

laboratory setups when conducting

tests, as prescribed in manufacturer’s

installation instructions. Therefore, we

do not recommend any change with

respect to this issue.’’ (ARI, No. 6 at 3).

Presently, any installation step is

acceptable so long as it is specified in

the manufacturer’s installation

instructions, including remarks that

only apply if conducting laboratory

testing. As discussed at the 25

September 1997 DOE workshop, the

difficult issue is where to draw the line.

Some special setups are justified and/or

required when lab testing. DOE is only

excluding special lab set-ups for

refrigerant charging. With assistance

from ARI and third-party laboratories,

DOE will monitor test setup

requirements to determine if

manufacturers are specifying

installation instructions inconsistent

with the majority of lab installations or

otherwise contrary to field practices.

Furthermore, DOE is seeking assistance

in establishing installation guidelines

for items such as pre-washing of coils

(e.g., what cleaning agent to use, basic

steps that specify the extent of the

cleaning), run-in times on compressors,

conditions where components (e.g.,

crankcase heaters) are or are not

electrically connected, exclusion of labonly (or 25 feet only) lineset

specifications, etc. These guidelines will

be incorporated into future revisions of

the test procedure to assist in obtaining

consistency in the testing.

In today’s proposed test procedure,

the title of Section 2.2.5 changes from

‘‘Exclusion of special setup

requirements if stated in the

manufacturer published installation

manual’’ to ‘‘Additional refrigerant

charging requirements.’’ The section is

included for two reasons. The first is to

disallow the specification of two

refrigerant charging criteria, one that

applies for lab testing and one that

applies for a field installation. The fact

that a lab setting provides better quality

control is not sufficient for permitting

lab testing using a different charging

criteria. The second reason for today’s

Section 2.2.5 is to avoid discrepancies

and delays when third party testing is

conducted. The third party testing

facility should not have to consult with

the manufacturer as to how the unit is

to be charged. In the case of a

certification failure, the issue of whether

the testing facility charged the unit

correctly should only be based on

whether the manufacturer’s charging

criteria, as specified in the unit’s

installation instructions, were followed.

D. Testing Procedures

1. Section 3.1.4. Indoor Air Volume

Rates for a Variable-Speed, Constant

CFM Blower

ARI stated: ‘‘ARI is aware of the need

to consider more explicit procedures for

testing units with variable speed

blowers. Therefore, we have organized a

task group to develop a prescribed test

method for testing units with variable

speed blowers, and we will pass our

recommendations on to DOE as soon as

they are available.’’ (ARI, No. 6 at 1)

Today’s proposed test procedure

contains several changes from the

existing test procedure to address

testing of units having a variable-speed,

constant CFM blower. For all tests, the

exhaust fan of the air flow measuring

apparatus is regulated to obtain an

external static pressure that is as close

to, while not being less than, the

minimum external static pressure

specified in the test procedure (see

3.1.4.1.1(b), 3.1.4.4.1, 3.1.4.4.2 and

3.1.4.4.3(b)). (The air flow measuring

apparatus, by comparison, is not

regulated to obtain the specified air

volume rate, as is done when testing

units having other than a constant-airVerDate 11<MAY>2000 00:31 Jan 21, 2001 Jkt 194001 PO 00000 Frm 00007 Fmt 4701 Sfmt 4702 E:\FR\FM\22JAP2.SGM pfrm08 PsN: 22JAP2
6774 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

volume-rate indoor fan.) For some units,

one or more tests may have to be

conducted at an external static pressure

that is higher than the required

minimum value because of instability

problems encountered when trying to

reduce the external static pressure to the

specified minimum. In such cases, steps

are outlined for correcting the test

results if the difference between the astested and the specified minimum

external static pressure is 0.03 inches of

water or more. An example of the

proposed correction method is provided

in the last paragraph of Sections 3.3 and

3.7. For systems that operate at multiple

air volume rates, the fan laws are used

to approximate the target external static

pressure for tests conducted at other

than the air volume rate used during the

A2 and/or H12 test.

The proposed test procedure includes

a check of the agreement between the

lab-measured and manufacturercertified air volume rates. Today’s

proposed test procedure calls for the

two values to agree within 8 percent

(see 3.1.4.1.1(b), 3.1.4.2, 3.1.4.4.2, and

3.1.4.4.3(b)). This percentage is

proposed based on manufacturer’s

comments on the variability of the

variable-speed motors relative to

estimates of the impact on rated

performance caused by an 8 percent

deviation. Using the heat pump

computer modeling program HPSIM,

DOE finds that an 8 percent deviation in

SCFM is expected to have a negligible

impact on both capacity and EER at the

B Test condition while still keeping the

maximum impact on capacity at the A

Test condition in the 2 percent range.

DOE asks that manufacturers provide

feedback on the proposed 8 percent

tolerance as well as findings from lab

testing and computer modeling on the

impact on capacity and EER of airflow

changes in the 5 to 10 percent range.

Cyclic tests on units having a constant

CFM blower may be conducted with or

without the indoor fan enabled. If the

cyclic test is conducted with the blower

disabled, steps for correcting for the

power draw of the blower are specified

(see 3.5 and 3.5.1).

2. Section 3.1.4.1. Cooling Air Volume

Rate

This issue is of interest to the ISO

working group that is revising its air

conditioner and heat pump test

standards. The adoption of a maximum

air flow limit has thus far been opposed

by the majority of the ISO working

group member countries. The following

comments were made at the DOE

workshop. A Trane representative noted

that the 37.5 SCFM per 1000 Btu/h (450

SCFM per ton) maximum air flow

requirement is long-standing and is of

value because it (1) sets a de facto

maximum sensible heat ratio and (2)

keeps the air flow in a range that avoids

water being blown off the wetted

evaporator. (Trane, No. 2HH at 193). A

representative of York International

suggested reevaluating the basis for the

37.5 SCFM per 1000 Btu/h maximum

while considering both full load and

part load capacity conditions. (York, No.

2HH at 197).

For today’s proposed revision, no

change is made in the maximum air

volume rate limit. DOE sees such a limit

as providing a hedge against promoting

efficiency gain at the expense of

compromised latent capacity, especially

for coil-only units. The limit also helps

in having the A and B Tests conducted

with a fully wetted coil that, in turn,

makes the capacity fluctuations less and

the collection of 30 minutes of steadystate data more readily obtainable. DOE

encourages and would participate in

investigations on whether this limit

should be other than its present value of

37.5 SCFM per 1000 Btu/h, or whether

an alternative mechanism, such as a

limit on sensible heat ratio, should be

considered.

Discussion of this issue is timely

because no such maximum air volume

limit is presently included in ISO

Standards 13253 and 5151 for ducted

and non-ducted air conditioners and

heat pumps. A U.S. proposal to adopt

the metric-equivalent of the 37.5 SCFM

per 1000 Btu/h limit was voted down by

the ISO working group that is presently

revising ISO Standards 5151 and 13253.

The vast majority of other member

countries on the working group perceive

air volume rate as a design parameter

that should not be impacted by a rating

standard. The ISO standards provide

capacity test conditions that correspond

to a hot, dry climate where latent

capacity is not a concern. ISO also

provides capacity test conditions for a

cool climate. ISO working group

members from countries that will rate at

this cool climate condition argue that

high air volume rates are needed in

order to assure that the air delivery

temperature is not objectionably cool.

Finally, with the exception of the U.S.,

most countries represented on the ISO

working group are predominantly

concerned with non-ducted products

and calorimeter testing where indoor air

volume rate is not typically measured.

The goal when converting the DOE

test procedure to a metric format is to

make it ISO compatible. Most ducted

units sold in the U.S. today are rated at

an air volume rate that is less than the

37.5 SCFM per 1000 Btu/h upper limit.

This fact suggests that maximum

efficiency is achieved at air volume

rates lower than 37.5 SCFM per 1000

Btu/h. Thus, having a upper limit may

not be important enough to warrant a

deviation from ISO. Either way, now is

the time to discuss this issue since the

revision of the ISO Standard 13253 is

still underway. However, it seems

unlikely that ISO will adopt an upper

limit on air volume rate.

3. Section 3.1.4.1.1. External Static

Pressure

Proctor Engineering Group

recommended the following changes to

make the test specification conform

better to measurements of installed

systems. When testing units having an

indoor fan, ‘‘the minimum static

pressure should be revised to:

• 0.50 inches of water column for all

systems, or

• The maximum allowable external

static pressure specified by the

manufacturer, whichever is less.’’

When rating fanless units, ‘‘the

default Btu/hr (watt draw of the indoor

fan motor) should be revised to 2000

Btu/hr per 1000 cfm (586 Watts per

1000 cfm).’’ For comparison, the

external static pressure and fan heat/

power defaults presently used in the

existing DOE test procedure are 0.1,

0.15, and 0.2 inches of water, with the

assigned value being a function of the

unit’s rated capacity. The presently

referenced fan heat/power default

adjustment is 1250 Btu/h per 1000

SCFM (365 Watts per 1000 SCFM).

Proctor Engineering Group supported its

proposed changes by providing results

from field measurements on 28 new

systems in new construction in Phoenix,

Arizona. (PEG, No. 3 at 3).

The Florida Solar Energy Center sent

a report on field monitoring work which

indicated that ‘‘the standard assumption

of an external static pressure of 0.2

inches of water column (IWC) for the air

handler fan was far lower than the

typical values encountered in the field.

The average we measured in 14

evaluated installations was 0.54 IWC

(range was 0.27 to 0.91 IWC).’’ The

commenter goes on to state his strong

belief that ‘‘the ARI test condition

should be modified to 0.5 IWC to better

reflect the actual performance that will

be achieved by the air conditioners

operating under realistic conditions.

Because of this change, the watt draw of

the fan motor (and heat released into the

supply air stream) should also be

revised to reflect the increase in fan

power from this change.’’ (FSEC, No. 7

at 1)

Because of concern that such changes

would impact the SEER and HSPF of

units that have ratings at or near the

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6775

NAECA minimum standard levels, DOE

does not plan to change the static

pressure requirements in this revision of

the test procedure. Instead, DOE will

continue dialogue with the working

group that is revising ISO Standard

13253. When the revision of ISO 13253

is completed, DOE will determine the

suitability of incorporating part or all of

this test procedure in the DOE metric

test procedure. ISO Standard 13253 is

presently under revision with the

present draft containing the following

requirements for the minimum external

static requirements. (The Inch-Pound

equivalent values are not part of the

proposed 13253 table but are included

here to aid the reader.)

Minimum static pressures

Standard capacity ratings

(kW) [kBtu/h]

Minimum external static

pressure (Pa) [inches of H2O]

0 to <8 [0 to <27.3] ................................................................................................................................................. 25 [0.10]

8 to <12 [27.3 to <41.0] .......................................................................................................................................... 37 [0.15]

12 to <20 [41.0 to <68.3] ........................................................................................................................................ 50 [0.20]

20 to <30 [68.3 to <102.4] ...................................................................................................................................... 62 [0.25]

30 to <45 [102.4 to <153.6] .................................................................................................................................... 75 [0.30]

45 to <82 [153.6 to <279.9] .................................................................................................................................... 100 [0.40]

82 to <117 [279.9 to <399.3] .................................................................................................................................. 125 [0.50]

117 to <147 [399.3 to <501.7] ................................................................................................................................ 150 [0.60]

[Above 147 Above 501.7] ........................................................................................................................................ 175 [0.70]

The numbers up to 20 kW are

consistent with the values presently

cited in the existing and in this

proposed revision of the DOE test

procedure.

As for fanless units, the draft revision

of ISO 13253 contains a

thermodynamically-based equation

(volume flow rate x total pressure drop

divided by fan static efficiency x fan

motor efficiency) to estimate default fan

heat/power adjustments. Total pressure

drop is taken as the sum of the

following:

(1) The lab-measured pressure drop

across the indoor, fanless unit

(2) The applicable minimum external

static pressure listed in the above table

(3) An estimate for the pressure drop

across a typical blower cabinet (=50 Pa).

The minimum external static pressure

requirements thus impact both the

rating for fanless and blower coil units.

For residential size equipment, ISO

Standard 13253R uses the following

empirical fits to determine the fan static

(SE) and fan motor efficiencies (MEr).

SE=0.1881*Ln(Pe + Pc + 50) ¥ 0.4700

MEr=0.060*Ln[Q*(Pe+Pc + 50)

/SE]+0.123

Where Q is the measured air volume

rate of standard air (m3/s), Pe is the

minimum external static pressure (Pa),

and Pc is the internal static pressure

drop of the indoor coil cabinet assembly

measured during the cooling capacity

test (Pa).

Any proposal to raise the minimum

external static pressure requirements

and possibly tweak the ISO approach for

estimating fan heat/power adjustments

will first have to be agreed upon by the

U.S. delegates on the ISO working

group. If the proposal is endorsed by the

U.S. delegation, then the delegation

must submit the proposed change for

the consideration of the full working

group. NIST, as a member of the U.S.

delegation, has raised the issue for

discussion among the U.S. delegation.

At this point, the U.S. delegation does

not have plans for recommending

changes to ISO 13253 in this area.

4. Sections 3.2.3 and 3.6.3. Testing a

Two-capacity Compressor System

ARI stated: ‘‘ARI agrees with DOE that

the test procedure should be modified to

accommodate more appropriate testing

of multiple capacity heat pumps that are

sized to meet the cooling load at fan

speeds lower than the maximum. We

have established a task group to

investigate this issue, and will provide

our recommendations to DOE as soon as

they are available.’’ (ARI, No. 6 at 2).

The proposed test procedure covers

two-capacity heat pumps that are

designed to operate exclusively at low

capacity in meeting the space cooling

load while using both low and high

capacities when space heating. SEER of

the unit is evaluated in the same way as

specified for a single-speed air

conditioner. HSPF is evaluated using

the same algorithm as specified for a

‘‘normal’’ two-capacity heat pump

except that the building loads for the

heating temperature bins are based on

the heat pump’s heating capacity when

tested at low capacity and 47 °F outdoor

dry bulb temperature. Previously, the

building loads were tied to the heat

pump’s heating capacity at 47 °F and

high compressor capacity. The change

will drive the balance point of the heat

pump down. The issue on this

particular subject is whether the heat

pump must have a lockout feature to

prevent cooling at high capacity or is it

sufficient that the rating is applicable so

long as the heat pump is sized to

operate at low capacity at design cooling

conditions? The advantages of the

lockout would be to (better) assure that

high compressor capacity would not be

used when cooling and a particular unit

would only have one unique NAECArequired SEER and HSPF rating.

Without the lockout feature, the unit

would have two SEER and HSPF

ratings. A lockout feature is required in

accordance with today’s proposed test

procedure but DOE welcomes further

discussion on this issue.

5. Section 3.3. Capacity Adjustments for

Barometric Effects

ARI commented: ‘‘ARI is aware that

barometric pressure can have an affect

on test results. However, we believe

DOE should allow ASHRAE to finish its

analysis of this issue before making

changes to the test procedure. The test

procedure should be revised to

reference ASHRAE Standard 37–1988,

with the exception of the section that

pertains to corrections made to

capacities based on measured

barometric pressures, since it is known

this section contains an error and is

being revised.’’ (ARI, No. 6 at 2).

Today’s proposed test procedure

reflects the recommendation made by

ARI.

6. Sections 3.5.3 and 3.8.1. Cyclic

Degradation Coefficients

In the existing DOE test procedure,

the default values provided for cooling

and heating cyclic degradation

coefficients, Cc

D and ChD, are both 0.25.

On the cooling side, the two optional

tests are conducted on the majority of

units because the experimentallydetermined Cc

D is lower than 0.25.

NIST, DOE and ARI members have

discussed developing new defaults. The

goal is to obtain more representative

defaults resulting in less CD testing

6776 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

while still crediting features that

enhance cyclic performance. The

manufacturers and ARI, as part of their

certification program, have

experimentally determined the CD of

many units. DOE believes the available

data could be used to evaluate a set of

new defaults that depend on the

hardware components of the air

conditioner or heat pump. The

compiling of the data, however, is a

formidable and thus far uncompleted

task.

ARI originally commented: ‘‘ARI

endorses the concept of providing

alternate degradation coefficients (CD)

for systems using specific components

known to reduce the typical 0.25 default

value. This could significantly reduce

test burden by decreasing the need for

the cumbersome cyclic test. ARI will

continue to work with NIST on this

effort, and provide whatever data our

members authorize, to help determine

appropriate alternatives.’’ (ARI, No. 6 at

3). More recently, ARI members have

reconsidered the merits of seeking new

CD defaults. A final decision from ARI

is pending.

DOE encourages ARI to provide data

and recommendations needed to begin

the investigation into better CD defaults.

If better CD defaults are identified, DOE

will initiate steps to implement defaults

that are lower than the existing values

of 0.25. Such lower defaults could only

positively impact the SEER and HSPF of

a unit and so would not require

adjustments to the existing NAECA

energy conservation standards. Defaults

that are higher than the existing 0.25

values, which could only negatively

impact SEER and HSPF, would most

likely become effective the same time as

new NAECA energy conservation

standards. We will not delay efforts to

move today’s proposed rulemaking into

a final rulemaking by the pursuit of

better CD defaults. If we identify better

defaults in sufficient time before the

issue of the final rule, so we can obtain

public comments on the proposed CD

values, then we will incorporate the

better defaults into the final rulemaking.

If better defaults are identified after the

final rulemaking, DOE will initiate a

new rulemaking process where changes

and comments are limited to the issue

of new CD defaults.

E. Calculations of Seasonal Performance

Descriptors

1. Sections 4.1.4 and 4.2.4. Variablespeed Bin Calculations

In the existing DOE air conditioner

and heat pump test procedure, a

quadratic fit is used to approximate the

change in EER and COP as a function of

the outdoor bin temperature. Prior to the

25 September 1997 DOE workshop,

consideration had been given to using

an alternative fit, a linear over linear

rational function of the form

Y=(A0+A1·X)/(1+B1·X). The rationale

function was considered because it

maintains a monotonic shape in all

cases whereas a quadratic fit can have

an inflection point between the points

that it is fitting. For the purposes of

interpolating the EER or COP of a

variable-speed, all-electric heat pump or

air conditioner, both fits are expected to

give comparable results because the

points being fitted have historically

been close to linear. For the one

variable-speed heat pump considered by

NIST, for example, the two fits resulted

in SEER and HSPF changes of 0.06%

and 0.14%, respectively.

At the 25 September 1997 DOE

workshop, the issue was discussed.

Trane spoke against adopting the

rational function on the basis that no

practical problems had arisen with

using the quadratic fit over the

approximately 15 years that it has been

used. (Trane, No. 2HH at 149–150).

Today’s proposed test procedure

maintains the use of the quadratic fit.

IV. Summary of Proposed

Modifications to the DOE Air

Conditioner and Heat Pump Test

Procedure

In addition to the modifications cited

in Section III, the proposed test

procedure also incorporates the

following changes.

A. Update and Add References for

ASHRAE and ARI Standards

The existing test procedure references

ASHRAE Standards 37–78 and 41.1 (no

year) and ARI Standards 210–79, 240–

77, and 320–76. The proposed revised

version references ARI Standard 210/

240–94 and ASHRAE Standards 23–93,

37–88, 41.1–86 (RA 91), 41.2–87 (RA

92), 41.6–94, 41.9–88, 51–99, and 116–

95.

B. Air Volume Rates

ARI Standard 240–77 was previously

referenced. Now, rather than referencing

ARI Standard 210/240–94, we have

added sections within this proposed test

procedure. The main reason for no

longer referencing ARI Standard 210/

240 is that it does not cover variablespeed, constant CFM blowers and does

not directly address two-capacity and

variable-speed systems. It is preferable

to have the overall issue of air volume

rates covered in one place rather than in

two. The main objective is to agree on

air flow rate specifications. If ARI

Standard 210/240 is revised to cover

these systems, DOE may again reference

the ARI Standard.

ASHRAE Standard 37–78 (or 37–88)

is no longer referenced for the equation

calculating the air volume rate of

standard air. The factor 1+Wn is missing

from the denominator of the equation

given in Standard 37–88. This change

has been adopted by the committee

working to revise Standard 37.

Today’s proposed test procedure

adopts the approach used in the ISO

Standard 5151 of conducting each test at

zero external static pressure when

testing a non-ducted unit.

C. Cyclic Testing

Industry practice and the method

described in ASHRAE Standard 116 was

adopted. Section 5.1 of the current

Appendix M implies that the air volume

rate is to be measured during cyclic

tests. Standard test laboratory practice is

to try to obtain the same velocity

pressure or nozzle static pressure drop

that was obtained during the

comparable steady-state test. The air

volume rate used in the cyclic test

calculations is assumed to be the same

air volume rate measured during the

comparable steady-state test. This

change is reflected in this proposed test

procedure.

Concerning split-type non-ducted

(ductless) systems, Section 4.1.1.5 of

Appendix M states that ‘‘The integration

time for capacity and power shall be

from compressor cut-on time to indoor

fan cutoff time.’’ The indoor fan is

operated for 3 minutes prior to

compressor cut-on and for 3 minutes

after compressor cutoff during the final

OFF/ON interval. This proposed test

procedure adopts industry practice and

integrates power from compressor OFF

to compressor OFF and subtracts the

electrical energy associated with

operating the indoor fan during the

initial 3-minute fan-only period. Space

cooling capacity is integrated from

compressor ON to indoor fan OFF. As

with the present test procedure, fan

energy for the three minutes after

compressor cutoff is added to the

integrated cooling capacity.

The present test procedure does not

contain specific information regarding

the air dampers: where to install them,

how well they should seal, and how

quickly they should respond. Much of

this information is given in Appendix B

of ARI Standard 210/240–94. Needed

information is incorporated within the

text of the proposed test procedure

rather than making specific references to

each pertinent section of Appendix B of

the ARI Standard.

For dry coil tests, the proposed test

procedure adopts ARI Standard 210/

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6777

240–94 Appendix B language with

regard to the requirement that the drain

pan be plugged and that the pan should

be completely dry.

This notice of proposed rulemaking

clarifies that the requirement of making

electrical energy measurements using an

instrument having an accuracy of ±0.5

percent of reading applies during both

the ON and OFF intervals of cyclic tests.

Existing Section 4.1.3.1, which reads

‘‘The indoor and outdoor average drybulb temperature for the cyclic dry coil

test D shall both be within 1.0 °F of the

indoor and outdoor average dry bulb

temperature for the steady-state dry coil

test C, respectively,’’ has been removed

from the proposed test procedure. This

requirement is automatically met given

the 0.5 °F test condition tolerance

associated with each test.

For units having a variable-speed

indoor fan, the manufacturer will have

the option of conducting the cyclic tests

with the indoor fan enabled or disabled,

the latter being the default option if an

attempt at testing with the fan enabled

is unsuccessful. Specifically, if testing

with the indoor fan operating and it

automatically reverses, shuts down, or

operates at an uncharacteristically high

external static pressure, then a pull-thru

method, where the fan is disabled, must

be used. Although allowing the option

of testing with the fan disabled is

needed because of the potential fighting

between the unit’s fan and the exhaust

fan of the air flow measuring apparatus,

DOE seeks data from cyclic tests where

the fan operates versus tests where the

fan is disabled and the pull-thru method

is used.

Although a unit having a variablespeed indoor fan may be designed to

ramp its fan speed when cycling on

and/or off, a step response in air volume

rate is nonetheless required during

cyclic tests. The work associated with

moving the additional air during the

ramp periods is performed by the

exhaust fan of the air flow measuring

apparatus. The step response begins at

the initiation of ramp up and ends at the

termination of ramp down. The

rationale for imposing the step change is

mainly due to the difficulty in obtaining

the ramp response and then making an

accurate measurement of the space

conditioning delivered. Systems having

indoor fans that ramp are expected to

have low cyclic degradation coefficients

(CD) regardless of whether the ramp

feature is used, thus the absolute

improvement in CD is expected to be

minor. Still, the proposed method of

testing will benefit these units. DOE has

only been able to obtain data from one

unit where two different ramp profiles

were compared to the results from

imposing step responses in air flow. In

one case CD went from 0.05 (‘‘truth’’:

ramp) to 0.02 (approximation: step

change) while in the second case the

values were 0.025 and 0.00. DOE seeks

additional data showing the difference

between the ramp and step responses

during cyclic tests.

D. Fanless (Coil-only) Units

Section 4.1 of the existing Appendix

M calls for corrections to capacity and

power based on CFM. Section 4.2 of

existing Appendix M calls for

corrections to capacity and power based

on SCFM. ITS uses SCFM in all cases.

Thus, the proposed test procedure

adopts the practice of only specifying

the corrections in terms of SCFM.

The proposed test procedure also

adopts the ARI Standard 210/240–94

Appendix B requirement that a specific

enclosure be constructed (1 inch

ductboard) when testing a coil only unit

that does not employ an enclosure.

E. Frost Accumulation Test

The proposed test procedure adopts

the ASHRAE Standard 116–95 and ARI

210/240–94 convention of specifying

the outdoor wet bulb temperature (33

°F) in place of the presently specified

dew point temperature (30 °F).

F. Test Tolerance Tables

The current Appendix M contains

tables covering all tests except steadystate cooling mode tests, for which

Table III in ASHRAE Standard 37–78 is

referenced. Table III of ASHRAE

Standard 37–78 has been added to the

proposed test procedure since all the

other tables are included in Appendix

M.

The test tolerance tables have been

improved. For example, although a test

condition tolerance for external

resistance to air flow is provided in the

current test procedure, it is not

applicable for ducted units. Such a test

condition tolerance is, however, now

applicable to non-ducted units. Also, a

test condition tolerance has been added

for electrical supply voltage (previously,

only a test operating tolerance was

specified). Because ASHRAE Standard

37–78 does not cover cooling mode dry

coil tests, a test condition tolerance on

the indoor inlet wet bulb temperature is

not applicable. Test tolerances given on

the outdoor outlet dry and wet bulb

temperatures are now noted as only

being applicable when the Outdoor Air

Enthalpy Method is used to provide the

secondary capacity measurement.

For the Frost Accumulation Test, the

intervals considered to be heating

versus defrosting have been modified

slightly. Specifically, in the existing test

procedure in Section 4.2.3.3, the first 5

minutes after a defrost termination was

included in the defrost interval. In the

proposed test procedure, the time

interval has been increased to 10

minutes. Also, in making the test

condition conversion of 30° F dew point

to 33° F wet bulb, the test operating

tolerance and test condition tolerance

convert to wet bulb temperature

tolerances of 0.6° F and 0.3° F,

respectively. This 0.6° F test operating

tolerance on outdoor wet bulb

temperature is more stringent than the

value allowed for the steady-state tests.

The 0.3° F test condition tolerance is the

same as required for steady-state tests.

Given that these tolerances should be

less stringent that those required of a

steady-state test, the proposed test

procedure adopts the values given in

ASHRAE Standard 37: 1.5° F and 0.5° F.

G. Pretest Intervals

Statements given in the DOE

proposed test procedure regarding

operation prior to recording data have

been modified. These changes are as

follows.

1. Wet Coil Tests

Existing: ‘‘The test room

reconditioning apparatus and the

equipment under test shall be operated

until equilibrium conditions are

attained’’ (Section 4.1.1.1).

Proposed: ‘‘For the pretest interval,

operate the test room reconditioning

apparatus and the unit to be tested until

maintaining equilibrium conditions for

at least 30 minutes at the specified

Section 3.2 test conditions’’ (Section

3.3).

2. Dry Coil Steady-State Test

Existing: ‘‘The test room

reconditioning apparatus and the

equipment under test shall be operated

until equilibrium conditions are

attained, but not for less than one hour

before data for test C are recorded’’

(Section 4.1.1.2).

Proposed: Same as proposed for

Section 3.3 wet coil tests with the

additional requirement to ‘‘ ***

operate the unit at least one hour after

achieving dry coil conditions’’ (Section

3.4).

3. Dry Coil Cyclic Test

Existing: ‘‘ * * * test unit shall be

manually cycled ‘off ’ and ‘on’ ***

until steadily repeating ambient

conditions are again achieved in both

the indoor and outdoor test chambers,

but for not less than two complete ‘off/

on’ cycles’’ (Section 4.1.1.2).

Proposed: ‘‘After completing a

minimum of two complete compressor

6778 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

OFF/ON cycles, determine the overall

cooling delivered and total electrical

energy consumption during any

subsequent data collection interval

where the test tolerances given in Table

8 are satisfied’’ (Section 3.5).

4. Maximum and High Temperature

Heating Mode Tests

Existing: ‘‘The test room apparatus

and test units must be operated for at

least one hour with at least one-half

hour at equilibrium and at the specified

test conditions prior to starting the test’’

(Section 4.2.1.1).

Proposed: ‘‘For the pretest interval,

operate the test room reconditioning

apparatus and the heat pump until

equilibrium conditions are maintained

for at least 30 minutes at the specified

Section 3.6 test conditions’’ (Section

3.7).

5. Heating Mode Cyclic Test

Existing: ‘‘ * * * and be cycled ‘on’

and ‘off’ as specified in 3.2.1.2 until

steadily repeating ambient conditions

are achieved for both the indoor and

outdoor test chambers, but for not less

than two complete ‘off’/‘on’ cycles’’

(Section 4.2.1.2).

Proposed: Same as for the dry coil

cooling mode cyclic test (see above).

6. Frost Accumulation Test

Existing: ‘‘The test room

reconditioning equipment and the unit

under test shall be operated for at least

one-half hour prior to the start of a

‘preliminary’ test period’’ (Section

4.2.1.3).

Proposed: ‘‘Operate the test room

reconditioning apparatus and the heat

pump for at least 30 minutes at the

specified Section 3.6 test conditions

before starting the ‘preliminary’ test

period’’ (Section 3.9).

7. Low Temperature Test

Existing: ‘‘The test room

reconditioning equipment shall first be

operated in a steady-state manner for at

least one-half hour at equilibrium and at

the specified test conditions. The unit

shall then undergo a defrost, either

automatic or manually induced’’

(Section 4.2.1.4).

Proposed: Same as for the Maximum

and High Temperature Heating mode

tests (see above) with the following

additions. ‘‘After satisfying the Section

3.7 requirements for the pretest interval,

but before you begin collecting data to

determine Q ̇ h

k(17) and E ̇ hk(17), conduct

a defrost cycle. This defrost cycle may

be manually or automatically initiated.

(Section 3.10).

H. Multi-Capacity Systems

1. Two-Capacity Heat Pumps that Lock

Out Low Capacity at Higher Outdoor

Temperatures.

The existing test procedure covers

two-capacity units that operate

exclusively at high capacity when the

building load exceeds the unit’s low

capacity. The Department is unaware of

any two-capacity units that implement

such a control strategy and so coverage

of them is excluded from today’s

proposed test procedure. However,

coverage was added to address units

that lock out low capacity operation at

low (heating) or high (cooling) outdoor

temperatures. For this new case, a step

was added which reverts to a single

capacity calculation. The proposed test

procedure uses the CD determined based

on cycling at low capacity (or the 0.25

default) in all cases. The Department

welcomes comments on any control

strategy used by two-capacity units that

are not adequately covered in today’s

proposed test procedure.

2. Systems Having a Single-Speed

Compressor and a Variable-Speed

Indoor Fan Where Fan Speed or Air

Volume Rate Depends on Outdoor

Temperature.

The proposed test procedure requires

two extra steady-state tests for the

cooling mode (see Table 4) and two

extra steady-state tests for the heating

mode (see Table 10). An extra Frost

Accumulation test is optional.

3. Specification of the Air Volume Rate

for Tests at Low Capacity

In the existing test procedure, the air

volume rate to be used when testing a

two capacity system while operating at

low capacity is not explicitly addressed.

The proposed test procedure requires

the use of the fan laws, as is now done

for variable-speed systems, to determine

the air volume rate when testing a unit

having an indoor fan. For fanless units,

the air volume rate used when

conducting tests at low capacity (i.e.,

the Minimum Air Volume Rate) is the

higher of

(1) The rate specified by the

manufacturer; or

(2) 75 percent of the air volume rate

used for the high capacity tests.

DOE believes that a lower limit is

needed given the finite capabilities of

the typical multi-speed furnace blower

that is used in field installations. The 75

percent minimum is based on very

limited data collected by NIST. The

subject has been discussed by industry

members at such forums as ASHRAE

meetings but no formal consensus has

yet been reached for the specified

percentage. Data and comments are

requested, especially with regard to the

specified value of the lower limit.

I. Triple-split Systems

The DOE test procedure refers to

ASHRAE Standard 37 on the issue of

equipment installation and test set up

procedures. ASHRAE Standard 37, in

turn, states that you must use the

calorimeter air-enthalpy method

arrangement when testing units where

the compressor is in the indoor section

and separately ventilated. For this

arrangement, an enclosure must be built

around the equipment under test within

the indoor chamber. The present

requirement is burdensome and DOE

knows of no one who uses it when

testing triple-splits. Furthermore, the

heat loss from the indoor compressor

section should be reflected in an

adjusted output capacity and not by a

raised entering air temperature. The

amount of heat dissipated to the

ambient by the indoor compressor

section of such units is usually

minimized as a result of the enclosure

of the third section being insulated

(mainly in an effort to reduce the

operating noise). Based on limited

information gained to date, the amount

of heat lost from the indoor compressor

section is on the order of 2 percent or

less of the unit’s space conditioning

capacity.

The proposed test procedure instructs

that triple-split systems are not to be

tested using the calorimeter air-enthalpy

method arrangement (see note in

Section 2.6). At this juncture, no

algorithm or method for assigning/

determining the heat loss from the

indoor compressor section is included.

If triple-split systems become more

popular and if information becomes

available indicating the heat loss from

the indoor compressor section exceeds 2

percent of the total, air-side capacity,

then DOE will revisit the option of

having a capacity adjustment.

J. Time-Adaptive Defrost Control

Systems

When conducting a Frost

Accumulation test on a heat pump

having a time-adaptive defrost control

system, repeatable frosting and

defrosting intervals typically require (if

obtainable at all) an excessive number of

cycles. Until a better alternative is

identified, defrosts initiated during the

‘‘preliminary’’ test and the ‘‘official’’ test

will be manually induced. The

manufacturer will be required to

provide information as to how long the

unit would optimally frost before

initiating a defrost. The manufacturer

will have to provide information on

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6779

how to induce a defrost cycle at the

appropriate elapsed time. The controls

of the unit, however, will still control

the duration of the defrost cycle, once

initiated.

K. Test Unit Installation

For the most part, equipment

installation requirements will continue

to be performed according to the

manufacturer’s installation instructions.

However, the proposed test procedure

adopts the lab and field practice of

insulating the low pressure line(s) of a

split system. Also, Section 2.2.5 restricts

the use of special refrigerant charging

criteria for lab testing.

L. Test Apparatus and Measurement/

Sampling Frequency

1. Inlet Plenum for Blower Coils

In the current DOE test procedure, no

inlet plenum is required when testing

blower coil units. The proposed test

procedure recommends that an inlet

plenum be installed if space permits.

(Lab ceiling height on vertical

installation is a limitation.) The test

procedure recommends using an inlet

plenum that is constructed according to

the design specified for fanless units.

See Section 2.4.2.

2. Manifolded Static Pressure Taps

The triple-T configuration was found

in 1976 to be the preferred method for

manifolding static pressure taps (‘‘The

design of piezometer rings’’ by K. A.

Blake, Journal of Fluid Mechanics, Vol.

78, part 2, pp. 415–428). The triple-T

configuration and the more widely used

complete ring, four-to-one manifolding

configuration are presently part of the

draft revision of ASHRAE Standard 37.

This revised test procedure recommends

use of either of these two manifolding

methods, which are shown in Figure 1.

The broken ring, four-to-one

manifolding configuration may be used

but is not recommended.

3. Temperature Measurement Intervals

The proposed test procedure specifies

that dry-bulb temperature

measurements are to be measured at the

intervals specified in ASHRAE Standard

41.1–86 (RA91). Wet bulb temperature,

dew point temperature, or relative

humidity are to be measured at the

minimum sampling interval specified in

Definition 1.14.

4. Temperature Measurement

Accuracies

The proposed test procedure defers

entirely to ASHRAE Standard 41.1–86

(RA 91) for accuracy and precision

requirements.

5. Grid of Individual Temperature

Sensors Within the Indoor-Side Outlet

Plenum

The proposed test procedure adopts

the ARI Standard 210/240–94 Appendix

B requirements that a temperature

spread of 1.5 °F or less be obtained, and

that the outlet temperature grid be

composed of a minimum of 9 sensors

(while recommending 16). Also, the

proposed test procedure recommends

redundant sensors to determine the

change in dry bulb temperature across

the indoor coil.

6. Duct Loss Correction

The proposed test procedure adds a

correction for the heat transfer between

the test room and an outlet duct

sandwiched between the coil and the

outlet temperature grid. This correction

is already an industry practice.

7. Water vapor measurements using a

dew-point hygrometer, a relative

humidity meter, or any other alternative

instrument

Today’s test procedure explicitly

permits alternatives to using wet bulb

temperature sensors. To ease

instrumentation selection, required

instrument accuracies are provided for

dew point hygrometers and relative

humidity meters.

8. Voltmeter Accuracy

The required accuracy of voltage

measurements has been changed from

±2% to ±1%.

9. Electrical Power Measurement

Adjustable-speed-driven motors, as

used in a variable-speed compressor,

distort the input current and, to a lesser

degree, voltage waveforms. Published

literature [1–7] supports avoiding the

use of induction type meters for

measuring such non-sinusoidal power

and instead recommends using a meter

that is capable of sampling up to the

50th harmonic. This point is included

in Section 2.8 of today’s test procedure

as a recommendation when testing a

heat pump or air conditioner having a

variable-speed compressor. (In terms of

a meter sampling frequency, a 50th

harmonic requirement corresponds to a

minimum sampling frequency between

3 and 30 kHz, depending upon which

technical recommendation you wish to

cite.)

The majority of the technical

references listed below report the

performance of specific meters with

specific waveforms, some of which

should be representative of those found

in presently-marketed residential-size

air conditioners and heat pumps. In

addition to induction watthour meters,

a disconcerting result reported in the

noted references is that the use of a noninduction meter that can measure up to

the 50th harmonic does not insure an

accurate measurement but only

improves your chances.

References:

1. P.S. Filipski and R. Arseneau, ‘‘Behavior

of Wattmeters and Watthour Meters

Under Distorted Waveform Conditions,’’

IEEE tutorial course, Nonsinusoidal

Situations: Effects on the Performance of

Meters and Definitions of Power, IEEE,

Piscataway, NJ, pp. 13–22, 1990.

2. A. Domijan, Jr., E. Embriz-Santander, A.J.

Gilani, G. Lamer, C. Stiles, and C.W.

Williams, Jr., ‘‘Watthour Meter Accuracy

Under Controlled Unbalanced Harmonic

Voltage and Current Conditions,’’ IEEE

Transactions Power Delivery, Vol. II, No.

1, pp. 64–78, Jan. 1996.

3. A. Domijan, D. Czarkowski, A. Abu-aisheh,

and E. Embriz-Santander,

‘‘Measurements of Electrical Power

Inputs to Variable Speed Motors and

Their Solid State Power Converters—

Phase II,’’ ASHRAE Research Project 770,

Final Report, November 30, 1995.

4. D. Czarkowski and A. Domijan, Jr.,

‘‘Performance of Electrical Power Meters

and Analyzers in Adjustable-Speed Drive

Applications,’’ American Society of

Heating, Refrigerating and AirConditioning Engineers (ASHRAE)

Transactions 1997, Vol. 103, Part 1.

5. A.J. Baldwin, N.G. Planer, D.E. Nordell, N.

Hohan, ‘‘Evaluation of Electrical

Interference to the Induction Watthour

Meter,’’ EPRI EL–2315, Research Project

1738, Final Report, April 1982.

6. Institute of Electrical and Electronics

Engineers (IEEE), Inc., ‘‘IEEE Standard

519–1992, IEEE Recommended Practices

and Requirements for Harmonic Control

in Electrical Power Systems,’’ New York,

New York.

7. A. Domijan, and E. Embriz-Santander,

‘‘Measurements of Electrical Power

Inputs to Variable Speed Motors and

Their Solid State Power Converters,’’

American Society of Heating,

Refrigerating and Air-Conditioning

Engineers (ASHRAE) Transactions 1993,

Vol. 99, Part I, pp. 241–258.

M. Different Compressor Speeds and

Indoor Fan Capacities Between Cooling

and Heating

In the existing test procedure,

variable-speed systems that operate at

higher speeds when heating than when

cooling are covered. In today’s proposed

revision (as noted above in III.D.4) this

allowance has been extrapolated to

coverage of two-capacity heat pumps

that only operate at low capacity during

the cooling season while using both low

and high capacities when heating. And,

in taking a generic approach, today’s

test procedure covers any case where

the heat pump uses different fan speeds

or air volume rates for cooling versus

when heating. (See Section 3.1.4.4.2)

6780 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

N. Secondary Test Requirements.

When using the Outdoor Air Enthalpy

test method, a preliminary test is

conducted to compensate, if necessary,

for any performance impact caused by

the outdoor air-side test apparatus. In

accordance with the existing test

procedure, a preliminary test is

conducted prior to all steady-state tests

(i.e., those tests where a secondary

measurement of capacity is required). In

today’s revision, relaxing this

requirement is proposed. Section 3.11.1

indicates that the number of preliminary

tests can be reduced in most cases to

one (for air conditioners or heating-only

heat pumps) or two (for heat pumps):

one for the first cooling mode steadystate test and one for the first heating

mode steady-state test.

O. HSPF Calculations

The last paragraph of Sections 5.2.1

and 5.2.2 of the existing test procedure

are not similarly placed in the proposed

test procedure. The paragraph in

question reads ‘‘Once the maximum and

minimum HSPF and operating cost

values have been obtained for each

region, the HSPF and operating cost

shall be determined for each

standardized design heating

requirement (see section 6.2.6) between

the maximum and minimum design

heating requirements by means of

interpolation.’’ The issue of how many

HSPF calculations are required has

been, and will remain, an item that is

covered elsewhere: In 10 CFR part 430,

subpart B, § 430.23(m)(3)(ii). In the

proposed test procedure, this section

along with a short restatement of its

contents are included in the Definition

(1.27) for HSPF. Because of the relative

ease of automating the calculation

process, and the nonlinearity of the

HSPF versus design heating requirement

relationship, no reference is made to

obtaining HSPF or operating cost via

interpolation.

V. Procedural Requirements

A. Review Under the National

Environmental Policy Act of 1969

In this notice, the Department

proposes amendments to the test

procedures for central air conditioners

and heat pumps. We have reviewed the

proposed rule under the National

Environmental Policy Act of 1969

(NEPA), 42 U.S.C. 4321 et seq., the

regulations of the Council on

Environmental Quality, 40 CFR parts

1500–1508, DOE regulations for

compliance with NEPA, 10 CFR part

1021, and the Secretarial Policy on the

National Environmental Policy Act

(June 1994). The Department has

determined that this rulemaking is

covered under the Categorical Exclusion

found at paragraph A.6 of appendix A

to subpart D, 10 CFR part 1021, which

applies to rulemakings that are strictly

procedural. This proposed rule is a

procedural rulemaking and its

implementation will not affect the

quality or distribution of energy usage

and therefore will not result in any

environmental impacts. Accordingly,

neither an environmental assessment

nor an environmental impact statement

is required.

B. Regulatory Review

Today’s regulatory proposal has been

determined not to be a ‘‘significant

regulatory action’’ under Executive

Order 12866, ‘‘Regulatory Planning and

Review,’’ (58 FR 51735, October 4,

1993). Accordingly, today’s action was

not subject to review under the

Executive Order by the Office of

Information and Regulatory Affairs in

the Office of Management and Budget.

C. Regulatory Flexibility Review

The proposed rule has been reviewed

under the Regulatory Flexibility Act, (42

U.S.C. 601–612), which requires

preparation of a regulatory flexibility

analysis for any regulation that will

have a significant economic impact on

a substantial number of small

businesses and other small entities. The

proposed rule affects manufacturers of

central air conditioners and heat pumps.

The test procedures would not have a

significant economic impact, but rather,

would provide common testing

methods. This revision of the test

procedure will not require a significant

investment for new testing equipment.

DOE accordingly certifies that the

proposed rule would not, if

promulgated, have a significant

economic impact on a substantial

number of small entities and that

preparation of a regulatory flexibility

analysis is not required.

D. ‘‘Takings’’ Assessment Review

DOE has determined pursuant to

Executive Order 12630 (52 FR 8859,

March 18, 1988) that this proposed

regulation, if adopted, would not result

in any takings which might require

compensation under the Fifth

Amendment to the United States

Constitution.

E. Federalism Review

Executive Order 13132 (64 FR 43255,

August 10, 1999) requires agencies to

develop an accountable process to

ensure meaningful and timely input by

State and local officials in the

development of regulatory policies that

have ‘‘federalism implications.’’ Policies

that have federalism implications are

defined in the Executive Order to

include regulations that have

‘‘substantial direct effects 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.’’ On March 14,

2000, DOE published a statement of

policy describing the intergovernmental

consultation process it will follow in the

development of such regulations (65 FR

13735). DOE has examined today’s rule

and determined that it does not have a

substantial direct effect on the States, on

the relationship between the national

government and the States, or on the

distribution of power and

responsibilities among the various

levels of government. No further action

is required by the Executive Order.

F. Paperwork Reduction Act Review

This proposed rule contains no new

collections of information under the

Paperwork Reduction Act, 44 U.S.C.

3501 et seq.

G. Review Under Unfunded Mandates

Reform Act of 1995

Section 202 of the Unfunded

Mandates Reform Act of 1995

(‘‘Unfunded Mandates Act’’) requires

that the Department prepare an impact

statement before promulgating a rule

that includes a Federal mandate that

may result in expenditure by state,

local, and tribal governments, in the

aggregate, or by the private sector, of

$100 million or more in any one year.

The impact statement must include: (i)

Identification of the Federal law under

which the rule is promulgated; (ii) a

qualitative and quantitative assessment

of anticipated costs and benefits of the

Federal mandate and an analysis of the

extent to which such costs to state,

local, and tribal governments may be

paid with Federal financial assistance;

(iii) if feasible, estimates of the future

compliance costs and of any

disproportionate budgetary effects the

mandate has on particular regions,

communities, non-Federal units of

government, or sectors of the economy;

(iv) if feasible, estimates of the effect on

the national economy; and (v) a

description of the Department’s prior

consultation with elected

representatives of state, local, and tribal

governments and a summary and

evaluation of the comments and

concerns presented.

The Department has determined that

the action proposed today does not

include a Federal mandate that may

result in estimated costs of $100 million

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6781

or more to state, local or to tribal

governments in the aggregate or to the

private sector. Therefore, the

requirements of sections 203 and 204 of

the Unfunded Mandates Act do not

apply to this action.

H. Review Under Executive Order

12988, ‘‘Civil Justice Reform’’

With respect to the review of existing

regulations and the promulgation of

new regulations, section 3(a) of

Executive Order 12988, ‘‘Civil Justice

Reform,’’ 61 FR 4729 (February 7, 1996),

imposes on executive agencies the

general duty to adhere to the following

requirements: (1) Eliminate drafting

errors and ambiguity; (2) write

regulations to minimize litigation; and

(3) provide a clear legal standard for

affected conduct rather than a general

standard and promote simplification

and burden reduction. With regard to

the review required by Section 3(a),

section 3(b) of the Executive Order

specifically requires that Executive

agencies make every reasonable effort to

ensure that the regulation: (1) Clearly

specifies the preemptive effect, if any;

(2) clearly specifies any effect on

existing Federal law or regulation; (3)

provide 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 the Executive Order requires

Executive agencies to review regulations

in light of applicable standards section

3(a) and section 3(b) to determine

whether they are met or it is

unreasonable to meet one or more of

them. DOE reviewed today’s proposed

rulemaking under the standards of

section 3 of the Executive Order and

determined that, to the extent permitted

by law, it meets the requirements of

those standards.

I. 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 or policy that may affect

family well-being. Today’s proposal

would not have any impact on the

autonomy or integrity of the family as

an institution. Accordingly, we have

concluded that it is not necessary to

prepare a Family Policymaking

Assessment.

J. Plain Language Review

The President’s Memorandum on

‘‘Plain Language in Government

Writing,’’ 63 FR 31885 (June 10, 1998)

directs each federal agency to write all

published rulemaking documents in

plain language. The Memorandum

includes general guidance on what

constitutes ‘‘plain language.’’ Plain

language requirements will vary from

one document to another, depending on

the intended audience, but all plain

language documents should be logically

organized and clearly written.

We have tried to make this proposed

rule easy to understand. We are also

requesting suggestions on how to

improve its readability further.

VI. Public Comment Procedures

A. Written Comment Procedures

The Department invites interested

persons to participate in the proposed

rulemaking by submitting data,

comments, or information with respect

to the proposed issues set forth in

today’s proposed rule to Ms. Brenda

Edwards-Jones, at the address indicated

at the beginning of this notice. We will

consider all submittals received by the

date specified at the beginning of this

notice in developing the final rule.

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 one complete copy of the

document and ten (10) copies, if

possible, from which the information

believed to be confidential has been

deleted. The Department of Energy will

make its own determination with regard

to the confidential status of the

information and treat it according to its

determination.

Factors of interest to the Department

when evaluating requests to treat as

confidential information that has been

submitted include: (1) A description of

the items; (2) an indication as to

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) an indication as to when

such information might lose its

confidential character due to the

passage of time; and (7) why disclosure

of the information would be contrary to

the public interest.

B. Issues for Public Comment

The Department of Energy is

interested in receiving comments and

data concerning these test procedures.

Also, the Department welcomes

comments on improvements or

alternatives to these approaches. In

particular, DOE is interested in

gathering comments on the following:

1. Non-defrost (limited-range) heat

pumps

Which of the three options described

in Section III.A.3 should be invoked?

2. Testing units having a constant-airvolume-rate indoor fan

Are the proposed changes described

in Section III.D.1 acceptable? In

particular, does the proposed 8 percent

tolerance on indoor air volume rate

provide a fair balance between assuring

repeatable results while not being too

restrictive given the variation in blower

motor performance?

3. Cyclic testing of units having a

variable-speed indoor fan (that may or

may not provide a constant air volume

rate)

For units that ramp the indoor fan

speed when cycling on and/or off, data

are sought of the type referenced in the

last paragraph of Section IV.C (i.e., data

that quantifies the effect on CD from

using a ramped air volume rate versus

forcing the air volume rate to have a

step profile). Also, as described in the

second-to-last paragraph of Section

IV.C, data from cyclic tests conducted

with the indoor fan enabled and

disabled are sought.

4. Two-capacity heat pumps that are

designed to meet the seasonal cooling

load while operating at low capacity

As discussed in the last paragraph of

Section III.D.4, should the heat pump be

required to have controls that lock out

high capacity operation when cooling?

5. Lower limit on the air volume rate

used when testing a fanless, twocapacity unit at low compressor

capacity

As discussed in Section IV.H.3, data

and comments are requested regarding

the assigned limit for the air volume rate

when testing a fanless, two-capacity

unit at low compressor capacity.

Related to this issue is whether the

manufacturer should be required to

supply, with the unit, the hardware

needed to allow the use of two fan

speeds on the furnace blower that the

unit would be used with in the field.

Conceivably, if such hardware was not

provided, the test procedure could call

for using the same air volume rate for all

6782 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

tests, regardless of whether the

compressor is operating at high or low

capacity. On the other extreme, do any

manufacturers provide hardware that

allows a multi-speed furnace blower to

operate as a variable-speed blower? Or,

are there safeguards that will result in

all or the vast majority of fanless, twocapacity units to be applied with

furnaces having variable-speed blowers?

If so, then the lower limit noted in the

previous paragraph may not be

applicable.

6. Fan defaults for fanless (i.e., coilonly) two-capacity units

In the existing test procedure, the fan

heat/power default that is applied when

rating fanless units is 1250 Btu/h per

1000 SCFM (365 watts per 1000 SCFM).

When testing two-capacity fanless units,

this adjustment is applied when

evaluating space conditioning capacities

and electrical power usages for both

high and low compressor capacity

operation. Do blower curves for multispeed indoor fans support the use of the

same default for both low and high

capacity?

7. Differentiation among two-capacity

air conditioners and heat pumps

Is there a need to differentiate

between two-capacity units that can

transition between high and low

compressor capacities on-the-fly versus

units that must shut off the compressor

for some finite time interval when

transitioning? Both the existing test

procedure and today’s proposed

revision do not offer a means for

providing such differentiation. To begin

to do so would require information on

how EER and COP are affected as they

change from the value associated with

steady operation at one compressor

capacity until steady operation is

obtained at the other compressor

capacity following the transition. DOE

seeks comments and data that would

help to determine whether the test

procedure needs to account for low/high

compressor transitioning performance.

8. Testing single-packaged units

Today’s proposed test procedure

includes new test requirements when

testing certain types of single-packaged

units. The proposed additions are

summarized in III.C.1. As presently

proposed, the changes are limited to

cooling mode tests where all or part of

the indoor section is located in the

outdoor test room and to heating mode

tests where all or part of the outdoor

section is located in the indoor test

room. Comments are sought on the

general proposal and on whether the

approaches should be invoked when

testing all packaged units.

9. Multi-capacity units

Are there any multi-capacity units

that operate at less than maximum

speed or high capacity at the lowest

outdoor temperatures (prior to cycling

off the compressor, if applicable)?

Possibly such a strategy is needed to

insure component reliability. Such a

contingency is not covered in the

existing or proposed test procedure.

10. Cyclic degradation coefficients

Comments are sought on the proposed

actions discussed above in Section

III.D.6 for working towards new CD

defaults.

11. NAECA energy conservation

standards

Changes introduced in today’s

proposed test procedure are not

expected to cause a minimallycompliant unit to now become noncompliant. If a particular proposed

change is found to negatively affect

minimally compliant units, then DOE

would like to know.

12. Small-duct, high-velocity systems

Comments are sought on the proposed

actions discussed in Section III.A.2.

C. Public Workshop

1. Procedures for Submitting Requests to

Speak

You will find the time and place of

the public workshop listed at the

beginning of this notice of proposed

rulemaking. The Department invites any

person who has an interest in today’s

notice of proposed rulemaking, or who

is a representative of a group or class of

persons that has an interest in these

proposed issues, to make a request for

an opportunity to make an oral

presentation. If you would like to attend

the public workshop, please notify Ms.

Brenda Edwards-Jones at (202) 586–

2945. You may hand deliver requests to

speak to the address indicated at the

beginning of this notice between the

hours of 8:00 a.m. and 4:00 p.m.,

Monday through Friday, except Federal

holidays, or send them by mail or e-mail

to brenda.edwards-jones@ee.doe.gov.

The person making the request should

state why he or she, either individually

or as a representative of a group or class

of persons, is an appropriate

spokesperson, briefly describe the

nature of the interest in the rulemaking,

and provide a telephone number for

contact.

The Department requests each person

wishing to speak to submit an advance

copy of his or her statement at least 10

days prior to the date of this workshop

as indicated at the beginning of this

notice. The Department, at its

discretion, may permit any person

wishing to speak who cannot meet this

requirement to participate if that person

has made alternative arrangements with

the Office of Building Research and

Standards in advance. The letter making

a request to give an oral presentation

must ask for such alternative

arrangements.

2. Conduct of Workshop

The workshop (hearing) will be

conducted in an informal, conference

style. The Department may use a

professional facilitator to facilitate

discussion, and a court reporter will be

present to record the transcript of the

meeting. We will present summaries of

comments received before the

workshop, allow time for presentations

by workshop participants, and

encourage all interested parties to share

their views on issues affecting this

rulemaking. Following the workshop,

we will provide an additional comment

period, during which interested parties

will have an opportunity to comment on

the proceedings at the workshop, as

well as on any aspect of the rulemaking

proceeding.

The Department will arrange for a

transcript of the workshop and will

make the entire record of this

rulemaking, including the transcript,

available for inspection in the

Department’s Freedom of Information

Reading Room. Any person may

purchase a copy of the transcript from

the transcribing reporter.

List of Subjects in 10 CFR Part 430

Administrative practice and

procedure, Energy conservation,

Household appliances, Incorporation by

reference.

Issued in Washington, DC., on December

19, 2000.

Dan W. Reicher,

Assistant Secretary, Energy Efficiency and

Renewable Energy.

For the reasons set forth in the

preamble, part 430 of Chapter II of Title

10, Code of Federal Regulations is

proposed to be amended as set forth

below:

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 430.22 is amended:

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6783

a. By adding paragraphs (b)(5)3.

through (b)(5)10.;

b. by adding paragraph (b)(7).

The additions specified above read as

follows:

§ 430.22 Reference Sources.

* * * * *

(b) * * *

(5) * * *

3. American Society of Heating,

Refrigerating, and Air-Conditioning

Engineers Standard 23–1993, ‘‘Methods of

Testing for Rating Positive Displacement

Refrigerant Compressors and Condensing

Units.’’

4. American Society of Heating,

Refrigerating, and Air-Conditioning

Engineers Standard 37–1988, ‘‘Methods of

Testing for Rating Unitary Air-Conditioning

and Heat Pump Equipment.’’

5. American Society of Heating,

Refrigerating, and Air-Conditioning

Engineers Standard 41.1–1986 (Reaffirmed

1991), ‘‘Standard Method for Temperature

Measurement.’’

6. American Society of Heating,

Refrigerating, and Air-Conditioning

Engineers Standard 41.2–1987 (Reaffirmed

1992), ‘‘Standard Method for Laboratory

Airflow Measurement.’’

7. American Society of Heating,

Refrigerating, and Air-Conditioning

Engineers Standard 41.6–1994, ‘‘Method for

Measurement of Moist Air Properties.’’

8. American Society of Heating,

Refrigerating, and Air-Conditioning

Engineers Standard 41.9–1988, ‘‘A Standard

Calorimeter Test Method for Flow

Measurement of a Volatile Refrigerant.’’

9. American Society of Heating,

Refrigerating, and Air-Conditioning

Engineers/Air Moving and Conditioning

Association, Inc. Standard 51–1999,

‘‘Laboratory Methods of Testing Fans for

Rating.’’

10. American Society of Heating,

Refrigerating, and Air-Conditioning

Engineers Standard 116–1995, ‘‘Methods of

Testing for Rating for Seasonal Efficiency of

Unitary Air Conditioners and Heat Pumps.’’

* * * * *

(7) Air-Conditioning and Refrigeration

Institute (ARI), 4301 North Fairfax

Drive, Suite 425, Arlington, Virginia

22203, (703) 524–8800, ARI Standard

210/240–1994, ‘‘Unitary AirConditioning and Air-Source Heat

Pump Equipment.’’

* * * * *

3. Appendix M to Subpart B is revised

to read as follows:

Appendix M to Subpart B—Uniform

Test Method for Measuring the Energy

Consumption of Central Air

Conditioners and Heat Pumps

1. Definitions

2. Testing Conditions

2.1 Test room requirements

2.2 Test unit installation requirements.

2.2.1 Defrost control settings

2.2.2 Special requirements for units

having a multiple-speed outdoor fan.

2.2.3 Special requirements for multi-split

air conditioners and heat pumps, and

systems composed of multiple mini-split

units (outdoor units located side-by-side)

that would normally operate using two

or more indoor thermostats.

2.2.4 Wet-bulb temperature requirements

for the air entering the indoor and

outdoor coils.

2.2.4.1 Cooling mode tests.

2.2.4.2 Heating mode tests.

2.2.5 Additional refrigerant charging

requirements

2.3 Indoor air volume rates.

2.3.1 Cooling tests.

2.3.2 Heating tests.

2.4 Indoor coil inlet and outlet duct

connections.

2.4.1 Outlet plenum for the indoor coil.

2.4.2 Inlet plenum for the indoor unit

2.5 Indoor coil air property measurements

and air damper box applications

2.5.1 Test set-up on the inlet side of the

indoor coil: for cases where the inlet

damper box is installed

2.5.1.1 If the Section 2.4.2 inlet plenum is

installed.

2.5.1.2 If the Section 2.4.2 inlet plenum is

not installed

2.5.2 Test set-up on the inlet side of the

indoor unit: for cases where no inlet

damper box is installed.

2.5.3 Indoor coil static pressure

difference measurement

2.5.4 Test set-up on the outlet side of the

indoor coil.

2.5.4.1 Outlet air damper box placement

and requirements

2.5.4.2 Additional recommendations

2.5.5 Dry bulb temperature measurement

2.5.6 Water vapor content measurement

2.5.7 Air damper box performance

requirements

2.6 Airflow measuring apparatus

2.7 Electrical voltage supply

2.8 Electrical power and energy

measurements

2.9 Time measurements.

2.10 Test apparatus for the secondary space

conditioning capacity measurement

2.10.1 Outdoor Air Enthalpy Method

2.10.2 Compressor Calibration Method

2.10.3 Refrigerant Enthalpy Method.

2.11 Measurement of test room ambient

conditions

2.12 Measurement of indoor fan speed

2.13 Measurement of barometric pressure

3. Testing Procedures

3.1 General Requirements

3.1.1 Primary and secondary test

methods.

3.1.2 Manufacturer-provided equipment

overrides.

3.1.3 Airflow through the outdoor coil.

3.1.4 Airflow through the indoor coil.

3.1.4.1 Cooling Certified Air Volume

Rate.

3.1.4.1.1 Cooling Certified Air Volume

Rate for Ducted Units.

3.1.4.1.2 Cooling Certified Air Volume

Rate for Non-ducted Units.

3.1.4.2 Cooling Minimum Air Volume

Rate.

3.1.4.3 Cooling Intermediate Air Volume

Rate.

3.1.4.4 Heating Certified Air Volume Rate

3.1.4.4.1 Ducted heat pumps where the

Heating and Cooling Certified Air

Volume Rates are the same.

3.1.4.4.2 Ducted heat pumps where the

Heating and Cooling Certified Air

Volume Rates are different due to indoor

fan operation.

3.1.4.4.3 Ducted heating-only heat

pumps.

3.1.4.4.4 Non-ducted heat pumps,

including non-ducted heating-only heat

pumps.

3.1.4.5 Heating Minimum Air Volume

Rate.

3.1.4.6 Heating Intermediate Air Volume

Rate.

3.1.4.7 Heating Nominal Air Volume

Rate.

3.1.5 Indoor test room requirement when

the air surrounding the indoor unit is not

supplied from the same source as the air

entering the indoor unit.

3.1.6 Air volume rate calculations.

3.1.7 Test sequence.

3.1.8 Requirement for the air temperature

distribution leaving the indoor coil.

3.1.9 Control of auxiliary resistive heating

elements.

3.2 Cooling mode tests for different types of

air conditioners and heat pumps.

3.2.1 Tests for a unit having a singlespeed compressor that is tested with a

fixed-speed indoor fan installed, with a

constant-air-volume-rate indoor fan

installed, or with no indoor fan installed.

3.2.2 Tests for a unit having a singlespeed compressor and a variable-speed

variable-air-volume-rate indoor fan

installed.

3.2.2.1 Indoor fan capacity modulation

that correlates with the outdoor dry bulb

temperature.

3.2.2.2 Indoor fan capacity modulation

based on adjusting the sensible to total

(S/T) cooling capacity ratio.

3.2.3 Tests for a unit having a twocapacity compressor.

3.2.4 Tests for a unit having a variablespeed compressor.

3.3 Test procedures for steady-state wet coil

cooling mode tests

3.4 Test procedures for the optional steadystate dry coil cooling mode tests

3.5 Test procedures for the optional cyclic

dry coil cooling mode tests (the D, D1, and

I1 Tests)

3.5.1 Procedures when testing ducted

systems.

3.5.2 Procedures when testing nonducted systems

3.5.3 Cooling mode cyclic degradation

coefficient calculation.

3.6 Heating mode tests for different types of

heat pumps, including heating-only heat

pumps.

3.6.1 Tests for a heat pump having a

single-speed compressor that is tested

with a fixed speed indoor fan installed,

with a constant-air-volume-rate indoor

fan installed, or with no indoor fan

installed.

3.6.1.1 Non-defrost heat pump.

3.6.1.2 Heat pump having a heat comfort

controller.

6784 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

3.6.2 Tests for a heat pump having a

single-speed compressor and a variablespeed, variable-air-volume-rate indoor

fan: capacity modulation correlates with

outdoor dry bulb temperature.

3.6.3 Tests for a heat pump having a twocapacity compressor

3.6.4 Tests for a heat pump having a

variable-speed compressor.

3.7 Test procedures for steady-state

Maximum Temperature and High

Temperature heating mode tests (the H0,

H01, H1, H12, H11, and H1N Tests).

3.8 Test procedures for the optional cyclic

heating mode tests (the H0C1, H1C, and

H1C1 Tests).

3.8.1 Heating mode cyclic degradation

coefficient calculation.

3.9 Test procedures for Frost Accumulation

heating mode tests

3.9.1 Average space heating capacity and

electrical power calculations

3.9.2 Demand defrost credit

3.10 Test procedures for steady-state Low

Temperature heating mode tests

3.11 Additional requirements for the

secondary test methods

3.11.1 If using the Outdoor Air Enthalpy

Method as the secondary test method

3.11.1.1 If a preliminary test precedes the

official test

3.11.1.2 If a preliminary test does not

precede the official test

3.11.1.3 Official test

3.11.2 If using the Compressor

Calibration Method as the secondary test

method

3.11.3 If using the Refrigerant Enthalpy

Method as the secondary test method

3.12 Rounding of space conditioning

capacities for reporting purposes.

4. Calculations of Seasonal Performance

Descriptors

4.1 Seasonal Energy Efficiency Ratio (SEER)

Calculations

4.1.1 SEER calculations for an air

conditioner or heat pump having a

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

4.1.2 SEER calculations for an air

conditioner or heat pump having a

single-speed compressor and a variablespeed variable-air-volume-rate indoor

fan

4.1.2.1 Units covered by Section 2.1.2.2.1

where indoor fan capacity modulation

correlates with the outdoor dry bulb

temperature

4.1.2.2 Units covered by Section 2.1.2.2.2

where indoor fan capacity modulation is

used to adjust the sensible to total

cooling capacity ratio

4.1.3 SEER calculations for an air

conditioner or heat pump having a twocapacity compressor.

4.1.3.1 Steady-state space cooling

capacity at low compressor capacity is

greater than or equal to the building

cooling load at temperature Tj

4.1.3.2 Unit alternates between high (k=2)

and low (k=1) compressor capacity to

satisfy the building cooling load at

temperature Tj

4.1.3.3 Unit only operates at high (k=2)

compressor capacity at temperature Tj

and its capacity is greater than the

building cooling load

4.1.3.4 Unit must operate continuously at

high (k=2) compressor capacity at

temperature Tj

4.1.4 SEER calculations for an air

conditioner or heat pump having a

variable-speed compressor

4.1.4.1 Steady-state space cooling

capacity when operating at minimum

compressor speed is greater than or equal

to the building cooling load at

temperature Tj

4.1.4.2 Unit operates at an intermediate

compressor speed (k=i) in order to match

the building cooling load at temperature

Tj

4.1.4.3 Unit must operate continuously at

maximum (k=2) compressor speed at

temperature Tj

4.2 Heating Seasonal Performance Factor

(HSPF) Calculations

4.2.1 Additional steps for calculating the

HSPF of a heat pump having a singlespeed compressor that was tested with a

fixed-speed indoor fan installed, a

constant-air-volume-rate indoor fan

installed, or with no indoor fan installed

4.2.1.1 Space heating capacity and the

electrical power consumption

calculations for a non-defrost heat pump

4.2.1.2 Space heating capacity and the

electrical power consumption

calculations for a heat pump having a

heat comfort controller

4.2.2 Additional steps for calculating the

HSPF of a heat pump having a singlespeed compressor and a variable-speed,

variable-air-volume-rate indoor fan.

4.2.3 Additional steps for calculating the

HSPF of a heat pump having a twocapacity compressor.

4.2.3.1 Steady-state space heating

capacity when operating at low

compressor capacity is greater than or

equal to the building heating load at

temperature Tj

4.2.3.2 Heat pump alternates between

high (k=2) and low (k=1) compressor

capacity to satisfy the building heating

load at a temperature Tj

4.2.3.3 Heat pump only operates at high

(k=2) compressor capacity at temperature

Tj and its capacity is greater than the

building heating load

4.2.3.4 Heat pump must operate

continuously at high (k=2) compressor

capacity at temperature Tj

4.2.4 Additional steps for calculating the

HSPF of a heat pump having a variablespeed compressor.

4.2.4.1 Steady-state space heating

capacity when operating at minimum

compressor speed is greater than or equal

to the building heating load at

temperature Tj

4.2.4.2 Heat pump operates at an

intermediate compressor speed (k=i) in

order to match the building heating load

at a temperature Tj

4.2.4.3 Heat pump must operate

continuously at maximum (k=2)

compressor speed at temperature Tj

4.3 Calculations

4.3.1 Calculation of actual regional

annual performance factors (APFA) for a

particular location and for each

standardized design heating requirement

4.3.2 Calculation of representative

regional annual performance factors

(APFR) for each generalized climatic

region and for each standardized design

heating requirement

4.4 Rounding of SEER , HSPF, and APF for

reporting purposes

1. Definitions

1.1 Annual performance factor means the

total heating and cooling done by a heat

pump in a particular region in one year

divided by the total electric energy used in

one year. Section 430.23(m)(3)(iii) of the

Code of Federal Regulations states the

calculation requirements for this rating

descriptor.

1.2 ARI means Air-Conditioning and

Refrigeration Institute.

1.3 ARI Standard 210/240–94 means the

test standard ‘‘Unitary Air-Conditioning and

Air-Source Heat Pump Equipment’’

published in 1994 by ARI.

1.4 ASHRAE means the American Society

of Heating, Refrigerating and AirConditioning Engineers, Inc.

1.5 ASHRAE Standard 23–93 means the

test standard ‘‘Methods of Testing for Rating

Positive Displacement Refrigerant

Compressors and Condensing Units’’

published in 1993 by ASHRAE.

1.6 ASHRAE Standard 37–88 means the

test standard ‘‘Methods of Testing for Rating

Unitary Air-Conditioning and Heat Pump

Equipment’’ published in 1988 by ASHRAE.

1.7 ASHRAE Standard 41.1–86 (RA 91)

means the test standard ‘‘Standard Method

for Temperature Measurement’’ published in

1986 and reaffirmed in 1991 by ASHRAE.

1.8 ASHRAE Standard 41.2–87 (RA 92)

means the test standard ‘‘Standard Method

for Laboratory Airflow Measurement’’

published in 1987 and reaffirmed in 1992 by

ASHRAE.

1.9 ASHRAE Standard 41.9–88 means the

test standard ‘‘A Standard Calorimeter Test

Method for Flow Measurement of a Volatile

Refrigerant’’ published in 1988 by ASHRAE.

1.10 ASHRAE Standard 51–99 means the

test standard ‘‘Laboratory Methods of Testing

Fans for Rating’’ published in 1999 by

ASHRAE and the Air Movement and Control

Association, Inc.

1.11 ASHRAE Standard 116–95 means

the test standard ‘‘Methods of Testing for

Rating for Seasonal Efficiency of Unitary Air

Conditioners and Heat Pumps’’ published in

1995 by ASHRAE.

1.12 CFR means Code of Federal

Regulations.

1.13 Constant-air-volume-rate indoor fan

means a fan that varies its operating speed to

provide a fixed air volume rate from a ducted

system.

1.14 Continuously recorded, when

referring to a dry bulb measurement, means

that the specified temperature must be

sampled at regular intervals that are equal to

or less than the maximum intervals specified

in Section 4.3 part ‘‘a’’ of ASHRAE Standard

41.1–86 (RA 91). If such dry bulb

temperatures are used only for test room

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6785

1Systems that vary defrost intervals according to

outdoor dry-bulb temperature are not demand

defrost systems.

control, sample at regular intervals that are

equal to or less than the maximum intervals

specified in Section 4.3 part ‘‘b’’ of the same

ASHRAE Standard. Regarding wet bulb

temperature, dew point temperature, or

relative humidity measurements,

continuously recorded means that the

measurements must be made at regular

intervals that are equal to or less than 1

minute.

1.15 Cooling load factor (CLF) means the

ratio having as its numerator the total cooling

delivered during a cyclic operating interval

consisting of one ON period and one OFF

period. The denominator is the total cooling

that would be delivered, given the same

ambient conditions, had the unit operated

continuously at its steady-state space cooling

capacity for the same total time (ON + OFF)

interval.

1.16 Coefficient of Performance (COP)

means the ratio of the average rate of space

heating delivered to the average rate of

electrical energy consumed by the heat

pump. These rate quantities must be

determined from a single test or, if derived

via interpolation, must be tied to a single set

of operating conditions. COP is a

dimensionless quantity. When determined

for a ducted unit tested without an indoor fan

installed, COP must include the Section 3.7,

3.8, and 3.9.1 default values for the heat

output and power input of a fan motor.

1.17 Cyclic Test means a test where the

unit’s compressor is cycled on and off for

specific time intervals. A cyclic test provides

half the information needed to calculate a

degradation coefficient.

1.18 Damper box means a short section of

duct having an air damper that meets the

performance requirements of Section 2.5.7.

1.19 Degradation coefficient (CD) means a

parameter used in calculating the part load

factor. The degradation coefficient for cooling

is denoted by Cc

D. The degradation

coefficient for heating is denoted by ChD.

1.20 Demand-defrost control system

means a system that defrosts the heat pump

outdoor coil only when measuring a

predetermined degradation of performance.

The heat pump’s controls monitor one or

more parameters that always vary with the

amount of frost accumulated on the outdoor

coil (e.g., coil to air differential temperature,

coil differential air pressure, outdoor fan

power or current, optical sensors, etc.) at

least once for every ten minutes of

compressor ON-time when space heating.

One acceptable alternative to the criterion

given in the prior sentence is a feedback

system that measures the length of the defrost

period and adjusts defrost frequency

accordingly.1 In all cases, when the frost

parameter(s) reaches a predetermined value,

the system initiates a defrost. In a demanddefrost control system, defrosts are

terminated based on monitoring a

parameter(s) that indicates that frost has been

eliminated from the coil.

A demand defrost control system, which

otherwise meets the above requirements, may

allow time-initiated defrosts if, and only if,

such defrosts occur after 6 hours of

compressor operating time.

1.21 Design heating requirement (DHR)

predicts the space heating load of a residence

when subjected to outdoor design conditions.

Estimates for the minimum and maximum

DHR are provided for six generalized U.S.

climatic regions in Section 4.2.

1.22 Dry-coil tests are cooling mode tests

where the wet-bulb temperature of the air

supplied to the indoor coil is maintained low

enough that no condensate forms on this coil.

1.23 Ducted system means an air

conditioner or heat pump that is designed to

be permanently-installed equipment and

delivers conditioned air to the indoor space

through a duct(s). The air conditioner or heat

pump may be either a split system or a

single-packaged unit.

1.24 Energy efficiency ratio (EER) means

the ratio of the average rate of space cooling

delivered to the average rate of electrical

energy consumed by the air conditioner or

heat pump. These rate quantities must be

determined from a single test or, if derived

via interpolation, must be tied to a single set

of operating conditions. EER is expressed in

units of

Btu h

W

/ .

When determined for a ducted unit tested

without an indoor fan installed, EER must

include the Section 3.3 and 3.5.1 default

values for the heat output and power input

of a fan motor.

1.25 Heating load factor (HLF) means the

ratio having as it numerator the total heating

delivered during a cyclic operating interval

consisting of one ON period and one OFF

period. The denominator is the total heating

that would be delivered, given the same

ambient conditions, if the unit operated

continuously at its steady-state space heating

capacity for the same total time (ON + OFF)

interval.

1.26 Heat pump having a heat comfort

controller means equipment that regulates

the operation of the electric resistance

elements to assure that the air temperature

leaving the indoor section does not fall below

a specified temperature. This specified

temperature is usually field adjustable. A

method for testing and rating heat pumps

having a heat comfort controller is presently

limited to heat pumps that meet the

equipment criteria of Section 3.6.1.

1.27 Heating seasonal performance factor

(HSPF) means the total space heating

required during the space heating season,

expressed in Btu’s, divided by the total

electrical energy consumed by the heat pump

system during the same season, expressed in

watt-hours. For all heat pumps, HSPF

accounts for the heating delivered and the

energy consumed by auxiliary resistive

elements when operating below the balance

point. This condition occurs when the

building load exceeds the space heating

capacity of the heat pump condenser. For

heat pumps with heat comfort controllers

(see Definition 1.26), in addition, HSPF also

accounts for resistive heating contributed

when operating above the balance point as a

result of maintaining a minimum supply

temperature. Unless an approved alternative

rating method is used, as set forth in 10 CFR

part 430, subpart B, § 430.24(m), HSPF must

be calculated according to this appendix.

Repeat the calculations for each of the six

generalized U.S. climatic regions listed in

this appendix. For each region, evaluate an

HSPF for each standardized design heating

requirement that applies. (See 10 CFR part

430 subpart B, § 430.23(m)(3)(ii).) The HSPF

used to evaluate compliance with the Energy

Conservation Standards (see 10 CFR part 430,

subpart C, § 430.32(c)) is based on Region IV,

the minimum standardized design heating

requirement, and the sampling plan stated in

10 CFR part 430, subpart B, § 430.24(m).

1.28 Mini-split air conditioners and heat

pumps means non-ducted systems that have

a single outdoor section and one or more

indoor sections. The indoor sections cycle on

and off in unison in response to a single

indoor thermostat.

1.29 Multiple-split air conditioners and

heat pumps means non-ducted systems that

have two or more indoor sections. The indoor

sections operate independently and can be

used to space condition multiple zones in

response to multiple indoor thermostats.

1.30 Non-defrost heat pumps means

equipment that is incapable of defrosting the

outdoor coil. The equipment ceases to

operate the refrigeration system at outdoor

temperatures that are conducive to frost

accumulation. A method for testing and

rating non-defrost heat pumps is presently

limited to heat pumps that meet the

equipment criteria of Section 3.6.1.

1.31 Non-ducted system means an air

conditioner or heat pump that is designed to

be permanently-installed equipment and

directly heats or cools air within the

conditioned space using one or more indoor

coils that are mounted on room walls and/

or ceilings. The unit may be of a modular

design that allows for combining multiple

outdoor coils and compressors to create one

overall system. Non-ducted systems covered

by this test procedure are all split systems.

1.32 Part-load factor (PLF) means the

ratio of the cyclic energy efficiency ratio

(coefficient of performance) to the steadystate energy efficiency ratio (coefficient of

performance). Evaluate both energy

efficiency ratios (coefficients of performance)

based on operation at the same ambient

conditions.

1.33 Seasonal energy efficiency ratio

(SEER) means the total heat removed from

the conditioned space during the annual

space cooling season, expressed in Btu’s,

divided by the total electrical energy

consumed by the air conditioner or heat

pump during the same season, expressed in

watt-hours. Unless using an approved

alternative rating method, as set forth in 10

CFR part 430, subpart B, § 430.24(m), SEER

must be calculated according to Section 4.1

of this appendix. [See 10 CFR part 430,

subpart B, 430.23(m)(3)(i).] This Section 4.1

SEER and the sampling plan stated in 10 CFR

subpart B, 430.24(m) are used to evaluate

compliance with the Energy Conservation

Standards. (See 10 CFR part 430, subpart C,

§ 430.32(c).)

1.34 Single-packaged unit means any

central air conditioner or heat pump that has

all major assemblies enclosed in one cabinet.

6786 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

1.35 Split system means any air

conditioner or heat pump that has one or

more of the major assemblies separated from

the others.

1.36 Standard Air means dry air at 70 °F

and 14.696 psia. Under these conditions, dry

air has a mass density of 0.075 lb/ft.3

1.37 Steady-state test means a test where

the test conditions are regulated to remain as

constant as possible while the unit operates

continuously in the same mode.

1.38 Temperature bin means the 5 °F

increments that are used to partition the

outdoor dry-bulb temperature ranges of the

cooling (≥ 65 °F) and heating (< 65 °F)

seasons.

1.39 Test condition tolerance means the

maximum permissible difference between the

average value of the measured test parameter

and the specified test condition.

1.40 Test operating tolerance means the

maximum permissible range that a

measurement may vary over the specified test

interval. The difference between the

maximum and minimum sampled values

must be less than or equal to the specified

test operating tolerance.

1.41 Time adaptive defrost control system

is a demand-defrost control system (see

Definition 1.20) that measures the length of

the prior defrost period(s) and uses that

information to automatically determine when

to initiate the next defrost cycle.

1.42 Time-temperature defrost control

systems initiate or evaluate initiating a

defrost cycle only when a predetermined

cumulative compressor ON-time is obtained.

This predetermined ON-time is generally a

fixed value (e.g., 30, 45, 90 minutes) although

it may vary based on the measured outdoor

dry-bulb temperature. The ON-time counter

accumulates if controller measurements (e.g.,

outdoor temperature, evaporator

temperature) indicate that frost formation

conditions are present, and it is reset/remains

at zero at all other times. In one application

of the control scheme, a defrost is initiated

whenever the counter time equals the

predetermined ON-time. The counter is reset

when the defrost cycle is completed. In a

second application of the control scheme,

one or more parameters are measured (e.g.,

air and/or refrigerant temperatures) at the

predetermined, cumulative, compressor ONtime. A defrost is initiated only if the

measured parameter(s) falls within a

predetermined range. The ON-time counter is

reset regardless of whether a defrost is

initiated. If systems of this second type use

cumulative ON-time intervals of 10 minutes

or less, then the heat pump may qualify as

having a demand defrost control system (see

Definition 1.20).

1.43 Triple-split system means an air

conditioner or heat pump that is composed

of three separate components: An outdoor fan

coil section, an indoor fan coil section, and

an indoor compressor section.

1.44 Two-capacity (or two-stage)

compressor means an air conditioner or heat

pump that has one of the following:

(1) A two-speed compressor,

(2) Two compressors where only one

compressor ever operates at a time,

(3) Two compressors where one

compressor (Compressor #1) operates at low

loads and both compressors (Compressors #1

and #2) operate at high loads but Compressor

#2 never operates alone, and

(4) A compressor that is capable of cylinder

or scroll unloading.

For such systems, low capacity means:

(1) Operating at low compressor speed,

(2) Operating the lower capacity

compressor,

(3) Operating Compressor #1, and

(4) Operating with the compressor

unloaded (e.g., operating one piston of a twopiston reciprocating compressor, using a

fixed fractional volume of the full scroll,

etc.).

High capacity means:

(1) Operating at high compressor speed,

(2) Operating the higher capacity

compressor,

(3) Operating Compressors #1 and #2, and

(4) Operating with the compressor loaded

(e.g., operating both pistons of a two-piston

reciprocating compressor, using the full

volume of the scroll).

1.45 Wet-coil test means a test conducted

at test conditions that typically cause water

vapor to condense on the test unit evaporator

coil.

1.46 Small-duct system means equipment

that contains a blower and indoor coil

combination that produces at least 1.5 inches

of external static across the indoor unit when

operated at the certified air volume rate.

When applied in the field, small-duct

systems use branch ducts having less than

6.0 square inches of free area.

1.47 ASHRAE Standard 41.6–94 means

the test standard ‘‘Method for Measurement

of Moist Air Properties’’ published in 1994

by ASHRAE.

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6787

2. Testing Conditions

a. This test procedure covers split-type and

single-packaged ducted units and split-type

non-ducted units. Except for units having a

variable-speed compressor, ducted units

tested without an indoor fan installed are

covered.

b. Only a subset of the sections listed in

this test procedure apply when testing and

rating a particular unit. Tables 1–A through

1–C show which sections of the test

procedure apply to each type of equipment.

In each table, look at all four of the Roman—

numeral categories to see what test sections

apply to your equipment.

1. The first category, Rows I–1 through I–

4 of the Tables, pertains to the compressor

and indoor fan features of the equipment.

After identifying the correct ‘‘I’’ row, find the

table cells in the same row that list the type

of equipment being tested: Air conditioner

(AC), heat pump (HP), or heating-only heat

pump (HH). Use the test section(s) listed

above each noted table cell for testing and

rating the unit.

2. The second category, Rows II–1 and II–

2, pertains to the presence or absence of

ducts. Row II–1 shows the test procedure

sections that apply to ducted systems, and

Row II–2 shows those that apply to nonducted systems.

3. The third category is for special features

that may be present in the equipment. When

testing units that have one or more of the four

(special) equipment features described by the

Table footnote for Category III, use Row III to

find test sections that apply.

4. The fourth category is for the secondary

test method to be used. If you know the

secondary method for determining the unit’s

cooling and/or heating capacity, use Row IV

to find the appropriate test sections.

Otherwise, include all of the test sections

referenced by Row IV cell entries—i.e.,

sections 2.10 to 2.10.3 and 3.11 to 3.11.3—

among those sections consulted for testing

and rating information.

c. Obtain a complete listing of all pertinent

test sections by recording those sections

identified from the four categories above.

d. The user should note that, for many

sections, only part of a section applies to the

unit being tested. In a few cases, the entire

section may not apply. For example, Sections

3.4 to 3.5.3 (which describe optional dry coil

tests), are not relevant if the allowed default

value for the cooling mode cyclic degradation

coefficient is used rather than determining it

from testing.

Example for Using Tables 1–A to 1–C.

Equipment Description:

A ducted air conditioner having a singlespeed compressor, a fixed-speed indoor fan,

and a multi-speed outdoor fan.

Secondary Test Method: Refrigerant Enthalpy

Method

Step 1. Determine which of four listed Row

‘‘I’’ options applies ==> Row I–2

Table 1–A: ‘‘AC’’ in Row I–2 is found in

the columns for sections 1.1 to 1.47, 2.1

to 2.2, 2.2.4 to 2.2.4.1, 2.2.5, 2.3 to 2.3.1,

2.4 to 2.4.1, 2.5, 2.5.2 to 2.10, and 2.11

to 2.13.

Table 1–B: ‘‘AC’’ is listed in Row I–2 for

sections 3 to 3.1.4, 3.1.5 to 3.1.8, 3.2.1,

3.3 to 3.5, 3.5.3, 3.11 and 3.12.

Table 1–C: ‘‘AC’’ is listed in Row I–2 for

sections 4.1.1 and 4.4.

Step 2. Equipment is ducted ==> Row II–1

Table 1–A: ‘‘AC’’ is listed in Row II–1 for

sections 2.4.2 and 2.5.1 to 2.5.1.2.

Table 1–B: ‘‘AC’’ is listed in Row II–1 for

sections 3.1.4.1 to 3.1.4.1.1 and 3.5.1.

Table 1–C: no ‘‘AC’’ listings in Row II–1.

Step 3. Equipment Special Features include

multi-speed outdoor fan ==> Row III, M

Table 1–A: ‘‘M’’ is listed in Row III for

section 2.2.2

Tables 1–B and 1–C: no ‘‘M’’ listings in

Row III.

Step 4. Secondary Test Method is Refrigerant

Enthalpy Method ==> Row IV, R

Table 1–A: ‘‘R’’ is listed in Row IV for

section 2.10.3

Table 1–B: ‘‘R’’ is listed in Row IV for

section 3.11.3

Table 1–C: no ‘‘R’’ listings in Row IV.

Step 5. Cumulative listing of applicable test

procedure sections

1.1 to 1.47, 2.1 to 2.2, 2.2.2, 2.2.4 to 2.4.1,

2.2.5, 2.3 to 2.3.1, 2.4 to 2.4.1, 2.4.2, 2.5,

2.5.1 to 2.5.1.2, 2.5.2 to 2.10, 2.10.3, 2.11

to 2.13, 3. to 3.1.4, 3.1.4.1 to 3.1.4.1.1,

3.1.5 to 3.1.8, 3.2.1, 3.3 to 3.5, 3.5.1,

3.5.3, 3.11, 3.11.3, 3.12, 4.1.1, and 4.4.

BILLING CODE 6450–01–P

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Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6791

Inside these test rooms, use artificial loads

during cyclic tests and frost accumulation

tests, if needed, to produce stabilized room

air temperatures. For one room, DOE

recommends using an electric resistance

heater(s) having a heating capacity that is

6792 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

approximately equal to the heating capacity

of the test unit’s condenser. For the second

room, DOE recommends using a heater(s)

having a capacity that is close to the sensible

cooling capacity of the test unit’s evaporator.

Cycle the heater located in the same room as

the test unit evaporator coil ON and OFF

when the test unit cycles ON and OFF. Cycle

the heater located in the same room as the

test unit condensing coil ON and OFF when

the test unit cycles OFF and ON.

2.2 Test unit installation requirements. a.

Install the unit according to Section 8.6 of

ASHRAE Standard 37–88. With respect to

interconnecting tubing used when testing

split systems, however, follow the

requirements given in Section 5.1.3.5 of ARI

Standard 210/240–94. When testing triplesplit systems (see Definition 1.43), use the

tubing length specified in Section 5.1.3.5 of

ARI Standard 210/240–94 to connect the

outdoor coil, indoor compressor section, and

indoor coil while still meeting the

requirement of exposing 10 feet of the tubing

to outside conditions. When testing nonducted systems having multiple indoor coils,

connect each indoor fan-coil to the outdoor

unit using: a. 25 feet of tubing, or b. tubing

furnished by the manufacturer, whichever is

longer. If they are needed to make a

secondary measurement of capacity, install

refrigerant pressure measuring instruments as

described in Section 8.6.5 of ASHRAE

Standard 37–88. Refer to Section 2.10 of this

Appendix to learn which secondary methods

require refrigerant pressure measurements.

At a minimum, insulate the low pressure

line(s) of a split system with foam insulation

having an inside diameter that matches the

refrigerant tubing and a nominal thickness of

1⁄2 inch.

b. For units designed for both horizontal

and vertical installation or for both up-flow

and down-flow vertical installations, the

manufacturer must specify the orientation

used for testing. Conduct testing with the

following installed:

(1) The most restrictive filter(s),

(2) Supplementary heating coils, and

(3) Other equipment specified as part of the

unit, including all hardware used by a heat

comfort controller if so equipped (see

Definition 1.26).

c. Testing a ducted unit without having an

indoor air filter installed is permissible as

long as the minimum external static pressure

requirement is adjusted as Table 2, note 3

states (see Section 3.1.4). Except as noted in

Section 3.1.9, prevent the indoor air

supplementary heating coils from operating

during all tests. For coil only indoor units

that are supplied without an enclosure,

create an enclosure using 1 inch fiberglass

ductboard having a nominal density of 6

pounds per cubic foot. Or alternatively, use

some other insulating material having a

thermal resistance (‘‘R’’ value) between 4 and

6 hr·ft2·°F/Btu. For units where the coil is

housed within an enclosure or cabinet, no

extra insulating or sealing is allowed.

2.2.1 Defrost control settings. Set heat

pump defrost controls at the normal settings

which most typify those encountered in

generalized climatic region IV. (Refer to

Figure 2 and Table 17 of Section 4.2 for

information on region IV.) For heat pumps

that use a time-adaptive defrost control

system (see Definition 1.41), the

manufacturer must specify the frosting

interval to be used during Frost

Accumulation tests and provide the

procedure for manually initiating the defrost

at the specified time. To ease testing of any

unit, the manufacturer should provide

information and any necessary hardware to

manually initiate a defrost cycle.

2.2.2 Special requirements for units

having a multiple-speed outdoor fan.

Configure the multiple-speed outdoor fan

according to the manufacturer’s

specifications, and thereafter, leave it

unchanged for all tests. The controls of the

unit must regulate the operation of the

outdoor fan during all lab tests except dry

coil cooling mode tests. For dry coil cooling

mode tests, the outdoor fan must operate at

the same speed as used during the required

wet coil test conducted at the same outdoor

test conditions.

2.2.3 Special requirements for multi-split

air conditioners and heat pumps, and

systems composed of multiple mini-split

units (outdoor units located side-by-side) that

would normally operate using two or more

indoor thermostats. During the steady-state

tests, shunt all thermostats to make all indoor

fan-coil units operating simultaneously. To

ease the testing burden of cyclic tests,

consider creating a single control circuit that

allows simultaneous cycling of all

compressor systems. In this test procedure,

references to a single indoor fan, outdoor fan,

and compressor means all indoor fans, all

outdoor fans, and all compressor systems.

2.2.4 Wet-bulb temperature requirements

for the air entering the indoor and outdoor

coils.

2.2.4.1 Cooling mode tests. For wet-coil

cooling mode tests, regulate the water vapor

content of the air entering the indoor unit to

the applicable wet-bulb temperature listed in

Tables 3 to 6. As noted in these same tables,

achieve a wet-bulb temperature during drycoil cooling mode tests that results in no

condensate forming on the indoor coil.

Controlling the water vapor content of the air

entering the outdoor side of the unit is not

required for cooling mode tests except when

testing:

(1) Units that reject condensate to the

outdoor coil during wet coil tests. Tables 3–

6 list the applicable wet-bulb temperatures.

(2) Single-packaged units where all or part

of the indoor section is located in the outdoor

test room. The average dew point

temperature of the air entering the outdoor

coil during wet coil tests must be within ±3.0

°F of the average dew point temperature of

the air entering the indoor coil over the 30-

minute data collection interval described in

Section 3.3. For dry coil tests on such units,

you may need to limit the moisture content

of the air entering the outdoor side of the unit

to meet the requirements of Section 3.4.

2.2.4.2 Heating mode tests. For heating

mode tests, regulate the water vapor content

of the air entering the outdoor unit to the

applicable wet-bulb temperature listed in

Tables 9 to 12. The wet-bulb temperature

entering the indoor side of the heat pump

must not exceed 60 °F. Additionally, if you

use the Outdoor Air Enthalpy test method

while testing a single-packaged heat pump

where all or part of the outdoor section is

located in the indoor test room, adjust the

wet-bulb temperature for the air entering the

indoor side to yield an indoor-side dew point

temperature that is as close as reasonably

possible to the dew point temperature of the

outdoor-side entering air.

2.2.5 Additional refrigerant charging

requirements. Charging according to the

‘‘manufacturer’s instructions,’’ as stated in

Section 8.6 of ASHRAE Standard 37–88,

means the manufacturer’s installation

instructions that come packaged with the

unit. For third party testing, for example, do

not consult the manufacturer about how to

charge the unit. If a unit requires charging

but the installation instructions do not

specify a charging procedure, then evacuate

the unit and add the nameplate refrigerant

charge. Where the manufacturer’s installation

instructions contain two sets of refrigerant

charging criteria, one for field installations

and one for lab testing, use the field

installation criteria.

2.3 Indoor air volume rates. If a unit’s

controls allow for overspeeding the indoor

fan (usually on a temporary basis), take the

necessary steps to prevent overspeeding

during all tests.

2.3.1 Cooling tests. a. Set indoor fan

control options (e.g., fan motor pin settings,

fan motor speed) according to the published

installation instructions that are provided

with the equipment while meeting the

airflow requirements that are specified in

paragraph b. of this section.

b. Express the Cooling Certified Air

Volume Rate, the Cooling Minimum Air

Volume Rate, and the Cooling Intermediate

Air Volume Rate in terms of standard air.

2.3.2 Heating tests. a. If needed, set the

indoor fan control options (e.g., fan motor

pin settings, fan motor speed) according to

the published installation instructions that

are provided with the equipment. Do this setup while meeting all applicable airflow

requirements that are specified in paragraph

b. of this section.

b. Express the Heating Certified Air

Volume Rate, the Heating Minimum Air

Volume Rate, the Heating Intermediate Air

Volume Rate, and the Heating Nominal Air

Volume Rate in terms of standard air.

2.4 Indoor coil inlet and outlet duct

connections. Insulate and/or construct the

outlet plenum described in Section 2.4.1 and,

if installed, the inlet plenum described in

Section 2.4.2 with thermal insulation having

a nominal overall resistance (R-value) of at

least 19 hr·ft2·°F/Btu.

2.4.1 Outlet plenum for the indoor coil.

Attach a plenum to the outlet of the indoor

coil. (Note: For some packaged systems, the

indoor coil may be located in the outdoor test

room.) For non-ducted systems having

multiple indoor coils, attach a plenum to

each indoor coil outlet. Add a static pressure

tap to each face of the (each) outlet plenum,

if rectangular, or at four evenly distributed

locations along the circumference of an oval

or round plenum. Create a manifold that

connects the four static pressure taps. Figure

1 provides recommended options for the

manifold configuration. See Figures 7 and 8

of ASHRAE Standard 37–88 for the crossVerDate 11<MAY>2000 00:31 Jan 21, 2001 Jkt 194001 PO 00000 Frm 00026 Fmt 4701 Sfmt 4700 E:\FR\FM\22JAP2.SGM pfrm08 PsN: 22JAP2
Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6793

sectional dimensions and minimum length of

the (each) plenum and the locations for

adding the static pressure taps for units

tested with and without an indoor fan

installed. For a non-ducted system having

multiple indoor coils, have all outlet

plenums discharge air into a single common

duct. At the plane where each plenum enters

the common duct, install an adjustable

airflow damper and use it to equalize the

static pressure in each plenum.

6794 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6795

2.4.2 Inlet plenum for the indoor unit.

Install an inlet plenum when testing a coilonly indoor unit or a packaged system where

the indoor coil is located in the outdoor test

room. Add static pressure taps at the center

of each face of this plenum, if rectangular, or

at four evenly distributed locations along the

circumference of an oval or round plenum.

Make a manifold that connects the four static

pressure taps. See Figure 8 of ASHRAE

Standard 37–88 for cross-sectional

dimensions, the minimum length of the inlet

plenum, and the locations of the static

pressure taps. When testing a ducted unit

having an indoor fan (and the indoor coil is

in the indoor test room), DOE recommends

installing an inlet plenum if sufficient space

exists within the test room. If using an inlet

plenum, add four static pressure taps and a

manifold that connects them together. DOE

recommends constructing the inlet plenum

and locating the static pressure taps as shown

in Figure 8 of ASHRAE Standard 37–88.

Never use an inlet plenum when testing a

non-ducted system.

2.5 Indoor coil air property

measurements and air damper box

applications. a. Measure the dry-bulb

temperature and water vapor content of the

air entering and leaving the indoor coil. If

needed, use an air sampling device to divert

air to a sensor(s) that measures the water

vapor content of the air. See Figure 2 of

ASHRAE Standard 41.1–86 (RA 91) for

guidance on constructing an air sampling

device. The sampling device may also divert

air to a remotely located sensor(s) that

measures dry bulb temperature. You may use

the air sampling device and the remotely

located temperature sensor(s) to determine

the entering air dry bulb temperature during

any test. You may use the air sampling

device and the remotely located leaving air

dry bulb temperature sensor(s) for all tests

except:

(1) Cyclic tests, and

(2) Frost Accumulation tests.

b. An acceptable alternative in all cases,

including the two special cases noted above,

is to install a grid of dry bulb temperature

sensors within the outlet and inlet ducts. Use

a temperature grid to get the average dry bulb

temperature at one location, leaving or

entering, or when two grids are applied as a

thermopile, to directly obtain the

temperature difference. A grid of temperature

sensors (which may also be used for

determining average leaving air dry bulb

temperature) is required to measure the

temperature distribution within a crosssection of the leaving airstream.

c. Use an inlet and outlet air damper box

when testing ducted systems if conducting

one or both of the cyclic tests listed in

Sections 3.2 and 3.6 . Otherwise, DOE

recommends installing an outlet air damper

box when testing heat pumps, both ducted

and non-ducted, that cycle off the indoor fan

during defrost cycles. Never use an inlet

damper box when testing a non-ducted

system.

2.5.1 Test set-up on the inlet side of the

indoor coil: for cases where the inlet damper

box is installed. a: Install the inlet side

damper box as specified in Section 2.5.1.1 or

2.5.1.2, whichever applies. Insulate or

construct the ductwork between the point

where the air damper is installed and where

the connection is made to the following:

(1) The inlet plenum (Section 2.5.1.1

units); or

(2) To the indoor unit (Section 2.5.1.2

units) with thermal insulation that has a

nominal overall resistance (R-value) of at

least 19 hr·ft2·°F/Btu.

b. Locate the grid of entering air dry-bulb

temperature sensors, if used, at the inlet of

the damper box. Locate the air sampling

device, or the sensor used to measure the

water vapor content of the inlet air, at a

location immediately upstream of the damper

box inlet.

2.5.1.1 If the Section 2.4.2 inlet plenum is

installed. Install the inlet damper box

upstream of the inlet plenum. The crosssectional flow area of the damper box must

be equal to or greater than the flow area of

the inlet plenum. If needed, use an adaptor

plate or a transition duct section to connect

the damper box with the inlet plenum.

2.5.1.2 If the Section 2.4.2 inlet plenum is

not installed. Install the damper box

immediately upstream of the air inlet of the

indoor unit. The cross-sectional dimensions

of the damper box must be equal to or greater

than the dimensions of the indoor unit inlet.

If needed, use an adaptor plate or a short

transition duct section to connect the damper

box with the unit’s air inlet. Add static

pressure taps at the center of each face of the

damper box, if rectangular, or at four evenly

distributed locations along the

circumference, if oval or round. Locate the

pressure taps between the inlet damper and

the inlet of the indoor unit. Make a manifold

that connects the four static pressure taps.

2.5.2 Test set-up on the inlet side of the

indoor unit: for cases where no inlet damper

box is installed. If using the Section 2.4.2

inlet plenum and a grid of dry bulb

temperature sensors, mount the grid at a

location upstream of the static pressure taps

described in Section 2.4.2, preferably at the

entrance plane of the inlet plenum. If you do

not use the Section 2.4.2 inlet plenum, but

you are using a grid of dry bulb temperature

sensors, locate the grid approximately 6

inches from the inlet of the indoor coil. Or,

in the case of non-ducted units having

multiple indoor coils, locate a grid

approximately 6 inches from the inlet of each

indoor coil. Position an air sampling device,

or the sensor used to measure the water

vapor content of the inlet air, immediately

upstream of the (each) entering air dry-bulb

temperature sensor grid. If you are not using

a grid of sensors, position the entering air

sampling device (or the sensor used to

measure the water vapor content of the inlet

air) as if the grid were present.

2.5.3 Indoor coil static pressure

difference measurement. Section 6.4.4.1 of

ASHRAE Standard 37–88 describes the

recommended method for fabricating static

pressure taps. Also refer to Figure 2A of

ASHRAE Standard 51–99. Use a differential

pressure measuring instrument that is

accurate to within ±0.01 inches of water and

has a resolution of at least 0.01 inches of

water to measure the static pressure

difference between the indoor coil air inlet

and outlet. Connect one side of the

differential pressure instrument to the

manifolded pressure taps installed in the

outlet plenum. Connect the other side of the

instrument to the manifolded pressure taps

located in either the inlet plenum or

incorporated within the air damper box. If

you are not using an inlet plenum or inlet

damper box, leave the inlet side of the

differential pressure instrument open to the

surrounding atmosphere. For non-ducted

systems that are tested with multiple outlet

plenums, measure the static pressure within

each outlet plenum relative to the

surrounding atmosphere.

2.5.4 Test set-up on the outlet side of the

indoor coil. a: Install an interconnecting duct

between the outlet plenum described in

Section 2.4.1 and the airflow measuring

apparatus described below in Section 2.6.

The cross-sectional flow area of the

interconnecting duct must be equal to or

greater than the flow area of the outlet

plenum or the common duct used when

testing non-ducted units having multiple

indoor coils. If needed, use adaptor plates or

transition duct sections to allow the

connections. DOE recommends taping joints

within the interconnecting duct (and the

outlet plenum). Construct or insulate the

entire flow section with thermal insulation

having a nominal overall resistance (R-value)

of at least 19 hr·ft2·°F/Btu.

b. Install a grid(s) of dry-bulb temperature

sensors inside the interconnecting duct. Also,

install an air sampling device, or the

sensor(s) used to measure the water vapor

content of the outlet air, inside the

interconnecting duct. Locate the dry-bulb

temperature grid(s) upstream of the air

sampling device [or the in-duct sensor(s)

used to measure the water vapor content of

the outlet air]. Air that circulates through an

air sampling device and passed a remote

water-vapor-content sensor(s) must be

returned to the interconnecting duct at a

point:

(1) Downstream of the air sampling device,

(2) Upstream of the outlet air damper box,

if installed, and

(3) Upstream of the Section 2.6 airflow

measuring apparatus.

2.5.4.1 Outlet air damper box placement

and requirements. If using an outlet air

damper box (see Section 2.5), install it within

the interconnecting duct at a location

downstream of the location where air from

the sampling device is reintroduced or

downstream of the in-duct sensor that

measures water vapor content of the outlet

air. The leakage rate from the combination of

the outlet plenum, the closed damper, and

the duct section that connects these two

components must not exceed 20 cubic feet

per minute when a negative pressure of 1

inch of water column is maintained at the

plenum’s inlet.

2.5.4.2 Additional recommendations.

DOE recommends installing a mixing

device(s) upstream of the outlet air, dry-bulb

temperature grid (but downstream of the

outlet plenum static pressure taps). Also,

consider using a perforated screen located

between the mixing device and the dry-bulb

temperature grid. DOE recommends using a

screen having a maximum open area of 40

percent. One or both items should help to

6796 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

meet the maximum outlet air temperature

distribution specified in Section 3.1.8.

Mixing devices are described in Sections

6.3—6.5 of ASHRAE Standard 41.1–86 (RA

91) and Section 5.2.2 of ASHRAE Standard

41.2–87 (RA 92).

2.5.5 Dry bulb temperature measurement.

a. Measure dry bulb temperatures as

specified in Sections 4, 5, 6.1–6.10, 9, 10, and

11 of ASHRAE Standard 41.1–86 (RA 91).

The transient testing requirements cited in

Section 4.3 of ASHRAE Standard 41.1–86

(RA 91) apply if conducting a cyclic or Frost

Accumulation test.

b. Distribute the sensors of a dry-bulb

temperature grid over the entire flow area.

DOE recommends using 16 temperature

sensors within each temperature grid. The

required minimum is 9 sensors per grid. DOE

recommends installing redundant inlet and

outlet dry bulb temperature sensors and

particularly a thermopile. If using

thermocouples, DOE recommends the

following:

(1) Use 24 gauge wire,

(2) Remove approximately 1 inch of

insulation from each lead when preparing to

make a junction, and

(3) Use no more than two bonded turns per

junction.

2.5.6 Water vapor content measurement.

Determine water vapor content by measuring

dry-bulb temperature combined with the air

wet-bulb temperature, dew point

temperature, or relative humidity. If used,

construct and apply wet-bulb temperature

sensors as specified in Sections 4, 5, 6, 9, 10,

and 11 of ASHRAE Standard 41.1–86 (RA

91). As specified in ASHRAE Standard 41.1,

the temperature sensor (wick removed) must

be accurate to within ±0.2 °F. If used, apply

dew point hygrometers as specified in

Sections 5 and 8 of ASHRAE Standard 41.6–

94. The dew point hygrometers must be

accurate to within ±0.4 °F when operated at

conditions that result in the evaluation of

dew points above 35 °F. If used, a relative

humidity meter must be accurate to within

±0.7% RH. Other means to determine the

psychrometric state of air may be used as

long as the measurement accuracy is

equivalent or better than the accuracy

achieved from using a wet-bulb temperature

sensor that meets the above specifications.

2.5.7 Air damper box performance

requirements. If used (see Section 2.5), the air

damper box(es) must be capable of being

completely opened or completely closed

within 10 seconds for each action.

2.6 Airflow measuring apparatus. a.

Fabricate and operate an Air Flow Measuring

Apparatus as specified in Section 6.6 of

ASHRAE Standard 116–95. Refer to Figure 12

of ASHRAE Standard 51–99 or Figure 14 of

ASHRAE Standard 41.2–87 (RA 92) for

guidance on placing the static pressure taps

and positioning the diffusion baffle (settling

means) relative to the chamber inlet.

b. Connect the airflow measuring apparatus

to the interconnecting duct section described

in Section 2.5.4. See Sections 6.1.1, 6.1.2,

and 6.1.4, and Figures 1, 2, and 4 of ASHRAE

Standard 37–88, and Figures B1, B2, and B4

of ARI Standard 210/240–94 for illustrative

examples of how the test apparatus may be

applied within a complete laboratory set-up.

Instead of following one of these examples,

you may use an alternative set-up to handle

the air leaving the airflow measuring

apparatus and to supply properly

conditioned air to the test unit’s inlet. The

alternative set-up, however, must not

interfere with the prescribed means for

measuring airflow rate, inlet and outlet air

temperatures, inlet and outlet water vapor

contents, and external static pressures, nor

create abnormal conditions surrounding the

test unit. (Note: do not use an enclosure as

described in Section 6.1.3 of ASHRAE

Standard 37–88 when testing triple-split

units.)

2.7 Electrical voltage supply. Perform all

tests at the voltage specified in Section

5.1.3.2 of ARI Standard 210/240–94 for

‘‘Standard Rating Tests.’’ Measure the supply

voltage at the terminals on the test unit using

a volt meter that provides a reading that is

accurate to within ±1.0 percent of the

measured quantity.

2.8 Electrical power and energy

measurements. a. Use an integrating power

(watt-hour) measuring system to determine

the electrical energy or average electrical

power supplied to all components of the air

conditioner or heat pump (including

auxiliary components such as controls,

transformers, crankcase heater, integral

condensate pump on non-ducted indoor

units, etc.). The watt-hour measuring system

must give readings that are accurate to within

±0.5 percent. For cyclic tests, this accuracy

is required during both the ON and OFF

cycles. Use either two different scales on the

same watt-hour meter or two separate watthour meters. Activate the scale or meter

having the lower power rating within 15

seconds after beginning an OFF cycle.

Activate the scale or meter having the higher

power rating active within 15 seconds prior

to beginning an ON cycle. For ducted units

tested with a fan installed, the ON cycle lasts

from compressor ON to indoor fan OFF. For

ducted units tested without an indoor fan

installed, the ON cycle lasts from compressor

ON to compressor OFF. For non-ducted

units, the ON cycle lasts from indoor fan ON

to indoor fan OFF. When testing air

conditioners and heat pumps having a

variable-speed compressor, avoid using an

induction watt/watt-hour meter. Instead,

consider using a watt-hour measuring system

that is capable of measuring up to the 50th

harmonic.

b. When performing Section 3.5 and/or 3.8

cyclic tests on non-ducted units, provide

instrumentation to determine the average

electrical power consumption of the indoor

fan motor to within ±1.0 percent. If required

according to Sections 3.3, 3.4, 3.7, 3.9.1, and/

or 3.10, this same instrumentation

requirement applies when testing air

conditioners and heat pumps having a

variable-speed constant-air-volume-rate

indoor fan or a variable-speed, variable-airvolume-rate indoor fan.

2.9 Time measurements. Make elapsed

time measurements using an instrument that

yields readings accurate to within ±0.2

percent.

2.10 Test apparatus for the secondary

space conditioning capacity measurement.

For all tests, use the Indoor Air Enthalpy

Method to measure the unit’s capacity. This

method uses the test set-up specified in

Sections 2.4 to 2.6. For all steady-state tests,

in addition, conduct a second, independent

measurement of capacity. For split systems,

use one of the following secondary

measurement methods: Outdoor Air Enthalpy

Method, Compressor Calibration Method, or

Refrigerant Enthalpy Method. Use either the

Outdoor Air Enthalpy Method or the

Compressor Calibration Method as the

secondary measurement when testing a

single packaged unit.

2.10.1 Outdoor Air Enthalpy Method. a.

To make a secondary measurement of indoor

space conditioning capacity using the

Outdoor Air Enthalpy Method, do the

following:

(1) Measure the electrical power

consumption of the test unit,

(2) Measure the air-side capacity at the

outdoor coil, and

(3) Apply a heat balance on the refrigerant

cycle.

b. The test apparatus required for the

Outdoor Air Enthalpy Method is a subset of

the apparatus used for the Indoor Air

Enthalpy Method. Required apparatus

includes the following:

(1) An outlet plenum containing static

pressure taps (Sections 2.4, 2.4.1, and 2.5.3),

(2) An airflow measuring apparatus

(Section 2.6),

(3) A duct section that connects these two

components and itself contains the

instrumentation for measuring the dry-bulb

temperature and water vapor content of the

air leaving the outdoor coil (Sections 2.5.4,

2.5.5, and 2.5.6), and

(4) On the inlet side, a sampling device and

optional temperature grid (Sections 2.5 and

2.5.2).

c. During the preliminary tests described in

Sections 3.11.1 and 3.11.1.1, measure the

evaporator and condenser temperatures or

pressures. On both the outdoor coil and the

indoor coil, solder a thermocouple onto a

return bend located at or near the midpoint

of each coil or at points not affected by vapor

superheat or liquid subcooling. Alternatively,

if the test unit is not sensitive to the

refrigerant charge, connect pressure gages to

the access valves or to ports created from

tapping into the suction and discharge lines.

Use this alternative approach when testing a

unit charged with a zeotropic refrigerant

having a temperature glide in excess of 1°F

at the specified test conditions.

2.10.2 Compressor Calibration Method.

Measure refrigerant pressures and

temperatures to determine the evaporator

superheat and the enthalpy of the refrigerant

that enters and exits the indoor coil.

Determine refrigerant flow rate or, when the

superheat of the refrigerant leaving the

evaporator is less that 5 °F, total capacity

from separate calibration tests conducted

under identical operating conditions. Install

instrumentation; measure refrigerant

properties; adjust the refrigerant charge

according to Section 7.4.2 of ASHRAE

Standard 37–88. Use refrigerant temperature

and pressure measuring instruments that

meet the specifications given in Sections

5.1.1 and 5.2 of ASHRAE Standard 37–88.

2.10.3 Refrigerant Enthalpy Method. For

this method, calculate space conditioning

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6797

capacity by determining the refrigerant

enthalpy change for the indoor coil and

directly measuring the refrigerant flow rate.

Refer to Section 7.6.2 of ASHRAE Standard

37–88 for the requirements for using the

method, the additional instrumentation

requirements, and information on placing the

flow meter and a sight glass. Use refrigerant

temperature, pressure, and flow measuring

instruments that meet the specifications

given in Sections 5.1.1, 5.2, and 5.5.1 of

ASHRAE Standard 37–88.

2.11 Measurement of test room ambient

conditions. a. If using a test set-up where air

is ducted directly from the conditioning

apparatus to the indoor coil inlet (see Figure

2, Loop Air-Enthalpy Test Method

Arrangement, of ASHRAE Standard 37–88),

add instrumentation to permit measurement

of the indoor test room dry-bulb temperature.

b. If you are not using the Outdoor Air

Enthalpy Method, add instrumentation to

measure the dry-bulb temperature and the

water vapor content of the air entering the

outdoor coil. DOE recommends measuring

water vapor content by using an air sampling

device to divert air to a remotely located

sensor(s). If used, construct and apply the air

sampling device as per Section 6 of ASHRAE

Standard 41.1–86 (RA 91). You may use the

air sampling device to also divert air to a

sensor that measures outdoor-side entering

dry bulb temperature. However, DOE

recommends positioning dry bulb

temperature sensors around the exterior of

the entire outdoor coil and using them to

determine an average entering dry bulb

temperature. In such cases, use individually

monitored sensors to identify any significant

temperature distribution. Take steps (e.g.,

add or re-position a lab circulating fan), as

needed, to minimize the magnitude of the

temperature distribution. Position any fan in

the outdoor test room while trying to keep air

velocities in the vicinity of the test unit

below 500 feet per minute.

c. Measure dry bulb temperatures as

specified in Sections 4, 5, 6.1–6.10, 9, 10, and

11 of ASHRAE Standard 41.1–86 (RA 91).

Measure water vapor content as stated above

in Section 2.5.6.

2.12 Measurement of indoor fan speed.

When required, measure fan speed using a

revolution counter, tachometer, or

stroboscope that gives readings accurate to

within ±1.0 percent.

2.13 Measurement of barometric

pressure. Determine the average barometric

pressure during each test. Use an instrument

that meets the requirements specified in

Section 5.2 of ASHRAE Standard 37–88.

3. Testing Procedures

3.1 General Requirements. If during the

testing process you make an equipment setup adjustment that would alter the

performance of the unit when conducting an

already completed test, then repeat all tests

affected by the adjustment. For cyclic tests,

instead of maintaining an air volume rate,

maintain the airflow nozzle(s)’ static pressure

difference or velocity pressure during an ON

period at the same pressure difference or

velocity pressure as measured during the

steady-state test conducted at the same test

conditions.

3.1.1 Primary and secondary test

methods. For all tests, use the Indoor Air

Enthalpy Method test apparatus to determine

the test unit’s space conditioning capacity.

The procedure and data collected, however,

differ slightly depending upon whether the

test is a steady-state test, a cyclic test, or a

Frost Accumulation test. The following

sections described these differences. For all

steady-state tests (i.e., the A, A2, A1, B, B2,

B1, C, C1, EV, F1, G1, H0, H01, H1, H12, H11,

HIN, H3, H32, and H31 Tests), in addition, use

one of the acceptable secondary methods

specified in Section 2.10 to determine indoor

space conditioning capacity. Calculate this

secondary check of capacity according to

Section 3.11. The two capacity measurements

must agree to within 6 percent to constitute

a valid test. For this capacity comparison, use

the Indoor Air Enthalpy Method capacity that

is calculated in Section 7.3 of ASHRAE

Standard 37–88 (and do not make the aftertest fan heat adjustments described in

Sections 3.3, 3.4, 3.7, and 3.10 of this

Appendix). However, include the appropriate

Section 3.3 to 3.5 and 3.7 to 3.10 fan heat

adjustments within the Indoor Air Enthalpy

Method capacities used for the Section 4

seasonal calculations.

3.1.2 Manufacturer-provided equipment

overrides. Where needed, the manufacturer

must provide a means for overriding the

controls of the test unit so that the

compressor(s) operates at the specified speed

or capacity and the indoor fan operates at the

specified speed or delivers the specified air

volume rate.

3.1.3 Airflow through the outdoor coil.

For all tests, meet the requirements given in

Section 5.1.3.4 of ARI Standard 210/240–94

when obtaining the airflow through the

outdoor coil.

3.1.4 Airflow through the indoor coil.

3.1.4.1 Cooling Certified Air Volume

Rate.

3.1.4.1.1 Cooling Certified Air Volume

Rate for Ducted Units. The manufacturer

must specify the Cooling Certified Air

Volume Rate. Use this value as long as the

following two requirements are satisfied.

First, when conducting the A or A2 Test

(exclusively), the measured air volume rate,

when divided by the measured indoor airside total cooling capacity, must not exceed

37.5 cubic feet per minute of standard air

(SCFM ) per 1000 Btu/h. If this ratio is

exceeded, reduce the air volume rate until

this ratio is equaled. Use this reduced air

volume rate for all tests that call for using the

Cooling Certified Air Volume Rate. The

second requirement is as follows:

a. For ducted units that are tested with a

fixed-speed, multi-speed, or variable-speed

variable-air-volume-rate indoor fan installed.

For the A or A2 Test (exclusively), the

measured external static pressure must be

equal to or greater than the applicable

minimum external static pressure cited in

Table 2. If the Table 2 minimum is not

equaled or exceeded, incrementally change

the set-up of the indoor fan (e.g., fan motor

pin settings, fan motor speed) until the Table

2 requirement is met while maintaining the

same air volume rate. If the indoor fan setup changes cannot provide the minimum

external static, then reduce the air volume

rate until the correct Table 2 minimum is

equaled. For the last scenario, use the

reduced air volume rate for all tests that

require the Cooling Certified Air Volume

Rate.

b. For ducted units that are tested with a

constant-air-volume-rate indoor fan installed.

For all tests that specify the Cooling Certified

Air Volume Rate, obtain an external static

pressure as close to (but not less than) the

applicable Table 2 value that does not cause

instability or an automatic shutdown of the

indoor blower. For the A or A2 Test

(exclusively), the average air volume rate

from the 30-minute data collection interval

(see Section 3.3) and the manufacturerprovided Cooling Certified Air Volume Rate

must differ by 8 percent or less.

c. For ducted units that are tested without

an indoor fan installed. For the A or A2 Test,

(exclusively), the pressure drop across the

indoor coil assembly must not exceed a

specified maximum. The maximum value is

0.30 inches of water for all units except

small-duct, high-velocity systems (see 1.46)

for which the limit is 0.50 inches of water.

If the maximum value is exceeded, reduce

the air volume rate until the measured

pressure drop equals the specified maximum.

Use this reduced air volume rate for all tests

that require the Cooling Certified Air Volume

Rate.

TABLE 2.—MINIMUM EXTERNAL STATIC

PRESSURE FOR DUCTED SYSTEMS

TESTED WITH AN INDOOR FAN INSTALLED

Rated cooling 1 or heating 2

capacity (Btu/h)

Minimum

external resistance 3

(inches of

water)

Up Thru 28,800 ........................ 0.10

29,000 to 42,500 ...................... 0.15

43,000 and Above .................... 0.20

1For 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. 2For 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. 3For ducted units tested without an air filter

installed, increase the applicable tabular value

by 0.08 inches of water.

3.1.4.1.2 Cooling Certified Air Volume

Rate for Non-ducted Units. For non-ducted

units, the Cooling Certified Air Volume Rate

is the air volume rate that results during each

test when the unit is operated at an external

static pressure of zero inches of water.

3.1.4.2 Cooling Minimum Air Volume

Rate. a. For ducted units that regulate the

speed (as opposed to the CFM) of the indoor

fan,

6798 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

Cooling Minimum Air Vol. Rate Cooling Certified Air Vol. Rate . Cooling Minimum Fan Speed 

 Test Fan Speed = A2

,

where ‘‘Cooling Minimum Fan Speed’’

corresponds to the fan speed used when

operating at low compressor capacity (twocapacity system), the fan speed used when

operating at the minimum compressor speed

(variable-speed system), or the lowest fan

speed used when cooling (single-speed

compressor and a variable-speed variable-airvolume-rate indoor fan). For such systems,

obtain the Cooling Minimum Air Volume

Rate regardless of the external static pressure.

b. For ducted units that regulate the air

volume rate provided by the indoor fan, the

manufacturer must specify the Cooling

Minimum Air Volume Rate. For such

systems, conduct all tests that specify the

Cooling Minimum Air Volume Rate—the A1,

B1, C1, F1, and G1 Tests—at an external static

pressure that does not cause instability or an

automatic shutdown of the indoor blower

while being as close to, but not less than,

A1

2

, , ,, B C F & G Test P P . Cooling Minimum Air Volume Rate

Cooling Certified Air Volume Rate , 1 1 1 1 st st,A2 ∆ ∆= 



 





where ∆Pst, A2 is the applicable Table 2

minimum external static pressure that was

targeted during the A2 (and B2) Test. Only for

the first test, the average measured air

volume rate and the manufacturer-specified

Cooling Minimum Air Volume Rate must

differ by 8 percent or less.

c. For ducted two-capacity units that are

tested without an indoor fan installed, the

Cooling Minimum Air Volume Rate is the

higher of the rate specified by the

manufacturer or 75 percent of the Cooling

Certified Air Volume Rate. During the

laboratory tests on a coil-only (fanless) unit,

obtain this Cooling Minimum Air Volume

Rate regardless of the pressure drop across

the indoor coil assembly.

d. For non-ducted units, the Cooling

Minimum Air Volume Rate is the air volume

rate that results during each test when the

unit operates at an external static pressure of

zero inches of water and at the indoor fan

setting used at low compressor capacity (twocapacity system) or minimum compressor

speed (variable-speed system). For units

having a single-speed compressor and a

variable-speed variable-air-volume-rate

indoor fan, use the lowest fan setting allowed

for cooling.

3.1.4.3 Cooling Intermediate Air Volume

Rate. a. For ducted units that regulate the

speed of the indoor fan,

Cooling Intermediate Air Volume Rate ooling Certified Air Volume Rate . E Test Fan Speed

A Test Fan Speed

V

2

= C .

b. For such units, obtain the Cooling

Intermediate Air Volume Rate regardless of

the external static pressure.

c. For ducted units that regulate the air

volume rate provided by the indoor fan, the

manufacturer must specify the Cooling

Intermediate Air Volume Rate. For such

systems, conduct the EV Test at an external

static pressure that does not cause instability

or an automatic shutdown of the indoor

blower while being as close to, but not less

than,

E Test P P . Cooling Intermediate Air Volume Rate

Cooling Certified Air Volume Rate V st st,A2 ∆ ∆ = 



 





2

,

where ∆Pst, A2 is the applicable Table 2

minimum external static pressure that was

targeted during the A2 (and B2) Test.

d. For non-ducted units, the Cooling

Intermediate Air Volume Rate is the air

volume rate that results when the unit

operates at an external static pressure of zero

inches of water and at the fan speed selected

by the controls of the unit for the EV Test

conditions.

3.1.4.4 Heating Certified Air Volume

Rate.

3.1.4.4.1 Ducted heat pumps where the

Heating and Cooling Certified Air Volume

Rates are the same.

a. Use the Cooling Certified Air Volume

Rate as the Heating Certified Air Volume Rate

for:

1. Ducted heat pumps that operate at the

same indoor fan speed during both the A (or

A2) and the H1 (or H12) Tests,

2. Ducted heat pumps that regulate fan

speed to deliver the same constant air

volume rate during both the A (or A2) and the

H1 (or H12) Tests, and

3. Ducted heat pumps that are tested

without an indoor fan installed (except twocapacity heat pumps that lock out high

capacity cooling—see 3.1.4.4.2).

b. For heat pumps that meet the above

criteria ‘‘1’’ and ‘‘3,’’ no minimum

requirements apply to the measured external

or internal, respectively, static pressure. For

heat pumps that meet the above criterion

‘‘2,’’ test at an external static pressure that

does not cause instability or an automatic

shutdown of the indoor blower while being

as close to, but not less than, the same Table

2 minimum external static pressure as was

specified for the A (or A2) cooling mode test.

3.1.4.4.2 Ducted heat pumps where the

Heating and Cooling Certified Air Volume

Rates are different due to indoor fan

operation.

a. For ducted heat pumps that regulate the

speed (as opposed to the CFM) of the indoor

fan,

Heating Certified Air Volume Rate Cooling Certified Air Volume Rate . H1 or H1 Test Fan Speed

A or A Test Fan Speed

2

2

= .

b. For such heat pumps, obtain the Heating

Certified Air Volume Rate without regard to

the external static pressure.

c. For ducted heat pumps that regulate the

air volume rate delivered by the indoor fan,

the manufacturer must specify the Heating

Certified Air Volume Rate. For such heat

pumps, conduct all tests that specify the

Heating Certified Air Volume Rate at an

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6799

external static pressure that does not cause

instability or an automatic shutdown of the

indoor blower while being as close to, but not

less than,

Heating Certified P rtified P Heating Certified Air Volume Rate

Cooling Certified Air Volume Rate

∆ ∆ st st = 



 



Cooling Ce  . ,

2

where the Cooling Certified ∆Pst is the

applicable Table 2 minimum external static

pressure that was specified for the A or A2

Test. For the first test that uses the Heating

Certified Air Volume Rate, the average

measured air volume rate and the

manufacturer-specified Heating Certified Air

Volume Rate, both expressed in SCFM, must

differ by 8 percent or less.

d. When testing ducted, two-capacity heat

pumps that lock out high capacity operation

when cooling, use the appropriate approach

of the above two cases for units that are

tested with an indoor fan installed. For coilonly (fanless) heat pumps that lock out high

capacity cooling, the Heating Certified Air

Volume Rate is the lesser of the rate specified

by the manufacturer or 133 percent of the

Cooling Certified Air Volume Rate. For this

latter case, obtain the Heating Certified Air

Volume Rate regardless of the pressure drop

across the indoor coil assembly.

3.1.4.4.3 Ducted heating-only heat

pumps. This section applies when testing

ducted two-capacity heat pumps that lock

out high capacity operation when cooling.

The manufacturer must specify the Heating

Certified Air Volume Rate. Use this value

when the following two requirements are

satisfied. First, when conducting the H1 or

H12 Test (exclusively), the measured air

volume rate, when divided by the measured

indoor air-side total heating capacity, must

not exceed 37.5 cubic feet per minute of

standard air (SCFM) per 1000 Btu/h. If this

ratio is exceeded, reduce the air volume rate

until this ratio is equaled. Use this reduced

air volume rate for all tests of heating-only

heat pumps that call for the Heating Certified

Air Volume Rate. The second requirement is

as follows:

a. For heating-only heat pumps that are

tested with a fixed-speed, multi-speed, or

variable-speed variable-air-volume-rate

indoor fan installed. For the H1 or H12 Test

(exclusively), the measured external static

pressure must be equal to or greater than the

Table 2 minimum external static pressure

that applies given the heating-only heat

pump’s rated heating capacity. If the Table 2

minimum is not equaled or exceeded,

incrementally change the set-up of the indoor

fan until the Table 2 requirement is met

while maintaining the same air volume rate.

If the indoor fan set-up changes cannot

provide the necessary external static, then

reduce the air volume rate until the correct

Table 2 minimum is equaled. For the last

scenario, use the reduced air volume rate for

all tests that require the Heating Certified Air

Volume Rate.

b. For ducted heating-only heat pumps

having a constant-air-volume-rate indoor fan.

For all tests that specify the Heating Certified

Air Volume Rate, obtain an external static

pressure that does not cause instability or an

automatic shutdown of the indoor blower

while being as close to, but not less than, the

applicable Table 2 minimum. For the H1 or

H12 Test (exclusively), the average air

volume rate from the 30-minute data

collection interval (see Section 3.7) and the

manufacturer-provided Heating Certified Air

Volume Rate must differ by 8 percent or less.

c. For ducted heating-only heat pumps that

are tested without an indoor fan installed.

For the H1 or H12 Test, (exclusively), the

pressure drop across the indoor coil assembly

must not exceed a specified maximum. The

maximum value is 0.30 inches of water for

all units except small-duct, high-velocity

systems (see 1.46) for which the limit is 0.50

inches of water. If the maximum value is

exceeded, reduce the air volume rate until

the measured pressure drop equals the

specified maximum. Use this reduced air

volume rate for all tests that require the

Heating Certified Air Volume Rate.

3.1.4.4.4 Non-ducted heat pumps,

including non-ducted heating-only heat

pumps. For non-ducted heat pumps, the

Heating Certified Air Volume Rate is the air

volume rate that results during each test

when the unit operates at an external static

pressure of zero inches of water.

3.1.4.5 Heating Minimum Air Volume

Rate. a. For ducted heat pumps that regulate

the speed (as opposed to the CFM) of the

indoor fan,

Heating Minimum Air Volume Rate rtified Air Volume Rate . Heating Minimum Fan Speed

H1 Test Fan Speed 2

=Heating Ce ,

where ‘‘Heating Minimum Fan Speed’’

corresponds to the fan speed used when

operating at low compressor capacity (twocapacity system), the lowest fan speed used

at any time when operating at the minimum

compressor speed (variable-speed system), or

the lowest fan speed used when heating

(single-speed compressor and a variablespeed variable-air-volume-rate indoor fan).

For such heat pumps, obtain the Heating

Minimum Air Volume Rate without regard to

the external static pressure.

b. For ducted heat pumps that regulate the

air volume rate delivered by the indoor fan,

the manufacturer must specify the Heating

Minimum Air Volume Rate. For such heat

pumps, conduct all tests that specify the

Heating Minimum Air Volume Rate—the

H01, H11, H21, and H31, at an external static

pressure that does not cause instability or an

automatic shutdown of the indoor blower

while being as close to, but not less than,

H0 , H1 , H2 & H3 Test P m Air Vol. Rate

Htg Certified Air Vol. Rate 1 1 1 1 st , . , ∆ ∆ = ,





 



P  Htg Minimu

st H1

2

2

where is ∆Pst,H12 is the minimum external

static pressure that was targeted during the

H12 Test. Only for the first test, the average

measured air volume rate and the

manufacturer-specified Heating Minimum

Air Volume Rate must differ by 8 percent or

less.

c. When testing ducted, two-capacity heat

pumps that lock out high capacity operation

when cooling, use the appropriate approach

of the above two cases for units that are

tested with a indoor fan installed.

d. For ducted two-capacity heat pumps

that are tested without an indoor fan

installed, use the Cooling Minimum Air

Volume Rate as the Heating Minimum Air

Volume Rate. For ducted two-capacity heat

pumps that are tested without an indoor fan

installed, and that lock out high capacity

operation when cooling, use the Cooling

Certified Air Volume Rate as the Heating

Minimum Air Volume Rate. For ducted twocapacity heating-only heat pumps that are

tested without an indoor fan installed, the

Heating Minimum Air Volume Rate is the

higher of the rate specified by the

manufacturer or 75 percent of the Heating

Certified Air Volume Rate. During the

laboratory tests on a coil-only (fanless) unit,

obtain the Heating Minimum Air Volume

Rate without regard to the pressure drop

across the indoor coil assembly.

6800 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

e. For non-ducted heat pumps, the Heating

Minimum Air Volume Rate is the air volume

rate that results during each test when the

unit operates at an external static pressure of

zero inches of water and at the indoor fan

setting used at low compressor capacity (twocapacity system) or minimum compressor

speed (variable-speed system). For units

having a single-speed compressor and a

variable-speed, variable-air-volume-rate

indoor fan, use the lowest fan setting allowed

for heating.

3.1.4.6 Heating Intermediate Air Volume

Rate. a. For ducted heat pumps that regulate

the speed of the indoor fan,

Heating Intermediate Air Volume Rate = Heating Certified Air Volume Rate . H2 Test Fan Speed

H1 Test Fan Speed

V

2

.

b. For such heat pumps, obtain the Heating

Intermediate Air Volume Rate without regard

to the external static pressure.

c. For ducted heat pumps that regulate the

air volume rate delivered by the indoor fan,

the manufacturer must specify the Heating

Intermediate Air Volume Rate. For such heat

pumps, conduct the H2V Test at an external

static pressure that does not cause instability

or an automatic shutdown of the indoor

blower while being as close to, but not less

than,

H2 Test P termediate Air Volume Rate

Heating Certified Air Volume Rate V st ∆ ∆= 



 



P  Heating In

st H, . , 1

2

2

where ∆Pst,H12 is the minimum external static

pressure that was specified for the H12 Test.

d. For non-ducted heat pumps, the Heating

Intermediate Air Volume Rate is the air

volume rate that results when the heat pump

operates at an external static pressure of zero

inches of water and at the fan speed selected

by the controls of the unit for the H2V Test

conditions.

3.1.4.7 Heating Nominal Air Volume

Rate. Except for the noted changes,

determine the Heating Nominal Air Volume

Rate using the approach described in Section

3.1.4.6. Required changes include

substituting ‘‘H1N Test’’ for ‘‘H2V Test’’

within the first Section 3.1.4.6 equation,

substituting ‘‘H1N Test ∆Pst‘‘ for ‘‘H2V Test

∆Pst‘‘ in the second Section 3.1.4.6 equation,

substituting ‘‘H1N Test’’ for each ‘‘H2V Test’’,

and substituting ‘‘Heating Nominal Air

Volume Rate’’ for each ‘‘Heating Intermediate

Air Volume Rate.’’

3.1.5 Indoor test room requirement when

the air surrounding the indoor unit is not

supplied from the same source as the air

entering the indoor unit. If using a test setup where air is ducted directly from the air

reconditioning apparatus to the indoor coil

inlet (see Figure 2, Loop Air-Enthalpy Test

Method Arrangement, of ASHRAE Standard

37–88), maintain the dry bulb temperature

within the test room within ±5.0 °F of the

applicable Sections 3.2 and 3.6 dry bulb

temperature test condition for the air entering

the indoor unit.

3.1.6 Air volume rate calculations. For all

steady-state tests and for Frost Accumulation

(H2, H21, H22, H2V) Tests, calculate the air

volume rate through the indoor coil as

specified in Sections 7.8.3.1 and 7.8.3.2 of

ASHRAE Standard 37–88. When using the

Outdoor Air Enthalpy Method, follow

Sections 7.8.3.1 and 7.8.3.2 to calculate the

air volume rate through the outdoor coil. To

express air volume rates in terms of standard

air, use:

 ̇  ̇

. . .

 ̇ V lbm

ft

s da

=

′ [ ] = V

 v 1+W

V

0.075 lbm

ft

. v

(3-1) mx

n n

mx

da 0 075 3 3 n

where,

V ̇

s =

air volume rate of standard (dry) air, (ft3/min)da

V ̇

mx =

air volume rate of the air-water vapor

mixture, (ft3/min)mx

v′

n =

specific volume of air-water vapor mixture at

the nozzle, ft3 per lbm of the air-water vapor

mixture

Wn= humidity ratio at the nozzle, lbm of

water vapor per lbm of dry air

0.075= the density associated with standard

(dry) air

Vn= specific volume of the dry air portion of

the mixture evaluated at the dry-bulb

temperature, vapor content, and barometric

pressure existing at the nozzle, ft3 per lbm of

dry air.

3.1.7 Test sequence. When testing a

ducted unit (except if a heating-only heat

pump), conduct the A or A2 Test first to

establish or verify the Cooling Certified Air

Volume Rate. For ducted heat pumps where

the Heating and Cooling Certified Air

Volume Rates are different, make the first

heating mode test one that requires the

Heating Certified Air Volume Rate. For

ducted heating-only heat pumps, conduct the

H1 or H12 Test first to establish or verify the

Heating Certified Air Volume Rate. When

conducting an optional cyclic test, always

conduct it immediately after the steady-state

test that requires the same test conditions.

For variable-speed systems, the first test

using the Cooling Minimum Air Volume Rate

should precede the EV Test if you expect to

adjust the indoor fan control options when

preparing for the first Minimum Air Volume

Rate test. Under the same circumstances, the

first test using the Heating Minimum Air

Volume Rate should precede the H2V Test.

The test laboratory makes all other decisions

on the test sequence.

3.1.8 Requirement for the air temperature

distribution leaving the indoor coil. For at

least the first cooling mode test and the first

heating mode test, monitor the temperature

distribution of the air leaving the indoor coil

using the grid of individual sensors described

in Sections 2.5 and 2.5.4. For the 30-minute

data collection interval used to determine

capacity, the maximum spread among the

outlet dry bulb temperatures from any data

sampling must be 1.5 °F or less. Install the

mixing devices described in Section 2.5.4.2

to minimize the temperature spread.

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6801

3.1.9 Control of auxiliary resistive heating

elements. Except as noted, disable heat pump

resistance elements used for heating indoor

air at all times, including during defrost

cycles and if they are normally regulated by

a heat comfort controller. For heat pumps

equipped with a heat comfort controller,

enable the heat pump resistance elements

only during the below-described, short test

that follows the H1 or, if conducted, the H1C

Test. Set the heat comfort controller to

provide the maximum supply air

temperature. With the heat pump operating

and while maintaining the Heating Certified

Air Volume Rate, measure the temperature of

the air leaving the indoor-side beginning 5

minutes after activating the heat comfort

controller. Sample the outlet dry-bulb

temperature at regular intervals that span 5

minutes or less. Collect data for 10 minutes,

obtaining at least 3 samples. Calculate the

average outlet temperature over the 10-

minute interval, TCC.

3.2 Cooling mode tests for different types

of air conditioners and heat pumps.

3.2.1 Tests for a unit having a single-speed

compressor that is tested with a fixed-speed

indoor fan installed, with a constant-airvolume-rate indoor fan installed, or with no

indoor fan installed. Conduct two steadystate wet coil tests, the A and B Tests. Use

the two optional dry-coil tests, the steadystate C Test and the cyclic D Test, to

determine the cooling mode cyclic

degradation coefficient, Cc

D. If the two

optional tests are not conducted, assign Cc

D

the default value of 0.25. Table 3 specifies

test conditions for these four tests.

TABLE 3.—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A FIXED-SPEED

INDOOR FAN, A CONSTANT AIR VOLUME RATE INDOOR FAN, OR NO INDOOR FAN

Test Description

Air entering indoor unit

Temperature (°F)

Air entering outdoor unit

Temperature (°F) Cooling Air Volume Rate

Dry bulb Wet bulb Dry bulb Wet bulb

A Test—required (steady, wet coil) ................................. 80 67 95 1 75 Cooling Certified 2

B Test—required (steady, wet coil) ................................. 80 67 82 1 65 Cooling Certified 2

C Test—optional (steady, dry coil) .................................. 80 3 82 – Cooling Certified 2

D Test—optional (cyclic, dry coil) ................................... 80 3 82 – 4

1The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in Section 3.1.4.1.

3The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air

wet-bulb temperature of 57 °F or less. 4 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity

pressure as measured during the C Test.

3.2.2 Tests for a unit having a single-speed

compressor and a variable-speed variable-airvolume-rate indoor fan installed.

3.2.2.1 Indoor fan capacity modulation

that correlates with the outdoor dry bulb

temperature. Conduct four steady-state wet

coil tests: The A2, A1, B2, and B1 Tests. Use

the two optional dry-coil tests, the steadystate C1 Test and the cyclic D1 Test, to

determine the cooling mode cyclic

degradation coefficient, Cc

D. If the two

optional tests are not conducted, assign Cc

D

the default value of 0.25. Table 4 specifies

test conditions for these six tests.

3.2.2.2 Indoor fan capacity modulation

based on adjusting the sensible to total (S/T)

cooling capacity ratio. The testing

requirements are the same as specified in

Section 3.2.1 and Table 3. Use a Cooling

Certified Air Volume Rate that represents a

normal residential installation. If performed,

conduct the steady-state C Test and the cyclic

D Test with the unit operating in the same

S/T capacity control mode as used for the B

Test.

TABLE 4.—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A VARIABLE AIR

VOLUME RATE INDOOR FAN THAT IS CONTROLLED AS SPECIFIED IN 3.2.2.1

Test description

Air entering indoor

unit

temperature (°F)

Air entering outdoor

unit

temperature (°F) Cooling air volume rate

Dry bulb Wet bulb Dry bulb Wet bulb

A2 Test—required (steady, wet coil) .......................................... 80 67 95 (1) 75 Cooling Certified 2.

A1 Test—required (steady, wet coil) .......................................... 80 67 95 (1) 75 Cooling Minimum 3.

B2 Test—required (steady, wet coil) .......................................... 80 67 82 (1) 65 Cooling Certified 2.

B1 Test—required (steady, wet coil) .......................................... 80 67 82 (1) 65 Cooling Minimum 3.

C1 Test 4—optional (steady, dry coil) ......................................... 80 (4) 82 ................ Cooling Minimum 3.

D1 Test 4—optional (cyclic, dry coil) .......................................... 80 (4) 82 ................ (5).

1The 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.

4The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air

wet-bulb temperature of 57 °F or less. 5 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity

pressure as measured during the C1 Test.

3.2.3 Tests for a unit having a twocapacity compressor. a. (See Definition 1.44.)

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, Cc

D. If the two

optional tests are not conducted, assign Cc

D

the default value of 0.25. Table 5 specifies

test conditions for these six tests.

b. For units having a variable speed indoor

fan that is modulated to adjust the sensible

to total (S/T) cooling capacity ratio, use

Cooling Certified and Cooling Minimum Air

Volume Rates that represent a normal

residential installation. Additionally, if

conducting the optional dry-coil tests,

operate the unit in the same S/T capacity

control mode as used for the B1 Test.

c. Two-capacity units that operate

exclusively, via a lockout feature, at low

compressor capacity when space cooling

must be tested as a single speed system (see

Section 3.2.1 and Table 3). If a two-capacity

6802 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

unit locks out low capacity operation at

outdoor temperatures that are less than 95 °F,

conduct the A1 Test using the outdoor

temperature conditions listed for the F1 Test

in Table 6 rather than using the outdoor

temperature conditions listed in Table 5 for

the A1 Test.

TABLE 5.—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR

Test description

Air entering indoor

unit

temperature (°F)

Air entering outdoor

unit

temperature (°F) Compressor

capacity Cooling air volume rate

Dry bulb Wet bulb Dry bulb Wet bulb

A2 Test—required (steady, wet coil) ..................... 80 67 95 1 75 High .................. Cooling Certified 2.

A1 Test—required (steady, wet coil) ..................... 80 67 95 1 75 Low ................... Cooling Minimum 3.

B2 Test—required (steady, wet coil) ..................... 80 67 82 1 65 High .................. Cooling Certified 2.

B1 Test—required (steady, wet coil) ..................... 80 67 82 1 65 Low ................... Cooling Minimum 3.

C1 Test 4—optional (steady, dry coil) .................... 80 4 82 ................ Low ................... Cooling Minimum 3.

D1 Test 4—optional (cyclic, dry coil) ...................... 4 80 82 ................ Low 5.

1The 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.

4The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air

wet-bulb temperature of 57 °F or less. 5 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity

pressure as measured during the C1 Test.

3.2.4 Tests for a unit having a variablespeed compressor. a. Conduct five steadystate wet coil tests: the A2, EV, B2, B1, and

F1 Tests. Use the two optional dry-coil tests,

the steady-state G1 Test and the cyclic I1 Test,

to determine the cooling mode cyclic

degradation coefficient, CDc. If the two

optional tests are not conducted, assign CDc

the default value of 0.25. Table 6 specifies

test conditions for these seven tests.

Determine the intermediate compressor

speed cited in Table 6 using:

Intermediate speed Minimum speed Maximum speed Minimum speed

3

= + −

where a tolerance of plus 5 percent or the

next higher inverter frequency step from that

calculated is allowed.

b. For units that modulate the indoor fan

speed to adjust the sensible to total (S/T)

cooling capacity ratio, use Cooling Certified,

Cooling Intermediate, and Cooling Minimum

Air Volume Rates that represent a normal

residential installation. Additionally, if

conducting the optional dry-coil tests,

operate the unit in the same S/T capacity

control mode as used for the F1 Test.

TABLE 6.—COOLING MODE TEST CONDITIONS FOR UNITS HAVING A VARIABLE-SPEED COMPRESSOR

Test description

Air entering indoor

unit

Temperature (°F)

Air entering outdoor

unit

Temperature (°F) Compressor speed Cooling air volume rate

Dry bulb Wet bulb Dry bulb Wet bulb

A2 Test—required (steady, wet coil) .................. 80 67 95 175 Maximum Cooling Certified 2

B2 Test—required (steady, wet coil) .................. 80 67 82 165 Maximum Cooling Certified 2

EV Test—required (steady, wet coil) .................. 80 67 87 169 Intermediate Cooling Intermediate 3

B1 Test—required (steady, wet coil) .................. 80 67 82 165 Minimum Cooling Minimum 4

F1 Test—required (steady, wet coil) .................. 80 67 67 153.5 Minimum Cooling Minimum 4

G1 Test5—optional (steady, dry coil) ................. 80 (5) 67 ................ Minimum Cooling Minimum 4

I1 Test5—optional (cyclic, dry coil) ..................... 80 5 67 ................ Minimum 6

1The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in Section 3.1.4.1.

3 Defined in Section 3.1.4.3.

4 Defined in Section 3.1.4.2.

5The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air

wet bulb temperature of 57 °F or less. 6 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity

pressure as measured during the G1 Test.

3.3 Test procedures for steady-state wet

coil cooling mode tests (the A, A2, A1, B, B2,

B1, EV, and F1 Tests). a. For the pretest

interval, operate the test room reconditioning

apparatus and the unit to be tested until

maintaining equilibrium conditions for at

least 30 minutes at the specified Section 3.2

test conditions. Use the exhaust fan of the

airflow measuring apparatus and, if installed,

the indoor fan of the test unit to obtain and

then maintain the indoor air volume rate

and/or external static pressure specified for

the particular test. Continuously record (see

Definition 1.14):

(1) The dry-bulb temperature of the air

entering the indoor coil,

(2) The water vapor content of the air

entering the indoor coil,

(3) The dry-bulb temperature of the air

entering the outdoor coil, and

(4) For the Section 2.2.4 cases where its

control is required, the water vapor content

of the air entering the outdoor coil.

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6803

b. Refer to Section 3.11 for additional

requirements that depend on the selected

secondary test method. After satisfying the

pretest equilibrium requirements, make the

measurements specified in Table 5 of

ASHRAE Standard 37–88 for the Indoor Air

Enthalpy method and the user-selected

secondary method. Except for external static

pressure, make the Table 5 measurements at

equal intervals that span 10 minutes or less.

Measure external static pressure every 5

minutes or less. Continue data sampling until

you obtain a 30-minute period (e.g., four

consecutive 10-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

capacity as specified in Section 7.3.3.1 of

ASHRAE Standard 37–88. Do not adjust the

parameters used in calculating capacity for

the permitted variations in test conditions.

Evaluate air enthalpies based on the

measured barometric pressure. Assign the

average total space cooling capacity and

electrical power consumption over the 30-

minute data collection interval to the

variables Q ̇ c

k(T) and E ̇ ck(T), respectively. For

these two variables, replace the ‘‘T’’ with the

nominal outdoor temperature at which the

test was conducted. The superscript k is used

only when testing multi-capacity units. Use

the superscript k=2 to denote a test with the

unit operating at high capacity or maximum

speed, k=1 to denote low capacity or

minimum speed, and k=v to denote the

intermediate speed. For units tested without

an indoor fan installed, decrease Q ̇ c

k(T) by

 1250 Btu/h

1000 scfm

.

 V ,

and increase E by,

 365 W

1000 scfm

.

 V ,

s

c

k

s

 ̇

 ̇ ( )

 ̇

T

Where

V ̇

s

is the average measured indoor air volume

rate expressed in units of cubic feet per

minute of standard air (SCFM).

TABLE 7.—TEST OPERATING AND TEST CONDITION TOLERANCES FOR SECTION 3.3 STEADY-STATE WET COIL COOLING

MODE TESTS AND SECTION 3.4 DRY COIL COOLING MODE TESTS

Test operating tolerance (1)Test Condition Tolerance (2)

Indoor dry-bulb, °F:

Entering temperature ............................................................................................................................................ 2.0 0.5

Leaving temperature ............................................................................................................................................. 2.0

Indoor wet-bulb, °F:

Entering temperature ............................................................................................................................................ 1.0 3 0.3

Leaving temperature ............................................................................................................................................. 3 1.0

Outdoor dry-bulb, °F:

Entering temperature ............................................................................................................................................ 2.0 0.5

Leaving temperature ............................................................................................................................................. 4 2.0

Outdoor wet-bulb, °F:

Entering temperature ............................................................................................................................................ 1.0 5 0.3

Leaving temperature ............................................................................................................................................. 4 1.0

External resistance to airflow, inches of water ............................................................................................................ 0.05 6 0.02

Electrical voltage, % of rdg. ......................................................................................................................................... 2.0 1.5

Nozzle pressure drop, % of rdg. ................................................................................................................................. 2.0 ......................

1See Definition 1.40.

2See Definition 1.39.

3Only applies during wet coil tests; does not apply during steady-state, dry coil cooling mode tests.

4Only applies when using the Outdoor Air Enthalpy Method.

5Only applies during wet coil cooling mode tests where the unit rejects condensate to the outdoor coil.

6Only applies when testing non-ducted units.

d. For air conditioners and heat pumps

having a constant-air-volume-rate indoor fan,

the five additional steps listed below are

required if the average of the measured

external static pressures exceeds the

applicable Section 3.1.4 minimum (or target)

external static pressure (∆Pmin) by 0.03 inches

of water or more.

1. Measure the average power consumption

of the indoor fan motor (E ̇ fan,1 ) and record

the corresponding external static pressure

(∆P1) during or immediately following the 30-

minute interval used for determining

capacity.

2. After completing the 30-minute interval

and while maintaining the same test

conditions, adjust the exhaust fan of the

airflow measuring apparatus until the

external static pressure increases to

approximately ∆P1 + (∆P1 ¥ ∆Pmin).

3. After re-establishing steady readings of

the fan motor power and external static

pressure, determine average values for the

indoor fan power (E ̇ fan,2) and the external

static pressure (∆P2) by making

measurements over a 5-minute interval.

4. Approximate the average power

consumption of the indoor fan motor at ∆Pmin

using linear extrapolation:

 ̇  ̇  ̇

( )  ̇ . ,min

, , E min ,

E E

P P fan P PE fan fan = fan

−

− − + 2 1

2 1

1 1 ∆ ∆

∆ ∆

5. Increase the total space cooling capacity,

Q ̇ c

k(T), by the quantity (E ̇fan,1 ¥ E ̇fan,min),

when expressed on a Btu/h basis. Decrease

the total electrical power, E ̇ k

c(T) , by the same

fan power difference, now expressed in

watts.

3.4 Test procedures for the optional

steady-state dry coil cooling mode tests (the

C, C1, and G1 Tests). a. Except for the

modifications noted in this section, conduct

the steady-state dry coil cooling mode tests

as specified in Section 3.3 for wet coil tests.

Prior to recording data during the steadystate dry coil test, operate the unit at least

one hour after achieving dry coil conditions.

Drain the drain pan and plug the drain

opening. Thereafter, the drain pan should

remain completely dry.

b. Denote the resulting total space cooling

capacity and electrical power derived from

6804 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

the test as Q ̇ k

ss,dry(T) and E ̇ ss,dry(T). In

preparing for the Section 3.5 cyclic test,

record the average indoor-side air volume

rate, V ̇ , specific heat Cp,a of the air,

(expressed on dry air basis), specific volume

of the air at the nozzle(s), vn , humidity ratio

at the nozzle(s),Wn , and either pressure

difference or velocity pressure for the flow

nozzle(s). For units having a variable-speed

indoor fan (that provides either a constant or

variable air volume rate) that will or may be

tested during the cyclic dry coil cooling

mode test with the indoor fan turned off (see

Section 3.5), include the electrical power

used by the indoor fan motor among the

recorded parameters from the 30-minute test.

3.5 Test procedures for the optional

cyclic dry coil cooling mode tests (the D, D1,

and I1 Tests). a. After completing the steadystate dry-coil test, remove the Outdoor Air

Enthalpy method test apparatus, if

connected, and begin manual OFF/ON

cycling of the unit’s compressor. The test setup should otherwise be identical to the setup used during the steady-state dry coil test.

When testing heat pumps, leave the

switchover valve during the compressor OFF

cycles in the same position as used for the

compressor ON cycles, unless automatically

changed by the controls of the unit. For units

having a variable-speed indoor fan, the

manufacturer has the option of electing at the

outset whether to conduct the cyclic test with

the indoor fan enabled or disabled. Always

revert to testing with the indoor fan disabled

if cyclic testing with the fan enabled is

unsuccessful.

b. For units having a single-speed or twocapacity compressor, cycle the compressor

OFF for 24 minutes and then ON for 6

minutes (∆τcyc,dry = 0.5 hours). For units

having a variable-speed compressor, cycle

the compressor OFF for 48 minutes and then

ON for 12 minutes (∆τcyc,dry = 1.0 hours).

Repeat the OFF/ON compressor cycling

pattern until you complete the test. Allow the

controls of the unit to regulate cycling of the

outdoor fan.

c. Sections 3.5.1 and 3.5.2 specify airflow

requirements through the indoor coil of

ducted and non-ducted systems, respectively.

In all cases, use the exhaust fan of the airflow

measuring apparatus (covered under Section

2.6) along with the indoor fan of the unit, if

installed and operating, to approximate a

step response in the indoor coil airflow.

Regulate the exhaust fan to quickly obtain

and then maintain the flow nozzle(s) static

pressure difference or velocity pressure at the

same value as was measured during the

steady-state dry coil test. The pressure

difference or velocity pressure should be

within 2 percent of the value from the steadystate dry coil test within 15 seconds after

airflow initiation. For units having a variablespeed indoor fan that ramps when cycling on

and/or off, use the exhaust fan of the airflow

measuring apparatus to impose a step

response that begins at the initiation of ramp

up and ends at the termination of ramp

down.

d. For units having a variable-speed indoor

fan, conduct the cyclic dry coil test using a

pull-thru approach if any of the following

occur when testing with the fan operating:

(1) The test unit automatically cycles off,

(2) Its blower motor reverses, or

(3) The unit operates for more than 30

seconds at a external static pressure that is

0.1 inches of water or more higher than the

value measured during the prior steady-state

test.

e. For the pull-thru approach, disable the

indoor fan and use the exhaust fan of the

airflow measuring apparatus to generate the

specified flow nozzle(s) static pressure

difference or velocity pressure. If the exhaust

fan cannot deliver the required pressure

difference because of resistance created by

the unpowered blower, temporarily remove

the blower. After completing a minimum of

two complete compressor OFF/ON cycles,

determine the overall cooling delivered and

total electrical energy consumption during

any subsequent data collection interval

where the test tolerances given in Table 8 are

satisfied. DOE recommends obtaining

repeatable results for two or more data

collection intervals before terminating the

test. If available, use electric resistance

heaters (see Section 2.1) to minimize the

variation in the inlet air temperature. With

regard to the Table 8 parameters,

continuously record the dry-bulb

temperature of the air entering the indoor

and outdoor coils during periods when air

flows through the respective coils. Sample

the water vapor content of the indoor coil

inlet air at least every 2 minutes during

periods when air flows through the coil.

Record external static pressure and the air

volume rate indicator (either nozzle pressure

difference or velocity pressure) at least every

minute during the interval that air flows

through the indoor coil. (These regular

measurements of the airflow rate indicator

are in addition to the required measurement

at 15 seconds after flow initiation.) Sample

the electrical voltage at least every 2 minutes

beginning 30 seconds after compressor startup. Continue until the compressor, the

outdoor fan, and the indoor fan (if it is

installed and operating) cycle off.

f. For ducted units, continuously record

the dry-bulb temperature of the air entering

(as noted above) and leaving the indoor coil.

Or if using a thermopile, continuously record

the difference between these two

temperatures during the interval that air

flows through the indoor coil. For nonducted units, make the same dry-bulb

temperature measurements beginning when

the compressor cycles on and ending when

indoor coil airflow ceases.

Integrate the electrical power over

complete cycles of length ∆τcyc,dry. For ducted

units tested with an indoor fan installed and

operating, integrate electrical power from

indoor fan OFF to indoor fan OFF. For all

other ducted units and for non-ducted units,

integrate electrical power from compressor

OFF to compressor OFF. (Some cyclic tests

will use the same data collection intervals to

determine the electrical energy and the total

space cooling. For other units, you will

terminate data collection used to determine

the electrical energy before you terminate

data collection used to determine total space

cooling.]

TABLE 8.—TEST OPERATING AND TEST CONDITION TOLERANCES FOR CYCLIC DRY COIL COOLING MODE TESTS

Test operating tolerance 1

Test condition tolerance 2

Indoor entering dry-bulb temperature 3, °F .................................................................................................................. 2.0 0.5

Indoor entering wet-bulb temperature, °F ................................................................................................................... ...................... (4)

Outdoor entering dry-bulb temperature 3, °F ............................................................................................................... 2.0 0.5

External resistance to airflow 3, inches of water ......................................................................................................... 0.05

Airflow nozzle pressure difference or velocity pressure 3, % of reading ..................................................................... 2.0 5 2.0

Electrical voltage (6), % of rdg. .................................................................................................................................... 2.0 1.5

1See Definition 1.40.

2See Definition 1.39.

3Applies during the interval that air flows through the indoor (outdoor) coil except for the first 30 seconds after flow initiation. For units having a

variable-speed indoor fan that ramps, the tolerances listed for the external resistance to airflow apply from 30 seconds after achieving full speed

until ramp down begins. 4Shall at no time exceed a wet-bulb temperature that results in condensate forming on the indoor coil.

5The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state dry coil test. 6Applies during the interval when at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor fan—are operating except for the first 30 seconds after compressor start-up.

g. If the Table 8 tolerances are satisfied

over the complete cycle, record the measured

electrical energy consumption as ecyc,dry and

express it in units of watt-hours. Calculate

the total space cooling delivered, qcyc,dry, in

units of Btu using,

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6805

qcyc,

 ̇

)

 ̇

(. ) dry

p,a

n n

p,a

n

. V . C .

v . (1+ W

. V . C .

v = [ ] ′ = − 60 60

35 1

Γ Γ

where V ̇ , Cp,a, vn′ (or vn), and Wn are the

values recorded during the Section 3.4 dry

coil steady-state test and,

Γ= − [ ] ∫ TT F a a 1 2

1

2

() () . τ ττ

τ

τ

 d , hr . o

Ta1(τ) = dry bulb temperature of the air

entering the indoor coil at time τ, °F.

Ta2(τ) = dry bulb temperature of the air

leaving the indoor coil at time τ, °F.

τ1 = for ducted units, the elapsed time when

airflow is initiated through the indoor coil;

for non-ducted units, the elapsed time

when the compressor is cycled on, hr.

τ2 = the elapsed time when indoor coil

airflow ceases, hr.

3.5.1 Procedures when testing ducted

systems. The automatic controls that are

normally installed with the test unit must

govern the OFF/ON cycling of the air moving

equipment on the indoor side (exhaust fan of

the airflow measuring apparatus and, if

installed, the indoor fan of the test unit). For

example, for ducted units tested without an

indoor fan installed but rated based on using

a fan time delay relay, control the indoor coil

airflow according to the rated ON and/or OFF

delays provided by the relay. For ducted

units having a variable-speed indoor fan that

has been disabled (and possibly removed),

start and stop the indoor airflow at the same

instances as if the fan were enabled. For all

other ducted units tested without an indoor

fan installed, cycle the indoor coil airflow in

unison with the cycling of the compressor.

Close air dampers on the inlet (Section 2.5.1)

and outlet side (Sections 2.5 and 2.5.4)

during the OFF period. Airflow through the

indoor coil should stop within 3 seconds

after the automatic controls of the test unit

(act to) de-energize the indoor fan. For

ducted units tested without an indoor fan

installed (excluding the special case where a

variable-speed fan is temporarily removed),

increase ecyc,dry by the quantity,

365 W

1000 scfm

. V . (3.5- 2)

and decrease q by,

1250 Btu/h

1000 scfm

. V .

s 2

cyc,dry

s 2

 ̇ ,

 ̇ . (. )

τ τ

τ τ

[ ] −

[ ] − −

1

1 35 3

where

V ̇

s

is the average indoor air volume rate from the

Section 3.4 dry coil steady-state test and is

expressed in units of cubic feet per minute

of standard air (SCFM). For units having a

variable-speed indoor fan that is disabled

during the cyclic test, increase ecyc,dryand

decrease qcyc/dry based on:

a. The product of [τ2 ¥ τ1] and the indoor

fan power measured during or following the

dry coil steady-state test or,

b. The following algorithm if the indoor fan

ramps its speed when cycling.

1. Measure the electrical power consumed

by the variable-speed indoor fan at a

minimum of three operating conditions: at

the speed/air volume rate/external static

pressure that was measured during the

steady-state test, at operating conditions

associated with the midpoint of the ramp-up

interval, and at conditions associated with

the midpoint of the ramp-down interval. For

these measurements, the tolerances on the

airflow volume or the external static pressure

are the same as required for the Section 3.4

steady-state test.

2. For each case, determine the fan power

from measurements made over a minimum of

5 minutes.

3. Approximate the electrical energy

consumption of the indoor fan if it had

operated during the cyclic test using all three

power measurements. Assume a linear

profile during the ramp intervals. The

manufacturer must provide the durations of

the ramp-up and ramp-down intervals. If a

manufacturer-supplied ramp interval exceeds

45 seconds, use a 45-second ramp interval

nonetheless when estimating the fan energy.

The manufacturer is allowed to choose

option a, and forego the extra testing burden

of option b, even if the unit ramps indoor fan

speed when cycling.

3.5.2 Procedures when testing non-ducted

systems. Do not use air dampers when

conducting cyclic tests on non-ducted units.

Until the last OFF/ON compressor cycle,

airflow through the indoor coil must cycle off

and on in unison with the compressor. For

the last OFF/ON compressor cycle—the one

used to determine ecyc,dry and qcyc,dry—use the

exhaust fan of the airflow measuring

apparatus and the indoor fan of the test unit

to have indoor airflow start 3 minutes prior

to compressor cut-on and end three minutes

after compressor cutoff. Subtract the

electrical energy used by the indoor fan

during the 3 minutes prior to compressor cuton from the integrated electrical energy,

ecyc,dry. Add the electrical energy used by the

indoor fan during the 3 minutes after

compressor cutoff to the integrated cooling

capacity, qcyc,dry. For the case where the nonducted unit uses a variable-speed indoor fan

which is disabled during the cyclic test,

correct ecyc,dry and qcyc,dry using the same

approach as prescribed in Section 3.5.1 for

ducted units having a disabled variablespeed indoor fan.

3.5.3 Cooling mode cyclic degradation

coefficient calculation. Use two optional drycoil tests to determine the cooling mode

cyclic degradation coefficient, Cc

D. If the two

optional tests are not conducted, assign Cc

D

the default value of 0.25. Evaluate Cc

D using

the above results and those from the Section

3.4 dry coil steady-state test.0

C

EER

EER

CLF D

c =

−

−

1

1

cyc, dry

ss, dry

where,

EER q

e cyc

cyc dry

cyc dry

,

,

,

, dry =

the average energy efficiency ratio during the

cyclic dry coil cooling mode test, Btu/W·h

EERss, dry

 dry

 dry

=

 ̇

 ̇ , ,

,

Q

E

ss

ss

the average energy efficiency ratio during the

steady-state dry coil cooling mode test, Btu/

W·h

CLF . 

 dry

 cyc cyc, dry

= q

Q

cyc

ss

,

,  ̇ , ∆τ

the cooling load factor, dimensionless.

Round the calculated value for Cc

D to the

nearest 0.01. If Cc

D is negative, then set it

equal to zero.

3.6 Heating mode tests for different types

of heat pumps, including heating-only heat

pumps.

6806 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

3.6.1 Tests for a heat pump having a

single-speed compressor that is tested with a

fixed speed indoor fan installed, with a

constant-air-volume-rate indoor fan installed,

or with no indoor fan installed. Conduct

three tests: the High Temperature (H1) Test,

the Frost Accumulation (H2) Test, and the

Low Temperature (H3) Test. Conduct the

optional High Temperature Cyclic (H1C) Test

to determine the heating mode cyclic

degradation coefficient, CDh . If this optional

test is not conducted, assign CDh the default

value of 0.25. Test conditions for these four

tests are specified in Table 9.

TABLE 9.—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A FIXED-SPEED

INDOOR FAN, A CONSTANT AIR VOLUME RATE INDOOR FAN, OR NO INDOOR FAN

Test description

Air entering indoor unit

Temperature (°F)

Air entering outdoor unit

Temperature (°F) Heating air volume rate

Dry bulb Wet bulb Dry bulb Wet bulb

H1 Test (required, steady) .................................... 70 60 (max) 47 43 Heating certified 1

H1C Test (optional, cyclic) ................................... 70 60 (max) 47 43 2

H2 Test (required) ................................................ 70 60 (max) 35 33 Heating certified 1

H3 Test (required, steady) .................................... 70 60 (max) 17 15 Heating certified 1

1 Defined in Section 3.1.4.4.

2 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity

pressure as measured during the H1 Test.

3.6.1.1 Non-defrost heat pump. For nondefrost heat pumps (see Definition 1.30) that

cease compressor operation at outdoor drybulb temperatures less than 37 °F, do not

conduct the H2 and H3 Tests. Instead,

conduct a Maximum Temperature (H0) Test

using the Table 9 Heating Certified Air

Volume Rate and the indoor and outdoor coil

air inlet conditions specified for the H01 Test

in Table 11.

3.6.1.2 Heat pump having a heat comfort

controller. Test any heat pump that has a

heat comfort controller (see Definition 1.26)

according to Section 3.6.1 and Table 9 with

the heat comfort controller disabled.

Additionally, conduct the abbreviated test

described in Section 3.1.9 with the heat

comfort controller active to determine the

system’s maximum supply air temperature.

3.6.2 Tests for a heat pump having a

single-speed compressor and a variablespeed, variable-air-volume-rate indoor fan:

capacity modulation correlates with outdoor

dry bulb temperature. Conduct five tests: two

High Temperature Tests (H12 and H11), one

Frost Accumulation Test (H22), and two Low

Temperature Tests (H32 and H31).

Conducting one Frost Accumulation Test

(H21), is optional. Conduct the optional High

Temperature Cyclic (H1C1) Test to determine

the heating mode cyclic degradation

coefficient, CDh If this optional test is not

conducted, assign CDh the default value of

0.25. Table 10 specifies test conditions for

these seven tests. If you do not conduct the

optional H21 Test, use the following

equations to approximate the capacity and

electrical power of the heat pump at the H21

test conditions:

 ̇  ̇ () .  ̇ ( )  ̇

 ̇  ̇ .  ̇  ̇

Q QR Q Q Q

E PR E E E

h

k

h

k

h

k

h

k

h

k

h

k

h

k

h

k

h

k

h

k

= = = ==

= = = ==

( ) = ( ) ⋅ +⋅ − { } [ ] ( )

( ) = ( ) ⋅ { } ( ) + ⋅[ ] ( ) − ( )

1 2 1 11

1 2 1 11

35 35 17 0 6 47 17

35 35 17 0 6 47 17

where,

QR Q

Q QQ

PR E

E EE

h

k h

k

h

k

h

k

h

k

h

k h

k

h

k

h

k

h

k

= =

= ==

= =

= ==

( ) = ( )

( ) + ⋅[ ] ( ) − ( )

( ) = ( )

( ) + ⋅[ ] ( ) − ( )

2

2

2 22

2

2

2 22

35 35

17 0 6 47 17

35 35

17 0 6 47 17

 ̇

 ̇ .  ̇  ̇

 ̇

 ̇ .  ̇  ̇

The quantities Q ̇ h

k=2(47), E ̇ hk=2(47), Q ̇ hk=1(47),

and E ̇ h

k=1(47) are determined from the H12

and H11 Tests and evaluated as specified in

Section 3.7; the quantities Q ̇ h

k=2(35) and

E ̇ h

k=2(35) are determined from the H22 Test

and evaluated as specified in Section 3.9; and

the quantities Q ̇ h

k=2(17), E ̇ hk=2(17), Q ̇ hk=1(17),

and E ̇ h

k=1(17) are determined from the H32

and H31 Tests and evaluated as specified in

Section 3.10.

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6807

TABLE 10.—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A SINGLE-SPEED COMPRESSOR AND A VARIABLE AIR

VOLUME RATE INDOOR FAN

Test description

Air entering indoor unit

Temperature (°F)

Air entering outdoor unit

Temperature (°F) Heating air volume rate

Dry bulb Wet bulb Dry bulb Wet bulb

H12 Test (required, steady) .................................. 70 60 (max) 47 43 Heating certified 1

H11 Test (required, steady) .................................. 70 60 (max) 47 43 Heating minimum 2

H1C1 Test (optional, cyclic) .................................. 70 60 (max) 47 43 3

H22 Test (required) ............................................... 70 60 (max) 35 33 Heating certified 1

H21 Test (optional) ................................................ 70 60 (max) 35 33 Heating minimum 2

H32 Test (required, steady) .................................. 70 60 (max) 17 15 Heating certified 1

H31 Test (required, steady) .................................. 70 60 (max) 17 15 Heating minimum 2

1 Defined in Section 3.1.4.4.

2 Defined in Section 3.1.4.5.

3 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity

pressure as measured during the H11 Test.

3.6.3 Tests for a heat pump having a twocapacity compressor (see Definition 1.44).

a. Conduct one Maximum Temperature

Test (H01), two High Temperature Tests (H12

and H11), one Frost Accumulation Test (H22),

and one Low Temperature Test (H32).

Conduct an additional Frost Accumulation

Test (H2)1 and Low Temperature Test (H31)

if both of the following conditions exist:

1. You need to know the heat pump’s

capacity and electrical power at low

compressor capacity for outdoor

temperatures of 37 °F and less to complete

the Section 4.2.3 seasonal performance

calculations, and

2. The heat pump’s controls allow low

capacity operation at outdoor temperatures of

37 °F and less.

b. Conduct the optional Maximum

Temperature Cyclic Test (H0C1) to determine

the heating mode cyclic degradation

coefficient, CDh. If this optional test is not

conducted, assign CDh the default value of

0.25. Table 11 specifies test conditions for

these eight tests.

TABLE 11.—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR

Test description

Air entering indoor unit

Temperature (°F)

Air entering outdoor unit

Temperature (°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

H0C1 Test (optional, cyclic) ............. 70 60(max) 62 56.5 Low .................... 2

H12 Test (required, steady) ............. 70 60(max) 47 43 High ................... Heating certified 3

H11 Test (required, steady) ............. 70 60(max) 47 43 Low .................... Heating minimum 2

H22 Test (required) .......................... 70 60(max) 35 33 High ................... Heating certified 3

H21 Test 4 (required) ....................... 70 60(max) 35 33 High ................... Heating minimum 1

H32 Test (required, steady) ............. 70 60(max) 17 15 High ................... Heating certified 3

H31 Test4 (required, steady) ........... 70 60(max) 17 15 Low .................... Heating minimum 1

1 Defined in Section 3.1.4.5.

2 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity

pressure as measured during the H01 Test. 3 Defined in Section 3.1.4.4.

4 Required only if the heat pump’s performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is needed to complete the Section 4.2.3 HSPF calculations.

3.6.4 Tests for a heat pump having a

variable-speed compressor. Conduct one

Maximum Temperature Test (H01), two High

Temperature Tests (H12 and H11), one Frost

Accumulation Test (H2V), and one Low

Temperature Test (H32). Conducting one or

both of the following tests is optional: an

additional High Temperature Test (H1N) and

an additional Frost Accumulation Test (H22).

Conduct the optional Maximum Temperature

Cyclic (H0C1) Test to determine the heating

mode cyclic degradation coefficient, CDh. If

this optional test is not conducted, assign CDh

the default value of 0.25. Table 12 specifies

test conditions for these eight tests.

Determine the intermediate compressor

speed cited in Table 12 using the heating

mode maximum and minimum compressors

speeds and:

Intermediate speed eed

eed

=

+ −

Minimum sp

Maximum sp Minimum speed

3

where a tolerance of plus 5 percent or the

next higher inverter frequency step from that

calculated is allowed. If you do not conduct

the H22 Test, use the following equations to

approximate the capacity and electrical

power at the H22 test conditions:

 ̇ () .  ̇ () .  ̇ ( )  ̇ ( )

 ̇ () .  ̇ () .  ̇ ( )  ̇ ( ).

Q Q

E E

h

k

h

k

h

k

h

k

= =

= =

= +− { } [ ]

= +− { } [ ]

2 2

2 2

35 0 90 17 0 6 47 17

35 0 985 17 0 6 47 17

. Q . Q

. E . E

h

k=2

h

k=2

h

k=2

h

k=2

6808 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

Determine the quantities Q ̇ h

k=2(47) and

E ̇ h

k=2(47) from the H12 Test and evaluate

them according to Section 3.7. Determine the

quantities Q ̇ h

k=2(17) and E ̇ hk=2(17) from the

H32 Test and evaluate them according to

Section 3.10. For heat pumps where the

heating mode maximum compressor speed

exceeds its cooling mode maximum

compressor speed, conduct the H1N Test if

the manufacturer requests it. If you conduct

the H1N Test, 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 to see how the results

of the H1N Test may be used in calculating

the heating seasonal performance factor.

TABLE 12.—HEATING MODE TEST CONDITIONS FOR UNITS HAVING A VARIABLE-SPEED COMPRESSOR

Test description

Air entering indoor unit

Temperature (°F)

Air entering outdoor unit

Temperature (°F) Compressor

speed

Heating air volume rate

Dry bulb Wet bulb Dry bulb Wet bulb

H01 Test (required, steady) ............. 70 60(max) 62 56.5 Minimum ............ Heating minimum 1

H0C1 Test (optional, cyclic) ............. 70 60(max) 62 56.5 Minimum ............ 2

H12 Test (required, steady) ............. 70 60(max) 47 43 Maximum ........... Heating certified 3

H11 Test (required, steady) ............. 70 60(max) 47 43 Minimum ............ Heating minimum 2

H1N Test (optional, steady) ............. 70 60(max) 47 43 Cooling Mode

Maximum.

Heating nominal 4

H22 Test (optional) .......................... 70 60(max) 35 33 Maximum ........... Heating certified 3

H2V Test (required) ......................... 70 60(max) 35 33 Intermediate ....... Heating intermediate 5

H32 Test (required, steady) ............. 70 60(max) 17 15 Maximum ........... Heating certified 3

1 Defined in Section 3.1.4.5.

2 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity

pressure as measured during the H01 Test. 3 Defined in Section 3.1.4.4.

4 Defined in Section 3.1.4.7.

5 Defined in Section 3.1.4.6.

3.7 Test procedures for steady-state

Maximum Temperature and High

Temperature heating mode tests (the H0,

H01, H1, H12, H11, and H1N Tests). a. For the

pretest interval, operate the test room

reconditioning apparatus and the heat pump

until equilibrium conditions are maintained

for at least 30 minutes at the specified

Section 3.6 test conditions. Use the exhaust

fan of the airflow measuring apparatus and,

if installed, the indoor fan of the heat pump

to obtain and then maintain the indoor air

volume rate and/or the external static

pressure specified for the particular test.

Continuously record the dry-bulb

temperature of the air entering the indoor

coil, and the dry-bulb temperature and water

vapor content of the air entering the outdoor

coil. Refer to Section 3.11 for additional

requirements that depend on the selected

secondary test method. After satisfying the

pretest equilibrium requirements, make the

measurements specified in Table 5 of

ASHRAE Standard 37–88 for the Indoor Air

Enthalpy method and the user-selected

secondary method. Except for external static

pressure, make the Table 5 measurements at

equal intervals that span 10 minutes or less.

Measure external static pressure every 5

minutes or less. Continue data sampling until

you obtain a 30-minute period (e.g., four

consecutive 10-minute samples) where the

test tolerances specified in Table 13 are

satisfied. For those continuously recorded

parameters, use the entire data set for the 30-

minute interval when evaluating Table 13

compliance. Determine the average electrical

power consumption of the heat pump over

the same 30-minute interval.

TABLE 13.—TEST OPERATING AND TEST CONDITION TOLERANCES FOR SECTION 3.7 AND SECTION 3.10 STEADY-STATE

HEATING MODE TESTS.

Test operating tolerance (1)Test condition tolerance (2)

Indoor dry-bulb, °F:

Entering temperature ............................................................................................................................ 2.0 0.5

Leaving temperature ............................................................................................................................. 2.0 ..............................

Indoor wet-bulb, °F:

Entering temperature ............................................................................................................................ 1.0 ..............................

Leaving temperature ............................................................................................................................. 1.0 ..............................

Outdoor dry-bulb, °F:

Entering temperature ............................................................................................................................ 2.0 0.5

Leaving temperature ............................................................................................................................. (3) 2.0 ..............................

Outdoor wet-bulb, °F:

Entering temperature ............................................................................................................................ 1.0 0.3

Leaving temperature ............................................................................................................................. (3) 1.0 ..............................

External resistance to airflow, inches of water ............................................................................................ 0.05 (4) 0.02

Electrical voltage, % of rdg .......................................................................................................................... 2.0 1.5

Nozzle pressure drop, % of rdg .................................................................................................................. 2.0 ..............................

1See Definition 1.40.

2See Definition 1.39.

3Only applies when the Outdoor Air Enthalpy Method is used.

4Only applies when testing non-ducted units.

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6809

Calculate indoor-side total heating capacity

as specified in Section 7.3.4.1 of ASHRAE

Standard 37–88. Do not adjust the parameters

used in calculating capacity for the permitted

variations in test conditions. Assign the

average space heating capacity and electrical

power over the 30-minute data collection

interval to the variables and Q ̇ h

k(T) and

E ̇ h

k(T), respectively. The ‘‘T’’ and

superscripted ‘‘k’’ are the same as described

in Section 3.3. Additionally, for the heating

mode, use the superscript k=N to denote

results from the optional H1N Test, if

conducted.

b. For heat pumps tested without an indoor

fan installed, increase Q ̇ h

k(T) by

 1250 Btu/h

1000 scfm

.

 V ,

and increase E by,

 365 W

1000 scfm

.

 V ,

s

h

k

s

 ̇

 ̇ ( )

 ̇

T

where

V ̇

s

is the average measured indoor air volume

rate expressed in units of cubic feet per

minute of standard air (SCFM). During the

30-minute data collection interval of a High

Temperature Test, pay attention to

preventing a defrost cycle. Prior to this time,

allow the heat pump to perform a defrost

cycle if automatically initiated by its own

controls. As in all cases, wait for the heat

pump’s defrost controls to automatically

terminate the defrost cycle. Heat pumps that

undergo a defrost should operate in the

heating mode for at least 10 minutes after

defrost termination prior to beginning the 30-

minute data collection interval. For some

heat pumps, frost may accumulate on the

outdoor coil during a High Temperature test.

If the indoor coil leaving air temperature or

the difference between the leaving and

entering air temperatures decreases by more

than 1.5 °F over the 30-minute data

collection interval, then do not use the

collected data to determine capacity. Instead,

initiate a defrost cycle. Begin collecting data

no sooner than 10 minutes after defrost

termination. Collect 30 minutes of new data

during which the Table 13 test tolerances are

satisfied. In this case, use only the results

from the second 30-minute data collection

interval to evaluate Q ̇ h

k(47) and E ̇ hk(47).

If conducting the optional cyclic heating

mode test, which is described in Section 3.8,

record the average indoor-side air volume

rate,

V,  ̇

specific heat of the air Cp,a (expressed on dry

air basis), specific volume of the air at the

nozzle(s), vn (or vn), humidity ratio at the

nozzle(s), Wn, and either pressure difference

or velocity pressure for the flow nozzle(s). If

either or both of the below criteria apply,

determine the average, steady-state, electrical

power consumption of the indoor fan motor

(E ̇ fan,1).

a. the Section 3.8 cyclic test will be

conducted and the heat pump has a variablespeed indoor fan that is expected to be

disabled during the cyclic test, or

b. the heat pump has a (variable-speed)

constant-air volume-rate indoor fan and

during the steady-state test the average

external static pressure (∆P1) exceeds the

applicable Section 3.1.4.4 minimum (or

targeted) external static pressure (∆Pmin) by

0.03 inches of water or more. Determine E ̇ fan,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

‘‘b’’ criteria applies, conduct the following

four steps after determining E ̇ fan,1 (which

corresponds to ∆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 ∆P1 + (∆P1 ¥ ∆Pmin).

2. After re-establishing steady readings for

fan motor power and external static pressure,

determine average values for the indoor fan

power (E ̇ fan,2) and the external static pressure

(∆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 ∆Pmin

using linear extrapolation:

 ̇  ̇  ̇

( )  ̇ . ,min

, , E min ,

E E

P P fan P PE fan fan = fan

−

− − + 2 1

2 1

1 1 ∆ ∆

∆ ∆

4. Decrease the total space heating

capacity, Q ̇ h

k(T), by the quantity (E ̇)fan,1 ¥

E ̇fan,min, when expressed on a Btu/h basis.

Decrease the total electrical power, E ̇)h

k (T),

by the same fan power difference, now

expressed in watts.

3.8 Test procedures for the optional cyclic

heating mode tests (the H0C1, H1C, and H1C1

Tests). a. Except as noted below, conduct the

cyclic heating mode test as specified in

Section 3.5. As adapted to the heating mode,

replace Section 3.5 references to ‘‘the steadystate dry coil test’’ with ‘‘the heating mode

steady-state test conducted at the same test

conditions as the cyclic heating mode test.’’

Use the test tolerances in Table 14 rather

than Table 8. Record the outdoor coil

entering wet-bulb temperature according to

the requirements given in Section 3.5 for the

outdoor coil entering dry-bulb temperature.

Drop the subscript ‘‘dry’’ used in variables

cited in Section 3.5 when referring to

quantities from the cyclic heating mode test.

Determine the total space heating delivered

during the cyclic heating test, qcyc, as

specified in Section 3.5 except for making the

following changes.

(1) When evaluating Equation 3.5–1, use

the values of,

V,  ̇

Cp,avb (or vn), and Wn that were recorded

during the Section 3.7 steady-state test

conducted at the same test conditions.

(2) Calculate γ using,

Γ= − [ ] ∫ TT F a a 1 2

1

2

() () . τ τ δτ

τ

τ

 , hr . o

b. For ducted heat pumps tested without

an indoor fan installed (excluding the special

case where a variable-speed fan is

temporarily removed), increase qcyc by the

amount calculated using Equation 3.5–3.

Additionally, increase ecyc by the amount

calculated using Equation 3.5–2. In making

these calculations, use the average indoor air

volume rate

(  ̇V )s

determined from the Section 3.7 steady-state

heating mode test conducted at the same test

conditions.

c. For non-ducted heat pumps, subtract the

electrical energy used by the indoor fan

during the 3 minutes after compressor cutoff

from the non-ducted heat pump’s integrated

heating capacity, qcyc.

d. For single-speed heat pumps that

defrosted before completing the Section 3.7

H1 (or H11) steady-state test, DOE

recommends initiating a defrost cycle before

cycling the heat pump OFF and ON

according to Section 3.5. Do not restrict air

movement through the indoor coil if the heat

pump cycles off its indoor fan during the

defrost cycle. If conducting a defrost cycle,

operate the single-speed heat pump for at

least 10 minutes after defrost termination.

After that, begin cycling the heat pump

immediately or delay until you have reestablished the specified test conditions. Pay

attention to preventing defrosts after

beginning the cycling process. However, if a

defrost is automatically or manually initiated

once the OFF/ON cycling begins, switch to

operating the heat pump continuously until

10 minutes after defrost termination. After

that, resume the OFF/ON cycling while

conducting a minimum of two complete

compressor OFF/ON cycles before

determining qcyc and ecyc.

3.8.1 Heating mode cyclic degradation

coefficient calculation. Use the results from

the optional cyclic test and the required

steady-state test that was conducted at the

same test conditions to determine the heating

mode cyclic degradation coefficient, CDh. If

the optional test is not conducted, assign CDh

the default value of 0.25.

6810 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

C

COP

COP T

HLF D

h

cyc

ss cyc =

−

−

1

1

( )

where,

COP q

Btu

W h

cyc

cyc =

⋅ 3.413

, . ecyc

the average coefficient of performance during

the cyclic heating mode test, dimensionless.

COP T Q T

Btu h

W

T

ss cyc

h

k

cyc

cyc

( )

 ̇ ( )

.413 /  ̇ ( )

= ,

3 . Eh

k

the average coefficient of performance during

the steady-state heating mode test conducted

at the same test conditions i.e., same outdoor

dry bulb temperature, Tcyc, and speed/

capacity, k, if applicable—as specified for the

cyclic heating mode test, dimensionless.

HLF . = the q

Q T

cyc

h

k

cyc cyc  ̇ ( ) , ∆τ

the heating load factor, dimensionless.

Tcyc = the nominal outdoor temperature at

which the cyclic heating mode test is

conducted, 62 or 47 °F.

∆τcyc = the duration of the OFF/ON intervals;

0.5 hours when testing a heat pump having

a single-speed or two-capacity compressor

and 1.0 hour when testing a heat pump

having a variable-speed compressor.

Round the calculated value for Ch

D to the

nearest 0.01. If Ch

D is negative, then set it

equal to zero.

TABLE 14.—TEST OPERATING AND TEST CONDITION TOLERANCES FOR CYCLIC HEATING MODE TESTS

Test operating

tolerance 1

Test condition

tolerance 2

Indoor entering dry-bulb temperature 3, °F ...................................................................................................... 2.0 3 0.5

Indoor entering wet-bulb temperature 3, °F ..................................................................................................... 1.0 ............................

Outdoor entering dry-bulb temperature 3, °F ................................................................................................... 2.0 0.5

Outdoor entering wet-bulb temperature 3, °F .................................................................................................. 2.0 1.0

External resistance to air-flow 3, inches of water ............................................................................................ 0.05 ............................

Airflow nozzle pressure difference or velocity pressure 3, % of reading ......................................................... 2.0 2.0 4

Electrical voltage 5, % of rdg ........................................................................................................................... 2.0 1.5

1 See Definition 1.40. 2 See Definition 1.39. 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 Test procedures for Frost Accumulation

heating mode tests (the H2, H22, H2V, and

H21 Tests). a. Confirm that the defrost

controls of the heat pump are set as specified

in Section 2.2.1. Operate the test room

reconditioning apparatus and the heat pump

for at least 30 minutes at the specified

Section 3.6 test conditions before starting the

‘‘preliminary’’ test period. The preliminary

test period must immediately precede the

‘‘official’’ test period, which is the heating

and defrost interval over which data are

collected for evaluating average space heating

capacity and average electrical power

consumption.

b. For heat pumps containing defrost

controls which are likely to cause defrosts at

intervals less than one hour, the preliminary

test period starts at the termination of an

automatic defrost cycle and ends at the

termination of the next occurring automatic

defrost cycle. For heat pumps containing

defrost controls which are likely to cause

defrosts at intervals exceeding one hour, the

preliminary test period must consist of a

heating interval lasting at least one hour

followed by a defrost cycle that is either

manually or automatically initiated. In all

cases, the heat pump’s own controls must

govern when a defrost cycle terminates.

c. The official test period begins when the

preliminary test period ends, at defrost

termination. The official test period ends at

the termination of the next occurring

automatic defrost cycle. When testing a heat

pump that uses a time-adaptive defrost

control system (see Definition 1.41),

however, manually initiate the defrost cycle

that ends the official test period at the instant

indicated by instructions provided by the

manufacturer. If the heat pump has not

undergone a defrost after 12 hours,

immediately conclude the test and use the

results from the full 12-hour period to

calculate the average space heating capacity

and average electrical power consumption.

For heat pumps that turn the indoor fan off

during the defrost cycle, take steps to cease

forced airflow through the indoor coil and

block the outlet duct whenever the heat

pump’s controls cycle off the indoor fan. You

should use the outlet damper box described

in Section 2.5.4.1, if installed, to affect the

blocked outlet duct.

d. Defrost termination occurs when the

controls of the heat pump actuate the first

change in converting from defrost operation

to normal heating operation. Defrost

initiation occurs when the controls of the

heat pump first alter its normal heating

operation in order to eliminate possible

accumulations of frost on the outdoor coil.

e. To constitute a valid Frost Accumulation

test, you must satisfy the test tolerances

specified in Table 15 during both the

preliminary and official test periods. As

noted in Table 15, test operating tolerances

are specified for two sub-intervals: When

heating, except for the first 10 minutes after

the termination of a defrost cycle (Subinterval H) and when defrosting, plus these

same first 10 minutes after defrost

termination (Sub-interval D). Evaluate

compliance with Table 15 test condition

tolerances and the majority of the test

operating tolerances using the averages from

measurements recorded only during Subinterval H. Continuously record the dry bulb

temperature of the air entering the indoor

coil, and the dry bulb temperature and water

vapor content of the air entering the outdoor

coil. Sample the remaining parameters listed

in Table 15 at equal intervals that span 10

minutes or less.

f. For the official test period, collect and

use the following data to calculate average

space heating capacity and electrical power.

During heating and defrosting intervals when

the controls of the heat pump (act to) have

the indoor fan on, continuously record the

dry-bulb temperature of the air entering (as

noted above) and leaving the indoor coil. If

using a thermopile, continuously record the

difference between the leaving and entering

dry-bulb temperatures during the interval(s)

that air flows through the indoor coil. For

heat pumps tested without an indoor fan

installed, determine the corresponding

cumulative time (in hours) of indoor coil

airflow, ∆τa. Sample measurements used in

calculating the air volume rate (refer to

Sections 7.8.3.1 and 7.8.3.2 of ASHRAE

Standard 37–88) at equal intervals that span

10 minutes or less. Record the electrical

energy consumed, expressed in watt-hours,

from defrost termination to defrost

termination, ek

DEF(35), as well as the

corresponding elapsed time in hours, ∆τFR.

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6811

TABLE 15.—TEST OPERATING AND TEST CONDITION TOLERANCES FOR FROST ACCUMULATION HEATING MODE TESTS

Test Operating Tolerance 1 Test Condition Tolerance 2 Subinterval H 3

Sub-interval

H 3

Sub-interval

D 4

Indoor entering dry-bulb temperature, °F ................................................................................................ 2.0 5 4.0 0.5

Indoor entering wet-bulb temperature, °F ............................................................................................... 1.0 .................... ....................

Outdoor entering dry-bulb temperature, °F ............................................................................................. 2.0 10.0 1.0

Outdoor entering wet-bulb temperature, °F ............................................................................................. 1.5 .................... 0.5

External resistance to airflow, inches of water ........................................................................................ 0.05 .................... 6 0.02

Electrical voltage, % of rdg ...................................................................................................................... 2.0 .................... 1.5

1See Definition 1.40.

2See Definition 1.39.

3Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a defrost cycle.

4Applies during a defrost cycle and during the first 10 minutes after the termination of a defrost cycle when the heat pump is operating in the

heating mode. 5For heat pumps that turn off the indoor fan during the defrost cycle, the noted tolerance only applies during the 10 minute interval that follows

defrost termination. 6Only applies when testing non-ducted heat pumps.

3.9.1 Average space heating capacity and

electrical power calculations. Evaluate

average space heating capacity, Q ̇ h

k(35), when

expressed in units of Btu per hour, using:

 ̇  ̇  ̇ , , Q

V C

v W

V C

v

h

k p a

FR n n

p a

FR n

35

60

1

60 ( ) = ⋅⋅ ⋅

[ ] ′ ⋅ + ( ) = ⋅⋅ ⋅

⋅

Γ

∆τ

Γ

∆τ

where,

V ̇ =

the average indoor air volume rate measured

during Sub-interval H, cfm.

Cp,a = 0.24 + 0.444 · Wn, the constant pressure

specific heat of the air-water vapor mixture

that flows through the indoor coil and is

expressed on a dry air basis, Btu / lbmda · °F.

Vn = specific volume of the air-water vapor

mixture at the nozzle, ft3 / lbmmx.

Wn = humidity ratio of the air-water vapor

mixture at the nozzle, lbm of water vapor per

lbm of dry air.

∆τFR = τ2 ¥ τ1, the elapsed time from defrost

termination to defrost termination, hr.

Γ = hr

1τ

τ

τ ττ

2

∫ 2 1 [ ] T Td F ( ) − ( ) ⋅ a a , . o

Tal(τ)= dry bulb temperature of the air

entering the indoor coil at elapsed time τ ,

°F; only recorded when indoor coil airflow

occurs; assigned the value of zero during

periods (if any) where the indoor fan cycles

off.

Ta2(τ)= dry bulb temperature of the air

leaving the indoor coil at elapsed time τ, °F;

only recorded when indoor coil airflow

occurs; assigned the value of zero during

periods (if any) where the indoor fan cycles

off.

τ1 = the elapsed time when the defrost

termination occurs that begins the official

test period, hr.

τ2 = the elapsed time when the next

automatically occurring defrost termination

occurs, thus ending the official test period, hr

Vn = specific volume of the dry air portion

of the mixture evaluated at the dry-bulb

temperature, vapor content, and barometric

pressure existing at the nozzle, ft 3 per lbm

of dry air.

Evaluate average electrical power, E ̇ k

h(35),

when expressed in units of watts, using:

E k

h

edef

FR

⋅

( ) = ⋅ ( ) 35 35

∆τ

For heat pumps tested without an indoor

fan installed, increase Q ̇ k

h(35) by,

1250

1000

 Btu/  ̇ , h

scfm

Vs a

FR

⋅ ⋅ ∆τ

∆τ

and increase E ̇ k

h(35) by,

365

1000

W

scfm

Vs a

FR

⋅ ⋅  ̇ , ∆τ

∆τ

where V ̇ s is the average indoor air volume

rate measured during the Frost Accumulation

heating mode test and is expressed in units

of cubic feet per minute of standard air

(SCFM). For heat pumps having a constantair-volume-rate indoor fan, the five

additional steps listed below are required if

the average of the measured external static

pressures exceeds the Section 3.1.4.4

minimum (or targeted) external static

pressure (∆Pmin) by 0.03 inches of water or

more.

1. Measure the average power consumption

of the indoor fan motor (E ̇ fan, 1) and record the

corresponding external static pressure (∆P1)

during or immediately following the 30-

minute interval used for determining

capacity.

2. After the 30-minute interval is

completed and while maintaining the same

test conditions, adjust the exhaust fan of the

airflow measuring apparatus until the

external static pressure increases to

approximately ∆P1 + (∆P1 ¥ ∆Pmin).

3. After re-establishing steady readings for

the fan motor power and external static

pressure, determine average values for the

indoor fan power (E ̇ fan, 2) and the external

static pressure (∆P2) by making

measurements over a 5-minute interval.

4. Approximate the average power

consumption of the indoor fan motor had the

30-minute tests been conducted at ∆Pmin

using linear extrapolation:

 ̇  ̇  ̇

( )  ̇ . ,min

, , E min ,

E E

P P fan P PE fan fan = fan

−

− − + 2 1

2 1

1 1 ∆ ∆

∆ ∆

5. Increase the total heating capacity,

Q ̇ h

k(35), by the quantity [(E ̇ fan,1 – E ̇ fan,min) ·

(∆τa / ∆τa FR)], when expressed on a Btu/h

basis. Decrease the total electrical power,

E ̇ k

h(35), by the same quantity, now expressed

in watts.

3.9.2 Demand defrost credit. Assign the

demand defrost credit, Fdef, that is used in

Section 4.2 to the value of 1 in all cases

6812 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

except for heat pumps having a demanddefrost control system (Definition 1.20). For

such qualifying heat pumps, evaluate Fdef

using,

Fdef =+ − −

−





 



1 0 03 1  1 5

1 5 . .

. ,

max

. ∆ def

∆

τ

τ

where,

∆τdef = the time between defrost terminations

(in hours) or 1.5, whichever is greater.

∆τmax = maximum time between defrosts as

allowed by the controls (in hours) or 12,

whichever is less.

For two-capacity heat pumps and for

Section 3.6.2 units, evaluate the above

equation using the ∆τdef that applies based on

the Frost Accumulation Test conducted at

high capacity and/or at the Heating Certified

Air Volume Rate. For variable-speed heat

pumps, evaluate ∆τdef based on the required

Frost Accumulation Test conducted at the

intermediate compressor speed.

3.10 Test procedures for steady-state Low

Temperature heating mode tests (the H3,

H32, and H31 Tests). Except for the

modifications noted in this section, conduct

the Low Temperature heating mode test

using the same approach as specified in

Section 3.7 for the Maximum and High

Temperature tests. After satisfying the

Section 3.7 requirements for the pretest

interval but before you begin collecting data

to determine Q ̇ h

k(17) and E ̇ hk(17), conduct a

defrost cycle. This defrost cycle may be

manually or automatically initiated. The

defrost sequence must be terminated by the

action of the heat pump’s defrost controls.

Begin the 30-minute data collection interval

described in Section 3.7, from which Q ̇ h

k(17)

and E ̇ h

k(17) are determined, no sooner than

10 minutes after defrost termination. Defrosts

should be prevented over the 30-minute data

collection interval.

3.11 Additional requirements for the

secondary test methods. Prior to evaluating if

the energy balance specified in Section 3.1.1

is obtained, you should make an adjustment

to account for the energy loss within the air

duct that connects the indoor coil and the

location where the outlet dry-bulb

temperature is measured. If using the

Outdoor Air Enthalpy Method, you should

make an adjustment to account for the energy

loss within the air duct that connects the

outdoor coil and the location where the

outlet temperature is measured. In all cases,

apply the correction to the indoor space

conditioning capacity that is determined

using the secondary test method.

3.11.1 If using the Outdoor Air Enthalpy

Method as the secondary test method. During

the ‘‘official’’ test, the outdoor air-side test

apparatus described in Section 2.10.1 is

connected to the outdoor unit. To help

compensate for any effect that the addition of

this test apparatus may have on the unit’s

performance, conduct a ‘‘preliminary’’ test

where the outdoor air-side test apparatus is

disconnected. Conduct a preliminary test

prior to the first Section 3.2 steady-state

cooling mode test and prior to the first

Section 3.6 steady-state heating mode test.

No other preliminary tests are required so

long as the unit operates the outdoor fan

during all cooling mode steady-state tests at

the same speed and all heating mode steadystate tests at the same speed. If using more

than one outdoor fan speed for the cooling

mode steady-state tests, however, conduct a

preliminary test prior to each cooling mode

test where a different fan speed is first used.

This same requirement applies for the

heating mode tests.

3.11.1.1 If a preliminary test precedes the

official test. The test conditions for the

preliminary test are the same as specified for

the official test. Connect the indoor air-side

test apparatus to the indoor coil; disconnect

the outdoor air-side test apparatus. Allow the

test room reconditioning apparatus and the

unit being tested to operate for at least one

hour. After attaining equilibrium conditions,

measure the following quantities at equal

intervals that span 10 minutes or less:

1. The Section 2.10.1 evaporator and

condenser temperatures or pressures

2. Parameters required according to the

Indoor Air Enthalpy Method.

Continue these measurements until a 30-

minute period (e.g., four consecutive 10-

minute samples) is obtained where the Table

7 or Table 13, whichever applies, test

tolerances are satisfied. After collecting 30

minutes of steady-state data, reconnect the

outdoor air-side test apparatus to the unit.

Adjust the exhaust fan of the outdoor airflow

measuring apparatus until averages for the

evaporator and condenser temperatures, or

the saturated temperatures corresponding to

the measured pressures, agree within ±0.5 °F

of the averages achieved when the outdoor

air-side test apparatus was disconnected.

Calculate the averages for the reconnected

case using five or more consecutive readings

taken at one minute intervals. Make these

consecutive readings after re-establishing

equilibrium conditions and before initiating

the official test.

3.11.1.2 If a preliminary test does not

precede the official test. Connect the outdoorside test apparatus to the unit. Adjust the

exhaust fan of the outdoor airflow measuring

apparatus to achieve the same external static

pressure as measured during the prior

preliminary test conducted with the unit

operating in the same cooling or heating

mode at the same outdoor fan speed.

3.11.1.3 Official test. a. Continue

(preliminary test was conducted) or begin (no

preliminary test) the official test by making

measurements for both the Indoor and

Outdoor Air Enthalpy Methods at equal

intervals that span 10 minutes or less.

Discontinue these measurement only after

obtaining a 30-minute period where the

specified test condition and test operating

tolerances are satisfied. To constitute a valid

official test,

(1) Achieve the energy balance specified in

Section 3.1.1 and,

(2) For cases where you conduct a

preliminary test, the capacities determined

using the Indoor Air Enthalpy Method from

the official and preliminary test periods must

agree within 2.0 percent.

b. For space cooling tests, calculate

capacity from the outdoor air enthalpy

measurements as specified in Section 7.3.3.2

of ASHRAE Standard 37–88. Calculate

heating capacity based on outdoor air

enthalpy measurements as specified in

Section 7.3.4.2 of the same ASHRAE

Standard. You may adjust outdoor side

capacities according to Section 7.3.3.3 of

ASHRAE Standard 37–88 to account for line

losses when testing split systems. Do not

correct the average electrical power

measurement as described in Section 8.5.3 of

ASHRAE Standard 37–88.

3.11.2 If using the Compressor Calibration

Method as the secondary test method. a.

Conduct separate calibration tests using a

calorimeter to determine the refrigerant flow

rate. Or for cases where the superheat of the

refrigerant leaving the evaporator is less than

5 °F, use the calorimeter to measure total

capacity rather than refrigerant flow rate.

Conduct these calibration tests at the same

test conditions as specified for the tests in

this Appendix. Operate the unit for at least

one hour or until obtaining equilibrium

conditions before collecting data that will be

used in determining the average refrigerant

flow rate or total capacity. Sample the data

at equal intervals that span 10 minutes or

less. Determine average flow rate or average

capacity from data sampled over a 30-minute

period where the Table 7 (cooling) or the

Table 13 (heating) tolerances are satisfied.

Otherwise, conduct the calibration tests

according to ASHRAE Standard 23–93,

ASHRAE Standard 41.9–88, and Section 7.5

of ASHRAE Standard 37–88.

b. Calculate space cooling and space

heating capacities using the compressor

calibration method measurements as

specified in Sections 7.5.7 and 7.5.8,

respectively, of ASHRAE Standard 37–88.

3.11.3 If using the Refrigerant Enthalpy

Method as the secondary test method.

Conduct this secondary method according to

Section 7.6 of ASHRAE Standard 37–88.

Calculate space cooling and space heating

capacities using the refrigerant enthalpy

method measurements as specified in

Sections 7.6.4 and 7.6.5, respectively, of the

same ASHRAE Standard.

3.12 Rounding of space conditioning

capacities for reporting purposes. When

reporting rated capacities, round them off as

follows.

1. For capacities less than 20,000 Btu/h,

round to the nearest 100 Btu/h.

2. For capacities between 20,000 and

37,999 Btu/h, round to the nearest 200 Btu/

h.

3. For capacities between 38,000 and

64,999 Btu/h, round to the nearest 500 Btu/

h.

For the capacities used to perform the

Section 4 calculations, however, round only

to the nearest integer.

4. Calculations of Seasonal Performance

Descriptors

4.1 Seasonal Energy Efficiency Ratio

(SEER) Calculations. For equipment covered

under Sections 4.1.2, 4.1.3, and 4.1.4,

evaluate the seasonal energy efficiency ratio,

SEER

q T

e T

q T

N

e T

N

c j

j

c j

j

c j

j

c j

j

= = =

=

=

=

∑

∑

∑

∑

( )

( )

( )

( )

1

8

1

8

1

8

1

8

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6813

where,

q T

N

c j ( ) =

the ratio of the total space cooling provided

during periods of the space cooling season

when the outdoor temperature fell within the

range represented by bin temperature Tj to

the total number of hours in the cooling

season (N), Btu/h.

e T

N

c j ( ) =

the electrical energy consumed by the test

unit during periods of the space cooling

season when the outdoor temperature fell

within the range represented by bin

temperature Tj to the total number of hours

in the cooling season (N), W.

Tj = the outdoor bin temperature, °F.

Outdoor temperatures are grouped or

‘‘binned.’’ Use bins of 5 °F with the 8 cooling

season bin temperatures being 67, 72, 77, 82,

87, 92, 97, and 102 °F.

j = the bin number. For cooling season

calculations, j ranges from 1 to 8.

Additionally, for Sections 4.1.2, 4.1.3, and

4.1.4, use a building cooling load, BL(Tj).

When referenced, evaluate BL(Tj) for cooling

using,

BL T

T Q

j

j c

k

( ) ( )  ̇ ( )

. = (. ) −− ⋅

= 65

95 65

95

11

41 2

2

-

where,

Q ̇ c

k=2(95) = the space cooling capacity

determined from the A2 Test and calculated

as specified in Section 3.3, Btu/h.

1.1 = sizing factor, dimensionless.

The temperatures 95 °F and 65 °F in the

building load equation represent the selected

outdoor design temperature and the zero-load

base temperature, respectively.

4.1.1 SEER calculations for an air

conditioner or heat pump having a singlespeed compressor that was tested with a

fixed-speed indoor fan installed, a constantair-volume-rate indoor fan installed, or with

no indoor fan installed. a. Evaluate the

seasonal energy efficiency ratio, expressed in

units of Btu/watt-hour, using:

SEER PLF EER = ⋅ B (.) 0 5

where,

EER Q

E B c

c

= 

 ̇ ( )

 ̇ ( ) , 82

82

the energy efficiency ratio determined from

the B Test described in Sections 3.2.1,

3.1.4.1, and 3.3, Btu/h per watt.

PLF(0.5) = 1 ¥ 0.5 · Cc

D, the part-load

performance factor evaluated at a cooling

load factor of 0.5, dimensionless.

b. Refer to Section 3.3 regarding the

definition and calculation of Q ̇ c(82) and

E ̇ c(82). If the optional tests described in

Section 3.2.1 are not conducted, set the

cooling mode cyclic degradation coefficient,

Q ̇ Dc, to the default value specified in Section

3.5.3. If these optional tests are conducted,

set Q ̇ c

d to the lower of:

1. The value calculated as per Section 3.5.3

or

2. The Section 3.5.3 default value of 0.25.

4.1.2 SEER calculations for an air

conditioner or heat pump having a singlespeed compressor and a variable-speed

variable-air-volume-rate indoor fan.

4.1.2.1 Units covered by Section 3.2.2.1

where indoor fan capacity modulation

correlates with the outdoor dry bulb

temperature. 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 °F to 102 °F.

Calculate SEER using Equation 5.4-1.

Evaluate the quantity

q T

N

c j ( )

in Equation 4.1-1 using,

q T

N

XT T

n

N

c j

j cj

j ( ) ( )  ̇ =⋅ ⋅ Q - ( ) ( .. ) 412 1

where

X T

Q T

j

c j

( )

)/  ̇ ( )

= ;

























BL(T

 or

 1 

j

the cooling mode load factor for temperature

bin j, dimensionless.

Q ̇ c(Tj) = the space cooling capacity of the test

unit when operating at outdoor temperature,

Tj, Btu/h.

n

N

j =

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.

a. For the space cooling season, assign

n

N

j

as specified in Table 16. Use Equation 4.1–

2 to calculate the building load, BL(Tj).

Evaluate Q ̇ C(Tj) using,

 ̇ ( )  ̇ ( )

 ̇ () () QT Q T () ( Q TQT

FP FP cj c FP T FP k

j

c

k

j c

k

j

c

k ck cj c

k = + −

− ⋅ − [ ] =

= =

= =

1 =

2 1

2 1

1 4.1.2 - 2)

where,

 ̇ ( )  ̇ ( )  ̇ ( )  ̇ ( ) QTQ ( ), Q Q c T k

j c

k c

k

c

k

j

= = = =

= + −

− ⋅ − 1 1

1 1

82 95 82

95 82

82

the space cooling capacity of the test unit at outdoor temperature Tj if operated at the Cooling Minimum Air Volume Rate, Btu/

h.

6814 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

 ̇ ( )  ̇ ( )  ̇ ( )  ̇ ( ) QTQ ( ), Q Q c T k

j c

k c

k ck

j

= = = =

= + −

− ⋅ − 2 2

2 2

82 95 82

95 82

82

the space cooling capacity of the test unit at outdoor temperature Tj if operated at the Cooling Certified Air Volume Rate, Btu/

h.

b. For units where indoor fan speed is the

primary control variable, FPc

k=1denotes the

fan speed used during the required A1 and B1

Tests (see Section 3.2.2.1), FPc

k=2 denotes the

fan speed used during the required A2 and B2

Tests, and FPc(Tj) denotes the fan speed used

by the unit when the outdoor temperature

equals Tj. For units where indoor air volume

rate is the primary control variable, the three

FPc’s are similarly defined only now being

expressed in terms of air volume rates rather

than fan speeds. Refer to Sections 3.2.2.1,

3.1.4 to 3.1.4.2, and 3.3 regarding the

definitions and calculations of Q ̇ c

k=1(82),

Q ̇ c

k=1(95), Q ̇ ck=2(82), and Q ̇ ck=2(95).

Calculate

e T

N

c j ( )

in Equation 4.1 using,

e T

N

XT E T

PLF

n

N

cj j cj

j

j () ()  ̇ ( ) = ( ⋅ ⋅ 4.1.2 - 3)

where,

PLFj = 1 ¥ CDc · [1 ¥ X (Tj), the part load

factor, dimensionless.

E ̇ c(Tj) = the electrical power consumption of

the test unit when operating at outdoor

temperature Tj, W.

The quantities X(Tj) and nj/N are the same

quantities as used in Equation 4.1.2–1. If the

optional tests described in Section 3.2.2.1

and Table 4 are not conducted, set the

cooling mode cyclic degradation coefficient,

CDc, to the default value specified in Section

3.5.3. If these optional tests are conducted,

set CDc to the lower of

a. The value calculated as per Section 3.5.3

or

b. The Section 3.5.3 default value of 0.25.

Evaluate E ̇(Tj) using,

 ̇ ( )  ̇ ( )

 ̇ ( )  ̇ ( ) ET E T () (

E TE T

FP FP cj c FP T FP k

j

c

k

j c

k

j

c

k

c

k cj c

k = + −

− ⋅ − [ ] =

= =

= =

1 =

2 2

2 1

1 4.1.2 - 4)

where,

c

k

j c

k c

k

c

k

E E j

E E

T T = =

= =

= +

−

− ⋅ − 1 1

1 1

82

95 82

95 82  ̇  ̇ 82

 ̇  ̇ () ()

() ()

( ),

the electrical power consumption of the test unit at outdoor temperature Tj if operated at the Cooling Minimum Air Volume Rate,

W.

c

k

j c

k c

k

c

k

E E j

E E

T T = =

= =

= +

−

− ⋅ − 2 2

2 2

82

95 82

95 82  ̇  ̇ 82

 ̇  ̇ () ()

() ()

( ),

the electrical power consumption of the test unit at outdoor temperature Tj if operated at the Cooling Certified Air Volume Rate,

W.

The parameters FPc

k=1, FPck=2, and FPc (Tj)

are the same quantities that are used when

evaluating Equation 4.1.2–2. Refer to

Sections 3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3

regarding the definitions and calculations of

E ̇ c

k=1(82),E ̇ ck=1(95),E ̇ ck=2(82),and E ̇ ck=2(95).

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6815

TABLE 16.—DISTRIBUTION OF FRACTIONAL HOURS WITHIN COOLING

SEASON TEMPERATURE BINS

Bin number, j

Bin

temperature

range

°F

Representative

temperature for

bin °F

Fraction of

total

temperature bin

hours,

nj/N

1 ........................ 65–69 67 0.214

2 ........................ 70–74 72 0.231

3 ........................ 75–79 77 0.216

4 ........................ 80–84 82 0.161

5 ........................ 85–89 87 0.104

6 ........................ 90–94 92 0.052

TABLE 16.—DISTRIBUTION OF FRACTIONAL HOURS WITHIN COOLING

SEASON TEMPERATURE BINS—Continued

Bin number, j

Bin

temperature

range

°F

Representative

temperature for

bin °F

Fraction of

total

temperature bin

hours,

nj/N

7 ........................ 95–99 97 0.018

8 ........................ 100–

104

102 0.004

4.1.2.2 Units covered by Section 3.2.2.2

where indoor fan capacity modulation is

used to adjust the sensible to total cooling

capacity ratio. Calculate SEER as specified in

Section 4.1.1.

4.1.3 SEER calculations for an air

conditioner or heat pump having a twocapacity compressor. Calculate SEER using

Equation 4.1–1. Evaluate the space cooling

capacity, Q ̇ c

k=1(Tj), and electrical power

consumption, E ̇ c

k=1(Tj), of the test unit when

operating at low compressor capacity and

outdoor temperature Tj using,

 ̇ ( )  ̇ ( )  ̇ ( )  ̇ ( ) QTQ ( )( Q Q c T k

j c

k c

k

c

k

j

= = = =

= + −

− ⋅ − 1 1

1 1

82 95 82

95 82 82 4.1.3-1)

 ̇ ( )  ̇ ( )  ̇ ( )  ̇ ( ) ETE ( )( E E c T k

j c

k c

k ck

j

= = = =

= + −

− ⋅ − 1 1

1 1

82 95 82

95 82 82 4.1.3- 2)

where Q ̇ c

k=1(95) and E ̇ ck=1(95) are determined

from the A 1 Test, Q ̇ c

k=1 (82) and E ̇ ck=1 (82)

are determined from the B1 Test, and all are

calculated as specified in Section 3.3. For

two-capacity units that lock out low capacity

operation at outdoor temperatures less than

95 °F (but greater than 82 °F), use Equations

4.1.4–1 and 4.1.4–2 rather than Equations

4.1.3–1 and 4.1.3.2 for estimating

performance at low compressor capacity.

Evaluate the space cooling capacity,

Q ̇ c

k=2(Tj), and electrical power consumption,

E ̇ c

k=2(Tj), of the test unit when operating at

high compressor capacity and outdoor

temperature Tj using,

 ̇ ( )  ̇ ( )  ̇ ( )  ̇ ( ) QTQ ( )( Q Q c T k

j c

k c

k ck

j

= = = =

= + −

− ⋅ − 2 2

2 2

82 95 82

95 82 82 4.1.3- 3)

 ̇ ( )  ̇ ( )  ̇ ( )  ̇ ( ) ETE ( )( E E c T k

j c

k c

k ck

j

= = = =

= + −

− ⋅ − 2 2

2 2

82 95 82

95 82 82 4.1.3- 4)

where Q ̇ c

k=2 (95) and E ̇ ck=2(95) are determined

from the A 2 Test, Q ̇ c

k=2 (82) and E ̇ ck=2 (82)

are determined from the B2 Test, and all are

calculated as specified in Section 3.3.

The calculation of Equation 4.1–1

quantities

q T

N

T

N

cj j () () and 

ec

differs depending on whether the test unit

would operate at low capacity (Section

4.1.3.1), cycle between low and high capacity

(Section 4.1.3.2), or operate at high capacity

(Sections 4.1.3.3 and 4.1.3.4) in responding

to the building load. For units that lock out

low capacity operation at higher outdoor

temperatures, the manufacturer must supply

information regarding this temperature so

that the appropriate equations are used. Use

Equation 4.1–2 to calculate the building load,

BL(T)j for each temperature bin.

4.1.3.1 Steady-state space cooling

capacity at low compressor capacity is

greater than or equal to the building cooling

load at temperature Tj, Q ̇ c

k=1(Tj) ≥ BL(Tj).

q T

N X TQ T

n

N

e T

N

X TE T

PLF

n

N

c j k

j c

k

j

j

c j

k

j c

k

j

j

j

( ) ( )  ̇ ( )

() ()  ̇ ( )

=⋅⋅

= ⋅ ⋅

= =

= =

1 1

1 1

where,

Xk=1(Tj) = the cooling mode low capacity

load factor for temperature bin j,

dimensionless.

PLFj = 1 ¥ CDc · [ ¥ Xk=1(Tj)], the part load

factor, dimensionless.

n

N

j =

fractional bin hours for the cooling season;

the ratio of the number of hours

6816 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

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.

n

N

j

,

Obtain the fractional bin hours for the

cooling season,

n

N

j

,

from Table 16. Use Equations 4.1.3–1 and

4.1.3–2, respectively, to evaluate Q ̇ c

k=1(Tj)

and E ̇ c

k=1(Tj). If the optional tests described

in Section 3.2.3 and Table 5 are not

conducted, set the cooling mode cyclic

degradation coefficient, CDc, to the default

value specified in Section 3.5.3. If these

optional tests are conducted, set CDc to the

lower of:

a. The value calculated according to

Section 3.5.3 or

b. The Section 3.5.3 default value of 0.25.

4.1.3.2 Unit alternates between high (k=2)

and low (k=1) compressor capacity to satisfy

the building cooling load at temperature Tj,

Q ̇ c

k=1(Tj) < BL(Tj) < Q ̇ ck=2(Tj).

q T

N X TQ T X TQ T

n

N

e T

N

X TE T X TE T

n

N

c j k

j c

k

j

k

j c

k

j

j

c j k

j c

k

j

k

j c

k

j

j

( ) ( )  ̇ () ()  ̇ ( )

( ) ( )  ̇ () ()  ̇ ( )

= ⋅+ ⋅ [ ]⋅

= ⋅+ ⋅ [ ]⋅

== ==

== = =

11 22

11 2 2

where,

Xk=1(Tj)=

 ̇ () ()

 ̇ ( )  ̇ ( ) , Q T BL T

Q TQT

c

k

j j

c

k

j c

k

j

=

= =

−

−

2

2 1

the cooling mode, low capacity load factor

for temperature bin j, dimensionless.

¥ Xk=2(Tj)=1 ¥ Xk=1(Tj), the cooling mode,

high capacity load factor for temperature bin

j, dimensionless.

Obtain the fractional bin hours for the

cooling season,

n

N

j

,

from Table 16. Use Equations 4.1.3–1 and

4.1.3–2, respectively, to evaluate Q ̇ c

k=1(Tj)

and E ̇ c

k=1(Tj). Use Equations 4.1.3–3 and

4.1.3–4, respectively, to evaluate Q ̇ c

k=2(Tj)

and E ̇ c

k=2(Tj).

4.1.3.3 Unit only operates at high (k=2)

compressor capacity at temperature Tj and

its capacity is greater than the building

cooling load, BL (Tj) < Q ̇ c

k=2(Tj). This Section

applies to units that lock out low compressor

capacity operation at higher outdoor

temperatures.

e T

N

X TE T

PLF

n

N

c j k j ck j

j

j () ()  ̇ ( ) = ⋅ ⋅

= = 2 2

q T

N X TQ T

n

N

c j k

j c

k

j

j ( ) ( )  ̇ =⋅⋅ ( ) = = 2 2

where,

Xk=2(Tj)= BL(Tj) / Q ̇ c

k=2(Tj), the cooling

mode high capacity load factor for

temperature bin j, dimensionless.

PLFj = 1 ¥ CDc · [1 ¥ Xk=2(Tj)], the part

load factor, dimensionless.

Obtain the fractional bin hours for the

cooling season,

n

N

j

,

from Table 16. Use Equations 4.1.3–3 and

4.1.3–4, respectively, to evaluate Q ̇ c

k=2(Tj)

and E ̇ c

k=2(Tj). When evaluating the above

equation for part load factor at high capacity,

use the same value of CDc as used in the

Section 4.1.3.1 calculations.

4.1.3.4 Unit must operate continuously at

high (k=2) compressor capacity at

temperature Tj BL(Tj) ≥ Q ̇ c

k=2(Tj).

q T

N Q T

n

N

e T

N

E T

n

N

c j

c

k

j

j

c j

c

k

j

j

( )  ̇ ( )

( )  ̇ () .

= ⋅

= ⋅

=

=

2

2

Obtain the fractional bin hours for the

cooling season,

n

N

j

,

from Table 16. Use Equations 4.1.3–3 and

4.1.3–4, respectively, to evaluate Q ̇ c

k=2(Tj)

and E ̇ c

k=2(Tj).

4.1.4 SEER calculations for an air

conditioner or heat pump having a variablespeed compressor. Calculate SEER using

Equation 4.1–1. Evaluate the space cooling

capacity, Q ̇ c

k=1(Tj), and electrical power

consumption, E ̇ c

k=1(Tj), of the test unit when

operating at minimum compressor speed and

outdoor temperature Tj. use,

 ̇ ( )  ̇ ( )  ̇ ( )  ̇ ( ) ( )(

 ̇ ( )  ̇ ( )  ̇ ( )  ̇ ( ) ( )(

QTQ Q Q T

ETE E E T

c

k

j c

k c

k ck

j

c

k

j c

k c

k

c

k

j

= = = =

= = = =

= + −

− ⋅ −

= + −

− ⋅ −

1 1

1 1

1 1

1 1

67 82 67

82 67

67

67 82 67

82 67

67

4.1.4 -1)

4.1.4 - 2)

where Q ̇ c

k=1(82) and E ̇ ck=1(82) are determined

from the B1 Test, Q ̇ c

k=1(67) and E ̇ ck=1(67) are

determined from the F1 Test, and all four

quantities are calculated as specified in

Section 3.3. Evaluate the space cooling

capacity, Q ̇ c

k=2(Tj), and electrical power

consumption, E ̇ c

k=2(Tj), of the test unit when

operating at maximum compressor speed and

outdoor temperature Tj. Use Equations 4.1.3–

3 and 4.1.3–4, respectively, where Q ̇ c

k=2(95)

and E ̇ c

k=2(95) are determined from the A2

Test, Q ̇ c

k=2(82) and E ̇ ck=2(82) are determined

from the B2 Test, and all four quantities are

calculated as specified in Section 3.3.

Calculate the space cooling capacity,

Q ̇ c

k=v(Tj), and electrical power consumption,

E ̇ c

k=v(Tj), of the test unit when operating at

outdoor temperature Tj and the intermediate

compressor speed used during the Section

3.2.4 (and Table 6) EV Test using,

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6817

 ̇ ( )  ̇ () ( ) (

 ̇ ( )  ̇ () ( ) (

Q TQ MT

T E MT

c

k v

j c

k v

Q j

j c

k v

E j

= =

=

= + ⋅−

= + ⋅−

87 87

87 87

4.1.4 - 3)

E 4.1.4 - 4) c

k=v

where Q ̇ c

k=v(87) and E ̇ ck=v(87) are determined

from the EV Test and calculated as specified

in Section 3.3. Approximate the slopes of the

k=v intermediate speed cooling capacity and

electrical power input curves, MQ and ME, as

follows:

M Q Q N N Q Q

M E E N N E

Q c

k ck

Q Q c

k ck

E c

k

c

k

E E c

k

= −

− ⋅ − 



 



 + ⋅ −

−





 





= −

− ⋅ − 



 



 + ⋅

== = =

= =

 ̇ ( )  ̇ ( ) ( )  ̇ ( )  ̇ ( )

 ̇ ( )  ̇ ( ) ( )  ̇

11 2 2

1 1

82 67

82 67

1 95 82

95 82

82 67

82 67

1

= = −

−





 





2 2 95 82

95 82

( )  ̇E ( ) c

k

where,

N Q Q

Q Q

N

E E

E E

Q c

k v

c

k

c

k

c

k

E c

k v

c

k

c

k

c

k

= ( ) − ( )

( ) − ( )

= ( ) − ( )

( ) − ( )

= =

= =

= =

= =

 ̇  ̇

 ̇  ̇ ,

 ̇  ̇

 ̇  ̇

87 87

87 87

87 87

87 87

1

2 1

1

2 1

 and 

.

Calculating Equation 4.1–1 quantities

q T

N

e T

N

cj cj () () and 

differs depending upon whether the test unit

would operate at minimum speed (Section

4.1.4.1), operate at an intermediate speed

(Section 4.1.4.2), or operate at maximum

speed (Section 4.1.4.3) in responding to the

building load. Use Equation 4.1–2 to

calculate the building load, BL(Tj), for each

temperature bin.

4.1.4.1 Steady-state space cooling

capacity when operating at minimum

compressor speed is greater than or equal to

the building cooling load at temperature Tj,

Q ̇ c

k=1(Tj) ≥ BL(Tj).

q T

N X TQ T

n

N

e T

N

X TE T

PLF

n

N

c j k

j c

k

j

j

c j

k

j c

k

j

j

j

( ) = ( ) ⋅ ( ) ⋅

( ) = ( ) ⋅ ( ) ⋅

= =

= =

1 1

1 1

 ̇

 ̇

where,

Xk=1(Tj) = BL(Tj) / Q ̇ c

k=1(Tj), the cooling mode

minimum speed load factor for temperature

bin j, dimensionless.

PLFj = 1 ¥ Cc

D · [1 ¥ Xk=1(Tj)], the part load

factor, dimensionless.

n

N

j =

fractional bin hours for the cooling season;

the ratio of the number of hours during the

cooling season when the outdoor temperature

fell within the range represented by bin

temperature Tj to the total number of hours

in the cooling season, dimensionless.

Obtain the fractional bin hours for the

cooling season,

n

N

j

,

from Table 16. Use Equations 4.1.4–1 and

4.1.4–2, respectively, to evaluate Q ̇ c

k=1(Tj)

and E ̇ c

k=1(Tj). If the optional tests described

in Section 3.2.4 and Table 6 are not

conducted, set the cooling mode cyclic

degradation coefficient, CDc, to the default

value specified in Section 3.5.3. If these

optional tests are conducted, set CDc to the

lower of:

a. The value calculated according to

Section 3.5.3 or

b. The Section 3.5.3 default value of 0.25.

4.1.4.2 Unit operates at an intermediate

compressor speed (k=i) in order to match the

building cooling load at temperature Tj,

Q ̇ c

k=1(Tj) < BL(Tj) < Q ̇ ck=1(Tj).

q T

N Q T

n

N

e T

N

E T

n

N

c j

c

k i

j

j

c j

c

k i

j

j

( )  ̇ ( )

( )  ̇ ( )

= ⋅

= ⋅

=

=

where,

Q ̇ c

k=i(Tj) = BL(Tj), the space cooling capacity

delivered by the unit in matching the

building load at temperature Tj, Btu/h. The

matching occurs with the unit operating at

compressor speed k = i.

E ̇ c

k=i(Tj) =

 ̇ ( )

( ) , Q TEER T

c

k i

j

k i

j

=

=

the electrical power input required by the

test unit when operating at a compressor

speed of k = i and temperature Tj, W.

EERk=i(Tj) = the steady-state energy efficiency

ratio of the test unit when operating at a

compressor speed of k = i and temperature

Tj, Btu/h per W.

Obtain the fractional bin hours for the

cooling season,

n

N

j

,

from Table 16. For each temperature bin

where the unit operates at an intermediate

compressor speed, determine the energy

efficiency ratio EERk=i(Tj) using,

EER T A B T C T k i

j jj

= () . = +⋅ +⋅ 2

For each unit, determine the coefficients A,

B, and C by conducting the following

calculations once:

D T T

T T v

= −

−

2

2

1

2

2

1

2

C EER T EER T B T T

A EER T T T C T

B

EER T EER T D EER T EER T

T T DT T

k k

k

k k k kv v

v

= − −⋅ −

= − − −⋅

= − −⋅ − [ ] − −⋅ −

= =

=

== ==

1

1

2

2 12

2

2 1

2

2

2

2

2

1

1

2

2

1

1

12 1

() () ( )

( )

() () () ()

( )

6818 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

where,

T1 = the outdoor temperature at which the

unit, when operating at minimum

compressor speed, provides a space cooling

capacity that is equal to the building load

[Q ̇ c

k=i

(T1) = BL(T1)], °F. Determine T1 by

equating Equations 4.1.4–1 and 4.1–2 and

solving for outdoor temperature.

Tv = the outdoor temperature at which the

unit, when operating at the intermediate

compressor speed used during the Section

3.2.4 EV Test, provides a space cooling

capacity that is equal to the building load

[Q ̇ c

k=v(Tv) = BL(Tv)], °F. Determine Tv by

equating Equations 4.1.4–3 and 4.1–2 and

solving for outdoor temperature.

T2 = the outdoor temperature at which the

unit, when operating at maximum

compressor speed, provides a space cooling

capacity that is equal to the building load

[Q ̇ c

k=2(T2) = BL(Tv)], °F. Determine T2 by

equating Equations 4.1.3–3 and 4.1–2 and

solving for outdoor temperature.

EER T

Q T Eqn.

T Eqn.

h per W.

T

Q T Eqn.

E T Eqn.

k c

k

j

j

v

c

k v

v vj

c

k v

v

=

=

=

=

( ) = ( ) [ ]

( ) [ ]

( ) = ( ) [ ]

( )

1

1

1

1 1

1 1

41 1

4 1

41 3

 ̇ . .4 ,

 ̇ . .4 ,

, /

 ̇ . .4 ,

 ̇

 - substituting T for T

E - 2 substituting T for T

 Btu

EER

 - substituting T for T

c

k=1

k=v

41 4

413 3

413 4 2

2

2 2

2

2 2

. .4 , ,

 ̇ .. ,

 ̇ .. , ,

- substituting T for T

 Btu/h per W.

EER

 - substituting T for T

 - substituting T for T

 Btu/h per W. k=2

v j

c

k

j

c

k

j

T

Q T Eqn.

E T Eqn.

[ ]

( ) = ( ) [ ]

( ) [ ]

=

=

4.1.4.3 Unit must operate continuously at

maximum (k=2) compressor speed at

temperature Tj, BL(Tj) ≥ Q ̇ c

k=2(Tj). Evaluate

the Equation 4.1–1 quantities

q T

N

e T

N

cj cj () () and 

as specified in Section 4.1.3.4 with the

understanding that Q ̇ c

k=2(Tj) and E ̇ ck=2(Tj)

correspond to maximum compressor speed

operation and are derived from the results of

the tests specified in Section 3.2.4.

4.2 Heating Seasonal Performance Factor

(HSPF) Calculations. Six generalized climatic

regions are depicted in Figure 2 and

otherwise defined in Table 17. For each of

these regions and for each applicable

standardized design heating requirement,

evaluate the heating seasonal performance

factor using,

HSPF

n BL T

e T RH T

F

n

N

BL T

e T

N

RH T

N

F

j

j

J

j

hj j

j

J

j

J def

j

j

j

J

hj j

j

J

j

J

= def

⋅ ( )

( ) + ( ) ⋅ =

⋅ ( ) 



 





( ) + ( ) ⋅ ( )

∑

∑ ∑

∑

∑ ∑

4 2. -1

where,

e T

N

h j ( ) =

the ratio of the electrical energy consumed by

the heat pump during periods of the space

heating season when the outdoor temperature

fell within the range represented by bin

temperature Tj to the total number of hours

in the heating season (N), W.

RH T

N

( )j =

the ratio of the electrical energy used for

resistive space heating during periods when

the outdoor temperature fell within the range

represented by bin temperature Tj to the total

number of hours in the heating season (N),

W. Except as noted in Section 4.2.1.2,

resistive space heating is modeled as being

used to meet that portion of the building load

that the heat pump does not meet because of

insufficient capacity or because the heat

pump automatically turns off at the lowest

outdoor temperatures.

Tj = the outdoor bin temperature, °F. Outdoor

temperatures are ‘‘binned’’ such that

calculations are only performed based one

temperature within the bin. Bins of 5 °F are

used.

n

N

j =

fractional bin hours for the heating season;

the ratio of the number of hours during the

heating season when the outdoor temperature

fell within the range represented by bin

temperature Tj to the total number of hours

in the heating season, dimensionless. Obtain

n

N

j

values from Table 17.

j = the bin number, dimensionless.

J = for each generalized climatic region, the

total number of temperature bins,

dimensionless. Referring to Table 17, J is the

highest bin number (j) having a nonzero entry

for the fractional bin hours for the

generalized climatic region of interest.

Fdef = the demand defrost credit described in

Section 3.9.2, dimensionless.

BL(Tj) = the building space conditioning load

corresponding to an outdoor temperature of

Tj for a given generalized climatic region and

design heating requirement, Btu/h.

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6819

TABLE 17.—GENERALIZED CLIMATIC REGION INFORMATION

Region Number ........................................................................................ I II III IV V VI

Heating Load Hours, HLH ....................................................................... 750 1250 1750 2250 2750 *2750

Outdoor Design Temperature, Tod ........................................................... 37 27 17 5 ¥10 30

j Tj(°F) Fractional Bin Hours, nj/N

1 ........................................................................................... 62 .291 .215 .153 .132 .106 .113

2 ........................................................................................... 57 .239 .189 .142 .111 .092 .206

3 ........................................................................................... 52 .194 .163 .138 .103 .086 .215

4 ........................................................................................... 47 .129 .143 .137 .093 .076 .204

5 ........................................................................................... 42 .081 .112 .135 .100 .078 .141

6 ........................................................................................... 37 .041 .088 .118 .109 .087 .076

7 ........................................................................................... 32 .019 .056 .092 .126 .102 .034

8 ........................................................................................... 27 .005 .024 .047 .087 .094 .008

9 ........................................................................................... 22 .001 .008 .021 .055 .074 .003

10 ......................................................................................... 17 0 .002 .009 .036 .055 0

11 ......................................................................................... 12 0 0 .005 .026 .047 0

12 ......................................................................................... 7 0 0 .002 .013 .038 0

13 ......................................................................................... 2 0 0 .001 .006 .029 0

14 ......................................................................................... ¥3 0 0 0 .002 .018 0

15 ......................................................................................... ¥8 0 0 0 .001 .010 0

16 ......................................................................................... ¥130 0 0 0 .005 0 0

17 ......................................................................................... ¥18 0 0 0 0 .002 0

18 ......................................................................................... ¥23 0 0 0 0 .001 0

*Pacific Coast Region.

Evaluate the building heating load using,

BL 

T

T

DHR J

OD

T C- ( )J = ( ) −

− ⋅ ⋅ 6565

42 2 .

where,

TOD = the outdoor design temperature, °F. An

outdoor design temperature is specified for

each generalized climatic region in Table

17.

C = 0.77, a correction factor which tends to

improve the agreement between calculated

and measured building loads,

dimensionless.

DHR = the design heating requirement (see

Definition 1.21), Btu/h.

Calculate the minimum and maximum

design heating requirements for each

generalized climatic region as follows:

DHR

Q T

Q

Rounded to

standardiz

h

k OD

h

k

min

 ̇ () ,

 ̇ ( ),

= ⋅

 −



 

























47 65

60

47

 for Regions I, II, III, IV, & VI

 for Region V

 the nearest

ed DHR 

given in Table 18. 

and

DHR

Q T

Q

Rounded to

standardiz

h

k OD

h

k

max

 ̇ () ,

 ̇ ( ),

= ⋅ ⋅ −



 





⋅ ⋅





















2 47 65

60

2 2 47

 for Regions I, II, III, IV, & VI

 for Region V

 the nearest

ed DHR 

given in Table 18. 

where Q ̇ h

k(47) is expressed in units of Btu/

h and otherwise defined as follows:

1. For a single-speed heat pump tested as

per Section 3.6.1, Q ̇ h

k(47) = Q ̇ hk(47), the space

heating capacity determined from the H1

Test.

2. For a variable-speed heat pump, a

Section 3.6.2 single-speed heat pump, or a

two-capacity heat pump not covered by item

3, Q ̇ h

k(47) = Q ̇ hk=2(47), the space heating

capacity determined from the H1N Test.

3. For two-capacity heat pumps that are

designed to operate exclusively, via an

equipment lockout feature, at low

compressor capacity when space cooling

while using both high and low capacities

when space heating, Q ̇ h

k(47) = Q ̇ hk(47), the

space heating capacity determined from the

H1n Test.

If the optional H1N Test is conducted on a

variable-speed heat pump, the manufacturer

has the option of defining Q ̇ h

k(47) as

specified above in item 2 or as Q ̇ h

k(47) =

Q ̇ h

k=N(47), the space heating capacity

determined from the H1N Test.

TABLE 18.—STANDARDIZED DESIGN HEATING REQUIREMENTS (BTU/H)

5,000 25,000 50,000 90,000

10,000 30,000 60,000 100,000

15,000 35,000 70,000 110,000

20,000 40,000 80,000 130,000

6820 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

4.2.1 Additional steps for calculating the

HSPF of a heat pump having a single-speed

compressor that was tested with a fixedspeed indoor fan installed, a constant-airvolume-rate indoor fan installed, or with no

indoor fan installed.

e T

N

X E T n

N

hj hj ( ) j = ( )⋅ ( )⋅ ( ) ⋅ T T

PLF - j j

J

 ̇

(.. )

δ

4 211

RH T

N

BL X T Q n

N

j j h ( ) j = ( ) −[ ] ( )⋅ ( )⋅ ( ) ⋅ T T T

3.413 Btu/h

W

-2 j jj  ̇(.. )

δ

421

where,

X 

Qh

T

BL T T

 or

 1

j

j j

( ) =

( ) ⋅( ) 



























/  ̇

whichever is less; the heating mode load

factor for temperature binj, dimensionless.

Q ̇ h(Tj) = the space hearing capacity of the

heat pump when operating at outdoor

temperature Tj, Btu/h.

E ̇ h(Tj) = the electrical power consumption of

the heat pump when operating at outdoor

temperature Tj, W.

δ(Tj) = the heat pump low temperature cutout factor, dimensionless.

PFLj = 1 ¥ CD>h · [1 ¥ X(Tj)], the part load

factor, dimensionless.

Use Equation 4.2–2 to determine BL(Tj).

Obtain fractional bin hours for the heating

season, nj/N, from Table 17. If the optional

H1C Test described in Section 3.6.1 is not

conducted, set the heating mode cyclic

degradation coefficient, CDh, to the default

value specified in Section 3.8.1. If this

optional test is conducted, set CDh to the

lower of:

a. The value calculated according to

Section 3.8.1 or

b. The Section 3.8.1 default value of 0.25.

Determine the low temperature cut-out factor

using,

δ( )

,

 ̇ ( )

.413  ̇ ( )

/ ,

 ̇ ( )

.413  ̇ ( )

,

 ̇ ( )

.413  ̇ ( )

T (

T

T

E T

T T

T

E T

T

T

E T

j

off

j

h j

off j on

j

h j

on

j

h j

=

≤ ⋅ <

< ≤ ⋅ ≥

> ⋅ ≥























0

3

1

1 2

3

1

1

3

1

 if T or Q

 if T and Q

 if T and Q

4.2.1- 3)

j

h

h

j

h

where,

Toff = the outdoor temperature when the

compressor is automatically shut off, °F. (If

no such temperature exists, Tj is always

greater than Toff and Ton).

Ton = the outdoor temperature when the

compressor is automatically turned back

on, if applicable, following an automatic

shut-off, °F.

For non-defrost heat pumps covered under

Section 3.6.1.1, determine its space heating

capacity, Q ̇ h(Tj), and the electrical power

consumption, E ̇ h(Tj), as specified in Section

4.2.1.1. For heat pumps having a heat

comfort controller that are covered under

Section 3.6.1.2, determine Q ̇ h(Tj) and E ̇ h(Tj)

as specified in Section 4.2.1.2. For all other

heat pumps covered under Section 4.2.1 (and

Section 3.6.1), calculate Q ̇ h(Tj) and E ̇ h(Tj)

using,

 ̇ ( )

 ̇ ( )

 ̇ ( )  ̇ ( )( ),

 ̇ ( )

 ̇ ( )  ̇ ( )( ),

Q T

Q

QQT

F or T F

Q

QQ T

FT F

h j

h

hhj

h

hhj

j

=

+ [ ] − ⋅ −

− ≥ ≤

+ [ ] − ⋅ −

− ≥ <<















17

47 17 17

47 17

45 17

17

35 17 17

35 17

17 45

 if T

 if T

 (4.2.1- 4) 

j j

j

o o

o o

 ̇

 ̇  ̇  ̇

,

 ̇  ̇  ̇

,

E T . .

E

EET

F or T F

E

EE T

F F

h j

h

hhj

j

h

hhj

j

( ) =

( ) + [ ] ( ) − ( ) ⋅ − ( ) − ≥ ≤

( ) + [ ] ( ) − ( ) ⋅ − ( ) − < <















( )

17

47 17 17

47 17

45 17

17

35 17 17

35 17

17 45

421

 if T

 if T

- 5

j

o o

o o

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6821

where

Q ̇ h(47) and E ̇ h(47) are determined from the H1

Test and calculated and as specified in

Section 3.7; Q ̇ h(35) and E ̇ h(35) are determined

from the H2 Test and calculated as specified

in Section 3.9.1; and Q ̇ h(17) and E ̇ h(17) are

determined from the H3 Test and calculated

as specified in Section 3.10.

4.2.1.1 Space heating capacity and the

electrical power consumption calculations

for a non-defrost heat pump. Calculate the

space heating capacity, Q ̇ h(Tj), and the

electrical power consumption, E ̇ h(Tj), for a

non-defrost heat pump covered under

Section 3.6.1.1 using,

 ̇ ̇  ̇ ̇

 ̇ ̇  ̇ ̇

QT Q Q Q

T

ET E E E

T

hj h h h

j

hj h h h

j

( ) = ( ) +[ ] ( ) − ( ) ⋅

( ) −

−

( ) = ( ) +[ ] ( ) − ( ) ⋅

( ) −

−

47 62 47

47

62 47

47 62 47

47

62 47

where

Q ̇ h(62) and E ̇ h(62) are determined from the H0

Test, Q ̇ h(47) and E ̇ h(47) are determined from

the H1 Test, and all four quantities are

calculated as specified in Section 3.7. The

low temperature cut-out factor, (Tj), must be

greater than or equal to 37 °F, in accordance

with Section 3.6.1.1.

4.2.1.2 Space heating capacity and the

electrical power consumption calculations

for a heat pump having a heat comfort

controller. Calculate the space heating

capacity and electrical power of the heat

pump without the heat comfort controller

being active as specified in Section 4.2.1

(Equations 4.2.1–4 and 4.2.1–5) for each

outdoor bin temperature, Tj, that is listed in

Table 17. Denote these capacities and

electrical powers by using the subscript ‘‘hp’’

instead of ‘‘h.’’ Calculate the mass flow rate

(expressed in pounds-mass of dry air per

hour) and the specific heat of the indoor air

(expressed in Btu/lbmda · °F) from the results

of the H1 Test using:

 ̇  ̇ .  ̇  ̇

, . .444

m V lbm

ft

V

v W

V

v

C W

da s

da mx

n n

mx

n

p da n

=⋅ ⋅ = ′ ⋅ + [ ] ⋅ =⋅

=+ ⋅

0 075 60

1

60 60

0 24 0

3

 min

hr

 min

hr

 min

hr

where,

 ̇ ,  ̇ VV v, , s mx n′ ( ) or v and W n n

are defined following Equation 3–1. For each

outdoor bin temperature listed in Table 17,

calculate the nominal temperature of the air

leaving the heat pump condenser coil using,

T T

Q T

m C o j

hp j

da p da

( ) = + ( )

⋅ 70 o

F . 

 ̇

 ̇ ,

For outdoor bin temperatures where To(Tj)

is equal to or greater than TCC,, the maximum

supply temperature determined according to

Section 3.1.9, determine Q ̇ h(Tj) and E ̇ h(Tj) as

specified in Section 4.2.1 [i.e., Q ̇ h(Tj) =

Q ̇ hp(Tj) and E ̇ h(Tj) = Ehp(Tj)].

For outdoor bin temperatures where To(Tj)

< TCC, Q ̇ h(Tj) = Q ̇ hp(Tj) + Q ̇ CC(Tj)

 

 

 

 ̇ ̇  ̇

,

 ̇  ̇

 ̇  ̇

.413

.

,

ET E T E T

where

Q T m C T TT

E T

Q T

Btu

W h

h j hp j CC j

CC j da p da CC o j

CC j

CC j

( ) = ( ) + ( )

( ) =⋅ ⋅ − [ ] ( )

( ) = ( )

⋅ 3

Calculate the HSPF of a heat pump having

a heat comfort controller as specified in

Section 4.2.1 with the exception of using the

space heating capacity and electrical power

given above [Q ̇ h(Tj) and E ̇ h(Tj)] for the

calculations at each outdoor bin temperature.

4.2.2 Additional steps for calculating the

HSPF of a heat pump having a single-speed

compressor and a variable-speed, variableair-volume-rate indoor fan. The manufacturer

must provide information about how the

indoor air volume rate or the indoor fan

speed varies over the outdoor temperature

range of 65 °F to –23 °F. Calculate the

quantities

e T

N

hj hj () () RH T

 and 

N

in Equation 4.2–1 as specified in Section

4.2.1 with the exception of replacing

references to the H1C Test and Section 3.6.1

with the H1C1 Test and Section 3.6.2. In

addition, evaluate the space heating capacity

and electrical power consumption of the heat

pump [Q ̇ h(Tj) and E ̇ h(Tj)] using,

6822 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

 ̇ ( )  ̇ ( )

 ̇ ( )  ̇ ( ) ( )

 ̇ ( )  ̇ ( )

 ̇ ( )  ̇ ( )

QT Q T Q TQT

FP FP

FP T FP

ET E T

E TET

FP FP

hj h

k

j

h

k

j h

k

j

h

k

h

k hj h

k

hj h

k

j

h

k

j h

k

j

h

k

h

k

= + −

− ⋅ − [ ]

= + −

−

=

= =

= =

=

=

= =

= =

1

2 1

2 1

1

1

2 1

2 1 ⋅ − [ ] = FP T FP hj h

k ( ) 1

where the space heating capacity and

electrical power consumption at both low

capacity (k=1) and high capacity (k=2) at

outdoor temperature Tj are determined using,

 ̇ ( )

 ̇ ( )

 ̇ ( )  ̇ ()( ),

 ̇ ( )

 ̇ ( )  ̇ ()( ),

Q T ( .

Q

QQ T

F or T F

Q

QQ T

FT F

h

k

j

h

k h

k

h

k

j

h

k h

k

h

k

j

j

=

+ [ ] − ⋅ −

− ≥ ≤

+ [ ] − ⋅ −

− < <















17

47 17 17

47 17

45 17

17

35 17 17

35 17

45

4 2

 if T

 if 17

.2 -

j j

o o

o o

1)

E

 if T

 if 17

4.2.2 - 2) h

k

j j

 ̇ ( )

 ̇ ( )

 ̇ ( )  ̇ ()( ),

 ̇ ( )

 ̇ ( )  ̇ ( )( ),

T (

E

EE T

F or T F

E

EET

FT F

j

h

k h

k

h

k

j

h

k h

k

h

k

j

j

=

+ [ ] − ⋅ −

− ≥ ≤

+ [ ] − ⋅ −

− < <















17

47 17 17

47 17

45 17

17

35 17 17

35 17

45

o o

o o

For units where indoor fan speed is the

primary control variable, FPh

k=1 denotes the

fan speed used during the required H11 and

H31 Tests (see Table 10), FPh

k=2 denotes the

fan speed used during the required H12, H22,

and H32 Tests, and FPh(Tj) denotes the fan

speed used by the unit when the outdoor

temperature equals Tj. For units where

indoor air volume rate is the primary control

variable, the three FPh’s are similarly defined

only now being expressed in terms of air

volume rates rather than fan speeds.

Determine Q ̇ h

k=1 (47) and E ̇ hk=1 (47) from the

H11 Test, and Q ̇ h

k=2 (47) and E ̇ hk=2 (47) from

the H12 Test. Calculate all four quantities as

specified in Section 3.7. Determine Q ̇ h

k=1 (35)

and E ̇ h

k=1 (35) as specified in Section 3.6.2;

determine Q ̇ h

k=2 (35) and E ̇ hk=2 (35) from the

H22 Test and the calculation specified in

Section 3.9. Determine Q ̇ h

k=1 (17) and E ̇ hk=1

(17) from the H31 Test, and Q ̇ h

k=2 (17) and

E ̇ h

k=2 (17) from the H32 Test. Calculate all

four quantities as specified in Section 3.10.

4.2.3 Additional steps for calculating the

HSPF of a heat pump having a two-capacity

compressor. The calculation of the Equation

4.2–1 quantities

e T

N

h j ( )

and

RH T

N

c j ( )

differs depending upon whether the heat

pump would operate at low capacity (Section

4.2.3.1), cycle between low and high capacity

(Section 4.2.3.2), or operate at high capacity

(Sections 4.2.3.3 and 4.2.3.4) in responding

to the building load. For heat pumps that

lock out high and/or low capacity operation

at low outdoor temperatures, the

manufacturer must supply information

regarding the cutoff temperature(s) so that

you can select the appropriate equations.

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,

 ̇ ( )

 ̇ ( )

 ̇ ( )  ̇ ( )( ),

 ̇ ( )

 ̇ ( )  ̇ ()( )

Q T ,

Q

QQ T

F

Q

QQ T

FT F

Q

h

k

j

h

k h

k

h

k

j

h

k h

k

h

k

j

j

h

k

=

=

= =

=

= =

=

=

+ [ ] − ⋅ −

− ≥

+ [ ] − ⋅ −

− ≤ ≤ 1

1

1 1

1

1 1

1

47

62 47 47

62 47

40

17

35 17 17

35 17

40

 if T

 if 17

j

o

o o

( )

 ̇ ( )  ̇ ()( ),

 ̇ ( )

 ̇ ( )

 ̇ ( )  ̇ ( )( ),

 ̇

17

47 17 17

47 17

17

47

62 47 47

62 47

40

1 1

1

1

1 1

+ [ ] − ⋅ −

− <























=

+ [ ] − ⋅ −

− ≥

= =

=

=

= =

QQ T

F

E T

E

EE T

F

E

h

k

h

k

j

h

k

j

h

k h

k

h

k

j

h

 if T

 if T

j

j

o

o

k h

k

h

k

j

j

h

k h

k

h

k

j

EE T

FT F

E

EE T

F

=

= =

=

= =

+ [ ] − ⋅ −

− ≤ <

+ [ ] − ⋅ −

− <























1

1 1

1

1 1

17

35 17 17

35 17

40

17

47 17 17

47 17

17

( )

 ̇ ( )  ̇ ()( ) ,

 ̇ ( )

 ̇ ( )  ̇ ( )( ),

 if 17

 if Tj

o o

o

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6823

b. Evaluate the space heating capacity and

electrical power consumption [Q ̇ h

k=2(Tj) and

E ̇ h

k=2(Tj)] of the heat pump when operating at

high compressor capacity and outdoor

temperature Tj by solving Equations 4.2.2–1

and 4.2.2–2, respectively, for k=2. Determine

Q ̇ h

k=1 (62) and E ̇ hk=1 (62) from the H01 Test,

Q ̇ h

k=1 (47) and E ̇ hk=1 (47) from the H11 Test,

and Q ̇ h

k=2 (47) and E ̇ hk=2 (47) from the H12

Test. Calculate all six quantities as specified

in Section 3.7. Determine Q ̇ h

k=2 (35) and

Q ̇ h

k=2 (35) from the H22 Test and, if required

as described in Section 3.6.3, determine

Q ̇ h

k=1 (35) and E ̇ hk=1 (35) from the H21 Test.

Calculate the required 35 °F quantities as

specified in Section 3.9. Determine Q ̇ h

k=2 (17)

and E ̇ h

k=2 (17) and from the H32 Test and, if

required as described in Section 3.6.3,

determine Q ̇ h

k=1 (17) and E ̇ hk=1 (17) from the

H31 Test. Calculate the required 17 °F

quantities as specified in Section 3.10.

4.2.3.1 Steady-state space heating

capacity when operating at low compressor

capacity is greater than or equal to the

building heating load at temperature Tj, Q ̇ h

k=1(Tj) ≥ BL(Tj).

e T

N

X TE T T

PLF

n

N

N

BL T T

Btu h

W

n

N

h j

k

j h

k

J j

j

j

j j j

() ()  ̇ () () (..

) () ()

.413 / (..

= ⋅ ⋅ ′ ⋅

= ⋅ − [ ] ′ ⋅

= = 1 1

423

1

3

423

δ

δ

-1)

RH(T - 2) j

where,

Xk=1= BL(Tj/Q ̇ h

k=1(Tj), the heating mode

low capacity load factor for temperature bin

j, dimensionless.

PLFj= 1 ¥ CDh · [1 ¥ Xk=1(Tj)], the part

load factor, dimensionless.

δ’(Tj = the low temperature cutoff factor,

dimensionless.

If the optional H0C1 Test described in

Section 3.6.3 is not conducted, set the

heating mode cyclic degradation coefficient,

CDh, to the default value specified in Section

3.8.1. If this optional test is conducted, set

CDh to the lower of:

a. The value calculated according to

Section 3.8.1 or

b. The Section 3.8.1 default value of 0.25.

Determine the low temperature cut-out

factor using,

δ'

,

/ ,

,

T . .

T

T

T

j

off

off on

on

( ) =

≤

≤













( )

0

1 2

1

423

if T

 if T < T

if T >

- 3

j

j

j

where toff and Ton are defined in Section

4.2.1. Use the calculations given in Section

4.2.3.3, and not the above, if:

(1) the heat pump locks out low capacity

operation at low outdoor temperatures and

(2) Tj is below this lockout threshold

temperature.

4.2.3.2 Heat pump alternates between

high (k=2) and low (k=1) compressor

capacity to satisfy the building heating load

at a temperature Tj, Q ̇ h

k=1(Tj) < BL(Tj) <

Q ̇ h

k=2(Tj).

Calculate 

RH T

N using Equation 4.2.3- 2. Evaluate 

e T

N using, () () j hj

e T

N

X TE T X TE T T

n

N

h j k

j h

k

j

k

j h

k

j j

( ) j = [ ] ( ) ⋅ ( ) + ( ) ⋅ ( ) ⋅ ′( ) ⋅ == = = 11 2 2  ̇  ̇ δ

where,

X T

Q T BL T

Q TQ T

k

j

h

k

j j

h

k

j h

k

j

=

=

= = ( ) = ( ) − ( )

( ) − ( )

1

2

2 1

 ̇

 ̇  ̇ .

Xk=2(Tj) 1 ¥ Xk=1(Tj), the heating mode,

high capacity load factor for temperature bin

j, dimensionless.

Determine the low temperature cut-out

factor, δ(T), using Equation 4.2.3–3.

4.2.3.3 Heat pump only operates at high

(k=2) compressor capacity at temperature Tj

and its capacity is greater than the building

heating load, BL(Tj) < Q ̇ h

k=2(Tj). This Section

applies to units that lock out low compressor

capacity operation at low outdoor

temperatures. Calculate

RH T

N

( )j

using Equation 4.2.3–2. Evaluate

e T

N

h j ( )

using,

6824 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

e T

N

X TE T T

PLF

n

N

h j

k

j h

k

j j

j

( ) j = ( ) ⋅ ( ) ⋅ ′( ) ⋅

= = 2 2  ̇ δ

where,

Xk=2(Tj)= BL(Tj) / Q ̇ h

k=2(Tj).

PLFj= 1 ¥ CDh · [1 ¥ Xk=2(Tj)].

When evaluating the above equation for

part load factor at high capacity, use the same

value of CDh as used in the Section 4.2.3.1

calculations. Determine the low temperature

cut-out factor, δ(Tj

), using Equation 4.2.3–3.

4.2.3.4 Heat pump must operate

continuously at high (k=2) compressor

capacity at temperature Tj, BL(Tj).

e T

N

ET T

n

N

RH T

N

BL T Q T T

Btu h

W

n

N

h j

h

k

j j

j

j j h

k

j j j

( ) = ( ) ⋅ ′′( ) ⋅

( ) = ( ) −[ ] ( ) ⋅ ′′( ) ⋅

=

=

 ̇

 ̇

.413 /

2

2

3

δ

δ

where,

′′( ) =

≤ ( ) ⋅ ( ) <

< ≤ ( ) ⋅ ( ) ≥

> ( ) ⋅ ( ) ≥











=

=

=

=

δ T

T

Q T

E T

T T

Q T

T

T

Q T

T

j

off

h

k

j

h

k

j

off j on

h

k

j

j

j on

h

k

j

j

0

3

1

12 1

1 1

2

2

2

2

,

 ̇

.413  ̇

/ ,

 ̇

 ̇

,

 ̇

 ̇

 if T or 

 if T and 

3.413 E

 if T and 

3.413 E

j 

h

k=2

h

k=2

















4.2.4 Additional steps for calculating the

HSPF of a heat pump having a variable-speed

compressor. Calculate HSPF using Equation

4.2–1. Evaluate the space heating capacity,

Q ̇ h

k=1(Tj), and electrical power consumption,

E ̇ h

k=1(Tj), of the heat pump when operating at

minimum compressor speed and outdoor

temperature Tj using,

 ̇  ̇  ̇  ̇ . .4

 ̇  ̇  ̇  ̇ . .4

QTQ Q Q T

ETE

E E

T

h

k

j h

k h

k

h

k

j

h

k

j h

k h

k

h

k

j

= = = =

= = = =

( ) = ( ) + ( ) − ( )

− ⋅ − ( ) ( )

( ) = ( ) + ( ) − ( )

− ⋅ − ( ) ( )

1 1

1 1

1 1

1 1

47 62 47

62 47

47 4 2 1

47 62 47

62 47

47 4 2 2

-

-

where Q ̇ h

k=1(62) and E ̇ hk=1(62) are determined

from the H01 Test, Q ̇ h

k=1(47) and E ̇ hk=1(47) are

determined from the H11 Test, and all four

quantities are calculated as specified in

Section 3.7. Evaluate the space heating

capacity, Q ̇ h

k=2(Tj), and electrical power

consumption, E ̇ h

k=2(Tj), of the heat pump

when operating at maximum compressor

speed and outdoor temperature Tj by solving

Equations 4.2.2–1 and 4.2.2–2, respectively,

for k=2. Determine the Equation 4.2.2–1

quantities Q ̇ h

k=2(47) and E ̇ hk=2(47) from the

H12 Test and the calculations specified in

Section 3.7. Determine Q ̇ h

k=2(35) and

E ̇ h

k=2(35) from the H22 Test and the

calculations specified in Section 3.9 or, if the

H22 Test is not conducted, by conducting the

calculations specified in Section 3.6.4.

Determine Q ̇ h

k=2(17) and E ̇ hk=2(17) from the

H32 Test and the calculations specified in

Section 3.10. Calculate the space heating

capacity, Q ̇ h

k=i(Tj), and electrical power

consumption, E ̇ h

k=1(Tj), of the heat pump

when operating at outdoor temperature Tj

and the intermediate compressor speed used

during the Section 3.6.4 H2V Test using,

 ̇  ̇ . .4

 ̇  ̇ . .4

Q TQ MT

E T E MT

h

k v

j h

k v

Q j

h

k v

j h

k v

E j

= =

= =

( ) = ( ) + ⋅− ( ) ( )

( ) = ( ) + ⋅− ( ) ( )

35 35 4 2

35 35 4 2

- 3

- 4

where Q ̇ h

k=v(35) and E ̇ hk=v(35) are determined

from the H2V Test and calculated as specified

in Section 3.9. Approximate the slopes of the

k=v intermediate speed heating capacity and

electrical power input curves, MQ and ME, as

follows:

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6825

M Q Q N N Q Q

M E E N N E

Q

h

k

h

k

Q Q

h

k

h

k

E

h

k

h

k

E E

h

k

= ( ) − ( )

− ⋅ − ( ) 



 



 + ⋅ ( ) − ( )

−





 





= ( ) − ( )

− ⋅ − ( ) 



 



 + ⋅

= = = =

= =

 ̇  ̇  ̇  ̇

 ̇  ̇  ̇

1 1 2 2

1 1

62 47

62 47

1 35 17

35 17

62 47

62 47

1

= = ( ) − ( )

−





 





2 2 35 17

35 17

E ̇ h

k

where,

N Q Q

Q Q

N E E

E E

Q

h

k V

h

k

h

k

h

k

E

h

k V

h

k

h

k

h

k

= ( ) − ( )

( ) − ( )

= ( ) − ( )

( ) − ( )

= =

= =

= =

= =

 ̇  ̇

 ̇  ̇ ,

 ̇  ̇

 ̇  ̇ .

35 35

35 35

35 35

35 35

1

2 1

1

2 1

 and

Use Equations 4.2.4–1 and 4.2.4–2,

respectively, to calculate Q ̇ h

k=1(35) and

E ̇ h

k=1(35).

The calculation of Equation 4.2–1

quantities

e T

N

and

RH T

N

hj j () ()

differs depending upon whether the heat

pump would operate at minimum speed

(Section 4.2.4.1), operate at an intermediate

speed (Section 4.2.4.2), or operate at

maximum speed (Section 4.2.4.3) in

responding to the building load.

4.2.4.1 Steady-state space heating

capacity when operating at minimum

compressor speed is greater than or equal to

the building heating load at temperature Tj,

Q ̇ h

k=1(Tj) ≥ BL(Tj). Evaluate the Equation 4.2–

1 quantities

e T

N

and

RH T

N

hj j () ()

as specified in Section 4.2.3.1. Except now

use Equations 4.2.4–1 and 4.2.4–2 to evaluate

Q ̇ h

k=1(Tj) and E ̇ hk=1(Tj), respectively, and

replace Section 4.2.3.1 references to ‘‘low

capacity’’ and Section 3.6.3 with ‘‘minimum

speed’’ and Section 3.6.4. Also, the last

sentence of Section 4.2.3.1 does not apply.

4.2.4.2 Heat pump operates at an

intermediate compressor speed (k=i) in order

to match the building heating load at a

temperature Tj, Q ̇ h

k=1(Tj) < BL(Tj) < Q ̇ hk=2(Tj).

Calculate

RH T

N

j ( )

using Equation 4.2.3–2 while evaluating

e T

N

h j ( )

using,

e T

N

ET T

n

N

h j

h

k i

j j

j ( )  ̇ = ⋅ () () ′ ⋅ = δ

where,

 ̇ ( )

 ̇ ( )

.413 / ( )

E T Q T

Btu h

W

COP T

h

k i

j

h

k i

j

h

k i

j

=

=

=

=

3 ⋅

and δ(Tj) is evaluated using Equation 4.2.3–

3 while,

Q ̇ h

k=i(Tj) = BL(Tj), the space heating

capacity delivered by the unit in matching

the building load at temperature Tj, Btu/h.

The matching occurs with the heat pump

operating at compressor speed k=i.

COPh

k=i(Tj) = the steady-state coefficient of

performance of the heat pump when

operating at compressor speed k=i and

temperature Tj, dimensionless.

For each temperature bin where the heat

pump operates at an intermediate compressor

speed, determine COPh

k=i(Tj) using,

COP T A B T C T h

k i

j jj

= () . = +⋅ +⋅ 2

For each heat pump, determine the

coefficients A, B, and C by conducting the

following calculations once:

D T T

T T

B

COP T COP T D COP T COP T

T T DT T

C

COP T COP T B T T

T T

A COP T

vh

k k k kv

vh

vh

k k

k

= −

−

= ( ) − ( ) − ⋅[ ] ( ) − ( )

− −⋅ − ( )

= ( ) − ( ) −⋅ − ( )

−

=

== ==

= =

=

3

2

4

3

2

4

2

2

4

1

3

2

4

43 4

2

4

1

3 43

4

2

3

2

2

( ) 4 −⋅ −⋅ BT CT 4 4

2

.

where,

T3 = the outdoor temperature at which the

heat pump, when operating at minimum

compressor speed, provides a space heating

capacity that is equal to the building load

[Q ̇ h k=1(T3) = BL(T3)], °F. Determine T3 by

equating Equations 4.2.4–1 and 4.2–2 and

solving for outdoor temperature.

Tvh = the outdoor temperature at which the

heat pump, when operating at the

intermediate compressor speed used during

the Section 3.6.4 H2V Test, provides a space

heating capacity that is equal to the building

load [Q ̇ h

k=v(Tvh) = BL(Tvh)], °F. Determine Tvh

by equating Equations 4.2.4–3 and 4.2–2 and

solving for outdoor temperature.

T4 = the outdoor temperature at which the

heat pump, when operating at maximum

compressor speed, provides a space heating

capacity that is equal to the building load

[Q ̇ h

k=2(T4)] = BL(T4)], °F. Determine T4 by

equating Equations by 4.2.2–1 (k=2) and 4.2–

2 and solving for outdoor temperature.

6826 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

COP T

Q T Eqn.

Btu h

W E T Eqn.

COP T

Q T Eqn.

Btu h

W E T Eqn.

k h

k

j

h

k

j

k v

vh

h

k v

vh vh j

h

k v

vh

=

=

=

=

=

=

( ) = ( ) [ ]

⋅ ( ) [ ]

( ) = ( ) [ ]

⋅ ( )

1

3

1

3 3

1

3 3 3

3

 ̇

.413 /  ̇

 ̇

.413 /  ̇

 4.2.4 -1, substituting T for T

 4.2.4 - 2, substituting T for T

 4.2.4 - 3, substituting T for T

 4.2.4 - 4, substituting T for T

 4.2.2 -1, substituting T for T

 4.2.2 - 2, substituting T for T

vh j

k h

k

j

h

k

j

COP T

Q T Eqn.

Btu h

W E T Eqn.

[ ]

( ) = ( ) [ ]

⋅ ( ) [ ]

=

=

=

2

4

2

4 4

2

4 4 3

 ̇

.413 /  ̇ .

4.2.4.3 Heat pump must operate

continuously at maximum (k=2) compressor

speed at temperature Tj, BL(Tj) ≥ Q ̇ h

k=2(Tj).

Evaluate the Equation 4.2–1 quantities

e T

N

RH T

N

hj j () () and 

as specified in Section 4.2.3.4 with the

understanding that Q ̇ h

k=2(Tj) and E ̇ hk=2 (Tj)

correspond to maximum compressor speed

operation and are derived from the results of

the specified Section 3.6.4 tests.

4.3 Calculations of the Actual and

Representative Regional Annual Performance

Factors for Heat Pumps.

4.3.1 Calculation of actual regional

annual performance factors (APFA) for a

particular location and for each standardized

design heating requirement.

APF CLH Q HLH DHR C

CLH Q

SEER

HLH DHR C

HSPF

A

A c

k

A

A c

k

A

= ⋅ ( ) + ⋅⋅

⋅ ( ) + ⋅ ⋅

 ̇

 ̇

95

95

where,

CLHA = the actual cooling hours for a

particular location as determined using the

map given in Figure 3, hr.

Q ̇ c

k(95)= the space cooling capacity of the

unit as determined from the A or A2 Test,

whichever applies, Btu/h.

HLHA = the actual heating hours for a

particular location as determined using the

map given in Figure 2, hr.

DHR = the design heating requirement

used in determining the HSPF; refer to

Section 4.2 and Definition 1.21, Btu/h.

C = defined in Section 4.2 following

Equation 4.2–2, dimensionless.

SEER = the seasonal energy efficiency ratio

calculated as specified in Section 4.1, Btu/

W·h.

HSPF = the heating seasonal performance

factor calculated as specified in Section 4.2

for the generalized climatic region that

includes the particular location of interest

(see Figure 2), Btu/W·h; the HSPF should

preferably correspond to the actual design

heating requirement (DHR) if known. But it

may correspond to one of the standardized

design heating requirements referenced in

Section 4.2.

4.3.2 Calculation of representative

regional annual performance factors APFR)

for each generalized climatic region and for

each standardized design heating

requirement

APF CLH Q HLH DHR C

CLH Q

SEER

HLH DHR C

HSPF

R

R c

k

R

R c

k

R

= ⋅ ( ) + ⋅⋅

⋅ ( ) + ⋅ ⋅

 ̇

 ̇

95

95

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6827

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.

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·h.

The SEER, Q ̇ c

k(95), DHR, and C are the

same quantities as defined in Section 4.3.1.

Figure 2 shows the generalized climatic

regions. Table 18 lists standardized design

heating requirements.

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

VI .......................................... 200 2750

4.4 Rounding of SEER, HSPF, and APF

for reporting purposes. After calculating

SEER according to Section 4.1, round it off

as specified in subpart b, § 430.23(m)(3)(i) of

the Code of Federal Regulations. Round

Section 4.2 HSPF values and Section 4.3 APF

values as per paragraphs (ii) and (iii),

respectively, of Subpart B, § 430.23(m)(3) of

the Code of Federal Regulations.

6828 Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules

Federal Register / Vol. 66, No. 14 / Monday, January 22, 2001 / Proposed Rules 6829

[FR Doc. 01–39 Filed 1–19–01; 8:45 am]

BILLING CODE 6450–01–P