CAS-RM-79-102 COMMENT 01

" 

Thursday 

AprU 19~ 1979 

Part II 

Depart:ment of 

Energy 

Office oj: Energy Conservation and Solar' 

Applications 

Proposed Rulemaking and Public Hearing 

Regarding Test Procedures for' Central 

Air Conditioners,~ Including Heat Pumps 
CAS-RM-79-102 COMMENT 01

23468 federal iRegister f VoL 44, No. 77 f Thursday, April 19, 1979 I Proposed Rules 

DEPARTMENT OF ENERGV 

. Office of Energy ConselNalt~ol1l WlIf1)(di 

Solar Applications 

["10 CFR Part 430] 

Proposed Rulemaking and PlIJJlblic 

Hearing Regarding Test Procecil.llres 

foll" Central Air Conditiol1lelrs, Ill1IcilUldlng 

Heat Pumps 

AGENCY: Department of 

ACTION: Proposed rule. 

SUMMARY: The of Energy 

hereby proposes to amend its test 

procedures for central air conditioners 

to include test procedures for heat 

pumps. These test are of 

the energy conservation 

consumer products pursuant 

to the Energy Policy and Conservation 

Act. Among other the 

legislation requires 

methods of testing be 

covered products. 

DATES: Comments by June 15, 1979; 

requests to speak by June 1, 1979; 

sta~ements by June 8, 1979; hearing to be 

held on June 13, 1979. 

ADDRESSES: Comments and requests to 

speak at the hearing to: Margaret W, 

Sibley, Conservation and Solar 

Applications, Department of Energy, 

Room 2221C, 20 Massachusetts Avenue, 

N.W., Washington, D.C. 20545. 

Hearing held at: Department of 

Energy, Room 2105, 2000 M Street, !\J,IN", 

Washington, D.C. 20461. 

FOR FURTHER INFORMATION CONTACll':: 

James A. Smith, U.S. Department of 

Ener~, Office of Conservation and 

Solar Applications, Division of 

Buildings and Community Systems, 

Consumer Products Efficiency Branch. 

20 Massachusetts Avenue, N.VV., 

Washington, D.C. 20545, (2021 37&-

4814. 

Margaret W. Sibley, U.S, Department of 

Energy. Office of Conservation and 

Solar Applications, 20 Massachusetts 

Avenue, N.W., D.C. 

20545, (202) 376-1651. 

William J. Dennison, Office of the 

General Counsel, 20 Massachusetts 

Avenue, N.W .. Room 3228, 

Washington, D.C. 20545. (202) 376-

4100. 

SUPPLEMENT ARY INIFOlRiMftAT"O~: 

A. Background 

On October 1,1977, the Department of 

Energy (DOE) assumed the authority 

the Federal Energy Administration 

WEAl for the energy conservation 

program for consumer products, 

pursuant to Section 301 of the 

Department of Energy Act 

(DOE Act) (Pub. L. energy 

conservation program for consumer 

pwciucts was established FEA 

I-'Uli DU'''''' to Title m. B the 

and Conservation Act 

~~ n,v,. Subsequently, the was 

the National Energy 

Policy Act (NECPA) (pub. 

References in this notice to 

"the or to sections of the Act refer 

to the Energy Policy and Conservation 

Act as emended by NECPA. Section 323 

U.S.C. 6293) of the Act that 

standard methods of 

covered 

appear at 10 

Test procedures were oe,')n.".,,,, 

central air conditioners 

7,1977 (42 FR 30401, 

and a 

test 

air conditioners were 

November 21, 1977 

November 25. 19(7). 

DOE is today proposing to amend the 

test procedures for central air 

conditioners to include 

for heat pumps, 

B. Discussion 

The heat pump is 

of air conditioner which 

mechanical refrigeration cycle to 

provide heating and may also 

cooling. DOE is proposing to include 

heal pumps as a class of central air 

conditioners because the 

function(s) of the equipment are 

essentialiy identical. 

The definition of central air 

conditioners is proposed to be modified 

to include both heating and cooling 

units. In order to clarify terms, 

definitions of "heat pump", "air-source 

heat pump", "water-source heat pump". 

and "cooling only unit", are proposed to 

be added in Section 430,2. Other new 

terms which specifically to the 

laboratory methodology for 

performance are proposed to be 

included in Section 1 of the proposed 

Appendix M. 

The lest methodology for 

units remains the same as 

adopted for central air rOlnrli,tw,n 

the organization of the test 

iI appears in the Code of 

Regulations has been revised so the 

heating performance methodology can 

be incorporated and the total 

can be more understandable the 

user. Sections 1, 2.1, 3.1, 4.1, and 5.1 of 

proposed Appendix M contain the test 

procedures for central' air conditioners 

as previously developed, while all other 

sections refer to new proposals 

heat pumps. The 

change to the central 

conditioner test procedure the 

inclusion of the cooling seasonal 

pelrtolrm;3,nc;e factor (CSPF) in order io 

maintain continuity between the 

proposed measure of 

and the measure of cooling 

With this change, the measures may 

combined or weighted to an 

annual efficiency which may be used 

consumers in purchasing decisions. 

that the measure of 

in the energy standards 

for centraJ air conditioners 

on the cooling seasonal nprtn"'p",,n 

factor (CSPF), the heating seasonal 

factor (HSPFj, or the 

annual performance factor These 

terms are defined 1.1,1.9, 

and 1.15 of the proposed M. 

the major additions have to do 

only testing for 

performance, interested 

comment on the cooling as well as 

portion. 

Air-source heat pumps are equipped 

with a means of providing 

supplementary heat by means of 

electrical resistance or a fossil fuel 

furnace. These systems are at 

low outdoor temperatures the heat 

itself cannot provide the required 

til> satisfy the building load. It 

understood that the proposed 

rule as it applies to air-source heat 

pumps only covers those units which are 

designed for use with electrical 

resistance back up systems. DOE is 

currently developing test procedures for 

other types of back up systems, 

including gas and oil furnaces, and 

intends to propose these as soon as 

practicable. 

As described in the definition of 

"'central air conditioner" only units 

which are electrically powered are 

covered by these procedures. A vail.able 

information indicates thai heat 

pumps and gas-fired 

conditioners are not distributed in 

commerce to any significant extent and 

therefore are not included in this 

proposal. 

Section 3Z3(a)(2) of the Acl ."""nr"''' 

DOE to direct the National Bureau of 

Standards (NBS) to deveiop test 

procedures for the determination of the 

estimated annual operating costs and at 

least one other useful measure of energy 

consumption which DOE determines is 

likely to assist consumers in making 

purchasing decisions. At DOE's request 

NBS evaluated existing test proceciure§ 

for measuring energy consumption of 

heat pumps. Present industry testing 
CAS-RM-79-102 COMMENT 01

Federnl Register I Vol. 44. No. 77 I Thursday, April 19. 1979 I Proposed Rules 23469 . 

procedures for heat pumps use 

steady state conditions and do not 

account for performance degradation 

due to defrosting and cycling of the unit 

NBS transmitted to DOE a test 

TU',"r>,>rl,,,'P review document which 

reviewed existing test procedures for 

measuring the energy consumption of 

heat pumps and which recommended a 

test procedure. Copies of this review 

document will be made available for 

inspection by interested persons as 

provided for later in this notice, 

The test procedure amendments 

recommended by NBS and proposed 

today incorporate. in part. test 

procedures used by industry to measure 

the heating capacity and efficiency of 

heat pump equipment as described in 

the Air Conditioning and Refrigeration 

Institute (ARI) Standards 240-77, 210-75, 

and 320-76 and the American Society of 

Heating. Refrigeration and Air 

Conditioning Engineers (ASHRAE) 

Standard 37-69. In addition. the 

amendments incorporate procedures for 

determining estimated annual operating 

costs and seasonal performance factors 

of heat pumps in both the heating and 

cooling modes. 

Pursuant to section 301 of the DOE 

Act. DOE is required to comply with 

section 32'of the Federal Energy 

Administration Act of 1974 (FEA Act) 

(Pub. L. 93-275), as amended by section 

9 of the Federal Energy Administration 

Authorization Act of 1977 (Pub. L. 95-

70). 

Sections 32(a) and (b) of the FEA Act 

provide that: 

(a) If any proposed rule by the 

Administrator contains any commercial 

standards. or specifically authorizes or 

requires the use of any such standards. 

then any general notice of the proposed 

rulemaking shall: 

(1) identify. by name. the organization 

which promulgated such standards; and 

(2) state whether or not, in the 

judgment of the Administrator. such 

organization complied with the 

requirements of subsection (b) in the 

promulgation of such standards. 

(b) An organization complies with the 

requirements of this subsection in 

promulgating any commercial standards 

if: 

(1) it gives interested persons 

adequate notice of the proposed 

promulgation of the standards and an 

opportunity to participate in the 

promulgation process through the 

presentation of their views in hearings 

or meetings which are open to the 

public; 

(2) the membership of the organization 

at the time of the promulgation of the 

standards is sufficiently balanced 80 as 

to allow for the effective rel:l'rI~'St:[Jt!:itl(m 

of an Interested persons; 

before promulgating such 

it makes available to th.e 

records or of the 

UWl.cOUVU, and anv 

letters. memorandu~s. and materials 

relating to such standards; and 

(4) it has procedures allowing 

interested persons to: 

(A) obtain a reconsideration of any 

action taken by the organization relating 

to the promulgation of such standards, 

and 

(B) obtain a review of the standards 

(including a review of the basis or 

adequacy of such standards). 

The findings required of DOE by 

section 32 of the FEA Act serve to alert 

the public and DOE to the use and 

background of commercial standards in 

a proposed rulemaking and, through the 

comment and hearing process, allow 

interested persons to make known their 

views regarding the appropriateness of 

the use of those particular commercial 

standards in that proposedrulemaking. 

Any negative finding does not reflect a 

determination by DOE of the 

advisability of utilizing a particular 

standard for part of the test procedure 

regulation. 

As noted above, the rulemaking 

proposed today contains elements of 

four commercial standards promulgated 

by two non-governmental organizations, 

ASHRAE and ARI. 

Determinations have not been made 

regarding ASHRAE because the 

ASHRAE standard cited is part of the 

existing central air conditioner test 

procedure and was previously subjected 

to review under section 32(c) of the FEA 

Act. With respect to the ARI standards 

cited. DOE has determined that ARI 

does not comply with the requirements 

of section 32(b) because among other--

things, its membership is limited to 

manufacturers of air conditioning and 

refrigeration equipment and. therefore is 

not "sufficiently balanced so as to allow 

for the effective representation .of all 

interested persons." As required by 

Section 32(c), DOE will consult with the 

Attorney General and the Chairman of 

the Federal Trade Commission 

concerning the impact of these 

standards on competition. prior to 

prescribing final test procedures. 

C. Measures of Energy Consumption 

The Act requires DOE to prescribe 

test procedures for the determination of 

estimated annual operating costs and at 

least one other useful measure of energy 

consumption which the Secretary 

determines is likely to assist consumers 

in making purchasing decisions. 

DOE ift proposing to amend § 430.22 

suh£tltuting a new paragraph (m) to 

include all measures of energ"y 

consumption specified for an classes of 

central air conditioners including heat 

pumps. The fonowing is a brief . 

description of each measure. 

The estimated annual operating cost 

for the cooling and/or heating functions 

of central air conditioners is an estimate 

of the electrical energy input necessary 

to satisfy a representative annual 

heating and/or cooling load multiplied 

by a representative average unit cost of 

electricity. For air-source central air 

conditioners (section 430.22(m)(1)). the 

annual electrical energy input for 

cooling is estimated by dividing the 

output (the cooling capacity times the 

representative annual average cooling 

load hours) by the seasonal energy 

efficiency ratio. The annual electrical 

energy input for heating is estimated by 

dividing the output (a representative 

design heating requirement times a 

representative average heating load 

hours) by a representative heating 

seasonal performance factor. For watersource heat pumps (§ 430.22{m){2n. the 

annual electrical energy input is 

estimated by multiplying the test 

m~asured electrical power input by the 

representative annual average cooling 

or heating load hours. 

Also proposed (§ 430.22(m) (5) and (6)) 

as test procedures for the determination 

of other measures of energy 

consumption which are likely to assist 

consumers in making purchasing 

decisions are test procedures regarding 

the measures of efficiency: The seasonal 

energy efficiency ratio, as described in 

430.22(m)(5)(iv). the cooling seasonal 

performance factor. as described in 

430.22(m}(5)(i) and 430.22(m}(6)[i). the 

heating seasonal preformance factor. as 

described in 430.22{in)(5}(ii) and 

430.22(m)(6)(ii), and the annual 

performance factor. as described in 

430.22(m)(5)(iii) and 430.22(m)(6)(iii). The 

cooling seasonal performance factor 

(CSPF) and the seasonal energy 

efficiency ratio (SEER) are an estimate 

of the total cooling output during the 

normal annual usage period for cooling, 

divided by an estimate of the total 

electric input during the same period. 

The heating seasonal performance 

factor (HSPF) is an estimate of the total 

heating output during the normal annual 

usage period for heating. divided by an 

estimate of the total electric input during 

the same period. The annual 

performance factor (APF) is a weighted 

average of the combined HSPF and 

CSPF depending on the number of 

annual heating load hours and cooling 
CAS-RM-79-102 COMMENT 01

23470 federal )Register I Vol. 44, No. 77 I Thursday. April 19. 1979 I Proposed Rules .i 

load hours for a SP€~cific region of the 

proposed measures which 

are likely to assist consumers in 

purchasing decisions are the 

regional annual operating costs for 

central air conditioners (§ 

arid (4)). The estimated regional 

op~rating cost for the cooling and/or 

heating functions of central air 

conditioners is an estimate of the annual 

.electrical energy input necessary to 

satisfy a local heating and/or cooling 

load multiplied by a representative 

average unit cost of electricity. The 

annual electrical energy input is 

estimated in the same manner as 

detailed above except that regional 

annual cooling and heating load hours 

(from,sections 6.1.3. and 6.2.5ln 

AppendixM to Subpart B) are 

performance factors described in 

430.22(m} (5) and (6) are used. 

DOE recognizes that there may be 

additional useful measures of energy 

consumption for central air conditioners 

other than the measures described 

above. Accordingly, today's proposed 

amendment in paragraph 430.22(m)(7) 

provides for other useful measures 

which the Secretary determines are 

likely to assist consumers in .making 

purchasing decisions. These measures~ 

however. must be derived from the 

application of the uniform test method 

prGposed. today as Appendix-M to 

Subpart B. 

D. Laboratory M~thodoll!))gy 

The proposed rule provides for a 

controlled laboratory environment for 

measuring energy consumption of.all 

central air conditioners. including heat 

pumps. The test methodology for the airsource cooling mode is the same as 

adopted in the existing central air 

conditioner test procedure. Appendix M 

has been renumbered with the aill'-

source cooling protion of the test 

methodology appearing in sections 2.1. 

:3.1. 4.1 and 5.1. Air-source heating test 

methodology appears in sections 2.2. 3.2. 

4.2, and 5.2. Water-source heating and 

cooling methpdologies appear in 

sections 2.4. 3.4. 4.4. 5.4, and 5.5. All 

reference material is now incorporated 

in sections 6.1 through 6.4. 

The proposed amendments specify 

methodologies for measuring the heating 

performance of both air-source and 

water-source heat pumps. The test 

method for air-source units in the 

heating mode utilizes four tests to 

evaluate: the steady state efficiency. the 

energy lost to defrosting the outdoor 

coil. th~ degradation effect caused by 

cycling of the unit. and the efficiency at 

low outdoor temperatures. UtHizingtbe 

results of these tests, an efficiency curve 

can be generated which is applicable to 

ail outdoor temperatures that may occur 

over the course of a heating season. A 

mathematical summation technique is 

then used incorporating the weather 

data of different regions across the 

country to calculate the perfomance 

factors for a given unit in a particular 

iocation. Because an air-source heat 

pump has different performance 

depending on outdoor temperature. a 

given unit will have varying 

performance depending on the 

geopraphicallocation of the unit 

In order to reduce the burden of 

increased testing on manufacturers with 

limited capability for testing heating 

performance, an assigned degradation 

coefficient. Cn. may be used in lieu of 

condicting the Cyclic Test on air-source 

heat pumps. If this option is chosen the 

value substituted is proposed to be 0.25 

in all cases. The derivation of this factor 

is consistent with the present 

methodology used in the cooling 

performance testing. If a manufacturer 

chooses this option. he must then use 

the assumed value in calculations for all 

his basic models. Another technique 

used to reduce testing is the use of a 

faCtor to show improved seasonal 

performance on units with sophisticated 

"demand-defrost control systems". Due 

to the complexity of a test that would be 

required to show the actual difference in 

seasonal performance between demanddefrost and the conventional timetemperature defrost systems. an 

estimated value of 5 percent 

improvement in the defrost capacity was 

assigned to units which utilize demanddefrost control systems. This factor may 

be adjusted by DOE depending on data 

presented during the comment period. 

lEo Representative Average-Use Cyde 

Section 323(b)(2) (42 U.S.C. 6293(b)(2)) 

of the Act provides that test procedures 

for determining estimated annual 

operating costs of any covered product 

shall be calculated from measurement of 

energy use in a representative averageuse cycle and from representative 

average unit costs needed to operate 

such product during such cycle. DOE 

proposes that the original representative 

average-use cycle of 1000 cooling load 

hours per year for the cooling mode be 

applicable for both cooling only and 

heating/cooling units. DOE has also 

determined that 2080 heating load hours 

is the representative average-use cycle 

for central air conditioners in the 

heating mode. These determinations are 

based upon NBS' recommendation. 

which in turnis based upon NBS' 

reports which estimated the annual 

compressor operating hours for central 

air conditioners in the cooling mode and 

the annual heating load hours for 

furnances. Because the average number 

of heating load hours is dependent on 

average weather data and the number of 

units in a given area, it is for 

an types of heating equipment 

f. Unit Costs of Energy 

Under section 323(b)(2) of the Act, 

DOE is required to provide 

manufacturers with information on 

representative average unit costs of 

energy. This information was provided 

by notice issued July 11. 1977 (42fR 

36549. July 15, 1977) and is expected to 

be updated on a continuing basis, 

G. Number of Units to be Tested 

On September 8. 1978. (43 FR 40192) 

DOE proposed to amend test procedures 

for all types of consumer products 

including central air conditioners. 

currently covered by this program, in 

order to prescribe sampling provisions 

applicable to any testing required under 

section 323(c) or 324 of the Act. This 

testing related specifically to 

representations regarding the energy 

consumption of or cost of energy 

consumed by the various products,and 

to the labeling of these products with 

eriergy consumption of or cost of energy 

consumedby the various products •. and 

to the labeling of these products, with 

energy consumption information as 

required by the Federal Trade 

Commission {FTC). 

DOE is today reproposing § 430.22(m) 

to receive comments on the sampling 

approach to be adopted for central air 

conditioners. including heat pumps; The 

major proposed changes from the 

present sampling requirements include 

the use of one sided sampling provisions 

in lieu of two sided. the use of computer 

modeling mathematical correlation to 

rate the condenser-evaporator-coil 

combinations other than those actually 

tested, and the ability to substitute 

certain components within Ii system if measures of energy consumption are not 

affected. 

Those commenting on the September 

8. 1978. notice recommended that DOE 

adopt sampling plans which required 

fewer units to be tested as compared to 

either of the distinct plans presented in 

DOE's proposed sampling rulenr FIC's 

proposed labeling rule which appeared 

in the federal Register on July 21. 1978 

(43 FR 31806). 

The two rules proposed by DOlE and 

FTC would have had different effects on 

the extent of testing. The rule proposed 

by FTC specified that units of every 

basic model need be tested. The rule 
CAS-RM-79-102 COMMENT 01

Federal Register I Vol. 44, No. 77 / Thursday, April 19, 1979 /Proposed Rules 23471 

= 

proposed by DOE contained provisions 

which had the effect of specifying that 

units of only certain basic models need 

be tested. Specifically, the DOE rule 

grouped basic models according to the 

condensing unit used and required that 

only units of the condenser-evaporatorcoil-combination (defined in DOE test 

procedures) which was expected to 

have the largest volume of retail sales 

among all basic models using that 

condensing unit need be tested. Both the 

DOE and FTC proposed rules specified 

90 percent confidence and toierances of 

± 5% for their sampling plans, and both 

utilized two-sided confidence limits. 

Commenters requested that any 

sampling plan adopted should require 

the testing of only certain basic models, 

and for those basic models tested, the 

statistical parameters should be 

modified to require fewer units to be 

tested as compared to either proposed 

rule. 

Commenters provided information on 

the time required to test one unit; the 

frequency of introducing new basic 

models; the number of units of each 

basic model which would have to be 

tested to satisfy sampling provisions 

using modified sampling parameters; the 

extent that existing test results can be 

used to fulfill the requirements of 

Federal program; the extent of testing 

beyond the level previously conducted 

to support programs either administered 

by trade associations or conducted for 

the manufacturers' own purposes; the 

number of basic models the commenter 

currently produces; the energy 

consuming characteristics or features 

that distinguish the commenter's basic 

models; the capacity of test facilities 

used by the commenter; and the cost of 

testing all the commenter's basic 

models, 

Commenters urged that if units of 

every basic model were to be tested, 

testing costs could be expected to be $65 

million. DOE has reviewed the data 

submitted and methods by which this 

figure was determined, and believes that 

actual costs would be substantially 

lower, but may still be significant. 

Commenters also stated that 

measures of energy consumption of 

basic models net tested could be 

determined by engineering analysis 

based on data obtained by testing other 

basic models which used the same 

condensing unit. It was argued that this 

method of determining measures of 

energy consumption would be 

accompanied by very little sacrifice in 

reliability of such measures. The DOE 

proposed sampling rule permitted the 

determination of measures of energy 

consumption in this manner. Industrywide, the number of basic models which 

would require actual testing would be 

thus reduced by a factor of about 5, with 

a commensurate reduction in the costs 

of testing. DOE is proposing that among 

all basic models using a single 

condensing unit, only units of the 

condenser-evaporator-coil combination 

expected to have the largest volume of 

retail sales need be tested. 

Other comments indicated that DOE's 

proposed sampling plan was logically 

inconsistent in that it specified 

confidence levels and tolerances for 

data not supported by testing. DOE 

agrees that any simulation employing 

computer programs or engineering 

analysis to determine measures of 

energy consumption cannot reasonable 

demonstrate that the true mean of such 

measures is contained in a certain range 

about represented values, Therefore ' 

today's proposed rules does not specify 

such confidence levels and tolerances 

for data not supported by testing. In 

order to provide manufacturers a 

guideline for determining measures of 

energy consumption applicable to all the 

units of all basic models, The proposed 

rule describes certain minimum criteria 

for computer simulations which may be 

used in place of testing certain basic 

models, Whenever measures of energy 

consumption determined by computer 

simulation do not agree with measures 

of energy consumption determined by 

actual testing, the values determined by 

testing will be assumed to be the more 

reliable values, 

The basis of the simulation technique 

must be a computer model of the 

mechanical vapor-compression 

refrigeration cycle, The major 

components in the refrigeration cycle 

are modeled as "fits" to manufacturer 

component performance data. For 

example, heat transfer characteristics of 

the coils are modeled as functions of 

face area, number of rows, air flow rate, 

fins per inch, and entering air enthalpy. 

Compressor performance curves must be 

used to provide refrigerant mass flow 

rate and compressor power as a 

function of suction temperature and 

condenser temperature. An iterative 

technique must then be used which 

varies the evaporator temperature, 

condensing temperature, and refrigerant 

mass flow rate to balance the cycle. 

When the cycle is balanced, the 

enthalpies of the process end points are 

knows as well as the refrigerant mass 

flow rate, and, as a result, the measure 

of steady state efficiency can be 

calculated, 

The computer model is then to be 

calibrated to actual test results and may 

be used to predict the energy efficieny of 

basic models which use the same 

condensing unit as a condenserevaporator-coil combination which has 

been tested. In order to insure the 

accuracy of ratings derived in this 

manner, and to insure compatibility 

between manufacturers, any 

manufacturer which uses the computer 

modeling provisions is required to 

submit to DOE a description of the 

analysis used, inchiding the computer 

model and the data and analysis used to 

verify the accuracy of the ratings 

obtained by computer modeling, At this 

time DOE does not plan to treat such 

information as confidential or 

proprietary, but is interested in receiving 

comments on this issue. DOE is also 

, interested in receiving comments on the 

feasibility of DOE prescribing a 

computer model for use by all 

manufacturers who elect to rate their 

products in this manner. 

Commenters stated that it is often 

necessary to substitute components 

manufactured by different suppliers and '-

that these substitutions typically have a 

minimal effect on energy consumption. 

Commenters further stated that based 

on certain of the definitions of the term 

"basic model" presented in DOE test 

procedures, it was not clear whether the 

units which include such component 

substitutions constituted a new basic 

model which would require additional 

testing. 

If the tested values of the measures of 

energy consumption for units having 

such component substitutions change by 

only a minimal amount from the tested 

values before the substitution, DOE 

agrees that additional testing of such 

units would not provide benefit to the 

consumer commensurate with costs 

incurred, For example, if a 350 watt 

condenser fan in a central conditioner is 

substituted for a 330 watt condenser fan 

and iflhis is the only design change 

which affects the tested values of the 

measures of energy consumption, then 

the total average power needed to 

operate the unit may be expected to 

increase by 20 watts. However, as 

compared to the total average power 

consumption of 4350 wa tts, any changes 

in the tested values of the measures of 

energy consumption wiil be less than 

errors caused by the numerical rounding 

specified in DOE test procedures. 

Therefore, a sample of units containing 

the substituted condenser fan need not 

be tested since, by not changing the 

values of the tested measure of energy 

consumption, the confidence statement 

remains satisfied for the represented 

values of the measures of energy 

consumption. However, if a 3500 watt 

compressor motor in a central air 
CAS-RM-79-102 COMMENT 01

Federal Register I Vol. 44, No. 77 I Thursday, April 19, 1979 I Proposed Rules 

conditioner is substituted for a 3300 watt 

compressor motor of identical capacity, 

then the efficiency of such units is likely 

to decrease and their energy 

consumption is likely to increase, It is 

probable that the represented value of 

the measure of efficiency based on 

testing units containing the 3300 watt 

compressor motor will no longer satisfy 

the sampling confidence statement. In 

such case, further testing would be 

needed to establish the represented 

value of the measures of energy 

consumption which will satisfy the 

confidence statement for units which 

use the 3500 watt compressor motor 

To clarify the test procedures, 

wherever the term "basic model"' is used 

in § 430.23, a footnote states that 

components of similar design may be 

substituted without necessitating further 

testing, if the represented values of the 

measures of energy consumption will 

not change as a result of the 

substitution, i.e" the represented values 

continue to satisfy the sampling 

confidence statement. With the adoption 

of sampling plans utilizing one-sided 

confidence limits, manufacturers may 

adjust the represented values of the 

measures of energy consumption from 

tested values of the measures of energy 

consumption to compensate for 

anticipated changes in the energy 

consuming characteristics of future 

production units that may include such 

component substitutions, 

After reviewing the data submitted, 

DOE by this notice is reproposing a 

sampling plan which specifies 90 

percent confidence and 5 percent 

tolerances on a one-sided sampling 

system, DOE believes that this system 

provides the most reliable data for 

determining measures of energy 

consumption when compared against 

increased costs for testing, 

An alternative approach under 

consideration by DOE is a pian in which 

manufacturers would be required to test 

two randomly selected units of the 

condenser-evaporator-coil combination 

likey to have the largest volume of sales. 

The measure of energy consumption 

used in labeling and representations 

would be required to be no higher than 

the mean of the values of efficiency 

derived from testing two units or no 

lower than the mean of the values of 

operation cost derived from the same 

testing. The advantage of this method 

would be to limit required testing to no 

more than two units. 

Computer modeling would then be 

used for other basic models which use 

the same condensing unit. 

Manufacturers might still rate 

conservatively depending on their prior 

knowledge of the coefficient of variation 

of the particular product. 

A disadvantage of this method is that 

the reliability of the measures of energy 

consumption could be expected to be 

high for basic models where test results 

among the units tested show little 

variability. and the reliability could be 

expected to be low \",here there was 

substantial variability. It should be 

noted that a major purpose for testing is 

to provide reliable measures of energy 

consumption in order to assist 

consumers in making purchasing 

decisions. 

Manufacturers and other interested 

persons are encouraged to comment on 

the proposed approach and the 

alternative. All comments and data 

pertaining to the alternate approach 

should be detailed specifically to 

provide a basis for incorporation into 

the final rule, in the event that the 

alternate approach is chosen for the 

final rule. 

H. Comment Procedure 

1. Written Comment. Interested 

persons are invited to participate in this 

ruJemaking by submitting data, views or 

arguments with respect to the proposed 

amendments set forth in this notice. 

Comments should be identified on the 

outside of the envelope and on 

documents submitted to DOE with the 

designation "Central Air ConditionersProposed Amendments (Docket No. 

CAS-RM-79-102)," Fifteen copies 

should be submitted. All comments 

received by june 15, 1979, and all other 

relevant information. will be considered 

by DOE before final action is taken on 

the proposed regulation. 

Pursuant to the provisions of 10 CFR 

1004.11(e). any person submitting 

information which he believes to be 

confidential should so identify the 

information and submit one copy only of 

the information. DOE reserves the right 

to determine the confidential status of 

the information or data and treat it 

according to its determination. 

2. Public Hearing. a. Request 

Procedure-The time and place of the 

public hearing are indicated at the 

beginning of this preamble. The hearing 

will be continued, if necessary on June 

14, 1979. DOE invites any person who 

has an interest in the proposed 

amendment issued today, or who is a 

representative of a group or class of 

persons that has an interest in today's 

proposed amendment, to make a written 

request for an opportunity to make an 

oral presentation. Such a request should 

be directed to the address indicated at 

the beginning of this preamble and must 

be received before June 1. 1979. Such a 

request may be hand delivered to such 

address. between the hours of 8 a.m. 

and 4:30 p.m., Monday through Friday. A 

request should be labeled both on the 

document and on the envelope "Central 

Air Conditioners-Proposed 

Amendments (Docket No. CAS-RM-79-

102)." 

The person making the request should 

brieflv describe the interest concerned: 

if appropriate. state why she or he is a 

proper representative of a group or class 

of persons that has such an interest. and 

given a concise summary of the 

proposed oral presentation and a 

telephone number where she or he may 

be contacted through. 

DOE will notify, before 4:30 p.m., June 

4. 1979, each person selected to appear 

at the hearing. Each person selected to 

be heard must submit 15 copies of her or 

his statement to the address and bv the 

date given in the beginning of this' 

preamble. In the event any person 

wishing to testify cannot meet the 15 

copy requirement, alternative 

arrangements can be made with 

Margaret W. Sibley in advance of the 

hearing by so indicating in the letter 

requesting an oral presentation or by 

calling (202) 376-1651. 

b, Conduct of Hearing. DOE reserves 

the right to select the persons to be 

heard at the hearing, to schedule their 

respective presentations and to 

establish the procedures governing the 

conduct of the hearing. The length of 

each presentation may be Umited. based 

on the number of persons requesting to 

be heard. 

A DOE official will be designated to 

preside at the hearing. This will not be a 

judicial or evidentiary type hearing. 

Questions may be asked only by those 

conducting the hearing, and there will 

be no cross-examination of persons 

presenting statements. Any decision 

made by DOE with respect to the 

subject matter of the hearing will be 

based on alJ information available to 

DOE. At the conclusion of all initial oral 

statements, each person who has made 

an oral statement will be given the 

opportunity if she or he so desires, to 

make a rebuttal statement. The rebuttal 

statements will be given in the order in 

which the initial statements were made 

and will be subject to time limitations. 

Any interested person may submit 

questions to be asked of any person 

making a statement at the hearing to 

Margaret W .. Sibley, Conservation and 

Solar Applications. DOE. 20 

Massachusetts Avenue. NW., 

Washington. D,C. before 4:30 p.m. June 

8, 1979, DOE will determine whether th(! 

question .is relevant, and whether the "', 
CAS-RM-79-102 COMMENT 01

Federal Register I Vol. 44. No. 77 I Thursday. April 19. 1979 I Proposed Rules 23473 

time limitations permit it to be presented 

for answer. 

Any further procedural rules needed 

for the proper conduct of the hearing 

will be announced by the presiding 

officer. 

A transcript of the hearing will be 

made and the entire record of the 

hearing, including the transcript, will be 

retained by DOE and made available for 

inspection at the DOE Freedom of 

Information Office in the Forrestal 

Building, Independence Avenue and 

L'Enfant Plaza, SW., Washington, D.C. 

20585, between the hours of 8 a.m. and 

4:30 p.m .. Monday through Friday. In 

addition. any person may purchase a 

copy of this transcript from the reporter. 

I. Environmental and Inflationary 

Review 

Pursuant to Section 7(c)(2) of the 

Federal Administration Act of 1974. a 

copy of this notice has been submitted 

to the Administrator of the 

Environmental Protection Agency for his 

comments concerning the impact of this 

proposal on the quality of the 

environment. The Administrator has no 

comments at the present time. 

The National Environmental Policy 

Act of 1969 requires DOE to assess the 

environmental impacts of any proposal 

issued by the Department for "major 

Federal Slctions significantly affecting 

the quality of the human environment." 

Since test procedures under the energy 

conservation program for consumer 

products will be used only to 

standardize the measurement of energy 

usage and will not affect the quality or 

distribution of energy usage. DOE has 

determined that the action of prescribing 

test procedures. by itself. will not result 

in any environmental impacts. On this 

basis. DOE has determined that. with 

respect to prescribing test procedures 

under the energy conservation program 

for consumer products. no 

environmental impact statement is 

required. 

The proposed rule has been reviewed 

in accordance with Executive Order 

12044 and DOE Order 2030. From the 

regulatory analysis performed. it was 

-determined that the proposal was 

significant in nature but did not have 

major impacts to manufacturers and 

consumers (imposing annual economic 

costs of $100 million or more). 

(Energy Policy and Conservation Act. Pub. L. 

94-163. as amended by Pub. L. 94-819; 

Department of Energy Organization Act. Pub. 

L. 95-91; E.O. 12009. 42 FR 46267.) 

In consideration of the foregoing. it is 

proposed to amend Chapter II of title 10, 

Code of Federal Regulations, as set forth 

below. 

Issued in Washington. D.C .• April 6. 1979. 

Omi G. Walden. 

Assistant Secretary, Conservation and Solar Applications. 

1. Section 430.2 is amended by 

deleting the present definition of 

"central air conditioner" and 

"condensing unit" and adding the 

following new definitions inappropriate 

alphabetical order: 

§ 430.2 Definitions. 

* * * * 

"Air-source heat pump" means a 

"heat pump" which consists of one or 

more assemblies, which utilizes an 

indoor conditioning coil, compressor(s), 

and refrigerant-to-outdoor-air heat 

exchanger to provide air heating. and 

which may also provide air cooling, 

dehumidifying. circulating, and air 

cleaning. 

* * * 

"Central air conditioner" means a 

consumer product which is powered by 

single phase electric current. which is 

rated below 65.000 Btu/hour, and which 

is either a "heat pump" or a "cooling 

only unit". 

* * * * * 

"Condensing unit" means a 

component of a central air conditioner 

which is designed to remove the heat 

absorbed by the refrigerant and to 

transfer it to the outside environment, 

and which consists of an outdoor coil, 

compressor(s), and air moving device. 

"Cooling only unit" means a "central 

air conditioner" which consists of a 

compressor(s). an air cooled condensing 

unit, and an evaporator or cooling coil. 

which is designed to provide air cooling, 

dehumidifying, circulating. and air 

cleaning. 

* 

"Heat pump" means a "central air 

conditioner" which is either an "airsource heat pump" or a "water-source 

heat pump". 

* 

"Water-source heat pump" means a 

"heat pump" which consists of one 

assembly which utilizes an indoor 

conditioning coil with air moving means. 

compressor(s), and refrigerant-to-water 

heat exchanger(s) to provide both air 

heating and cooling, dehumidifying, 

circulating, and air cleaning. 

* * * * 

2. Section 430.22 is amended by 

substituting a new paragraph (m) to read 

as follows: 

§ 430.22 Test procedures for measures of 

energy consumption. 

* * * * * 

(m) Central Air Conditioners~ (1) The 

estimated annual operating cost for 

cooling only units and air-source heat 

pumps shall be one of the following: 

(i) For cooling only units or the cooling 

portion of the estimated annual 

operating cost for air-source heat pumps 

which provide both heating and cooling. 

the product of (A) the quotient of the 

cooling capacity, in Btu's per hour, 

determined from the steady-state wetcoil test (test A) measured at the highest 

compressor speed, as described in 

Section 3.1 of Appendix M to this 

subpart, and the average seasonal 

energy efficiency ratio, in Btu's per watthour, determined from section 5.1 of 

Appendix M to this subpart; (B) the 

representative average use cycle of 1000 

cooling load hours per year; (C) a 

conversion factor of .001 kilowatts per 

watt; and (D) a representative average 

unit cost of electricity in dollars per 

kilowatt-hour as provided pursuant to 

section 323(b )(2) of the Act. the resulting 

product then being rounded off to the 

nearest dollar per year; 

(ii) For heat pumps which provide 

only heating or the heating portion of the 

estimated annual operating cost for 

central air conditioners which provide 

both heating and cooling. the product of 

(A) the quotient of the standardized 

design heating requirement nearest the 

capacity measured in the High 

Temperature Test, Q .. (47) in Btu's per 

hour, determined in sections 5.2 and 

6.2.6 of Appendix M to this subpart. and 

the heating seasonal performance factor 

corresponding to the above mentioned 

standardized design heating requirement 

determined from section 5.2 of Appendix 

M to this subpart; (B) the representative 

average use cycle of 2080 heating load 

hours per year; (C) a correction factor -

described in section 5.2 of Appendix M 

to this subpart; (D) a representative 

average unit cost of electricity in dollars 

per kilowatt-hour as provided pursuant 

to section -323(b )(2) of the Act; and (E) a 

conversion factor of one kilowatt-hour 

per 3.413 Btu's, the resulting quotient 

then being rounded off to the nearest 

dollar per year; or 

(iii) For central air conditioners which 

provide both heating and cooling, the 

quantity determined in paragraph (i) 

above added to the quantity determined 

in paragraph (m)(l)(ii) above. 

(2) The estimated annual operating 

cost for water-source heat pumps shall 

be the sum of: 

(i) The product of (A) the electrical 

power input in watts, and described by 

the quantity EF in section 5.4 of 
CAS-RM-79-102 COMMENT 01

23474 

AppendiX M to 'this il'tlbpHri; {B} the 

representative average use cycle of 1,000 

cooling load hours per year; (C) a 

comrefslon factor of.ool kilowatts per 

watt; and(j)) a representative average 

unit cost of electricity in dollars per 

kilowatt-hour as provided pursuant to 

section 323(b)(Z) of the Act, the resulting 

product then being rounded off to the 

nearest t'Iollm- per year, and 

iii} The product of (A) the electrical 

po~inputin watts, as described by 

the quanti,tyEtJ in section 5.5 of 

Appendix ~tothis subpart; {B} the 

representative average use cycle of 2000 

hea ting load hours per year; ,( C) a 

conversWn factor of .001 kilowatts per 

watt; and (D,a representative average 

trolt costaf ele.ctricity in dollars per 

'kilowatt-hour as provided pursuant to 

section :3Z3(b}(a).of the Act. the resulting 

prodiJcr then being rounded off to the 

nearest dollar per year. 

{:at The 'estimated regional annual 

operating OOst(s) for cooling only units 

and air-source heat pumps shaH be one 

of the folloWing: 

til For ;cooling Qnly units or the cooling 

portion of the estimated annual 

operating cost for central air 

conditioners which provide both heating 

and,cooling. the product of (A) the 

quotient of cooling capacity in Btu's per 

hour determined from the steady-state 

wet-coil test (testA) measured at the 

highest compressor speed. and the 

average seasonal energy efficiency ratio 

in ,Btu's per waH-hour both determined 

from section 5.1 Qf Appendix M to this 

subpart; (B) the estimated number of 

local cooling load hours per year 

determmedfrom section 6.1.3 of 

Appendix M to this subpart; (C) a 

conversion factor of .001 kilowatts per 

watt; and (D) arepresentative average 

umtcost of electricity in dollars per 

kilowatt-hour as provided pursuant to 

section 323{b)(2) of the Act, the resulting 

produ:ct then being rounded off to the 

nearesrdoHar per year; 

{ti} Fnr heat pumps which provide 

only heating nr the heating porlinn of the 

estimated annual operating cost for 

central'air conditioners which provide 

both heating and cooling. for each 

applicable standardized design heating 

requirement, the product of (A) the 

quotient9f the estimated number of 

local heating load hours per year 

determirred from section 13.2.5 of 

ApPendix M to this subpart. and the 

heating seasonal performance factor 

corresponding to the appropriate 

s tandardizeddesign heating requirement 

determined from section 5.2 of Appendix 

M to this subpart; (B) 0.77, a correction 

factor described in section 5.2 of 

Appendix M to this subpart; {C) the 

standardized design heating requirement 

in Btu?s per hour determined in secJi:ons 

5.2 and 6.2.6 of Appendix M to this 

, subpart; (D) a representative average 

unit cost of electricity in dollars per 

kilowatt-hour as provided pursuant to 

section 323(b}{2) of the Act; and {E) a 

conversion factor of one kilowatt-hour 

per 3,413 Btu's, the resulting quotient 

then being rounded off to the nearest 

dollar per year; or . 

(iii) For central air conditioners which 

provide both heating and cooling, the 

quantity determined in paragraph 

(m)(3)(i) above added to each quantity 

determined in paragraph (m){3}(ii) 

above, 

(4) The estimated regional annual 

operating cost for wat.er-source heat 

pumps shall be the sum of: 

(il The product of (A) the quotient of 

the cooling capacity from test F in Btu's 

per hOllrand the cooling seasonal 

performance factor as determined in 

section 5.4 of Appendix M to this 

subpart for the local ground water 

temperature determined from section 5.4 

and 6.4 of AppendiX M to this subpart: 

(B) the estimated number of local 

cooling load hours per year determined 

from section 6.1.3 of Appendix M to this 

subpart; (C) a conversion factor of .. 293 

watt-hours per Btu; (D) a conversion 

factor of .001 kilowatts per watt; and (E) 

a representative average unit cost of 

electricity in dGllars per kilowatt hour as 

provided pursuant to section 323{b){2) of 

the Act, the resulting product then being 

rounded off to the nearest dollar year, 

and 

(ii) The product of (A) the quotient of 

the heating capacity from test G, in Btu's 

per hour, and the heating seasonal 

performance factor as determined in 

section 5,5 of Appendix Mto the subpart 

for the local ground water temperature 

determined from section 5.5 and 6.4 of 

Appendix M to this subpart; (B) the 

estimated number of local heating load 

hours per year determined from section 

6.2.5 of Appendix M to this subpart; (C) 

a conversion factor of .293 watt-hours 

per Btu: {D} a conversion factor of .001 

kilowatts per watt; and eE) a _ 

representative average unit cost of 

electricity in dollars per kilowatt-hour 

as provided pursuant to section 323(b)(2) 

of the Act. the resulting product then 

being rounded off to the nearest dollar 

per year. 

(5) The measure(s) of efficiency for 

cooling only units and aiT-source heat 

pumps shan be one or more of the 

following: 

(i) The cooling seasonal performance 

factor for cooling only units and airsource heat pumps which provide 

cooling shall be the cooling seasonal 

performance factor determined 

according to section 5.1 ofAppendix'M 

to thi$ subpart, rounded off to the 

nearest a.m. 

(ii) TheheatiIlgseasonal performance 

factors for air-source heat pumps shall 

be the heating seasonal perforffiance 

factors determined according to section 

5.2 of Appendix M to this subpart for 

each applicable standardized design 

heating requirement within each 

climatic region, rounded off to the 

nearest 0.01. 

rill] The annual performance factors 

for air source heat pumps which provide 

heating and cooling, shaH be the annual 

performance factors determined 

according to section 5.3.1 of Appendix M 

to this subpart for each standardized 

design heating requirement within each 

climatic region, rounded off to the 

nearest 0.01. 

(iv) The seasonal energy efficiency 

ratio for cooling only units and airsource heat pumps which provide 

cooling shan be the 'Seasonal energy 

efficiency factorde!ermined according 

to section 5.1 of Appendix M to this 

Subpart. rounded off to the nearest (lOl. 

(6) The measurers) of efficiency for 

water-source heat pumps shall be one or 

more of the following: {i} The cooling 

seasonal performance factors for watersourci'! heat pumps shall be the cooling 

seasonal performance factors 

determined according to section 5,4 of 

Appendix M to this subpart, rounded off 

to the nearest 0.01. 

(ii) The heating seasonal performance 

factors for water-source heat pumps 

shan be the heating seasonal 

performance factors determined 

according to section 5.5 of Appendix M 

to this subpart, rounded off to the 

nearest 0.01. 

(ill) The annual performance factors 

for water-source heat pumps shall be the 

annual performance factors determined 

according to section 5.6 of Appendix M 

to this subpart for the local ground 

water temperature, cooling load hours 

and heating load hours, rounded to the . nearest 0.01. ' 

(7) Other useful measures of energy 

consumption for central air conditioners 

shall be those measures of energy 

consumption which the Secretary of 

Energy determines are likely to assist 

consumers in making purchasing 

decisions and which are derived from 

the application of Appendix M to this 

subpart. 

* * 

3. Section 430.23 is amended by 

establishing a new paragraph (m) to 

read as foHows: 
CAS-RM-79-102 COMMENT 01

Federal Register I Vol. 44. No. 77 I Thursday. April 19. 1979 I Proposed Rules 23475 

§ 430.23 Units to be tested 

* * 

(m)(l) For central air conditioners. each 

condensing unit shall have a basic 

model selected and a sample of 

sufficient size tested in accordance with 

applicable provisions of this subpart 

such that: 

(i) Any represented value of estimated 

annual operating cost, energy 

consumption or other measure of energy 

consumption of a basic model for which 

consumers would favor lower values 

shall be no less than the higher of (A) 

the mean of the sample or (B) the upper 

90 percent confidence limit of the true 

mean divided by 1.05, and 

(ii) Any represented value of the 

energy factor or other measure of energy 

consumption of a basic model for which 

consumers would favor higher values 

shall be no greater than the lower of (A) 

the mean of the sample or (B) the lower 

90 percent confidence limit of the true 

mean divided by .95. 

(Z) The basic model 1 selected for tests 

shall be that condenser-evaporator-coiIcombination likely to have the largest 

volume of retail sales. For every other 

basic model 1 using that condensing unit, 

either-

(i) A sample of sufficient size shall be 

tested to insure that: 

(A) Any represented value of 

estimated annual operating cost, energy 

consumption or other measure of energy 

consumption of a basic model for which 

consumers would favor lower values 

shall be no less than the higher of (1) the 

mean of the sample or (Z) the upper 90 

percent confidence limit of the true 

mean divided by 1.05 and 

(B) Any represented value of the 

energy factor or other measure of energy 

consumption of a basic model for which 

consumers would favor higher values 

shall be no greater than the lower of (1) 

the mean of the sample or (Z) the lower 

90 percent confidence limit of the true 

mean divided by .95. or 

(ii) Represented values of measures of 

energy consumption shall be based on a 

computer simulation of the energy 

consuming characteristics of such basic 

model. as described in paragraph (m)(4) 

of this section. 

(3) The sample selected for paragraph 

(m)(l) of this section shall be comprised 

of units which are production upjts. or 

representative of production units. 

(4)(i) The basis 'of the computer 

simulation technique referred to in 

paragraph (Z)(ii) of this section shall be 

I Components of similar design may be 

substituted ... ithout requiring additional testing if 

the represented measures of energy consumption continue to satisfy the applicable sampling 

provision. 

a computer model of the,mechanical 

vapor-Compression refrigeration cycle. 

The major components in the 

refrigeration cycle shall be modeled as 

"fits" to manufacturer component 

performance data. Heat transfer 

characteristics of the coils shall be 

modeled as functions of face area, 

number of rows, air flow rate, fins per 

inch, and entering air enthalpy. 

Compressor performance curves shall be 

used to provide refrigerant mass flow 

rate and compressor power as a 

function of suction temperature and 

condenser temperature. An interative 

mathematical technique shall be used 

which varies the evaporator 

temperature, condensing temperature, 

and refrigerant mass flow ra te to 

balance the cycle. 

(ii) The computer model shall be 

calibrated to actual test results derived 

pursuant to paragraph (m)(l) of this 

section and may be used to derive 

measures of energy consumption of 

other basic models which use the same 

condensing unit as the condenserevaporator-coil-combina tion actually 

tested. Any manufacturer who chooses 

to rate products by computer simulation 

shall submit to DOE a document 

describing the analysis used to derive 

such ratings. including the computer 

model. and the data and engineering 

analysis used to verify the accuracy of 

such ratings. 

(iii) Whenever measures of energy 

consumption'determined by computer 

simulation do not agree with measures 

of energy consumption determined by 

actual testing, the values determined by 

actual testing shall be used to comply 

with section 3Z3(c) of the Act. or to 

comply with rules preflcribed under 

section 324 of the Act. 

§ 430.24 [Revoked] 

4. Section 430.Z4(m) is revoked. 

5. Appendix.M to Subpart B of Part 

430 is amended to read as follows: 

Appendix M To Subpart B-Uniform Test 

Method for Measuring the Energy 

Consumption of Central Air Conditioners 

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 power used in one year. 

1.2 "ARI" means Air-Conditioning and 

Refrigeration Institute. 

1.3. "AR} Standard 210--75" means the test 

standard published in 1975 by the ARI and 

titled "Standard for Unitary Air-Conditioning 

Equipment". 

1.4 "ARI Standard 210-77" means the test 

standard published in 1977 by the ARI and 

titled "Standard for Air-Source Unitary heat 

Pump Equipment". 

1.5 "ARI Standard 320-76" means the test 

standard publi$hed in 1976 by the ARI and 

titled "Standard for Water-Source Heat 

Pumps". 

1.6 "ASHRAE" means the American 

Society of Heating, Refrigeration and AirConditioning Engineers. Inc. 

1.7 "ASHRAE Standard 37-69" means the 

test standard published by ASHRAE in 1969 

and titled "Methods of Testingfor Rating 

Unitary Air-Conditioning and Heat Pump 

Equipment." 

1.8 "Cooling load factor (eLF)" means the 

ratio of the total cooling done in a complete 

cycle of a specified time period. consisting of 

an "on" time and "off' time, to the steadystate cooling done over the same period at 

constant ambient conditions. 

1.9 "Cooling seasonal performance factor 

(CSPFj" means the estimated total cooling 

output of a unit during its normal annual 

usage period for cooling divided by the total 

electric power input during the same period. 

1.10 "Cyclic Test" means a test where the 

indoor and outdoor conditions are held 

constant, but the unit is manually turned "on" 

and "off' for specific time periods to simulate 

part-load operation. 

1.11 "Degradation coefficient (Cu)" means 

the measure of the efficiency loss due to the 

cycling of the unit 

1.12 "Demand-defrost control system" 

me"ms a system which is designed to perform 

the defrost function on the outdoor coll of the 

heat pump only when a predetermined 

degradation of performance is sensed by 

measuring the difference between the 

outdoor air temperature and the saturated 

refrigerant temperature leaving the outdoor 

coil. The control system is able to defrost at 

all frosting temperature conditions while 

compensating for pressure differentials 

across the outdoor coil caused by factors 

other than defrosting. 

1.13 "Design heating requirement (DHR)" 

is the amount of heating required to maintaIn 

a given indoor temperature at a particular 

outdoor design temperature. 

1.14 "Dry-coil test" means a test conducted 

at a wet-bulb temperature and a dry-bulb 

temperature such that moisture will not 

condense on the evaporatol/coil of the unit. 

1.15 "Heating seasonal performance !:actor 

(HSPF)" means the total hearing output of-a 

heat pump during its normal annual usage 

period for heating divided by the total 

electric power input during the same period. 

1.16 "Heating load factor (HLF)" means the 

ratio of the total heating done in a complete 

cycle of a specified time period, consisting of 

an "on" time and "off' time. to the steady , 

state heating done over the same period at 

constant ambient conditions. 

1.17 "Latent cooling" means the amount of 

cooling in Btu's necessary to remove water 

vapor from the air passing over the indoor 

coil by condensation during a period of time. 

1.18 "Part-load factor (PLF)" means the 

ra tio of the cyclic energy efficiency ratio to 

the s1eady-state energy efficiency ratio at' 

identical ambient conditions. 

1.19 "Seasonal energy efficiency ratio 

(SEER)" means the total cooling of a central 
CAS-RM-79-102 COMMENT 01

23476 Federal Register I Vol. 44. No. 77 I Thursday. April 19. 1979 I Proposed Rules 

air conditioner in Btu's during its normal 

annual usage period for cooling divided by 

the total electric power input in watt-hours 

during the same period. 

1.20 "Sensible cooling" means the amount 

of cooling in Btu's performed by a unit over a 

period of time. excluding latent cooling. 

1.21 "Single package unit" means any 

central air conditioner in which all the major 

assemblies are enclosed in one system. 

1.22 "Split system" means any central air 

conditioner in which one or more of the major 

assemblies are separate from the others. 

1.23 "Steady-state test" means a test in 

which all indoor and outdoor conditions are 

held constant and the unit is in a continuous 

operating mode. 

1.24 "Temperature bin" means a 5'F 

increment over a dry-bulb temperature range 

of 65'F through 104°F for the cooling cycle 

and _25°F through MOF for the heating cycle. 

1.25 "Time-temperature defrost control 

system" means a system which automatically 

provides the defrost function at a ~ predetermined time interval whenever the 

outdoor temperature drops below a level 

where frosting will occur. 

1.26 "Test condition tolerance" means the 

maximum permissible variation of the 

average of the test observations from the 

standard or desired test condition as 

provided in 6.1.1. 6.2.1. 6.2.2. and 6.2.3 of this 

Appendix. 

1.27 "Test operating tolerance" means the 

maximum permissible difference between the 

maximum and the minimum instrument 

observation during a test as provided in 6.1.1. 

6.2.1. 6.2.2 and 6.2.3 of this Appendix. 

1.28 "Wet-coil test" means a test 

conducted at a wet-bulb temperature and a 

dry-bulb temperature such that moisture will 

condense on the test unit evaporator coil. 

2. Testing'Required 

2.1 Testing required for air source cooling 

only units with single speed compressors, 

two-speed compressors, two compressors, or 

cylinder unloading. Two steady state wet coil 

tests required to be performed. test A and 

test B. Test A is to be conducted as an 

outdoor dry bulb temperature of 95'F and test 

B at 82°F. Tests C and D are optional tests to 

be conducted when cyclic performance 

parameters are to be measured in order to 

determine the degradation coefficient. Cn. 

Test C is a steady state dry coil test 

conducted at an outdoor dry bulb 

temperature of 82°F. Test D is a cyclic test 

also conducted at an outdoor dry bulb 

temperature of 82°F. In lieu of condUcting 

tests C and D, an assigned value of 0.25 may 

be used for the degradation coefficient. Cn' 

Any manufacturer who chooses to use the 

ass.igned value must use it in calculations for 

all basic models. 

2.1.1 . Testing required for units with 

single speed compressors and single speed 

condenser fans. Test A and test B shall be 

performed according to the test procedures 

outlined in 4.1 of this Appendix. In addition. 

the cyclic performance shall be .evaluated by 

conducting test C and D according to the 

requirements outlined in 4.1 of this Appendix. 

2.1.2 Testing required for units with 

single speed compressors and multiple-speed 

condenser fans. The test requirements for 

multiple-speed condenser fan units shall be 

the same as describea in section 2.1.1 for 

single speed condenser. fan units. 

2.1.3 Testing required for units with twospeed compressors, two compressors, or 

cylinder unloading. The test requirements for 

two-speed compressor units. two compressor 

units. or units with cylinder unloading are the 

same as described in 2.1.1 of this Appendix 

except that tes.t A and test B shall be 

performed at each compressor speed or at 

each compressor capacity. 

2.1.4 Testing required for units with twospeed compressors, two compressors, or 

cylinder unloading capable of varying the 

sensible to total (SIT) capacity ratio. When a 

unit employing a two-speed compressor. two 

compressors. or cylinder unloading provides 

a method of varying the ratio of the sensible 

cooling capacity to the total cooling capacity. 

(SIT). the test requirements are the same as 

for two-speed compressor units as described 

in 2.1.3 of this Appendix. 

2.2 Testing required for air source heating 

only units with single speed compressors, 

two-speed compressors, two compressors, or 

cyclinder unloading. Four types of tests are 

required to be performed: High Temperature, 

Cyclic, Frost Accumulation, and Low 

Temperature. In lieu of conducting the Cyclic 

Test an assigned value of 0.25 may be used 

for the degradation coefficient. Cn. 

2.2.1 Testing required for units with 

single speed compressors. Units with single 

speed compressors shall be subjected 

respectively to the High Temperature Test at 

47°F described in section 3.2.1.1, the Cyclic 

Test as described in section 3.2.1.2. the Frost 

Accumulation Test as described in section 

3.2.1.3. and the Low Temperature Test as 

described in section 3.2.1.4. Any 

manufacturer who chooses to use the 

assigned value must use it in calculations for 

all basic models. 

2.2.2 Testing required for units with twospeed compressors, two compressors, or 

cylinder unloading. With the unit operating: 

at the high compressors speed (two-speed 

compressor), with both compressors in 

operation (two compressors), or at the 

maximum capacity (cylinder unloading); the 

follOWing tests are required to be performed 

on all units; the High Temperature Test at 

47'F, the Frost Accumulation Test, and the 

Low Temperature Test. An additional test 

(cyclic at 47°F) is required, with the unit 

operating at the high compressor speed (twospeed compressor), with both «ompressors in 

operation (two compressors), or at the 

maximum capacity (cylinder unloading); if 

the normal mode of operation requires 

cycling "on" and "off' of the compressor(s) at 

high speed or maximum capacity. 

With the unit operating: at the low 

compressor speed (two-speed compressor). 

with the single compressor which normally 

operates at low loads (two compressors), or 

at the low compressor capacity (cylinder 

unloading); the following tests are required to 

be performed on all units: the High 

Temperature Test at 47°F, the High 

Temperature Test at 62'F, and the Cyclic 

Test. Additional tests, (Frost Accumulation 

Test and Low Temperature Test) are 

required. with the unit op.erating: on low 

compressor speed (two-speed compressor), 

with the single compressor which normally 

operates at low loads (two compressors) or at 

the low compressor capacity 1cylinder 

unloading), if the unit's low speed. one' 

compressor or low capacity performance at 

and below 40°F is needed to calculate its 

seasonal performance. 

2.3. Testing required for air...source units 

which provide both heating and cooling; The 

requirements for units which provide both 

heating and cooling shall be the same as the 

requirements in Section 2.1 and 2.2 of this 

Appendix. 

2.4 Testing required for water source 

units which provide both heating and cooling. 

The following four steady state tests, each 

employing two methods as described in 4.4, 

are required to be performed on all units: test 

E and test F as described in 3.4.1 and 3.4.3 of 

this Appendix and test G and test H as 

described in 3.4.2 and 3.4.3 of this Appendix. 

2.4.1 Cooling testing required for units 

with single speed compressors. Two steadystate cooling tests, test E and test F. shall be 

performed according to the te.st procedures 

and test conditions outlined in 3.4 and 4.4 of 

this Appendix. 

2.4.2 Heating testing required for units 

with single speed compressors. Two steadystate heating tests, test G and test H. shall be 

performed ·according to the test procedures 

and test conditions outlined in 3.4 and 4.4 of 

this Appendix. 

2.4.3 Cooling testing required for single 

speed compressor units capable of 

modulating water and refrigerant flow to 

maintain constant capacity. The cooling tests 

required shall be the same as those detailed 

in 2.4.1 of this Appendix. 

2.4.4 Heath1g testing required for single 

speed compressor units capable of 

modulating water and refrigerant flow to 

maintain constant capacity. The heating tests 

required shall be the same as those detailed 

in 2.4.2 of this Appendix. 

3. Testing conditions 

3.1 Testing conditions for air source 

cooling only units with single speed 

compressors, two-speed compressors, two 

compressors or cylinder unloading. Th" test 

room requirement and equipment installation 

procedures are the same as those specified in 

sections 11.1 and 11.2 of ASHRAE Standard 

37-69. Units designed for either horizontal or 

vertical installation shall be tested in the 

vertical upflow position. All tests shall be 

performed at the normal residential voltage 

and frequency for which the equipment is 

designed (either 115 or 230 volts and 60 

hertz). the test installation shall be designed 

such that there will be no air flow through the 

cooling coil due to natural or forced 

convection while the indoor fan is "off'. This 

shall be accomplished by installing automatic 

dampers upstream and downstream of the 

test unit to block the off period air flow. 

The following conditions listed in ARI 

Standard 210-75 shall apply to all tests 

performed in Section 3.1 of this Appendix: 

5.1.1 Values of the Standard Capacity 

Ratings. 

5.1.2 Values of the Standard Input Ratings. 
CAS-RM-79-102 COMMENT 01

Federal Register I Vol. _44. No. 77 I Thursday, .April 19, 1979 I Proposed Rules 23477 

5.1.3 Values of the Standard Energy 

Efficiency Ratio. 

5.1.4.4 Cooling Coil Air Quantity. 

5.1.4.5 Requirements for Separated 

Assemblies. 

3.1.1 Testing conditions for units with 

single speed compressors and single speed 

condenser fans. 

3.1.1.1 Steady state wet·coil performance 

tests (Tests A and Test B). Test A and test B 

shall be performed w;th the air entering the 

indoor side of the unit having a dry-bulb 

temperature of 80' F and a wet-bulb 

temperature of 67' F. The dry-bulb 

temperature of the air entering the outdoor 

side of the unit shall be 95' F in test A and 

82' F in test B. The temperature of the air 

surrounding the outdoor side of the unit in 

each test shall be the same as the outdoor 

en tering air tempera ture except for units or 

sections thereof intended to be installed only 

indoors, in which case the dry-bulb 

temperature surrounding that indoor side of 

the unit shall be 80' F. For those units which 

reject condensate to the condenser, located in 

the outdoor side of the unit, the outdoor wetbulb temperature surrounding the outdoor 

side of the unit shall be 75' F in test A and 

65' F in test B. 

3.1.1.2 Steady state dry coil performance 

test (Test C) and cyclic dry coil performance 

test {Test D}. Test C and test D shall be 

performed with the air entering the indoor 

side of the unit having a dry-bulb 

temperature of 80° F and a wet-bulb 

temperature which does not result in 

formation of condensate on the indoor coil. (It 

is recommended that an indoor wet-bulb 

temperature of 57° F or less be used.) The 

dry-bulb temperature of the air entering the 

outdoor portion of the unit shall be 82' F. The 

outdoor portion of the unit shall be subject to 

the same conditions as the requirements for 

conducting test B as stated previously in 

section 3.1.1.1. Test C shall be conducted with 

the unit operating steadily. Test D shall be 

conducted by manually cycling the unit "on" 

and "off." The unit shall cycle 1Nith the 

compressor "on" for 6 minutes and "off' for 

24 minutes. The indoor fan shall also cycle 

"on" and "off', the duration of the indoor fan 

"on" and "off' periods being governed by the 

automatic controls which the manufacturer 

normally supplies with the unit. The results of 

tests C and D shall be used to calculate a 

degradation coefficient. Cn, by the procedures 

outlined in 5.1 of this Appendix. 

3.1.2 Testing conditions for unds with 

single speed compressors and multiple-speed 

condenser fans. The condenser fan speed to 

be used in test A shall be that speed which 

normally occurs at an outdoor dry-bulb 

temperature of 95° F, and for test B, the fan 

speed shall be that which normally occurs at 

an outdoor dry-bulb temperature of 82' F. If 

elected to be performed, tests C and D shall 

be conducted at the same condenser fan 

speed as in test B. 

3.1.3 Testing conditions for units with 

two-speed compressors, two compressors, or 

cylinder unloading. The condenser fan speed 

used in conducting test A at each compressor 

speed shall be that which normally occurs at 

an outdoor dry-bulb temperature of 95' F. For 

test B. the condenser fan speed at each 

compressor speed shall be that which 

normally occurs at an outdoor dry-bulb 

temperature of 82' F. If elected to be 

performed, tests C and D shall be conducted 

at the low compressor speed with the same 

condenser fan speed as used in test B. For 

those two-speed units in which the normal 

mode of operation involves cycling the 

compressor "on" and "off' at high speed, 

tests C and D shall also be performed with 

the compressor operating at high speed and 

at a condenser fan speed that normally 

occurs at Test A ambient conditions. Units 

consisting of two compressors are subject to 

the same requirements as those units 

containing two-speed compressors, except 

that when operated at. high speed, both 

compressors shall be operating and when 

operating at low speed, only the compressor 

which normally operates at an outdoor drybulb temperature of 82' F shall be operating. 

In lieu of conducting tests C and D, an 

assigned value of 0.25 may b used for the 

degradation coefficient, Cn at each 

compressor speed. lfthe assigned 

degradation coefficient is used for one 

compressor speed it must also be used for the 

other compressor speed. 

In the case of units with cylinder 

unloading, the loaded and the unloaded 

conditions correspond to high and low 

compressor speed on two-speed units 

respectively. 

3.1.4 Testing conditions for units with 

two-speed compressors. two compressors, or 

cylinder unloading capable of varying the 

sensible to total (SIT) capacity ratio. The 

mode of operation selected for controlling the 

SIT ratio in the performance of test A and 

test B at each compressor speed shall be such 

that it does not result in an operabng 

configuration which is not typical of a normal 

residential installation. If elected to be 

performed. tests C and D shall be conducted 

at low compressor speed (single compressor 

operating) with the same SIT control mode as 

used in test B when performed at the low 

compressor speed. Likewise, tests C and D 

shall also be conducted at high compressor 

speed (two compressors operating) and with 

the same SIT control mode as in test A when 

. performed at the high compressor speed. 

In the case of units with cylinder 

unloading. the loaded and unloaded 

conditions correspond to high and low 

compressor speed on two-speed units 

respectively. 

3.2 Testing conditions for air source 

heating only units with single speed 

compressors, two-speed compressors. two 

compressors. or cylinder unloading. "(he 

equipment under test shall be installed 

according to the requirements of Section 11.2 

of ASHRAE Standard 37-69 and Secbon 

5.1.4.5 of ARI Standard 24077. Test chamber 

requirements are the same as given in Section 

11.1 of ASHRAE Standard 37-39. Units 

designed for either horizontal or vertical 

installation shall be tested in the vertical 

upflow position. All tests shall be performed 

at the normal residential voltage and 

frequency for which the equipment is 

designed (either 115 of 230 volts and 80 

hertz). 

3.2.1 Testing conditions for units with 

single speed compressors. 

3.2.1.1 High temperature test conditions. 

The High Temperature Test at 47' F shall be 

conducted at an outdoor dry-bulb 

temperature of 47° F and an outdoor wet-bulb 

temperature at 43' F_ The High Temperature 

Test at 62' F shall be conducted at an outdoor 

dry-bulb temperature of 62° F and an outdoor 

wet-bulb temperature of 56.5° F. For both 

tests, the dry-bulb air temperature entering 

and surrounding the indoor portion of the unit 

shall be 70' F and a maximum wet-bulb 

temperature of 80' F. The duration of the tests 

shall be for a minimum of 'h hour. 

3.2.1.2 Cycling test conditions. The 

Cycling Test at 47' F shall be conducted at 

the same dry-bulb and wet-bulb temperature 

as the High Temperature Test at 47' F as 

described in 3.2.1.1. During the Cycling Test, 

the indoor fan shall cycle "on" and "off' as 

the compressor cycles "on" and "off', except 

that the indoor fan cycling times may be 

delayed due to controls that are normally 

installed with the unit. The compressor 

cycling times shall be 6 minutes "On" and 24 

minutes "off." The test installation shall be 

designed such that there will be no airflow 

through the indoor unit due to natural or 

forced convection while the indoor fan is 

"off." This shall be accomplished by 

installing automatic dampers upstream and 

downstream of t'le test unit to block the off 

period airflow. 

3.2.1.3 Frast accumulatioIl test conditions. 

The dry-bulb temperature and dew-point 

temperature of the air entering the outdoor 

portion of the unit shall be 35' F and 30' F 

respectively. The indoor dry-bulb 

temperature shall be 70° F and the maximum 

indoor wet-bulb temperature shall be 80' F. 

The Frost Accumulation Test requires that 

the unit undergo a defrost prior to the actual 

test. The test then begins at defrost 

termination and ends at the next defrost 

termination. Defrost termination occurs when 

the controls normally installed within the unit 

are actuated to cause it to change defrost 

operation to normal heating operation. During 

the test. auxiliary resistance heaters shall not 

be employed during either the heating or 

defrost portion of the test. 

3.2.1.4 Low temperature test conditions. 

The tow Temperature Test shall be 

conducted at a dry-bulb temperature entering 

the outdoor portion of the unit of 17' F and a 

wet-bulb temperature of 15' F. The air 

entering the indoor portion of the unit shall 

have a dry-bulb temperature of 70° F and a 

maximum wet-bulb temperature of 80' F. 

3.2.1.5 Additional testing conditions. All 

tests shall be conducted at the indoor-side air 

quantities specified in Sections 5.1.4.3 and 

5.1.4.6 and Table 2 of ARI Standard- 240-77. 

The following conditions listed in ARI 

Standard 240-77 shall apply to all tests 

performed in Section 3.2 of this Appendix: 

5.4.4.4 Outdoor-Side Air Quantity: and 

5.1.4.5 Requirements for Separated 

Assemblies. 

In all tests. the specified dry-bulb 

temperature entering the outdoor portion of 

the unit also applies to the air temperature 

surrounding the outdoor portion of the unit. 

Similarly, models where portions are 
CAS-RM-79-102 COMMENT 01

23478 ,Federal Register / Vol. 44, No. 77 / Thursday, April 19, 1979 / Proposed Rules 

intended tobe installed indoors shall have 

the airtemperature surroundingtbat poriton 

of the rmit. the same as the indoor air 

temperature. ~ . 

3.2.2 Testing conditions/or units with two 

speed compressors, two compressors or 

qylinder unloading. The testing conditions for 

two speed compressors, two compressors, or 

cylinder unloading shall be the same as those 

for single speed units,as described in 3.2.1. 

3.3 Testing'coJiditions for air source units 

which provide both heating and cooling. The 

testing conditions fOfunits which provide 

, ,both heating and cooling shall be the,same as 

the requirements in Sections 3.1 and 3.2 of 

this Appendix;,' 

3:4 Testing conditions for water source 

units which pravide both heating and cooling. 

The test to'om requirements and equipment 

installation...procedures are the same as those 

specified in Sections 11.1 and 11.2 of 

ASHRAE Standard 37-69. All tests shall be 

performed at the normal residential voltage 

and frequency for which the equipment is 

designed (either 115 or 230 volts and 60 

hertz). 

'3.4;1 Cuolingtesting conditions for units 

with single speed compressors. Test E and 

_ test F shatl be performed with the air entering 

the indoor'side of the unit having a dry-bulb 

temperature of BO° F and a wet-bulb 

temperature of 67°F. The water temperature 

entering the refrigerant-to-water heat 

exchanger on the outdoor side of the rmit 

shall be 85° F for test E and 60° F for test F. 

The water tliinperature leaving the 

refrigeranHo-water heat exchanger on the 

outdoor side of the unit shall be 95° F in test 

E. For test F, the temperature shall be one 

which corresponds to the same flow rate as 

determined'in test E. The temperature of the 

air surrounding the unit in each test shall be 

BOO F. 

3.4.2 Heating testing conditions for units 

with single speed compressors. Test G and 

test H /lhall be 'performed with the air 

enteriIlg the indoor side of the unit having a 

dry bulb temperature of 70° F and a maximum 

wet bulb temperature of 60° F. The water 

temperature entering the refrigerant-to-water 

heat exchanger on the outdoor side of the 

unit shall be 80' F for test G and 60' F for test 

H. The water flow rate shall be the same as 

determined from test E and F in 3.1.1 of this 

Appendix. The temperature surrounding the 

unit in each test shall be 70' F. 

3.4.3 Cooling testing conditions for single 

speed compressor units capable of 

lI/odulating water and refrigerant flow to 

maintiJin constant capacity. The same 

conditions as detailed in 3.4.1 shall apply 

except that no constraint shall be placed on 

the outlet, water temperature leaving the 

refrigerant-to-water heat exchanger in test E 

and test F. 

,3.4.4 Heating testing conditions for single 

speed compressor units capable of 

modulating water and'refrigerant flow to 

maintain constant capacity. Test G and test 

H shall be performed with the air entering the 

indoor side of the unit having a dry-bulb 

temperature of 70' F and a maximum wetbulb temperature of 60' F. The water 

temperature entering the refrigerant-to-water 

heat exchanger on the outdoor side of the 

unit shall be 80° F with test G and 60' F for 

test H. The water flow rate shall be 

determined by the controls set by the 

manufacturer. The_control shall not be 

adjusted between the tests on the cooling 

performance and the test on lhe heating 

performance. 

4.0 Testing procedures. Measure all 

electrical inputs as described in the 

procedures below. All electrical 

measurements shall include auxiliary power 

or energy (controls, transformers, crankcase 

heaters, etc.) delivered to the unit. 

4.1 Testing procedures for air source 

cooling only units with single speed 

compressors, two-speed compressors, two 

compressors, or cylinder unloading. All 

steady-state wet- and dry-coil performance 

tests on single package units shall 

simultaneously employ the Air-Enthalpy 

Method (Section 3 of ASHRAE Standard 37-

69) on the indoor side and one other method 

consisting of either the Air-Enthalpy Method 

or the Compressor Calibration Method 

{Section 40f ASHRAE Standard 37-69) on the 

outdoor side. All steady-state wet- and drycoil performance tests on split systems shall 

simultaneously employ the Air-Enthalpy 

Method or the Compressor Calibration 

Method on the indoor side and the AirEnthalpy Method, the Compressor 

Calibration Method, or the Volatile 

Refrigerant Flow Method (Section 5 of 

ASHRAE Standard 37-69) on the outside. All 

cyclic dry-coil performance tests shall 

employ the Air-Enthalpy Method, indoor side 

only. The values calculated from the two test 

methods must agree within 6 percent in order 

to constitute a valid test. Only the results 

from the Air-Enthalpy Method on the indoor 

side shall be used in the calculations in 

Section 5.1. Units shall be installe'd and 

tested in such a manner that when operated 

under steady-state conditions, the cooling 

coil and condenser coil air flows meet the 

requirements of Sections 5.1.4.3, 5.1.4.4, and 

5.1.4.6 of Standard 210-75. 

4.1.1 Test operating procedures. 

4.1.1.1 Steady-state wet-coil performance 

tests (Test A and Test B), Steady-state wetcoil performance tests [A and B) shall be 

conducted in accordance with the conditions 

described in sections 3.1.1.1, 3.1.2. 3.1.3, 3.1.4, 

and 3.1.5 of this Appendix and the procedures 

described for cooling tests in Section 11.3 of 

ASHRAE Standard 37-69 and evaluated in 

accordance with the cooling-related 

requirements of Section 12 of the ASHRAE 

Standard 37-69. The test room reconditioning 

apparatus-and the equipment under test shall 

be operated until equilibrium conditions are 

attained. 

4.1.1.2 Steady-state and cyclic dry-coil 

performance tests (Test C and Test D). The 

steady-state and cyclic dry-coil tests (C and 

D) shall be conducted as described below in 

accordance with the conditions described in 

sectibns3.1.1.2, 3.1.2, 3.1.3,3.104, and 3.1.5 of 

this Appendix. The results shall be evaluated 

in accordance with the cooling related 

requirements of Sections 12.1.5, 12.1.6, 12.1.7, 

of ASHRAE Standard 37-69. The test room 

reconditioning apparatus and the equipment 

under test shall be operated until equilibrium 

conditions are attained, but not for less than 

one houi' before data for test C are recorded. 

For all equipment test methods including the 

Comptessor Calibration Method, testC shall 

be performed with data recorded at 10-

minute intervals until four consecutive sets of 

readings are attained with the tolerance 

prescribed in Section 11.6 of ASHRAE 

Standard 37-69. When the Afr-Entlialpy 

Method is used on the outdoor side for test C, 

the requirements of this section shall apply to 

both the preliminary test and the regular 

equipment test; the requirements of Section 

3.6 of ASHRAE Standard 37~9 shall also 

apply. Immediately after test C is completed, 

the test unit shall be manually cycled "ofP' 

and "on" using the time periods from 3.1.1 of 

this Appendix rmtil steadily repeating 

ambient conditions are again achieved in 

both the indoor and outdoor test chambers, 

but for not less than 2 complete "ofP'I"an" 

cycles. Without Ii break in the cycling 

pattern, the rmit shall be run through an 

additional "off'/"on" cycle during which the 

test data required in 5.1 shall be recorded. 

During this last cycle, which is referred to as 

the tllsl cycle, the indoor and outdoor test 

room ambient conditions shall remain within 

the tolerances specified in 4.1.3 of this 

Appendix during the cyclic dry-coil tests, all 

air moving equipment on the condenser side 

shall cycle "on" and "ofP' when the 

compressor cycles "on" and "ofP'. The indoor 

air moving equipment shall also cycle "ofP' 

as governed by any automatic controls 

normally installed with the unit. This last 

requirement applies to units having an indo'or 

fan time,.delay. Units not supplied with an 

indoor fan time delay shall have the indoor 

air moving equipment cycle "on" and "ofP' as 

the compressor cycles "on" and "off." 

4.1.2 Test instrumentation. The steadystate and cyclic performance tests shall have 

the same requirements pertaining to 

instrumentation and data as those specified 

in Section 10 and Table II of ASHRAE 

Standard 37-69. For the cyclic dry-coil 

performance tests, the dry-bulb temperature 

of the air entering and leaving the cooling 

coil, or the difference between these two drybulb temperatures, shall be continuously 

recorded with instrumentation accurate to 

within ± 0.3' ,F of indicated value and have a 

response time of 2.5 seconds or less. 

Response time in the time required for the 

instrumentation to obtain 63 percent of the 

final steady-state temperature difference 

when subjected to a step change in 

temperature difference of 15' F or more. 

Electrical measurement devices (watt-hour 

meters) used during all tests shall be accurate 

to within ± 0.5 percent of indicated value. 

4.1.3 Test tolerances. All steady-state 

w~t- and dry-coil performance tests shall be 

performed within the applicable operating 

and test condition tolerances specified in 

Section 11.6 and Table III of ASHRAE 

Standard 37-69. 

4:1.3.1 The indoor a~d outdoor average 

dry-bulb temperature for the cyclic dry coil 

test D shall both be within 1.0' F of the indoor 

and outdoor average dry bulb temperature for 

the steady-state dry coil test C. 

4.1.3.2 The test· condition and test 

operating tolerances for conducting test Dare 

stated in 6.1.1 of this Appendix. Variation in 
CAS-RM-79-102 COMMENT 01

IF<edre~@lll lRregi£jae~ ! 'if 01. 44, No. 77 { Thursday, April 1il. 1979 I lProposed lRules 

the tres! conditions than the tolerance6 

inll.l.l this-Appendix ahaH 

the test. It is suggested that an 

,,!ectricresistance heater having a equal to the sum 

co:m.pres,sOl: and 

i.nstalled in 

"'oft" arl€ll 

and "off' 

control in the mltcioot 

an electric resistam;e 

a heating capacHy 

to the cooling 

ins tal!ed in the 

"on" and "off" al? the 

test unit cycles and "off' to hnprovB 

indoor room control. 

4.2 Testing procedures for air source 

heating only units with single speed 

compre.ssors, two-speed compressors, two 

compressors, or cylinder unloading. 

4.2.1. Test operating procedures. All High 

Temperature Tests. the Cyclic Test, the Frost 

Accumulation Test. and the LmN 

Temperature test shall have the perfonnance 

evaluated the Air-Enthalpy Method em the 

indoor side. addition, the High 

Temperature Test and the Low Temperature 

Test shall have a simultaneous test method 

(as described in 4.1) used as 8 check. The 

values calculated from the two methods must 

agree within I) percent in order to constitute ill 

v8lid test. Only the results from the AirEnthalpy Method on the indoor side shall be 

used.in the calculations in section 5.2, 

4.2.1.1 Test procedure for high 

temperature test. When the outdoor Air--

Enthalpy Method isused. the outdoor 

chamber must not interfere with the norm81 

air circulating pattern during the preliminary 

test. It is necessary to determine and adjust 

for system resistance when the outdoor air 

measuring apparatus is attached to the 

outdoor portion of the unit. The test room 

apparatus and test units must he operated for 

al least one hour with at least '!z hour at 

equilibrium and a t the specified lest 

conditions prior to starting the test. The High 

Temperature Test shall then he conducted for 

iii munimum of ¥2 hour with intermil!ent data 

being recorded at 10-minute intervals. For all 

units, especially those having controls which 

periodically cause the unit to operate in 

defrosl mode. attention should be given to 

prevent defrost during the High Temperature 

Test. Units which have undergone a defrost 

should operate in the heating mode for at 

least 10-minutes after defrost temination prior 

to the start of the test. When the outdoor AirEnthalpy Method is used as a second test. 

then a preliminary test must be conducted for 

a minimum of 30 minutes with 4 or more sets 

of data recorded at 10 minute intervals, all 

remaining requirements of Section 3.6.1 in the 

ASHRAE Standard 37-69 shall then apply in 

conducting the preliminary lest for the 

outdoor air enthalpy method. For some units. 

at the ambient condition of the teet, frost may 

accumulate on the outdoor coil. if the 

air temperature or the difference between 

supply air temperature and the indoor air 

entering temperature has decreased by more 

than 1.5" F at the end of the test, the unit shaii 

be defrosted and the les! restarted. Only the 

resulis of ihis second High Temperature Test 

the heating seasonal 

O"l1rnrman,p''' "".,,'"'''''''''' in section 5.2. mol!' 

beginnulg the High Temperature Test. a 

in the mode for at 

after defrost termination to 

establish equilibrium conditions for the unH 

and the room reconditioniP..g The T •• ml,pf·"h"p Test when 

test and room are within 

the test condition tolerances 1.n 

Section 1l.2.1 of this Appendix. 

4.2.1.2 Test procedures for the cyclic test. 

The cyclic test shall follow the High 

Tesland be cycled "on" and 

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 2 cOlnpl'ete 

"off'/"on" cycles. Without a break in 

cycling pattern. the unit shall be operated 

through all additional "off' /"on" cycle, 

which the required test data shall be 

rp"nrn",i During the last cycle. which is 

referred to as the test cycle. the indoor and 

outdoor test room ambient conditions shall 

remain within the tolerance specified in 

section 1l.2.2. of this Apendix. If. prior to the 

High Temperature Test. the unit underwent iii 

defrost cycle to rid the outdoor coil of 

accumulated frost. then prior to cycling 

unit "off' and "on" it should be made to 

undergo a defrost. After defrost is compeleted 

and before starting the cycling process. the 

unit shall be operated continuously in the 

heating mode for at least 10 minutes to assure 

that equilibrium conditions have again been 

established for the unit and the room 

conditioning apparatus. Cycling the unit may 

begin when the test unit and room conditions 

are within the High Temperature Test 

condition tolerances specified in section 6.2.1 

of this Appendix. Attention should be given 

to prevent defrost after the cycling process 

has begun. 

4.2.1.3 Test procedures for tbe frost 

accumulation test. The defrost controls shall 

be set at the normal settings which most 

typify those encountered in Region IV as 

described in section 6.2.4 and 6.2.5 of this 

Appendix. The test room reconditioning 

equipment and the unit under test shall be 

operated for at least % hour prior to the start 

of a "preliminary" test period. The 

preliminary test period and the test period 

itself are to be conducted within the test 

tolerances given in section 4.2.3.3 of this 

Appendix. In some cases. the preliminary 

defrost cycle may be manually induced. 

however, it is important that the normally 

operating controls govern the defrost 

termination in all cases. For units containing 

defrost controls which are likely to cause 

defrost at intervals less than one hour when 

the unit is operating at the required test 

conditions, the preliminary test period shall 

start a t the termina lion of a defrost cycle 

which aulomatically occurs and shall end at 

the termination of the next automatically 

occuring defrost cycle. For units containing 

defrost controls which are likely to cause 

defrost at intervals exceeding one hour when 

operating at the required test condition. the 

preliminary test period consists of "heatingonly" preliminary operation for at least one 

hour, after which a defrosl may be ""HI'!''''} 

autornaltlC!ilIy induced, The ~e:st 

at termination of defrost 

ends at the termination of the next 

aumr[Ja'QlC~Ul~ occurring defrost cycle, llf the 

unit has not undergone II defrost after 12 

hours, then the tests shall be concluded and 

the results calculated for this 12-hour 

For units which tum the indoor flln 

defrost. the indoor supply duct shall be 

blocked during all defrost cycles to provent 

natural or forced convection through the 

indoor unit. During defrost. resistance heater§ 

normally installed with the unit shall be 

prevented from operating, 

4.2.1.4 Test procedures for the low 

temperature test. Where applicable. the High 

Temperature Test preparation and 

performance requirements shall also be used 

in the Low Temperature Test. 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. It is important that the 

nnit terminate the defrost sequence by the 

action of its own defrost controls. The defrost 

controls are to remain at the same setting as 

specified in 4.2.1.3. At a time" no earlier than 

10 minutes after defrost termination. the test 

shall start. Test duration is one-half hour. For 

all units. defrost should be prevented during 

the one-half hour test period. 

4.2.2 Test instrumentation. 

4.2.2.1 Test instrumentation for the high 

temperature test: The indoor air flow rale 

shall be determined as described in Section 

7.1 through 7.4 of ASHRAE Standard 37-69. 

This requires the construction of an air 

receiving chamber and discharge chamber 

separated by partition in which one or more 

nozzles are located. The receiving chamber)B 

connected to the indoor air discharge "side of 

the test specimen through a short plenum. 

The exhaust side of the air flow rate 

measuring device contains an exhaust fan 

with some means to vary its capacity to 

obtain the desired external resistance to air 

flow rate. The exhaust side is then left open 

to the test room or is ducted through II " 

conditioning apparatus and then back to the 

test specimen inlet. The static pressure 

across the nozzles. the veolcity pressure. and 

the static pressure measurements at the 

nozzle throat shall be measured with 

manometers which will result in errors which 

are no greater than ±1.0 percent of indicated 

value and having minimum scale divisions 

not exceeding 2.0 percent of the reading. 

Static pressure and temperature 

measurements must be taken at the nozzle 

throat in order to obtain density of the air. 

The areas of the nozzles shall be determined 

by measuring their diameter with an error no 

greater than ±O.2 percent in four places 

approximately 45 degrees apart. around the 

nozzle in each of two places through the 

nozzle throat. one at the outlets and the 

others in the straight section near the radius. 

The energy usage of the compressor. indoor 

and outdoor fan. and all other equipment 

components shall be measured with a walthour meter which is accurate to within ±0.5 ' 

percent of the quantity measured. 

Measurements of the air temperature entering 
CAS-RM-79-102 COMMENT 01

23480 Federal Register I Vol.. 44, No. 77 I Thursday. April 19, 1979 I Proposed Rule's 

and leaving the indoor coifor the difference 

between these two shall be made in 

accordance with the requirements of 

ASJ-IRi\,E Standard 41 part 1. These 

temperatures shall be continuously recorded 

with instrumentation having a total system 

accuracy within ±O.39F of indicated value 

arid a response time of 2.5 seconds or less. 

Temperature measurements are to be made 

upstream of the static pressure tap on the 

inlet and downstream of the static pressure 

taps on the outlet. The indoor and outdoor 

dry-bulb temperatures shall be continuously 

recorded with instrumentation which will 

resultin an error no greater than ±0.3"F of 

indicated value. The outdoor wet-bulb 

temperature shall be continuously recorded. 

Static pressure measurements in the ducts 

and across the unit shall be continuously 

recorded. Static pressure measurements in 

the ducts and across the unit shall be made in 

accordance with Section 8 of ASHRAE 

Standard 37-69 using a manometer which will 

result in an error no greater than ±0.01 inch 

of water. All other data not continuously 

recorded shall be recorded at 10 minute 

intervals. 

4.2.2.2 Test instrumentation for the 

cycling test. The air flow rate during the onperiod of the Cyclic Test shall be ~e same 

agree within ±1. percent} as the air flow rate 

measured during the previously conducted 

Hiah Temperature Test. All other 

in:trumentatioil requirements are identical to 

4.2.2.1 of this Appendix. 

4.2.2.3 Test instrumentation for the frost 

accumulation test. The air flow rate for the 

Frost Accumulation Test shall be the same as 

described in 4.2.2.1. The indoor-side dry-bulb 

temperature and outdoor-side dry-bulb 

temperature shall be continuously recorded 

with ins'trumentation having a total system 

accuracy within ±O:3"F of indicated value. 

The outdoor dew point temperature shall be 

measured with an error no greater than 

±OSF of indicated value using continuously 

recording instrumentation. ,All other data 

shall be continuously recorded at 10 minute 

intervals during the heating cycle. Defrost 

initiation. termination and complete test 

cycle time (from defrost termination to 

defrost termination) shall be recorded. 

Defrost,initiation is defined as the actuation 

[either automatically or manually) of the 

controls normally installed with the unit 

which cause itto alter its normal heating 

operation in order to eliminate possible 

accumulations of frost on the outdoor coil. 

Defrost termination occurs when the controls 

normally within the unit are actuated to 

change from defrost operation to normal 

heating operation. Provisions should be made 

so that instrumentation is capable of 

recording the cooling done during defrost as 

well as the total electrical energy usage 

during defros.1. These data and the 

continuously recorded data need be the only 

data obtained during defrost. 

4.2.2.4 Test instrumentation for the Jaw 

temperature test. Instrumentation for the Low 

Temperature Test is identical to that of the 

High Temperature Test described in section 

4.2.2.1 of this Appendix. 

4.2.3 Test tolerances. 

4.2.3.1 Test tolerances for the 

temperature test. All tests shall be conducted 

within the tolerances specified in Section 

6.2.1. Variation greater than those given shall 

invalidate the test. The heating 

results by the indoor Air Enthalpy 

shall agree within 6 percent of the value 

determined by any other simultaneously 

conducted capacity test in order for the test 

to be valid, 

4.2.3.2 Test tolerances for the cyclic test. 

The test condition toleran~es and test 

operating tolerances for the on-period portion 

of the test cycle are specified in Section 6,2.2. 

Variation exceeding any specified test 

tolerance shall invalidate the test results. 

4.2.3.3 Test tolerances for the frost 

accumulation test. Test condition and test 

operating tolerances for Frost Accumulation 

Tests are specified in Section 6.2.3. Test 

operating tolerances during heating applies 

when the unit is in the heating mode. except 

for the first 5 minutes after the termination of 

a defrost cycle. Test operating tolerance 

during defrost applies during a defrost cycle 

and during the first 5 minutes after defrost 

termination when the unit is operating in the 

heating mode. In determining whether the 

test condition tolerances are met, only the 

heating portion of the test period shall be 

used in calculating the average values. 

Variations exceeding the tolerances 

presented in Section 6.2.3 shall invalidate the 

test. 

4.2.3.4 Test tolerances for the low 

temperature test. During the test period for 

the Low Temperature Test, the operating 

conditions shall be within the tolerances 

specified in Section 6.2.1 of this Appendix. 

4.3 Testing procedures for air source 

units which provide both heating and cooling. 

The testing procedures for units which 

provide both hea ting and cooling shall be the 

same as those specified in Section 4.1 and 4.2 

of this Appendix. Also during the off-period 

of the dry-coil cooling test (test D). the 

switch-over valve shall remain in the cooling 

mode. unless the controls normally supplied 

with the unit are designed to reverse it. in 

which case the controls shall operate the 

valve. During the off-period of the cyclic 

heating test at 47'F. the switch-over valve 

shall remain in the heating mode, unless the 

controls normally supplied with the unit are 

designed to reverse it. in which case the 

controls shall operate the valve. 

4.4 Testing procedures for water source 

units which provide both heating and cooling. 

All steady-state heating and cooling 

performance tests on units shall 

Simultaneously employ the Air Enthalpy 

Method [Section 6 of ASHRAE Standard 37-

69) on the outdoor side. 

4.4.1 Test operating procedures. All 

heating and cooling performance tests shall 

be conducted in accordance with the 

procedures in Section 11 of ASHRAE 

Standard 37-69 and evaluated in accordance 

with the related requirements of Section 6 

and 12 of ASHRAE Standard 37-69. 

4.4.2 Test instrumentation. The heating 

and cooling performance tests shall have the 

same requirements pertaining to 

instrumentation and data as those specified 

inSeclion 10 and Table II of ASHRAE 

££ ,m71 

Standard 37-6.9. Units shall be installed and 

tested in soch a manner that when operated 

d~"ltlv-':t"i!" conditions, the cooling 

condemser air flows meet the 

of Sections 5,1.'1.3 and 5,1.4.5 

Standard 32G-7ft 

4.4.3 Test tolerances, AU 

r.n~fn"~~n,r" tests shall be "PFlllnll"'!! 

within applicable operating 

condition tolerances specified in Section 11.6 

and Table In of ASHRAE Siandard 37-00, 

n.O Caicujatjons for performance factors. 

5.1 CalcuJaUons of cooling seasonal 

peliormance factars (CSPF) and seasonal 

energy effjciencJi raUos (SEER) in air-source 

units. 

The testing data and results required for 

these calculations shall include the following: 

(i) Cooling capacities (Btu/hr) from tests A 

and B and, if applicable, the cooling capacity 

(Btu/hr) from test C and the total cooling 

done from test D (Btu·s). 

Oss" (95F) Ossk [82F) 

Os., dry 

Qcyc, dry 

(il) Electrical power input to all 

components and controls (watts] from tests 

A, B. and if applicable the electrical power 

input to all components and controls (watts) 

from testC and the electrical usage (walthour) from test D. 

~ .. k [95F) 

E .. k (82F) 

Essk, dry 

E.".co dry 

[iii) Indoor air flow rate (SCFM) and 

external resistance to indoor air flow (inches 

of water). 

(iv) Air temperature (oF) 

Outdoor dry bulb 

Outdoor wet bulb 

Indoor dry bulb 

Indoor wet bulb 

Where the cooling capacities Q .. k [95FJ. 

from test A. Qssk (82), from test B. and 0 .. , dry. from test C. are calculated using the 

equations specified in section 3.7 of ASliRAE 

Standard 37-69. The total cooling done. Qcyc' 

dry from test D. is calculated using equation 

(lJ below. 

Units which do not have indoor air 

drculating fans furnished as part of the 

model shall have their measured total cooling 

capacities adjusted by subtracting 1250 Btu/ 

hr per 1.000 CFM of measured indoor air flow 

and adding to the total steady-state electrical 

power input 365 watts per 1.000 CFM of 

measured indoor air flow. . 

~ Energy efficiency ratios from tests A. B, 

and C. EERA• EERs, and EER. •. dry 

respectively. are each calculated as the ratio 

of the total cooling capacity in Btu/hr to the 

total electrical power input in watts. 

Units which do not have indoor air 

circulating fans furnished as part of the 

model shall adjust their total cooling done 

and energy used in one complete cycle for the 

effect of circulating indoor air equipment 

power. The value to be used for the 

circulating indoor air equipment power shall 

be 1250 Btu/hr per 1.000 CFM of Circulating 

indoor air. The energy usage required in one 

complete cycle required for indoor air 

circulation is the product of the circulating 
CAS-RM-79-102 COMMENT 01

uv 

indoor air equipment 

of time in one cycle 

indoor air """l"fJ'"'''''' 

done shall 

test cycle. 

federal IRegEster. ! Vol. 44. No. 77 I Thursday, April 19. 1979 I Proposed Rules 

efficiency ratio from. D, ElEl'-o,c, 

dfv is as the ratio of total 

co"oliag done in Btu's to the total el.ectrical 

energy usage in 1NaH-llOur,~, 

1!l!IiLlUltiG CODE M5tHll-i!11 

23481 
CAS-RM-79-102 COMMENT 01 

Federal Register I Vol. 44. No. 77 I Thursday, April 19, 1979 I Proposed Rules 

The results of the cyclic ?rrl ~·p·~~-sttte dry-coil 

performance tests shell bfi! llSI'" ;P the fo11o\<,;ng (11) eauations: 

(l) 

where 

60 x T x Cpa x 

Cleye ; dry'" [V n • x (1 + \4 n)] 

Ocyc,dry 

v 

Cpa 

V n' 

., Total con1 in" ever 1:. ctcl" cO'isi5tin'1 01' one 

compressor "~ff· period and on~ comnressor 

"on" aerior (Rtu'sl 

Indr:'or eir ~lr\" rate (cf!) at the dry-bulb 

temperature. humidity ratio. and pressure existing in the reninn 0f ~easure~ent. 

• 5necific heat !t constant rressure of airwater mixture ner nrund nf dr· t air, 

(Btu/lb-°F). 

" Specific voluJ11e of air-,,'atPr r~;y.ture at 

the same dry-bulb tf"-'-,ril.~ure. humidity ratio. and '1rf'SS'IrE' used in the determinati0n rf '::\(' i'ldrnr ~ir ~10'" rilte 

(ft3/lb). 

1;1 " Humidity ratio (lb/lb). 

and r ~hr.-OF), which is described by the equation: 

(2) 

where 

Tal (t) 

Ta2 (t) 

((time indoor fan off) 

r "J (lhfle indoor fan on) 

" Dry bulb tem~ercture of air enterin" tJ-.o 

indoor coil (l'F) :ot time (t). 

" Dry-bulb ter.~0roture of air leavin~ the 

indoor coil (oF) at time (t). 

(3) 

where 

ClF 

QCYC, dry 

elF" Qss dry x T 

: cooling load factor. 

Qss dry = Total steady-state coolinq capacity from 

test C (Btu/hr). 

= Duration cf time (hours) for one completa 

cycle cnnsistino of one compressor "on" 

ti!"e ilnrl or~ cnmDres~or "off" time. 

The oroceding equatiors a\"~ then us~r\ in the followinq 

equatlon to calculate a degradation coefficient CD rounded 

to the nearest .01. . 

(4) 

1 _ EERcyc,dry 

EERss,rlry 

1 - ClF 

where 

EERss,dry= Energy efficiency rat;('l froPl ~est r, 

(Btu/watt-hr) • 
CAS-RM-79-102 COMMENT 01 

federal Register I Vol. 44. No. 77 I Thursday. April 19. 1979 I Proposed "Rules 

Calculate the cooling seasonal performance factor (CSPFl 

for air source central air conditioner or heat pump. 

where: 

SEER 

3.413 

SEER 

CSPF .. 3.413 

the seasonal energy efficiency ratio as determined 

in section 5.1.1. 5.1.2. 5.1.3. or 5.1.4 below. 

a conversion factor which converts watt-hours 

to Btu·s. 

5.1.1 ~ethod f,r calcu1utinn > SErR for units with 

single-speed comnressor and sinr.1e ~n~ed condenser fans. 

The seasonal energy efficiency ratio for units employin!) 

single-speed compressors and single-speed condenser 

fans shall be based on the performance of te~t B and a 

method outlined in 2.1.1 and 3.1.1 of this Arnendix to account 

for the cyclic performance. 

The seasonal energy efficiency ratio in Btu's/Vlatt-hou~ 

shall be determined by the equation: 

where 

where 

SEER = PLF (0.5) X EERS 

EERB Energy efficiency ratio determined fro~ 

test C as oQt1ined in 2.1.1 

PLF(O.5)= Part-load performance factor determined 

from the equction: 

PlF (0.5) = 1 - Co (1-n.3) 

= Is the degradation coefficient described 

in 2.1.1 or as calculated in e0uation (4) 

above 

5.1.2 'lethod for calculating a SEER for units with sing1e- speed compressors and multi-speed condenser fans. -he 

seasonal energy efficiency ratio (SEER) for units e~nloying 

single-speed compressors and multi-saeed condenser "~ns 

shall be based on the energy efficiency ratio obtained for 

test B and the method outlined in 2.1.2 of this Apnpndix to 

account for the performance under cyc1 ic condition!". The 

energy efficiency ratio for test B is obtained witr. tOle unit 

operating with the condenser fan speed which nOrMal'" occurs 

at test B ambient conditions. 

The seasonal energy efficiency ratio i!' Ptu'sf"att-hour 

shall be determined by" the equation: 

where 

SEER = PlF (0.5) X EERr, 

erpr" .. e"ficiency ratio determined from tp~': f>. in 2.8 

Part-load performance factor as determined from the equation: 

~Lf ,U.b) = I - LO (I - 0.5) 
CAS-RM-79-102 COMMENT 01 

23484 Federal Register I Vol. 44. No:77 I Thursday. April 19. 1979 I Proposed Rules 

where 

The desrad~tion co~fficient described in 

2.1.2 or as calculated in enuation (4) 

above. 

5.1.3 tlethod for calculatinq a SE":P. fer units ~Iith t,·'o 

speed compressors or blo compressors, or cyl i nder 

unloadinq. The calculation orocedure described in this 

section shall be based on the performance of test fl, and B 

at each of the compressor soeeds for two-speed compressor 

units, subject to the conditions on condenser fan sneed 

described in 3.1.3. . 

Units operating with two compressors shall have the 

SEER calculated in the same manner as two-speed compressor 

units. The superscripted index k=l, (and the term 

"low-speed") designates the compressor that normally 

operates at an outdoor dry-bulb temperature of 820 F 

and k=2 (and the term "hioh snee{''') denotes o~eration 

with both compressors. ' 

In order to evaluate the steady-statecaoacity 

Qssk(Tj), and power input, E"ssk(Tj)' at tel'1perature 

Tj for each comoressor speed, k=l, k=2, the results 

of tests A and B from 5.1 shall be used in the followinq equation: . 

Qssk (Tj) = Qssk (95 F) 

where 

+ 0ss k(82 F) - Qssk(95 F) 

95 - 82 [33-(5 X j)] 

Steady-state capacity measured from t~st A as outlined in 2.1.3. 

Steady-state capacity measurep frnm 

test B as outlined in 2.1.~. 

EsSk(Tj) ~ ~k(95 F) 

+ Essk(82 F} - Essk(95 F) [33 _ (5 X i)] 

95 - 82 

vlhen 

Electrical power input measurpd usinq 

test A as outlined in 2.1.3. 

= Electrical power input measured from 

using test A as outlined in 2.1.3. 

The building coolino load .• Bl(Ti) for the four cases 

descri bed in secti on 5.1. 3.1 through 5.1. 3.4 s ha 11 be obta i ned 

from the following equation: 

)'Ihere 

(5Xj) - 3 

-= 95 - 65 

Qs~=2 (95 F) 

it 1.1 

= Steady-state capacity measured +ro~ test A 

in 2.9 at the hiqh compressor speed. 

The value of the degradation coefficient CDk=1 for low 

compressor speed cycling and CDk=2 for hiqh s~eed on/off 

compressor cycling is determined as described in section 2.1.3, 

or as calculated above in equation (1). 

5.1.3.1 Units operating at low compressor speed (k=l) for 

which the steady-state cooling capacity, Qssk=l(T,i), is 

greater than or equal to the building cooling load, 

Bl(Tj). evaluate the following equations: 

(1) k=l = Bl(Tj) X Qssk=l(Tj) 

where 

Xk=l 

Bl(T i) 

= Load f;>ct.,r. 

Building cooling load (Btu/hr) at 

temperature (Tj) fro~ section 5.1.3 

Qssk=l(Tj)= Steady-state coolina capacity (Btu/hr) 

at temperatures (Tj) from section 5.1.3. 

I 
CAS-RM-79-102 COMMENT 01 

Federal Register / Vol. 44. No. 77 I Thursday. April 19. 1979 I Proposed Rules 23485 

(2) 'llliJ 

N 

where 

(3) E~T j) 

where 

PlFk=l 

,t=1 X Qsst.' (TI) y nj 

r: 

ratio of total cooling (Stll) in temoerature bin 

to the number of temperature bin hr·lrs. 

is the fract i ona 1 number of hours in temoel'2tur" 

bin j from 6.1.2 

ratio of Energy usage (I',att-hr) in temperature ri n ; t.o tr" "I\~h~~ ~< t"'~~~Y'" t"Y'~ H n hours. 

Where Co the degradation coefficient as described in section 

2.1.3 or as calculated above in equation (1) 

5.1.3.2 Hhen a unit must alternate between hi"h \1:=2) and 

low (k=l) compressor speeds to satisfy the building coolinq 

load at a temperature T5, evaluate the following equati0rs: 

(l) Xk=l QSS k=2(Tj) = BL (Tj) 

Ossk=2(Tj) - 05s k=1(Tj) 

(2) Xk=2 = 1 _ Xk=l 

(3) Q (Tj) 

N 

(4) E(Tj) 

N 

[Xk=' X 0ss

k='(Tj} 

+ Xk"2 X n k=2(T. '1 . "\Iss 'l ... 

X E k=2(T'\ . 55 " 

+ Xk=2 X E

s

-

s

-r.=2(TJ.)] X n· rl 

5.1.3.3 ~Ihen a unit must cycle ('n a!'d /'Iff at hiqh compl'essor 

speed (k=2) in order to satisfy the building coolinq load at 

a temperature Tj, evaluate the equations orovided in section 

5.1.3.1 replacinq (k=l) data with the (k=?) data. 

5.1.3.4 When a unit operates continuously at hioh compressor 

speed.(k=2) at an outdoor temperature Tj evaluate the following equatlons: . 

(1) Q(Tj) 

"1[- "Q ss k=2(T') J X~ N 

(2) E(Tj) = Ess k=2(Tj) X OJ 

N i-C 

5.1.3.5 Calculate the SEER in P.tU'S/V'iltt-'Y'. !Isinl1 t"e 

values for the terms 

and 

as determined at each temperatw'e bin according to the 

applicable conditions described in sections 5.1.3.1 throunh 

5.1.3.4 as follows: 8 

L Q\~j) 

SEER j=l 

8 E(Tj) L 

j=l N 

5.1.4 Method for calculating a SEER for units with two speed compressor, two compressor or cylinder unloading capable of varying 

the sensible to total caoacity (SIT) ratio. Multi-speed compressor 

and two-speed compressor units capable of varying the sensih1e 

to total capacity ratio (SIT) shall have the seasonal energy 

efficiency ratio determined as r.escribed in section 5.1.3. 

For such units. the mode of ooeration selected to determine 

the steady-state capacjties Qssk(95), Ossk(82), Essk(95), 

Ess k(82), and power inputs at each compressor speed k=l, k=2, 

for tests A and B is outlined in section 2.10 
CAS~RM-79-102 COMMENT 01 

23486 Federal Register /Vol. 44. No. 77 / Thursday, April 19. 1979 I Proposed Rules 

5.2 Calculation of H ea t 1.ng Seasonal Performance 

Factors (HSPF) for Air-Sou=ce Units. 

The testing data and results required for these calculations shall include the following: 

(i) Heating capacities (Btu/hr) from the indoor air 

enthalpy method for the High Temperature Tests, and 

the total heating done (Btu's) for the cyclic 

and frost accumulation tests 

Q ss (47) or Q ss (62) 

Q ss (17) 

Q cyc (47) 

Q DEF (35) 

---

Hi) Electrical power input to all components (watts) 

for the steady state tests, and the electrical 

usage (watt-hours) for the cyclic and frost 

accumulation tests 

E 55 (47) or E ss (62) 

E ss (17) 

E cyc (47) 

E DEF (35) 

..... ,. 

(H 

(iv) 

:cor air flow ra te-{SCF:n an? external res istance 

to indoor air flm ... (inches of ·.rater) 

Air temperature (oF) 

Outdoor dry bulb 

Outdoor wet bulb or dew point 

Indoor dry bulb and 

Indoor wet bulb 

(v) Data as specified in Table II of ASHRAE 

Standard 37-69 

Where the heating caoacities 0ss(47), 0ss(62) and 

Qss(17) and the indoor air'flow rate are calculated using 

the equations specified in section 3.8.1 and 7.4 of ASHPAE 

standard 37-69. The total heating done, 0cyc(47) and 

QDEF(35) are calculated using the eauations below. 

Units not havincr an indoor fan as part of the model tested 

shall add 1250 Btu/hr per 1,000 SCFM o~ indoor air handled to 

the measured capacity to obtain the total heating ca~acity, 

. . Qss(17), Qss(47) or Qss(62), and add 365 watts oer 1,000 

SCFM of indoor air handled to the m~asured power to obtain 

the total power input, Ess (17), Ess (47), or ES5 (62), to the 

unit. 

The coefficients of performance (COP) for the High 

Temperature Tests COPss (62) or COPSS (47) , and Low Temperature 
CAS-RM-79-102 COMMENT 01 

Fooeral lRegister ! Vo!' 44. No. 77 I Thursday. April 19. 1979 / Proposed Rules -

Test, COPss (l7), are calculated as the ratio of the heating 

capacity in Btu/hr to the product of 3.413 and ~~e power 

inputs to the indoor fan in watts and the power inputs to 

the remaining equipment oomponents (including all controls) 

in watts. 

Por units which do not have indoor air circulating fans 

furnished as part of the model shall adjust their total heating 

done (Qcyc(47) and energy used £c'1c(471 in one comolete 

cycle for the effect of circulating indoor air equioment 

pmver. For unit£! tested withol,lt an indoor fan as part of 

the model, Qcyc(47) shall be increased by a ~uantity of heat 

equal to the product of 1250 Etu/hr per 1, Ol)O SCFf1, the lengt:. 

of the on-period of the test cycle in hours, and the flow 

rate of indoor air circulated in units of 1,000 SCFM. The 

tot~l energy usage, Ecyc (47), shall be the sum of the energy 

usage required for air circulation during the test cycle and 

the energy used by the remaining equipment components 

(including all controls) during the test cycle. Units not having 

an indoor fan as part of the model tested, shall set the 

energy recruired =or indoor air circulation equal to the 

quanti.ty given by the oroduct of 365 watts oer 1000 SC!"" , 

the length of the on-Deriod of the test c:'c1e in 'lours, and 

the rate or indoor air circula tedl:: uni t3 of 1000 SC!,,~i. 

'C'he cyclic coefficient of performance, COPcyc (47) is 

calculate.a as the ratio o~ the total heating done (Ocyc (47), 

in Btu's to the product of 3.413 Btu/watt-hour and Lhe total 

energy usage (Ecyc (47» in watt hours. 

The net heating capaCity, QDEP(35) (Btu/hrJ, is the t()tal 

net heating done over the test period (including any credit 

for the indoor fan heat) divided by the total length of the 

test period, in hours. For units with "demand defrost control 

system", the net heating capacity, QDEP(35), shall be 

multiplied by an enhancement factor of 1,05 to compensate 

for improved performance not measured in the Prost Accunulation 

Test. For units tested without indoor fans, the vahle 

determined for QDEF(3Sl below shall be increased by a 

quantity of heat equal to the product of 1250 Btu/hr per 

1000 SCF~\, the length of time in hours during the Frost 

Accl,lmulation Test that there was indoor air circ'.llating, and 

the average flow rate, of indoor air ci::cculated in units of 

1000 SCFM. 

The total energy usage, Em::F (351 shall be t.;';!? sum of 

the energy. usage required for indoor-air circulation during 

the test period and the energy used by the remaining eq-ui?1l'en'C 

components during the -test period, t'ni ts not having an 

indoor fan as part of the model tested, shall set ~he energy 

required for indoor air circulat:ion equal to the quantity 

given by the product of 365 watts per 1000 SCI''''. the length 

of time in hours during the ~rost Acc~mulaticn Test that 

there was indoor air circula.ting, and the average f10'\;, rate 

6f indoor air circulated in units of 1000 SCF~, 
CAS-RM-79-102 COMMENT 01 

, 

'23488 Federal Register I Vol. 44, No. 77 I Thursday. Apn119. 1979 I Proposed Rules 

:~ng:h of che :esc period. in hours. 

~~e ac:~al heating cone c~ring the Cyclic Test, 

- .- s.'nall be deter~inee using the followino, ea.uatior.: -=1':. .. I' , 

'1) 

where 

v ,.. the flow rate during the on-~eriod 

Cpa .. 

calculated in accordance with section ;,4 

of ASHRAE Standard 37-69 in CF~ 

S~ecifit heat at cor.stant Dressure of air-

'Iater Mixture per pound of dry air, 

(Btull boO!') , 

" Specific volume of air-vlater l'Iixture at 

the saMe dry-tulb temoerature. huric1ty 

ratiO, and pressure used in t"e :eter-ination 

of the indoor air flew rate (ft3/lb). 

Hum; dity ratio (1 b/l b l. 

and r (hr-OF), which is described by tre equation: 

where 

f (time indoor fan off) 

f'" [-:32(t; - "'"l(t; )dt (time indoor fan on) 

Tal (t) " Dry-bulb terrperature of air enterir9 tre 

indoor coil (OF) at time (t), 

Drv-bulb terrperature of air leavino the 

indoor coil (OF) at til"e (t). 

The net heating, QOEF (35) in Btu's done during the 

test period shall be determined using the following 

equationi 

(2) 

where 

v s the average, of the air flow rate calculated 

at four or more time intervals throughout 

the heating phase of ·the test using the 

equation in section 7.4 of ASHRAE Standard 

17-69 

Specifi~ heat at constant pressure of airwater mlxture per pound of dry air 

(Stull b-oF) • ' 

Specific volume of air-water rnixtllre ,t 

the same dry-bul b tem'ler~turp, hlJm; rli ty 

ratio, and pressure used in ·the determination 

of the indoor air flo., rate (ft3/lb), 

Wn % Humidity ratio (lb/lb). 

and r (hr. _oF), whi ch is descri bed by the equa t ion 

where 

r "'f (time indoor fan off) 

(time indoor fan on) 

I.· 

Dry-bulb temperature of air entering the 

indoor coil (OF) at time (t), 

Dry-bulb temperature of air leavinq the 

indoor coil (OF) at time (t), -
CAS-RM-79-102 COMMENT 01 

Federal Register I Vol. 44. No. 77 I Thursday, April 19. 1979 I Proposed Rules 23489 

(3) ~yc1ic degradation coefficient shall be calculated wheI"e 

where 

as [01101"5, 

1-

COPcYC(47) 

COPss (47) 

HLF 

c ~ the cyclic degradation coefficient rounee D 

to the nearest ,01 

COPcyc (47) as defined abo'"e 

COPss (47) as defined above 

HLF is the heating load factor calculated as 

follows; 

as defined above 

OS5(47) as defined. above 

T ~ Duration of time (hours) for one complete 

cycle consisting of one compressor "on" 

time and oue compressor "off" time, 

5.2,1 calculation of the heating seasonal performance 

factor (HSPF) far air~saurce heat pumps with 

single speed compressors, 

For each climatic region listed in section 6.2.4, and 

for design heating reqUirements equal to both the standardized 

minimum and maximum de$ign hea'.:ing requirements defined below, 

calculate the HSPP defined as: 

HSPf w ----------__________ 4-~ ______ d_ ______________________ ___ 

where 

[

= fl, CL413) Ji;, .....J.. 

N 

RHCfJ)1 :l J 

j 1,2,3, ---, It corresponds to the jth temperature 

bin 

total number of non-zero temperature bins in 

the climatic region 
CAS-RM-79-102 COMMENT 01 

23490 Federal Register I Vol. 44, No. 77 I Thursday, April 19. 1979 I Proposed Rules 

Tj = (67 - 5jl is the representative temperature 

fof the jth bin,'(OF) 

I 

j = indicated the quantity following the symbol 

is to be summed over all temparature bins 

ru!(Tjl supplementary resistance heat term,. ~t 

3.413 

-1'1--

temperature Tj required in those caseswhere the heat pump automatically turns 

off (Tj<Toffl or when it is needed to 

meet,the balance of the building heating 

requirements. (kW) 

~ = is the number of hours in the jth temperature 

1'1 

bin divided by N=I nj and is referred,to as 

the "fractional hours in jth temperature bin" 

is a conversion factor ,.,hich converts 

watt hours to Btu 

building load at temperature Tj! (Btu/hrl 

heat pump low temperature cut-out factor 

"X(Tj) '" heat pump heating load factor 

PLF(X) heat pump part load factot 

are defined by the following equations: 

(

65 - Tj )(C) (DHRl 

65 - TOO 

and 

,,'here 

(el - 0.77 is a correction factor which tends 

to improve the agreement l"etween calculated 

and measured building loads 

(DHR) the minimum and maximum design heating 

where 

where 

requirement which the heat pump is likely. 

to encounter when installed in a residence, 

rounded off to the nearest standardized 

OHR in section 6.26 in kBtu/hr 

(c5-Ton) • 60 ~ for regions ., II, :::, 

IV, ana \"1 

f or reg ion \1 

(65-T ) , • 00 l

2C:SS (47) --6-0-- • for regions 

2.2Qss(47), for region V 

Qss (47) is the heat pump capacity measured 

,during the High Temperature 

Test @ 47°F 

is the outdoor design temperature 

given in, section 6.2.4 

I,. I1 ~ II!, 

IV t a~.d Vl 
CAS-RM-79-102 COMMENT 01 

Federal Register I Vol. 44. No. 77 I Thursday. April 19. 1979 I Proposed Rules 23491 

0(1j

) . 

X(TJ) I 

I'L.(X) • 

RH(T. ) 

--L. 

N 

where 

TOFF .. 

0 1j .! 10FF or Q(TJ

> < 1 

(3.413)(ECTJ» 1 

1 

To' F < Tj .! TON and 

Q(TJ

) 

1. '2 1 

O.413)(i(Tj» 

1 Tj > TON and 

Q(TJ> 

1. 1 

(3.413) (t(Tj

) 

BL(TJ

) 

Q(Tj ) 1. BL(Tj

) Q(Tj

) 

1 Q(T j) .! BL(Tj ) 

[SL(T J) - iHTJ

) XCTJ

) 6(TJ

) ] i :1 

3.413 

the outdoor temperature that the compressor 

is automatically shut off at' (If no such 

temperature exists, T

J 

is always greater 

than TOFF and TON'} 

TON • the outdoor temperature that the compressor 

is automatically turned on (if applicable) 

if designed for low temperature automatic 

shut-off. 

C = deg' radation factor determined described in D 

section 5.2 and 2.2.1 

In using the above equation to calculate HSPF, the heat 

pump capacity in Btu/hr, Q, and the cower in watts, E, shall 

be obtained as follows: 

, (ESS (47) - Ess(17»{!j - 17) 

ESS(17) + 30 ' Tj 1. ~5'F or Tj .! 17-: 

where Oss(47) and Ess(47) and QOEF(35) and Ess (47) and . 

Qss(17) and Ess (17) are the capacities (in Btu/hr) and powers 

(in watts) measured during the High Temoerature Test, the 

Frost Accumulation test, and the Low Temperature 7est, 

respectively, 

\ 
,CAS-RM-79-102 COMMENT 01 

23492 Federal Register I Vol. 44. No. 77 I Thursday. April 19. 1979 I Proposed J 

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. 

5.2.2 Calculation of the heating seasonal performan~e 

factor (RSPF) for air source heat pumps with a 

two-speed compressor. two compressors. or 

cylinder unloading. 

For each climatic region listed in section 6.2.4. 

and for design heating requirements equal to both the 

standardized minimum and maximum design heating requirements 

defined below, calculate the HSPF defined as: 

HSPF 

[ 

.. !CTj) .. RHCT j)] 

(3 4' 3) .. +.. . •• jill II 

where 

.. as defined in 5.2.1 

j 

~ as defined in S.2.1 

N 

3.413 as defined in S.2.1 

T" as defined in S.2.1 

,j BLITj) is the buildinq load at temperature Tj' in 

Btu/hr. calculated by: 

where 

(e) R 0.77 is a correction factor which tend. 

(ORR) 

where 

to improve the agreement between 

calculated and measured building loads 

the minimum and maximum design heating 

requirement which the heat pump is likely 

to encounter when installed in a residence, 

rounded off to the nearest standardized 

OHR in section 6.2.6 in Btu's per hour 

Q (k-Z)C'.7) (65-ToO) 

(~in~um desi~n heating ~equirement) 

\ 

5S 60' for regions I. n. II!. _ tv, and 'l! • (ksZ) QSS (47), for region V 

.and 

(maximum design heating requirement) -\ 

• k-2 (65-TOD) 

20SS (47)--6-0-- • for regions I. II. III, 

1'1, and VI . K*2 2'~'QSS (47) fo1' region V 
CAS-RM-79-102 COMMENT 01 

Federal Register I Vol. 44, No. 77 I Thursday, April 19, 1979 /Proposed Rilles 23493 

Q 

ss (47) is the heat pump capacitj' measured 

during the hiqh temperature performance 

test at 47 o r, with the unit operating 

at the high compressor s~eed or with 

both compressors i.n operation. in 

otu/hr 

is the outdoor design ta~pera~ure 

given in section 6.~.4 in degrees of 

Note: the superscript (k"'l) and (k~2) refer ~.O the heat 

pump operating at. low speed 01: sin91e cpmpressor 

op~ration and high speed or t~o co~pressor 

operation respectivel~. 

is the heat pum? elec~ric~l energy 

tlsage in the ~~ t,~mperature bi~ divided 

by the totaL nurn~er 0~ bin hours and is 

evaluated according to ~he four p0ssibl~ 

cases of heat ?um? operation de~oted 

belOW in watts 

RS (T j 1 as defined in 5.2.1 and is evaluated 

--N--

according to the four possible :ases of 

heat pump operation denoted below. 

(in watts) 

cnits operating at low conpresso; speed or with a sinAte compressor, i.e., 

k,l, for which the building heating load, BL(T j

} 1s less than or equal to 

the heating eapaci'y. Qk=l(Tj). 

oL(t j

) ~ Qk~l(Tj) 

RH(T. ) ---L 

:l 

6' (1 j) 

( 

. t 

E:C'l(Tj

} xk:lcr

j

) S'(Tj

? 

?LFk~l 

0 Tj .!. Ton 

1 <Tj~TON 2 Tor: 

1 T j > TON 
CAS-RM-79-102 COMMENT 01 

23494 Federal Register I .vol. 44, No. 77 I Thursday, April 19, 1979 I Proposed Rules 

Units alternating bet~een high speed or t~o co~pressor opera,ccn (k~2) 

and low speed or single compressor operation (k-1) to satisfy the 

building heating load at temperature Tj 

'k-l( .k=2( ) Q T j ) < BL (T j) < Q T j 

n. -+ BL(T j)[ 1 - 6' (T j) J 

3.413 

\ 

0 T . .: Ton- J 

:'(T .) = t 

TOfF < T. :: To~; J Z J 

T

J > TO'! 

CASE III 

Units cycling on and off at high compressor speed or cycling both 

compressors on and off together (k-2) in order to satisfy the building 

heating load at temperature Tj . 

Qkal(T j> < BL(T j> < Qk.2(Tj

) 

tk"2(Tj) Xk"'2(Tj) ~"(Tj) + 

PLFk' Z 

n. -t BL(Tj)[l 

3.413 

1 

0 Tj ~ TOFf 

"(T ) " 

1 TOFr < T • j j ~ To~ '2 

1. ' T()~ J 

t:nits operating continuously at high compressor speed or ..,ith both 

compressors in continuous operation (k-2) in order to satisfy the buildinl 

heating load at temperature Tj . 
CAS-RM-79-102 COMMENT 01 

Federal Register' Vol. 44, No. 77 / Thursday, April 19, 1979 'Proposed Rules 23495 

, .. (T.) 

J 

- 1.0 

Qk-2 (T ) 

---~jL,,--- < 1 

(j.413)(tkaZ (!j» 

qk=2 (r.) ___ ~JI-__ > 1 

(J.41J)(Ek=2(!.» J 

<?*2(! ) ___ --,..J.j ..,-__ ! 1 

(J .413) (Ek=Z (T j)) 

Where in each of the above cases 

PLF 

heat pump heating load factor 

heat pump part load factor (not 

required for cases II and III 

heat pump low temperature cut-out 

factor 

as defined in 5.2.1 

as defined in 5.2.1 

the part load degradation factor described 

in section 2.2.1 and 5.2 for the unit 

cycling at high compressor Speed or with 

both compressors simultaneously cycling 

(if applicable). 

.k-1 

Q Cr j) • 

~k=-2 

Q (!j)= 

.k-2(T ) 

E j 

r 

1 

the part load degradation factor 

described in section 2.2.1 and 5.2 

for the unit cycling at low compressor 

speed or with the single compressor 

that normally operates at low heating 

loads. 

('k-1 .k-l) 'k=1 Qss (62) - Qss (47) (!j Qss (47) + 15 - 47) 

('k=1 • • k-1 ) 

6k=1(17) °DEF(35) - Qss (t7) (T 1 - 17) .Jo 55 18 

~.k.l .k-1 ) ·,,-1 Qss (47) - Qss (17) (Tj - 17) Qss (17) + 30 

(.k=2 .k-2 ) . k-2 QS5 (47) - Qss (17) (Tj - 17) Qss (17) + )0 

(

• k-2 • k=2 ) 

• k=2 C)"~F (35) - ''ss (17) (T j - 17) 

Qss (17) + -- 18 -

(

.k=l .k-l) 

'k-1 ESS (62) - ESS (47) (Tj - 47) 

ESS ( 47) + ...::;:::.-----=-1=-5- - .... -'----

(

.ka l .k-1) 

'k-1 ED",,(35) - EoS (17) ('j - 17) E' (17) + ~. __ -:"::-'::-_...1._ --'--_ 55 18 

(

.k-1 .k-1) l . k-1 ._E~S5::......(_4_7 }_-_E..:S::;S:.-{_17_>..!..._{!..,Jj_-_1_7l ESS (17) + 30 

(

.1<=2 .k=2) 

"k"2 ESS (47) - ESS (17) (Tj - 17) 

E55 (17) + 30 

!j !. 40°1' 

17°F! Tj < 40°1' 

T. 

J < 17°F 

, Tj ! 45°F or r

J ! 17°1' 

17°, < !j < 45·1' 

T j 2. 40·1' 

17'F ~ !j < 40'1' 

17°F < Tj < 4S·F 
CAS-RM-79-1 02 COMMENT 01 

23496 Federal R~ister I Vol. 44. No. 77 I· Thursday, Aprii lB. 1979 I Pl'Oposeli.Rules 

Calculate the heating seasonal performance factors 

and seasonal operating costs corresponding to the standardized 

maximum and minimum design heating requirements for each of 

the six regions specified in Section 6.2.5. When the 

maximum and minimum HSPF's 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 of that particular unit 

by means of interpolation. 

5.3 Calculations of the Actual Representative 

Regional Annual Performance Factors ~cr Air 

Source Central Air Conditioners (Heat Pumps) 

l'ihich Provide Both Heating and Cooling. 

5.3.1 Calculation of actual reaional annual perfor~ance 

factors (APFA) for a ?articular location and 

for each standardized de~ign heating requirement. 

(CLEu) (Qssk(95Fl 1 + (HLH&' (ORR) (Cl 

(CLHA) U;ssk (95Fl) + (HLHA) (DflR) (e) 

(CSPF) (!-{SPF) 

tvhere 

is the actual cooling load hours for 

the particular location, determined 

from the map in section 6.1.3 

(Q ssk(95,)) is defined in 5.1 

(OHR) is defined in 5.2.2 

(el is defined in 5.2.2 

where 

(HLHA) is the actu~l heating load hours for 

the particular location dete"rinined 

from .. the map in section 6, ~. 5 I 

(CSPF) is the cooling seasonal performance 

factor as determined in section 5.1 

(HSPF)" is the heating seasonal performance 

factors as determined in section 5.2 

for each standardized design heating 

requirement within the particular 

location's region or f?r the actual 

design heating requirement if known. 

the particular location's region is determined from 

the map in section 6.2.5 and, the standardized design 

heating requirements within the region are determined 

in sections 5.2 and 6.2.6 

5.3.2 Calculation of representative regional annual 

(APFR) 

performance factors (APFRl for each region 

and fer each standardized design heating 

requirement 

(CLHRl (Qssk( 95Fl 1 + ~HLHRl (OHR) (Cl 

(CLHRl (Csl( 951"» + (HLHR) (DHR) (-C ) 

CSPF HSPF 

Qssk (95F) ) is defined in 5.1 

(OHR) is defined in 5.2.2 

(Cl is defined in 5.2.2 
CAS-RM-79-102 COMMENT 01 

Federal Register '/ Vol. 44, No. 77 / Thursday, April 19, 1979 / Proposed Rules 23497 

where 

(CLHR) is the representative cooling load hours 

for each heating load hours region, as 

determined in section 6.3. 

(HLHR

) is the representative heating load hours 

for each region as determined in section 6.2.5 

(CSPF) is the cooling seasonal performance factor 

as determined in section 5.1 

(HSPF) is the heating seasonal performance tactor 

as determined in section 5.2 for each region 

and for each standardized design healing 

requirement within each region. 

where 

the regions are listed in section 6.2.5 and, the 

standardized design heating requirements within the 

regions are determined in sections 5.2 and 6.2.6 

5.4 Calculations of cooling Seasonal Performance Factor 

for Water Source units Which Provide Both Heating and 

Cooling. The cooling seasonal performance factor (CSPF) 

for water-source heat pumps shall be calculated from the 

following equation: 

CSPFj = (Tj - TF) COPE - COPp) + COP p 

(Tf; - Tp) 

j 

Nhere Tj = 

Tp = 

Where 

any location from 6.4 of this Appendix 

ground water temperature of a given location 

in (OF) from 6.3 of this Appendix or a known 

design inlet water temperature between Soop 

and 900 F. 

the inlet water temperature (OF) as described in test E from 3.4.1 and 3.4.3 of 

this appendix 

the inlet water temperature (OF) as described in test F ,from 3.4.1 

is the coefficient of performance from test E 

detailed in sections 2.4, 3.4, and 4~4 of 

this Appendix' ' 

is the steady state cooling capacity (Btu/hr) 

obtained from test E described above 

is the electric input (watts) obtained from 

test E described above, which shall include a factor of 60 watts per 12,000 Btu/hr of capacity 

measured in test p detailed in section 2.4, 

3.4, and 4.4 of this Appendix to account for pump 

usage required to move the water through the 

heat exchanger 

(3.413) is the conversion factor for Btu's per watthour 
CAS-RM-79-102 COMMENT 01 

23496' Federal Register-I Vol. 44; No. 77 .1 .Thursday, Api-i119; .1979 I· Proposed R~es 

COPy 

Where 

COPF 

(3.413) 

~; ,(3.413) 

is the coeffic,ient of performance from test B 

detailed in sections 2.4, 3.4, and 4.4 of 

this Appendix 

is the steady state cooling capacity (Btu/hr) 

obtained from test F described above 

is the electrical input (watts) obtained from 

test B described above, which shall include a factor of 60 watts per 12,000 Btu/hr of 

capacity measured in test F described above, 

to account for pump usage required to move the 

water through the heat e'xchanger. 

is the conversion factor for Btu's per 

watt-hour. 

5.5 calculation of Heating Seasonal Performance Factor :or water Source Units I-Ihlich Provide Both Heating and 

cooling. The heating seasonal performance factor (HSPF) 

for water-source heat pumps shall be calculated from the 

following equation: 

HSPFj 

Nhere 

j 

I,here 

any location from 6.4 of this Appendix 

= as described in 5.4 of this Appendix 

= the inlet water temperature (OF) as described in test G from 3.4.2 and 3.4.4 of 

this Appendix: 

the inlet water temperature (OF) as described in test H from 3.4.2 and 3.4.4 

of this Appendix. 

£(; (3.413) 

is the coefficient of performance from test 

G detailed in section 2.4, 3.4, anc 4.4 of 

this Appendix. 

(3.413) 

I,here 

(3.413) 

is the steady state heating capacity (Btulhr) 

obtained from test G as. described above. 

is the electric input (watts) obtained 

from test G as described above, which shall 

include a factor of 60 wattS per 12,000 

Btu/hr of capacity measured in test E as 

described above, to account for pump usage 

required to move the water through the heat 

exchanger. ' 

is the conversion factor for Btu per watthour. 

is the coefficient of performance from test 

H detailed in sections 2.4, 3.4, and 4.4 

of this Appendix 

is the steady state heating ca?acity (Btu/hrl 

obtained from test G as described above. 

is the electric input (watts) obtained from 

test H as described above, which shall include 

a factor of 60 watts per 12,000 Btu/hr of 

capacity measured in test G as described 

above, to account for pump usage required to move the water through the heat exchanger. 

is the conversion factor for Btu per watthour. 

5.6 Calculation of Annual Performance Factor For Water source Units Which Provide Both Heating and cooling. 

The annual performance factor (APF) for water-source 

heat pumps shall be calculated from the following equation: 

APYj (HSPF; ~ HLHj) + (CSPFj x CLRj) 

HLHj + CLHj 
CAS-RM-79-102 COMMENT 01 

Federal Register I Vol. 44. No. 77 I Thursday. April 19. 1979 I Proposed Rules .2349fJ 

Where 

j 

HSPFj 

CSPF j 

.: 

= 

any location from 6.4 of this Appendix 

heating seasonal performance factor 

for any location j as calculated in 

5.5 of this Appendix 

heating seasonal performance factor for 

any location j as calculated in 5.4 of this 

Appendix 

heating load hours for any location j 

from 6.2.5 of this Appendix. 

cooling load 'hours for any location j 

from 6.1.3 of this Appendix. 
CAS-RM-79-102 COMMENT 01

23500 

6.0 

• 

Federal Register I Vol. 44. No. 77/ThursdaYi April 19. 1979 I Proposed Rules 

Reference f1ateria1 

6.1 Cooling reference material 

6.1.1 

-Test operating and tcst condition" 

tolerance fOT cyclic d ry-coi/ testa 

Test Test condltlon 

Readings. remarks 

(.pt" .. ting tole"'T)ce 

tolerance (variation 

(lolal of a\'erage 

ob~l)n'(:d from 

range) spt>cified 

tt:st, 

conciltion) 

Outdoor dry.rulb ai~ 

temperatllr~ l-'ahrr'nhcit: 

Entering ...•.. ., ......... ; ................ , 2.0 0.5 Indoor drY.·btli!; ~.1:' 

tempcratcre, F:.-~hr<:"'nheit: 

l.'nt€ling .................................. . 

Indoor w~·t·Lulb air 

tr.mrwra: ur.e. l-\.nrenheit: 

2.0 .5 

Ezlter;r.g ................ , ............... .. ('j (I) 

Alter till' I:;t 30 s after 

E!o\:t-rria.1 r·~.,i..,t .... r:-:,C to 

au fivlJ.'. lnrtH;~ wa!.t'T ......• 

NOl.;".k pr.:~. tire dr('~)~. 

.05 

p('r('i'!1~ 01 r(·:.::!~r:~ .,. ...... :.0 

Elf'Cf!"I~;.! ~·{;lt;:.;::(': Ui;-:t.ts "'0 the tp)t. unit. t:1{'rc(.'nt.. 2.lI 

------------_._--------

'Shall at no timt' f'XC'N J lh::'d vatu? .,f t'nf; Wt·t .. 

bulb t~·mp. r·t.! Il,r \l;hirh rl·.<.tll~5 in ~ l.f ~_.I ",(b!"tif'\~. 

0! C'n~l'!j·n~;\'~· by T i;f u)(ku"'r (.,!l ::~t thp dry butb 

t'·!npc~;\.tu:,'>": {';'.].:! .n~ l;;r thi: ::~.r C)lt'rlllt! lhc 

indoor portIon of t.he unit. 

6.1.2 . -iJi«ri'JI:fion of fractional hours in 

tU;:}Jcrflil.1fe: ~'I~;S /() (ll .. • i.~{!fifvr c.llcl:lalion 

of the Si.·ER fo,- 2·spccl1 cor,prf's;wr and 2-

(·t.l1iLprC~:80T lint's 

---------.~.- - - -- -------- !1.1H t~.'rri· J~~.'~Jlt'S('fttf\· Fn;.,c.tion 01 

Ilf'LJ.tt;:,(· L1~":' t';'ln· tv~al len~1 

I"<llor.'" per:nuro::- lIP H\l urr! 

(dl-grct's b\ll for bir~ huurs 

f1;':rt'nheiO (dt>8 .... r:.::S nJN 

Fi:lhrcntH·il) 

---------------------------

Bin No.,J; 

--.-------. -. -- _.-. -.------ ------- I........ C "" <,9 2 .........•...•.. "iiJ I.') 'j<j 

3 ............... ' ~1:J l'l 

................ ". (," t,., c.'; 5 .... , ........... n':"lv 1:9 ..... .. 

6 .... _ ........... 9l) to fi4 ...... . 

7, ............... 95 to 1.19 ..... .. 

C ................ Iv.) tv WL. 

.:! 

7'j 

82 

t'; 

92 

9'/ 

102 

.214 

.2~1 

.216 

.161 

.104 

.Oli:J 

.018 

.004 

• 
Alaska 

Canal lone 

Guam 

Hawaii 

Puerto Rico 

Samoa 

Virgin Island -

o 

6,000 

6,600 

2,300 

6,000 

6,600 

6,000 

(). 1. 3 

Cooling Load 

CAS-RM-79-102 COMMENT 01 

Federal Register I Vol. 44, No. 77 I Thursday, April 19, 1979 I Proposed Rules 

[)i~,trj bution of l\ctual Cooling Load IIours (UAll\' 

'~hrouqhout the Uni lp.d States' 

Hours 

23501 
CAS-RM-79-102 COMMENT 01 

Z3502 . Federal Register I Vol. 44. No. 77 I Thursday. April'19. 1979 I Proposed Rules 

6.2 ReaC1ng Ref~renee Material 

6.2.1 Test operating and test cond1tion tolerance for 

Steady-State High Temperature Test tat 47°F (8.3·C) or 62°F (16.70C)1 

and 

Low Temperature Test tat 17°F (-8.3°C>1 

Indoor dry-bulb. 

Entering 

Leaving 

Indoor we e-bulb, 

Entering 

Leaving 

Outdoor dry-bulb, 

Entering 

Leaving 

Outdoor vee-bulb, 

, 

Entering 

Leaving 

OF 

OF 

OF 

OF 

External resistance to ~ir 

flow, inches of water 

Electrical voltage, : 

Test Operating* 

Tolerance 

2.0 

2.0 

l.0 

1.0 

2.0 

2.0 

l.0 

l.0 

.05 

2.0 

Test Condition~~ 

Tolennce 

0.5 

O.S 

0.3 

• 02 

• Test Operating Tolerance is the maximum permissable variation of any mea.ur~­

ment; When expressed as • percentage, the .... ximum a1 towable variation is the 

specified percencage of the average value • 

•• Test Condition Tolerance i. the maximum per~is.able variation of the aver •• e 

value of the measurement from the standard or desired test condition. 

.. 

6.2.2 Teat.. onerat1n& aw:L.teat-.cond4.e1cI:o- eole_M-ioT- t~4tI.period 

portion of. C-1'el.ic. " .. rfol:1ll~nCl!. ~ 

Indoor dry-bulb, ·F 

Entering 

Leaving 

Indoor vet-bulb, OF 

Entering 

Leaving 

Outdoor dry-bulb, OF 

Entering 

Leaving 

Outdoor vet-bulb, OF 

Entering 

Leaving 

External relileance to air-flow, 

inches of .. ater 

Electrical voltage, : 

Test Operating Toler.nees~ 

(App11e. after the ist 30 aec. after c.ompr.ssor 

eeart-up) 

2.0 

1.0 

2.0 

2.0 

.05 

2.0 

Test. Con.h non 

Tolerancew';. 

O.S 

O.S 

1.0 

.02 

• Test Operating Tolerance i. the maximum permi.sable variation of any measure- ment. When expresled as a percentage. the maximum allowable variation is 

the Ipacified percentage of the aver.ge value • 

... Te.t Condition Tolerance is the maximum permi.lable variation of the average 

.alu. of the .... ur ... nt from the atand.rd or desired telt condition • 
CAS-RM-79-102 COMMENT 01 

Federal Register J Vol. 44. No. 77 / Thurs'day. April 19. 1979 /Proposed Rules 23.503 

6.2.3 Test oPp.t'3ting and test condition. tolerances fo[, frost 

acc"J.mU':'ati...,n ta.S~5 t 

'Ttlsting Ofl~r.ting Iolet"anceO ) 

Our1.ng He4tlng uurlog Delrost 

Indoor dry-bulb, ., 

Entering 

Lelving 

Indoor wet-bulb, ., 

Entering 

Leaving 

Outdoor dry-bulb, ., 

Entering 

Leaving 

outdoor dew-point I -r 

Entering 

Leaving 

'E:x:tenal resistance to 

&ir-flow. inc:.hell of water 

2.0 

1.0 

2.0 

1.5 

.os 

&lectrical .,oltage. % 2.0 

4.0(3) 

10.0 

Test Condition Tolerance(2) 

(Heatlng POtt1on Otih) 

O.S 

1.0 

0.7 

.02 

Test Operating Tolerance i. the maximum 'Pemiaaable variation of any measurement. When expre,sed a. a percentage, the uximum allowable variation is 

the specified percentage of the ~v1l!r.ge value. Test Operating ToleTanee During 

Heating applies when the heat pump is LO the ht!ating mode, except :or the 

first S minutes after te1:'1Dioation of • defrost cycle. Teat OperatlDg Tolerance 

During 'Defrolt applies during. defrost cycle and. during the. first 5 ~nu~es after the tendnatioo of • defrost cycle when the heat ?W2IP l' operau.ng In 

the beatiag ...,de. 

2 test Condition Tolerartee i. the. maximum pet'rAiss.b~e variation o~ ~b. average 

value of the me •• utemenc frOD the .tandard or de'1re~ teet. co~(h.t~ou. "test 

Conditioa Tolerance applies only vben the beat pump 1.. operaclug UI. t.he 

beating ...,de. 

lIat applicable during defrost if the indoor fan is off. 

6.2.4 Ilistribution of fractional hours in temperature bins, heatirg 

load hours and outdoor design temp'erature for the different 

climatic regions 

r Region I n III IV 

r Heat ing Load Hours, HLR 750 1250 1750 2250 

I Outdoor DeSign Temperatur~ 

TOO for the region 37 27 17 5 

Frac.tional ROUTS: 

Bin # T1 (OF) 

j • 1 62 .291 .215 .153 .132 

2 57 .239 .189 .142 .111 

3 52 .194 .163 .138 .103 

4 47 .129 .143 .137 .093 

5 42 .081 .112 .135 .100 

6 37 .041 .088 .U8 .109 

7 32 .019 .056 .092 .126 

8 27 .005 .024 .047 .087 

9 22 .001 .OOS .021 .055 

10 17 0 .002 .009 .036 

11 12 0 0 .005 .026 

12 7 0 0 .002 .013 

13 2 0 0 .001 .006 

14 -3 0 0 0 .002 

15 -8 0 0 0 .001 

16 -13 0 0 0 0 

17 -18 0 0 0 I 0 

18 -23 0 0 0 0 

t-In Pacifie Coast Region 

V VI , 2150 2750' 1 -10 30 

I .106 .113 , 

, .092 .206 

.086 .215 

.076 .204 

.078 .141 

.087 .076 

.102 .034 

.094 .008 , .074 .003 

.055 0 

.047 0 

.038 0 

.029 0 , .018 0 

.010 0 i 

.005 a 

.002 0 , .001 0 I ----
23504 

b. ::. ~) 

VI 

3500 

CAS-RM-79-102 COMMENT 01 

Federal Register / Vol. 44. No. 77 I Thursday. April 19. 1979 I Proposed Rules 

Ac tUed hea t ing load hours (III 

(HUI r) for the lIni ted States 

2500 

and regional heating 103, irs 

Regional Heating Load Hours 

Region HLlB __ 

750 

11 1250 

llr 1750 

1\' 1250 

V 2750 

VI 27S0 

This map IS reasonabty accurate lor most parts 01 the UllIted Stales but IS necessan/y hlUh/Y 

,generallled lind consequently oot 100 accurate in mounlaUlOUS regIOns, piJlllcularly io the Rockies 

III 

1500 

II 

IV 

Alaska 

Hawaii and -

Territories 

3500 HLH 

o HLH 
CAS-RM-79-102 COMMENT 01

• 

• r 

Federal Register I Vol. 44. No. 77 / Thursday. April 19. 1979 I Pnoposed Rules 

6.2.6 Standard Design Heating Requirements (Btu/hr) 

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 

6.3 Representative Cooling Load Hours (CLHR) for Each Heating 

Load Hours Region 

Region CLHR HLHR 

I 2400 750 

II 1800 1250 

III 1200 1750 

IV 800 2250 

V 400 2750 

VI 200 2750 

23505 
CAS-RM-79-102 COMMENT 01 

23506 Federal Register I Vol. 44. No. 77 I Thursday. April 19. 1979 { Proposed Rules 

6.4 Ground Water Temperature Map 

AVERAGE TElvjflEIlATURE OF SHALLOW 

GROUND WATER IN O::=GIlEES FAHAENHErr