h' 8 0 U L E /1, Fi LIN G OJ . i " (0 1\ i /

1981' STA AR for "

UNITARY·

AIR-CONDITIONING

EQUIPMENT

EE-RM-90-201 COMMENT OOR5
SECTION

Section 1. Purpose

TABLE OF CONTENTS

PAGE

Section 2. Scope .

Section 3. Definitions .

Section 4. Classification . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. 2

Section 5. Testing and Rating Requirements " 2

Section 6. Performance Requirements

Section 7. Safety Requirements

Section 8. Conformance .

Appendix A

FOREWORD

This standard is prepared primarily for use in connection with, and is a part

of, the ARI Unitary Air-Conditioner Certification Program. ARI, as

copyright owner of the standard, reserves the right at all times to question any

claims of conformance and to test the equipment of any manufacturer making

such claims. It is also understood that non-participants in the ARI Certification Program based on this standard shall have no right to use the ARI

Certification Symbol, or any facsimile or reproduction thereof, on any of

their equipment or literature pertaining to said equipment.

This standard supersedes ARI Standard 210-79

5

7

8

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Price $6.50

Prmtecl in US.A © COPYRIGHT" 1981, by Air-Conditioning and Refrigeration Institute

EE-RM-90-201 COMMENT OOR5
__________________________ A RI ST AN DA R D 210-81

UNITARY AIR-CONDITIONING EQUIPMENT

Section 1. Purpose

1.1 Purpose. The purpose of this standard is to establish, for unitary air-conditioning equipment: definitions

and classification; requirements for testing and rating;

specifications, literature and advertising requirements;

performance requirements; safety requirements; and

conformance conditions.

1.1.1 This standard is intended for the guidance of

the industry, including manufacturers, distributors, installers, contractors, consumers and all

levels of government.

1.2 Review and Amendment. This standard is subject to

review and amendment as the art of the industry advances.

Section 2. Scope

2.1 Scope. This standard applies to factory-made residential, commercial, and industrial air-conditioners or

matched assemblies defined in 3.1.

2.1.1 Energy Source. This standard applies only

to electrically-driven, mechanical compression

type systems.

2.2 Exclusions. This standard does not apply to the

rating and testing of individual assemblies, such as condensing units or coils, for separate use.

2.2.1 This standard does not include standards for

heating equipment or for the heating function of

unitary air-conditioning equipment except for

safety requirements. (See 7.3.)

2.2.2 This standard does not apply to unitary

heat-operated air-conditioning equipment, to heat

pumps, to packaged terminal air-conditioners, or

to room air-conditioners.

2.2.3 This standard does not apply to unitary airconditioners as defined in ARI Standard 360, with

capacities 135,000 Btuh [40 kW] and greater.

Section 3. Definitions

3.1 Unitary Air-Conditioner. A unitary air-conditioner

consists of one or more factory-made assemblies which

normally include an evaporator or cooling coil, a compressor and condenser combination, and may include a

heating function as well. Where such equipment is

provided in more than one assembly, the separated assemblies are to be designed to be used together, and the

requirements of rating outlined in this standard are

based upon the use of matched assemblies.

3.1.1 Functions. The functions of unitary airconditioners, either alone or in combination with a

heating plant, are to provide air-circulation, aircleaning, cooling with controlled temperature, and

dehumidification, and may optionally include the

function of heating and possibly humidifying.

3.2 Published Rating. A statement of the assigned

values of those performance characteristics, under

stated rating conditions, by which a unit may be chosen

to fit its application. These values apply to all units of like

nominal capacity and type (identification) produced by

the same manufacturer. As used herein, the term "published rating" includes the rating of all performance

characteristics shown on the air-conditioner or published in specifications, advertising, or other literature

controlled by the manufacturer, at stated rating conditions.

3.2.1 Stcindard Rating. A rating based on tests

performed at Standard Rating Conditions.

3.2.2 Application Rating. A rating based on tests

performed at application rating conditions (other

than Standard Rating Conditions).

3.3 Rating Conditions. Any set of operating conditions

under which a single level of performance results, and

which causes only that level of performance to occur.

3.3.1 Standard Rating Conditions. Rating conditions used as the basis of comparison of performance characteristics.

3.4 Energy Efficiency Ratio. A ratio calculated by dividing the cooling capacity in Btuh by the power input in

watts at any given set of rating conditions, expressed in

Btuh per watt [Btuh/watt].

3.4.1 Standard Energy Efficiency Ratio. A ratio

calculated from the capacity and power input

values obtained at Standard Rating Conditions.

3.5 Seasonal Energy Efficiency Ratio (SEER). Seasonal

Energy Efficiency Ratio means the total cooling of a

central air-conditioner Btu's during its normal usage

period for cooling (not to exceed 12 months) divided by

the total electric energy input in watt-hours during the

same period, as determined in Appendix A.

3.6 "Shall", "Should", "Recommended", or "It Is Recommended". "Shall", "should", "recommended", or"it

is recommended" shall be interpreted as follows:

3.6.1 Shall. Where "shall" or "shall not" is used

for a provision specified, that provision is mandatory if compliance with the standard is claimed.

3.6.2 Should, Recommended, or It Is Recol1l

mended. "Should", "recommended" , or "it is n",

EE-RM-90-201 COMMENT OOR5
AR I ST A NDA R 0 210-81 _

Table 1-Classification of Unitary Air-Conditioners

Types of Unitary Air-Condilioners

Designation ARI Type Heat Rejection Arrangement

Single Package "'SP-A Air I

FAN I COMP I

SP-E Evap Cond EVAP COND

SP-W Water

Refrigeration RCH-A Air I COMP I

Chassis RCH-E Evap Cond j EVAP COND

RCH-W Water

Year-Round SPY-A Air IFAN I Single SPY-E Evap Cond COMP I

Package SPY-W Water ~EAT YAP COND

Remote RC-A Air mi3 Condenser RC-E Evap Cond AP I COND I

RC-W Water

Year-Round RCY-A Air FAN

Remote RCY-E Evap Cond EVAP I COND I Condenser RCY-W Water HEAT

COMP

Condensing RCU-A-C Air I EVAP I I COND I

Unit Coil RCU-E-C Evap Cond COMP

Alone RCU-W-C Water

Condensing RCU-A-CB Air I FAN I I COND I

Unit Coil RCU-E-CB Evap Cond EVAP COMP

and Blower RCU-W-CB Water

Year-Round RCUY-A-CB Air r FAN 1

Condensing RCUY-E-CB Evap Cond r EVAP 1

I COND I

Unit and Blower RCUY-W-CB Water HEAT COMP

Extracted by permission from Table J. Chapter 42. 1979 ASH RAE Handbook.

A suffix of" -0" following any of the above classifications indicates equipment not intended for use with field-installed duct systems

(See 5.1.3.7).

ommended" is used to indicate provisions which

are not mandatory but which are desirable as good

practice.

Section 4. Classification

4.1 Classification. Normally, unitary air-conditioners

within the scope of this standard may be classified as

shown in Table 1:

Section 5. Testing and Rating Requirements

5.1 Standard Ratings. Standard ratings shall be established at the Standard Rating Conditions specified in

5.1.3. All standard ratings shall be verified by tests conducted in accordance with the ASHRAE Standard

Methods ofTesting for Rating Unitary Air-Conditioning

and Heat Pump Equipment (American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc.

Standard 37-78), and with the test methods and procedures as described in this standard.

In addition, Seasonal Energy Efficiency Ratio (SEER)

shall be determined for units rated less than 65,000 Btuh

with air-cooled condensers and single-phase power

2

input in accordance with Appendix A. Other equipment

within the scope of this standard may have the SEER

determined (as an application rating) in accordance with

Appendix A, at the option of the manufacturer.

Standard Cooling Capacity shall be stated as total (sensible plus latent) cooling capacity. Power input shall be

the total power input to the compressor(s) and fanes),

plus controls and other items included as part of the

model number(s).

Standard Ratings of units which do not have indoor

air-circulating fans furnished as part of the model, i.e.,

refrigeration chassis units and condensing units with coil

alone (See Table 1), shall be established by subtracting

from the total cooling capacity 1250 Btuh/l 000 cfm

[0.172 W per tis) and by adding to the total power input

365 watts/lOOO dm {0.172 W per tis) of indoor air

handled. Standard Ratings of water-cooled units shall

include a total allowance for cooling tower fan motor

and circulating water pump motor power inputs to be

added in the amount of 10 watts per 1000 Btuh cooling

capacity [10 watts per 293.1 watts cooling capacity).

Units equipped with desuperheater/water heaters shall

be rated in accordance with ARI Standard 290.

EE-RM-90-201 COMMENT OOR5
_________________________ AR I STAN DARD 210-81

5.1.1 Values ofStandard Capacity Ratings. These

ratings shall be expressed only in terms of Btu per

hour (Btuh) [watts] in multiples of:

5.1.3.2 Seasonal Energy Efficiency Ratios.

SEER's shall be determined at the temperature

conditions specified in Appendix A.

"For units or portions thereof intended to be installed only indoors,

this temperature may be reduced to 80 F [26.7"C] dry bulb.

5.1.2 Values ofStandard Energy Efficiency Ratios

and Seasonal Energy Efficiency Ratios. Standard

ratios of energy efficiency, whenever published,

shall be expressed in multiples of 0.05 Btuh/watt

[cooling COP to 0.05].

5.1.3 Standard Rating Conditions. The conditions

of test for Standard Ratings shall include the following:

5.1.3.1 Standard Rating Temperatures. Standard Capacity Ratings and Standard Energy Efficiency Ratios shall be determined at the following temperature conditions:

Item Conditions

Air temperature entering 80 F [26.7°C]

indoor portion of unit dry bulb

67 F [19.4°C]

wet bulb

Air temperature 95F [3SOC]

surrounding unit dry bulb*

For air-cooled units

Air temperature entering 95 F [35°C] dry

outdoor portion of unit bulb (and 75 F

[23.9°C] wet

bulb when condensate is rejected to the

air stream)

For evaporatively-cooled

units

Air temperature entering 95 F [35°C]

outdoor portion of unit dry bulb

75 F [23.9°C]

wet bulb

For water-cooled units

Water temperature entering 85 F [29.4°C]

condenser

Water temperature leaving 95F [35°C]

condenser

Capacities

(Btuh) [W]

Less than 20,000[5,900]

20,000-37,800[5,900-11,000]

38,000-64,500[11,100-18,900]

65,000 and above [19,000]

Multiples

(Btuh) [W]

100[30]

200[60]

500[160]

1,000[300]

5.1.3.3 Electrical Conditions. Recommended

nameplate voltages are shown in Table 1 of ARI

Standard 110 for Air-Conditioning and Refrigerating Equipment Nameplate Voltages.

Standard Rating Tests shall be performed at the

nameplate rated voltage and frequency.

For air-conditioners with dual nameplate voltage ratings, Standard Rating tests shall be performed at both voltages, or at the lower of the

two voltages, if only a single Standard Rating is

to be published.

5.1.3.4 Cooling Coil Air Quantity. All Standard Ratings shall be determined at a cooling

coil air quantity, delivered against at least the

minimum external resistance required by

5.1.3.7, as outlined below. All air quantities

shall be expressed as dm [tis] of Standard Air

(density of 0.075 lb per Cll ft) [1.2 kg/m3 ].

a. Air-conditioners employing cooling coil

fans with adjustable-speed drives shall be

rated at the air quantity specified by the

manufacturer in his Standard Ratings, not

to exceed 37.5 dm per 1,000 Btuh !0.06

tis per watt] ofrated cooling capacity, or at

the air quantity of which the drive is capable when operating against the external

resistance specified in 5.1.3.7, whichever is

less.

b. For air-conditioners employing directconnected air-circulating fans, the cooling

coil air quantity shall be as specified by the

manufacturer in his Standard Ratings, not

to exceed 37.5 dm per 1,000 Btuh [0.06

tis per watt] of rated cooling capacity, or

the air quantity produced by the fans when

operatin.g against the external resistance

specified in 5.1.3.7, whichever is less.

c. Air-conditioners whit:h do not incorporate

a cooling coil fan, but are rated in combination with a device employing a fan shall be

rated as described under a. or b. above,

whichever applies. For air-conditioners of

this class which are rated for general use to

be applied to a variety of heating plants,

the cooling coil air quantity shall be as

specified by the manufacturer in his Standard Ratings, not to exceed 37.5 dm per

1,000 Btuh [0.06 tis per watt] of rated

cooling capacity or the air quantity obtained through the coil assembly when the

3

EE-RM-90-201 COMMENT OOR5
A R1STAND A R 0 210- 81 ._._.--.---.,,,,..-------------

Table 2- Minimum LOMVI n.1 -

Standard Cooling Rates

Thousands of Btuh) [kwl (Inches of Water) [Pal

Up thru 28 Up thru 8.2 0.10 24.9

29 thru 42 8.5 thru 12.3 0.15 37.4

43 thru 70 12.6 thru 20.5 0.20 49.8

71 thru 105 20.8 thru 30.8 0.25 62.3

106 thru 134 31.1 thru 39.3 0.30 74.7

4

pressure drop across the cooling roil assembly and the recommended enclosures

and attachment means is not greater than

0.30 inches of water [74.7 Pal, whichever

is less.

Cooling -coil air quantities as referred to herein

apply to the air quantity experienced when the

unit is cooling and dehumidifying under the

Standard Rating Conditions, specified in this

section. The air quantity determined under this

test, except as altered by automatic controls or

as noted in 6.4, 6.5 or 6.6 shall be employed in

. all other tests prescribed herein without regard

to the resulting external static pressure.

5.1.3.5 Condenser Air Quantity. All Standard

Ratings for air-cooled or evaporatively-cooled

units shall be determined at the condenser air

quantity specified by the manufacturer where

the fan drive is adjustable; or, where the fan

drive is direct-connected, they shall be determined at the condenser air quantity inherent in

the air-conditioner when operated with all of the

resistance elements associated with inlet louvres

and any ductwork and attachments considered

by the manufacturer as normal installation practice. Once established, the condenser air circuit

of the air-conditioner shall remain unchanged

throughout all tests prescribed herein, except as

altered by automatic controls.

5.1.3.6 Requirements for Separated Assemblies. All Standard Ratings for airconditioners in which the condenser or condensing unit is separated from the cooling coil, as in

Types RC, RCY, RCV and RCUY (shown in

Section 4), shall be determined with at least 25

feet [7.62 m] of interconnection tubing on each

line, of the size recommended by the manufacturer. Such air-conditioners in which the interconnection tubing is furnished as an integral part

of the machine not recommended for cutting to

length shall be tested with the complete length of

tubing furnished, or with 25 feet [7.62 m] of

tubing, whichever is greater. At least 10 feet

[3.05 m] of the interconnection tubing shall be

exposed to the outside conditions, with the rest

of the tubing exposed to the inside conditions.

The line sizes, insulation, and details of installation shall be in accordance with the manufacturer's published recommendations.

5.1.3.7 Minimum External Resistances. Where

the conditioned air-moving equipment is

supplied as part of the unitary air-conditioner,

such equipment shall be designed to work

against, and tested at not less than, the minimum

external resistance shown in Table 2 when delivering the rated capacity and air quantity

specified in 5.1.3.4 and 5.1.3.5. Indoor airmoving equipment not intended for use with

field-installed duct systems shall be tested at 0

in. water [0 Pal external pressure.

In interpreting this requirement, it is understood

that filters, heating coils, and other equipment

recommended as part of the air-conditioner be

in place and that the net external resistances

specified above are available for the duct system.

5.2 Application Ratings. Ratings at conditions of temperature or air quantity other than those specified in

5.1.3, may be published as application ratings, and shall

be based on data determined by the methods prescribed

in 5.1.

5.3 Publication of Ratings. Wherever application ratings are published or printed, they shall include, or be

accompanied by, the Standard Rating, clearly designated as such, including a statement of the conditions at

which the ratings apply.

5.3.1 Capacity Designation. The capacity designation used in published specifications, literature

or advertising, controlled by the manufacturer, for

air-conditioners rated under this standard, are to

be expressed only in Btuh [watts] at the Standard

Rating Conditions specified in 5.1.3 and in the

terms described in 5.1.1 and 5.1.2. Horsepower.

EE-RM-90-201 COMMENT OOR5
_________________________ARIST AN DARD 210-81

tons, or other units shall not be used as capacity

designations.

5.4 Tolerances. To comply with this standard, pub;-

lished cooling capacity ratings, energy efficiency ratios,

and/or seasonal energy efficiency ratios shall be based on

data obtained in accordance with the provisions of this

section, and shall be such that any production unit, when

tested, will meet these ratings except for an allowance to

cover testing and manufacturing variations; the amount

of allowance to be minus 5 per cent.

Section 6. Performance Requirements

6.1 Performance Requirements. To comply with this

standard, unitary air-conditioners shall be designed and

produced in accordance with the provisions of this section in such a manner that any production unit will meet

the requirements detailed herein.

6.2 Maximum Operating Conditions Test. * Unitary

air-conditioners shall be designed and produced to pass

the following maximum operating conditions test with a

cooling coil air quantity as determined in 5.1.3.4. For

multi-capacity units, this test shall be conducted with

unit controls set for maximum capacity.

6.2.1 Temperature Conditions.

For all units

Air temperature

surrounding unit 115 F [46.10c]

dry bulb**

Air temperature entering

indoor portion of 80 F [26.7°C]

dry bulb

67 F [19.4°C]

wet bulb

For water-cooled units

Water temperature entering

condenser 90 F [32.2°C]

Water temperature leaving

condenser , 100 F [37.8°C]

*This test will become effective on publication of this standard, at the manufacturer's option, but not later than January

1, 1982. If the manufacturer does not elect the new test

procedures, the requirements for this test are those shown in

6.2 of ARI Standard 210-79.

**For units or portions thereof intended to be installed only

indoors, this temperature may be reduced to 80 F [26.7°C]

dry bulb.

For air-cooled units

Outside air temperature .....11'5 F [46.1°el dry

bulb (and 75 F

[23.9°C] wet bulb

when condensate is

rejected to the

condenser air

stream) at the standard condenser air

quantity specified

and stated by the.

manufacturer

For evaporativeiy-cooled units

Outside air temperature 100 F [37.8°C]

dry bulb

80 F [26.7°C]

wet bulb

Make-up water temperature 90 F [32.2°C]

6.2.2 Voltages. The test shall be run at the Range

A minimum utilization voltage from ARI Standard

11 0, Table 1, based upon the unit's nameplate

rated voltage(s). This voltage shall be supplied at

the unit's service connection and at rated frequency.

6.2.3 Procedure. The air-conditioner shall be operated for one hour at the temperature conditions

and voltage specified.

6.2.4 Requirements. The air-conditioner shall operate .continuously without interruption for any

reason for one hour.

6.2.4.1 Units with water-cooled condensers

shall be capable of operation under these

maximum conditions at a water-pressure drop

not to exceed 15 psi [l03.4 kPa], measured

across the unit.

6.3 Voltage Tolerance Test. * Unitary air-conditioners

shall be designed and produced to pass the following

voltage tolerance test with a cooling coil air quantity as

determined under 5.1.3.4.

6.3.1 Temperature Conditions. Temperature

conditions shall be maintained as shown in 5.1.3.1.

6.3.2 Voltages.

6.3.2.1 Tests shall be run at the Range B

minimum and maximum utilization voltages

from ARI Standard 110, Table 1, based upon

the unit's nameplate rated voltage(s). These voltages shall be supplied at the unit's service connection and at rated frequency. A lower or a

higher volta.ge shall be used, if listed on the

nameplate.

5

EE-RM-90-201 COMMENT OOR5
ARt STAN DAR 0 210-81 _

6

6.3.2.2 The power supplied to the airconditioner shall be adjusted just prior to the

shut down period (See 6.3.3.2) so that the resulting voltage at the unit's service connection is 86

per 'Cent of nameplate rated voltage when the

compressor is on locked rotor. For the purpose

of this standard, the compressor nameplate

locked-rotor amperes may be used to determine

this voltage. The proper value of no-load voltage

which will give the specified voltage at lockedrotor conditions should be determined prior to

the test.

The locked-rotor current value of any motor

shall be measured as follows:

a. All hermetic compressor motors shall be

tested as a compressor assembly.

b. The motor winding temperature shall not

exceed 77 F [25°C] when the voltage is

applied.

c. The current reading shall be taken within

four seconds after the voltage is applied. If

the test is repeated, the motor winding

shall be allowed to cool to 77 F [25°C] or

lower before the current is reapplied.

d. The voltage at the unit service connection,

at the time the current reading is taken,

shall be the manufacturer's nameplate

rated voltage.

e. The locked-rotor current shall be measured with an ammeter, with the rotor actually locked.

6.3.2.3 Within one minute after the airconditioner has resumed continuous operation

(See 6.3.4.3), the voltage shall be restored to the

values specified in 6.3.2.1.

6.3.3 Procedure.

6.3.3.1 The air-conditioner shall be operated

for one hour at the temperature conditions and

voltage(s) specified.

6.3.3.2 All power to the air-conditioner shall be

cut off for a period sufficient to cause the compressor to stop (not to exceed five seconds) and

then restored.

6.3.4 Requirements.

6.3.4.1 During both entire tests, the airconditioner shall operate without failure of any

of its parts.

6.3.4.2 The air-conditioner shall operate continuously without interruption for any reason for

the one hour period preceding the power interruption.

6.3.4.3 The unit shall resume continuous operation within two hours of restoration of power

and shall then operate continuously for one half

hour. Operation and resetting of safety devices

prior to establishment of continuous operation is

permitted.

6.4 Low- Temperature Operation Test. Unitary airconditioners shall be designed and produced to pass the

following low-temperature operation test when operatin,g with initial air quantities as de~rmined in 5.1.3.4,

5.1.3.5 and with controls and dampers set to produce the

maximum tendency to frost or ice the evaporator,

provided such settings are not contrary to the manufacturer's instructions to the user:

6.4.1 Temperature Conditions.

For all units

Air temperature entering

indoor portion of unit 67 F [l9.4°C]

dry bulb

57 F [13.9°C]

wet bulb

For water cooled units

Water temperature leaving

condenser 70 F [21.1°C]

For air-cooled and evaporativelycooled units

Outside air temperature 67 F [l9.4°C]

dry bulb

57 F [13.9°C]

wet bulb*

6.4.2 Procedure. The testshall be continuous with

the unit on the cooling cycle, for not less than four

hours after establishment ofthe specified temperature conditions. The unit will be permitted to start

and stop under control of an automatic limit device, if provided.

6.4.3 Requirements.

6.4.3.1 During the entire test, the aircon?itioner shall operate without damage to the

eqUipment.

6.4.3.2 During the entire test, the air quantity

shall not drop more than 25 per -cent from that

determined under the Standard Rating test.

6.4.3.3 During the test, and during the defrosting period after the completion of the test, all ice

'The wet-bulb temperature condition is not required when

testing air-cooled condensers which do not evaporate condensate.

EE-RM-90-201 COMMENT OOR5
_________________________ARI ST ANDAR 0 210-81

or meltage must be caught and removed by the

drain provisions.

6.5 Insulation Efficiency Test. Air-conditioners shall be

designed and produced to pass the following insulation

efficiency test when operating with air quantities as determined in 5.1.3.4 and 5.1.3.5 with controls, fans, dampers, and grillesset to produce the maximum tendency to

sweat, provided such settings are not contrary to the

manufacturer's instructions to the user:

6.5.1 Temperature Conditions.

For water-cooled units

Air temperature entering and

surrounding indoor portion

of unit 80 F [26.7°C]

dry bulb

75 F [23.9°C]

wet bulb

Water temperature

leaving condenser 80 F [26.7°C]

For air-cooled and evaporativelycooled units

Air temperature entering and

surrounding indoor portion

of unit 80 F [26.7°C]

dry bulb

75 F [23.9°C]

wet bulb*

Outside air temperature 80 F [26.7°C]

dry bulb

75 F [23.9°C]

wet bulb*

6.5.2 Procedure. After establishment of the

specified temperature conditions, the unit shall be

operated continuously for a period of four hours.

6.5.3 Requirements. During the test, no condensed water shall drop, run, or blow off from the

unit casing.

6.6 Condensate Disposal Test. ** Air-conditioners

which reject condensate to the condenser air shall be

designed and produced to pass the following condensate

disposal test when operating with air quantities as determined in 5.1.3.4 and 5.1.3.5 and with controls and

dampers set to produce condensate at the maximum

rate, provided such settings are not contrary to the manufacturer's instructions to the user:

'The wet-bulb temperature condition is not required when

testing air-cooled condensers which do not evaporate condensate.

"This test may be run concurrently with the Insulation Efficiency Test (See 6.4).

6.6.1 Temperature Conditions.

Air temperature entering and

surrounding indoor portion

of unit 80 F [26.7°C]

dry bulb

75 F [23.9°C]

wet bulb

Outside air temperature 80 F [26.7°C]

dry bulb

75 F [23.9°C]

wet bulb

6.6.2 Procedure. After establishment of the

specified temperature conditions, the airconditioner shall be started with its condensate

collection pan filled to the overflowing point and

shall be operated continuously for four hours after

the condensate level has reached equilibrium.

6.6.3 Requirements. During the test, there shall

be no dripping, running-off, or blowing-off of

moisture from the unit casing.

6.7 Tolerances. The conditions for the tests outlined in

6.2, 6.3, 6.4, 6.5 and 6.6 are average values subject to

tolerances of ±1.0 F [±0.56°C] for air wet-bulb and

dry-bulb temperatures, ±0.5 F [±0.28°C] for water

temperatures, and ± 1.0 per cent of the reading for voltages.

Section 7. Safety Requirements

7.1 Refrigerating System. It is strongly recommended

that the refrigerating system be designed, constructed,

and assembled so as to be in accordance with the latest

edition of the ANSI!ASHRAE 15-1978 Safety Code for

Mechanical Refrigeration (American Society of Heating,

Refrigerating and Air-Conditioning Engineers, Inc.).

7.2 Underwriters' Laboratories, Inc. It is strongly recommended that unitary air-conditioners be designed.

constructed, and assembled so as to meet the safety

requirements of UL Standard for AirConditioners, Central Cooling (Underwriters' Laboratories, Inc. Standard

465, July 1978).

7.3 Heating Functions. In addition to the foregoing requirements of this section, it is strongly recommended

that air-conditioners incorporating a gas-fired, oil-fired,

or electrical heating function be designed, constructed,

and assembled so as to meet the applicable safety requirements of one of the following standards:

a. Gas-fired: American National Standard for GasFired Gravity and Forced Air Central Furnaces

(American National Standards Institute Standard

Z21.47-1978 or American National Standard for

Gas-Fired Heavy Duty Forced Air Heaters (American National Standards Institute Standard

Z21.53-1967).

7

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ARI STAN DAR 0 210-81 _

b. Oil-Fired: UL Standard for Oil-Fired Central Furnaces {Underwriters' Laboratories, Inc. Standard

727, October 1975) or UL Standard for Oil-Fired

Unit Heaters (Underwriters' Laboratories, Inc.

Standard 731, October 1975).

c. Electrical: UL Standard for Heat Pumps (Underwriters' Laboratories, Inc. Standard 559, March

1980).

Section 8. Conformance

8.1 Conformance. Conformance with this standard

shall not be claimed or implied for unitary airconditioners coming within the scope of this standard

unless the unitary air-conditioners for which such claims

are made meet all the performance, safety and rating

requirements specified herein.

2. Testing Required

2.1 Testing required for airsource cooling

only units with single speed compressors.

two-speed compret1llOrs, two compressors. or cylinder unloading. Two steady state wet coil

tests required to be performed. test A and

test B. TestA is to be conducted as an

outdoor dry bulb temperature of 95" F and

test B at 82" F. Test C and 0 are optional tests

to be conducted when cyclic performance

parameters are to be measured in order to

determine the degradation coefficient, en

Test C is a steady state dry coil test

conducted at an outdoor dry bulb

temperature of 82° F. Test 0 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, CD.

APPENDIX A

*Uniform Test Method for Measuring the Energy Consumption of Central Air-Conditioners

Appendix M to Subpart B-Uniform Test 1.12 "Demand-defrost control system" which all indoor and outdoor conditions are Method for Measuring the Energy means a system which is designed to perform held constant and the unit is in non-changing

Consumption of Central Air Conditioners the defrost function on the outdoor coil of the operating mode.

1. Definitions heat pump only when a predetermined 1.24 '"Temperature bin" means a S" F

degradation of performance is measured. increment over a dry-bulb temperature range

1.1 "Annual performance factor" 1.13 "Design heating requirement (m·m)" of 65" F through 104" F for the cooling cycle

means the total heltting and cooling is the amount of heating required to maintain and -25" F through 64" F for the heating

done by a heat pump in a particular a given indoor temperature at a particular cycle.

region in one year divided by the total outdoor design temperature. 1.25 '"TIme-temperature defrost control

electric power used in one year. 1.14 "Dry-coil test" means a test system" means a system which automatically

1.2 "ARI" means Air-Conditioning and conducted at a wet-bulb tempera'l'r~ and a provides the defrost function at a Refrigeration Institute. dry-bulb temperature su,h that moisture will predetermined time interval whenever the

1.3 "ARI Standard 210-79" means the test not condense on the evaporator coil of the outdoor temperature drops below a level

standard published in 1979 by the ARI and unit. where frosting will occur.

titled "Standard for Unitary Air-Conditioning 1.15 "Heating seasonal performance 1.26 '"Test condition tolerance" means the

Equipment". factor (HSPF)" means the total heating output maximum permissible variation of the

1.4 "ARI Standard 240-77" means the test of a heat pump during its normal annual average of the test observations from the

standard published in 1977 by the ARI and usage period for heating divided by the total standard or desired test condition as tilled "Standard for Air-Source Unitary Heat electric power input during the same period. provided in 6.1.1, 6.2.1. 6.2.2, and 6.2.3 of this

Pump Equipment". 1.16 "Heating load factor (HLF)" means Appendix.

1.5 "ARI Standard 320-76" means the test the ratio of the total heating done in a 1.27 '"Test operating tolerance" means the

standard published in 1976 by the ARI and complete cycle of a specified time period. maximum permissible difference between the

titled "Standard for Water-Source Heat consisting of an "on" time "off' time, to the maximum and the minimum instrument

Pumps". steady state heating done over the same observation during a test as provided in 6.1.1,

1.6 "ASHRAE" means the American period at constant ambient conditions. 6.2.1, 6.2.2, and 6.2.3 of this Appendix.

Society of Heating, Refrigeration and Air- 1.17 "Latent cooling" means the amount 1.28 "Wet-coil test" means a test

Conditioning Engineers, Inc. of cooling in Btu's necessary to remove water conducted at a wet-bulb temperature and a

1.7 "ASHRAE Standard 37-78" means the vapor from the air passing over the indoor dry-bulb temperature such that moisture will

test standard published by ASHRAE in 1978 coil by condensation during a period of time. condense on the test unit evaporator coil.

and titled "Methods of Testing for Rating 1.18 "Part-load factor (PLF)" means the

Unitary Air-Conditioning and Heat Pump ratio of the cyclic energy efficiency ratio to

Equipment." the steady-state energy efficiency ratio at

1.8 "Continuously recorded" means a identical ambient conditions.

method of recording measurements in 1.19 "Seasonal energy efficiency ratio

intervals no greater than 5 seconds. (SEER)" means the total cooling of a central

1.9 "Cooling load factor (CLF)" means the air conditioner in Btu's during its normal

ratio of the total cooling done in a complete annual usage period for cooling divided by

cycle of a specified time period, consisting of the total electric power input in watt-hours

an "on" time and "off' time, to the steady- during the same period.

state cooling done over the same period at 1.20 "Sensible cooling" means the amount

constant ambient conditions. of cooling in Btu's performed by a unit over a

1.10 "Cyclic Test" means a test where the period of time, excluding latent cooling.

indoor and outdoor conditions are held 1.21 "Single package unit" means any

constant, but the unit is manually turned "on" central air conditioner in which all the major

and "off' for specific time periods to simulate assemblies are enclosed in one cabinet.

part-load operation. 1.22 "Split system" means any central air

1.11 "Degradation coefficient (Cn)" means conditioner in which one or more of the major

the measure of the efficiency loss due to the assemblies are separate from the others.

cycling of the unit. 1.23 "Steady-state test" means a test in

'Copied from Appendix M, pages 76707 thru 76723 Federal Register. Vol. 44, No. 249. Thursday. December 27. 1979. This Appendix M is

subject to change by the U.S. Government. Only those portions of Appendix M pertaining to air-source cooling-only units are to be used.

8

EE-RM-90-201 COMMENT OOR5
_________________________ARI STAN DAR 0 210-81

2.1.1 Testing required for units with

single speed compressors and single speed

condenserfans. 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 andmultiple-speed

condenserfans. The test requirements for

multiple-speed condenser fan units shall be

the same as described in section 2.1.1 for

single speed condensor 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 test 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.

(S/T), 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 airsource heating

only units with single speed compressors.

two-speed compressors. two compressors. or

cylinder 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. CD.

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.

2.2.2 Testing required for units with twospeedcompressors. two compressors. or cylinder unloading. With the unit operating:

at 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 compressors 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 Cyclil;

Test Additional tests. (Frost Accumulation

Test and Low Temperature Test) are

required, with the unit operating: 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 (cylinder

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 watersource

units which provide both heating and cooling.

(Reserved)

3. Testing conditions

3.1 Testing conditions for airsource cooling only units with single speed

compressors. two-speed compressors, two

compressors or cylinder unloading. The test

room requirement and equipment installation

procedures are the same as those specified in

sections 11.1 and 11.2 of ASHRAE Standard

37-78. Units designed for both horizontal and

vertical installation shall be tested in the

orientation in which they are most frequently

installed. 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 dampers upstream and downstream

of the test unit to block the off period air

flow. Values of capacity for rating purposes

are to be rounded off to the nearest 100 Btu!

hour for capacities less than 20,000 Btu/hour;

to the nearest 200 Btu/hour for capacities

between 20,000 and 37,999 Btu/hour; and to

the nearest 500 Btu/hour for capacities

between 38.000 and 64.999 Btu/hour.

The follOWing conditions listed in ARI

Standard 210.79 shall apply to all tests

performed in Section 3.1 of this Appendix:

5.1.3.4 Cooling Coil Air Quantity.

5.1.3.6 Requirements for Separated

Assemblies.

3.1.1 Testing conditions for units with single

speed compressors and single speed

condenserfans.

3.1.1.1 Steady state wet-coil performance

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

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 of 87° 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

entering air temperature except for units or

sections thereofintended to be installed only

indoors. in which case the dry-bulb

temperature surrounding that indoor side of

t.'le 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 reco=ended 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 cycling the unit "on" and "off'

by manual or automatic operation of the

normal control ~t of the unit. The unit

shall cycle with mpressor "(m" for 6

minutes and "for 24 minutes. The indoor

fan shall also cyde "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, CD by the procedures

outlined in 5.1 of this Appendix.

3.1.2 Testing conditions for units with

single speedcompressors and multiple-speed

condenserfans. 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 cyh'nder 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

9

EE-RM-90-201 COMMENT OOR5
AR I STAN DAR 0 210-81 _

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 be used for the

degradation coefficient, Co. at each

compressor speed. If the 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 operating

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 S/

T 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 airsource

heating only units with single speed

compressors. two-speed compressors. two

compressors, or cylinder unloading. The

equipment under test shall be installed

according to the requirements of Section 11.2

of ASHRAE Standard 37-78 and Section

5.1.4.5 of ARI Standard 240-77. Test chamber

requirements are the same as given in Section

11.1 of ASHRAE Standard 37-78. Units

designed for both horizontal and vertical

installation shall be tested in the orientation

in which they are most often installed. 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). Values of capacity for

rating purposes are to be rounded off to the

nearest 100 Btu/hour for capacities less than

20.000 Btu/hour: to the nearest 200 Btu/hour

for capacities between 20,000 and 37.999 Btul

hour; and to the nearest 500 Btulhour for

capacities between 38,000 and 84.999 Btul

hour.

10

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 82· F and an outdoor

wet-bulb temperature of 58.5· 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 60· F. The duration of the tests

shall be for a minimum of Ifs 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 dampers upstream and downstream

of the test unit to block the off period airflow.

3.2.1.3 Frost accumulation test conditions.

The dry-bulb temperature and the resultant

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 60· 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 Low 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 60· F.

3.2.1.5 Additional testing conditions. All

tests shall be conducted at the indoor-side air

quantities specified in Sections 4.1.4.3 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

intended to be installed indoors shall have

the air temperature surrounding that portion

of the unit the same as the indoor air

temperature.

3.2.2 Testing conditions for units with

two-speed compressors. two compressors or cylinder 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 conditions for air source units

which provide both heating and cooling. The

testing conditions for units 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 provide hoth heatiIlg andcooling.

(Reserved)

4.0 Testing procedures. Measure all

electrical inputs as described in the

procedures below. All electrical

measurements during all "on" and "off'

periods 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-

78) on the indoor side and one other method

consisting of either the Air-Enthalpy Method

or the Compressor Calibration Method

'(Section 4 of ASHRAE Standard 37-78 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 37-78) 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 installed 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 5.1.3.4. 5.1.3.5, and

5.1.3.7 of ARI Standard 210.79.

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 37-78 and evaluated in

accordance with the cooling-related

requirements of Section 12 of the ASHRAE

EE-RM-90-201 COMMENT OOR5
_________________________ARI STAN DARD 210-81

Standard 37-78. 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

sections 3.1.1.2, 3.1.2, 3.1.3, 3.1.4, 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 37.78. The test room

reconditioning apparatus and the equipment

under test shall be operated until equilibrium

conditions are attained, but not for less than

one hour before data for test C are recorded.

For all equipment test methods including the

Compressor Calibration Method. test C 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 37-78. When the Air-EnL'lalpy

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 37-78 shall also

apply. Immediately after test C is completed

the test unit shall be manually cycled "off'

and "on" using the time periods from 3.1.1 of

this Appendix until steadily repeating

ambient conditions are again achieved in

both the indoor and outdoor test chambers,

but for not less than 2 complete "off'/"on"

cycles. Without a break in the cycling

pattern, the unit 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 test 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 "off' when the

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

air moving equipment shall also cycle "off'

as governed by any automatic controls

normally installed with the unit. This last

requirement applies to units having an indoor

fan time delay. Units not supplied with an

indoor fan time delay shall have the indoor

air moving equipment cycle "on" and "off' 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 D of ASHRAE

Standard 37.78. 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

wet-and dry-coil performance tests shall be

performed within the applicable operating

and test condition tolerances specified in

Section 11.6 and Table mof ASHRAE

Standard 37-78.

4.1.3.1 The indoor and outdoor average

dry-bulb temperature for the cyclic dry coil

test D shall both be within 1.00

F of the indoor

and outdoor average dry bulb temperature for

the steady-state dry coil test C, respectively.

4.1.3.2 The test condition and test

operating tolerances for conducting test D are stated in 6.1.1 of this Appendix. Variation in

the test conditions greater than the tolerances

prescribed in 8.1.1 of this Appendix shall

invalidate the test. It is suggested that an 'electric resistance heater having a heating

capacity approximately equa'! to the sum of

the cooling capacity and compressor and

condenser fan power should be installed in

the outdoor test room and cycled "off' and

"on" as the unit cycles "on" and "off'

respectively to improve control in the outdoor

test room. Similarly, an electric resistance

heater having a heating capacity

approximately equal to the cooling capacity

of the unit could be installed in the indoor

test room. and cycled "on" and "off' as the

test unit cycles "on" and "off' to improve

indoor room control.

4.2 Testing procedures for airsource heating only units with single speed

compressors, 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 low Temperature

test shall have the performance evaluated by

the Air-Enthalpy Method on the indoor side.

In addition. the High Temperature Test and

the Low Temperature Test shall have a simultaneous test method (as described in

4.1) used as a check. The values calculated

from the two 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 calulations in section 5.2.

4.2.1.1 Test procedure for high

temperature test. When the outdoor AirEnthalpy Method is used, the outdoor

chamber must not interfere with the normal

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

ou,tdoor portion of the unit. The test room

apparatus and test units must be operated for

at least one hour with at least Ih hour at

equilibrium and at the specified test

conditions prior to starting the test. The High

Temperature Test shall then be conducted for

a minimum of Ih hour with intermittent data

being recorded at lo-minute intervals. For all

units. especially those having controls which

periodically cause the unit to operate in

defrost 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 lO-minutes after defrost termination

prior to the start of the test. When the

outdoor Air-Enthalpy 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 37-78

shall then apply in conducting the " preliminary test for the outdoor air enthalpy

method. For some units, at the ambient

condition of the test, frost may accumulate on

the outdoor coil. If the supply air temperature or the difference between the supply air

temperature and the indoor air entering

temperature has decreased by more than 1.50

F at the end of the test. the unit shall be

defrosted and the test restarted. Only the

results of this second High Temperature Test

shall be used in the heating seasonal

performance calculation in section 5.2. Prior

to beginning the High Temperature Test, a unit shall operate in the heating mode for at

least 10 minutes after defrost termination to

establish equilibri1.lm conditions for the unit

and the room reconditioning apparatus. The

High Temperature Test may only begin when

the test unit and room conditions are within

the test condition tolerances specified in

Section 6.2.1 of this Appendix.

4.2.1.2 Test procedures for the cyclic test.

The cyclic test shall follow the High

Temperature-Test and by cycled "on" and

"off' as specified in 3.2.1.2 until steadily

repeating anibient conditions are achieved

for both the indoor and outdoor test

chambers, but for not less than 2 complete

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

cycling pattern. the unit shall be operated

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

during which the required test data shall be

recorded. 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 6.2.2. of this Appendix. If, prior to the

High Temperature Test, the unit underwent a

defrost cycle to rid the outdoor coil of any

accumulated frost. then prior to cyciing the

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

undergo a defrost. After defrost is completed

and before starting the cycling process, the

unit shall be operated continuously in the

heating mode for a 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 the frost

accumulation test. The defrost controls shall

be set at the normal settings which most

typify those encountered in Region IV as

11

EE-RM-90-201 COMMENT OOR5
ARI STANDAR D 210-81 _

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 If2 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 preliminal"J

-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 at the termination of a defrost cycle

which automatically occurs and shaH end at

the termination of the next automatically

occurring defrost cycle. For units containing

defrost controls which are likely to cau~e

defrost at intervals exceeding one hour when

operating at the required lest condition. the

preliminary test period consi§ts of "healingonly" preliminary operation for at least one

hour. after which a defrost may be manually

or automatically induced. The test period

then begins at the termination of this defrost

cycle and ends at the termination of the next

automatically occurring defrost cycle. If the

unit has not undergone a defrost after 12

hours. then the tests shall be concluded and

the results calculated for this 12-hour period.

For units which turn the indoor fan off during

dekost the indoor supply duct shall be

blocked during all defrost cycles to prevent

natural or forced convection through the

indoor unit During defrost. resistance heaters

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

unit 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

tempe!'Qture test. The indoor air flow rate

shall be determined as described in Section

7.1 through 7.4 of ASHRAE Standard 37-78.

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 is

connected to the indoor air discharge side of

the test specimen through a short plenum.

The exhaust side of the air flow rate

12

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 a

conditioning apparatus and then back to the

test specimen inlet. The static pressure

across the nozzles. the velocity 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 exceedin~ :.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 ±0.2 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 ali other equipment

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

percent of the quantity measured.

Measurements of the air temperature ~ntering

and leaVing the indoor,coil or the difference

between these two shall be made in

accordance with the requirements of

ASHRAE Standard 41 part 1. These

temperatures shall be continuously recorded

with instrumentation having a total system

accuracy within ±O.3° F of indicated value

and 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 win

result in an error no greater than ±O.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 made in

accordance with Section 8 of ASHRAE

Standard 37-78 using equipment which will

result in an error no greater than ±0.01 inch

of water. Static pressure measurements shall

be made and recorded at S minute intervals.

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 the same

agreed within ±1. percent as the air flow rate

measured during the previously conducted

High Temperature Test. All other

instrumentation 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 instrumentation having a total system

accuracy within ±0.3° F of indicated value.

The outdoor dew point temperature shall be

determined with an error no greater than

±O.SO F of indicated value using continuously

recording instrumentation. All other data

shall be 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 dermed as the actuation (either

automatically or manually) of the controls

normally installed with the unit which cause

it to 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 in capable of recording the

cooling done during defrost as well as the

total electrical energy usage during defrosl.

These data and the continuously recorded

data need be the only data obtained during

defrost.

4.2.2.4 Test instrumentation for the low

temperature test. Instrumentation for the Lew

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 tbe high

temDerature test. All tests shall be conducted

within the tolerances specified in Section

6.2.1. Variation greater than those given shaH

invalidate the test. The heating capacity

results by the indoor Air Enthalpy Method

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 tolerances 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 tesL 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 S 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 tesL 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 airsource units which provide both heating and cooling.

EE-RM-90-201 COMMENT OOR5
_________________________ARI STAN DAR 0 210-81

The testing procedures for units which

provide both heating and cooling shall be the

same as those specified in Sections 4.1 and

4.2 of this Appendix. Also during the offperiod 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 watersource

units which provide both heating and cooling.

(Reserved)

5.0 Calculations for performance factors.

5.1 Calculations ofseasonal energy

efficiency ratios (SEER) in air-source units.

The testing data and results required to

calculate the seasonal energy efficiency ratio

(SEER) in Btu's per watt-hour 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).

Q..k (95F]

Ouk (82F)

Q.., dry

Qeye. dry

(ii) 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 test C and the electrical usage (watthour) from test D.

E."k (95F]

E..k (82F)

E..k • dry

Ec.c. dry

(iii) Indoor air flow rate (SCFM) and

external resistance to indoor air flow (inches

of water).

(iv) Air temperature (" F]

Outdoor dry bulb

Outdoor wet bulb

Indoor dry bulb

Indoor wet bulb

Where the pooling capacities Quk (In!F).

from test A. Quk (82). from test B. and Qu,

dry. from test C. are calculated using the

equations specified in section 3.7 of ASHRAE

Standard 37-78. The total cooling done. Q"".. dry from test D. is calculated using equation

(1) below.

Units which do not have indoor air

circulating fans furnished as part of the

model shall have their measured total cooling

capacities adjusted by subtracting 1250 Btul

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 eFM of

measured indoor air flow.

Energy efficiency ratios from tests A. B.

and C. EERA• EERa. 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

indoor air equipment power and'the duration

of time in one cycle that the circulating

indoor air equipment is on. The total cooling

done shall then be the measured cooling in

one complete cycle minus the energy usage

required for indoor air circulation in one

complete cycle. The total electrical energy

usage shall be the sum of the energy usage

required for indoor air circulation in one complete cycle and the energy used by the r~maining .equipment components

(compressor{s). outdoor fan. crankcase

heater. transformer{s). etc.) in one complete

test cycle.

Energy efficiency ratio from tests D. EER""c

dry is calculated as the ratio d ihe total

cooling done in Btu's to the total electrical

energy usage in watt-hours.

13

EE-RM-90-201 COMMENT OOR5
AR I STAN DA R 0 210-8. _

PLF( 0.5) =1-0.5X CD

Q:.-2( Ti) - BL( Ti)

(f..-'( Ti) -Q:.-' ( Ti)

(1)

where

The value of the degradation coefficient.

Cl',-' for low compressor speed cycling and

ct-· for high speed on/off compressor

cYlJling 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= 1) for which the steady-state

cooling capacity, Q':.-' (Ti), is great€r

than or equal to the building cooling load,

BL (Ti), evaluate the following equations:

Xi-l BL(T;)

(f..-I( Ti )

(1)

Xl-t-Load factor.

B L(Ti) = Bullditlg cooling load (Btu/hr) at tempera- ture (Ti) from section 5.1.3.

Q..l-J(Ti)=Steady-state cooling capacity (BtU/hr) at temperatures (Ti) from section 5.1.3.

(2) Xk-'=l-Xk-l

(3) Q<ffi) =[Xk-1X<l..-I(Ti)

+Xk-·X Q~;'( Ti)]X~

(4) E<;i)=[Xi-1XE~._1(Ti)

+Xk-·X E~.~'( Ti)]X~

PLFk-l= 1-Cl',-'(l- Xk-l).

Where CD the degradation coefficient as described in section 2.1.3 or as calculated

above in equation (1).

5.1.3.2 When a unit must alternate between high (k=2) and low (k= 1) compres- sor speeds to satisfy the building cooling

load at a temperature Ti , evaluate the

following equations:

where

E(Tj) . . -N=ratIO of Energy usage{watt-hr.) III temperature bin j to the number of temperature bin hours.

(3)

(2) Q<ffi)=Xk-1XQ:;'(T;)XN

where

Q7;i) = ratio of total cooling (Btu) in temperature

bin j to the number oftemperature bin hours.

"'j is the fractional number of bours in temperature N binj from 6.1.2.

5.1.3.3 When a unit must cycle on and

off at high compressor speed (k=2) in

order to satisfy the lmilding cooling load

at a temperature T;, evaluate the equations provided in sect.ion 5.1.3.1 replacing (k=l) data with the (k=2) data.

5.1.3.4 When a unit operates continuously

at high compressor speed (k = 2) at an outdoor temperature Ti evaluate the following

equations:

(1) Q<;i) = (f..-2( T;) X lJ

E( T i ) _ El-'( T.) X N - u 2 N (2)

energy efficiency ratio (SEER) for units

employing single-speed compressors and

multi-speed condenser fans shall be based on the energy efficiency ratio obtained for

test B and the method outlined in 2.1.2 of

this Appendix to account for the perform- ance under cyclic conditions. The energy

efficiency ratio for test B is obtained with

the unit operating with the condenser fan

speed which normally occurs at test B

ambient conditions.

The seasonal energy efficiency ratio in

Btu's/watt-hour shall be determined by

the equation:

SEER= PLF(0.5) X EERB

where

Q..l(ll5 F) = Bteady-state capacity measured from test A as outlined in 2.1.3.

/;/u'(82 F) = Btelldy-state capacity measured from test B as outlined in 2.1.3.

wben

where

CD=Tbe dClll'lldation coefficient described in 2.1.2 or as calcUlated in equation (4) above.

5.1.3 Method for calculating a SEER for

units with two speed compressors or two

compressors, or cylinder unloading. The

calculation procedure described in this

section shall be based on the performance

of test A and B at each of the compressor

speeds for two-speed compressor units,

subject to the conditions on condenser fan

speed 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 = 1 ( and the

term "low-speed") designates the com- pressor that normally operates at an outdoor dry-bulb temperature of 82° F and

1=2 (and the term "high speed") denotcs

operation with both compressors.

In order to evaluate the steady-state

capacity Qui ( Ti), and power input, Eui(Ti), at temperature Ti for each

compressor speed, k=l, k=2, the results

of tests A and B from 5.1 shall be used in

the following equation:

Q•."(Ti)=Q•." (95 F)

+ Qui (82 ~~=~:/ (95 F) [33-(5Xj)]

where

Q,.·..(llIl F)=Bteady-state capacity measured from test A in 2.9 at the high compressor speed.

PLF(O.5) = 1-0.5X CD

where

EERB=energy efficiency ratio determined from test B In 2.8 P LF(O.f» = Part-load performance factor as determined from the equation:

Eu l(llIl F) = Electrical power Input measured using test A as outlined in 2.1.3.

Eu l(82 F) = Electrical power input measured from

using test A as outlined in 2.1.3.

The building cooling load BL (Ti) for

the four cases described in section 5.1.3.1

through 5.1.3.4 shall be obtained from the

following equation:

BL(T)= (5Xj)-3XQ:·~'(95 F)

'95-65 1.1

EER,yc.d,y

EER... d,y

l-CLF

1

(4) CD =

(1)

(3)

where

CLF=cooling load factor.

Q.. '"= Total steady-state cooling capacity from test C

(Btu/hr). T= Duration of time (hours) for one complete cycle consisting o( one compressor H on" time

and one COID.pressor Hoff" time.

The results of the cyclic and steadystate dry-coil performance tests shall be

used in the following (4) equations:

60X'VXC""xr

QCYC.d....=[V,,'X(l+ W,,)]

where

CD=Is the degradation coefficient described in 2.1.1 or as calculated in equation (4) above.

5.1.2 Method for calculating a SEER for

units with single-speed compressors and

multi-speed condenser fans. The seasonal

where

Q.... d,,=Total cooling over a.cycle comisting of one compressor "off" ~nod and one compressor . "on" period (Btu s). V=Indoor air flow rate (cfm) at the dry-bulb

temperature, humidity ratio, and pressure existing in the region of mpssttrement. C•• = Specific heat at constant pressure of air- water mixture per pound of dry air,

(Btu/lb-°F). V.' = Specific volmne of air-water mixtttre at the . same dry-bulb temperature, humidity ratio,

and pressure used in the determination of

the indoor sir flow rate (ft'/lb).

W.=Humidity ratio (lb/lb).

and r (hr.-OF), which is described by the

equation:

(2)

r = f(tlme Indoor fan off) [Ta1(t) - Ta2 (t)]dt

J(time Indoor fan on)

where

T.I(t)=Dry bulb temperature of air entering the

indoor coil (OF) at time (I).

T.2(t) = Dry-bulb temperature of air leaving the indoor

coil ("F) at time (t).

where

EERs= Energy efficiency ratio determined from test B as outlined in 2.1.1. P LF(O.5) = Part-load performance factor when cooling load factor=O.5 as determined from the

equation:

The preceding equations are then used

in the following equation to calculate a degradation coefficient CD rounded to the

nearest .01.

where

EER.•. d••= Energy efficiency ratio from test C. (Btu!

watt-hr).

5.1.1 Method for calculating a SEER for

units with single-speed compressor and

single-speed condenser fans. The seasonal

energy efficiency ratio for units employing

single-speed compressors and single-speed

condenser fans shall be based on the performance of test B and a method outlined

in 2.1.1 and 3.1.1 of this Appendix to

account for the cyclic performance.

The seasonal energy efficiency ratio in

Btu's/watt-hour shall be determined by

the equation:

SEER=PLF(0.5) XEERB

14

EE-RM-90-201 COMMENT OOR5
_________________________ARI STAN DARD 210-81

where

X [Ta2(t) - T.I(t)!dt

lating, and the average flow rate of indoor

air circulated in units of 1000 SCFM.

15

COP. y .(47)

COP••(47)

I-HLF

Q.y.(47)

Q••(47)XT

1

HLF

CD

(1)

The actual heating done during the

Cyclic Test, Q.,.•(47), shall be determined

using the following equation:

60XVXC""xr

lV"IX (l+W,,)]

V=the flow rate during the on-period calculated in

accordance with section 7.4 of ASURAE Slaud·

ard 37-78 in CFM.

Cpo=Specific heat at constant pressure of air-waler

mixture per pound of dry air, (Btu/lb-°F).

Vo' = Specific volume of air-water mixture at the same dry-bulb temperature. humidity ratio. aud

pressure used in the detennination of the indoor

air flow rate (ft'/Ib). W.=Humidity ratio (lb/lb).

and r (hr-OF), which is described by the

equation:

f

(time indoor fan off)

r = . . [T.2(t) - T.I(t)]dt (time mdoorfan on)

where

Tol(t) = Dry-bttlb temperature of air entering the indoor coil (OF) at time (I).

To,(t)=Dry-bulb temperature of alr leaving the indoor coil (OF) at time (I).

The net heating, QDEF {35) in Btu's

done dming the test period shall be determined using the following equation:

CD=the cyclic degradation coefficient roundcd to the nearest .01

COPcy.(47) as defined above

COP..(47) as defined above

H LF is the heating load factor calculated as follows:

where

v=the average of the alr flow rate calculated at four or more time intervals throughout the healing phase of the test usiug the equation iu section U

of ASH RAE Siandard 37-i8. Cpo = Specific heat at constant pressure of air-water

mixture per pound of dry air, (Btu/lb-OF).

Vn'=Specific voltune of air-water mhture at the same dry-bttlb temperature, humidity ratio, and pres- sure used in the determination of lite indoor air now rate (ft,!lb).

Wn=Utunidity ratio (lb{lb).

and r (hr.-OF), which is described by the

equation:

f

<time of next defrost termination)

r=

(time of defrost termination

(3)

where

To'(I)=Dry-bulb temperature of air entering the indoor coil <0 F) at time (I).

To'(I) = Dry-bulb temperature of airieaving the indoor

coil eF) at time (I).

The cyclic degradation coefficient shall

be calculated as follows:

where

(2)

Units not having an indoor fan as part

of the model tested shall add 1250 Btu/hI'

per 1,000 SCFM of indoor ail' handled to

the measured capacity to obtain the total

heating capacity, Q..(17), Q..(47) or

Q..(62), and add 365 watts per 1,000 SCFM

of indoor air handled to the measured

power to obtain the total power input,

B..(17), E..(47), or B..(62), to the unit.

The coefficients of performance (COP)

for the High Temperature Tests COP••(62) or COP..(47), and Low TemperatUl'e Test,

COP..(l7), are calculated as the ratio of

the heating capacity in Btu/hI' to the

product of 3.413 and the power inputs to

the indoor fan in watts and the power

inputs to the remaining equipment com- ponents (including all controls) in watts.

Units which do not have indoor air circulating fans furnished as part of the

model shall have their total heating done

(Q.y.(47» and energy used E.y.(47) in one complete cycle adjusted for the effert of

circulating indoor air equipment power.

For units tested without an indoor fan as part of the model, Q.y.(47) shall he increased by a quantity of heat equal to the

product of 1250 Btu/hr per 1,000 SCF:YI,

the length of the on-period of the test cycle

in hours, and the flow rate of indoor air

circulated in units of 1,000 SCFl\1. The

total energy usage, E.y.(47), shall be the sum of the energy usage required for air

circulation during the test cycle and the

energy used hy 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 required for indoor ail' circulation

equal to the quantity given by the product

of 365 watts per 1000 SCFM, the length of

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

the rate of indoor air circulated in units of

1000 SCFM.

The cyclic coefficient of performance,

COP.y .(47) is calculated as the ratio of the

total heating done (Q.y.(47» in Btu's to

the product of 3.413 Btu/watt-hour and the

total energy usage (Eoyo (47» in watt hours.

The net heating· capacity, QDEF(35)

(Btufhr), is the total net heating done over the test period (including any credit

for the indoor fan heat) divided hy the

total length of the test period, in hours.

For units with "demand defrost control system", the net heating capacity, QDEF(3.'i),

shall be multiplied hy an enhancement

factor of 1.07 to compensate for improved

performance not measured in the Frost

Accumulation Test. For units tested without indoor fans, the value determined for

(jDEP(35) below shall he increased by a quantity of heat equal to the product of

1250 Btu/hI' per 1000 SCFM, the length of time in hours during the Frost Accumulation Test that there was indoor ail' cil'-

culating, and the average flow rate of indoor air circulated in units of 1000 SCFM.

The total energy usage, E DEF(35) shall

he the sum of the energy usage required

for indoor-air circulation oming the test

period and the energy useo hy the remaining equipment components during the test

period. Units not having an indool' fan as part of the model tested, shall set the

energy required for indoor ail' circulation

equal to the quantity given hy the product

of 365 watts per 1000 SCFM, the length of

time in hours during the Frost Accumulation Test that there was indoor air circllas determined at each temperature bin

according to the applicable conditions described in sections 5.1.3.1 through 5.1.3.4 as folloVl'S:

5.1.3.5 Calculate the SEER in Btu's/

watt-hr. using the values for the terms

Q(T;)

z;r

5.2 Calculation of Heating Seasonal Performance Factors (HSPF) for AirSource Units.

The testing data and results required to

calculate the heating seasonal performance factor (HSPF), in Btu's per watt-hI', shall

include the following: (i) Heating capacities (Btu/hI') from

the indoor air enthalpy method fOl

the High Temperature Tests, and

the total heating done (Btu's) for

the cyclic and frost accumulation

tests.

Q..(47) or Q••(62).

Q..(17).

Q.y.(47).

QDEF(35).

(ii) Electrical powel' input to all com- ponents (watts) for the steady state

tests, and the electrical usage

(watt-hours) for the cyclic and frost

accumulation tests

k ..(47) or E..(62).

k ••(17).

E.y .(47).

EDEP(35).

(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 or dew point

Indoor dry bulb and

Indoor wet bulb.

(v) Data as specified in Table II of

ASHRAE Standard 37-78.

Where the heating capacities Q••(47),

Q••(62) and Q..(I7) and the indoor air

flow rate are calculated using the equations specified in section 3.8.1 and 7.4 of

ASHRAE standard 37-78. The total

heating done, Q.y.(47) and Q(DEP35) are calculated using the equations below.

±Q(T;)

. 1 N SEER-,,-:J=,.:c--- -± E(T;)

j=l N

5.1.4 Method for calculating a SEER for

units with two speed compressor, two com- pressor or cylinder unloading capable of

varying the sensible to total capacity (S/T)

ratio. Multi-speed compressor and twospeed compressor units capahle of varying

the sensihle to total capacity ratio (SIT)

shall have the seasonal energy efficiency

ratio determined as described in section

5.1.3. For such units, the mode of operation selected to c1etel'mine the steady-state capacities Q..k(95), Q..k(82), E•• k(95),

E.. k(82), and power inputs at each com- pressor speed k= 1, k=2, for tests A and B

is outlined in section 2.10.

E(T;)

""f./

and

EE-RM-90-201 COMMENT OOR5
r

ARI ST ANDAR D 210-81, _

where

lJ BL(T;) J HSPF

:z: as defined in 5.2.1 j

71; N as defined in 5.2.1

T j as defined in 5.2.1

where

{

. (65-ToD ) Ql;g2)(47) 60 ,for regions I,

= II, III, IV, and VI

Q;~-2)( 47), for region V

wtlcr.. Q..(47) and 1t'••(47) and QDE,.,(35)

Ilnd £ ..(47) and Q..(17) and 1t'..(17) are

the capacities (in Btu/hr) and pow~rs (in

watts), meallured during the High Temperature Tellt, the Frost Accumulation

test, and tht Low Temperature Test,

respectively.

'For each of lhe six regions specified in sec- tion 6.2.5, calculate the heating seasonal performance factors and seasonal operating costs

corresponding to the standardized maximum

and minimum design heating requirements and

for all other standardized design heating re- quirements (see section 6.2.6) belween the

maximum and the minimum.

5.2.2 Calculation of the heating seasonal

performance factor (HSPF) 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:

and BL(T;) is thp huilding load at temperature T;, in Btu/hI', calculated by:

BL( T j ) =(6~5~:£~) X(C) X(DHR)

where

(C}=O.ii is a correction fact.or which tends to improve the sgre.ement between calculated

and measured building loads

(DHR}=the minimum and maximum design heating requirement which t he heat pump is likely to encounter when installed in a residence,

rounded off to the nearest standardized DHR in section 6.2.V in Btu's per bour

where

(minimum design heating requirement)

and

(maximum design heating requirement)

{2

ilk-2(47) {65- TaD) f . I "".. 60' or regIOns ,

= II, III, IV and VI

. 2.2Q:-.-2(47) for region V

where

<2.. U-7) (4i) is the heat pump capacity measured during the high temperature perlormance test at 4;oF, with the unit operatine at the high compressor speed or with both

compressors in operation, in Btn/hr Too is the outdoor design temperature gi"en in section 6.2.4 in degrees OF.

and

17°F<T;<45°F

(E..(47) -E..(l7»

E..(l7) + 3~(T;-17),

T;'?,45°F or T;S;17°F

(EDEF(35) - E••(l7))

E ·(1~)+ X(T;-17) IS , 18'

17°F<Tj <45°F

(QDEF(35) -Q..(7»

Q

. (17) + X(Tj -17) '" 18'

(Q,,(47) -Q..(7»

. Q,,(7)+ 3~(T;-17),

T;'?,45°F or T;S;17°F

Q(T~) >1

(3.413)(E( T;» -

j

BL(T;) .

X(T;)= Q(.T;) iQ{T;)'?,BL(T;)

1; Q(T;)S;BL(Tj )

Q(T;) 1

or (3,413)(E( T;» <

TOFF= the outdoor temperature that the compressor is

automatically shut off at (If no such tempera- ture exists, Tj is always greater than Ton and

To,;.)

TOI<=the outdoor tempemlllre that the compressor is

automatically turned on (if applicable) if designed for low temperatnre automatic shutoff.

Co=degradation factor determined described in

section 5.2 and 2.2.1.

0; T; S; T OFF

PLF(X)=l-CD (l-X( Tj»

. n· [BL(T;)-Q(T;)X(T;)6(T;»)-N' RH(Tj )

N 3,413

where

<I" (4i) is the heat pump capacity measured during the High Temperature Test @ 4;0 F TOD is the outdoor design temperature given in

section 0.2.4

and Q(T~) >1

(3,413)(E( T;» -

and

maximum design heating requirement

{

. (65- TaD) . 2Q..( 47) 60 ' for regIOns I,

= II, III, IV, and VI

2.2Q..(47), for region V

E(T;)=

Q(T;)=

In using the above equation to calculate

HSPF, the heat pump capacity in Btu/hI',

Q, and the power in watls, E, shall be

obtained as follows:

~n; X(T,) . ~N PLF(X) 6(T;)E(T;)

+~ RH(T;)]

i N

where

Q",(47} as defined above

Q..(4i} as defined above

T = Dwation of time (hour.<) for one complete

cycle consisting of one compressor "on" time

8ud one compressor "oft" time.

BL(T;) J

where

(minimum design heating requirement)

{

. (65-TaD) _ Q..(47) 60 ,for regions I,

- II, III, IV, and VI

Q..(47), for region V

i=l,2,3, ..• , n corresponds to the it. tempera- ture bin.

n=total number of non-zero temperature bins

in the climatic rcgion.

Tj=(fii-5j) is the representative temperature of

the it. bin, (oF).

:&=indicated the Quanlit.y following the symbol j is to be summed over all temperature bins.

RH(Tj} =supplementary resistance heat term at N temperature Tj required in those cases where

the he.at pump automatically turns off

(Tj<T.,,) or when it is needed to meet the

balance of tbe building beating requir~ments.

n' (watts). ~=iS tbe number of hours in thej'. temperature • bip. divided by N=:& OJ and is referred to l>S , the "fractional hoursinjt. temperature bin".

30413=is a conversion factor whicb converts watt hours to Btu.

BLCTj}=building load at temperature Tjn (Btu/hr).

6(Tj}=heat pump low temperature cut-out factor.

X(Tj} = heat pump heating load factor.

PLF(X}=heat pump part load factor.

The Quantities BLCTj ) , 6(T;), X(T;),

PLF'(X)" and

where

RH(T;)

N

are defined by the following equations:

BUT;) =(6~5~:£~)(C)(DHR)

where

(C}=O.77 is a correction factor which tcnds to improve the agreement between calcnlated

and measured building loads

(DlTR}=the minimum and maximum design heating requirement which the heat pump is likel)' to enconnte.r when installed in a resid2f'.t"e"

rounded off to the neareststandardized D H R in section U.2G in Btu/lIr

5.2.1 Calculation of the heating seasonal

performance factor (HSPF) for air- source heat pumps with single speed

compressors.

For each climatic region listed in section

6.2.4, and for design heating requi!'ements

equal to both the sl.andardized minimum

lind maximum design heating requirements

de1iDed below, calculate the HSPF defined

as:

'HSPF

'These items have been corrected in accordance with a letter from the

Department of Energy, dated December 7, 1980.

16

EE-RM-90-201 COMMENT OOR5
_________________________ARI STAN DARD 210-81

NOTE: The sup€rscript'(A:=I) and (1:=2)

refer to the heat pump opera.ting at low

speed or single compressor operation and

high speed or two -compressor operation

respectively.

E(NT1) is the heat pwnp electrical energy usage in the

jtb temperature bin divided by the total

nwnber o( bin hollrS and is evalnated according to the (onr possible case!l o( heat pwnp

operation denoted below in _tts.

RHN'(T;) as defined In 5.2.1 and is evaluated according to the Cour possible o( heat pwnp operation denoted below (in watts).

ClUe I.-Units operating at low compressor speed or with a single compressor,

i.e., k= 1, for which the building heating

load, BL( T;) is less than or equal to the

heating capacity, ¢-t-l( Tj ).

BL( Tj ) Qk-l( T;)

E(Tj ) Ek-I(Tj)Xk-l(Tj)8'(Tj) nj

-r= PLFk-l N

Case III.-Units cycling on and off at

high compressor speed or cycling both com- pressors on and off together (k=2) in order

to satisfy the building heating load at temperature Ti•

Qk-t(Tj)<BL( T,)<Qk-2( Tj )

Ek-2( Tj )Xk-2( T i ) 0" ( T i ) lJ

PLFk-2

~BL( Tj )[l-&" (Tj »)

3.413

. (1..-1 (47)

(Q:.-1{62)-ll..-1{47»

X (Tj -47). +-----;1;-;5i-'-'--'--~,

~.-1(l7)

(Qbi:~(35) - ~.-1(17»)

X (T·-17) + 18';

170 F~Tj<40o F

tl.- 1 (17)

(~;l (47) - tl.,-I( 17»

X(T·-17) + 30 ' ;

Tj <17° F

RH(T;) lJ BL(Tj)[l-&'(T;»)

N 3.413

Xk-l(T;) BL(T;)

¢-t-I( T;)

PLFk-I=1-G,-1(1-X7- 1 )

{

O; Tj~ TOFF

&'(T;)=~; TOFF<T;~ToN

1; T1>ToN

Case II.-Units alternating between high

speed or two compressor operation (k=2)

and low speed or single compressor operation (k= 1) to satisfy the building heating

load at temperature Tj •

cjk-I( T;)<BL( T;)<(j<-2( T;)

E<J;) = [Ek-l( T;)Xk-l( Tj )

+Ek-2( T j )Xk-2( Tj »)&'( T /)

RH(T;) !jJ BL(Tj)[l-&'(Ti)]

N 3.413

Qk-2( T;) - BL( Tj )

Xk-l( Tj )

Qk-2( Tj)_Qk-l( T j)

Xk-2( T i ) = I-Xpl(T;)

{

O; Ti~ Ton

6'(Tj)~; TOFF<Ti5:.ToM

1; T;>ToN

{

O; Tj~ToFF

a"(T;)= ~; TOFF<T;~ToN

1; Tj>ToN

Case IV.-Units operating continuously

at high compressor speed or with both com- pressors in continuous operation (k=2) in

order to satisfy the building heating load

at temperature Tj •

BL(T;) ';?Qk-2(Tj )

E<:i) =Ek-2( Tj)Xk-2( Tj)o" (Tj ) lJ

RH(T;)

N

[BL( T j) - Qk-2( T j)Xk-2( T j )&"( Tj») lJ

3.413

Xk-2( Tj ) = 1.0

0; T;~ TOFF

or Qk-2(T/ ) <1

(3.413) (Ek-2( Tj »

~; Ton' T j 5:. TON

&"(T,') = Q' (T) d '-2 j > 1

an (3.413)(Ek-2(Ti )

1; T j';? TON

d Qk-2(T;) >1

an (3.413)(Ek-2(Tj»)

Where in each of the above cases

X(T;) = heat pnmp heating load (actor. PI,F=heat pnmp part load (actor (not reqnired [or cases 11 and IV.)

6"(T;) = heat pmnp low tempcratnre cnt-ont (actor.

To" as defined in 5.2.1.

Too as defined in 5.2.1.

Cvl -1=th. part load degradation [actor described in

section 2.2.1 and 5.2 [or the nnit cyding at high eompressor speed or with both com- pressors simnltaneonsly cycling (if applicable). Cv (l-I) = the part load degradation [actor described in

seclion 2.2.1 and 5.2 for the nnit cycling at low compressor speed or Wilh the single com· ~rthat nonnally operates at low heating

Q~-'(17)

(~.-' (47) - Q~.-'( 17)

X (T·-17) + 30';

Qk-2 (Tj ) = Q':.-' (17)

(€loEH35)- il..-'( 17)

X(T;-I7).

+ 18 '

17° F<Tj<45° F

E;;' (47)

(E~;l (62)-~-1(47)

+ ~X.:...:('-T-'-;--47---:.) .

15 '

T j ';?400 F

E~;'(17)

(EbEH35) -E~;'(17»)

+ --.-;~X.:...:('-T..:..j--17---:.) .

18 '

(E:;' (47) - E~-'( 17»

+ --:-:~X.:...:('-T..:..;-_17-'-) .

30 '

T j<17° F

E~;-2(17)

(E~-2( (7) - E';.-·( 17»)

+ ~X...:....:...(T-!-;-_1_7-,-).

30 '

T j ';?45° F or T j5:.lio F

E~.-·(17)

(Ett-}(35) - E~,-'(17»

+ ~-::X-,--,-,(T::...<;_-_l___:.7) .

18 '

17° F<T;<45° F

17

EE-RM-90-201 COMMENT OOR5
AR

I STAN DA R 0 210-81_

For each of the six regions specified in

section 6.2.5, calculate the heating sl'asonal

performance factors anel seasonal operating

costs corresponeling to the stanelarclized

maximum and minimum elesign heating requirement!! and for all othl'r standardized

design heating requirements (see section

6.2.6) between the maximum and the

minimum.

s.a CalculatiOlll1 of the Actual Repr6llentatitle Region41 Annual Perfonnance

Factorll for Air Source Central Air

Conditione", (Heal PumplI) Which

Prol'ide Both Healing and Cooli1Jg.

5.3.1 Calculation of actllal regional annual performance factors (APFA)

fora particular location and for

each standarelizeel (Iesign henting

requirement.

(CLHA

) (Q.l(95F»

(APF )= ~(HLH.'>(DHR)(C)

.• (CLHA )(Q.!(95F»

(SEER) +(HLH..

) (DH R) (C)

(HSPF)

where

(eLHA) Is th~ ll<'lnal coolinI': load honrs {or the p8rtirn)ar Ioration, determinE<! {rom the

• map in 8I'<'lion 1;.1.3.

(Q..'(95F» is defined in 5.1. (DHR) is defined In 5.2.2. (e) is defined in 5.2.2. (HLHA) Is the actnal htoeUnf( load bonrs {or the parti~ular Ioration d~lermined from Ibe map in _lion 6.2.5. (SEER) is the eeasonal en~rgy ~mci~nry rallo detennined in _lion 5.1. (1fSPF) is the htoetinf( _nal ~rtormanl'f'(aetors as detennhlt'd in _tion 5.2 lor _·h sland· ardized design htoeling reqnirem~nt within the parti~lllar Iorallon's region or for the ll<'tnal design heating reqniremrnt if

known.

where the particular location'll region is

determined from the map in section 6.2.,')

and, the standardized design hf'ating re- quirements within the rl'gion are (Ietermined in sections 5.2 and 6.2.6.

5.3.2 Calculation of rcprcscntativt' re- gional :lOnllal pelformance factors

(APF

R

) fOI' f"al'h rE-gion and for each

standardized design heating re- quirement.

(CLHR

) (Q••t(95F» +(HLHR)(DHR)(C)

(CLH

R)(Q.!(95F»

SEER +(HLHR

) (DHR)(C)

HSPF

(Q.-'(llIjF» Is dellned In 6.L (DHR) is dellned in 502.2. (e) II dellnedin 5.2.2.

18

where

(eLHa) III tbe represenlatln cooUng load bours for eaeh healing load houn region, as deter· mined in _lion 6.3-

(HLHa) is the representative heating load hours (or

each region as determined in &ecUon 6.2.5.

(SEER) is the seasonal energy elDcieney ratio as determined in aeolian 5.1.

(HSPF) Is the healing seasonal performance laelor as determined in seelion 5.2 for eaeh region and for each standardized design healing re- quirement within each region.

where the regions are listed in section 6.2.5

and, the standardized design heating re- quirements within the regions are fletermined in sections 5.2 and 6.2.6.

a.4 Calculations of Seasonal Energy Efficiency Ratio lor Water Souree UniUi

Which Provide Both Heating and

Cooling. (Reserved)

a..') Calculation of Heating Seasonal Performance Factor for Water Source

UniUi Which Pro/'ide Both Heatil/g and Cooling. (Reserved)

,').6 Calculatioll of Annual Performance

Factor For Water SOllree UniUi Which

Provide Both Healing and Cooling. (Reserved)

BlWHG COIlE 1450-0,....

EE-RM-90-201 COMMENT OOR5
-

6.0 Reference Material

6.1 Coolinq reference material

6.1. 2 -Distribution of fractional 

temperature bins to be use~ fo

of the SEER for 2-speed comp

compressor units

-Test operating and test condition

tolerance for cyclic dry-coil tests

Test

operating

tolerance

(total

observed

range) 1 ••... 65 to 69 .•. 67 

2 ••••• 70 to 74 ••• 72 

3 ••••. 75 to 79 .•• 77 

4 .•••. 80 to 84 ••• 82 

5 .••.. a5 to 89 ... 87 

6 .•••• 90 to 94 •.• 92 

7 .•.• , 95 to 99 .•• 97 

8 ••••• 100 to 104. 102 

6.1.1

Rea~ings, remarks

Outdoor dry-bulb air

temperature, Fahrenheit:

Entering •••••••••••••••••••••

Indoor dry-bulb air

temoerature, Fahrenheit:

Entering ••.••••.••.•..••. '" .

Indoor wet-bulb air

temperature, Fahrenheit:

Bnterilig •••••••..•••...••.••.

After the 1st 30 Sec after

comnressor startup.

External resistance to

airflow, inches water••..

Nozzle pressure drops,

percent of reading ..••..•.

Electrical voltage inputs

to the test unit, percent.

2.0

2.0

(* )

0.05

2.0

2.0

Test

condition

tolerance

(variation

of average

from

specified

test

condition)

0.5

0.5

(* )

0.02

Bin temperature

range

(degrees

Fahrenheit)

Bin No., j:

Representative temperature

bin fol'

(degrees

Fahrenheit)

Fra

to

D

bi

.....

\0

* Shall at no time exceed that value of the wet-bulb

ternoerature which results in the oroduction of condensate by the indoor coil at the dry-bulb temperatura

existing for the air enterina the indoor portion OF

the unit.
A'.skl - 0 Cooling Load Hours Cana' Zone - 6.000 .. .. .. Guam - 6.600

Hawaii - 2.300 .. .. Puerto Rico - 6.000

SI"'OO - 6.600 .. .. .. Virgin 'sland - 6.000 .. .. ..

N

o

88 0

"'- " 0

"

6.1. 3 Distribution of Actual Cooli~g Load Hours (C

Throughout the U~ilcd States
Beatiog Refe~eoce Material 6.2

6.2.1 Test op.rating aDd t.st coadit1on tol.ranca for

6.2.2 Tast. oneratUS- and-t..eat_J::o~t0111"nc.. ~

portion of. e)lclie ,ollrfocnanca, _ _ ._.

Staadr-Suu Il~h T~at1tte Tes: lu 47·' (8.3·C) or 62·F (16. 7·C»)

.N

L....,., T""'i"'rllt'=e Tut !n 17·F (-S.3·C»)

Te.t Op.rating Tol.ranc•

(Appllas alt.r th. lat 36 ••c. aft.r compr•••or

atart-up)

** T••t Condition Toleranca ia the aaximum p.rmi•••bl. va

••lua of the ....ure••nt fro. th••tand.rd or de.ir.d 

* T••t Op.rating Tol.ranca i. the maxi.um p.rmi•••bl. va

••nt. Wb.n .xpr•••ed a•• p.rc.nt.ga, th. maximum allo

the .pacifi.d percant.ge of the .v.r.g. v.lue.

..,

..,

Or

buring

La....ing

~tdoor vat-bulb, OF

tnt erine

Le.ving

Extarnal ra.i.tanca to .ir

flow, inches of v.tar

Elactric.l volt.g., :

Tut Op.rating*

Toleranc.

2.0

2.0

1.0

1.0

2.0

2.0

1.0

1.0

.05

'1.0

Te.t Conditionvv

Toleranc •

0.5

0.5

0.3

.02

Iodoor dry-bulb, of

Entering

Leaving

IodoOT v.t-bulb, OF

Entaring

LuviDg

Outdoor dry-bulb, or

Entariog

Leaving

Outdoor v.t-bulb, OF

Entering

Leaving

txtamal re.i.tance to air-flow,

inch•• of vatar

Electrical voltage, :

2.0

1.0

2.0

2.0

.05

2.0

N

.....

- Teat Op.r.tinc Tolar.nca i. the ••xi.um per.i•••ble v.riation ~£ an1 me ••ure-

••nt. Wh.n .xpr••••d a. a p.rtantag., the maximum .llow.bl. variation is t~e

ap.cified p.rcantaca of tha averag. v.lu••

*- Teat Condition Tol.ranca ia tha .aximum permi••able variation of the aver••e

value of the ••••ure.ent from the .t-and.rd or desired test condition.
N

N

6.2.3 TIIlI.C operat1D8 aad test condition tolerance. for frost

acc:Jmulat1oD celt'

6.2.4 'lis~d.but1on of fractional houn in temp

load hours and outdoor duign temperature 

cl1JDAUc regLons

Te.t Oplr.ting Tollr.nc. i. tb. aaximum plr.oiaa.bl. y.ri.tion of .ny me.aure-

.nt. When expreued ••• perc.nt.g•• the ...ill1:1ll1 .llov.ble yari.tion i.

the Ipecified percenuge of the avarag. valu.. Tut Operating Tolerailce Duri~g

Heating .ppUu vh.n the heat pUlllp ia in the hutina mode. except for the

Hrat 5 .inutu after t .....ination of • defroat cycle. Test Operating Tol.rance

During Defrolt .ppUaa duri"g • defrolt cycle and during til. firlt 5 .unutu

after tbe terainatioD of a dafron cycle vhaD the hut pump ia operating in

tbe beating aDd••

2 Tut Condition Tolera"c. ia thl maximwa permi...bll yariation of the .verage

value of the .uura..."t frOll the auncl.rd or cluired teat conclition. Telt

(ontlitioll Toluanc. appU.. oal, "".11 the beat pump ia operati". in the

b..tiD. _d••

, Ifot appl1cabl. dur1n& d.fro.t if the 1IIdoor fan 11 off .

Il.ctrical volug., :z: 2.0

Ent.ring 1. 5

Le.ving

External reli.tlnce to

.i....flov. incbu of v.ter .05

fI Pacllic: Coast Region

--- aegion I II II

Beating Load Bours, IlLIl 750 1250 17

Outdoor Design Temperatur'l

Too for the region 37 27 

Fractional Hours:

B1II , T1 (oF)

J • 1 62 .291 .215 .1

2 57 .239 .189 .1

3 52 .194 .163 .1

4 47 .129 .143 .1

5 42 .081 .112 .1

6 37 .041 .088 .1

7 32 .019 .056 .0

8 27 .005 .024 .0

9 22 .001 .008 .0

10 17 0 .002 .0

11 12 0 0 .0

12 7 0 0 .0

13 2 0 0 .0

14 -3 0 0 

15 -e 0 0 

16 -13 0 0 

17 -18 0 0 

18 -23 0 0 

.02

0.5

1.0

0.7

Tut Condition Tolerance(2)

(HeatIng Portion v::dyJ

4.0(3 )

10.0

2.0

1.0

2.0

Tuting Operating ToleranceO)

DuTlng He.clDt Durlog DeTroIt

Enuring

Le.Ying

Enuring

IA.Ying

Indoor vet-bulb. ·r

Outdoor dew-point. ·F

ladoor dry-bulb, ·r

Ent.ring

Le.Ying

Outdoor dry-bulb, ·r

..... -
Regional Heating Load Hours

N

W

6.2.5

VI

Region HL"g

I 750

II 1250

III 1750

IV 2250

V 2750

VI 2750

Actual heating load hours (ULHA) and regional heating load hours (ULH~ for the United States

2500

This map IS leasoniJlJlv acwlale tor Illost paIlS of Ule Ulliled Stales but is necessarilv hl!Jhlv

.ueneraltled. i11lj cOllsequenl1v nOI 100 accurale in mounlalllous regIOns, pal1lcula/ti in Ihe Rockies

IV

III

1500

II

Alaska

Hawaii a

Territor
ARI STANDARD 210-81

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

6.4 Ground Water Temperature Map (Reserved)

(FR Doc. 79-3a293 Filed 12-17-79; 8:45 am)

BILLING CODE 6450~1-C

24

EE-RM-90-201 COMMENT OOR5