ARI 210.240-94

1994 STANDARD for

AIR-CONDITIONING & REFRIGERATION INSTITUTE

UNITARY AIR= CONDITIONING

SOURCE HEAT PUMP EQUIPMENT

AND AIR=

I Standard 2101240 I

4301 NORTH FAIRFAX DRIVE 0 ARLINGTON, VIRGINIA 22203

IMPORTANT

SAFETY RECOMMENDATIONS

It is strongly recommended that the product be designed, constructed, assembled and installed in accordance with nationally recognized safety requirements appropriate for products covered by this standard.

ARI, as a manufacturers' trade association, uses its best efforts to develop standards employing state-of-the-art and accepted industry practices. However, ARI does not certify or guarantee safety of any products, components or systems designed, tested, rated, installed or operated in accordance with these standards or that any tests conducted under its standards will be non-hazardous or free from risk.

ARI CERTIFICATION PROGRAM PROVISIONS

Scope of the Certification Program

The Certification Program includes all unitary air-conditioning and air-source unitary heat pump equipment rated below 135,000 Btu/h [40 kw] at ARI Standard Rating Conditions (Cooling), as defined in Section 3.

Certified Ratings

The following Certification Programs ratings are verified by test:

Unitary Air-Conditioners (See Section 5.1) A. Air-Cooled under 65,000 Btu/h [ 19 kw]

1. ARI Standard Rating Cooling Capacity Btuh [wl 2. Seasonal Energy Efficiency Ratio. SEER. Btu/h/W [ w m

B. Air-Cooled from 65,000 Btuh [19 kWl to 135,000 Btu/h [40 kWl and Water-cooled and Evaporative Cooled all sizes 1. ARI Standard Rating Cooling Capacity. Btu/h [wl 2. Energy Efficiency Ratio. EER. Btu/h/W [Wm

Air-Source Unitary Heat Pump Equipment (See Section 5.1) A. Air-Cooled Under 65,000 Btu/h [ 19 kWl Single Phase Equipment

1. ARI Standard Rating Cooling Capacity, Btuh [wl 2. Seasonal Energy Efficiency Ratio. SEER. Btu/h/W W/WI 3. High Temperature Heating Standard Rating Capacity, Btu/h [wl 4. Region IV Heating Seasonal Performance Factor, HSPF. Btu/h/W [ W W Minimum Design Heating

Requirement

B. Air-Cooled from 65,000 Btu/h [ 19 kw] to 135,000 Btuh [40kWl 1. ARI Standard Rating Cooling Capacity. Btu/h [wl 2. Energy Efficiency Ratio. EER. B t u M [W/WI 3. High Temperature Heating Standard Rating Capacity. Btu/h Iw] 4. High Temperature Coefficient of Performance (COP 47°F) [COP 8.3"CI 5. Low Temperature Heating Standard Rating Capacity. Btu/h [wl 6. Low Temperature Coefficient of Performance (COP 17°F) [COP 8.3"CI

Conformance to the requirements of the Maximum Operating Condition Test, Voltage Tolerance Test, Low- Temperature Operation Test (Cooling), Insulation Efficiency Test (Cooling), and Condensate Disposal Test (Cooling), (see Section 6) are also verified by test.

Note:

This standard supersedes ARI Standard 210/240-89.

Price $20.00 (M) $40.00 (NM) Printed in U.S.A.

ams Wopyright 1994, by Air-conditioning and Refrigeration Institute - ma\. Registered United States Patent and Trademark Office

TABLE OF CONTENTS

SECTION PAGE

Section1 . Purpose . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1

Section2 . Scope . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1

Section 3 . Definitions . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1

Section 4 . Classification . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . - 3.

Section 5 . Testing and Rating Requirements . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 2

Section 6 . Operating Requirements . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 10

Section 7 . Marking and Nameplate Data . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 13

Section 8 . Voluntary Conformance .......................................... 13

TABLES

Table 1 . Classification of Unitary Air-Conditioners ............................. 3

Table 2 . Classification of Unitary Heat Pumps . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 4

Table 3 . Operating Conditions for Standard Rating and Performance Tests Using AppendixA . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 5

Table 4 . Operating Conditions for Standard Rating and Performance of Variable Speed Equipment Meeting the Requirements of Appendix A .................... 6

Table 5 . Operating Conditions for Standard Rating and Performance Tests Using ASHRAE Standud 37-1988 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 7

Table 6 . Minimum External Pressure . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9

FIGURES

Figure 1 . Part Load Factor Curve . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11

APPENDICES

Appendix A. Uniform Test Method for Measuring the Energy Consumption of Central Airconditioners . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 14

Appendix B. References. .............................. . . . . . . . . . . . . . . . . . 33

Appendix C. Prescriptive Methodology for the Cyclic Testing of Ducted Systems Required by Appendix A, Sections A4.1 and A4.2 . . . . . . . . . . . . . . . . . . 34

ARI STANDARD 210/240-94

UNITARY AIR-CONDITIONING AND AIR-SOURCE HEAT PUMP EQUIPMENT

Section 1. Purpose

1.1 Purpose. The purpose of this standard is to establish, for unitary equipment: definitions and classification: requirements for testing, rating and operating: marking and nameplate data and conformance conditions.

1.1.1 Intent. This standard is intended for the guid- ance of the industry, including manufacturers, engineers, installers, contractors, and users.

1.1.2 Review and Amendment. This standard is subject to review and amendment as technology advances.

Section 2. Scope

2.1 Scope. This standard applies to factory-made residential, commercial, and industrial equipment defined in 3.2 and 3.3..

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 apply to heat operated air-ConditioningJheat pump equipment, or packaged terminal air-conditionersheat pumps, or to room air-conditionersheat pumps.

2.2.2 This standard does no1 apply to unitary airconditioners as defined in ARI Standard 340/360-93 with capacities 135.000 Btu/h (40 k W ) or greater.

2.2.3 This standard does not apply to unitary heat pumps as defined in A R I Standard 340/360-93 with cooling capacities of 135,000 Bhlh (40 kW ) or greater, nor to water-source heat pumps as defined in ARI Standard 320-93 nor to ground water-source heat pumps as defined in A N Standard 325-93.

2.2.4 This standard does not include water heating heat pumps.

3.1

2.25 This standard does not apply to rating units equipped with desuperheater/water heating devices in operation.

Section 3. Definitions

Definitions. All terms in this document will follow the standard industry definitions in the current edition of ASHRAE Terminology of Hearing, Ventilation, Air Conditioning, and Refrigeration unless otherwise defined in this section.

Note: S e e Appendix A for definitions that apply to the testing and calculation procedures required by Appendix A.

3.2 Air-Source Unirary Heat Pump. An air-source unitary heat pump consists of one or more factory- made assemblies which normally includes an indoor conditioning coil(s), compressor(s), and outdoor coil(s), including means to provide a heating function. When such equipment is provided in more than one assembly, the separated assemblies shall be designed to be used together, and the requirements of rating outlined in the standard are based upon the use of matched assemblies.

3.2.1 Functions. Unitary heat pumps shall provide the function of air heating with controlled temperature, and may include the functions of air-cooling, air-circulating, air-cleaning, dehumidifying or humidifying.

3 3 Unitary Air-Conditioner. A unitary air-conditioner consists of one or more factory-made assemblies which normally include an evaporator or cooling coil(s), compressor(s), and condenser(s). 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.

33.1 Functions. The functions of unitary air-conditioners either alone or in combination with a heating plant, are to provide air-circulation, air-cleaning, cooling with controlled temperature and dehumidification, and may optionally include the function of heating and possible humidifying.

3.4 Published Rating. A published rating is a statement of .

the assigned values of those performance characteristics, under stated rating conditions, by which a unit may be

1

' 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 equipment or published in specifications, advertising, or other literature controlled by the manufacturer, at stated rating conditions.

35 Rating Conditions. Rating conditions are any se t of operating conditions under which a single level of performance results, and which causes only that level of performance to occur.

3.6 Energy Eficiency Ratio (EER). EER is a ratio calculated by dividmg the cooling capacity in Btu/h Iw] by the power input in watts [Wl at any given set of rating conditions, expressed in BtuflMr [Wm (While there is no direct SI Units equivalent, the analogous measure is a cooling COP.)

3.7 Seasonal Energy Eficiency Ratio (SEER). Seasonal Energy Efficiency Ratio is the total cooling of a central air-conditioner in 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 Appendices A (Section 4.1) and C.

3.8 Coefficient of Performance (COP) Heating. COP is a ratio calculated by dividing the total heat capacity provided by the refrigeration system including circulating fan heat, but excluding supplementary resistance heat, by the total elecmcal input in consistent units at any given set of rating conditions.

3.9 Heating Seasonal Petformanee Factor (HSPF). HSPF is the total heating output of a heat pump, including supplementary electric heat in Btu [kJ] necessary to achieve buildmg heating requirements during its normal annual usage period for heating lvided by the total elecmc power in watt-hours [Wh] during the same period, as determined in Appendices B (Section 4.2) and C.

3.10 Degradarion Coefficient (CJ. The C, is the measure of the efficiency loss due to the cycling of the units as determined in Appendices A and C.

3.11 Integrated Part Load Value (IPLV). A single number part load efficiency calculated per the method described in 5.2.2.

3.12 "Shall," "Should," "Recommended," or "It is Recommended." "Shall," "should," "recommended" or "it is recommended" shall be interpreted as follows:

3.12.1 Shall. Where "shall" or "shall not" is used for . a provision specified, that provision is mandatory if

compliance with the standard is claimed.

3.123 Shoatid, Recommended, or I t is Recommended. "Should," "recommended" or "It is recommended" is .-

used to indicate provisions which are not mandatory but which are desirable as good practice.

Section 4. Classification

4.1 Classifcution. Normally, unitary equipment within the scope of this standard may be classified as shoM In Tables 1 and 2.

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 ANSI/ ASHRAE Standard 37- 1988 and with the test methods, procedures and appendices as described in this standard.

The following types of air to air units rated less ,than 65,000 Btuh [ 19 kWl cooling or less than 65.000 Btu/h [19 kWl heating for heating only equipment shall be tested in accordance with Appendices A and C and rated at conditions specified in Table 3 or Table 4. .

SP-A; SPY-A; RCUY-A-CB; RCU-A-C; RCU-A-CB; HSP-A HOSP-A; HRCU-A-CB; HORCU-A-CB; HRCU-AX-: HORCU-A-C

All other types and/or capacities of equipment within the scope of thu standard shall have the capacity, EER and COP (as required) tested in accordance with ASHRAE Standard 37-1988 and rated at conditions specified in Table 5. SEER and/or HSPF may be determined on air-to-air equipment (as application ratings) at the option of the minufacturer.

Standard Ratings relating to cooling or heating capacities shall be net values. including the effects of circulating-fan heat but not including supplementary heat. Power input shall be the total power input to the compressor(s) and fan(s), plus controls and other items required as part of the system for normal operation.

Standard ratings of units which do not have indoor air-circulating f a n s furnished as part of the model, i.e., split system with indoor coil alone, shall be established by subtracting from the total cooling capacity 1250 Btu/h per lo00 cfm [775 W/m3/s], and by adding the same amount to the heating capacity. Total power input for both heating and cooling shall be increased by 365 W/lOOO cfm [226 W/m'/sl of indoor air circulated.

2


Table 1. Classification of Unitary Air-Conditioners

Types of Unitary Air-Conditioners

Desiqnation ARI Type Heat Rejection Arranqement I 1 I

Single Package SP-A SP-E SP-w

Air Evap Cond Water

Refrigeration Air RCH-A Chassis Evap Cond RCH-E

RCH-W Water

Year-Round Ai r SPY-A Single w-, Water SPY-w Package

Evap Cond SPY-E EVAP COND

Rem0 t e Air RC -A Condenser Evap Cond RC-E

RC-W pq ICONDJ Water COMP

Year-Round Ai r RCY-A Rem0 t e

Water RCY -W Condenser ( C O N D I Evap Cond RCY-E

COMP

Condensing Air RCU-A-C .Unit Coil

Water RCU-W-C Alone Evap Cond RCU-E-C

I Condensing

RCU-E-CB Unit Coil RCU-A-CB

RCU-W-CB and Blower

Air Evap Cond Water

Year-Round

Unit and Blower RCW-E-CB Condensing RCUY-A-CB

RCUY-W-CB

Air Evap Cond Water

I m

Extracted by permission from Table 1, Chapter 46. 1992, ASHRAE System and Equipment Handbook. A suffix of "-0" following any of the above classifications indicates equipment not intended for use with field-instdled duct systems (See 5.1.3.3b).

3


Table 2. Classification of Unitary Heat Pumps

'I

Designation t Single Package

Remote Outdoor Coil

1 Remote Outdoor Coil

with No Indoor 1 Fan

I System I

I Fan 1 with No Indoor Split System

'ypes of Unitary Air-Source Heat

Heating and Heating Only

HSP-A HOSP-A

HRC-A-CB HORC-A-CB

~~

HRC -A- C HORC-A-C

HRCU-A-CB HORCU-A-CB

HRCU-A-C HORCU-A-C

Pumps

Arrangement

INDOOR OUTDOOR

I FAN

FAN COMP I

COMP

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 lo00 Btuh [34.1 W per 1000 w] cooling capacity.

5.1.1 Values of Standard Capacity Ratings. These ratings shall be expressed only in terms of Btu/h in multiples of

Capacities Multiples BUbLYLl . € i t & N l

Less than 20,000 [5,900] 100 [30]

20,000 up to 38,000, 200 [60] [5.900 up to 11,0001

38,000 up to 65,000. 500 [ 1501 [ I 1,000 up to 19,0001

65,000 and above. loo0 [300] [ 19,000 and above]

5.13 Values of Measures of Energy Eficiency. Standard measure of energy efficiency, whenever published, shall be expressed in multiples of the nearest 0.05 Btu/h per W [0.01 W per w] for EER, SEER and HSPF. Coefficients of performance (COP) for heating or cooling, whenever published, shall be expressed in multiples of the nearest 0.02. [0.005].

5.13 Standard Rating Tests. Tables 3, 4 and 5 indicate the test and test conditions which are required to determine values of standard capacity ratings and values of measures of energy efficiency.

5.13.1 Assigned Degradation Factor. In lieu of conducting C and D tests or the heating cycling test, an assigned value of 0.25 may be used for the degradahon coefficient, C, for either the cooling C,, or both. For units with two compressor speeds, two compressors or cylinder unloading, if the assigned degradation coefficient is used for one cooling mode, it must be used for both cooling modes. If the assigned degradation

4


Table 3. Operating Conditions for Standard Rating and Performance Tests Using Appendix A r I

TEST i Conditions

"B" Cooling Steady State

"C" Cooling Steady State

"D' Cooling Cyclic

Low Temperature Operation Cooling

Insulation Efficiency

Condensate Disposal

Maximum Operating Conditions I

HEATING Standard Rating Conditions High Temperature Heating' Steady State

High Temperature Heating

High Temperature Heating4

Low Temperature Heating Steady State

I Frost Accumulation I 1

Maximum Operating Conditions

- INDOOR UNIT

Air Entering

DB WB "F ["Cl

67 [ 19.41 80 f26.71

O F [" CI

80 [26.71

575 [13.9] 80 l26.71

67 [19.4]

80 c26.71 575 . [13.9]

67 [19.4] 57 [13.9]

80 [26.7]

80 [26.7]

75 [23.9] 80 [26.7]

75 [23.9]

67 [ 19.41

70 [21.1] 60 [ 15.61 ( m a )

70 [21.1] 60 [ 15.61 ( m a )

70 [21.1] 60 [ 15.61 ( m a )

70 [21.1] 60 [ 15.61 ( m a )

70 [21.1] 60 C15.61 ( m a )

80 [26.7] -

OUTDOOR UNIT

82 [27.8]

65' [ 18.31 82 [27.8]

65' [ 18.31

82 [27.8] 65' [ 18.31

67 [19.4] 57' t13.91

80 [26.7]

75' 123.91 80 [26.7]

75* r23.91

75' L23.91 115 [46.1]

47 L8.31 43 f6.11

62 116.71 56.5 i13.61

17 [-8.31 15 [-9.41

35 [1.7] 33 ' [0.6]

75 [23.9] 65 f18.31

1. S h e conditions used for Voltage Tolerance Tests. 2. The wet bulb temperature condition is not required when testing air-cooled condensers which do not evaporate

3. Same conditions used for Voltage Tolerance Tests (Heating-only units). 4. For two speed, two compressor or units with compressor unloading capability. 5. Wet bulb sufficiently low that no condensate forms on evaporator.

condensate.

5


Table 4. Operating Conditions for Standard Rating and Performance of Variable Speed Equipment Meeting the Requirements of Appendix 1

I n

INDOOR COIL

AIR ENTERING TEST

WE!

Intermediate Cooling Steady State

High Temperature Heating

70 [21.1] Frost Accumulation' At Maximum &=2) and/or

At Minimum &=1) Compressor Speed 60 115.61 70 121.11

At Maximum &=2) Compressor Speed 60 I 15.61 70 121.11 Low Temperature Heahng

Intermediate &=i) Compressor Speed 60 115.61

~~

OUTDOOR COIL

AIR Eb

DB "F [ T I

95 [35.0]

82 . [27.8]

82 127.81

67 [ 19.41

67 [19.4]

67 [19.4]

87 130.61

47 18.31

62 [ 16.71

62 I 16.71

17 18.31

47 18.3)

35 11.71

17 [-8.3[

ERING

WE! "F r q 75l 123.91

65' I 18.31

65' 118.31

5 3 s 1 11.91

53.5l [ I 1.91

53.5' [11.9]

69' [20.6]

43 i6.11

56.5 11 3.61

56.5 [ 13.61

1 3 16.11

53 16.11

33 10.61

15 1-9.41

All tests are performed at the outdoor fan speed and indoor blower speed Intended for normal operatlon.

NOTES: 1. Not maintained if no condensate rejected to outdoor coil. 2. Optional test used to determine the Designed Heating Requirement @HR). The nominal s p e d is the lesser of the cooling and heating maximum

3. Optional equations may be used in lieu of the maximum speed test. The intermediate speed is the same as the cooling intermediate speed. 4. Wet bulb sufficiently low that no condensate forms on evmrator.

speeds.

6


: I

I

7

ARI STANDARD 210~40-94

coefficient is used for one heating mode, it must be used for both heating modes.

5.13.2 Electrical Conditions. Recommended nameplate voltages are shown in Table 1 of ARI Standard 110-90. Standard Rating Tests shall be performed at the nameplate rated voltage and

. frequency.

For equipment which is rated with 208-230V dual nameplate voltages and is air-to-air rated less than 65,000 Btu/h [ 19 kWl cooling (or less than 65.000 Btub [19 kWl at 47°F [8.3"C] outdoor ambient heating for heating only heat pumps), Standard Rating Tests shall be performed at 230 volts. For all other dual nameplate voltage equipment covered by this standard. the 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. .

5.133 Indoor-Side Air Quann'ty. All Standard Ratings shall be determined at an indoor-side air

. quantity as outlined below. All air quantities shall be expressed as cfm of Standard Air (scfm) as defined in the 1993 ASHRAE Fundamentals Hand- book, Chapter 2.

a Equipment with indoor fans intended for use with field installed duct systems shall be rated at the indoor-side air quantity (not to exceed 37.5 scfm per 1,000 Btu/h [60.4 SL/s per lo00 Wl of rated capacity) delivered when operating against the minimum external resistance specified in 5.1.3.6 or at a lower indoor-side air quantity if so specified by the manufacturer.

b. Equipment with indoor fans not intended for use with field .installed duct systems (free discharge) shall be rated at the indoor-side air quantity delivered when operating at 0 inches of water [O Pal external pressure as specified by the manufacturer.

c. Equipment which does not incorporate an indoor fan, but is rated in combination with a device employing a fan shall be rated as described'under a. above. For equipment of this class which is rated for general use to be applied to a variety of heating units, the indoor-side air quantity shall be specified by the manufacturer in his standard ratings, not to exceed 37.5 scfm/lOOO Btu/h [60.4 SL/s per lo00 Wl of rated capacity of the air quantity obtained through the indoor coil assembly when the pressure drop across the indoor coil assembly and the recommended enclosures

8

and attachment means is not greater than 0.30 inches of water [74.6 Pa], whichever is less. --

Indoor-side air quantities and pressures as referred to herein apply to the air quantity experienced when the unit is cooling and dehumidifying under the conditions specified in this section. This air quantity, except as noted in 5.1.3.3b and 6.4, shall be employed in all other tests prescribed herein . without regard to resulting external static pressure. Heating only units shall use the air quantity experienced when the unit is operating under the High Temperature Heating Standard Rating Conditions test.

5.13.4 Ourdoor-Side Air Quantity. All standard ratings shall be determined at the outdoor-side air quantity specified by the manufacturer where the f a n drive is adjustable. Where the fan drive is non-adjustable, they shall be determined at the outdoor-side quantity inherent in the equipment when operated with all of the resistance elements associated with inlets. louvers. and any ductwork and attachments considered by .the manufacturer as normal installation practice. Once established, the outdoor side air circuit of the equipment shall remain unchanged throughout all tests prescribed herein. -

5.135 Requirements for Separated Assemblies. All standard ratings for equipment in which the outdoor section is separated from the indoor section, as in Types RC, RCY. RCU. RCW, HRC, HORC, HRCU and HORCU (shown in Section 4). shall be determined with at least 25 feet [7.6 m] of interconnection tubing on each line of the size recommended by the manufacturer. Such equipment 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 [7.6 ml of tubing, whichever is greater. At least 10 feet [3 m] of the interconnection tubing shall be exposed to the outside conditions. The line sizes, insulation, and details of installation shall be in accordance with the manufacturer's published recommendation.

5.13.6 Minimum Exrernal Pressure. Indoor air-moving equipment intended for use with field installed duct systems shall be designed to operate against and tested at not less than, the minimum external pressure shown in Table 6 when delivering the rated capacity and air quantity specified in - 5.1.3.3. Indoor air-moving equipment not intended for use with field installed duct systems (free discharge) shall be tested at 0 inches of water [O Pal external pressure.


Table 6

Minimum External Pressure I I

Standard Capacity Ratings himum External Resistance I I

(Thousands of S a ) [kw] (Inches of Water) [Pa]

Up thru 28 [up thru 8.21

43 thru 70 [ 12.6 thru 20.51 0.15 [37.4] 29 thru 42 [8.5 thru 12.41 0.10 124.91

0.30 [74.7] 106 thru 134 [31.1 thru 39.31 0.25 [62.3] 71 thru 105 [20.8 thru 30.81 0.20 [49.8]

Cooling capacity for units with cooling function: High Temperature Heating Capacity for heating- onlv units (See 5.1.3.3).

Interpreting this requirement, it is understood that the most restrictive filters, supplementary heating coils, and other equipment specified as part of the unit be in place and.that the net external pressure specified above is available.

5.13.7 Moismre Removal Determination. Indoor air moisture removed shall be determined at Standard Rating Conditions, Cooling for units tested in accordance with both ASHRAE Standard 37-1988 and Appendix A. The expression of the removal rate shall be based upon the net cooling capacity, including an allowance of 1250 Btu/h per 1,000 cfm [775 W/m2/s] fan heat for blowerless equipment.

5.2 Part Load Rating. Systems which are capable of capacity reduction shall be rated at 100% and at each step of capacity reduction provided by the refngeration system(s) as published by the manufacturer. These rating points shall be used to calculate the IPLV (see 5.2.2).

a. Determine the capacity and EER at the conditions specified in 5.2.

b. Determine the part-load factor (PLF) from Figure 1 "Part-Load Factor Curve" at each rating point (see example Appendix D).

c. Use the following equation to calculate IPLV:

PLY = (PU, - PLF,) ( =I + EQG) 2

+ (PLF, - PIT$ ( EER, + w ' >

2

52.1 Part Load Rating Conditions. The conditions of test for part load ratings shall be per Table 5 .

where: Any water flow required for system function shall be at water flow rates established at (full load) Standard Rating Conditions.

The capacity reduction means may be adjusted to obtain the specified step of unloading. No manual adjustment of indoor and outdoor air quantities from those of the Standard Rating Conditions shall be made. However, automatic adjustment of air quantities by system function is permissible.

53.2 Integrated Part Load Value (IPLV). For equipment covered by this standard, the IPLV (in EER) shall be calculated as follows:

PLF = Part-LoadFactor determined from Figure I

n = Total number of capacity steps

Superscript 1 = 100% capacity and.EER at part-load rating conditions

Subscript 2; 3 etc. = specific capacity and EER at part-load steps per 5.2.

9

ARI STANDARD 210t240-94

5 3 Application Ratings. Ratings at conditions of temperature or air quantity other than those specified in 5.1.3 and 5.2.1 may be published as application ratings, and shall be based on data determined by the methods prescribed in 5.1. Application ratings in the defrost region shall include net capacity and COP based upon a complete defrost cycle.

5.4 Publication ofRatings. Wherever application ratings are published or printed, they shall include, or be accompanied by the Standard Ratings plus the Part Load Rating (where applicable), clearly designated as such, including a statement of the conditions at which the ratings apply.

5.4.1 Capacify Designation. The capacity designation used in published specifications, literature or advertising, controlled by the manufacturer, for equipment rated under this standard, are to be expressed only in Btu/h [Wl at the Standard Rating Conditions specified in 5.1.3 plus Part Load Rating Conditions specified in 5.2.1 and in the terms described in 5.1.1 and 5.1.2. Horsepower, tons or other units shall not be used as capacity designation.

5.4.2 Moisture Removal Designation. The moisture removal designation shall be published in the manufacturer's specifications and literature or a statement, in such publications, shall be made to advise the user that thls information is available upon request. The value shall be expressed in one or more of the following forms:

a. Sensible (net) capacityhotal (net) capacity ratio

b. Latent capacity and total (net) capacity c. Sensible (net) capacity and total (net) capacity.

55 Tolerances. To comply with this standard, published cooling capacity(s), heating capacity(s), and. efficiency ratings, and/or seasonal energy ratios shall be based on data obtained in accordance with the provisions of this section, and shall be such that any product 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 percent.

and total (net) capacity.

Section 6. Operating Requirements

6.1 Operating Requirements. To comply with this standard, unitary equipment 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 equipment shall be designed and produced to pass the following maximum operating conditions test with an indoor coil air quantity as determined under 5.1.3.3.

.lo

63.1 Temperature Conditions. Temperature conditions shall be maintained as shown in Tables 3 or ..

5.

6 2 3 Voltages. The test shall be run at the Range A minimum utilization voltage from ARI Standard 1 10-90, 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 equipment shall be operated for one hour at the temperature conditions and voltage specified.

6.2.4 Requiremenrs. The equipment 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 [lo3 Walt measured across the unit.

6 3 Voltage Tolerance Test. Unitary equipment shall be designed and produced to pass the following voltage tolerance test with a cooling coil air quantity as determined under 5.1.3.3.

63.1 Temperature Conditions. Temperature conditions shall be maintained at the Standard Cooling (and/or Standard Heating, as required) steady state conditions as shown in Table 3, Table 4 or Table 5.

6 3 3 Voltages.

6.3.2.1 Tests shall be run at the Range B minimum and maximum utilization voltages from ARI Standard 110-90, 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 minimum or a higher maximum voltage shall be used, if listed on the nameplate.

6.3.2.2 The power supplied to single phase equipment shall be adjusted just prior to the shutdown period (see 6.3.3.2) so that the resulting voltage at the unit's service connection is 86 percent of nameplate rated voltage when the compressor motor is on locked-rotor. (For 200V or 208V nameplate rated equipment the restart voltage shall be set at 180V when the compressor motor is on locked rotor). Open circuit voltage for three-phase equipment shall not be greater than 90 percent of nameplate rated voltage.


PERCENT OF FULL-LOAD CAPACITY AT PART-LOAD CONDITIONS

Note: Curve is Based on.Following Equation:

PLF = A 0 + (A1xQ)+(A2xQ' )+ (A3xQ3)+ (A4xQJ)+ (A5xQ5)+ (A6xQ' )

where: PLF = Part-Load Factor Q = Percent of full-load capacity at part-load rating

conditions. A 0 = -0.12773917 X lo-'' A1 = -0.27648713 X l o - ' A 2 = 0.50672449 x A 3 = -0.25966636 X lo-' A4 = 0.69875354 x 10 - " A5 = -0.76859712 X l o - " A6 = 0.28918272 x 10- I "

1

Figure 1. Part Load Factor Curve

11

6.3.23 Within one minute after the equipment has resumed continuous operation (See 6.3.4.31, the voltage shall be restored to the values specified in 6.3.2.1.

633 Procedure.

6.33.1 The equipment shall be operated for one hour at the temperature conditions and voltage(s) specified.

6.3.32 All power to the equipment shall be cut off for a period sufficient to cause the compressor to stop (not to exceed five seconds) and then restored

63.4 Requirements.

6.3.4.1 During both entire tests, the equipment shall operate without failure of any of its parts.

6.3.4.2 The equipment shall operate continuously without interruption for any reason for the one hour period preceding the power interruption.

6.3.43 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-Temperarure Operarion Tesr (Cooling). (Not required for h&g-only units.) Unitary equipment shall be designed and produced to pass the following low-temperature operation test when operating with initial air quantities as determined in 5.1.3.3 and 5.1.3.4 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. Temperature Conditions shall be maintained as shown in Table 3 or Table 5.

6.4.2 Procedure. The test shall be continuous with the unit on the cooling cycle, for not less than four hours after establishment of the specified temperature conditions. The uni t will be permitted to start and stop under control of an automatic limit device, if provided.

6.43 Requirements. 6.43.1 During the entire test, the equipment shall operate without damage or failure of any of its parts.


6.43.2 * During the entire test, the air quantity shall not drop more than 25 percent from that --

determined under the Standard Rating test.

6.433 During the test and during the defrosting period after the completion of the test, all ice or meltage must be caught and removed by the drain provisions.

6.5 Insulation Eficiency Test (Cooling). (Not required for heating-only units.) Unitary equipment shall be designed and produced to pass the following insulation efficiency test when operating with air quantities as determined in 5.1.3.3 . and 5.1.3.4 with controls, fans, 'dampers, and grilles s e t to produce the maximum tendency to sweat, provided such settings are not contrary to the manufacturer's instructions to the user.

65.1 Temperature Conditions. Temperature conditions shall be maintained as shown in Table 3 or Table 5. .

65.2 Procedure. After establishment of the specified temperature conditions, the unit shall be operated continuously for a period of four hours.

653 Requiremenrs. During the test. no condensed water shall drop, run. or blow off from the unit casing. -

6.6 Condensare Disposal Test (Cooling)*. (Not required for heating-only units.) Unitary equipment 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 5.1.3.3 and 5.1.3.4 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.

* Thls test may be run concurrently with the Insulation Efficiency Test (See 6.5).

6.6.1 Temperature Condirions. Temperature Condi- tions shall be maintained as shown in Table 3 or Table 5.

6.62 Procedure. After establishment of the specified temperature conditions, the equipment 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.

6.63 Requirements. During the test, there shall be no dripping. running-off, or blowing-off of moisture from the unit casing.

12

ARI STANDARD 21Oi240-94

6.7 Tolerances. ' The conditions for the tests outlined in Section 6 are average values subject to tolerances of f 1 .o" F [fo.6"C] for air wet-bulb and dry-bulb temperatures, f 1 .O percent of the reading for voltages.

Section 7. Marking and Nameplate Data

7.1 Marking and Nameplate Data. The nameplate shall display the manufacturer's name, model designation. and electrical characteristics.

Recommended nameplate voltages for 60 Hem systems include one or more of the utilization voltages shown in Table 1 of AM Standard 110-90. Recommended nameplate voltages for 50 Hertz systems shall include one or more of the utilization voltages shown in Table 1 of IEC Standard Publication 38.

Section 8. Voluntary Conformance

8.1 Conformance. While conformance with this standard is voluntary, conformance shall not be claimed or implied for products or equipment within i ts Purpose (Section 1) and Scope (Section 2) unless such claims meet all of the requirements of the Standard.

13

"


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

Foreword This ap ndix to ARI Standard 210/240-94

is denvefirom the appropriate combinin and editing by ARI of "Uniform Test Metho! for Measurin the Energy Consumption of

Subpart B, pages 76707 through 76723, Fed- Central Air-Eonditioners" Appendix M to

eral Register, Vol. 44, No. 249, Thursday, De- cember 27,1979 and "Part 430-Energy Con- servation Program for Consumer products," pa es 8311 through 8319 (omitting pa e 8312 an5 parts of pages 8311 and 8313), federal Register, Vol. 53 No. 49, Monday, March 14, 1988. Note the prefix A has been added to all section numbers in this appendix for clarity (to avoid confusion with section numbers in the standard).

Appendix M to Subpart B-Uniform Test Method for Measuring the Energy Consumption of Central Air ,

Conditioners

Al . Definitions

A l . l 'Annual performance factor" means the total heating and cooling done by a heat pum in a particular region in one year di- vide$ by the total electric power used in one year. Ala "F m v Air-Conditioning and Re- frigerauon Instatute. Al3 "ARI Standard 210/240-94" means the test standard published in 1994 by the ARI and titled W n i t a y Au-Conhtioning and Air- Source Heat Pump Equipment". Al.4 'ARI Standard 320-93" means the test standard published in 1993 by ARI and titled Water-Source Heat Pumps". A15 'ASHRAE" means the American Soci- ety of Heating, Refrigeration and Air-Condi- tioning Engineers, Inc. Al.6 'ASHRAE Standard 37-88 means the test standard published by ASHRAE in 1988 and titled 'Methods of Testing for Rating Un- itary Aw-Conhtioning and Heat Pump Equip ment." A1.7 "Continuously recorded" means a method of recording measurements in intervals no greater than 5 seconds. AlS "Cooling load factor (CLF)" means the

cycle of a specified time period. consisting of ratio of the total cooling done in a complete

coo- done over the same period at constant an -on" time and "off time, to the steady-state

ambient conditions. Ala "Cyclic Test" means a test where the indoor and outdoor conditions are held constant, but the unit is manually turned "on" and "of€" for specific time periods to simulate part-load operation. Al.10 Pegradation coefficient (CD)" means the measure of the efficiency loss due to the cycling of the unit. Al.11 "Demand-defrost control system"

the defrost function on the outdoor coil of the means a system which is designed to perform

heat pump oniy when a predetermined degradation of performance is measured.

Note: The following examples of ?e- tions are offered (reference James A m&

Department of Energy, letter of November 23, 1981 to Robert Newell, Rheem A/C Div.):

"Examples which comply are:

2. differential temperature ( c o i l to ambient 1. differential alr pressure sensors,

air). 3. feedback systems that measure length of

defrost period and adjust defrost frequency accordingly,

4. systems that measure outdoor fan

5. optical sensors. power, and/or current,

monitor at least one parameter which always A demand defrost system must be able to

varies with the amount of frost accumulated on the outdoor coil of the heat pump. When this parameter reaches a certain value, the

the defrost can be accomplished by measuring system initiates a defrost. The termination of

elimination of frost from the coil. any parameter that can be used to sense the

Systems that vary defrost intervals according to outdoor dry-bulb tem rature are not demand defrost systems. R i s is because knowledge of dry-bulb temperature only pre- dicts the Occurrence of frost. A demand defrost system must function in response to a parameter which varies directly with frosting.

When a demand defrost system is used in conjunction with a time-initiated defrost system, the combination will not be considered a demand system iftime initiated defrosts occur more fiquently than every 6 hours of compressor operating time."

A1.12 'Design heating requirement (DHR)" is the amount of heating required to maintain a given indoor temperature at a particular outdoor design temperature. A1.13 Prycoi l test" means a test conducted

temperature such that moisture will not con- a t a wet-bulb temperature and a dry-bulb

dense on the evaporator coil of the unit. A1.14 'Heating seasonal performance factor (HSPF)" means the total heating output of a heat um during its normal annual usage

power input during the same period. A1.15 "Heating load factor (HLF)" means the ratio of the total heating done in a complete cyde of a speafied time period, consisting of an 'LI" time "off time, to the steady state heating done over the same period at constant ambient conditlons. Al.16 "Latent cooling" means the amount of cooling in Btu's neessaxy to remove water va- por from the air assing over the indoor coil by condensation c f k n g a period of time. Al.17 "Part-load factor (PLF)" means the ratio of the cy&c ene effiaency ratio to the steady-state energy ezciency ratio at identical ambient conditions. Al .18 "Seasonal energy efficiency ratio (SEER)" means the total cooling of a central air conditioner in Btu's during its normal annual usage period for coolrng divided by the total electric power input in watt-hours during the same period. Al.19 'Sensible cooIing" means the amount of coo? in Btu's performed by a unit over a period o tune. excluding latent cooling. Al.20 "Single package unit" means any cen-

perid for i eatmg . dmded ' . by the total electric

tral air conditioner in which all the major assemblies are enclosed in one cabinet. A131 "Split system" means any central air conditioner in which one or more of the major assemblies are separate from the others. A1.22 "Steady-state test" means a test in which all indoor and outdoor conditions are held constant and the unit is in non-changing operating mode. A123 Temperature bin" means a 5 F inme- ment over a dry-bulb temperature range of 65 F through 104 F for the cooling cycle and - 25 F through 64 F for the heating cycle. A1.24 "Time-temperature defrost control system" means a system whch automatically

mined time interval whenever the outdoor provides the defrost function a t a predeter-

temperature drops below a level where frost-

Al.25 T e s t condition tolerance" means the maximum permissible variation of the aver- aee of the test observations from the standard

ingWillOCCUr.

oFdesired test condition as provided inA6.1.1, A6.2.2, and A6.2.3. Al.26 Test operating tolerance" me- the maximum permissible difference between the maximum and the minimum instrument ob-

A6.2.1, A6.2.2 and A6.2.3. servation during a test as provided in A6.1.1,

A1.27 "Wet-coil test" means a tes t conducted at a wet-bulb temperature and a dry- bulb temperature such that moisture will con- dense on the test unit evaporator coil. A 1 3 "Central air conditioner" (DOE Cov- ered) means a product, other than a packaged terminal air conditioner powered by single phase electric current. which is air-cooled, rated below 65,000 Btuh, not contained within the same cabinet as a furnace, the rated capacity of which is above 225.000 Btuh, and is a heat pump or a cooling only unit. Al.29 "Heat pump" (DOE Covered) means a product, other than a packaged terminal heat pump, which consists of one or more assemblies, powered by single phase electric current, rated below 65,000 Btuh, utiliz' indoor conditioning coil, compressor, 3 2 frigerant-to-outdoor air heat exchanger to provide air h e a 3 . and may also provide air amling, dehum ymg, humidifying drculat- ing, and am cleaning. A130 "Coil family" means a p u p of wi with the same basic design features that af- fect the heat exchanger performance. These features are the basic c o d tion, Le., A- shape, V-shape, slanted or E o p , the heat transfer surfaces on refi rant and air sides

tube and fin matenals. and the cod mtry. When a group of coils has all these features in common. it constitutes a 'coil family."

A2. Testing R e q u i d

A2.l Testing required for air source cooling only units. Two steady state wet coil tests are mquirt+ to be performed test A and test B. Test A IS to be conducted as an outdoor dry bulb temperature of 95 F and test B at 82 F. Test C and D are optional tests to be conducted when cyclic performance parameters

(flat tubes ys. grooyed tUEs, fin *pes),. the

14

ARI STANDARD 210/240-94 - are to be measured in order to determine the degradation coefficient, C, Test C is a steady state dry coil test conducted at an outdoor dry bulb temperature of 82 F. Test D is a cyclic test also conducted at an outdoor dry bulb temperature of 82 F. In lieu of conducting tests C and D, an assigned d u e of 0.25 may be used for the degradation coefficient, C,. ~U.1.1 Testing requwed for units with singk speed compressors and single speed condenser fans. Test A and test B shall be perform+ A4.1 of t%is Appendix. In addition, the cyclic accordin to the test procedures outhned m

test C and D according to the requirements performance shall be evaluated by conducting

outlined in A4.1. A2.1.2 Testing required for units with single speed compressors and multiple-speed condenser fans. The test requirements for multiple-speed condenser fan units shall be the

speed condensor fan units. same as described in section A2.1.1 for single

A2.1.3 Testing required for units with two- speed compressors, two compressors, or cylinder unloading. The test requirements for two- speed compressor units, two compressor units, or units with cylinder unloadmg are the

A and test B shall be performed at each com- same as described in A2.1.1 except that test

pressor speed or at each compressor capacity. U1.4 Testing required for units with two-

der unloading capabk of varying the sensible speed compressors, two compressors. or cylin-

to total (S/T) capacity ratw. When a unit employing a two-speed compressor, two compressors, or cylinder unloatbg provides a method of varying the ratio of the sensible cooling capacity to the total cooling capacity, (SIT), the test requirements are the same as for two- speed compressor units as described in A2.1.3. A2.15 Testing required for units with tripk- capocity compressors. ( R e s e r v e d )

A2.1.6 Testing required for units with vM- abk-speed compressors. The tests for variable- speed equipment consist of five (5) wet coil tests and two (2) dry coil tests. Two of the wet coil tests, A and B, are conducted at the max-

temperature test, are conducted at the mini- imum speed. Two wet coil tests, B2 and low

mum speed. The fifth wet coil test is conducted at an intermediate speed. Dry coil

speed if the coemclent of de adation (C,) tests, C and D, are conducted at the minimum

value of 0.25 is not adopted. R e test conditions and procedures for' the above are oui- lined in sections A3.1 and A4.1. A21.7 Testr required for split-type ductless systems. % systems are determined by the type of com-

e tests for split-type ductless

pressor installed in the outdoor unit. For the appropriate tests refer to sections A2.1.1, A2.1.2,A2.1.3, A2.1.4. A2.1.5, orA2.1.6. A22 Testing required for air source heating only u i t s .

speed compressors. Units with single speed A 2 2 1 Testing required for units with single

the High Temperature Test at 47 compressors shall be subjected res

in section A3.2.1.1, the Cylic Test as described in section A3.2.1.2, the Frost Accumulation Test as described in section A3.2.1.3, and +e Low Temperature Test as descrxbed in section A3.2.1.4. A2222 Testing requimd for units with two- speed compressors. two compressors, or cylinder unloading. With the unit operating: at W compressor speed (two-speed wmpres-

sor), with both compressors in operation (two- compressors), or at the maximum capacity (cylinder unloading); the following tests are

High Temperature Test at 47 F, the Frost Ac- required to be performed on all units; the

Test. An additional test (cyclic at 47 F) is re- cumulation Test, and the Low Temperature

quired, with the unit operating at the high compressor speed (two-speed compressor), with both compressors in operation (two com-. pressors), 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 sin le compressor which normally oper-

low compressor capacity (cylinder unloadmg); ates at fow loads (two compressors), or at the

the following tests are required to be per-

Test at 47 F. the High Temperature Test at formed on all units: the High Temperature

62 F, and the Cyclic Test. Additional tests, (Frost Accummulation Test and Low Temper- ature Test) are reqwred, 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), ifthe unit's low speed, one compressor or low capacity performance at and below 40F is needed to calculate its seasonal performance. A233 Testing required for units with tripk- capacity compressors. (Reserved) u . 4 Testing requirrd for units with u r n . - able-speed compres.wrs. There are seven basic tests and one optional test for variable-speed units. Three tests (high temperature test, low temperature test, and frost accumulation test) are performed at the maximum speed. Three tests (two high temperatures and one cyclic t e s t ) arp performed with the unit operating at mirumurn speed. A second fmst accumulation test is performed a t an intermediate speed. The intermediate speed is the same as in the cooling mode.

mulation test, two equations are provided in In lieu of the maximum speed frost accu-

section A4.2. In lieu of the cyclic test an assigned value of 0.25 may be used for the coefficient of degradation C, The optional test is a nominal capacity test applicable to units which have a heating mode maximum speed greater than the cooling mode maximum speed. The conditions and procedures for the

A4.2 respectively. above tests are decribed in sections A3.2 and

A.22.5 Testing required for split-type ductless system. The type of compressor mstalled in the outdoor unit determines the testing re-

A2.2.2, A2.2.3, or A2.2.4. The conditions and quired, refer to previous sections A2.2.1,

procedu,res unll be modified as indicated for the vanous types as stated in sections A3.2 and A4.2 respectively. A23 Testing required for air source units which provide both heating and cooling. The requirements for units which provide both heatmg and cooling shall be the same as the requirements in Section A2.1 and A2.2.

A3. Testing conditions

e3.1 Testing conditions for air soume cool- ~ng only units. The test mom requirement and equipment installation procedures are the

of ASHRAE Standard 37-88. Units designed same as those speafkd in section 8.1 and 8.6

for both horizontal and vertical instahtion

they are most frequently installed. AU tests shall be tested m the orientation in which

shall be performed at the normal residential voltage and frequency for which the equip ment 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

This shall be accomplished by installing dam- forced convection while the indoor fan 'is "o'ofp.

pers upstream and downstream of the test unit to block the off period air flow. Values of

offpto the nearest 100 Btuh for capacities less ca acity for rating purposes are to be rounded

than 20,000 Btuh, to the nearest 200 Btuh for capacities between 20,000 and 37,999,Btuh. and to the nearest 500 Btuh for capacities Be- tween 38,000 and 64,999 Btuh.

The following conditions listed in ARI Stan- dard 210/240-94 shall apply to all tests performed in Section A3.1: 5.1.3.3 "Cooling Coil Air Quantity." 5.1.3.5 "Requirements for Sep arated Assemblies." A3.1.1 Testing conditions for units with single speed compressors and srngle speed condenser fans. A3.1.1.1 Steady state wet-cod performance tests (Test A and Test 3). Test A and test B indoor side of the unit having a dry-bulb tem- shall be performed with the air entering the

perature of 80 F and a wet-bulb temperat- of 67 F. The dry-bulb temperature of the au 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 t e m p e r a t e except for units or sections thereof intended to be installed only indoors, in which case the dry- bulb temperature surrounding that indoor side of the unit shall be 80 F. For those units which reject condensate to the condenser, l e cated in the outdoor side of the unit, the outdoor wet-bulb temperature surrounding the

Aand65Fin te s tB . outdoor side of the unit shall be 75 F in test

A3.1.1.2 Steady state dry coil performance test (Test C) and cyclrc cod performance test fTest 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

wet-bulb temperature of 57 F or less be used.) indoor coil. (It is recommended that an indoor

The dry-bulb temperature of the air entering

The outdoor portion of the unit shall be sub- the outdoor portion of the unit shall be 82 F.

ject to the same conditions as the requirements for conducting test B as stated previously in section A3.1.1.1. 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 opera-

The unit shall cycle with the compressor "on" tion of the normal control circuit of the unit.

for 6 minutes and "off for 24 m u t e s . The indoor fan shall also cycle "onn and "off", the duration of the indoor fan uon" and u o f f periods being governed by the autamatx am- tmls which the manufacturer normally sup plies with the unit. The results of tests C p d D shall be used to calculate a degredatlon

A5.1. coeficient, C, by the procedures outlined in

A3.1.2 Testing conditions for units with sin- g& speed compressors and multiple-speed con- &mer fans. The condenser fan speed to be . used in test A shall be that speed which nor-

15


mally occurs at an outdoor dry-bulb temper- sure requirements ody apply wheno&etirn is ature 95 F, and for test B. the fan speed shall running at the maximum speed.

at the same condenser fan speed as in test B. A3.1.3 Testing conditions for units with tyo- speed compressors, two compressors. or cylcn- der unloading. The condenser fan speed used in conducting test A at each compressor speed

door dry-bulb temperature of 95 F. For test B. shall be that which normall occurs at an out-

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 a t high speed, tests C and D shall also be performed with the compressor operating at high speed and at a condenser fan speed that normally occurs at test A ambient conditions. Units consisting of two compressors are subject to the same require-

compressors. except that when operated a t ments as those units containing two-speed

high speed, both compressors shall be operating and when operating at low speed, only the compressor which normally operates at an outdoor dry-bulb temperature of 82 F shall be operating.

signed value of 0.25 may be used for the deg- In lieu of conducting tests C and D. an as-

radation coefficient, CD, 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.

the loaded and the unloaded conditions cor- In the case of units with cylinder unloading,

respond to high and low compressor speed on two-speed units respectively. A3.1.4 Testzng conditions for units with two- speed compressors. two compressors, or cylinder unloading capable of varying the sensible to total ISIT) capaczty ratio. The mode of operation selected for controlling the ST ratio

compressor speed shall be such that it does in the performance of test A and test B a t each

not result in an operating configuration which is not typical of a normal residential instal-

D shall be conducted at low compressor speed lation. If elected to be performed, tests C and

(single compressor operating) with the same SrT control .mode as used In test B when per-

wise, tests C and D shall also be conducted at formed at the low compressor speed. Like-

erating) and with the same ST control mode high compressor speed (two compressors op-

as in test A when performed at the high compressor speed.

In the case of units with cylinder unloading, the loaded and unloaded conditions corre- spond to high and low compressor speed on two-speed units respectively.

ple-capacity compressors. (Reserved) A3.1.5 Testing condrtions for units with tri-

coolzng-only units with variable-speed com- A3.1.6 Additional testing conditions for

pressors. For cooling-only units and air-source heat pumps with variable-speed compressors, the air flow rate at fan speeds less than the maximum fan speed shall be determined by

tem. The air flow rate is given by the ratio of using the fan law for a fixed resistance sys-

the actual fan speed to the maximum fan speed multiplied by the air flow rate at the maximum fan speed. Minimum static pres-

formed at the maximum s d a t e d o n s specified in section A3.1.1. E t B, a n $ h low temperature test are performed at &%mini-

tures of 82 F and 67 F respectively. inter- mum speed with outdoor dry bulb. t s q e r a -

mediate speed wet coil test is peFsomred at the outdoor dry bulb temperature d85E For

bulb temperature shall be maintarmkd.,nt75 F units which reject condensate t h e d a m w e t

the low temperature test and 6 9 F &x !&e in- for Test A. 65 F for Tests B and Bc. 835F for

termediate test. The indoor con&hmrjr ‘iir all wet coil tests are the same as t h s s 9- in section A3.1.1. A3.1.6.2 Test conditions for ctrlr. xii’ tests.

outdoor dry bulb temperature &Et?‘FE For Dry coil Tests C and D are conh??di& an

units which reject condensate themut.itmrwet bulb temperature shall be m-t- a t

be 80 F and the wet bulb tempemtra=shall 53.5 F. The indoor dry bulb tempemtumeshall

on the evaporator (It is recommededtb t an be sufficiently low so no condensatim w u r s

indoor wet bulb temperature of 57 B cn ltrss be used).

A3.1.7 Split-type ductless systemc Tctetaon- ditions shall be the same as thosesgwjfiei for the same single outdoor unit compvswu-type, assuming i t was matched with a smgSeiircloor coil. A3.1.7.1 Interconnection. For qxi5ritype ductless systems, all standard reti= tksts shall be performed with a minimum Irsmh of

each indoor fan-coil unit and the cmmmonout- 25 feet of interconnecting tub& IxTween

door unit. Such equipment in whichtkteixter- connection tubing is furnished as a m . h?gral part of the machine not recornm&$S+cutting to length shall be tested wrtmmzxplete length of tubing furnished, or with Z5 :Bet of tubing, whichever is greater. At keas!; ‘.X?, feet of the intercnnection tubin+ s h e & :+xqosed to the outside conditions. he 1- <me. In- sulation and details of installation .dsdi3e in accordance with the manufactwnuis Rub- lished recommendation. A3.1.7.2 Control testzng conditims +Flit- type ductless systems. For split-type c i d e s s systems. a single control circuit &d. !aesub- stituted for any multiple t h e r m o ~ . - i n m d e r to maintain a uniform cycling rate &zl.;i.qgtest D and the hi h temperature heabsg cyclic test. During t i e steady-state tesw. mostats shall be shunted reslting ixcaI3 d o o r

, aCi +her-

fan-coil units being in operation. A3.1.7.3 Split-type ductless ~ S & . W T ~ .uith multiple coils or multiple dtsckmge cadets shall have short plenums attached ~9 w d w u t - let. Each lenum shall discharge i&na%ngle common xuct section, the duct &.wirnturn discharging into the air measuring &-mice (or a suitable dampering device when (SImut air measurement is not employed). E~&~$i.mum shall have an adjustable restrictm lraatad In the plane where the lenums enter cikmm- mon duct section for t!e purpose o f q d l j d n g the static pressures in each plenrum. The length of the plenum is a minimum a f r 325 x (A x B)?, A = width and B = hex@ih,~Kduct

or outlet. Static pressure readings metdcen a t a distance of 2 X (A x B) frormt!hexutiet. A3.2 Testing conditions for air auu-w &at- zng only units. The equipment underbwthall

be installed according to the of

Section 5.1.3.5 of AFU Stand& -94 Section 8.6 of ASHRAE Standad.9T48 urd -

Test chamber requirements are tht as pven in Section 8.1 of ASKRAE Shnfard 37- 88. Units designed for both ho-1 and vertical installation shall be testedt;zcthe orientation in which they are most &en installed. All tests shall be performectamhe normal residential voltage and f m q for which the equipment is m e & <e&er I15 or 230 volts and 60 hertz). Values o€capacity for rating purposes are to be rouded off to the nearest 100 Btuh for capacities-Less than 20.000 Btuh: to the nearest 200 -for capacities between 20,000 and 37.999BtuIx and s

to the nearest 500 Btuh for capacitiekretween 38.000 and 64,999 Btuh. A3.2.1 Testing conditions for U R L ~ ~ G t h single speed compressors. A3.2.1.1 High temperature test rmditions. The High Temperature Test a t 47 Q shall he conducted a t an outdoor dry-bulb-Impera- ture of 47 F and an outdoor wet-bulb temperature of 43 F. The High Temperarur-eTest at 62 F shall be conducted at an outdoordry-bulb temperature of 62 F and an outdoorwet-bulb temperature of56.5 F. For both tes&s.thedq- bulb air temperature entering and? wnround- ing the indoor portion of the unit sldlbe 70 F and a maximum wet-bulb tempmature of 60 F. The duration of the tests shall: be for a minimum of Yl hour. A3.2.1.2 Cyclin test conditions The Cy- cling Test at 47 I! shall be conductat at the same dry-bulb and wet-bulb temperature as the High Temperature Test at 17 F as described in A3.2.1.1. 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 slrall be ae- complished by installing dampers upstream and downstream of the test unit to block the off period airflow. A3.2.13 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. 1 ::e Frost Accumulation Test requires t h t the unit undergo a defrost prior to the actual test. The test then begms a t defrost termination and ends at the next defrost termination. De- frost termination occurs when the controls normally installed within the unit are actuated to cause it to change defrost operatim to normal heating operation. During the test, auxiliary resistance heaters shall not be employed during either the heating nr d m portion of the test. A3.2.1.4 Low temperature test cozrdir inm. The Low Temperature Test shall beat a dry-bulb temperature entering the outdoor portion of the unit of 17 F and a w e t a b temperature of 15 F. The air enterin the indoor portion of the unit shall have a &-bulb temperature of 70 F and a maxlmum wet-bdb temperature of 60 F. A3.2.1.5 Additional testing conditions. All

-.

-

16


tests shall be conducted at the Indoor-side air quantities specified in Section 5 ! 3.3. 5.1.3.6 and Table 6 of ARI Standard 2 10/240-94. The

210/240-94 shall apply to all tests performed following conditions listed in ARI Standard

Quantity”: 5.1.3.5 “Requirements for Sepa- In Section A3.2; 5.1.3.4 “Outdoor-Side Air

dry-bulb temperature entering the outdoor rated Assemblies.” In all tests. the specified

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. A3.2.2 Testing conditions for units with two- speed compressors, two compressors or cylinder unloading. The testing conditions for two-

inder unloading shall be the same as those for speed compressors. two compressors. or cyl-

single speed units as described in A3.2.1. A3.23 Testzng conditions for units with triple-capacity compressors. (Reserved) A3.2.4 Testing conditions for units with uariable-speed compressors. The testing condition for variable-speed compressors shall be the same as those for single speed units as described in section A 3 2 1 with the following exceptions; the cyclic test is performed with an outdoor dry bulb temperature of 62 F and a wet bulb temperature of 56.5 F. The optional. nominal capacity test shall be performed at the conditions specified for the 47 F high temperature test. A3.2.5 Testing conditions for split-type ductless systems. The testing conditions for split- type ductless systems shall be based on the type of compressor installed in the single outdoor unit. The heating mode shall have the same piping and control requirements as in A3.1.7. A35 Testing conditrons for azr source units whrch prourde both heatrng and cooling. The -testing conditions for units which provide both heating and cooling shall be the same as the requirements in Section A3.1. and A3.2. 4.0 Testing procedures. Measure all electrical inputs as described in the procedures be-

“on” and “off periods shall include auxiliary low. All electrical measurements during all

crankcase heaters, etc. ) delivered to the unit. power or energy (controls. transformers.

A4.1 Testzng procedures, for azr source cwl- rng only unrts. All steady-state wet- and dry- coil performance tests on sin le package units shall simultaneously empfoy the Air-En- thalpy Method (Section 7.3 of ASHRAE Stan- dard 37-88) on the indoor side and one other

Method or the Compressor Calibration method conslsting of either the kr-Enthalpy

Method (Section 7.4 of ASH= Standard 37- 88) on the outdoor side. All steady-state wet-

terns shall simultaneously employ the Air-En- and dry-coil performance tests on split sys-

Method on the indoor side and the Air-En- thalpy Method or the Compressor Calibration

thalpy Method, the Compressor Calibration Method or the Refrigerant Flow Method (Sec- tion 7.6.2 of ASHRAE Standard 37-88) on the outside. All cyclic drysoil performance tests

side only. The values calculated fmm the two shall employ the Air-Enthalpy Method, indoor

test methods must agree within 6 percent in

s u b from the Air-Enthalpy Method on the order to constitute a valid test. Only the re-

indoor side shall be used in the calculations Ln Section 5.1. Units shall be installed and

tested in such a manner that when operated

and condenser coil alr flows meet the reauire- under steady-state conditions, the cooling coil

ments of Sections 5.1.3.4. 5.1.3.5, and 5:1.3.6 of A R I Standard 210/240-94. A4.1.1 Test operating procedures. A4.1.1.1 Steady-state wet-coil performance tests (Test A and Test B/. Steady-state wet-coil

ducted in accordance with the conditions de- performance tests (A and B) shall be con-

scribed in sections A3.1.1.1, A3.1.2, A3.1.3, A3.1.4. and A3.1.5 of this appendix and the test procedures described for cooling tests in Section 8 of ASHRAE standard 37-88 and evaluated in accordance with the cooling-related requirements of Section 10 of the ASH- RAE Standard 37-88. The test room reconditioning apparatus and the equipment under test shall be operated until equilibrium conditions are attained. A4.1.1.2 Steadystate and cyclir and dry-coil performance tests (Test C and Dl. 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 A3.1.1.2. A3.1.2. A3.1.3. A3.1.4. and A3.1.5 and A3.1.6.2. The results shall be evaluated in accordance with the cooling related requirements of Section 10.1.5, 10.1.6 and 10.1.7. of ASHRAE Standard 37-88. The test room reconditioning apparatus and the equip-

librium conditions are attained, but not for ment under test shall be operated until equi-

less than one hour before data for test C are

cluding the Compressor Calibration Method, recorded. For all equipment test methods in-

test C shall be performed with data recorded at lominute intervals until four consecutive

ance prescribed in Section 9.2 of ASHRAE sets of readings are attained with the toler-

Method is used on the outdoor side for test C, Standard 37-88. When the Air-Enthalpy

the requirements of this section shall apply to both the preliminary test and the regular equpment test; the requirements of Section 8.5 of ASHRAE Standard 37-88 shall also apply. Immediately after test C is completed the test unit shall be manually cycled “off‘ and

Appendix untd steadily repeating ambient “on” using the time penods from A3.1.1 of this

conditions are again achieved in both the indoor and outdoor test chambers, but for not less than 2 complete “offP’on” cycles. Without a break in the cycling pattern, the unit shall be run through an additional “off‘Yon” cycle during which the test data required in A5.1

which is referred to as the test cycle, the in- shall be recorded. Durmg this last cycle, door and olltdoor test room ambient conditlons shall remain wthin the tolerances specified in A4.1.3 dunng the cyclic dry-coil tests, all air moving equipment on the condenser side shall cycle “on” and ”OF‘ 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 “OW as the compressor cycles “on” and “off,”

Cooling cyclic tests for Variable-speed units shall be conducted by cycling the com ressor 12 minutes “on” and 48 minutes “off. h e ca-

time (8). which is the compressor “on’ time of pacity shall be measured for the integration

fan delay, if so equipped. The electrical energy 12 minutes or the “on” time as extended by

shall be measured for the total integration

time (e,,) of 60 minutes. In lieu of conductin C and D tests, an assigned value of 0.25 sld? be used for the degradation coefficient for mol- ing. C,. A4.1.1.3 Testingprocedures for triple-capac. ity compressors. (Reserved) A4.1.1.4 Intermediate cooling steady-state test for units with carzable-speed compressors. For units with variable-speed compressors, an

conducted in whlch the unit shall be operated intermediate cooling steady-state test shall be

a t a constant, intermediate compressor speed tk= i ) in which the dry-bulb and wet-bulb

coil are 80 F,, and 6i F,, and the outdoor coil temperatures of the alr entering the indoor

are 87 DB and 69 FwR. The tolerances for the dry-bulb and wet-bulb temperatures of the air entering the indoor and outdoor coils shall & the test operating tolerance and test condition tolerance specified in A6.1.1. The intermediate compressor speed shall be the minimum compressor speed plus one-third the difference between the max~mum and minimum speeds of the cooling mode. (Inter. speed = min. speed - ’13 max. speed - min. s tolerance of plus five percent or higher inverter frequency step frqm that c a l - culated ls allowed. A4.1.1.5 Testing procedures for split-type ductless systems. Cyclic tests of ductless units will be conducted without dampers The data cycle shall be preceded by a minimum of two cycles in which the indoor fan cycles on and off with the compressor. For the data cycle the indoor fan will operate three minutes prior to compressor cut-on and remain on for three minutes after compressor cut-off. The integration time for capacity and power shall be from compressor cut-on time to indoor fan cut-off time. The fan power for three minutes aRer compressor cut-off shall be added to the integrated cooling capacity. A4.1.2 Test znstrmentation. The steady- state and cyclic performance tests shall have the same requirements pertaining to instru-

tion 5 and Table 5 of ASHRAE Standard 37- mentation and data as those specified in Sec-

88. 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 dry-bulb temperatures, shall be continuousIy 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 is the time required for the instrumentation to obtain 63

difference when subjected to a step chan percent of the final steady-state temperature

temperature difference of 15 F or more. trical measurement devices (watt-hour me- ters) used during all tests shall be accurate to within ~ 0 . 5 percent of indicated value. A4.1.3 Test tolerances. All steady-state wet- and dry-coil performance tests shall be performed within the applicable operating and test condition tolerances s cified in Section 9.2 and Table 4 of A S H d S t a n d a r d 37-88. A4.1.3.1 The indoor and outdoor average dry-bulb temperature for the cyclic dry coil test D shall both be within 1.0 F of the indoor and outdoor average dry bulb temperature for the steady-state dry coil test C, respectively. 4.1.33 The test condition and test operating tolerances for conducting test D are stated in A6.1.1. Variation in the test conditions greater than the tolerances prescribed in A6.1.1 shall invalidate the test. I t is suggested that an electric resistance heater having a

17

ARI STANDARD 210240-94

capacity approximately equal to the K T t h e cooling capaaty and compressor and condenser fan power should be installed in the outdoor test room and cycled " ~ f f and *on" as the unit cycles "on" and "off respectively to improve control m the outdoor test room. Similarly, an elect+ resistance heater having a heating capacity approxlmately 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 mom control. A49 Testing procedures for air source heating oniy units. A49.1 Test o rating procedures. All High Temperature Gts, 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 adhtlon, the Hlgh Temperature Test and

. the Low Temperature Test shall have a si- multaneous test method (as described inA4.1) used as a check. The values calculated from the two methods must agree within 6 percent in order to constitute a valid test. Oily the results from the Am-Enthalpy Method on the indoor side shall be used in the calculations in s&on A5.2. A43.1.1 Test procedure for hcgh temperature test. When the outdoor Air-Enthalpy 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 outdoor portion of the unit. The test room apparatus and test units must be operated for a t least one hour with at least Y2 hour a t equilibrium and at the specified test conditions prior to star t ing the test. The Hi h Temprature Test shall then be conductef for a mmimum of 1/2 hour mth

ute intervals. For all units, especially those intermittent data being recorded at 10-min-

having controls which periodically cause the unit to operate in defrost mode, attention should be given to prevent defrost d u r y the High Temperature Test. Units wbch ave undergone a defrost should operate in the heating mode for at least 10-minutes after de-

When the outdoor Air-Enthalpy Method is frost termination proir to the start of the test.

wdasasecondtestthenaprehmarytest 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 8.5 in the ASHRAE Standard 37-88 shall then apply in conducting the preliminary test for the outdoor air enthalpy method. For some units, at the amblent 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 1.5 F at the end of the test, the unit shall be defrosted and the test restarted. Only the results of this second Hlgh Temperature Test shall be used in the heating seasonal performance calculation in

Temperature Test, a unit s % h operate in t%e section A5.2. Prior to be 'nning the Hi h

heating mode for at least 10 minu- after defrost termination establish eqlullbriurp conditions for the urut and the mom recon&- tioning apparatus, The Hi h Temperature Test may only begm when &e test u n i t , p n d

room conditions are within the test con&tion tolerances spedficd in Section A6.2.1. AU.13 Test proecdures for the die test. The cyclic test shall follow the High Temper-

ature Test and by cycled "on" and 'off as specified in A3.2.1.2 until steadily repea bient conditions are achieved for bot Y"- the indoor and outdoor test chambers. but for not less than 2 complete 'off'ron" cycles. Without a break in the cycling pattern, the unit shall be operated through an additional "offron" cvcle, during which the required test data s i i l 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 tolerances specified in section A6.2.2. If, prior to the High Temperature, Test, the unit underwent a defrost cycle to nd the outdoor coil of any accumulated frost, then prior to cycling the unit "off" and "on" i t

defrost is completed and before starting the should be made to undergo a defrost. After

tinuously in the heating mode for at least 10 cyclingprocess, the unit shall be operated con-

minutes to assure that equilibrium conditions have again been established for the unit and the mom conditioning apparatus. Cycling the unit may begin when the test unit and room

Test condition tolerances specified in section conditions are within the High Temperature

A6.2.1. Attention should be given to prevent defrost atter the cycllng process has begun.

The cycle times for variable-speed units is the same as the cyclic time in the cooling mode as specified in section A4.1.1.2. Cyclic tests of split-type ductless units will be conducted without dampers, and the data cycle shall be preceded by a minimum of two cycles in which the indoor fan cycles on and off with the compressor. During the data cyde for the split type ductless units, the indoor fan will operate three minutes prior to compressor "cut-on" and remain on for thfee minutes after compressor 'cutoff. The mtegmbon time for capacity and power will be from compressor "cuton' time to indoor fan "cutoff time. The fan power for the three minutes after compressor "cut-off shall be subtracted from the inte ated heatin capacity. For split-type d u x s s systems wfuch turn the indoor fan off during defrost, the indoor supply duct shall not be blocked. 43.1.3 Test rocedures for the frost accumulation test. ' h e defrost controls shall be set

encountered in Region N as described in sec- at the normal settmgs which most type those

tion A6.2.4 and A6.2.5. The test mom reconditioning equipment and the unit under test

the start of a "prelimmary" test period. The shall be operated for a t least hour prior to

preliminary test period and the test period itself are to be conducted wih the test tolerances given in section A4.2.3.3. In some cases, the preliminary defrost cycle may be manually induced, however, it is important that the normally opera controls govern the defrost termination in% cases. For units containing defrost controls whch are likely to cause defrost a t intervals less than one hour when the unit is operating at the reqd test conditions. the preliminary test period shall start at the terminatlon of a defrost cycle

the Frmination of the next automaty+ly oc- which automatically occurs and +I end at

curnng defrost cycle. For units contammg defrost controls which are likely to cause defrost at intends exceeding one hour when opeat- ing at the required test conditaon, the p r e h - inary test period consists of "heating-only" preliminary operation for at least one hour, lfLrwhicha&fro&maybemanuallyorau- t o m a t i d y induced. The test period then be- gins at the termination of this defrost cyde and ends at the termination of the next automatically OECurring defrost cycle. If the unit

then the tests shall be concluded and the R- has not undergone a defrost after 12 ho-.

sults calculated for this 12-hour period. For units which turn the indoor fan off during de-

during all defrost cycles to prevent natural or frost the indoor supply duct shall be blocked

forced convection through the indoor unit. During defrost, resistance heaters normally installed with the unit shall be prevented from operating.

the frost accumulation test at the intermedi- a te speed shall be conducted such that the unit will operate a t a constant. intermediate compressor speed (k = i ) a s d e t e m e d m section A4.1A.4. The following two equations may be used in lieu of the frost accumulation test for variable-speed.

(a) aiY35) = 0.90 x [ a - ' ( 1 7 )

For units with variable-speed compressors. .

- (QL=2 (47) - e-' (17)) X (35 - 17)/(47 - 17)l

(b)'EL;*(35) = 0.985 X [EL-' (17) + (E&-' (47) - E&-* (17)) X (35-17H47-1733

A4Z1.4 Test pnxedures for the low temperature test. Where applieble, the High Tem- perature Test preparabon and performance

Temperature Test. The test mom recondition- requirements shall also be used in the Low.

ing equipment shall first be operated in a

a t equilibrium and at the speafied test con- steady-state manner for at least onehalfhour

ditions. The unit shall then undergo a defrost, either automatic or manually induced. It is - sequence by the action of i t s own defrost con- important that the unit terminate the defrost

trois. The defrost controls are to remain at the same setting as speafied in A4.2.1.3. 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 dunng the one-half test period. A 4 2 2 Test tnstrumentntwn. A422.1 Test rnstrumentatwn for the hrgh temperature test. The indoor air flow rate shall

through 7.8.3 of ASH- Standard 37-88. be determined as described in Section 7.8

This requires the constru&on of an air r e ceivin chamber and d d x u g e chamber sep ara te fby partition in whlch one or more nozzles are located. The receiving chamber is connected to the indoor air discharge side of the test specunen through a short plenum. The exhaust side of the air flow rate measuring device contains an exhaust fan with some means to vary its capaaty to obtain the de- sired 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 measure ments a t the nozzle throat shall be m d with manometers which will result in errors which are no greater than 2 1.0 percent of indicated value and having minimum scale divisions not exceeding 2.0 Kent of the reading. Static pressure anrtemperature measurements must be taken at the nozzle throat in order to obtain density of the,&. The areas of the nozzles shall be detvrmned by measuring tbeir diameter with an error no greater than 20.2 percent in four places a p p-tely 45 degrees apart around the noz- de rn each of two places through the n o d e

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18


throat. one at the outlets and the othem in the straight section near the radius. The energy usage of the compressor, indoor and outdoor

shall be measured with a watt-hour meter fan. and all other equipment components

which is accurate to within -0.5 percent of the quantity measured. Measurements of the air temperature entering and leaving the indoor coil or the difference between these two shall be made in accordance with the re uire- ments of ASHRAE Standard 41.1-86 %tan- dard Method for Temperature Measurement." These temperatures shall cont+uously recorded w t h instrumentation havlng a total system accuracy with 5 0.3 F of indicated value and a response time of 2.5 seconds or less. upstream of the static pressure tap on the inlet and downstream of the static pressure taps on the outlet. The indoor and out-

ously recorded with instrumentation which door dry-bulb temperatures shall be continu-

of indicated value. The outdoor wet-bulb tem- will result in an error no greater than = 0.3 F

perature shall be continuously recorded. Static pressure measurements in the ducts and across the unit shall be made in accordance with Section 6.4 of ASHRAE Standard 37-88 using equipment which will result in an emr no greater than 20.01 inch of water.

and recorded at 5 minute intervals. Ail other Static pressure measurements shall be made

corded a t 10 minute intervals. data not continuously recorded shall be re-

A4.2.22 Test instrumentations for the cycling test. The air flow rate during the on- period of the Cyclic Test shall be the same agreement within 2 1. percent as the air flow

ducted High Temperature Test. All other in- rate measured during the previously con-

strumentation requirements are identical to A4.2.2.1. A4.22.3 Test instrumentation for the frost accumulation test. The air flow rate for the

described in A4.2.2.1. The indoor-side dry- Frost Accumulation Test shall be the same as

temperature shall be continuously recorded bulb temperature and outdoor-side dry-bulb

with instrumentation having a total system accuracy within I 0.3 F of indicated value. The outdoor dew point temperature shall be determined with an error no greater than = 0.5 F of indicated value using continuously recording instrumentation. All other data shall be recorded a t 10 minute intervals during the heating cycle. Defrost initiation, ter-

defrost termination to defrost termination) mination and complete test cycle time (from

shall be recorded. Defrost initiation is defined as the actuation (either automatically or manually) of the controls normally installed with the unit which cause it to alter i t s 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 heatmg operation. Provisions should be made 50 that instnunentation is ca ble of recording the cooling done dunng de& as. well as the

These data and the continuously recorded total electrical energy usage dunng defrost.

defrost. data need be the only data obtained during

4.2.2-4 Test instrumentation for the low ten- perature test. Instrumentation for the LOW Temperature Test is identical to that of the High Temperature Test described in section A4.2.2.1.

A423 Test tolemnces. A4.2.3.1 Test tolerances for the htgh temperature test. All tests shall be conducted within

Variation greater than those oven shall in- the tolerances specified in Section A6.2,l .

validate the test. The heating capacity results by the indoor Air Enthalpy Method shall

mined by any other simultaneously conducted agree within 6 percent of the value deter-

capacity test in order for the test to be valid. A 4 3 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 A6.2.2. Variations exceeding any specified test tolerances shall invalidate the test results. A42.3.3 Test tolerances for the frost accumulation test. Test condition and test operating tolerances for Frost Accumulation Tests are specified in Section A6.2.3. 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 operatin tolerance during defrost applies during a defrost cycle and during the first 5 minutes after defrost termination when the unit is operating in the heatmg mode. In determining whether the test condition tolerances are met, only the heating portion of the test period shall be used n caicula the average values. v h a t i o n s e x c e h s e tolerances presented in Section A6.2.3 shall invalidate the test. A4.2.3.4 Test tolemnces for the low temperature test. During the test period for the Low Temperature Test, the operating conditions shall be within the tolerances specified in Sec- tion A6.2.1. A43 Testing procedures for air source units which provide both hating and cooling. The testing procedures for units which provide both heating and cooiing shall be the same as

during the off-period of the dry-coil cooling those specified in Sections A4.1 and A4.2. Also

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 test a t 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. A5.0 Calculations for performunce factors. AS-1 Calcuiations of seasonal energy efficiency ratios (SEER) in air-source unats. The testir4 data and results required to calculate the seasonal energy efficiency ratio (SEER) in Btu's per watt-hour shall include the following:

and B and, if applicable, the cooling capaaty ( i ) Cooling capacities (Btuh) from tests.A

(Btuh) from test C and the total cooling done from test D (Btu's).

and ,controls (watts) from tests A, B, and, if (ii ) Electrical power input to all components

applicable, the electrical power input to all components and controls (watts) from test C and the electrical usage (watt-hour) from test D.

E _' (95F) E ..'. dry E,. dry

E ..' (82F)

(iii) Indoor a i r flow rate (SCFM) and exter-

water W.C.). nal resistance to indoor a i r flow (inches of

Outdoor dry bulb Outdoor wet bulb Indoor dry bulb Indoor wet bulb

from test A, Q.,' (82). from test B. and Q... Where the .cooling capacities Q ..' (95.F).

dry, from test C. are calculated using the equation specified in section 7.3.3 of .4SHRAE Standard 37-88. 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 parr of the model shall

adjusted by subtracting 1250 Bt& per 1,OOO have their measured total coolin capacities

CFM of measured indoor air flow and ad- to the total steady-state electrical power input 365 watts per 1,OOO CFM of measured indoor air flow.

Energy efficiency ratios from tests A, B, and C. EER,, EER,, EER,., dry respectively, are each calculated as the ratio of the total cooling capaaty in Btuh 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

equipment power shall be 1250 Btuh per vaue to be used for the circulating indoor air

1,OOO CFM of circulating indoor air. The energy usage required in one comlete cycle re-

of the circulating indoor air equipment power quired for indoor air circulation is the product

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 remaining equipment components (compres-

formerb). etc.) in one complete test cycle. soT(s). outdoor fan. crankcase heater. trans-

(,.,. dry is calculated as the ratio of the total Energy efficiency ratio from tests D. EER-

cooling done in Btu's to the total electrical energy usage in watt-hours.

(iv) Air temperatures (F)

19


state dry-coil performance tests shdl be The results of the cyclic a d sbrdy-

used in the following (4) equations:

where Q.. I, dr ,=T~t . l canling over a eye10 cornisling of one

.&on" penod (Btll's). compressor "off' p n o d and one mmp-

V=lndoor a1r flow nte (cfm) at the dry-bulb temperature. hllmidity ratio. and prasw exsung 111 the reglon of mcIuuemLnt.

C,.=Spec~~ heat a t constant resure of air- water mlxturp per pounS of dry .L,

whzre . CLF-coolina l a d factor.

Q-. dry = Total steady-state coohng capacltv from test C

r=D~lrsr lon of tImc (hours) for one Wmplcte cycle consmng of one comprewr ''on'' tuna and one compressor "otl" tlme.

IBtuhl

in the following equation to calculate 8 The preceding equstions are then used

degradation coefficient CD rounded to the nearest .01.

where EER,. ro=Enerpy eficieney ratio h r r test C, (BtW

A5.1.1 Method for calculating a SEER for units wlth smgle-speed compressor and sin-

ergy efficiency ratio for units employing single-speed condenser fans. The seasonal en-

condenser fans shall be based on the perfor- gle-speed compressors and single-speed

mance of test B and a method outlined in A2.1.1 and A3.1.1 to account for the cyclic performance.

The seasonal enrrgy efficiency ratio in Btu's/wntt-hour shall I- determined by the equation:

htt-hr).

SEER= PLF(0.5) X EERs where

E E R , = E m y cmciency n t i o determined fmm test B u outlrncd In 2.1.1.

PI.F(O.5) = Part-lcul perromance factor when d i n g l o a d (.ctor=O.:, u dewrmrrled from the equation:

where PLF(O.5)=1-O0.5XC~

Cu-Is the degradation mfkient dadbed in 2.1.1 or m &ulaml m equuuln (4) above.

A5.1.2 Method 'for calculating a SEER for units with single-speed compressors and multi-speed condenser fans. The seasonal en-

ergy efficiency ratio (SEER) for units employ-

condenser fans shall be based on the energy ing single-speed compressors and multi-speed

efficiency ratio obtained for test B and the method outlined in A2.1.2 to account for the

ergy efficiency ratio for test B is obtained with performance under cyclic conditions. The en-

the unit operating with the condenser fan speed which normally occurs at test B ambient conditions.

The seasonal energy efficiency ratio i l

the equation: Btu's/watthour shall be d2termined by

SEER-PLF(O.5) X EERB where

EERs-en efkiency ntio determined from PLLF(O.5) -Pul-kmd p c r f o r m m c e factor u deter-

-Tin ' mined Lorn the equatron:

where PtF(3.5)=1-0.5XC0

cD-P&3P Uon eamcienf desrribed In 2.1.2 or red In m q t i o n (4) above.

A5.1.3 Method for calculati~g a SEER for

pressors, or cylinder unloading. The calcula- units with two speed compressors or two com-

tion procedure described in this section shall be based on the performance of test A and B at each ofthe compressor speeds for two-speed compressor units, subject to the conditions on condenser fan speed described in A3.1.3.

have the SEER calculated in the same man- Units operating with two compressors shall

ner as two-speed compressor units. The su-

speed) designates the compressor that nor- perscripted index k = 1 (and the term "low-

mally operates at an outdoor dry-bulb temperature of 82 F ad k = 2 (and the term "high speed") denotes operation with both compressors.

In order to evaluate the steady-state capacity Q..'YT.), and power input. E.."(T,), at temperature T, for each compressor speed, k = 1 . k = 2. the results of tests A and B from A5.1 shall be used in the following equation:

O a f ( 7',)=Qaak(95 F)

where Q,.'195 F I = steady-state capaclty measured from test A

Q..'i82 FI = Steady-state capacltv measured from test B as outlmed in A2.1.3

as outllned In A2 1 3

&a'( Ti) = Ea,' (95 F)

wben E.."195 F I = Electrxal power Input measured usmg test

A a5 outltned In A 2 . 1 3

E..'l82 FI = Electrlcal power Input measured from usmg test A as outlmed In A2 1 3

The building coolin load BL CT,) for the four cases describef in section A5.1.3.1 through A5.1.3.4 shall be obtained from the following equation:

Where

Q..* '195 Fl= Steady-state capacnv measured from teat A In A2 9 at the hlgh compresaor speed

C k I The value of the degradatlon coefficient

C;, for high speed odof f compressor cycling for low compressor speed cycling and -

is determined as described in section A2.1.3. or as calculated above in equation ( 1 ). A5.1.3.1 Units operating a t low compressor speed ( k = 1 ) for which the steady-state cooling capacity. Q!; ' (T,I, is greater than or equal to the building cooling load. BL (T.1. evaluate the following equations:

BL(T , i = Budding coollng load {Btuhl at temperature 8 T; 8 from sectlon A5 1.3.

@ \ - I ~ T , I = Steadv-statecwllngcapac:tyIBtuh~attemper aturei IT, 1 from sectlon A5 1 3

where - Q(Ti )=n t io 01 total cooling tu) in tempentllre

" r

bln i to the number of temperature brn hours. 15 the fractlonal number of hours In temperature bin,

fmmA6.1.2.

where

E ~ = n t l o o f E n e r g y ~ e ( w a t t - h r . ) i n t e m p c r a t : t r r bin j to the number of temperaruse bm hol~rs.

PLF.L- '= l -~D- ' ( l -x~ - l ) .

scribed in section A2.1.3 or as calculated Where C,, the degradation coefficient as de- - above in equation (1 ). A5.1.3.2 When a unit must alternate between high (k = 2 ) and low tk = l ) com ressor speeds to satisfy the building cooling Toad at a temperature T,. evaluate the followingequa- tlons:

+X+*X E : . - z ( T , ) I x ~

A5.1.3.3 When a unit must cycle on and off at high compressor speed (k = 2) in order to satisfy the building cooling load a t a temperature T,, evaluate the equations provided in section A5.1.3.1 replacing rk = 1 ) data with ( k = 2 ) data. Ak1.3.4 When a unit operates continuously at high compressor speed (k = 2) at an outdoor temperature T, evaluate the following equations:

20


A5.13.5 Calculate the SEER in Btu'dwatt- hr. using the values for the terms

- Q( Ti) N

and

as determined a t each temperature bin according to the applicable conditions described in sections A5.1.3.1 through A3.1.3.4 as follows:

A5.1.4 Method for calculating a SEER for units with two speed compressor, two compressor or cylinder unloading capable of vary-

Multi-speed compressor and two-speed com- ing the sensible to total capacity ( S I ' ) ratio.

to total capacity ratio ( S I T ) shall have the sea- pressor units capable of varylng the sensible

described in section A5.1.3. For such units, sonal energy efficiency ratio determined as

the mode of operation selected to determine the steady-state capacities Q,,*(93), Q,,*(82), E,'(93), E,,*(82), and power inputs at each compressor speed k = 1, k = 2, for tests A and B is outlined in section A2.10. A5.1.5 Seasonal energy efficiency ratio for air-source unzts with triple-capacity compressors. (Reserved) A5.1.6 Seasonal energy efficiency ratio for arr-source units with uariable-speed compressors. For air-source units with variable-speed compressors, the seasonal energy efficiency ratio (SEER), shall be defined as follows:

Q(T 1

SEER = E(T ) CIS_ 1 N C,"l $-

where the number of hours in the/* temperature bin (n I / N is defined in Table A6.1.2.

The SEEh shall be determined by evaluat- ing three cases of the compressor operation. Case I is the same as specified in A5.1.3.1 with

and E$;YT,) shall be calculated by the follow- the exception that the quantities Q,.*-YT,)

1ng equations: e; V T , ) = '(82 F)

4 qi '(67 F) - Qb-'(82 F)

82 - 67 X (82 - T , )

F;'(T,) = E$i1 (82 F)

f E:,- '(67 F) - E:,- Y82 F)

82 - 67 x (82 - T , )

any intermediate (k = u) speed between the Case I1 is when the compressor operates a t

to satisfy the building cooling load. Evaluate maximum (k = 2) and minimum (k = 1 ) speeds

the following equations: B t ; " ( T , ) = BL(T,)

where E,.~h-L.CT,l the electncal power lnput requlred by the

unlt to deliver capaclty matchmgthe building load a t temperature q.

where Q S s k - ' ( T )-the capaclty delivered by the unit

ma&& the buildlng load at temperature T .

EER,'-'~T,I =the steady-state energy efficiency ratlo at temperature T, and an intermedlate speed at whlch the unlt capacity matches the buildmg load.

energy efficiency ratio, EERW4="(T ), can be Before the steady-state intermediate speed

calculated, the unit performance has to be evaluated at the compressor speed (k = i) at which the intermediate speed test was conducted. The capacity of the unit at any temperature T, when the compressor operates at the intermediate speed (k = i) may be determined by: @c'(T,) = @,"(87) + MQ ( T , - 87)

Where: Qs.' - '(871 =the capacrty of the unit at 87 F detcrmrned by

Mq = slope of thecapacity curve for the rntermediate the Intermediate coaling steady-state test.

compressor speed tk = I I

determined, the temperature where Once the equation for Q,:-'(T,) has been

Q$-'=BL(T,) can be found. This temperature is designated as (TJ. The electrical power input for the unit operating at the intermediate compressor speed (k = i ) and the temperature (T,) is determined by:

El. ' (TcT) = E:..' (87) + MK(T, - 87)

where: Es,'-'(6?)= the electrlcal power Input of the unit at 87 F

determlned bv the lntermedtate cool lng steady-state test

M,=scopeoftheelectr~calpower~nputcurveforthe mtermediate compressor speed lk = 1 1

X 1 - N E )

EERJT,), at the intermediate speed (k = i) The energy efficiency ratio of the unit ,

and temperature T, can be calculated by the equation:

Similarly, ener efficiency ratios a t tern- perature T, and E can be calculated by the equations:

where

EER..' -

temperatureatwhlchtheunlt.operat1ngat t h e m ~ n ~ m u m compressor speed. dellvers capfclty equal t o the bul ldlng load

the capaclty equatlon l ( Q , , k ' i , 4 ~ l an! 16,. 1(TII=BLtT3)). found bv e uatm

building load equation IBL IT 11 in sectton A5.1.3 and solvlng for temperiture. temperature a t whlch the unlt, operating at the maxlmum compressor speed. delivers capacitv equal t o the bul ldlng load I Q . . ' - ~ ~ ? ~ ~ = E L (T21l. found bv equatlng the capaclty equatlon I ~Q,~ '=~ (T , ) I and the buiId~ngequat~onlBL~T,~IinsectronA5.1.3 and solvlng for temperature.

.the steady state energy efficiency ratlo at the mlnlmum compressor speed a t temper-

EERS,'-'(T2l=the steady state energy efficiency ratio at ature TI.

the maxlmum compressor speed at temper.

- ' i T ~ l = the electrlcal power Input at the mlnimum ature Tz.

culated by the equhon ~n sectlon A5.1.3. compressor speed at temperature TI . cal-

*f T ~ I = the electrlcal power Input at the maxlmum compressor speed at temperature T2. calculated by the equation In sectlon A5.1.3.

shall be calculated by the following equation: The energy efficiency ratio. EER,,*- YT,),

EER;:' (T , ) = A + B X T, + C x 'I: where coefficients A. B, and C shall be evaluated using the following calculation steps:

Case I11 is the same as specified in A5.1.3.4. The quantities Q,,"VT,) and E,, -YT,) .and Ev:-YT,) shall be calculated by the equations prescribed in A5.1.3. A5.1.7 Secrsonal energy efficiency ratio for split-type ductless systems. For split-type ductless systems, SEER shall be defined as specified in section A5.1.1 for each combination set of indoor coils to be used with a common outdoor unit.

A52 Calculation of Heati Seasonal Per- formance Factors (%SPF) for Air-

The testing data and results required to cal- Source Units.

culate the heating seasonal performance factor (HSPF), in Btu's per watt-br, shall include the following:

( i ) Heating capacities (Btuh) h m the in-

Tern rature Tests, and the total heat- door air enthalpy method for the High

inn g n e (Btu's) for the cyclic and frost

21


(ii) Electrical power inpttt to 311 con)- ponents (watts) for the steadx state tests, anti the electrical usage (wntt-ho~~rs) for the cyclic and frost accumulation tests

E,,(47) or E.,(62).

Ecye(40. ~. . (172.

EDEF@). tiiil Indoor air flow rate tSCFM1 andexter-

nal resistance to indoor air flow (Inches

(iv) Air temperature (F) of water W.C.)

Outdoor dry bulb Outdoor wet bulb or dew point Indoor dry bulb and Indoor wet hulh.

RAE Standard 37-88 ( V I Data as specified in Tab& 5 of ASH-

Q,,(62) and Q,,\(17) and the indoor air flow rate Where the heating capacities Q . , ( 4 7 ) ,

are calculated using the equations specified in section 7.3.4 and 7.8.3 of A S H W standard 37-88. The total heating done, Q,,(47) and Q ( & 3 5 ) are calculated using the equations below.

Units not having an indoor fan as part of the model tested shall add 1250 Btuh per’ 1.000 SCFM of indoor air 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 alr handled to the measured power to obtain the total power input, E,>(17), E,,(47), or E,,(62), to the unit.

for the High Temperature Tests cOP,,f62) The coeffirients of performance (COP)

or COP..(47), and Low Temperature Test, COP..(l7), are calculated as the ratio of the heatin capacity in Btuh to the product of 5.413 and the power inptits to the indoor fan in watts and thc power

ponents (inciucliog all controls) in watts. inputs to the remaining eqcipment coin-

Units which do not have indoor air circulating fans furnished as pnrt of the model shall have their total hearing done

complete cycle adjustcd for the effect of (Q,,.i47)) and energy used E,,,(47) in one

circulating indoor air equipment power.

part of the model, Q0,(47) shall !)e in- For units tc>ted without an indoor f3n 1s

creased by a quantity of heat equal to the product of 1250 Btuh .per 1,000 SCFM, the length of the on-period of the test cycle

cmulated in units of 1,000 SCFM. The in hours, and the flow rate of indoor air

total energy usage, KyO(47) , shall ‘he t:le sum of the cnelgy usage required for n ~ r circulation during t5e test cycle :md the energy u.cec! I)y the remninlng eqtlipment components (including all controls) tlurmg

fan as part of the moclcl tested, shall set the the test cyc!c. Units not hnvinp an indoor

qua! to the quantity given by the product energy reqllired for indoor air circulation

of 365 watts per 1000 SCFM, the length of the on-period of t h e tes t cycle in houls, and Lhe rate of indoor air circulated in units of lo00 SCFM.

The cyclic coefficient of performance,

total heating done (Qcrc(47)) in Btu’s to coPey,(47) is calcuiated as the ratio of the

the product of 3.413 Btulwatt-hour and the total energy usage (E.,.(47)? in watt hours.

The net heating capacity, Q uEbi35) Btuh, is

( ~ncluding any credit for the indoor fan heat) the total net heating done over the test penod

divided hy the total length of the test period, hours.

“demand defrost control systems”. the value For air-source unlts that are equipped with

for HSPF. as determined above shall be multiplied by an enhancement factor F,,,.! to com- pensate for improved performance not measured in the Frost Accumulation Test. The factor F,,,.: depends on the number of defrost cycles in a 12-hour period and should be calculated as follows:

where: F,,,., - 1 - 0 03 X , I - ! T,, .I - 90 111 T,,,., - 90 1 t

F,,.,=dernand defrost credlr lused as a rnultlpllerto

T,. ., - tlme between defrost termlnatlons In rnmutes or

T,.,,,, - maxtrnurn tlme between defrosts allowed by con

HSPF 4 90 tu-hichever IS greater1

trols. I ~n rnlnutes or 720 lwhlchever IS less^^

For units tested without indoor fans, the value determined for Q,,,J35) below shall be

product of 1250 Btuh per 1000 SCFM. the increased by a quantity of heat equal to the

length of time in hours during the Frost Ac- cumulation Test that there were indoor air clrculatmg, and the average flow rate of indoor air circulated in units of 1000 SCFM.

the sum of the energy usage required for in- The total energy usage, E,,,,i35) shall be

door-air circulation during the test period and the energy used by the remaining equipment components during the test period. Units not having an indoor fan as part of the model tested, shall set the energy required for indoor air circulation equal to the quantity the product of 365 watts per 1000 SC%nt$ length of time in hours during the Frost Ac-

culating, and the avera e flow rate of indoor cumulation Test that there was indoor alr cir-

air circulated in units of1000 SCFM.

Cyclic Test, Q,,,(47), shall be cletermincd The actual heating done during the

using the following equation:

where - V= the flow rate durlng the on-pen& calculated In

accordance wlth sectlon 7.8.3 of ASHRAE Stan- dard 37-88 In CFM.

and I‘ lhr-F). which is described by the equation:

door cod < F I a i time I I I

d o o r c o ~ l ~ f l a t t m e l r l T.z(f)=br~-ouiu temperalure 01 a r ieavmg the in-

done during the test period shall !,e detcr- The net heating, QDEF (35) in Btu’s

mined using the foilowing equation:

‘where - V5 the average of the alr hou raw calculated at four - or more time Intervals throughout the heatme

hase of the test usin the equatlon In scctmn

C,.=SpecrIic heat at colnsmlt p m s l l r e Of air-r&tC P.8.3 of ASHRAE Stanfard 37.88

V.x=mmnc vowne 01 alr-water r n l x t w r at thr smr rnlxture per pound of dry alr. IBtu/lb-FI.

dry-hudb lemperatttre. htlrnld~~y ratio. and pm slue used rn I.he devrmlnstlon 01 the Indoor l l r llow rate bftTlb).

H;=&un~diry ratio (lbilbj. and I ’ (hr.-Fb, which is described by the equation:

T.I(f)= Dry-bulb’ temperatnre of air entering the in-

T.Z(Z)=Dry-bulb temperature 01 vrltaving the indav door cod 1 k~ at t m e I r

c o 1 l 1 F l a t r m e 1 1 1

1,c cslculntecl as follows: The cyclic degradation coefficient shdl

where

n-hm ~ 4 4 7 ) 8s d&ed above

& ( A i ) u defined above roDuration of time ( h o w ) for one complete

and one conprelsor “ o f f ’ ume. cycle consistlnf of one compressor “on” time

A5.2.1 Calculation of the heatin seasonal performance factor (HSP’~) for air- source heat pumps with single speed compressors.

A6.2.4, and for design teati? req)lirernents For each climate re .on listed in section

equal to both the standardize mlnunum and maximum design heating requirements defined below, calculate the HSPF defined as:

‘HSPF

‘These items have been corrected in accordance with a letter from the Department of tnergy. dared December 7. 1980.

22


where

Z=lndleated the quantity lollowiilg lhe symbol I IS to be summed over all temperature blns.

RH;T,)=suppkmentary resistance heat turn at 3' l empera tw T, reqrured m those eayS where

the heat pump automat!cdlY f u n s Oc

balance of the bu1lQng hurrng requIrm1enrJ. iT,<T.,q]) or when 11 IS needed to m e t the

2 =IS the number of hours in theisb temperature tW81W.

-V bln dmded by N S ni and IS referred lo us the "fnctlonal hotus'in j t h umpemture bin".

3 .413~ i s a wr.veism1 factor whrch w n v e m watt h o r n to B tu.

[hellh bln. IF]

BLiTi= buildme load at temoerature T., Btuh.

The quantities BLCT,), 6(Tj), X(T,). PLF(S) and

RH(T;) N

are defined'by the following equations:

where (C)=O.7i is a correction factor ah ich tcnds to

mmprove the agreement brrreen calcnlstfd

(DlfR)=the mlnimtun and msxlmum design hratlne and mensurd buildmp loads

requuur.ent rluch the beat pump is hkely

rounded 05 to the neswt nandsrdlred DER 1.0 encounter r h r n tnstalltd In a residzpcr.

In sectton A626 in Btuh KheR (minimum design heating requirement)

~ , , ( 4 7 ) (556p) 9 for regions I,

11, 111, IV, and VI 0,,(47), for region V

and . maximum design heating requirement

11, 111, IV, and VI 2.20,.(47), for region V

where Q,, (GT) IS thc h e a t pnmp capacity messmed dunng

Too is the otttaws aeslgn temperature piwn in the Hlah Trmperature Test (1' 4 i F

sectlon A6.2.4

10; TiITom

where Torr- the outdoor temperattire that the compressor IS

autommcally shut off at (If no such tempen- cure ems, T, IS .IVAJJ greater than Torr and TON.)

, ailtomatically ttuned 011 (If apphcable) 11 Tox-the o1ttdoor temDera?lm that the compressor is

d z s w e d L o r lor tempcnttue automatic shut- 03.

Cn=dcgradztior, factm delemined described in s e c t m A 5 2 and A2.2.1.

In using the above equation to calculate

and the power in watts, E, shall be obtained HSPF, the heat pump capacity in Btuh. Q,

as follows:

where $..(47) and E..*(47) and QDEF(35) and E,,(47)andQ..t17)andE..(17)arethecapac- ities (in Btuh) and powers (in watts), measure.! during the High Temperature Test, the Frost Accumulat~on test, and the Low Tem- perature Test. respectively.

tion A6.2.5, calculate t f e heating seasonal "For each of the six re '0116 specified in sec-

costs corresponding to the standardized max- performance factors and seasonal operating

imum and minimum design heating uire- ments and for all other standardM%gn heating requirements (see secti0n~A6.2.8) between the maximum and the minimum. A532 Calculation of the heating seasonal

performance factor (HSPF) for air source heat pumps with a two-speed compressor, two compressors, or cyl-

For each climatic re n listed in section inder unloading.

h6.2;4. szd-for design g a t i n g requirements c-1.c: L. *he standardized minimum and --... .A.G.- . .~~:~. I-d~gn heating requirements de- hned Mow. calculate the HSPF defined as:

where as defined In A5 2.1

n, s as defined In A5.2 !

T, as defined In A5 2 I

and BUT 1 is the building load at temperature T,, in Btuh. calculated by:

~ 0 . ; ; is a mrreetlon kctar which tends to

DHR In sectlon A6.2.6 In Btuh

where (xinimum design hcsting requiremeEtj

11, 111, ITr, and V I

Qi-2~(47) , for region v and (maximum design heating requirement)

=I 11, 111, IV and V!

.2&:(47) for region V where

Q,,'*-"1471 is the heat pumpcapaclty measureddunng

41 F. wlth the unlt operatmg a t the bgh the hlgh temperature performance teal at

compressor speed or with both compressors In operatmn. In Btuh

Too IS the outdoor deslgn temperature pven ~n section A6.2.4 In degrees F.

NOTE: The srrpewcript ( k = l ) mrl (&=Z) refer to the heat pump operating at lor speed or single compressor operation and high speed or two compressor operatim respectively. Q IS the heat pump electrlcal energy usage in the Ih

temperature bln dwlded bvthetotal numberofdm hours and IS evaluated according to the four pos- skble cases of heat pump operation denoted below In watts.

RHIT,I as defined In A5.2.1 and IS evaluated according to the four posslble caws of heat pump operatton denoted below inn watts)

Car z.-unita operating st low com- p:-cssor speed or with a single compressor, i.e., k = l , for which the building hesting load, BL(Ti) is less than or equal to the heating capacity, @-a( Ti).

23


Case ZZ.-Units d t e m t i n g between high speed or two compressor operntion (k=2) and low speed or single compressor operation ( k = l ) to satisfy the building heating load at temperature Ti.

high compressor speed or cycling both com- Carc ZZZ.--Units cycling on and off at

pressors on and off together (k=2) in order to satisfy the building heating lo3d at tem- pent= Ti.

Ti)<BL(T,)<Qc-'( Ti)

24

at high compressor speed or with both com- Case N.--Units operating continuously

presson in continuous opention (k= 2) in order to satisfy the building heating lo3d at temperature Ti.

BL(Ts) 1 e 2 ( T i )

Where in each of the above cases XI T, I -heat pump heatrng load factor PLF = heat pump part load factor tnot requrred Cor

cases 11 and IVI

T,,nas defined in A5.2.1 T,," as defined in A5.2.1

h7T, I - heat pump low temperature cut-out factor.

C,: I =the part load degradation factor dexnbed In section A 2 2 1 and A5.2 for the unit cyclrnp at hiph compressor speed or wrth both mmpres-

Cr," I ' =the part load degradation factor descrlbd in sors slmultaneourlv cvclrnp ~~Cappl~cablei

sectLon A2.2 1 and A52 for the unit cyclrng at low compressor speed or with the rinple mm- oressor that normally operates at low heatrnf loads.

I 17 F<T,<45 F

&-* ( Ti) =

tion A6.2.5. calculate the heating seasonal For each of the six reQons specified in sec-

performance factors and seasonal operating costs correspondmg to the standardized maximum and minimum design heating require-

heating requirements (see section A6.2.6) be- ments and for all other standardized design

tween the maxirnum and the minimum. ASS Heating sccsonal performance fzctor for air-source units with tripLecapacity corn

A 5 2 4 Heating seasonal performance fzctor for units with variable-speed compressors. For units with variable-speed compressors, the heating seasonal performance factor (HSPF! is defined by the following equation:

pressors. I R e s e r v e d )

HSPF =

N


where: all symbols in the above equations are as defined A5.2.2

sign requirements, DHR,,, and D d , , , , The minimum and maximum heatin de-

which a variable-speed heat pump is likely to encounter, shall be evaluated as described for two-speed units in A5.2.2, with the option of using the nominal capacity. Q,,*-"(47 F)! in lieu of the maximum speed capaclty, QA,'-2(4i), in the prescribed equations if the manuf?cturer performed the nominal capacity test.

sidered, the quantities E (TIN,) and RH(TINJ) In evaluation of HSPF, three cases are con-

shall be calculated depending on compressor mode of operation.

minimum speed (k = 1 ) for which the building Case I.-The compressor operates at the

heating load. BL(T,), is less than or equal to the heating capacity, Q,k - YT).

Calculations shall be performed as pre-

A5.2.2, with the exception that system capac- scribed for two-speed systems in Case I of

calculated by the followng equations: ity Qssk-'(7',), and power, E,*'YT,), shall be

Case 11.-The compressor operates a t any intermediate (k = u1 speed between the maximum speed ( K = 2) and minimum (k = 1) speed to satisfy the building load.

P-YT,) = BL;(T,) Evaluate the following equations:

where: @-I'(ql =capacrty delivered by the unit at any Inter-

manmum compressor speed matchxng the medrate speed between the mrnimum and

,C"-"IT,)=the elcctrrcal power Input rqulred by the buildrng load at temperature T,.

unit at temperature T ta delmer capacity marchmr the buildinghad

COP'. "fql = the coefficrent of perfornunce at which the unrt delivers capanty matehrng the build- Ing load a t temperature T,

C O P - V , ) , can be calculated, the unit perfor- Before the coefficient of performance.

mance has to be evaluated at the compressor speed (k = i) at whlch the intermediate speed test was conducted. The capacity of the unit at any temperature T when compressor operates at the intermediate speed (A = i ) may be determined by:

Q@351= the capacity of the un~t at 35 F determined at the Intermediate compressor speed ~k=i~rnthefmnMlmulatioetest

Mq = slope of the capacity curve for the intermediate compressor speed (& = E l

Once the equation for Q"Q,) has been determined, the temperature where Qd$ 'I T ) = BL( T , ) can be found. This temperature is designated at Tu,. A separate T,, shall be determined for each design heating requirement.

erating at the intermediate compressor speed The electrical power input for the unit op-

(k = IJ) and at the temperature (Tu,,) is determined by: E:>'(Tu,,) = E&'(35) + ME(T,, - 35) where:

&'i351 =the electrrcal power input of the unit a t 35 F determlned at the memedia te compressor speed IC = i ~ In the frost accumuiatlon test ME = slope of the e lmr iu l power znpu curve for the intennedtate compressor speed I k = i i

ME EL-' (62) - E::' (47) x (1 - Iv,, 62 - 47

The coefficient of performance, COF"-'(T,,), at the intermediate speed ( K = i ) and temperature T,, can be calculated by the equation:

temperature T3 and T, can be calculated by Similarly, coefficients of performance at

the equations:

shall be calculated by the following equatxon: The coefficient of performance. COP-v!T,).

COP-"(T, )=A+BxT,+CxT, ' where coefficients A, B and C shall be evaluated using the following calculations step:

T: - T i D = - T8i - T$

Case III.--The compressor operates at the

heatin load BL(T,). is greater than or equal maximum speed (k = 2) for which the building

to the kea& capaclty e- z( T, ). Calculations shall be performed as pre-

A5.2.2. scribed for two-speed systems in Case N of

A525 Heating seasonal performance fmtm for split-type ductless systems. For split-type ductless systems, HSPF shall be defined as specified in section A5.2.1 of this Appendix. Separate values of HSPF shall be determined

door cots used in the develo ment of SEER for each corresponding combination set of in-

as specified in section A5.1.7. h e calculations used shall be the same as those used for unit with the same type of compressor.

A53 Calculations of the Actual Represenb-

. tors of Air Source Central Akr C o d - t iw Regional Annual Performance Fac-

tioners (Heat Pum sl Which Provide Both Heating and &ling.

A5.3.1 Calculation of actual re 'onal annual performancefactors (A$F,) for a par-

ardized design heating requirement. ticular locahon and for each stand-

where tCL&I is the actual cooling load hours for the par-

trcular loutron. detenarned from the map in m t l o n A6.1.3.

IQ,*(95Fll IS defined In A5.1. IDHRI IS defined rn A5.2.2.

CCI IS defined in A5.2.2. f H M A 1 is the actual heaung load hours for the par-

trcular loeation determrned from the map

(SEER1 is the season+ energy efiiciency ratio detcr- rcction A6.2.5.

mrned m ractmn A5.1. IHSPF) is the beatan seaaonal performance factors

udetcrmrne8in s+ionA5.2~forearhrc+- u d i ,&sign heapng rquvrment n b the partrcular I w t ~ o n I region or for the .e- tual design heating requirement if known.

where the particular location's region is determined from map in section A6.2.5 and, the standardized design heating requirements

A52 and A6.2.6. within the region are determined in sections

25


A5.3.2 Calculation of representative re- monal annual performance factors (APF,,) for each region and for each standardized design heatmg requirement.

(CLHR) (QSt(95F) 1 (APFR) = + ( H L H R ) ( D H R ) (C)

. ( C L H R ) ( & . ' ( ~ ~ F ) SEER

(HLHR) ( D H R ) (C) + HSPP

'' I(DHRI IS defined rn A5.2.2. %.' 95FII IS defined ~n A5.1.

IC) IS defined in A5.2.2.

where ICLHH I IS the representative cooling load hours for each

heatlng load hours region. as determmed In sec-

lHLHn> IS the representtwe hearlng load hours for each tion A6.3.

regton as determined ~n sect~on A6.2.5 ISEERI IS the seasonal energy efficlency ratlo as deter-

mined In sectlon A5.1. ' HSPFl is the heating seasonal performance factor as

determmed In sectlon A5 2 for each reglon and for each standardized design heatlng require- men1 wlthrn each reglon.

where the regions are listed in section A6.2.5 and, the standardized design heating requirements within the reeons are determined in sections A5.2 and A6.2.6.

A5.4

A5.5

A5.6

Calculations of Seasonal Energy Eff! - ciency Ratio for Water Source Units Which Provide Both Heating and Coo/ ing. (Reserved)

formance Factor for Water Source Calculation of Heating Seasonal Per-

Units Which Provide Both Heating and Cooling. (Reserved Calculatron of Annual Performance Factor For Water Source Units Whit h . Provide Both Heating and Cooling (Reserved)

26


n

2 0

E

m .4

. . . . . . . . . . . . . . . - . . . . . . '0 c n v m - m ~ m . + a + f - w m m m

u u u u u u u

a + + r n e m m - l

0 0 0 0 0 0 0 4 J C

moLT.oLnoLno 0

. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . - ~ N P . I . P ~ W * W

PPI c u r l a

m Y

In

0

0

N

... u . .d . al. c . c .

Ln

0

. . 0

.II

... u .

.c. PI. .4 .

L C C

c -

L.

3

N

0

r d

d o c c o a l - 3 G u - u j -

I n c

27

ARI STANDARD 2101'240-94

F? rl

t

I 8 : : : : : :

;::::::

0 0 0 0 0 8 ooooa

0100N10rnO 9 1 9 c ? 9 ( 9 0 ,

1 1 1 1 1 1 1

28


I . ¶ m . .* t e -2 .. C Y n~ 0 : I I

1 : 1 : 0 8

n ? I 4 9 Nl N

S j r..

. E U I M 4 W

d

0 u n

a 1 a -.

P W L

0 0 Y 0 0

I "

U ? i

n ? ?

n

i i

39 -.d

n~ 0 :

99 c.cI

n~ 0 :

--. 99

n L L 1

2 0

h

W

2

: a Y

0

a 0

Y

a

:

a -. Y a h

W Y 0

W Y

d

L

0 0

LI

L 0 :: d :

29


n t . I

0 1

n w

0 1 U I

9 : N I

.. .,

I I I t

u Y Y

30

c


0 m 0 00

31


A6.2.6 Standard Design Heating Requirements (Btuh) -

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

A6.3 Representative Cooling Load Hours (CLHR) for Each Heating Load Hours Region

Region =R

I

I1

I11

IV

V

VI

2400 7 50

1800 1250

1200 1750

800 2250

4 00 2750

200 2750

A6.4 Ground Water Temperature Map (Reserved) i F R Doc. -38293 Filed 12-17-79: 8:U am]

BILLING COO€ H504l-C

. 32

ARI STANDARD 2101240-94 -

APPENDIX B. REFERENCES

B1 Listed here are all standards, handbooks and other 81.5 AM Standard 320-93, Water-Source Heat publications essential to the formation and implementation of Pumps, Air-conditioning and Refrigeration Institute, the standard. All references in this appendix are considered 1993,4301 North Fairfax Drive, Suite 425, Arlington, as part of this standard. VA 22203, U.S.A.

B1.1 ASHRAE Handbook of Heating, Ventilating, and Air Conditioning Systems and Equipment. American Society of Heating, Refrigerating, and Air- Conditioning Engineers, Inc., 1791 Tullie Cicle N.E., Atlanta, GA 30329, U.S.A.

B1.2 ASHRAE Termimlogy of Hearing, Ventilation, Air Conditioning & Refrigeration. American Society of Heatmg, Refrigerating, and Air-conditioning Engineers, Inc.. 1991, 1791 Tullie Circle N.E., Atlanta, GA 30329, U.S.A.

B 1 3 ASHRAE Standard 37-1988, Methods of Testing for Rating Unitary Air-conditioning and Heat Pump Equipment, American Society of Heating, Refrigerating, and Air-conditioning Engineers. Inc., 1988, 1791 Tullie Circle N.E., Atlanta, GA 30329, U.S.A.

B1.6 ARI Standard 325-93. Ground 'Warer-Source Heat Pumps, Air-conditioning and Refrigeration Institute. 1993, 4301 North Fairfax Drive, Suite 425. Arlington, VA 22203, U.S.A.

B1.7 ARI Standard 34OP60-93. Commercial and Industrial Unitary Air-conditioning and Heat Pump Equipment, Air-conditioning and Refrigeration Institute, 1993, 4301 North Fairfax Drive. Sulte 425. Arlington, VA 22203, U.S.A.

B1.8 . IEC .Standard Publication 38, IEC Standard Voltages. International Electrotechnical Commission, 1983,3. rue de Varembe, P.O. Box 131, 1211 Geneva 20, Switzerland.

B1.4 ARI Standard 110-90, Air-conditioning and Refrigerating Equipment Nameplate Voltages, Air- Conditioning and Refrigeration Institute, 1990, 4301 North Fairfax Drive, Suite 425, Arlington, VA 22203, U.S.A.

33


APPENDIX C. PRESCRIPTIVE METHODOLOGY -

FOR THE CYCLIC TESTING OF DUCTED SYSTEMS REQUIRED BY APPENDIX A, SECTIONS A4.1 and A4.2

C1 For the purpose of uniformity in the cyclic test requirements of Appendix A, the following test apparatus and conditions shall be met:

C1.1 The test apparatus is a physical arrangement of dampers, damper boxes. mixers, thermopile and ducts all properly sealed and insulated. See Figures C1 through C4 for typical test apparatus. Note arrangement and size(s) of the components may be altered to meet the physical requirements of the unit to be tested.

C2.1 Dampers and their boxes shall be located outside of the ASHIUE Standard 37-88 pressure measurement locations in the inlet air and outlet air ducts.

C3.1 The entire test apparatus shall not have a leakage rate which exceeds 20 cfm [94 Us] when a negative pressure of 1 inch of water r0.25 Wa] is maintained at the apparatus exit air location.

C4.1 The apparatus shall be insulated to have 'ZT' value not to exceed 0.04 total.

C5.1 The air mixer and a 40% maximum open area perforated screen shall be located in the outlet air portion of the apparatus upstream of the outlet damper. The mixer(s) shall be as described in ASHRAE 41.1-1986 Standard Merhod for Temperature Measurement. The mixing device shall achieve a maximum temperature spread of 1.5"F [0.8 k] across the device. An inlet air mixer is not required.

C7.1 The dampers shall be capable of being . completely opened or completely closed within a time period not to exceed 10 seconds for each action. Airflow through the equipment bemg tested should stop within 3 seconds after the airflow measuring device is de-energized. The air pressure difference (AP) at the nozzle should be within 2% of steady state AP within 15 seconds from the time the air measuring device is re-energized.

C8.1 Test set up, temperature, and electrical measurements must be identical for "C" and " U ' tests in order to obtain minimum error in C,. Electrical measurements shall be taken with an integrating type meter per 5.4.1 of ASHRAE 37-88 having an accuracy in accordance with 5.4.2 of ASHRAE 37-88 for all ranges experienced during the cyclic test.

C9.1 Prior to taking test data, the uni t shall be operated at least one hour after achieving dry coil conditions. The drain pan shall be drained and the drain opening plugged. The drain pan should be completely dry in order to maximize repeatability and reproducibility of test results.

C10.1 For coil only units not employing an enclosure, the coil shall be tested with an enclosure constructed of 1 inch [2.54 cm] (6 pounds per cubic foot [96 kg/m'], density) fiberglass ductboard or an equivalent "R" value. For units with enclosures or cabinets, no extra insulating or sealing shall be employed.

(26.1 The temperature d'flerence between inlet air and outlet air shall be measured by a thermopile. The thermopile shall be constructed of 24 gauge thermocouple wire with 16 junctions at each end. At each junction point the wire lnsulation shall be stripped for a length of 1 inch. The junction of the wires shall have no more than two bonded turns.

34

ARI STANDARD 21OQ40-94

c


36 !

I

I/ 1 jlI ' ,

I I

I

I i

' + I CL I I

U v)

f


K

I '

I


c

1

a W c W

9 I I

l & I

VI c W z

s a z c VI

0

L 5 Y 3 m a

W

3 a

a a

t W

I ' I

38 I'

c C w


APPENDIX D. METHOD AND EXAMPLE OF CALCULATING INTEGRATED PART LOAD VALUES (IPLV)

Section Dl. Purpose and Scope

D1.l Purpose.

D1.l.l This appendix shows sample calculations for determining Integrated Part Load Values (IPLV).

D l 3 Scope

D1.2.1 This appendix is for equipment covered by this standard.

Section D2. Equations and Definition of Terms

D2.1 General Equarion.

Section D3. Calculation Example for a Four Capacity Step System

D3.1 Unit Performance Dara & Sample Calculation.

D3.1.1 Assume equipment has four capacity steps as follows:

100% (full load) 75% of full load 50% of full load 25% of full load

D3.1.2 Obtain part load factors from Figure 1 (see Figures D 1. and D2.).

D3.13 Obtain EER at each capacity step per 5.2.

D3.1.4 Calculate IPLV using the general equation with:

n = 4 PLF, = 1.0 EER, = 8.9 [2.6] PLF, = 0.9 EER, = 7.7 [2.3] PLF, = 0.4 EER, = 7.1 [2.1]

L PLF, = 0.1 EER, = 5.0 [ 1-51

where:

PLF = Part-LoadFactor determined from Figure I

n = Total number of capacity steps

Superscript 1 = 100% capacity and EER at part-load rating conditions

Subscript 2; 3 etc. = Specific capacity and EER at part-load steps per 5.2.

Enter the above values in the general equation, (D2.1).

PLV = (1.0 - 0.9) (- -) 8.9 + 7.7 2

+ (0.9 - 0.4) ( 1 7.7 + 7.1 2

+ (0.4 - 0.1) ( 1 7.1 + 5.0 2

+ (0.1 x 5.0)

= (0.1 x 83) + (0.5 x 7.4)

+ (03 L 6.0) + 0.5

39


= 0.83 + 3.70 + '1.80 + 0.5

IPLV = 6.83 rounded to 6.8

sL!h&

PLV = (1.0 - 0.9) ( 1 2.6 + 23 2

+ (0.9 - 0.4) (2'3 + 2'1) + (0.4 - 0.1) (2'1 +

2 2 1

+ (0.1 x 5.0)

= (0.1 x 2.45) + (0.5 x 22) + (0.3 x 1.8) + 1.5

= 0245 + 1.1 + 0.54 + 1.5

IPLV = 2.0

To further illustrate the calculation process. see Figure D2. Example.


0 20 40 80 100

PERCENT OF FULL-LOAD CAPACITY AT PART-LOAD CONDITIONS

Note: Curve is Based on Following Equation:

PLF = A0 + (AI X Q) + (A2 X 0') + (A3 x 0') + (A4 x Q") + (A5 x 0') + ( A 6 x 0") where: PLF = Part-Load Factor

Q = Percent of full-load capacity at part-load rating

A 0 = -0.12773Y 17 x IO -'' A I = -0.27648713 x 10-3 A2 = 0.50672449 x IO- ' A3 = -0.259 66636 x IO-' A 4 = 0.69875354 X l o - " A5 = -0.76859712 x lo-" A 6 = 0.28918272 x IO-"'

conditions.

Figure Dl. Part Load Factor Curve

41


Figure M. Example IPLV Calculation (EP Units)

Using information from D3.1.1.; D3.1.2 and D3.1.3

capacity step

1

2

3

4

t Full Load PLF' cap.

100%

0.9 75%

1 .o

50%

0.1 25%

0.4

0.0 090

Mrs. Part F'LF Diff. Avg. Part LoadEER LoadEER

8.9'

(0.1 - O.O)=o. 1 5.0

(0.4 - 0.1)=0.3 7.1

(0.9 - 0.4)=0.5 7.7

(1.0 - 0.9)d.l - -

-

7.4 -

8.3

6.0

- 5.0'

-

-

- -__-_

Avg. EER x F'LF Diff. =

8.3 x 0.1

7.4 x 0.5

6.0 x 0.3

5.0' x 0.1

Single number JPLV

- - - - - - - -

*Rounded to 6.8

NOTES: 'For the range between 0% capacity and the last capacity step, use EER of the last capacity step for the average W. 'The 100% capacity and EER are to be determined at the part-load rating conditions; 'Pan-load factor from Figure Dl.

IPLV Calculation (SI Units)

Using information from D3.1. I.; D3.1.2 and D3.1.3

Capacity step

1

2

3

4

% F u l l h a d PLF' cap.

100%

0.9 75%

1 .o

50% 0.4

25%

0.0 0%

0.1

Mrs. Part Avg. Part Load EER Load EER

2.6

2.3

2.1

1.5

=

2.2 =

2.45

=

1.5 =

1.8

_____ I PLF Diff.

( 1 .O - 0.9)dl.l

(0.9 - 0.4kO.5

(0.4 - 0.1)=0.3

(0.1 - O.O)=O. 1

Avg. -1 Weighted

0.83

3.70

1.80

LIZ!

6.83'

Avg. EER X PLF M. =

2.45 x 0.1 - -

2.2 x 0.5 - -

1.8 x 0.3 - -

1.5' x 0.1 - -

Smgle number IPLV

NOTES: 'For the range between 0% capacity and the last capacity step. use EER of the last capacity step for the average EER. 'The 100% capacity and EER arc to be determined at the part-load mmg condmonr. 'Pan-load factor from Figure Dl.

Weighted Avg.

0.245

1 . 1

0.54

Q,Ll

2.0

I

42

ARI 210.240-94

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Transcript of ARI 210.240-94