draft standard for variable refrigerant flow (vrf)

draft standard for variable refrigerant flow (vrf)
DRAFT STANDARD FOR VARIABLE REFRIGERANT FLOW (VRF) MULTIPLE SPLITSYSTEM AIR-CONDITIONERS AND HEAT PUMPS —
GENERAL REQUIREMENTS, PERFORMANCE TESTING AND RATING
ISHRAE RAMA Standards Development committee
Ashish Rakheja
The National Chair – ISHRAE
Standards Committee
Sudhir Kumar Sinha
Head Standards Development – RAMA
Managing Director,
Aeon Integrated Building Design
Consultants,
CEO, Swegon Blue Box Pvt. Ltd.
Core Committee:
Dr. Jyotirmay Mathur
Manjunath V
Nirmal Ram D
Professor, Mechanical Engineering Department, Centre for Energy and
Environment, Malviya National Institute of Technology, Jaipur, India
Standards & Program Manager, UL India Pvt. Ltd, India, Bengaluru, India
Ramchandran
Fellow ASHRAE, Past President ISHRAE Bangalore Chapter,
Principal Consultant, Cerebration Consultants, Bangalore, India.
Director, Eskayem Consultants Pvt. Ltd. Mumbai, India.
Sudipta Sanyal
Vice President – Data Centre design, Sterling & Wilson Ltd. Mumbai, India
Sanjay Goyal
Director & Senior Vice President, Daikin Air Conditioning India Pvt. Ltd.
Gurgaon, India
Director - Marketing & Strategy, Carrier Ai rconditioning & Refrigeration
Limited, Gurgaon, India
Viney Khunger
Advisory committee:
Technical Committee
Amit Maheshwari
Director – Marketing & Strategy, Carrier India.
Anil Kumbhar
Head R&D, Voltas Ltd., India
Anuj Kumar
Assistant General Manager, LG Electronics, India
Ashish Ojha
General Manager – LC, Carrier Midea, India.
Bimal Tandon
Director – Engineering, Carrier India
Frank Zhou
General Manager, Carrier Midea, India
Gaurav Mehtani
Senior Manager, Daikin India
Gurmeet Singh
Managing Director, Hitachi Home & Life Solutions (India) Limited, India
Henry Hu
Deputy Manager, Carrier Midea, India
Hoshiyar Singh
Manager, Samsung India Pvt Ltd., India
Jawa K J
Managing Director, Daikin India, India
Kazuyuke Kato
Deputy General Manager, Mitsubishi Electric India. India
M P Agarwal
Vice President, LG Electronics, India
Nilesh Shah
Deputy Vice President, Hitachi Home & Life Solutions (India) Limited, India
Pankaj Dharkar
Managing Director, Pankaj Dharkar Associates, India
R K Sahu
Senior General Manager, ETA Engineering Pvt. Ltd, India
R K Srivastava
Senior Manager, ETA Engineering Pvt. Ltd., India
Rajesh Nagari
Assistant Vice President, Hitachi Home & Life Solutions (India) Ltd., India
Rajkumar Iyer
Consultant, Mitsubishi Electric India, India
Sachin Maheshwari
National President, ISHRAE
Sampath Kumar
Product Development Manager, Voltas Ltd., India
Seemant Sharma
Director – ESG, JCI India, India
Senthil Thangam
General Manager, Blue Star Ltd., India
Sheetal M Kulkarni
General Manager R&D, Blue Star Limited. India
Foreword
This DRAFT standard is an initiative of ISHRAE (Indian Society of Heating Refrigerating and Air
conditioning Engineers) and RAMA (Refrigeration and Air conditioning Manufacturers Association) to
introduce equipment testing standards for HVAC&R industry applicable for Indian industry &
environment. This work of preparing DRAFT standard is carried out through a joint technical committee
set up by ISHRAE & RAMA. The Technical committee comprised of representatives from Consultants,
User Industry, Manufacturers, and International organizations, governmental and non-governmental
bodies in liaison with ISHRAE-RAMA standards core committee. ISHRAE-RAMA standards core committee
collaborates and proposes to Bureau of Indian Standards (BIS) and / or Bureau of Energy Efficiency (BEE)
on matters of performance standardization.
ISO Guide 59 guidelines have been considered and followed to a large extent in drafting this standard.
This DRAFT standard after wide circulation amongst the member bodies of ISHRAE-RAMA and industry
at large shall be offered for adoption as consensus based Indian standard.
1.0 Scope
a) This standard covers the performance criteria, general requirements, method of testing for
the measurement of performance and Part load performance for calculating Indian Seasonal
Energy Efficiency Ratio and Seasonal Performance Factor of factory-made,
b) electrically driven, Variable refrigerant flow multiple split air conditioners working on vapor
compression principle, ,
c) with a single refrigeration circuit, utilizing one or more variable capacity compressors, one or
more outdoor units and two or more indoor units of non-ducted and/or ducted type,
d) designed for individual operation and combined operation,
e) air cooled cooling only and / or cooling and heat pump,
f) to work with rated voltage up to and including 250 V, 50 Hz AC, single phase and up to and
including 415 V, 50 Hz AC for three phase input power supply
1.1 This standard does not cover
a)
Air conditioners working on Vapor Absorption principle
b)
Individual assemblies not constituting complete refrigerant system
c)
Evaporative cooled condensing units
d)
Air conditioners with Water cooled condenser
e)
Air conditioners with Heat recovery system
2.0 REFERENCES
The following referenced documents are indispensable for the application of this document. For dated
references, only the edition cited applies. For undated references, the latest edition of the referenced
document (including any amendments) applies.
The following Standards contain provisions which through reference in this text, constitute provisions of
the standards. At the time of publication, the editions indicated were valid. All standards are subject to
revision and parties to agreements based on this standard are encouraged to investigate the possibility of
applying the most recent editions of the Standards indicated below:
IS Number
Title
101 (Part 6 : Sec 1)
Methods of sampling and test for paints, varnishes and related
products – Part 6 : Durability tests – Section 1 : Resistance to
humidity under conditions of condensation
IS 101 (Part 6 : Sec 5)
Method of sampling and test for paints, varnishes and related
products Part 6 Durability test on Paint films section 5 Accelerated
weathering test
IS 101 (Part 7 : Sec 1)
Methods of Sampling and Test for Paints, Varnishes and Related
Products – Part 7 : Environmental Tests on Paint Films – Section 1
: Resistance to water
IS 101 (Part 7 : Sec 2)
Methods of sampling and test for paints, varnishes and related
products part 7 Environmental tests on paint films Sec 2
Resistance to liquids
IS 101 (Part 7 : Sec 3)
Methods of sampling and test for paints, varnishes and related
products Part 7 Environmental tests on paint films Sec 3
Resistance to heat
IS 196
Atmospheric conditions for testing
IS 325
Three phase induction motors
IS 1391 – Part 1
Room air conditioners – Unitary type
IS 1391 – Part 2
Room air conditioner – Split type
IS 8148
Packaged Air Conditioners
IS 2360
Voltage bands for electrical installations including preferred
voltages and frequency
IS 3615
Glossary Of Terms Used In Refrigeration And Air Conditioning
ISO 5151
Non-ducted air conditioners and heat pumps — Testing and
rating for performance
ISO 15042
Multiple split-system air-conditioners and air-to-air heat pumps
— Testing and rating for performance
ISO 16358 – 1
Air-cooled air conditioners and air-to-air heat pumps — Testing
and calculating methods for seasonal performance factors —
Part 1: Cooling seasonal performance factor
ISO 16358 – 2
Air-cooled air conditioners and air-to-air heat pumps — Testing
and calculating methods for seasonal performance factors —
Part 2: Heating seasonal performance factor
ISO 16358 – 3
Air-cooled air conditioners and air-to-air heat pumps — Testing
and calculating methods for seasonal performance factors —
Part 3: Annual performance factor
ISO 5149 – 1
Refrigerating systems and heat pumps – Safety and
environmental requirements – Part 1: Definitions, classification
and selection criteria
ISO 5149 – 2
Refrigerating systems and heat pumps – Safety and
environmental requirements – Part 2: Design, construction,
testing, marking and documentation
ISO 5149 – 3
Refrigerating systems and heat pumps – Safety
environmental requirements – Part 3: Installation site.
and
ISO 5149 – 4
Refrigerating systems and heat pumps – Safety and
environmental requirements – Part 4: Operation, maintrenance,
repair and recovery
EN 14825
Air conditioners, liquid chilling packages and heat pumps with
electrically driven compressors for space heating and cooling Testing and rating at part load conditions
EN 145111 – 1
Air conditioners, liquid chilling packages and heat pumps with
electrically driven compressors for space heating and cooling –
Part 1: Terms, definitions and classification
EN 145111 – 2
Air conditioners, liquid chilling packages and heat pumps with
electrically driven compressors for space heating and cooling Part 2: Test conditions
EN 14511 – 3
Air conditioners, liquid chilling packages and heat pumps with
electrically driven compressors for space heating and cooling Part 3: Test methods
EN 14511 – 4
Air conditioners, liquid chilling packages and heat pumps with
electrically driven compressors for space heating and cooling Part 4: Operating requirements, marking and instructions
IS / ISO 817
Organic refrigerants – Number designation
ISO 3744
Acoustics -- Determination of sound power levels and sound
energy levels of noise sources using sound pressure -- Engineering
methods for an essentially free field over a reflecting plane
ISO 9614 – 1
Acoustics - Determination of Sound Power Levels of Noise
Sources Using Sound Intensity - Part 1: Measurement at Discrete
Points
ISO 9614 – 2
Acoustics - Determination of Sound Power Levels of Noise
Sources Using Sound Intensity - Part 2: Measurement by Scanning
AHRI 1230
Performance Rating of Variable Refrigerant Flow (VRF) Multi-Split
Air-Conditioning and Heat Pump Equipment
3.0 Terms and definitions
For the purposes of this standard, the terms given in IS 3615 – Glossary of terms used in Refrigeration and
Air conditioning, and in addition following definitions listed below shall apply.
3.1 Standard air
Dry air at 20 °C and at a standard barometric pressure of 101.325 kPa, having a mass density of 1.204
kg/m3
3.2 Air-conditioner
An encased assembly or assemblies designed primarily to provide free or ducted delivery of conditioned
air to an enclosed space room or zone (conditioned space)
NOTE: It can be either single-package or split-system and comprises a primary source of refrigeration for cooling and
dehumidification. It can also include means for heating other than a heat pump, as well as means for circulating,
cleaning, humidifying, ventilating or exhausting air. Such equipment can be provided in more than one assembly,
the separated assemblies (split-systems) of which are intended to be used together.
3.3 Heat pump
An encased assembly or assemblies designed primarily to provide free or ducted delivery of conditioned
air to an enclosed space, room or zone (conditioned space) and includes a prime source of refrigeration
for heating.
NOTE: It can be constructed to remove heat from the conditioned space and discharge it to a heat sink if cooling and
dehumidification are desired from the same equipment. It can also include means for circulating, cleaning,
humidifying, ventilating or exhausting air. Such equipment can be provided in more than one assembly, the
separated assemblies (split-systems) of which are intended to be used together.
3.4 Variable Refrigerant Flow Multi-Split system
A split-system air-conditioner or heat pump incorporating a single refrigerant circuit, and one or more
outdoor units at least one variable speed compressor or an alternative compressor combination for
varying the capacity of the system by five or more steps, multiple indoor units, each of which can be
individually controlled, each capable of individual zone temperature control, through zone temperature
control devices and common communications network
3.5 Full capacity
Capacity of the system at rated condition when all indoor units and outdoor units are operated at fullload (100% load) operating conditions.
Note: Rated capacity = Full capacity for purpose of this standard
3.6 Total cooling capacity
Amount of sensible and latent heat that the equipment can remove from the conditioned space in a
defined interval of time
3.7 Latent cooling capacity
Amount of latent heat that the equipment can remove from the conditioned space in a defined interval
of time
3.8 Sensible cooling capacity
Amount of sensible heat that the equipment can remove from the conditioned space in a defined interval
of time
3.9 Heating capacity
Amount of heat that the equipment can add to the conditioned space (but not including supplementary
heat) in a defined interval of time
3.10
Part-load capacity
Capacity of the system when the indoor and outdoor units are operating at part load.
3.11
Capacity ratio
Ratio of the total stated cooling capacity of all operating indoor units to the stated cooling capacity of the
outdoor unit at the rating conditions
3.12
Energy efficiency ratio (EER)
Ratio of the total cooling capacity to the effective power input to the device at any given set of rating
conditions
3.13
Coefficient of performance (COP)
Ratio of the heating capacity to the effective power input to the device at any given set of rating conditions
3.14
Effective power input (PE)
Average electrical power input to the equipment obtained from the
3.14.1 Power input for operation of the compressor(s),
3.14.2 The power input to electric heating devices used only for defrosting,
3.14.3 The power input to all control and safety devices of the equipment, and
3.14.4 The power input for operation of all fans, factory installed condensate pumps, if applicable.
3.15
Total power input (kW)
Average electrical power input to the equipment as measured during the standard rated condition test
3.16
Full-load operation
Operation with the equipment and controls configured for the maximum continuous duty refrigeration
capacity specified by the manufacturer.
3.17
Indian Seasonal Energy Efficiency Ratio (ISEER)
A single value number that is a representation of the Cooling part load efficiency of a multi system air
conditioner calculated based as described in Annexure F
3.18
Part load factor
Ratio of the performance when the equipment is cyclically operated to the performance when the
equipment is continuously operated, at the same temperature and humidity conditions
3.19
Defined cooling load
Heat defined as cooling demand for a given outdoor temperature.
3.20
Cooling full-load operation
Operation with the equipment and controls configured for the maximum continuous refrigeration
capacity specified by the manufacturer and allowed by the unit controls
Note: Unless otherwise regulated by the automatic controls of the equipment, all indoor units and
compressors shall be functioning during the full-load operation.
3.21
Cooling half load operation
Operation with the equipment and controls configured for the 50% continuous refrigeration capacity
specified by the manufacturer.
Note: All indoor units shall be functioning during the half-load operation.
3.22
Cooling minimum-load operation
Operation of the equipment and controls at minimum continuous refrigeration capacity
Note: All indoor units shall be functioning during the minimum-load operation.
3.23
Heating full-load operation
Operation with the equipment and controls configured for maximum continuous refrigeration capacity at
rated heating capacity condition
Note: Unless otherwise regulated by the automatic controls of the equipment, all indoor units and
compressors shall be functioning.
3.24
Minimum-load operation
Operation of the equipment and controls at minimum continuous refrigeration capacity
Note: All indoor units shall be functioning
3.25
Standard heating full capacity
Heating capacity at rated condition at full-load operating condition
3.26 Ratings
3.26.1 Published rating
A statement of the assigned values of those performance characteristics, under stated rating conditions,
by which a unit may be chosen to fit its application. These values apply to all systems of like nominal size
and type produced. As used herein, the term Published Rating includes the rating of all performance
characteristics shown on the unit or published in specifications, advertising or other literature controlled
by the manufacturer, at stated Rating Conditions.
Note: The published ratings are the ratings declared by the manufacturer in any form as defined above.
3.26.2 Standard Rating
Standard ratings shall be published for cooling capacities (sensible, latent and total), heating capacity, EER
and COP, as appropriate, for all systems produced in conformance with this Standard. These ratings shall
be based on data obtained at the established rating conditions in accordance with the provisions of this
Standard.
3.26.3 Other rating
Additional ratings may be published based on conditions other than those specified as standard rating
conditions, or based on conditions specified by specific customer needs, if they are clearly specified and
if the data are determined by the methods specified in this Standard, or by analytical methods which are
verifiable by the test methods specified in this Standard.
3.27
Sound Power Level:
Ten times the logarithm to the base 10 of the given sound power to the reference sound power which is
1 pW(10-12 W), and expressed in decibels (dB)
Note: The Sound power should be measured as per ISO 13261 – 1; ISO 13261 – 2, for non-ducted indoor
units and ducted indoor units.
4.0 Construction
The construction of the variable refrigerant flow system should conform to the relevant requirements as
defined in ISO 5149 – 1: Refrigerating systems and heat pumps – Safety and environmental requirements
– Part 1: Definitions, classification and selection criteria and ISO 5149 – 2: Refrigerating systems and heat
pumps – Safety and environmental requirements – Part 2: Design, construction, testing, marking and
documentation.
5.0 Rating requirements
Standard rating shall be established by testing at standard rating conditions specified in clause 6 for
cooling only equipment and clause 7 for heat pump.
5.1 Test requirements
5.1.1
Compressor and controller setting
The manufacturer shall specify the specific setting that is required to give full load capacity, half load
capacity and minimum load capacity. Also, manufacturer must provide a schematic and sequence of
operation for providing control of the system. If the manufacturer does not define the setting, the
thermostat or controller shall be set to its allowable minimum temperature setting.
Manufacturer shall designate intermediate and minimum compressor speeds / controller setting for both
cooling and heating.
If the equipment cannot be maintained at steady-state conditions by its normal controls, then the
manufacturer shall modify or override such controls so that steady-state conditions are achieved.
5.1.1.1 Maximum compressor speed (or) controls setting for full capacity:
Shall be the compressor speed or controller setting as defined by manufacturer at which the compressor
delivers full capacity. The maximum compressor speed or controller setting shall be a fixed value for
cooling mode tests and heating mode tests. The value of maximum compressor speed or controller setting
for heating mode tests may be same or different from the cooling mode value.
5.1.1.2 Half compressor speed (or) controls setting for half capacity:
Shall be the compressor speed or controller setting as defined by manufacturer at which the 50% of full
capacity is delivered and falls within difference between minimum and maximum speeds (controller
setting) for both cooling and heating mode.
5.1.1.3 Minimum compressor speed (or) controls setting for minimum capacity:
Shall be the compressor speed or controller setting as defined by manufacturer at which the compressor
operates at a steady-state level below which the system would rarely operate. The minimum compressor
speed or controller setting shall be a fixed value for cooling mode tests and heating mode tests. The value
of minimum compressor speed or controller setting for heating mode tests may be the same or different
from the cooling mode value.
5.2 Connecting tubing length
The connecting tubing for all standard ratings of equipment connecting tubing shall be as per
manufacturer's specifications or 5 m on each line. The lengths shall be actual lengths, not equivalent
lengths, and no account shall be taken of the resistance provided by bends, branches, connecting boxes
or other fittings used in the installation for the test equipment. The tubing length shall be measured from
the enclosure of the indoor unit to the enclosure of the outdoor unit. Minimum of 40 % of the total length
of the interconnecting tubing shall be exposed to the outdoor conditions with the rest of the tubing
exposed to the indoor conditions. The tubing diameters, insulation, details of installation, evacuation and
charging shall be in accordance with the manufacturer's published recommendations.
The Figure 1 The installation of indoor and outdoor unit
Test room outdoor side
Indoor unit 1
OUTDOOR UNIT
Indoor unit 2
Indoor unit 3
Indoor unit ‘n’
Test room indoor side
5.3 Indoor unit selection:
Figure – 1 Unit installation and tubing layout
For all tests other than part load test, the capacity ratio of indoor units to outdoor unit shall be equal to 1
(±5%). The number and capacity of individual indoor units shall be selected such that the capacity ratio
requirement as per part load testing requirement shall be met.
5.4 Airflow setting
5.4.1
General
The airflow settings for ducted and non-ducted units is specified as below.
Ducted indoor units rated less than 8 kW and intended to operate at an external static pressure of less
than 25 Pa shall be tested as non-ducted units.
5.4.2
Airflow setting for non-ducted indoor units measured by air-enthalpy method
The louvers and fan speed shall be set such that maximum steady state air flow is delivered by the indoor
unit as specified by the manufacturer.
For inverter type control units, if the manufacturer indicates a speed of the fan different from the
maximum one to set on the control device for a given rating condition, then this speed shall be used.
Tests shall be conducted with 0 Pa external static pressure maintained at the air discharge of the
equipment. All air quantities shall be expressed as m3/s of standard air.
The Cooling Minimum air volume rate is the air volume rate during minimum cooling test, unit operated
at an external static pressure of 0 Pa and at the indoor fan setting used with compressor speed / controller
setting at minimum capacity test.
The cooling half air volume rate is the air volume rate during half cooling test, unit operated at external
static pressure of 0 Pa and at the indoor fan setting used with compressor speed / controller setting at
half capacity test.
For heating test the air volume rate shall be selected similarly as defined above
5.4.3 Airflow setting for ducted indoor units
5.4.3.1 General
The airflow rate shall be specified by the manufacturer. This flow rate shall be for full-load cooling and be
expressed in cubic meters per second (m3/s) of standard air conditions, as defined in 3.1, and correspond
to a non-operating compressor.
The airflow settings of the units shall be in accordance with Annexure A.
The rated airflow rate given by the manufacturer shall be set and the resulting external static pressure,
𝑃𝑒 (ESP) measured. The measured ESP shall be larger than the ESP for rating, defined in Table 1. If the unit
has an adjustable speed, it shall be adjusted to the lowest speed that provides at least the ESP for rating.
5.4.3.2 Cooling Minimum Air Volume Rate
For ducted units that regulate the speed (as opposed to the air volume) of the indoor fan,
𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝑚𝑖𝑛𝑖𝑚𝑢𝑚 𝑎𝑖𝑟 𝑣𝑜𝑙𝑢𝑚𝑒 = 𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝑓𝑢𝑙𝑙 𝑙𝑜𝑎𝑑 𝑣𝑜𝑙𝑢𝑚𝑒 𝑟𝑎𝑡𝑒 ×
𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝑚𝑖𝑛𝑖𝑚𝑢𝑚 𝑓𝑎𝑛 𝑠𝑝𝑒𝑒𝑑
𝐹𝑎𝑛 𝑠𝑝𝑒𝑒𝑑 𝑎𝑡 𝑟𝑎𝑡𝑒𝑑 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛
Where cooling minimum fan speed corresponds to the fan speed used when operating at the minimum
compressor speed. For such systems, obtain the Cooling Minimum Air Volume Rate regardless of the
external static pressure
Manufacturer shall specify the cooling minimum air volume rate if the air volume is regulated by indoor
fan.
5.4.3.3 Cooling half air volume rate
For ducted units that regulate the speed (as opposed to the air volume) of the indoor fan,
𝐶𝑜𝑜𝑙𝑖𝑛𝑔 ℎ𝑎𝑙𝑓 𝑎𝑖𝑟 𝑣𝑜𝑙𝑢𝑚𝑒 = 𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝑓𝑢𝑙𝑙 𝑙𝑜𝑎𝑑 𝑣𝑜𝑙𝑢𝑚𝑒 𝑟𝑎𝑡𝑒 ×
𝐶𝑜𝑜𝑙𝑖𝑛𝑔 ℎ𝑎𝑙𝑓 𝑓𝑎𝑛 𝑠𝑝𝑒𝑒𝑑
𝐹𝑎𝑛 𝑠𝑝𝑒𝑒𝑑 𝑎𝑡 𝑟𝑎𝑡𝑒𝑑 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛
Where cooling half fan speed corresponds to the fan speed used when operating at the intermediate
compressor speed. For such systems, obtain the Cooling intermediate Air Volume Rate regardless of the
external static pressure
Manufacturer shall specify the cooling half air volume rate if the air volume is regulated by indoor fan.
5.4.4
External Static Pressure (ESP) for rating
5.4.4.1 If the rated External Static Pressure specified by the manufacturer is greater than or equal to the
minimum value given in Table 1, the specified rated ESP is used as the ESP for rating.
5.4.4.2 If the rated ESP specified by the manufacturer is less than the minimum value given in Table 1,
and larger than or equal to the 80 % of the maximum ESP, the specified rated ESP is used as the
ESP for rating. The maximum ESP may either be specified by the manufacturer or identified from
fan curves provided by the manufacturer.
5.4.4.3 If the rated ESP specified by the manufacturer is less than the minimum value given in Table 1 and
less than 80 % of the maximum ESP, the value of Table 1 or 80 % of the maximum ESP, whichever
is smaller, is used as the ESP for rating.
5.4.4.4 If the rated ESP is not specified by the manufacturer, the value of Table 1 or 80 % of the maximum
ESP, whichever is smaller, is used as the ESP for rating.
5.4.4.5 The process of selecting the ESP for rating is shown in Figure 2.
If the determined ESP for rating is less than 25 Pa, the unit can be considered a non-ducted indoor unit.
Airflow measurements shall be made in accordance with the provisions specified in Annex A, as
appropriate, as well as the provisions established in other appropriate annexes of this Standard.
Table 1 – External Static Pressure requirement for ducted split indoor units
Standard capacity ratings kW
Minimum external static pressure – Pa
0<∅<8
25
8 ≤ ∅ ≤ 12
37
12 ≤ ∅ ≤ 20
50
20 ≤ ∅ ≤ 30
62
30 ≤ ∅ ≤ 45
75
45 ≤ ∅ ≤ 82
100
The rated ESP specified by
the manufacturer is equal to
or greater than the value in
Table 11
YES
The ESP for rating is equal to the
rated ESP specified by
manufacturer
NO
The rated ESP specified by
the manufacturer is equal to
or greater than 80% of
maximum ESP
YES
The ESP for rating is equal to the
rated ESP specified by
manufacturer
NO
The value specified in Table 1
is greater than or equal to
80% of maximum ESP
NO
YES
The ESP for rating is equal to the
80% of maximum ESP
The ESP for rating is equal to the value in
Table 1
Figure – 2 – Flowchart for selecting External static pressure (ESP) for rating test
5.4.5
Outdoor air flow
If outdoor units with adjustable airflow, all tests shall be conducted at fan control setting as specified by
the manufacturer.
For outdoor units with fixed airflow, all tests shall be conducted at the air volume flow rate inherent in
the equipment operated with all the standard accessories like louvers or ductwork and any such
attachments supplied by the manufacturer for normal installation practice. Once established, the outdoor
side air circuit of the equipment shall be unchanged throughout all the tests.
6.0 Cooling tests:
6.1 General conditions:
6.1.1
The standard rating test shall be conducted with all indoor units and compressors functioning, at
test conditions as specified in Table 1. The test methods and uncertainty of measurement shall be
as specified in Clause 8.0 and all tests shall be carried out in accordance with the test requirements
of Annex B and the test methods of Annex D and Annex E. The electrical input values used for
rating purposes shall be measured during the cooling capacity test.
6.1.2
Tests may be conducted to determine the cooling capacities of individual indoor units, operating
with or without all other indoor units functioning. If tests for individual indoor unit capacity are
conducted, the capacities shall be determined in accordance with the requirements of Annex G.
6.1.3
The specific setting of compressor and controller to deliver full load capacity shall be provided by
the manufacturer and the equipment shall be maintained at that setting. If the manufacturer does
not define the setting, the thermostat or controller shall be set to its minimum allowable
temperature setting.
6.1.4
If the equipment under test cannot be maintained at steady-state conditions by its normal
controls, then the manufacturer shall modify or override such controls so that steady-state
conditions are achieved
6.1.5
Temperature conditions:
The temperature conditions are as specified in Table 2.
6.1.6
Pre-conditions:
Equilibrium condition as specified in clause 8.3.1 has to be achieved for at least 60 minutes
between the test room reconditioning apparatus and equipment under test.
6.1.7
Testing requirements:
Total, sensible and latent cooling capacity and rated power consumption shall be determined
6.1.8
Duration of test:
The output shall be measured in the steady state condition as specified in clause 8.3.1. The
recording of the data shall continue for at least a 30 min period during which the tolerances
specified in clause 8.2.1 shall be met and 6 sets of reading at every 10 minutes interval shall be
recorded. Data shall be sampled at equal intervals that span 30 s or less
6.1.9
Calculation for cooling capacity:
The calculation for cooling capacity shall be done as defined in Annex D if testing done using
Calorimeter method and as defined in Annex E if the testing is done using air enthalpy method.
6.1.10 Standard rating cooling capacity test
Table 2 – Cooling capacity rating conditions
Parameter
Temperature of air entering indoor side
 Dry Bulb Temperature
 Wet Bulb Temperature
Temperature of air entering outdoor side
 Dry Bulb Temperature
Standard rating condition
Test frequency
Test voltage
Compressor speed *
Rated frequency
Rated voltage
Rated speed for full capacity (or)
Controller setting for full capacity #
Rated air flow
27˚ C
19˚ C
39.0˚ C
Indoor side air flow **
* Refer to clause 5.1.1
** Refer to clause 5.4 to 5.8
# For compressors with variable refrigerant flow other than variable speed type
6.2 Maximum operating test:
6.2.1
Pre-conditions:
The test shall be conducted with equipment run at full capacity condition. The temperature and electrical
input shall be maintained at conditions as in Table 3.
6.2.2
Testing requirements:
The test voltage to the equipment shall be maintained as specified percentage of rated supply under
running condition in the Table 3. During the restart of equipment after shutdown as required by the test,
the test voltage shall be adjusted so that it is not less than 86 % of the rated voltage at the moment of
restarting the equipment after the shut-down required after the test duration as specified in Table 3. The
determination of cooling capacity and electrical power input is not required for this performance test.
Table 3 – Maximum operating Test conditions
Parameter
Temperature of air entering indoor side
 Dry Bulb Temperature
 Wet Bulb Temperature
Temperature of air entering outdoor side
 Dry Bulb Temperature
Standard rating condition
32˚ C
23˚ C
46.0˚ C
Test frequency
Test voltage – Condition 1
Test voltage – Condition 2
Compressor speed *
Rated frequency
110% Rated voltage
90% Rated voltage
Full load speed (or)
Controller setting for full capacity delivery #
Indoor side air flow **
Full load air flow as specified by manufacturer
Test duration for test voltage condition 1 and 60 minutes continuous run after temperature
test voltage condition 2 each
conditions achieved. And then power cut – off to
equipment for 3 minutes. Restart unit and run for 60
minutes continuously
* Refer to clause 5.1.1
** Refer to clause 5.4 to 5.8
# For compressors with variable refrigerant flow other than variable speed type
6.2.3
Performance requirement:
The equipment shall meet the following performance requirements.
a. During the entire test duration there shall be no indication of damage
b. The motors and compressors shall run continuously without any safety device operation or
tripping of any safety protection device during the first 60 minutes of test
c. After the power cut-off 3 minutes and restart, the equipment shall resume operation within 30
minutes and then run continuously for 60 minutes.
d. The safety protection devices may trip only during first 5 minutes operation after power cut-off
for 3 minutes and restart. Then equipment shall run continuously for 60 minutes without tripping
of any safety protective device. For equipment designed not to start operation after initial trip
within the first 5 minutes, the equipment shall resume operation within 30 minutes and then shall
run continuously for 60 minutes.
Steady state
condition
5 mins
60 minutes running at condition
3 min
1) 90% rated supply voltage
2) 110% rated supply voltage
30 minutes
60 minutes after operation restart
POWER ON
60 minutes
POWER OFF
Test Start
Power
cut off
Power
cut in
End of test
If Protection device
operated, maximum period
for unit to restart operation
End of test if EUT restart
after protection device
operated
6.3 Freeze-up air blockage test:
6.3.1
Pre-conditions:
The test conditions as specified in Table 4 shall be maintained. All indoor units shall be functioning during
this test. The equipment shall be started and operated until operating test conditions as specified in table
4 have stabilized.
6.3.2 Air flow conditions:
The controls, fan speeds, dampers and grilles of the equipment shall be set to produce the maximum
tendency to frost or ice the evaporator, providing such settings are not contrary to the manufacturer's
operating instructions.
6.3.3
Testing requirements:
Tests temperatures shall be as specified in Table 4. If lower minimum operating temperature conditions
are specified in the manufacturer's specification sheets, they shall be used in lieu of those given in Table
4. The measurement of cooling capacity and electrical parameters is not required for this test.
6.3.4 Test duration:
After the operating test conditions have stabilized as specified in table 4, the equipment shall be operated
for a period of 4 h. The equipment shall be permitted to stop and start under the control of an automatic
limit device, if provided.
Table 4 – Freeze up air blockage test and Freeze up drip test
Parameter
Temperature of air entering indoor side
 Dry Bulb Temperature
 Wet Bulb Temperature
Temperature of air entering outdoor side
 Dry Bulb Temperature
Test frequency
Test voltage
Test condition
21.0˚ C
15.0˚ C
21.0˚ C
Rated frequency
Rated voltage
6.3.5
Performance requirement:
6.3.5.1 The equipment shall operate under the conditions specified without any indication of damage.
6.3.5.2 At the end of 4 h test, any accumulation of frost or ice on the indoor coil shall not cover more
than 50 % of the indoor-side face area of the indoor coil or reduce the airflow rate by more than
25 % of the initial airflow rate. If the equipment and test apparatus do not allow visual observation
of the indoor coil or if the indoor air volume rate is not measured, then the requirements of 6.3.5.3
shall be met.
6.3.5.3 During the 4 h test period, the midpoint temperature of every indoor coil circuit or the refrigerant
suction pressure shall be measured at equal intervals that span 1 min or less. The measurement(s)
made 10 min after beginning the 4 h test shall be defined as the initial value(s). If the suction
pressure is measured, it shall be used to calculate the saturated suction temperature.
a) If the compressor(s) does(do) not cycle off on automatic controls during the test and
 if coil circuit temperatures are measured, the temperatures shall not remain more than 2 °C below
the corresponding initial value for each circuit for more than 20 consecutive min, or
 If suction pressure is measured, the saturated suction temperature shall not remain more than 2
°C below the initial value for more than 20 consecutive min.
b) If the compressor(s) cycle(s) on and off on the automatic controls during the test and
 if coil circuit temperatures are measured, the individual circuit temperatures measured 10 min
after the beginning of any on cycle during the test shall not be more than 2 °C below the
corresponding initial circuit temperature(s), or
 If suction pressure is measured, the saturated suction temperature measured 10 min after the
beginning of any “on” cycle during the test shall not be more than 2 °C below the initial saturated
suction temperature.
6.4 Freeze-up drip test
6.4.1
General conditions
This test is applicable for non-ducted split units only. The freeze-up drip test shall be followed by
completion of the freeze-up air blockage test. The test conditions shall be as specified in Table 4. The
equipment shall be operating at functioning of full-load except for the airflow setting. The measurement
of capacity and electrical power is not required for this performance test.
6.4.2
Temperature conditions
The temperature and test conditions shall be as specified in table 4.
6.4.3
Airflow conditions
The air entry to indoor heat exchanger shall be blocked completely, so as to attempt to achieve complete
blockage of air by frosting or ice on indoor heat exchanger.
6.4.4
Test conditions:
6.4.4.1 Pre-conditions:
The equipment shall be started and operated till the test conditions as specified in table 4 are stabilized.
6.4.4.2 Test duration:
After the test conditions are stabilized, the equipment shall be operated for 4 hours continuously. The
start and stop operation of the equipment is permitted by an automatic limit device, if provided. Stop the
equipment at the end of the 4 hours of test, allow the frost or ice to be melted by removing the air inlet
covering. Then, turn on the equipment with fans operating at high speed for 5 minutes.
6.4.4.3 Performance requirement:
During the test, the equipment shall not blow off any water or ice on the indoor side. Also there shall be
no water or ice dripping in to indoor side from the coil.
6.5 Condensate disposal test and enclosure sweat test:
6.5.1
General conditions:
This test is applicable for non-ducted split units only. The test conditions shall be as specified in Table 5.
The equipment shall be operating with all indoor units on and functioning at full-load except for the
airflow setting. The measurement of capacity and electrical power is not required for this performance
test.
6.5.2
Temperature conditions:
The temperature and test conditions shall be as specified in table 5.
6.5.3
Airflow condition:
The controls, fans, dampers and grilles of the equipment shall be set to produce the maximum tendency
to sweat, provided such settings are not contrary to the manufacturer's operating instructions.
6.5.4
6.5.4.1
Test conditions:
Preconditions:
After establishing the specified temperatures, equipment shall be started with the condensate collection
pan filled to the overflowing point and shall be run until the condensate flow has become uniform.
6.5.4.2
Test duration:
After the test conditions are stabilized, the equipment shall be operated for 4 hours continuously.
6.5.4.3
Performance requirement:
During the test, the equipment shall not blow off any condensate water on the indoor side. Also there
shall be no water or ice dripping in to indoor side from the coil and equipment shall not shutdown.
Table 5 – Condensate disposal test
Parameter
Temperature of air entering indoor side
 Dry Bulb Temperature
 Wet Bulb Temperature
Temperature of air entering indoor side
 Dry Bulb Temperature
Test condition
Test frequency
Test voltage
Rated frequency
Rated voltage
27.0˚ C
24.0˚ C
27.0˚ C
7.0 Heating tests
7.1 Heating capacity tests
7.1.1
General conditions:
7.1.1.1 The standard rating test shall be conducted with all indoor units and compressors functioning, at
test conditions as specified in Table 6. The test methods and uncertainty of measurement shall be
as specified in Clause 8.0 and all tests shall be carried out in accordance with the test requirements
of Annex B and the test methods of Annex D and Annex E. The electrical input values used for
rating purposes shall be measured during the heating capacity test.
7.1.1.2 The test methods and uncertainty of measurement shall be as specified in Clause 8.3 and all tests
shall be carried out in accordance with the test requirements of Annex B and the test methods of
Annex D and Annex E. The electrical input values used for rating purposes shall be measured
during the heating capacity test.
7.1.1.3 Resistive elements used for heating indoor air other than those used for defrosting shall be
prevented from operating during the heating capacity tests.
7.1.1.4 Tests may be conducted to determine the heating capacities of individual indoor units, operating
with or without all other indoor units functioning. If tests for individual indoor unit capacity are
conducted, the capacities shall be determined in accordance with the requirements of Annex G.
7.1.1.5 If the manufacturer does not specify otherwise, the thermostat or controller shall be set at its
maximum allowable temperature setting.
7.1.2
Temperature conditions
The temperature conditions are as specified in Table 6
7.1.2.1 Pre-conditions:
Equilibrium condition as specified in clause 8.3.1 has to be achieved for at least 60 minutes between the
test room reconditioning apparatus and equipment under test.
7.1.2.2 Testing requirements:
Total heating capacity and rated power consumption shall be determined
7.1.2.3 Duration of test:
The output shall be measured in the steady state condition as specified in clause 8.3.1. The recording of
the data shall continue for at least a 60 min period during which the tolerances specified in clause 8.2 shall
be met and 6 sets of readings at every 10 minutes interval shall be recorded. Data shall be sampled at
equal intervals that span 30 s or less
7.1.2.4 Calculation for heating capacity:
Annexure D defines the heating capacity calculation for testing done using Calorimetric method and
Annexure E defines the calculation for testing done using air enthalpy method.
Table: 6: Heating capacity Rating condition
Parameter
Temperature of air entering indoor side
 Dry Bulb Temperature
 Wet Bulb Temperature
Temperature of air entering outdoor side
 Dry Bulb Temperature
 Wet Bulb Temperature
Test frequency
Test voltage
Compressor speed *
Standard rating condition
20˚ C
15˚ C
7˚ C
6˚ C
Rated frequency
Rated voltage
Rated speed for full capacity (or)
Controller setting for full capacity #
Rated air flow
Indoor side air flow **
* Refer to clause 5.1.1
** Refer to clause 5.4 to 5.8
# For compressors with variable refrigerant flow other than variable speed type
7.1.3
Air flow conditions
7.1.3.1 For ducted indoor units, measurement of the indoor-side air volume rate is required in all cases,
regardless of whether the calorimeter test method or the indoor air enthalpy test method is used
to provide the primary measurement of heating capacity.
7.1.3.2 Airflow measurements shall be done as specified in specified in Annex A for ducted units and
Annex C for other units, as appropriate, as well as the provisions established in the other annexes.
7.1.3.3 The air flow setting for both indoor and outdoor shall be same as that established during the
cooling capacity tests. The heating capacity tests shall be conducted at the outdoor-side airflow
rate that is inherent in the outdoor-side air circuit, with the exception of any adjustments allowed
if using the outdoor air-enthalpy test method (see Annex K).
7.1.3.4 For ducted indoor units, heating capacity tests shall be conducted with the same setting of the
damper or exhaust fan as set for the cooling capacity test
7.1.4
Defrost operation
7.1.4.1 Automatic defrost controls shall not be disabled or overridden. Only if manual defrosting has to
be initiated during preconditioning, then the automatic controls can be overridden.
7.1.4.2 Any defrost cycle, whether automatically or manually initiated, that occurs while preparing for
or conducting a heating capacity test, shall always be automatically terminated by the action of
the heat pump's defrost controls.
7.1.4.3 If the heat pump turns the indoor fan off during the defrost cycle, airflow through the indoor coil
shall stop.
7.1.5
Test procedure — General
7.1.5.1 The test procedure consists of three periods: a preconditioning period, an equilibrium period and
a data collection period. The duration of the data collection period differs depending on whether
the heat pump's operation is steady-state or transient. In addition, in the case of transient
operation, the data collection period specified when using the indoor air enthalpy method (see
7.1.11.5) is different from the data collection period required if using the calorimeter method
(see 7.1.11.6).
7.1.5.2 The pictorial representation of possible different sequences while conducting a heating capacity
test sequences is described in Annex R.
7.1.6
Preconditioning period
7.1.6.1 The test room reconditioning apparatus and the heat pump under test shall be operated until the
test tolerances specified in 8.3 are attained for at least 10 min.
7.1.6.2 A defrost cycle may end a preconditioning period. If a defrost cycle does end a preconditioning
period, the heat pump shall operate in the heating mode for at least 10 min after defrost
termination prior to beginning the equilibrium period.
7.1.7
Equilibrium period
7.1.7.1 The equilibrium period immediately follows the preconditioning period.
7.1.7.2 A complete equilibrium period is 60 minutes in duration.
7.1.7.3 The test tolerances as specified in table 13 of clause 8.3 shall be applicable except for transient
test.
7.1.8
Data collection period
7.1.8.1 The data collection period immediately follows equilibrium period.
7.1.8.2 The data collection period shall be based on the test procedure selected.
7.1.8.3 An integrating electrical power (watt-hour) meter or measuring system shall be used for
measuring the electrical energy supplied to the equipment. During defrost cycles and for the first
10 min following a defrost termination, the meter or measuring system shall have a sampling rate
of at least every 10 s.
7.1.8.4 Except as specified in 7.1.8.3 and 7.1.8.5, data shall be sampled at equal intervals that span 30 s
or less
7.1.8.5 During defrost cycles, plus the first 10 min following defrost termination, certain data used in
evaluating the integrated heating capacity of the heat pump shall be sampled at equal intervals
that span 10 s or less. When using the indoor air enthalpy method, these more frequently sampled
data include the change in indoor-side dry-bulb temperature. When using the calorimeter
method, these more frequently sampled data include all measurements required to determine
the indoor-side capacity.
7.1.8.6 For heat pumps that automatically cycle off the indoor fan during a defrost, the contribution of
the net heating delivered and/or the change in indoor-side dry-bulb temperature shall be assigned
the value of zero when the indoor fan is off, if using the indoor air enthalpy method. If using the
calorimeter test method, the integration of capacity shall continue while the indoor fan is off.
7.1.8.7 For both the indoor air-enthalpy and calorimeter test methods, the difference between the drybulb temperature of the air leaving and entering the indoor coil shall be measured. For each 5
min interval during the data collection period, an average temperature difference shall be
calculated, ∆𝑡𝑖(𝜏) ). The average temperature difference for the first 5 min of the data collection
period, ∆𝑡𝑖(𝜏=0) , shall be saved for the purpose of calculating the change, ∆𝑡, expressed as a
percentage, as given in Equation (1):
∆𝑡𝑖(𝜏=0) − ∆𝑡𝑖(𝜏)
%∆𝑡 = [
∆𝑡𝑖(𝜏=0)
] × 100
Equation (1)
7.1.9 Test procedure when a defrost cycle (whether automatically or manually initiated) ends the
preconditioning period (7.1.6)
7.1.9.1 If the quantity %∆𝑡 exceeds 2.5 % during the first 35 min of the data collection period, the heating
capacity test shall be designated as a transient test (see 7.1.11). Likewise, if the heat pump
initiates a defrost cycle during the equilibrium period or during the first 35 min of the data
collection period, the heating capacity test shall be designated as a transient test.
7.1.9.2 If the conditions specified in 7.1.9.1 do not occur and the test tolerances given in 8.3 are satisfied
during both the equilibrium period and the first 35 min of the data collection period, then the
heat capacity test shall be designated a steady-state test. Steady-state tests shall be terminated
after 35 min of data collection.
7.1.10 Test procedure when a defrost cycle does not end the preconditioning period (7.1.6)
7.1.10.1 If the heat pump initiates a defrost cycle during the equilibrium period or during the first 35 min
of the data collection period, the heating capacity test shall be restarted as specified in 7.1.10.3.
7.1.10.2 If the quantity %∆𝑡 exceeds 2.5 % any time during the first 35 min of the data collection period,
the heating capacity test shall be restarted as specified in 7.1.10.3. Prior to the restart, a defrost
cycle shall occur. This defrost cycle may be manually initiated or delayed until the heat pump
initiates an automatic defrost.
7.1.10.3 If either 7.1.10.1 or 7.1.10.2 apply, then the restart shall begin 10 min after the defrost cycle
terminates with a new, 1-hour-long equilibrium period. This second attempt shall follow the
requirements of 7.1.7 and 7.1.8, and the test procedure of 7.1.9.
7.1.10.4 If the conditions specified in 7.1.10.1 or 7.1.10.2 do not occur and the test tolerances given in
8.3 are satisfied during both the equilibrium period and the first 35 min of the data collection
period, then the heat capacity test shall be designated as a steady-state test. Steady-state tests
shall be terminated after 35 min of data collection.
7.1.11 Test procedure for transient tests
7.1.11.1 When, in accordance with 7.1.9.1, a heating capacity test is designated as a transient test, the
adjustments specified in 7.1.11.2 to 7.1.11.5 shall apply.
7.1.11.2 The outdoor air-enthalpy test method shall not be used and its associated outdoor-side
measurement apparatus shall be disconnected from the heat pump. In all cases, the normal
outdoor-side airflow of the heat pump shall not be disturbed. The use of other confirming test
methods is not required.
7.1.11.3 To constitute a valid transient heating capacity test, the test tolerances specified in Table 8 shall
be achieved during both the equilibrium period and the data collection period. As noted in Table
8, the test tolerances are specified for two subintervals. Interval H consists of data collected
during each heating interval, with the exception of the first 10 min after defrost termination.
Interval D consists of data collected during each defrost cycle plus the first 10 min of the
subsequent heating interval.
7.1.11.4 The test tolerance parameters in Table 7 shall be sampled throughout the equilibrium and data
collection periods. All data collected during each interval, H or D, shall be used to evaluate
compliance with the Table 8 test tolerances. Data from two or more H intervals or two or more
D intervals shall not be combined and then used in evaluating Table 6 compliance. Compliance
is based on evaluating data from each interval separately.
7.1.11.5 If using the indoor air enthalpy method, the data collection period shall be extended until 3 h
have elapsed or until the heat pump completes three complete cycles during the period,
whichever occurs first. If, at an elapsed time of 3 h, the heat pump is conducting a defrost cycle,
the cycle shall be completed before terminating the collection of data. A complete cycle consists
of a heating period and a defrost period, from defrost termination to defrost termination.
7.1.11.6 If using the calorimeter method, the data collection period shall be extended until 6 h have
elapsed or until the heat pump completes six complete cycles during the period, whichever
occurs first. If, at an elapsed time of 6 h, the heat pump is conducting a defrost cycle, the cycle
shall be completed before terminating the collection of data. A complete cycle consists of a
heating period and a defrost period, from defrost termination to defrost termination.
Note: Consecutive cycles are repetitive with similar frost and defrost intervals before selecting data
used for calculating the integrated capacity and power.
7.1.11.7 Because of the confirming test method requirement of 8.1.3.1, the outdoor air enthalpy test
apparatus may have to be disconnected from the heat pump, as specified in 7.1.11.2, during a
heating capacity test. If removal during a test is required, the changeover interval shall not be
counted as part of the elapsed time of the equilibrium or data collection periods. The
changeover interval shall be defined as starting the instant the heating capacity test is
designated a transient test and ending when the test tolerances from Table 7 are first reestablished after the outdoor air-enthalpy apparatus is disconnected from the heat pump.
Table 7: Variations allowed in heating capacity tests when using the Transient test procedure
Reading
Variation of arithmetical mean Variation of individual readings
values from specified test from specified test conditions
conditions
Interval H*
Interval D**
Interval H*
Interval D**
Temperature of air
entering indoor-side:
dry-bulb
±0.6 °C
±1.5 °C
±1.0 °C
±2.5 °C
wet-bulb
—
—
—
—
Temperature of air
entering outdoorside:
dry-bulb
±0.6 °C
±1.5 °C
±1.0 °C
±5,0 °C
wet-bulb
±0.3 °C
±1.0 °C
±0.6 °C
—
Voltage
—
—
±2 %
±2 %
External resistance to
—
—
±5 Pa
—
airflow
* Applies when the heat pump is in the heating mode, except for the first 10 min after
termination of a defrost cycle.
** Applies during a defrost cycle and during the first 10 min after the termination of a defrost
cycle when the heat pump is operating in the heating mode.
7.1.12 Heating capacity test results
7.1.12.1 The electrical energy supplied to the heat pump during the applicable test period specified in
7.1.8 shall be measured along with the corresponding elapsed time, in hours, of the test period.
7.1.12.2 Average heating capacity and average electrical power input shall be calculated in accordance
with 9.1.4 and 9.1.5 using data from the total number of complete cycles that are achieved
before data collection is terminated. In the event that the equipment does not undergo a
defrost cycle during the data collection period, the entire 6 hours data set shall be used for the
calculations.
7.2 Maximum heating performance test
7.2.1
General conditions
The conditions given in Table 8 shall be used during the maximum heating performance test. The
determination of heating capacity is not required for this performance test. The test voltages in Table 9
shall be maintained at the specified percentages under running conditions. All indoor units and
compressors shall be functioning during this test.
7.2.2
Temperature conditions
The temperature conditions given in Table 8 shall be used during these tests, unless the manufacturer
specifies higher temperature conditions in the manufacturer's equipment specification sheets.
7.2.3
Airflow conditions
The maximum heating test shall be conducted using the indoor-side fan speed setting determined in 5.2.
7.2.4
Test conditions
7.2.4.1 Preconditions
The controls of the equipment shall be set for maximum heating.
7.2.4.2 Duration of test
The equipment shall be operated for 60 minutes after the specified air temperatures have been attained.
The equipment shall be permitted to stop and start under the control of an automatic limit device, if
provided.
Table 8: Maximum heating operating condition test
Parameter
Temperature of air entering indoor-side:
dry-bulb
Temperature of air entering outdoor-side:
dry-bulb
wet-bulb
Test conditions
27 °C
24 °C
18 °C
Test frequency
Test voltage – Condition 1
Test voltage – Condition 2
Compressor speed *
Rated frequency
110% Rated voltage
90% Rated voltage
Full load speed (or) Controller setting for full
capacity delivery
Indoor side air flow **
Full load air flow as specified by manufacturer
Test duration for test voltage condition 1 and 60 minutes continuous run after temperature
test voltage condition 2 each
conditions achieved. And then power cut – off to
equipment for 3 minutes. Restart unit and run for
60 minutes continuously
* Refer to clause 5.1.1
** Refer to clause 5.4 to 5.8
7.2.4.3 The equipment shall operate under the conditions specified in Table 8 and 7.2.4.2, without
indication of damage.
7.2.4.4 For equipment designed so that resumption of operation does not occur after initial trip within
the first 5 min, the equipment may remain out of operation for not longer than 3 min. It shall then
operate continuously for 60 minutes.
7.3 Minimum heating performance test
7.3.1
General conditions
The conditions given in Table 9 shall be used for this test. The test shall be conducted with the equipment
functioning at full-load operation, as defined in 3.31. The voltage shall be maintained at the specified
value under running conditions. All indoor units and compressors shall be functioning during this test. The
determination of the heating capacity and electrical power input is not required for this performance test.
7.3.2 Temperature conditions
The temperature conditions shall be as given in Table 9, unless the manufacturer specifies lower
conditions in the manufacturer's equipment specification sheets.
7.3.3 Airflow conditions
The controls of the equipment shall be set for maximum heating. All ventilating air dampers and exhaust
air dampers, if provided, shall be closed.
Table 9: Minimum heating operating condition
Parameter
Temperature of air entering indoor-side:
dry-bulb
Temperature of air entering outdoor-side*:
dry-bulb
wet-bulb
Test frequency
Test voltage
7.3.4
Test conditions
20 °C
1 °C
Rated frequency
Rated voltage
Test conditions
7.3.4.1 Preconditions
The equipment shall be operated for a sufficient period of time to reach stable operating conditions as
specified in Table 10.
7.3.4.2 Duration of test
After the equipment has reached stable operating conditions (Tables 10 and 13), these conditions shall
be maintained for 60 minutes.
7.3.4.3 Performance requirements
The equipment shall operate throughout the test without activation of any manual reset device. The
equipment shall be permitted to stop and start under the control of an automatic limit device, if provided.
The equipment shall operate under the conditions specified in Table 10 and 7.3.4.2, without indication
of damage.
7.4 Automatic defrost test
7.4.1
General conditions
This test is not required if provision is made to ensure that cool air (less than 18 °C) is not blown into the
conditioned space during defrost. The test shall be conducted with the equipment functioning at full
capacity, as defined in 3.31, except as required in 7.4.3. The determination of heating capacity and
electrical power input is not required for this performance test.
7.4.2
Temperature conditions
The temperature conditions specified as below in table 10 shall be used during the automatic defrost
test.
Table 10: Automatic defrost test condition
Parameter
Temperature of air entering indoor side
 Dry Bulb Temperature
 Wet Bulb Temperature
Temperature of air entering outdoor side
 Dry Bulb Temperature
 Wet Bulb Temperature
Test frequency
Test voltage
Compressor speed *
Test condition
20˚ C
15˚ C
2˚ C
1˚ C
Rated frequency
Rated voltage
Rated speed for full capacity (or)
Controller setting for full capacity #
Rated air flow
Indoor side air flow **
* Refer to clause 5.1.1
** Refer to clause 5.4 to 5.8
# For compressors with variable refrigerant flow other than variable speed type
7.4.3
Airflow conditions
Unless prohibited by the manufacturer, the indoor-side fan is to be adjusted to the highest speed and
the unit outdoor-side fan to the lowest speed, if separately adjustable.
7.4.4 Test conditions
7.4.4.1 Preconditions
The equipment shall be operated until the temperatures specified conditions in Table 10 have been
stabilized.
7.4.4.2 Duration of test
The heat pump shall remain in operation for two complete defrosting periods or for 3 h, whichever is
longer.
7.4.5 Performance requirements
During the defrosting period, the temperature of the air from the indoor-side of the equipment shall not
be lower than 18 °C for longer than 1 min.
8.0 Test methods and uncertainties of measurement
8.1 Test methods
8.1.1
General
The standard capacity rating tests shall be conducted as per the testing requirements specified in Annex
B using either the calorimeter test method (see Annex D) or the indoor air-enthalpy test method (see
Annex E) subject to the provision that the test results are within the limits of uncertainties of
measurements established in Clause No.8.2
8.1.2
Calorimeter test method
8.1.2.1 In calorimeter test method, two simultaneous methods for determining capacities shall be used.
While one method determines the capacity on the indoor side, the other measures the capacity
on the outdoor side. For the test data to be valid, the capacity determined using the outdoor-side
data shall agree within 5 % of the value obtained using the indoor-side data for the test.
8.1.2.2 Steady-state shall considered to be achieved and the measurements shall be considered valid only
if the measured capacity at each 10 minutes time interval does not vary by more than 2 % from
the average measured capacity of the entire test period.
8.1.2.3 The airflow measurement apparatus for setting the indoor-side airflow and static pressure
measurements shall be located within the indoor-side compartment of the calorimeter for all
tests, except where specifications in A.3 are used for setting the airflow. In this case, the airflow
measuring apparatus may be removed after the damper has been set to obtain the required
airflow and static pressure.
8.1.3
Indoor air enthalpy method
8.1.3.1 A confirming test may be conducted to verify the results obtained using the indoor air-enthalpy
test method. The following test methods may be used for confirming purposes:

Compressor calibration method (see Annex H);

Refrigerant enthalpy method (see Annex J);

Outdoor air-enthalpy test method (see Annex K);

Indoor calorimeter confirmative test method (see Annex L);

Outdoor calorimeter confirmative test method (see Annex M);

Balanced-type calorimeter confirmative test method (see Annex N).
Note: Annex N is not used as a confirmative test by testing laboratories (see N.1.1).
8.1.3.2 The results of the primary test shall agree with the results of the confirmative test within 6 % to
be valid.
8.2 Uncertainty of measurement
8.2.1
The uncertainty of measurement values shall be as specified in Table 11.
8.2.2
The steady-state cooling and heating capacities determined using the calorimeter method shall
be determined with a maximum uncertainty of 5 %. This value is an expanded uncertainty of
measurement expressed at the level of confidence of 95 %.
8.2.3
Heating capacity determined during transient operation (defrost cycles) using the calorimeter
method shall be determined with a maximum uncertainty of 10 %. This value is an expanded
uncertainty of measurement expressed at the level of confidence of 95 %.
8.2.4
The heating and cooling capacities measured on the air side using the air enthalpy method shall
be determined with a maximum uncertainty of 10 %. This value is an expanded uncertainty of
measurement expressed at the level of confidence of 95 %.
Table 11 — Uncertainties of measurement
Measured quantity
Uncertainty of measurement*
Air:
Dry-bulb temperature
Wet-bulb temperature **
Volume flow
Static pressure difference
0.2 °C
0.3 °C
5%
5 Pa for pressure ≤ 100 Pa
Electrical inputs
0.5 %
Time
0.2 %
Mass
1.0 %
Speed
1.0 %
Note: Uncertainty of measurement comprises, in general, many components. Some of these
components may be estimated on the basis of the statistical distribution of the results of a series of
measurements and can be characterized by experimental standard deviations. Estimates of other
components can be based on experience or other information.
* Uncertainty of measurement is an estimate characterizing the range of values within which the true
value of the measurement lies, based on a 95 % confidence interval (see ISO/IEC Guide 98-3).
** Can be measured directly or indirectly.
8.3 Test tolerances for the capacity tests
8.3.1
The maximum permissible variation of any individual observation from a specific test condition
during a steady-state capacity test is listed in Table 12. If a test condition is not specified, the
values in column 3 of Table 12 represent the greatest permissible difference between maximum
and minimum instrument observations during the test. When expressed as a percentage, the
maximum allowable variation is the specified percentage of the arithmetical average of the
observations.
8.3.2
The maximum permissible variations of the average of the test observations from this Standard
or specified test conditions are shown in Table 12.
8.3.3
Under defrost conditions, the normal functioning of the test room reconditioning apparatus may
be disturbed. Because of this, the maximum allowable deviation of air temperature readings shall
be three times those specified in Table 12.
Table 12 — Variations allowed during steady-state cooling and heating capacity tests
Reading
Variations of arithmetical mean Maximum
variation
of
values from specified test individual readings from
conditions
specified test conditions*
Temperature of air entering indoor-side:
dry-bulb
wet-bulb *
± 0.3 °C
± 0.2 °C *
± 0.5 °C
± 0.3 °C *
Temperature of air entering outdoor-side:
dry-bulb
wet-bulb **
±0.3 °C
±0.2 °C
±0.5 °C
±0.3 °C
Voltage
±1%
±2%
Air volume flow rate ***
±5%
± 10 %
* Not applicable for heating tests.
** Applicable for Heating capacity test only
*** Only applies to the indoor air enthalpy method. The test condition is defined as the measured arithmetical
mean of airflow taken within the first 5 min of the data collection period.
8.4 Test tolerances for performance tests
The maximum allowable variation of any individual observation made during a performance test from the
specified test condition is established in Table 13.
Table 13 — Test tolerances for performance tests
Readings
Maximum variation of individual readings
from specified test conditions*
Air temperatures:
dry-bulb
± 1.0 °C
wet-bulb
± 0.5 °C
Voltage
±2%
* The test tolerances do not apply when the equipment is stopped, changing compressor
speed or from defrost initiation to 10 min after defrost termination. Except during these
intervals, dry-bulb temperature tolerances of ± 2.5 °C on the indoor side and ± 5 °C on the
outdoor side shall apply.
9.0 Test results
9.1 Capacity calculations
9.1.1
General
The results of a capacity test shall express quantitatively the effects produced upon air by the equipment
being tested. For given test conditions, the capacity test results shall include the following quantities as
are applicable to cooling or heating:
a. Total cooling capacity, in kW;
b. Sensible cooling capacity, in kW;
c. Latent cooling capacity, in kW;
d. Heating capacity, in kW;
e. Indoor-side airflow rate, in m3/s of standard air;
f.
External static pressure / External resistance to indoor airflow, in Pa;
g. Effective power input to the equipment or individual power inputs to each of the electrical equipment
components, in kW.
Note: For determination of latent cooling capacity, see Annex D if using the calorimeter test method and
Annex E if using the indoor air enthalpy test method
9.1.2
Adjustments
Test results shall be used to determine capacities without adjustment for permissible variations in test
conditions. Air enthalpies, specific volumes and isobaric specific heat capacities shall be based on the
measured barometric pressure.
9.1.3
Cooling capacity calculations
9.1.3.1 An average cooling capacity shall be determined from the set of cooling capacities recorded over
a data collection period of at least 60 min.
9.1.3.2 An average electrical power input shall be determined from the set of electrical power inputs
recorded over the data collection period or from the integrated electrical power for the same
interval in cases where an electrical energy meter is used.
9.1.3.3 Standard ratings of capacities shall include the effects of circulating-fan heat, but shall not
include supplementary heat.
9.1.4
Heating capacity calculations
9.1.4.1
Steady-state capacity calculations
9.1.4.1.1
If the heating capacity test is conducted in accordance with the provisions of 7.1.9.2 or
7.1.10.4, the heating capacity shall be calculated using data from each data sampling in
accordance with Annex D, if using the calorimeter test method, or in accordance with Annex
E, if using the indoor air-enthalpy test method.
9.1.4.1.2
An average heating capacity shall be determined from the set of heating capacities recorded
over the data collection period.
9.1.4.1.3
An average electrical power input shall be determined from the set of electrical power inputs
recorded over the data collection or from the integrated electrical power for the same data
collection period.
9.1.4.2 Transient capacity tests
9.1.4.2.1
If the heating capacity test is conducted in accordance with the provisions of 7.1.11, an
average heating capacity shall be determined. This average heating capacity shall be
calculated as specified in Annex D if using the calorimeter test method and as specified in
Annex E if using the indoor air-enthalpy test method.
9.1.4.2.2
For equipment where one or more complete cycles occur during the data collection period,
the following shall apply.
The average heating capacity shall be determined using the integrated capacity and the
elapsed time corresponding to the total number of complete cycles that occurred over the
data collection period. The average electrical power input shall be determined using the
integrated power input and the elapsed time corresponding to the total number of complete
cycles during the same data collection period as the one used for the heating capacity.
NOTE: A complete cycle consists of a heating period and defrost period from defrost termination to
defrost termination.
9.1.4.2.3
For equipment that does not conduct a complete cycle during the data collection period, the
following shall apply.
The average heating capacity shall be determined using the integrated capacity and the
elapsed time corresponding to the total data collection period (3 h if using the indoor airenthalpy test method; 6 h if using the calorimeter test method).The average electrical power
input shall be determined using the integrated power input and the elapsed time
corresponding to the same data collection period as the one used for the heating capacity.
9.1.4.2.4
For equipment in which a single defrost occurs during the test period, the following shall
apply.
The average heating capacity shall be determined using the integrated capacity and the
elapsed time corresponding to the total test period (3 h if using the indoor air-enthalpy test
method; 6 h if using the calorimeter test method). The average electrical power input shall be
determined using the integrated power input and the elapsed time corresponding to the total
test period.
9.1.5
Power input of fans
The fan power measured during the test shall be included in the declared power consumption and in the
calculation of efficiencies. Standard ratings of capacities shall include the effects of circulating-fan heat,
but shall not include supplementary heat.
9.2 Data to be recorded
The data to be recorded for the capacity tests are given in Table 14 for the indoor air enthalpy test method
and Tables 16 and 17 for the room calorimeter test method. The tables identify the general information
required but are not intended to limit the data to be obtained. Electrical input values used for rating
purposes shall be those measured during the capacity tests.
Table 14 — Data to be recorded for the indoor air-enthalpy capacity tests
No.
1
2
3
4
5
6
7
8
9
Data
Date
Observers
Barometric pressure, in kPa
Fan speed setting indoor and outdoor
Applied voltage, in V
Frequency, in Hz
Total current input to equipment, in A
Total power input to equipment*, in kW
Setting of variable capacity compressor at full load, control dry-bulb and wet-bulb temperature of
air (indoor-side calorimeter compartment), in ˚C
10
Control dry-bulb and wet-bulb temperature of air (outdoor-side calorimeter compartment)**, in
˚C
11
Average air temperature outside the calorimeter if calibrated (see Figure D.1), in ˚C
12
Total power input to indoor-side and outdoor-side compartments, in Watts
13
Quantity of water evaporated in humidifier, in kilograms
14
Temperature of humidifier water entering indoor-side and outdoor-side (if used) compartments
or in humidifier tank, in ˚C
15
Cooling water flow rate through outdoor-side compartment heat-rejection coil, in liters per second
16
Temperature of cooling water entering outdoor-side compartment, for heat-rejection coil, in ˚C
17
Temperature of cooling water leaving outdoor-side compartment, from heat-rejection coil, in ˚C
18
Temperature of condensed water leaving outdoor-side compartment, in ˚C
19
Mass of condensed water from equipment, in kilograms
20
Volume of airflow through measuring nozzle of the separating partition, in cubic meters per
second
21
Air-static pressure difference across the separating partition of calorimeter compartments, in Pa.
22
Refrigerant charge added by the test house, in kilograms
* Total power input to the equipment, except if more than one external power connection is provided
on the equipment; record input to each connection separately.
** See D.1.5.
Table 15 — Data to be recorded for calorimeter cooling capacity tests
No.
1
2
3
4
5
6
7
8
9
10
11
12
13
14
15
Data
Date
Observers
Barometric pressure, in kPa
Fan speed setting indoor and outdoor
Applied voltage, in V
Frequency, in Hz
Total current input to equipment, in A
Total power input to equipment*, in kW
Setting of variable capacity compressor at full load
Control dry-bulb and wet-bulb temperature of air (indoor-side calorimeter compartment), in ̊C
Control dry-bulb and wet-bulb temperature of air (outdoor-side calorimeter compartment)**, in ̊C
Average air temperature outside the calorimeter if calibrated (see Figure D.1), in ̊C
Total power input to indoor-side and outdoor-side compartments, in Watts
Quantity of water evaporated in humidifier, in kilograms
Temperature of humidifier water entering indoor-side and outdoor-side (if used) compartments or
in humidifier tank, in ̊C
16
Cooling water flow rate through outdoor-side compartment heat-rejection coil, in liters per second
17
Temperature of cooling water entering outdoor-side compartment, for heat-rejection coil, in ̊C
18
Temperature of cooling water leaving outdoor-side compartment, from heat-rejection coil, in
degrees Celsius
19
Mass of condensed water from equipment, in kilograms
20
Temperature of condensed water leaving outdoor-side compartment, in ̊C
21
Volume of airflow through measuring nozzle of the separating partition, in cubic metres per second
22
Air-static pressure difference across the separating partition of calorimeter compartments, in Pa
23
Refrigerant charge added by the test house, in kilograms
* Total power input to the equipment, except if more than one external power connection is provided on
the equipment; record input to each connection separately.
** See D.1.5
Table 16 – Data to be recorded for calorimetric heating capacity tests
No.
1
2
3
4
5
6
7
8
9
10
11
12
13
14
15
Data
Date
Observers
Barometric pressure, in kPa
Fan speed setting indoor and outdoor
Applied voltage, in V
Frequency, in Hz
Total current input to equipment, in A
Total power input to equipment*, in Watts
Setting of variable capacity compressor at full load
Control dry-bulb and wet-bulb temperature of air (indoor-side calorimeter compartment)**, in ̊C
Control dry-bulb and wet-bulb temperature of air (outdoor-side calorimeter compartment)**, in ̊C
Average air temperature outside the calorimeter if calibrated (see Figure D.1), in ̊C
Total power input to indoor-side and outdoor-side compartments, in watts
Quantity of water evaporated in humidifier, in kilograms
Temperature of humidifier water entering indoor-side and outdoor-side (if used) compartments or
in humidifier tank, in ̊C
16
Cooling water flow rate through outdoor-side compartment heat-rejection coil, in liters per second
17
Temperature of cooling water entering outdoor-side compartment, for heat-rejection coil, in ̊C
18
Temperature of cooling water leaving outdoor-side compartment, from heat-rejection coil, in
degrees Celsius
19
Mass of condensed water from equipment, in kg
20
Temperature of condensed water leaving outdoor-side compartment, in ̊C
21
Volume of airflow through measuring nozzle of the separating partition, in cubic meters per second
22
Air-static pressure difference across the separating partition of calorimeter compartments, in
pascals
23
Refrigerant charge added by the test house, in kg.
* Total power input to the equipment, except if more than one external power connection is provided
on the equipment; record input to each connection separately.
** See D.1.5
9.3 Test report
9.3.1
General information
As a minimum, the test report shall contain the following general information:
a)
b)
c)
d)
e)
f)
g)
h)
9.3.2
a reference to this Standard,
the date;
The test lab name;
The test location;
The test method(s) used (calorimeter or air-enthalpy);
The test supervisor;
A description of the test set-up, including equipment location;
The nameplate information (see 10.2).
Rating test results
The values reported shall be the mean of the values taken over the data collection period, and
shall be stated with an uncertainty of measurement at a confidence level of 95 % and in
accordance with ISO/IEC Guide 98-3.
9.3.3
Performance tests
All relevant information regarding testing shall be reported.
10.0
Marking provisions
10.1
Nameplate requirements
Each individual unit of the air-conditioner and heat pump system shall have a durable nameplate
firmly attached to it and in a location accessible for reading.
10.2
Nameplate information
The nameplate shall provide the following minimum information in addition to the information required
by applicable safety standards:
a) the manufacturer's name or trademark;
b) Manufacturing location Address
c) any distinctive type or model designation and serial number;
d) the rated voltage;
e) the rated frequency;
f)
Rated capacity (Cooling / Heating)
g) Maximum current
h) Refrigerant charge quantity (check with other standards)
i)
The refrigerant designation in accordance with ISO 817.
10.3
Additional information
In addition to the nameplate information in 10.2, the factory refrigerant mass charge shall be provided on
the outdoor unit.
11.0
Publication of ratings
11.1
Standard ratings
11.1.1 Standard ratings shall be published for cooling capacities (sensible, latent and total), heating
capacity, EER and COP, as appropriate, for all systems produced in conformance with this
Standard. These ratings shall be based on data obtained at the established rating conditions in
accordance with the provisions of this Standard.
11.1.2 The values of standard capacities shall be expressed in kilowatts, rounded to two decimals.
11.1.3 The values of EER and COP shall be expressed in multiples, rounded to two decimals.
Note: The rating conditions and the operating limits other than those prescribed above shall be mutually agreed
upon between the manufacturer and buyer.
11.2
Other ratings
Additional ratings may be published based on conditions other than those specified as standard rating
conditions, or based on the testing of various combinations of operating evaporators and/or compressors,
if they are clearly specified and if the data are determined by the methods specified in this Standard, or
by analytical methods which are verifiable by the test methods specified in this standard.
12.0
Symbols:
Annex A
Airflow settings for ducted units
A.1 General
Either of the following two methods of airflow settings are deployed for measurement:
1. fixed duct resistance method;
2. Adjusted exhaust fan setting method.
Both methods with their respective test apparatus are described in this annex.
For measuring the static pressure of the air delivery of a ducted equipment, the measuring duct is
connected to the duct flange of the equipment. This measuring duct is used in either methods. The
equivalent diameter of the measurement duct shall be calculated as defined in equation A.1, where ‘a’
and ‘b’ are the dimensions of the outlet duct section:
𝑑𝑒 = √
(4𝑎.𝑏)
(Equation: A.1)
𝜋
b
a
Air delivery outlet flange
de
Measurement duct
If the outlet of ducted equipment is circular in section with diameter d, then the equivalent diameter de
is equal to d.
d = de
Air delivery outlet flange = measurement duct
The length of the measuring duct (Ld) shall be minimum 2.5 times de. The tapping for measurement of
static pressure should be located at the distance Lm = 2de from the outlet flange.
A.2 Test method
A.2.1 The Fixed duct resistance method air flow setting for the unit shall be as shown in Figure A.1 and for
adjusted exhaust fan setting is as shown in Figure A.2.
A.2.2 The static pressure measurement taps shall be arranged as shown in Figure A.1 and Figure A.2. The
equipment under test shall be operated without the compressor being ON.
A.2.3 Airflow measurements should be made as per the provisions specified in Annex C, as appropriate,
as well as other provisions established in this Standard.
Note: Additional guidance concerning airflow measurements can be found in ISO 3966 and ISO 5167-1.
A.3 Fixed duct resistance method
A.3.1 General
A measuring duct shall be connected to the test equipment and a damper installed on the opposite end
of the measuring duct, to which a discharge chamber is connected. The discharge chamber shall have
sufficient cross-sectional dimensions so that airflow velocities along the wall surface at the static pressure
tap (Figure A.1, item 4) is less than or equal to 1.25 m/s. The minimum length of the discharge chamber
in the flow direction ‘J’ shall be 2 times of equivalent diameter de.
Note: The test set-up is as illustrated in Figure A.1.
A.3.2 Test procedure
A.3.2.1 Test conditions
The temperature and humidity conditions of the test room shall be within the range specified in 5.7. The
equipment under test shall be operated in the fan only mode without the compressor being ON. The
damper shall be adjusted so that the rated airflow rate in standard air conditions is obtained. At the same
time, the airflow rate of the airflow measuring apparatus shall be adjusted such that static pressure in the
discharge chamber is (0 ± 2) Pa. The above conditions shall be maintained for at least 60 minutes.
A.3.2.2 Blowing test
The dry-bulb and wet-bulb temperatures of the inlet air, airflow rate, ESP, pe, dry-bulb and wet-bulb
temperatures in front of the nozzle, and barometric pressure shall be measured. The measured airflow
rate, qm, shall be converted into the standard flow rate, qs.
A.3.2.3 Evaluation
The ESP, pe, shall be that specified in 5.7.
A.3.2.4 Cooling and heating tests
The damper's position shall remain fixed at the setting obtained in A.3.2.1 for all cooling and heating tests,
which shall be conducted at the respective temperature and humidity conditions. During the cooling and
heating tests, the static pressure of the discharge chamber shall be maintained at (0 ± 2) Pa.
The ESP, pe, of the measuring duct at the cooling and heating tests is for reference only, and therefore
does not need to be published. The airflow rate measured when the equipment is operating in the cooling
or heating mode is used for calculation of cooling and heating capacities.
123456-
Air flow measuring apparatus
Exhaust fan
Manometers
Static pressure taps of Discharge chamber
Equipment under test
Damper
7JLd Lm pe -
Discharge chamber
Minimum length of discharge chamber
Minimum length of measuring duct
Distance of static pressure taps
External Static pressure of equipment
Figure A.1 – Fixed duct resistance method setup
A.4 Adjusted exhaust fan setting method
A measuring duct shall be connected to the equipment under test and an airflow measuring apparatus
connected to the opposite end of the measuring duct.
Note: The set-up of the equipment under test unit, measuring duct and airflow measuring apparatus is
illustrated in Figure A.2
A.4.1 Test procedure
The temperature and humidity conditions of the test room shall be within the range specified in 5.7. The
equipment under test shall be operated in the fan only mode without the compressor being ON. The
airflow measuring apparatus shall be adjusted so that the rated airflow rate in standard air is obtained.
The above conditions shall be maintained for at least 60 minutes.
A.4.2 Blowing test
The dry-bulb and wet-bulb temperatures of the inlet air, airflow rate, External Static Pressure, pe, dry-bulb
and wet-bulb temperatures in front of the nozzle, and barometric pressure shall be measured. The
measured airflow rate, qm, shall be calculated according to Equation (C.6). The measured airflow rate, qm,
shall be converted into the standard flow rate, qs.
A.4.3 Calculation of the value of C
The value of C shall be calculated from Equation (A.2).
𝐶=
𝑝𝑚
2
𝑞𝑚
Equation (A.2)
Where
pm - static pressure of the measuring duct, KPa, and pm is considered to be equal to the external static
pressure pe.
A.4.4 Evaluation
The External Static Pressure, pe, shall be as specified by 5.7.
A.4.5 Cooling and heating tests
Cooling and heating tests shall be performed following the blowing test, at their respective temperature
and humidity conditions. The speed of the exhaust fan of the airflow measuring apparatus shall be
adjusted for the cooling and heating tests as below.
For the cooling test, operate the equipment with the compressor in the cooling mode and allow the
temperature to stabilize. Once the temperature is stabilized adjust the airflow measuring apparatus to
achieve the same value of ‘C’ by changing its exhaust fan speed in small increments. The resulting value
of ‘C’ shall be in the range of ±1 % of that measured during the blowing test. Once stabilized, the cooling
airflow rate and ESP shall be measured.
For the heating test, repeat the cooling test above, this time with the compressor operating in the heating
mode. Measure the heating airflow rate and ESP.
The airflow rate measured when the equipment is operating in the cooling or heating mode shall be used
to calculate the cooling and heating capacities.
The ESP of the measuring duct during the cooling and heating tests is for reference only, and therefore
does not need to be published.
1
2
3
4
5
Air flow measuring apparatus
Exhaust fan
Manometers
Equipment under test
Nozzles
Ld
Lm
Pm
Pe
Length of measuring duct
Distance of static pressure taps
External static pressure of equipment under test
Static pressure of the measuring duct
Figure A.2 – Adjusted exhaust fan setting method setup
Annex B
Test room requirements
B.1 General Requirements of test room
B.1.1 The indoor condition test room shall be a room or space in which the desired test conditions can be
maintained within the prescribed tolerances. It is recommended that air velocities in the vicinity of the
equipment under test do not exceed 2.5 m/s.
B.1.2 The outdoor condition test room or space shall be of sufficient volume and shall circulate air in such
a manner that it does not change the normal air circulating pattern of the equipment under test. It shall
be of such dimensions that the distance from any room surface to any equipment surface from which air
is discharged is not less than 1.8 m and the distance from any other room surface to any other equipment
surface is not less than 1.0 m, except for floor or wall relationships required for normal equipment
installation. The room conditioning apparatus should handle air at a rate not less than the outdoor airflow
rate, and should preferably take this air from the direction of the equipment air discharge and return it at
the desired conditions uniformly and at low velocities.
B.1.3 For the calorimeter room with a facility having more than two rooms, the additional rooms shall also
comply with the requirements of Annex D.
B.1.4 For the air enthalpy method test facility having more than two rooms, the additional rooms shall
also comply with the requirements of Annex E.
B.2 Equipment installation
B.2.1 The equipment to be tested shall be installed in accordance with the manufacturer's installation
instructions using recommended installation procedures and accessories. If the equipment can be
installed in multiple positions, then all tests shall be conducted in a position specified in the
manufacturer's installation instructions. If the equipment can be installed in multiple positions as per
installation manual of manufacturer, then all tests shall be conducted using the worst configuration. In all
cases, the manufacturer's recommendations with respect to distances from adjacent walls, amount of
extensions through walls, etc. shall be followed.
B.2.2 No other alterations to the equipment shall be made except for the attachment of the required test
apparatus and instruments in the prescribed manner.
B.2.3 Ducted equipment rated at less than 8 kW and intended to operate at external static pressures of
less than 25 Pa shall be tested at free delivery of air.
B.2.4 If necessary, the equipment shall be evacuated and charged with the type and amount of refrigerant
specified in the manufacturer's instructions.
B.2.5 All standard ratings for equipment shall be determined by manufacturer's specifications within pipe
lengths as per 5.1, of connecting tubing on each line. The lengths shall be actual lengths, not equivalent
lengths, and no account shall be taken of the resistance provided by bends, branches, connecting boxes
or other fittings used in the installation for the test piece. The length of the connecting tubing shall be
measured from the enclosure of the indoor unit to the enclosure of the outdoor unit. Such equipment in
which the interconnecting tubing is furnished as an integral part of the unit and not recommended for
cutting to length shall be tested with the complete length of tubing furnished. Not less than 40 % of the
total length of the interconnecting tubing shall be exposed to the outdoor conditions with the rest of the
tubing exposed to the indoor conditions. The line diameters, insulation, details of installation, evacuation
and charging shall be in accordance with the manufacturer's published recommendations.
B.3 Static pressure measurements across indoor coil
B.3.1 Equipment with a fan and a single outlet
B.3.1.1 A short plenum shall be attached to the outlet of the equipment. This plenum shall have crosssectional dimensions equal to the dimensions of the equipment outlets. A static pressure tap shall be
added at the center of each side of the discharge plenum, if rectangular, or at four evenly distributed
locations along the circumference of an oval or round plenum. These four static pressure taps shall be
manifolded together. The minimum length of the discharge plenum and the location of the static pressure
taps relative to the equipment outlets for testing a split-system shall be as shown in Figure B.1, and for a
single-package unit as shown in Figure B.2.
B.3.1.2 A short plenum should be attached to the inlet of the equipment. The cross section of the plenum
shall have the same cross-sectional dimensions as the equipment inlet. In addition, four static pressure
taps shall be added and manifolded together. This plenum should otherwise be constructed as shown for
the inlet plenum in Figure B.2, if testing a single-package unit, and as shown in Figure B.3, if testing a splitsystem.
B3.2.1 Equipment with multiple outlets or multiple indoor units
B.3.2.1 Equipment with multiple outlet duct connections or multiple indoor units shall have a short
plenum attached to each outlet connection or indoor unit, respectively. Each of these short plenums shall
be constructed as described in B.3.1.1, including static pressure taps. All outlet plenums shall discharge
into a single common duct section. For the purpose of equalizing the static pressure in each plenum, an
adjustable restrictor shall be located in the plane where each outlet plenum enters the common duct
section. Multiple blower units employing a single discharge duct connection flange shall be tested with a
single outlet plenum in accordance with B.3.1. Any other test plenum arrangements shall not be used
except to simulate duct designs specifically recommended by the equipment manufacturer.
B.3.2.2 A short plenum should be attached to the inlet of each inlet duct connection or indoor unit. Each
of these short plenums shall be constructed as described in B.3.1.2, including static pressure taps.
a
1
2
3
4
a
A&B
Manometer
Exhaust plenum
Equipment under test
Static Pressure Taps
To air flow measuring apparatus
Dimension of the EUT
Figure B.1 – External Static Pressure Measurement
Figure B.2 – External Static Pressure measurements (continued)
1
2
3
4
Equipment under test – Single package unit
Static Pressure Taps – inlet (4 taps required)
Equipment under test – outlet (4 taps required)
Static Pressure Taps
For circular ducts with diameter ‘d’ substitute
𝜋𝑑 2
4
for (A X B) or (C X D)
Figure B.3 – External Static Pressure measurement
Annex C
Airflow measurement
C.1 Airflow determination
C.1.1 Airflow should be measured using the apparatus and testing procedures given in this annex.
C.1.2 Airflow quantities are determined as mass flow rates. If airflow quantities are to be expressed for
rating purposes in volume flow rates, such ratings should state the conditions (pressure, temperature and
humidity) at which the specific volume is determined.
C.2 Airflow and static pressure
The area of a nozzle, An, should be determined by measuring its diameters to an accuracy of ±0.2 % in
four locations approximately 45° apart around the nozzle in each of two places through the nozzle throat,
one at the outlet and the other in the straight section near the radius.
C.3 Nozzle apparatus
C.3.1 Nozzle apparatus, consisting of a receiving chamber and a discharge chamber separated by a
partition in which one or more nozzles are located (see Figure C.1). Air from the equipment under test is
conveyed via a duct to the receiving chamber, passes through the nozzle(s), and is then exhausted to the
test room or channeled back to the equipment's inlet.
The nozzle apparatus and its connections to the equipment's inlet should be sealed such that air leakage
does not exceed 1.0 % of the airflow rate being measured.
`
a
b
1
2
3
4
5
a
b
Discharge chamber
6 Receiving chamber
Exhaust fan
7 Apparatus for differential pressure measurement (manometer)
Diffusion baffle
8 Adapter duct (measurement duct)
Pitot tube (Optional)
Dn Nozzle throat diameter
Nozzles
Diffusion baffles with uniform perforation with approximately 40% free area
Air flow direction
Figure C.1 – Air flow measuring apparatus
The center-to-center distance between nozzles in use should be not less than 3 times the throat diameter
of the larger nozzle, and the distance from the center of any nozzle to the nearest discharge or receiving
chamber side wall should not be less than 1.5 times its throat diameter.
C.3.2 Diffusers, installed in the receiving chamber (at a distance of at least 1.5 times the largest nozzle
throat diameter) upstream of the partition wall and in the discharge chamber (at a distance of at least 2.5
times the largest nozzle throat diameter) downstream of the exit plane of the largest nozzle.
C.3.3 Exhaust fan, capable of providing the desired static pressure at the equipment's outlet; it should be
installed in one wall of the discharge chamber and means should be provided to vary the capacity of this
fan.
C.3.4 Manometers, for measuring the static pressure drop across the nozzle(s): One end of the
manometer should be connected to a static pressure tap located flush with the inner wall of the receiving
chamber and the other end to a static pressure tap located flush with the inner wall of the discharge
chamber, or, preferably, several taps in each chamber should be connected to several manometers in
parallel or manifolded to a single manometer. Static pressure connections should be located so as not to
be affected by airflow.
Alternatively, the velocity head of the air stream leaving the nozzle(s) may be measured by a Pitot tube as
shown in Figure C.1, but when more than one nozzle is in use, the Pitot tube reading should be determined
for each nozzle.
C.3.5 Means for determining the air density at the nozzle throat
C.3.5.1 The throat velocity of any nozzle in use should be not less than 15 m/s and not more than 35 m/s.
C.3.5.2 Nozzles should be constructed in accordance with Figure C.2, and applied in accordance with the
provisions of C.3.5.3 and C.3.5.4.
C.3.5.3 Nozzle discharge coefficients, Cd, for the construction shown in Figure C.2, which have a throatlength-to-throat-diameter ratio of 0.6, may be determined using Equation (C.1):
𝐶𝑑 = 0.9886 −
7.006
√𝑅𝑒
+
1.346
𝑅𝑒
Equation (C.1)
For Reynolds number Re of 12000 and above.
The Reynolds number is defined as in equation C.2
𝑅𝑒 =
𝑉𝑛 𝐷𝑛
𝜇
where
Vn is the mean airflow velocity at the throat of the nozzle;
Dn is the diameter of the throat of the nozzle;
μ is the kinematic viscosity of air.
The nozzle dimension and construction shall be as in figure C.2
Equation (C.2)
1
2
3
Dn
Axes of ellipse
Throat section
Elliptical approach
Diameter of nozzle throat, mm
Figure C.2 – Air flow measuring nozzle
C.4 Static pressure measurements
C.4.1 The pressure taps should consist of 6.25 mm (± 0.25 mm) diameter nipples soldered to the outer
plenum surfaces and centered over 1 mm diameter holes through the plenum. The edges of these holes
should be free of burrs and other surface irregularities.
C.4.2 The plenum and duct section should be sealed to prevent air leakage, particularly at the connections
to the equipment and the air measuring device, and should be insulated to prevent heat leakage between
the equipment outlet and the temperature measuring instruments.
C.5 Discharge airflow measurements
C.5.1 The outlet or outlets of the equipment under test should be connected to the receiving chamber by
adapter ducting of negligible air resistance, as shown in Figure C1.
C.5.2 To measure the static pressure of the receiving chamber, a manometer should have one side
connected to one or more static pressure connections located flush with the inner wall of the receiving
chamber.
C.6 Indoor-side airflow measurements
C.6.1 The following readings should be taken:
Barometric pressure;
Nozzle dry- bulb and wet-bulb temperatures or dew point temperatures;
Static pressure difference at the nozzle(s) or, optionally, nozzle velocity pressure.
C.6.2 Air mass flow rate, qm, through a single nozzle is determined using Equation (C.3):
𝑞𝑚 = 𝑌 × 𝐶𝑑 × 𝐴𝑛 √
2 𝑃𝑣
𝑉𝑛′
Equation (C.3)
Where Pv is the velocity pressure at the nozzle throat or the static pressure difference across the nozzle.
The expansion factor, Y, is obtained using Equation (C.4):
𝑌 = 0.452 + 0.548 ∝
Equation (C.4)
The pressure ratio, 𝛼, is obtained using Equation (C.5):
∝= 1 −
𝑃𝑣
𝑃𝑛
Equation (C.5)
Air volume flow rate through a single nozzle is determined using Equation (C.6):
𝑞𝑣 = 𝐶𝑑 × 𝐴𝑛 × √2𝑃𝑣 𝑉𝑛′
Equation (C.6)
Where 𝑉𝑛′ is calculated using equation (C.7):
𝑉𝑛′ =
𝑣𝑛
1+𝑊𝑛
Equation (C.7)
Where 𝑊𝑛 is the specific humidity at nozzle inlet.
C.6.3 Airflow through multiple nozzles may be calculated in accordance with C.6.2, except that the total
flow rate is then the sum of the 𝑞𝑚 or 𝑞𝑣 values for each nozzle used.
C.7 Ventilation, exhaust and leakage airflow measurements — Calorimeter test method
C.7.1 Ventilation, exhaust and leakage airflows should be measured using apparatus similar to that
illustrated in Figure C.3 with the refrigeration system in operation and after condensate equilibrium has
been achieved.
C.7.2 With the equalizing device adjusted for a maximum static pressure differential between the indoorside and outdoor-side compartments to 1 Pa, the following readings should be taken:
a) Barometric pressure;
b) Nozzle wet- and dry-bulb temperatures;
c) Nozzle velocity pressure.
C.7.3 Airflow values should be calculated as defined in C.6.2.
1
2
3
4
5
6
Dn
Pc
Pv
Apparatus for differential pressure measurement (manometer)
Discharge chamber
Exhaust fan
Damper
Nozzle
Pick-up tube
Nozzle throat diameter
Compartment equalization pressure
Nozzle velocity pressure
Figure C.3 – Pressure equalizing device
Annex D
Calorimeter test method
General
D.1.1 The calorimeter provides a method for determining capacity simultaneously on both the indoor side
and the outdoor side. In the cooling mode, the indoor-side capacity determination should be made by
balancing the cooling and dehumidifying effects with measured heat and water inputs. The outdoor-side
capacity provides a confirmative test of the cooling and dehumidifying effect by balancing the heat and
water rejection on the condenser side with a measured amount of cooling.
D.1.2 The two calorimeter compartments, indoor side and outdoor side, are separated by an insulated
partition having an opening into which the non-ducted, single-packaged equipment is mounted. The
equipment should be installed in a manner similar to a normal installation. No effort should be made to
seal the internal construction of the equipment to prevent air leakage from the condenser side to the
evaporator side or vice versa. No connections or alterations should be made to the equipment which
might in any way alter its normal operation.
D.1.3 A pressure-equalizing device as illustrated in Figure C.3 should be provided in the partition wall
between the indoor-side and the outdoor-side compartments to maintain a balanced pressure between
these compartments and to permit measurement of leakage, exhaust and ventilation air. This device
consists of one or more nozzles of the type shown in Figure C.2, a discharge chamber equipped with an
exhaust fan, and manometers for measuring compartment and airflow pressures.
Since the airflow from one compartment to the other may be in either direction, two such devices
mounted in opposite directions or a reversible device should be used. The manometer pressure pick-up
tubes should be so located as to be unaffected by air discharged from the equipment or by the exhaust
from the pressure-equalizing device. The fan or blower, which exhausts air from the discharge chamber,
should permit variation of its airflow by any suitable means, such as a variable speed drive, or a damper
as shown in Figure C.3. The exhaust from this fan or blower should be such that it does not affect the inlet
air to the equipment.
The pressure equalizing device should be adjusted during calorimeter tests or airflow measurements so
that the static pressure difference between the indoor-side and outdoor-side compartments is not greater
than 1.25 Pa.
D.1.4 The size of the calorimeter should be sufficient to avoid any restriction to the intake or discharge
openings of the equipment. Perforated plates or other suitable grilles should be provided at the discharge
opening of the reconditioning equipment to avoid face velocities exceeding 0.5 m/s. Sufficient space
should be allowed in front of any inlet or discharge grilles of the equipment to avoid interference with the
airflow. Minimum distance from the equipment to the side walls or ceiling of the compartment(s) should
be 1 m, except for the back of console-type equipment, which should be in normal relation to the wall.
Ceiling-mounted equipment should be installed at a minimum distance of 1.8 m from the floor. Table D.1
gives the suggested dimensions for the calorimeter. To accommodate peculiar sizes of equipment, it may
be necessary to alter the suggested dimensions to comply with the space requirements.
Table D.1 – Sizes of Calorimeter
Rated cooling capacity
of equipment
In Watts *
Suggested minimum inside dimensions of
each room of calorimeter
in meter
Width
Height
Length
3000
2.4
2.1
1.8
6000
2.4
2.1
2.4
9000
2.7
2.4
3.0
12000 **
3.0
2.4
3.7
* All figures are round numbers.
** Larger capacity equipment will require larger calorimeters.
D.1.5 Each compartment should be provided with reconditioning equipment to maintain specified airflow
and prescribed conditions. Reconditioning apparatus for the indoor-side compartment should consist of
heaters to supply sensible heat and a humidifier to supply moisture. Reconditioning apparatus for the
outdoor-side compartment should provide cooling, dehumidification and humidification. The energy
supply should be controlled and measured.
D.1.6 When calorimeters are used for heat pumps, they should have heating, humidifying and cooling
capabilities for both rooms (see Figures D.1 and D.2). Other means, such as rotating the equipment, may
be used as long as the rating conditions are maintained.
D.1.7 Reconditioning apparatus for both compartments should be provided with fans of sufficient capacity
to ensure airflows of not less than twice the quantity of air discharged by the equipment under test in the
calorimeter. The calorimeter should be equipped with means of measuring or determining specified wetand dry-bulb temperatures in both calorimeter compartments.
D.1.8 It is recognized that in both the indoor-side and outdoor-side compartments, temperature gradients
and airflow patterns result from the interaction of the reconditioning apparatus and test equipment.
Therefore, the resultant conditions are peculiar to, and dependent upon, a given combination of
compartment size, arrangement and size of reconditioning apparatus, and the air discharge characteristics
of the equipment under test.
The point of measurement of specified test temperatures, both wet- and dry-bulb, should be such that
the following conditions are fulfilled.
The measured temperatures should be representative of the temperature surrounding the equipment,
and should simulate the conditions encountered in an actual application for both indoor and outdoor
sides, as indicated above.
At the point of measurement, the temperature of air should not be affected by air discharged from any
piece of the equipment. This makes it mandatory that the temperatures be measured upstream of any
recirculation produced by the equipment.
Air sampling tubes should be positioned on the intake side of the equipment under test.
D.1.9 During the heating capacity test, the temperature of the air leaving the indoor-side of the heat pump
shall be monitored to determine if its heating performance is being affected by a build-up of ice on the
outdoor-side heat exchanger. A single temperature measuring device, placed at the center of the indoorair outlet, will be sufficient to indicate any change in the indoor-air discharge temperature caused by a
build-up of ice on the outdoor-side heat exchanger.
D.1.10 Interior surfaces of the calorimeter compartments should be of non-porous material with all joints
sealed against air and moisture leakage. The access door should be tightly sealed against air and moisture
leakage by use of gaskets or other suitable means.
D.1.11 If defrost controls on the heat pump provide for stopping the indoor airflow, provision shall be
made to stop the test apparatus airflow to the equipment on both the indoor and outdoor sides during
such a defrost period. If it is desirable to maintain operation of the reconditioning apparatus during the
defrost period, provision may be made to bypass the conditioned air around the equipment as long as
assurance is provided that the conditioned air does not aid in the defrosting. A watt-hour meter shall be
used to obtain the integrated electrical input to the equipment under test.
6
7
8
6
3
5
7
2
1
8
12
9
11
9
3
10
10
4
1
2
3
4
5
11
Outdoor side compartment
Indoor side compartment
Equipment under test – Indoor unit
Air sampling tube
Pressure equalization device
Connecting refrigerant pipe
4
6
7
8
9
10
12
Cooling coil
Heating coil
Humidifier
Fan
Mixer
Equipment under test – Outdoor unit
Figure D.1 – Typical calibrated room-type calorimeter
1
7
1
6
7
4
8
8
2
9
3
9
10
4
10
11
5
5
1
2
3
4
5
6
Controlled temperature air space
Outdoor side compartment
Indoor side compartment
Equipment under test – Indoor unit
Air sampling tube
Pressure equalization device
11
12
12
7
8
9
10
11
12
Cooling coil
Heating coil
Humidifier
Fan
Mixer
Equipment under test – Outdoor unit
Figure D.2 – Typical balanced ambient room-type calorimeter
Calibrated room-type calorimeter
D.2.1 Heat leakage may be determined in either the indoor-side or outdoor-side compartment by the
following method. All openings should be closed. Either compartment may be heated by electric heaters
to a temperature of at least 11 °C above the surrounding ambient temperature. The ambient temperature
should be maintained constant within ±1 °C outside all six enveloping surfaces of the compartment,
including the separating partition. If the construction of the partition is identical to that of the other walls,
the heat leakage through the partition may be determined on a proportional area basis.
D.2.2 For calibrating the heat leakage through the separating partition alone, the following procedure
may be used. A test is carried out as described above. Then the temperature of the adjoining area on the
other side of the separating partition is raised to equal the temperature in the heated compartment, thus
eliminating heat leakage through the partition, while the 11 °C differential is maintained between the
heated compartment and the ambient surrounding the other five enveloping surfaces.
The difference in heat input between the first test and second test determines the leakage through the
partition alone.
D.2.3 For the outdoor-side compartment equipped with means for cooling, an alternative means of
calibration may be used to cool the compartment to a temperature at least 11 °C below the ambient
temperature (on six sides) and carry out a similar analysis.
D.2.4 In addition to the two-room simultaneous method of determining capacities, the performance of
the indoor room-side compartment shall be verified at least every six months using an industry standard
cooling capacity calibrating device. A calibrating device may also be another equipment whose
performance has been measured by the simultaneous indoor and outdoor measurement method at an
accredited national test laboratory as part of an industry-wide cooling capacity verification program.
D.3 Balanced ambient room-type calorimeter
D.3.1 The balanced ambient room-type calorimeter is shown in Figure D.2 and is based on the principle
of maintaining the dry-bulb temperatures surrounding the particular compartment equal to the dry-bulb
temperatures maintained within that compartment. If the ambient wet-bulb temperature is also
maintained equal to that within the compartment, the vapour-proofing provisions of D.1.10 are not
required.
D.3.2 The floor, ceiling and walls of the calorimeter compartments shall be spaced at a sufficient distance
away from the floor, ceiling and walls of the controlled areas in which the compartments are located in
order to provide a uniform air temperature in the intervening space. It is recommended that this distance
be at least 0.3 m. Means shall be provided to circulate the air within the surrounding space to prevent
stratification.
D.3.3 Heat leakage through the separating partition shall be introduced into the heat balance calculation
and may be calibrated in accordance with D.2.2 or may be calculated.
D.3.4 It is recommended that the floor, ceiling and walls of the calorimeter compartments be insulated so
as to limit heat leakage (including radiation) to no more than 10 % of the test equipment's capacity, for
an 11 °C temperature difference, or 300 W for the same temperature difference, whichever is greater, as
tested using the procedure given in D.3.2.
Calculations for cooling capacities
D.4.1 The energy flow quantities used to calculate the total cooling capacity based on indoor-side and
outdoor-side measurements are shown below in Figure D.3.
∅𝑙𝑝
∅𝑙𝑖
∑ 𝑃𝑖𝑐
∅𝑡𝑐𝑖
∅𝑙𝑜
3
∅𝑐
1
2
∑ 𝑃𝑜𝑐
(ℎ𝑤1 − ℎ𝑤2 )𝑊𝑟
𝑃𝑡
(ℎ𝑤3 − ℎ𝑤2 )𝑊𝑟
1
Outdoor side compartment
2
Indoor side compartment
3
Equipment under test
Note: Values for the variables identified in the figure are calculated using the equations in D.4.2 to D.4.10.
Figure D.3 — Calorimeter energy flows during cooling capacity tests
D.4.2 The total cooling capacity on the indoor side, as tested in either the calibrated- or balanced-ambient
room-type calorimeter (see Figures D.1 and D.2), is calculated using Equation (D.1):
∅𝑡𝑐𝑖 = ∑ 𝑃𝑖𝑐 + (ℎ𝑤1 − ℎ𝑤2 )𝑊𝑟 +
∅𝑙𝑝 + ∅𝑙𝑖
Equation (D.1)
Note: If no water is introduced during the test, ℎ𝑤1 is taken at the temperature of the water in the
humidifier tank of the conditioning apparatus.
D.4.3 When it is not practical to measure the temperature of the air leaving the indoor-side compartment
to the outdoor-side compartment, the temperature of the condensate may be assumed to be at the
measured or estimated wet-bulb temperature of the air leaving the test equipment.
D.4.4 The water vapour condensed by the equipment under test, 𝑊𝑟 , may be determined by the amount
of water evaporated into the indoor-side compartment by the reconditioning equipment to maintain the
required humidity.
D.4.5 Heat leakage, ∅𝑙𝑝 , into the indoor-side compartment through the separating partition between
the indoor-side and outdoor-side compartments may be determined from the calibrating test or, in the
case of the balanced-ambient room-type compartment, may be based on calculations.
D.4.6 The total cooling capacity on the outdoor side, ∅𝑡𝑐𝑜 , as tested in either the calibrated- or balancedambient room-type calorimeter (see Figures D.1 and D.2), is calculated using Equation (D.2):
∅𝑡𝑐𝑖 = ∅𝑐 − ∑ 𝑃𝑜𝑐 −
𝑃𝑡 + (ℎ𝑤3 − ℎ𝑤2 )𝑊𝑟 + ∅𝑙𝑝 + ∅𝑙𝑜
Equation (D.2)
Note: The hw3 enthalpy is taken at the temperature at which the condensate leaves the outdoor-side
compartment of the reconditioning apparatus.
D.4.7 The heat leakage rate into the indoor-side compartment through the separating partition, ∅𝑙𝑝 ,
between the indoor-side and outdoor-side compartments may be determined from the calibrating test
or, in the case of the balanced-ambient room-type compartment, may be based on calculations.
Note: This quantity will be numerically equal to that used in Equation (D.1) if, and only if, the area of the
separating partition exposed to the outdoor-side is equal to the area exposed to the indoor-side
compartment.
D.4.8
∅𝑑 = 𝐾1 𝑊𝑟
Equation (D.3)
D.4.9 The sensible cooling capacity, ∅𝑠𝑐𝑖 , is calculated using Equation (D.4):
∅𝑠𝑐𝑖 = ∅𝑡𝑐𝑖 − ∅𝑑
Equation (D.4)
D.4.10 Sensible heat ratio (SHR) is calculated using the following:
∅𝑠𝑐𝑖
⁄∅
𝑡𝑐𝑖
D.5 Calculation of heating capacity
D.5.1 The energy flow quantities used to calculate the total heating capacity based on indoor- and
outdoor-side measurements are shown below in Figure D.4.
∅𝑙𝑖
∅𝑙𝑝
∅𝑐𝑖
∅𝑙𝑜
3
1
2
∑ 𝑃𝑜𝑐
∑ 𝑃𝑖𝑐
𝑃𝑡
(ℎ𝑤4 − ℎ𝑤5 )𝑞𝑚,𝑤
1
Outdoor side compartment
2
Indoor side compartment
3
Equipment under test
Note: Values for the variables identified in the figure are calculated using the equations in D.4.2 to D.4.10.
Figure D.4 — Calorimeter energy flows during heating capacity tests
D.5.2 Determination of the indoor-side heating capacity by measurement in the indoor-side compartment
of the calorimeter is calculated using Equation (D.5):
∅ℎ𝑖 = ∅𝑐𝑖 − ∑ 𝑃𝑖𝑐 − ∅𝑙𝑝 − ∅𝑙𝑖
Equation (D.5)
Note: ∑ 𝑃𝑖𝑐 is the other power input to the indoor-side compartment (e.g. illumination, electrical and
thermal power input to the compensating device, heat balance of the humidification device), in watts.
D.5.3 Determination of the heating capacity by measurement of the heat-absorbing side, ∅ℎ𝑜 , is
calculated for equipment where the evaporator takes the heat from an airflow using Equation (D.6):
∅ℎ𝑜 = ∑ 𝑃𝑜𝑐 + 𝑃𝑡 + (ℎ𝑤4 − ℎ𝑤5 )𝑞𝑚,𝑤 − ∅𝑙𝑝 − ∅𝑙𝑜
Where
∑ 𝑃𝑜𝑐 is the total power input to the outdoor-side compartment with the exception of the power input
to the equipment, in watts;
𝑞𝑚,𝑤 is the water mass flow supplied to the outside compartment to maintain the test conditions, in
kilograms per second;
ℎ𝑤5
is the specific enthalpy of, respectively, the condensed water (in the case of test condition, high)
and frost (in the case of test condition, H2 or H3) in the equipment, in joules per kilogram
∅𝑙𝑜
is the heat flow through the remaining enveloping surfaces into the outdoor-side compartment,
in watts.
Annex E
Indoor air enthalpy test method
E.1 General
In the air enthalpy method, capacities are determined from measurements of entering and leaving wetand dry-bulb temperatures and the associated airflow rate.
E.2 Application
E.2.1 Air leaving the equipment under test shall lead directly to the discharge chamber. If a direct
connection cannot be made between the equipment and the discharge chamber, a short plenum shall be
attached to the equipment. In this case, the short plenum shall have the same size as the discharge
opening of the equipment or shall be constructed so as not to prevent the leaving air from expanding. The
cross-section area of the airflow channel through the discharge chamber shall be such that the average
air velocity is less than 1.25 m/s against the airflow rate of the equipment under test. The static pressure
difference between the discharge chamber and intake opening of the equipment under test shall be zero.
An example of the discharge chamber test setup is shown in Figure E.1.
Airflow measurements shall be made in accordance with the provisions specified in Annex C.
E.2.2 When conducting cooling or steady-state heating capacity tests using the indoor air enthalpy test
method, the additional test tolerances given in Table E.1 shall apply.
Table E.1 — Variations allowed during steady-state cooling and heating capacity tests that only apply
when using the indoor air enthalpy method
Reading
Variations of arithmetical Maximum
variation
of
mean values from specified individual readings from
test conditions
specified test conditions
Temperature of air leaving indoor-side:
dry-bulb
—
External resistance to indoor airflow
± 5 Pa
±2.0 °C *
± 5 Pa
* The tolerance represents the greatest permissible difference between the maximum and minimum
observations during the test.
≥ 𝐽
∗∗
𝐽/2
𝐽/2
0 < 𝐾 ≤ 𝐽/2
PL. 1
PL. 2
𝑉2 ≤ 1.25 𝑚/𝑠 𝐶
1
2
1
2
3
a
c
Static pressure tapings
Equipment under test
To air sampler and airflow measuring apparatus
J = 2 De, where De = √4𝐴𝐵/𝜋 and A and B are the dimensions of the equipment’s air outlet
V2 is the average air velocity at PL.2
Figure E.1 — Discharge chamber requirements when using the indoor air enthalpy test method
E.2.3 When conducting transient heating capacity tests using the indoor air enthalpy test method, the
additional test tolerances given in Table E.2 shall apply.
Table E.2 — Variations allowed during the transient heating tests that only apply when using the indoor
air enthalpy test method
Reading
Variations of arithmetical mean Variation of individual readings
values
from
specified
test from specified test conditions
conditions
External resistance to airflow
Interval H *
Interval D **
Interval H *
Interval D **
±5 Pa
—
±5 Pa
—
NOTE For transient heating tests, see 7.1.11.
* Applies when the heat pump is in the heating mode, except for the first 10 min after termination of a
defrost cycle.
** Applies during a defrost cycle and during the first 10 min after the termination of a defrost cycle when
the heat pump is operating in the heating mode.
Calculations for cooling capacities
The total capacity based on the indoor-side test data, ∅𝑐𝑖 , shall be calculated using Equation (E.1):
∅𝑡𝑐𝑖 =
𝑞𝑉,𝑖 (ℎ𝑎1 −ℎ𝑎2 )
𝑉𝑛
=
𝑞𝑉,𝑖 (ℎ𝑎1 − ℎ𝑎2 )
Equation (E.1)
𝑉𝑛′ (1+𝑊𝑛 )
The sensible cooling capacity based on the indoor-side test data, ∅𝑠𝑐𝑖 , shall be calculated using Equation
(E.2):
∅𝑠𝑐𝑖 =
𝑞𝑉,𝑖 (𝑐𝑝𝑎1 𝑡𝑎1 −𝑐𝑝𝑎2 𝑡𝑎2 )
𝑉𝑛
=
𝑞𝑉,𝑖 (𝑐𝑝𝑎1 𝑡𝑎1 −𝑐𝑝𝑎2 𝑡𝑎2 )
𝑉𝑛′ (1+𝑊𝑛 )
Equation (E.2)
The latent cooling capacity based on the indoor-side test data, ∅𝑑 shall be calculated using Equation (E.3)
or (E.4):
∅𝑑 =
𝐾1 𝑞𝑉,𝑖 (𝑊𝑖1 −𝑊𝑖2 )
𝑉𝑛
∅𝑑 = ∅𝑡𝑐𝑖 − ∅𝑠𝑐𝑖
=
𝐾1 𝑞𝑉,𝑖 (𝑊𝑖1 −𝑊𝑖2 )
𝑉𝑛′ (1+𝑊𝑛 )
Equation (E.3)
Equation (E.4)
E.4 Calculations for heating capacities
Total heating capacity based on indoor-side data,∅𝑡ℎ𝑖 , shall be calculated using Equation (E.5):
𝑞𝑡ℎ𝑖 =
𝑞𝑉,𝑖 (𝑐𝑝𝑎2 𝑡𝑎2 −𝑐𝑝𝑎1 𝑡𝑎1 )
𝑉𝑛
=
𝑞𝑉,𝑖 (𝑐𝑝𝑎2 𝑡𝑎2 −𝑐𝑝𝑎1 𝑡𝑎1 )
𝑉𝑛′ ( 1+𝑊𝑛 )
Equation (E.5)
Note: Equations (E.1), (E.2), (E.3) and (E.5) do not take into consideration heat leakage in the test duct
and the discharge chamber.
E.5 Airflow enthalpy measurements
The following test apparatus arrangements are recommended.
E.5.1 Tunnel air enthalpy method
The equipment to be tested is typically located in one as more test rooms. An air measuring device is
attached to the equipment air discharge (indoor, outdoor or both, as applicable). This device discharges
directly into the test room or space, which is provided with suitable means for maintaining the air entering
the equipment at the desired wet- and dry-bulb temperatures (see Figure E.2). Suitable means for
measuring the wet- and dry-bulb temperatures of the air entering and leaving the equipment and the
external resistance shall be provided.
11
1
3
8
9
7
4
5
10
1
2
3
4
5
6
2
6
Outdoor side test room
Outdoor of equipment under test
Indoor side test room
Indoor of equipment under test
Air flow measuring apparatus
Air temperature & humidity measuring instrument
7
8
9
10
11
Mixer
Apparatus for differential pressure measurement
Insulation
Door / window
Room conditioning equipment
Figure E.2 — Tunnel air enthalpy test method arrangement
Figure E 2.1: Arrangement for Cassette type and hi-wall type indoor units
Figure E 2.2: Arrangement for Ducted type indoor units
E.5.2 Loop air enthalpy method
This arrangement differs from the tunnel arrangement in that the air measuring device discharge is
connected to suitable reconditioning equipment which is, in turn, connected to the equipment inlet (see
Figure E.3). The resulting test “loop” shall be sealed so that air leakage at places that would influence
capacity measurements does not exceed 1.0 % of the test airflow rate. The dry-bulb temperature of the
air surrounding the equipment shall be maintained within ±3.0 °C of the desired test inlet dry-bulb
temperature. Wet- and dry-bulb temperatures and external resistance are to be measured by suitable
means.
5
7
3
1
6
a
4
5
a
2
8
1
2
3
4
5
Outdoor side test room
Outdoor of equipment under test
Indoor side of test room
Indoor of equipment under test
Temperature and humidity measuring instrument
6
7
8
a
Air flow measuring apparatus
Apparatus for differential pressure measurement
Reconditioning apparatus
Air flow direction
Figure E.3 — Loop air enthalpy test method arrangement
E.6 Calorimeter air enthalpy method
For equipment in which the compressor is ventilated independently of the indoor air stream, the
calorimeter air enthalpy method arrangement shall be employed to take into account compressor heat
radiation (see Figure E.4). In this arrangement, an enclosure is placed over the equipment, or applicable
part of the equipment, under test. This enclosure may be constructed of any suitable material, but shall
be non-hydroscopic, airtight and preferably insulated. It shall be large enough to permit inlet air to
circulate freely between the equipment and the enclosures and in no case shall the enclosure be closer
than 150 mm to any part of the equipment. The inlet to the enclosure shall be remotely located from the
equipment's inlet so as to cause circulation throughout the entire enclosed space. An air measuring device
is to be connected to the equipment's discharge. This device shall be well insulated where it passes
through the enclosed space. Wet- and dry-bulb temperatures of the air entering the equipment are to be
measured at the enclosure inlet. Temperature and external resistance measurements shall be carried out
by suitable means.
10
4
6
9
5
1
a
4
a
7
8
1
2
3
4
5
6
Outdoor side test room
Outdoor of equipment under test
Air inlet
Air temperature & humidity measuring instrument
Apparatus for differential pressure measurement
Indoor side test
a
2
3
7
8
9
10
A
Indoor of equipment under test
Enclosure
Air flow measuring apparatus
Room conditioning apparatus
Air flow direction
Figure E.4 — Calorimeter air enthalpy test method arrangement
Annex F
Determination of India Seasonal Energy Efficiency Ratio (ISEER)
F1
Purpose
The purpose of this annex is to define a uniform procedure for the calculation of a single value number
that is a representation of the part load efficiency of the variable refrigeration flow system. The single
value number will be called as India Seasonal Energy Efficiency Ratio or ISEER.
F 2 Scope
This annex procedure is only for equipment covered by this standard. The ISEER equation and procedure
are intended to be an average representation of a Variable refrigerant flow system in a typical application
with conventional operating parameters. A fixed set of operating load points and conditions are defined
to allow comparison of products.
The equation has been derived to provide a representation of the average part load efficiency. However,
for operating cost and energy analysis it is best to use a comprehensive analysis tool that reflects the
actual weather data, building load characteristics, operational hours, when calculating the applied
variable refrigerant flow system efficiency.
F 3 Equation
F 3.1 The single value part load rating shall be determined by using the following equation;
𝐼𝑆𝐸𝐸𝑅 = 𝐴 × 𝐸𝐸𝑅100% + 𝐵 × 𝐸𝐸𝑅75% + 𝐶 × 𝐸𝐸𝑅50% + 𝐷 × 𝐸𝐸𝑅25%
where:
𝐸𝐸𝑅100% = EER at full load rating point and operating conditions
𝐸𝐸𝑅75% = EER at 75% load rating point and operating conditions
𝐸𝐸𝑅50% = EER at 50% load rating point and operating conditions
𝐸𝐸𝑅25% = EER at 25% load rating point and operating conditions
A= weighting factor for 100% load
B= weighting factor for 75% load
C= weighting factor for 50% load
D= weighting factor for 100% load
The values of A, B, C, and D are based on the average of the most common building types across climatic
zones of India. Values that have been developed are shown in Table F1.
Table F 1: Weighting coefficients A to D for calculation of ISEER
Load rate (%)
100
75
50
25
Weighting coefficients
A= 4
B= 40
C= 39
D= 17
The ISEER rating requires that the unit efficiency be determined at 100%, 75%, 50% and 25% at the
conditions specified in Table F2.
Table F2: India Seasonal Energy Efficiency Testing Conditions
Parameter
Temperature of air entering indoor side
 Dry Bulb Temperature
 Wet Bulb Temperature
Temperature of air entering outdoor side
 Dry Bulb Temperature – 100% load
 Dry Bulb Temperature – 75% load
 Dry Bulb Temperature – 50% load
 Dry Bulb Temperature – 25% load
Testing condition
Test frequency
Test voltage
Compressor speed *
Rated frequency
Rated voltage
Rated speed for full capacity (or)
Controller setting for full capacity #
Rated air flow
27˚ C
19˚ C
39˚ C
32˚ C
26˚ C
20˚ C
Indoor side air flow **
* Refer to clause 5.1.1
** Refer to clause 5.4 to 5.8
# For compressors with variable refrigerant flow other than variable speed type
F 3.3 Part load test method:
F 3.3.1 General conditions:
The standard rating test shall be conducted with all indoor units and compressors functioning, at test
conditions as specified in Table F2. The test methods and uncertainty of measurement shall be as specified
in Clause 8.0 and all tests shall be carried out in accordance with the test requirements of Annex B and
the test methods of Annex D and Annex E. The electrical input values used for rating purposes shall be
measured during the cooling capacity test.
Tests may be conducted to determine the cooling capacities of individual indoor units, operating with or
without all other indoor units functioning. If tests for individual indoor unit capacity are conducted, the
capacities shall be determined in accordance with the requirements of Annex G.
The specific setting of compressor and controller to deliver full load capacity shall be provided by the
manufacturer and the equipment shall be maintained at that setting. If the manufacturer does not define
the setting, the thermostat or controller shall be set to its minimum allowable temperature setting.
If the equipment under test cannot be maintained at steady-state conditions by its normal controls, then
the manufacturer shall modify or override such controls so that steady-state conditions are achieved
F 3.3.2 Temperature conditions:
The temperature conditions are as specified in Table F2.
F 3.3.3. Pre-conditions:
Equilibrium condition as specified in clause 8.3.1 has to be achieved for at least 60 minutes
between the test room reconditioning apparatus and equipment under test.
F3.3.4. Testing requirements:
Total, sensible and latent cooling capacity and rated power consumption shall be determined
F3.3.5. Duration of test:
The output shall be measured in the steady state condition as specified in clause 8.3.1. The
recording of the data shall continue for at least a 30 min period during which the tolerances
specified in clause 8.2.1 shall be met and 6 sets of reading at every 10 minutes interval shall be
recorded. Data shall be sampled at equal intervals that span 30 s or less
F3.3.6. Calculation for cooling capacity:
The calculation for cooling capacity shall be done as defined in Annex D if testing done using
Calorimeter method and as defined in Annex E if the testing is done using air enthalpy method.
The EER at different load conditions shall be calculated as below from the capacity and power
consumption determined by testing unit at conditions specified in Table F2.
𝐸𝐸𝑅𝑋% =
∅𝑋%
𝑃𝑋%
F4 Approach adopted for ISEER coefficient calculations:
(I)
Weather data is taken from ISHRAE weather file used for energy simulation of buildings.
(II)
Following building types have been analysed through simulation for studying the variable
refrigerant flow system load variation:
a.
b.
c.
d.
e.
f.
g.
h.
Office (Small): 24*7, 12*5
Office (Medium): 24*7, 12*5
Office (Large): 24*7, 12*5
Hotel
Retail
Hospital
Educational: School, University
Residential: Group housing, villa
(III)
Building envelopes, occupancy, LPD, EPD etc. are the taken from recently built buildings
(IV)
Models of all buildings have been simulated for representative cities of various climatic
zones: hot & dry, composite, warm & humid, and moderate.
(V)
Grouping of data as per bin method for computation of ISEER coefficients is done on the
basis of load on variable refrigerant flow system.
(VI)
Bin group is selected in such a way that average of peak bin group should be 75% load
and similarly average of low bin group and min bin group should be 50% and 25% load
respectively.
(VII)
ISEER coefficients for 25%, 50%, 75% and 100% load are first computed separately for
each building type in each representative city. Average of all the cases has led to the final
set of ISEER coefficients.
Annex G
Individual indoor unit capacity tests
G.1 General
The test methods described provide means to determine the capacity of an individual indoor unit, either
operating on its own with the other indoor units switched off, or with all indoor units operating.
All tests shall be made in accordance with the requirements of Annex B.
G.2 The calorimeter method
If measurements are made by the calorimeter method, then the testing of an individual unit, with all
others operating, will require at least a three-room calorimeter test facility. If only one unit is operating,
a two-room calorimeter will suffice. Each calorimeter shall satisfy requirements described in Annex D.
G.3 The air enthalpy method
G.3.1 If measurements are made by the air enthalpy method, then the testing shall be done with one or
more indoor rooms and one or more air measuring devices connected to the indoor units. The outdoor
unit shall be situated at least in an environmental test room.
G.3.2 The test facility shall satisfy the requirements described in Annex E, except that the individual indoor
unit to be tested shall have its own plenum and airflow measuring device.
G.4 Temperature conditions
Temperature conditions shall be as specified in 6.1.2 and 7.1.2.
G.5 Airflow conditions
All air quantities shall be as specified in Clause 5.
G.6 Test conditions
Test conditions shall be as specified in 6.1.3 and from 7.1.4 to 7.1.11.
G.7 Test methods and uncertainty of measurement
Test methods and uncertainty of measurement shall be as specified in Clause 8.
G.8 Test results
Test results shall be recorded and expressed as specified in Clause 9.
G.9 Published ratings
The publication of individual capacities of indoor units shall be as specified in Clause 11. The published
results shall specify if all indoor units are operating or only one indoor unit is operating during the test
Annex H
Compressor calibration test method
H.1 General Description
H.1.1 In the compressor calibration test method, total cooling or heating capacity is determined as
follows.
From measurements of properties of the refrigerant entering and leaving the indoor-side of the
equipment and the associated refrigerant flow rate as determined by subsequent calibration of the
compressor under identical operating conditions. Direct capacity measurements should be used when the
superheat of the refrigerant leaving the evaporator is less than 3.0 °C.
By measuring capacity directly with a calorimeter when the compressor is operating at the identical
conditions encountered during the equipment test.
H.1.2 When the compressor calibration method is employed, the requirements in H.2 and H.3 apply to
both the equipment test and the compressor calibration test.
H.1.3 Cooling and heating capacities obtained by the compressor calibration method should include
thermal effects of the fan.
H.2 Measurement of refrigerant properties
H.2.1 The equipment should be operated at the desired test conditions, and measurements of the
temperature and pressure of the refrigerant entering and leaving the compressor should be recorded at
equal intervals that span 5 min or less. These readings should be obtained during the data collection
period of the cooling or heating capacity test.
H.2.2 On equipment not sensitive to refrigerant charge, pressure gauges may be tapped into the
refrigerant lines.
H.2.3 On equipment sensitive to refrigerant charge, refrigerant pressures should be determined after this
test because the connection of pressure gauges might result in a loss of charge. To accomplish this,
temperatures are measured during the test by means of thermocouples soldered to return bends at the
midpoints of each indoor and outdoor coil circuit or at points not affected by vapour superheat or liquid
sub-cooling. Following the test, gauges are connected to the lines and the equipment is evacuated and
charged with the type and quantity of refrigerant specified on the nameplate. The equipment is then
operated again at test conditions and, if necessary, refrigerant charge is added or removed until the coil
thermocouple measurements are within ±0.3 °C of their original values, the temperatures of the
refrigerant vapour entering and leaving the compressor are within ±2.0 °C of their original values, and the
temperature of the liquid entering the expansion device is reproduced within ±0.6 °C. The opeating
pressures should then be observed.
H.2.4 Refrigerant temperatures should be measured by means of thermocouples soldered to the lines at
appropriate locations.
H.2.5 No thermocouples should be removed, replaced, or otherwise disturbed during any portion of a
complete capacity test.
H.2.6 Temperatures and pressures of the refrigerant vapour entering and leaving the compressor should
be measured in the refrigerant lines approximately 250 mm from the compressor shell. If the reversing
valve is included in the calibration, these data should be taken on the lines to the coils and approximately
250 mm from the valve.
H.3 Compressor calibration
H.3.1 The refrigerant flow rate should then be determined from the calibration of the compressor at the
predetermined compressor, entering and leaving refrigerant pressures and temperatures, by one of the
primary test methods described in the IS 5111 or ISO 917.
H.3.2 Calibration tests should be performed with the compressor and reversing valve (where used) at the
same ambient temperature and air pattern as in the tested equipment.
H.3.3 The refrigerant flow, qr, is calculated using Equation (H.1):
𝑞𝑟 =
∅𝑡𝑐𝑖
⁄ℎ − ℎ
𝑔1
𝑓1
Equation H.1
For the:
a)
b)
c)
d)
Secondary refrigerant calorimeter method;
Flooded system primary refrigerant calorimeter method;
Dry system primary refrigerant calorimeter method;
Concentric tube calorimeter method.
H.3.4 The gaseous refrigerant flow meter method gives refrigerant flow directly.
H.3.5 Total cooling capacity is calculated as prescribed in H.5.1 and H.5.2. Total heating capacity is
calculated as prescribed in H.6.
H.4 Direct heating capacity measurements
H.4.1 For compressor calibration tests, when the evaporator superheat on the heating cycle is less than
3.0 °C, the refrigerant flow rate should be determined using the heat rejection from the calorimeter
condenser. A water-cooled condenser, insulated against heat leakage, is required. The condenser may be
used with any of the calorimeter arrangements in H.3.3.
H.4.2 This method may be used only when the calculated heat leakage from the condenser to the ambient
is less than 2 % of the refrigerating effect of the compressor.
H.4.3 The compressor calibration test should be run as specified in H.3. Additional data required are:
a)
b)
c)
d)
e)
f)
Refrigerant pressure and temperature entering the condenser;
Refrigerant pressure and temperature leaving the condenser;
Water temperatures entering and leaving the condenser;
Ambient temperature surrounding the condenser;
Quantity of condenser cooling water;
Average temperature of the condenser jacket surface exposed to ambient.
H.4.4 The refrigerant flow rate, qr, is calculated using Equation (H.2):
𝑞 𝑐 (𝑡 − 𝑡𝑤2 ) + 𝐴1 (𝑡𝑐 − 𝑡𝑎 )
𝑞𝑟 = [ 𝑒 𝑝𝑤 𝑤1
]
⁄
(ℎ𝑔2 − ℎ𝑓2 )
Equation (H.2)
H.4.5 The total heating capacity, ∅𝑡ℎ𝑖 , is calculated as given in H.6.
H.5 Calculations for cooling capacities
H.5.1 For tests in which the evaporator superheat is 3.0 °C or more, total cooling capacity based on
compressor calibration data is calculated from the refrigerant flow rate using Equation (H.3):
∅𝑡𝑐𝑖 = 𝑞𝑟 (ℎ𝑟2 − ℎ𝑟1 ) − 𝑃𝑡
Equation (H.3)
H.5.2 For tests in which the evaporator superheat is less than 3.0 °C, total cooling capacity is calculated
using Equation (H.4):
∅𝑡𝑐𝑖 = ∅𝑒 + 𝐴1 (𝑡𝑎 − 𝑡𝑐 ) − 𝑃𝐼
Equation (H.4)
H.6 Calculations for heating capacities
The total heating capacity, ∅𝑡ℎ𝑖 , based on compressor calibration data is calculated from the refrigerant
flow rate using Equation (H.5):
∅𝑡ℎ𝑖 = 𝑞𝑟 (ℎ𝑟1 − ℎ𝑟2 ) − 𝑃𝐼
Equation (H.5)
Annex J
Refrigerant enthalpy test method
J.1 General
J.1.1 In this method, capacity is determined from the refrigerant enthalpy change and flow rate. Enthalpy
changes are determined from measurements of entering and leaving pressures and temperatures of the
refrigerant, and the flow rate is determined by a suitable flow meter in the liquid line.
J.1.2 This method may be used for tests of equipment in which the refrigerant charge is not critical and
where normal installation procedures involve the field connection of refrigerant lines.
J.1.3 This method should neither be used for tests in which the refrigerant liquid leaving the flow meter
is sub-cooled less than 2.0 °C nor for tests in which the superheat of the vapour leaving the indoor side is
less than 3.0 °C.
J.2 Refrigerant flow method
J.2.1 The refrigerant flow rate should be measured with an integrating-type flow meter connected in the
liquid line upstream of the refrigerant control device. This meter should be sized such that its pressure
drop does not exceed the vapour pressure change that a 2.0 °C temperature change would produce.
J.2.2 Temperature and pressure measuring instruments and a sight glass should be installed immediately
downstream of the meter to determine if the refrigerant liquid is adequately sub-cooled. Sub-cooling of
2.0 °C and the absence of any vapour bubbles in the liquid leaving the meter are considered adequate. It
is recommended that the meter be installed at the bottom of a vertical downward loop in the liquid line
to take advantage of the static head of the liquid thus provided.
J.2.3 At the end of the test, a sample of the circulating refrigerant and oil mixture may be taken from the
equipment and its percentage of oil, co, calculated using Equation (J.1):
𝑐0 =
𝑚5 −𝑚1
𝑚3 −𝑚1
Equation (J.1)
The total indicated flow rate should be corrected for the amount of oil circulating.
J.3 Refrigerant temperature and pressure measurements
The temperature of the refrigerant entering and leaving the indoor side of the equipment should be
measured with instruments having an accuracy of ±0.1 °C. The pressure of the refrigerant entering and
leaving the indoor side of the equipment should be measured with instruments having an accuracy of ±2.0
% of the indicated value.
J.4 Calculation of cooling capacity
The total cooling capacity, ∅𝑡ℎ𝑖 , based on volatile refrigerant flow data is calculated using Equation (I.2):
∅𝑡𝑐𝑖 = 𝑋𝑟 𝑞𝑟0 (ℎ𝑟2 − ℎ𝑟1 ) − 𝑃𝑖
Equation (J.2)
J.5 Calculation of heating capacity
The total heating capacity, ∅𝑡ℎ𝑖 , based on volatile refrigerant flow data is calculated using Equation (I.3):
∅𝑡ℎ𝑖 = 𝑋𝑟 𝑞𝑟0 (ℎ𝑟1 − ℎ𝑟2 ) − 𝑃𝑖
Equation (J.3)
Annex K
Outdoor air enthalpy test method
K.1 General
K.1.1 In the air enthalpy method, capacities are determined from measurements of entering and leaving
wet- and dry-bulb temperatures and the associated airflow rate.
K.1.2 Outdoor air enthalpy tests are subject to the apparatus arrangement limitations specified in J.2.1.
Additional provisions apply if the compressor is independently ventilated (see J.2.2). Line loss adjustment
permitted by J.4.3 may be made if the equipment employs remote outdoor coils.
K.2 Test room requirements
K.2.1 When the air enthalpy method is employed for outdoor-side tests, it should be ascertained whether
the attachment of the airflow measuring device changes the performance of the equipment being tested
and, if so, corrections should be made for this change (see Figure J.1). To accomplish this, the equipment
should have thermocouples soldered to return bends at approximately the midpoints of each indoor and
outdoor coil circuit. Equipment not sensitive to refrigerant charge may, alternatively, be provided with
pressure gauges connected to access valves or tapped into the suction and discharge lines. The equipment
should then be operated at the desired conditions, with the indoor-side test apparatus connected but not
the outdoor-side apparatus. Data should be recorded at 10 min intervals for a period of not less than 30
min after equilibrium has been attained. The outdoor-side test apparatus should then be connected to
the equipment and the pressure or temperatures indicated by the aforementioned gauges or
thermocouples noted. If, after equilibrium is again attained, these do not average within ±0.3 °C or its
pressure equivalent of the averages observed during the preliminary test, the outdoor airflow rate should
be adjusted until the specified agreement is attained. The test should be continued for a period of 30 min
after equilibrium has been attained at the proper conditions, with the outdoor test apparatus connected,
and the indoor-side test results during this interval should agree within ±2.0 % with the results obtained
during the preliminary test period. This applies to both the cooling and the heating cycle, but needs to be
done at any one condition for each.
K.2.2 For equipment in which the compressor is ventilated independently of the outdoor air stream, the
calorimeter air enthalpy method arrangement should be employed to take into account compressor heat
radiation (see Figure J.1).
K.2.3 When the outdoor airflow is adjusted as described in J.2.1, the adjusted airflow rate is employed in
the capacity calculation. In such cases, however, the outdoor fan power input observed during the
preliminary tests should be used for rating purposes.
Figure K.1 – Outdoor calorimeter test method arrangement
K.3 Testing conditions
When the outdoor air enthalpy method is used, the requirements in 6.1.3.1 apply to both the preliminary
test (see K.2.1) and the regular equipment test.
K.4 Calculations
K.4.1 The total indoor cooling capacity based on outdoor-
ated using Equation (J.1):
K.4.2 The total heat capacity based on outdoor-side data, ∅tho, is calculated using Equation (K.2):
K.4.3 If line loss corrections are to be made, they should be included in the capacity calculations.
Allowance should be made using Equation (K.3):
Where
Dt is the temperature difference between the inside and outside of the tube
Annex L
Indoor calorimeter confirmative test method
L.1 General
L.1.1 This annex provides a test method for confirming the test results when the cooling and heating
capacities are determined by the indoor air enthalpy test method.
L.1.2 In this test method, confirmation should be carried out in the test room specified in L.2 using the
measuring method specified in L.3.
L.2 Test room requirements
A recommended test room is shown in Figure L.1. This test room should be constructed such that the air
enthalpy test apparatus is installed in the indoor-side compartment of the calorimeter described in Annex
D. The calorimeter should be of either the calibrated-room type or the balanced-ambient room type. The
air enthalpy test apparatus should be equipped with means of not only measuring airflow rate and
enthalpies at the inlet and outlet of the equipment under test but also means for measuring the total
power input to the air-enthalpy test apparatus. It is recommended that air leaving the air-enthalpy test
apparatus lead to the vicinity of the intake opening of the reconditioning apparatus of the calorimeter.
L.3 Measurement
L.3.1 Measurements should be made 1 h after attaining equilibrium conditions.
L.3.2 Simultaneous measurements made by the calorimeter and the air enthalpy test apparatus should
be made in accordance with the methods specified. The cooling capacity determined by measurements
using the calorimeter should be calculated in accordance with Equation (D.1), and the heating capacity
should be calculated in accordance with Equation (D.5). Likewise, the cooling capacity determined by
measurements with the air enthalpy test apparatus is calculated in accordance with Equation (E.3), and
the heating capacity in accordance with Equation (E.5).
Figure L.1 - Indoor calorimeter test method arrangement
Annex M
Outdoor calorimeter confirmative test method
M.1 General
M.1.1 This annex provides a test method for confirming the test results when the cooling and heating
capacities are determined by the indoor air enthalpy test method.
M.1.2 In this test method, confirmation should be made in the test room specified in L.2 using the
measuring method specified in L.3.
M.2 Test room requirements
The air enthalpy test apparatus in the indoor-side compartment should be constructed in accordance with
this International Standard. The outdoor-side apparatus is the calorimeter, which should be constructed
and equipped with the measuring means described in Annex D. A recommended test room is shown in
Figure L.1.
M.3Measurement
M.3.1 Measurements should be made 1 h after attaining equilibrium conditions.
M.3.2 Simultaneous measurements should be made using the air enthalpy apparatus on the indoor side
and the calorimeter on the outdoor side in accordance with the methods specified. The cooling capacity
determined by measurements using the calorimeter should be calculated in accordance with Equation
(D.2), and the heating capacity should be calculated in accordance with Equation (D.6).
Annex N
Balanced-type calorimeter confirmative test method
N.1 General
N.1.1 This annex provides a test method for manufacturers to confirm the test results when the cooling
and heating capacities are determined by the indoor air enthalpy test method.
This test method should not be used as a confirmative method by testing laboratories because it does not
provide for simultaneous confirmative test results.
N.1.2 This method should be carried out by installing the equipment, which has been measured by the
balanced-type calorimeter, in the indoor air enthalpy test apparatus for measurement under the same
conditions as in the balanced-type calorimeter.
N.1.3 The performance of the indoor air enthalpy apparatus should be verified at least every 12 months
using an industry standard cooling/heating calibrating device. A calibrating device may also be another
piece of equipment for which the performance has been measured at an accredited test laboratory as
part of an industry-wide cooling/heating capacity verification programme.
N.2 Measurement
N.2.1 When this test method is employed, it is desirable to confirm that there is no difference between
the capacities measured by the calorimeter and the indoor air enthalpy test apparatus. To accomplish
this, the equipment should have thermocouples soldered to the return bends at approximately the
midpoints of each of indoor and outdoor coil circuits. Equipment not sensitive to refrigerant charge may,
alternatively, be provided with the pressure gauges connected to access valves or tapped into the suction
and discharge lines.
N.2.2 Firstly, the equipment to be tested should be installed in the balanced-type calorimeter described
in Annex D to carry out the measurement of the capacity. Then, the equipment should be moved to the
indoor air enthalpy test apparatus and measured by the specified method. It is desirable to measure both
cooling and heating capacities, though only one may be measured. However, if the cooling capacity is
measured by the calorimeter, the same measurement should also be made in the indoor air-enthalpy test
apparatus.
N.2.3 If no alteration is made to the installation of the equipment under test, a series of tests which are
conducted subsequently should be deemed valid.
Annex O
Cooling condensate measurements
O.1 General
The latent cooling capacity should be determined from measurements of the condensate flow rate. The
drain connection should be trapped to stabilize the condensate flow.
O.2Calculations
N.2.1 The latent cooling capacity, ∅𝑑 , is calculated using Equation (N.1):
∅𝑑 = 1000 𝐾1 𝑞𝑤𝑐
Equation O.1
O2.2 The sensible cooling capacity, ∅𝑠𝑐𝑖 , is then calculated using Equation (N.2):
∅𝑠𝑐𝑖 = ∅𝑡𝑐𝑖 − ∅𝑙𝑐𝑖
Equation O.2
Annex R
Pictorial examples of the heating capacity test procedures given in 7.1
R.1 General
The six schematic diagrams given in the examples in O.2 show several of the cases which could occur while
conducting a heating capacity test as specified in 7.1. All examples show cases where a defrost cycle ends
the preconditioning period. Examples 2 to 6 in O.2 represent cases where the indoor air enthalpy method
is used and, as a result, the data collection period for the transient test lasts 3 h or three complete cycles
(as opposed to 6 h or six complete cycles if using the calorimeter test method).
R.2 Procedure flowchart for heating capacity test
The following flowchart gives the procedures to adopt and the clauses in the main text to use when
conducting the heating capacity test.
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