BRITISH STANDARD BS EN 1216:1999€¦ · 2011. 8. 24. · This European Standard replaces ENV...

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BRITISH STANDARD
BS EN 1216:1999Incorporating Amendment No. 1
Heat exchangers — Forced circulation air-cooling and air-heating coils — Test procedures for establishing the performance

The European Standard EN 1216:1999, with the incorporation of amendment A1:2002, has the status of a British Standard

ICS 27.060.30

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This British Standard, having been prepared under the direction of the Engineering Sector Committee, was published under the authority of the Standards Committee and comes into effect on 15 May 1999

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National forewordThis British Standard is the English language version of EN 1216:1999, including amendment A1:2002. It supersedes DD ENV 1216:1994 which is withdrawn.

The start and finish of text introduced or altered by amendment is indicated in the text by tags !". Tags indicating changes to CEN text carry the number of the CEN amendment. For example, text altered by CEN amendment A1 is indicated by !".

The UK participation in its preparation was entrusted by Technical Committee RHE/30, Heat exchangers, which has responsibility to:

A list of organizations represented on this committee can be obtained on request to its secretary.

Cross-references

The British Standards which implement international or European publications referred to in this document may be found in the BSI Catalogue under the section entitled “International Standards Correspondence Index”, or by using the “Search” facility of the BSI Electronic Catalogue or of British Standards Online.

This publication does not purport to include all the necessary provisions of a contract. Users are responsible for its correct application.

Compliance with a British Standard does not of itself confer immunity from legal obligations.

— aid enquirers to understand the text;— present to the responsible European committee any enquiries on the

interpretation, or proposals for change, and keep the UK interests informed;

— monitor related international and European developments and promulgate them in the UK.

Summary of pages

This document comprises a front cover, an inside front cover, the EN title page,pages 2 to 22, an inside back cover and a back cover.

The BSI copyright notice displayed in this document indicates when the document was last issued.

Amendments issued since publication

Amd. No. Date Comments

14280 28 March 2003 See national foreword

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EUROPEAN STANDARD

NORME EUROPÉENNE

EUROPÄISCHE NORM

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EN 1216December 1998

+ A1October 2002

ICS 27.060.30

nsee=Burements ab

Supersedes ENV 1216:1993

Descriptors: heat exchangers, definitions, symbols, performance evaluation, calorific power, measurements, installation, tests, computation

English version

Heat exchangers — Forced circulation air-cooling and air-heating coils — Test procedures for establishing the

performance(includes amendment A1:2002)

Echangeurs thermiques —Batteries à aillettes à circulation forcée —Procédures d’essai pour la détermination des performances(inclut l’amendement A1:2002)

Wärmeaustauscher —Luftkühler und Lufterhitzer für erzwungene Konvektion —Prüfverfahren zur Leistungsfestellung(enthält Änderung A1:2002)

This European Standard was approved by CEN on 28 November 1998.Amendment A1 was approved by CEN on 14 September 2002.

CEN members are bound to comply with the CEN/CENELEC InternalRegulations which stipulate the conditions for giving this European Standardthe status of a national standard without any alteration. Up-to-date lists andbibliographical references concerning such national standards may be obtainedon application to the Central Secretariat or to any CEN member.

This European Standard exists in three official versions (English, French,German). A version in any other language made by translation under theresponsibility of a CEN member into its own language and notified to theCentral Secretariat has the same status as the official versions.

CEN members are the national standards bodies of Austria, Belgium, CzechRepublic, Denmark, Finland, France, Germany, Greece, Iceland, Ireland, Italy,Luxembourg, Netherlands, Norway, Portugal, Spain, Sweden, Switzerland andUnited Kingdom.

CENEuropean Committee for Standardization

Comité Européen de NormalisationEuropäisches Komitee für Normung

Central Secretariat: rue de Stassart 36, B-1050 Brussels

© 1998 CEN All rights of exploitation in any form and by any means reserved worldwide for CEN national Members.

Ref. No. EN 1216:1998 + A1:2002 E

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EN 1216:1998

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Foreword

This European Standard has been prepared by Technical Committee CEN/TC 110, Heat exchangers, the Secretariat of which is held by BSI.

This European Standard replaces ENV 1216:1993.

This European Standard shall be given the status of a national standard, either by publication of an identical text or by endorsement, at the latest by June 1999, and conflicting national standards shall be withdrawn at the latest by June 1999.

According to the CEN/CENELEC Internal Regulations, the national standards organizations of the following countries are bound to implement this European Standard: Austria, Belgium, Czech Republic, Denmark, Finland, France, Germany, Greece, Iceland, Ireland, Italy, Luxembourg, Netherlands, Norway, Portugal, Spain, Sweden, Switzerland and the United Kingdom.

Foreword to amendment A1This document EN 1216:1998/A1:2002 has been prepared by Technical Committee CEN/TC 110, Heat exchangers, the Secretariat of which is held by BSI.

This European Standard shall be given the status of a national standard, either by publication of an identical text or by endorsement, at the latest by April 2003, and conflicting national standards shall be withdrawn at the latest by April 2003.

According to the CEN/CENELEC Internal Regulations, the national standards organizations of the following countries are bound to implement this European Standard: Austria, Belgium, Czech Republic, Denmark, Finland, France, Germany, Greece, Iceland, Ireland, Italy, Luxembourg, Malta, Netherlands, Norway, Portugal, Spain, Sweden, Switzerland and the United Kingdom

This amendment is introduced to accommodate newly available refrigerants such as R404A, R407C and R410A.

Contents

PageForeword 20 Introduction 31 Scope 32 Normative references 33 Definitions 34 Symbols 85 Standard capacity 96 Manufacturer’s data 107 Measurements 118 Testing methods and equipment 139 Test procedures 1510 Capacity calculation 1611 Conversion to standard conditions 1812 Test report 18Annex A (normative) Circuit diagrams 19Annex B (informative) Oil content measurement procedure 22Annex C (informative) Bibliography 22

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0 Introduction

This European Standard is one of a series of European Standards dedicated to heat exchangers.

1 Scope

This European Standard applies to forced circulation air-cooling or air-heating coils operating:

a) with an evaporating or condensing refrigerant;

b) with a cooling or heating fluid;

c) without fans.

Operation with steam is not part of the standard.

This standard specifies uniform methods of testing under non-frosting conditions conducted on test samples to test and ascertain the following:

— product identification;— the capacity;— air side pressure drop;— fluid side pressure drop.

at standard conditions, unless otherwise stated by the user.

It is not the purpose of this standard to specify the types of test used for production or field testing.

2 Normative referencesThis European Standard incorporates by dated or undated reference, provisions from other publications. These normative references are cited at the appropriate places in the text and the publications are listed hereafter. For dated references, subsequent amendments to or revisions of any of these publications apply to this European Standard only when incorporated in it by amendment or revision. For undated references the latest edition of publication referred to applies:

EN 45001, General criteria for the operation of testing laboratories.

3 DefinitionsFor the purposes of this Standard, the following definitions apply:

3.1 forced-circulation air-cooling or air-heating coila tubular heat exchanger, with or without extended surfaces, for use in an air flow, circulated by fans

3.1.1 forced-circulation air-cooling coilan air-cooling coil through which a cooling fluid is circulated for the purpose of the sensible cooling, or sensible cooling and dehumidification of a forced-circulation air flow, including all components necessary for the distribution and collection of the cooling fluid

3.1.2 forced-circulation air-heating coilan air-heating coil through which a heating fluid is circulated for the purpose of the sensible heating of a forced-circulation air flow, including all components necessary for the distribution and collection of the heating fluid

3.1.3 cooling fluideither refrigerant or a liquid used for cooling

3.1.4 heating fluideither refrigerant or a liquid used for heating

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3.1.5 (primary) refrigerantthe working fluid, in a refrigeration system, that absorbs heat by evaporation at a low temperature and rejects it by condensation at a higher temperature. In the following, the term refrigerant is used

3.1.6 liquida working fluid circulated through a heating or cooling system which remains liquid during the absorption or rejection of heat

3.2 Coil dimensions

3.2.1 rowa bank of tubes that are located in a plane at right angle to the direction of the air flow

3.2.2 coil inlet areathe internal cross-sectional area of the duct containing the heat exchanger supplied by the manufacturer

3.2.3 total heat transfer surface (air side)whole external surface of the coil which is exposed to the air flow passing through the coil

3.3 Capacity

3.3.1 Air-cooling capacity

3.3.1.1 sensible (dry) air-cooling capacityheat flow which is rejected by the air by means of temperature drop

3.3.1.2 latent air-cooling capacitylatent heat flow which is rejected by the condensing water vapour of the air

3.3.1.3 total cooling capacity on air sidesum of the sensible and the latent capacities measured at the same time. It is equal to the enthalpy change of the air across the air cooling coil reduced by the enthalpy flow removed by the condensed water

3.3.1.4 total cooling capacity on fluid sideheat flow absorbed by the cooling fluid, expressed as the product of the mass flow of the cooling fluid and the difference between specific enthalpies at the outlet and inlet connections of the coil

3.3.1.5 enthalpy flow of condensatedifference between the total cooling capacities on air side and on fluid side which is equal to the specific enthalpy of the condensate multiplied by its flow rate

3.3.2 Air-heating capacity

3.3.2.1 heating capacity on air sideheat flow absorbed by the air passing through the coil

3.3.2.2 heating capacity on fluid sideheat flow rejected by the heating fluid, expressed as the product of the mass flow of the heating fluid and the difference between specific enthalpies at the inlet and outlet connections of the coil

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!3.4 pressuresNOTE All pressures are average values ascertained over the test duration, and are absolute pressures.

3.4.1 condensing pressurethe pressure of the refrigerant at the inlet connection of the condenser

3.4.2 evaporating pressurethe pressure of the refrigerant at the outlet connection of the calorimeter (applicable only to low pressure calorimeter method)

3.5 TemperatureNOTE All temperatures are average values ascertained over the measuring period.

3.5.1 Air temperature

3.5.1.1 air inlet temperatureaverage dry bulb or wet bulb temperature of the air at the coil inlet, taking into consideration the local air velocities

3.5.1.2 air outlet temperatureaverage dry bulb temperature of the air at the coil outlet, taking into consideration the local air velocities

3.5.2 Liquid temperature

3.5.2.1 liquid inlet temperatureaverage temperature of the liquid at the inlet connection of the coil, taking into consideration the local liquid velocities

3.5.2.2 liquid outlet temperatureaverage temperature of the liquid at the outlet connection of the coil, taking into consideration the local liquid velocities

3.5.3 Refrigerant temperature

3.5.3.1 evaporating temperaturedew point temperature of the refrigerant, corresponding to the evaporating pressure

3.5.3.2 condensing temperaturedew point temperature of the refrigerant corresponding to the condensing pressure

3.5.3.3 superheated vapour temperatureactual temperature of the refrigerant vapour:

a) at the air-cooling coil suction outlet connection;b) at the air-heating coil inlet connection

3.5.3.4 subcooled refrigerant temperaturetemperature of the liquid refrigerant:

a) at the inlet of the expansion device (not part of the air-cooling coil);b) at the outlet connection of the air-heating coil"



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!3.5.3.5 bubble point temperaturetemperature corresponding to the absolute pressure of the refrigerant at the outlet connection of the condenser

3.6 Temperature difference

3.6.1 Operation with refrigerant

3.6.1.1 inlet temperature differenceabsolute value of the difference between the air inlet dry bulb temperature and:

a) for air-cooling coils the evaporating temperature;b) for air-heating coils the condensing temperature

3.6.1.2 superheatingdifference between:

a) for air-cooling coils the superheated vapour temperature and the evaporating temperature;b) for air-heating coils the superheated vapour temperature and the condensing temperature

3.6.1.3 subcoolingdifference between the bubble point temperature and the subcooled refrigerant temperature:

a) in the case of an air-cooling coil at the inlet of the expansion device;b) in the case of an air-heating coil at the outlet connection of the coil

3.6.2 Operation with liquid

3.6.2.1 inlet temperature differenceabsolute value of the difference between air inlet temperature and liquid inlet temperature

3.6.2.2 liquid temperature differenceabsolute value of the difference between liquid inlet and outlet temperature

3.6.3 air temperature differenceabsolute value of the difference between air inlet and outlet temperature

3.7 high gliderefrigerant where the difference between the condensing and bubble point temperatures at a condensing temperature of 40 °C is greater than 3 K

3.8 Air flow/velocity

3.8.1 air face velocityair volume flow rate through the coil divided by the coil face area

3.8.2 air mass fluxair mass flow through the coil divided by the coil face area"



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!3.9 Pressure drop

3.9.1 air side pressure dropstatic pressure difference between the air inlet and outlet of the coil

3.9.2 fluid side pressure dropstatic pressure difference of the fluid between the inlet and outlet connections of coil

3.10 Specific enthalpy

3.10.1 air specific enthalpyspecific enthalpy corresponding to the dry bulb temperature and the dew point or wet bulb temperature

3.10.2 liquid specific enthalpyproduct of the temperature and the specific heat capacity of the liquid

3.10.3 Refrigerant specific enthalpy

3.10.3.1 refrigerant inlet specific enthalpyspecific enthalpy is the specific enthalpy of the refrigerant at the inlet connection of the coil:

— for air heating coils defined as the specific enthalpy of the refrigerant corresponding to the condensing pressure and the superheated vapour temperature;— for air cooling coils defined as the specific enthalpy of the liquid refrigerant at the inlet of the expansion device corresponding to the subcooled refrigerant temperature

3.10.3.2 refrigerant outlet specific enthalpyspecific enthalpy is the specific enthalpy of the refrigerant at the outlet connection of the coil:

— for air heating coils defined as the specific enthalpy of the refrigerant corresponding to the subcooled refrigerant temperature;— for air cooling coils defined as the specific enthalpy of the refrigerant corresponding to the evaporating pressure and the superheated vapour temperature

3.11 specific enthalpy differencedifference in the specific enthalpy at the inlet of the coil and the specific enthalpy at the outlet of the coil"



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4 Symbols

For the purpose of this European Standard, the following apply:

4.1 Letters

cpA specific heat capacity of air under test conditions kJ/(kgK)cpW specific heat capacity of air side condensate kJ/(kgK)hA specific enthalpy of air kJ/kghF specific enthalpy of fluid at coil connections kJ/kghL specific enthalpy of liquid at coil connections kJ/kghR0 specific enthalpy of refrigerant at the inlet of the expansion device kJ/kghR specific enthalpy of refrigerant at the coil connections kJ/kghW vaporization heat of water at 0 °C (hW = 2500,4) kJ/kgPlat measured latent cooling capacity kWPsens measured sensible cooling capacity kWPtotA measured total cooling or heating capacity on the air side kWPtotF measured total cooling or heating capacity on the fluid side kWPtotL measured total cooling or heating capacity on the liquid side kWPtotR measured total cooling or heating capacity on the refrigerant side kWPtot measured total cooling or heating capacity kWPW measured capacity on the air side condensates kWpatm atmospheric pressure hPape evaporating pressure kPapc condensing pressure kPapL liquid pressure at the coil connections kPaPR0 refrigerant pressure at expansion device inlet (air cooling coils) kPaPR2 refrigerant pressure at the coil outlet (for heating coils with refrigerant) kPaqmA mass flow rate of dry air kg/sqmF mass flow rate of fluid kg/sqmL mass flow rate of liquid kg/sqmR mass flow rate of refrigerant kg/sqmW mass flow rate of air side condensate kg/stA air temperature (dry bulb) °Ctc condensing temperature °Cte evaporating temperature °CtL liquid temperature °CtMR temperature of the refrigerant at the flow measuring point °CtML temperature of the liquid at the flow measuring point °CtR0 refrigerant temperature at the inlet of the expansion device (air cooling coils) °CtR1 refrigerant inlet temperature (air heating coils) °CtR2 refrigerant outlet temperature °CtW air side condensate temperature °Ctdp air dewpoint temperature °CtWb air wet bulb temperature °CVA air face velocity m/sVmA air mass flux kg/(s.m2)



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4.2 Subscripts

4.3 Superscripts

5 Standard capacity

5.1 Basis for standard-capacity data

The capacity of a given forced-circulation air-cooling or air-heating coil is dependent on:

a) inlet temperature and the moisture content of the entering air;

b) mass flow of air and of the cooling or heating fluid;

c) inlet and outlet conditions of the cooling or heating fluid.

Therefore the capacities of a forced-circulation air-cooling or air-heating coil are to be given for specific operating conditions.

5.2 Standard conditions for coil capacity

As coils may be used in a wide range of applications, conditions shall be specified for each particular case with minimum values of:

∆tL = 5 K;

∆t1 = 10 K;

∆t2 = 7 K.

Table 1 provides a set of standard conditions, which can be used for comparison purposes.

X mass of water vapour per kg of dry air (vapour content) kg/kgZ test duration spA air side pressure drop PapL liquid side pressure drop PapF fluid side pressure drop Pa∆t1 inlet temperature difference K∆t2 difference between air inlet wet bulb temperature and liquid inlet or evaporating

temperature K∆tL liquid temperature difference K∆tsub subcooling K∆tsup superheating K

1 refers to inlet;2 refers to outlet.

(st) refers to standard conditions



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! Table 1 — Standard conditions for comparison purposes

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6 Manufacturer’s dataThe manufacturer or supplier shall supply to the test house the following minimum information for every air-cooling or air-heating coil, to identify the air-heating or air-cooling coil and allow its traceability:

a) manufacturer’s identification;

b) type, model and size (designation);

c) name of fluid used;

d) mounting instructions, maximum working pressure;

e) number of rows;

f) tube nominal outside diameter;

g) tube spacing in direction of air flow;

h) tube spacing in a row perpendicular to the air flow;

i) tube row alignment, parallel or staggered;

j) tube material and thickness;

k) number of circuits;

l) cool circuit arrangement diagram;

m) direction of air flow (horizontal, vertical, oblique);

n) internal volume;

and where applicable:

o) connection sizes and type;

p) nominal fin thickness;

q) fin spacing;

r) fin material;

s) oil type.

Cooling Heating

Air side conditions Temperature:Dry bulb (°C) 27 27 20 20 35Wet bulb (°C) 24 19 10 — —Mass flux [kg/(s.m2)] 2,93 2,92 2,91 4,80 4,54

Liquid Liquid type = water: — — — — —Inlet temperature (°C) 7 7 7 50 —Outlet temperature (°C) 12 12 12 40 —

Fluid side conditions

Refrigerant Evaporating temperature (°C) 8 8 8 — —Condensing temperature (°C) — — — 40 55Superheating (K) 8 8 8 a a

Subcooled liquid temperature (°C) 30 30 30 k3 k3Subcooling (K) — — — k1 % k1 %Oil content k1 % k1 % k1 % — —

a Superheating temperature, %tsup for common refrigerants shall be determined according to:

R134A 25KNH3 50KR404A 25KR407C 35KR410A 40K



EN 1216:1998


7 Measurements

7.1 Uncertainty of measurements

The testing equipment shall meet the requirements for uncertainty of measurements given in Table 2.

Table 2 — Uncertainty of measurements

7.2 Measurement criteria

7.2.1 Air temperature

The air inlet and air outlet temperature shall be measured in the centre of equal sections of the heat exchanger inlet area. There shall be a minimum of four sections.

The use of any other method of measurement is acceptable provided the same accuracy is obtained.

Temperature sensing elements shall be shielded against thermal radiation.

7.2.2 Moisture content

In the case of air-cooling coils with dehumidification, the moisture content shall be measured and controlled accurately, because the latent capacity is very sensitive to its value. Dewpoint temperature measurement is recommended. There is no objection to the use of other methods of measurement if the same accuracy is obtained. If the wet bulb temperature is measured, the uncertainty of measurement shall be sufficiently small for the dew point temperature to be calculated to within ±0,2 K.

The measurement plane for the moisture content shall be located as close as possible to the measurement plane for the air temperature.

7.2.3 Air pressure drop

The static pressure measurement upstream and downstream of the coil can be performed with a Pitot tube traverse inserted in the duct line.

The use of any other method of determining the air pressure drop is acceptable provided the same accuracy is obtained.

7.2.4 Air velocity

The air velocity measured evenly over an area not less than 75 % of the total duct area, whose boundary is parallel with the duct wall for a rectangular duct or concentric with the duct for a circular duct, and equidistant about the centre line of the duct, shall not vary by more than ±5 % from the mean value.

Measurement Uncertainty of measurement

Air temperature (dry bulb, dewpoint [see 7.2.2]) ±0,2 KLiquid temperature and temperature difference ±0,1 KRefrigerant temperature ±0,2 KAmbient air temperature ±0,2 KRefrigerant pressure Sufficiently small for the related refrigerant

temperature to be obtained within ±0,2 KAtmospheric pressure ±5 hPaAir side condensate flow rate ±1 % or 3 g/h whichever is greaterAir flow rate ±2 % of the measured valueLiquid flow rate ±1 % of the measured valueRefrigerant flow rate ±2 % of the measured valueAir side pressure drop ±5 % or 2 Pa whichever is greaterFluid side pressure drop ±5 % or 1 Pa whichever is greaterTime interval ±0,1 % of the reading or ±2 s whichever is smallerMass ±0,5 % of the measured value!Refrigerant mixture ±1 % by mass for each refrigerant component"

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7.2.5 Heating or cooling fluid temperature

7.2.5.1 General

The fluid temperature shall be measured as close as possible to the coil connection and in any case within fifteen times the connection outside diameter and in accordance with the following:

a) when the temperatures are measured on the outside of the pipe, it shall be at two opposite points of the same cross-section and, if the pipe is horizontal, there shall be one point above and one below;

b) when the temperatures are measured by a sensor immersed in the pipe, it shall be ensured that temperatures stratification and flow patterns do not influence the accuracy of the measurements.

The pipe shall be insulated from the coil for a length of at least ten times the outside diameter beyond the temperature measuring point. Good thermal contact between the sensor and the pipe at the measuring point, shall be ensured.

7.2.5.2 Liquid temperature

For liquid temperatures measurement in accordance with 7.2.5.1b) is preferred.

7.2.5.3 Refrigerant temperature

Measurement of refrigerant temperatures shall be as follows:

a) for the superheated vapour temperature on air heating coils measurement in accordance with 7.2.5.1b) is preferred;

b) for the subcooled liquid refrigerant temperature in front of the expansion device measurement in accordance with 7.2.5.1a) is preferred to avoid the risk of generation of flash gas;

c) for the subcooled refrigerant leaving an air heating coil, only measurement in accordance with 7.2.5.1b) is applicable, ensuring that the sensing element is totally immersed into the liquid phase;

d) for the superheated refrigerant vapour leaving an air cooling coil, measurement in accordance with 7.2.5.1a) is preferred due to the non-homogeneous nature of the vapour/liquid mixture and the fact that the sensors of control devices are also fixed onto the outside of the pipe.

7.2.6 Fluid pressure measuring points

The pressure measuring points shall be located in the middle of a straight part of the connecting pipe of constant diameter, (equal to the coil connections) having a length of not less than ten diameters ensuring that there is no restriction involved. They shall be positioned between the temperature measuring points and the connections of the coil.

7.2.7 Fluid flow rate

7.2.7.1 General

The flow rates of the fluid shall be measured using measuring devices calibrated and installed in accordance with the instructions of the measuring device manufacturer.

If the fluctuations of the flow increase the uncertainty of the measurement noticeably, integrating devices shall be used.

7.2.7.2 Refrigerant

If volume flowmeters are used in the liquid line, the refrigerant has to be sufficiently subcooled in order to prevent flashgas which causes inaccurate measurement. In order to check that there is no flashgas a sight glass shall be placed on each side of the flowmeter.

7.2.8 Oil content

The oil content shall be less than 1 % by mass. The oil content shall be measured unless it is otherwise guaranteed. For recommended measurement procedure, see Annex B.

7.2.9 Air-side condensate flow rate

In the case of dehumidifying coils, the condensate shall be collected during the test duration. The condensate flow rate shall be determined by dividing the collected mass of condensate by the test duration.

Any other method of determining the flow rate of condensate is accepted provided the same accuracy is obtained.

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!7.2.10 Non-azeotropic refrigerant

For high glide refrigerants the refrigerant mixture shall be measured unless it can be guaranteed that the mass fraction varies by less than 2 % from the refrigerant manufacturer’s data."

8 Testing methods and equipment

8.1 Testing method

8.1.1 General

In order to fulfil the requirements of this standard, two methods of determining the coil capacity shall be used simultaneously.

The primary method shall determine the cooling or heating capacity on the cooling or heating fluid side.

The confirming method shall determine the cooling or heating capacity on the air side, allowing for the enthalpy flow of the condensed water, if any.

The result of the confirming method shall agree with that of the primary method within ±5 %.

The fluid-side capacity shall be used as the capacity of the coil.

The testing method and measuring points are given in Annex A.

!Care shall be taken with non-azeotropic refrigerants, that there are no liquid refrigerant accumulations in the refrigerant cycle. While testing non-azeotropic refrigerants, the concentration of the individual refrigerants within the mixture circulating through the unit cooler shall remain identical to the concentration with which it was originally filled.NOTE Non-azeotropic refrigerants are mixtures of more than one refrigerant with different individual boiling temperatures. If the mixture is separated at a two phase state e.g., in a vessel, one of the two phases can accumulate affecting the concentration of each refrigerant within the rest of the system."

8.1.2 Fluid side capacity

8.1.2.1 Liquid

The principle of the method is to obtain the fluid side capacity by measuring directly the flow rate of the liquid and multiplying this by the specific enthalpy difference across the coil.

8.1.2.2 Refrigerant

The principle of the method is to obtain the fluid side capacity by measuring directly the flow rate of the refrigerant and multiplying this by the absolute difference between the specific enthalpies at the inlet and outlet connections of the coil.

8.1.3 Air side capacity (confirming method)

8.1.3.1 Capacity of air-heating coils

The principle of the method is to obtain the air side capacity by measuring the air mass flow rate directly and multiplying it by the difference between the specific enthalpy at air outlet and air inlet.

8.1.3.2 Capacity of air-cooling coils

The measurement of the capacity of air-cooling coils shall be in accordance with the following.

a) The principle of this method is to obtain the air side capacity by adding the sensible cooling capacity to the latent cooling capacity. The sensible cooling capacity is obtained by measuring the air mass flow rate directly and multiplying it by the sensible part of the difference between specific enthalpies at the air inlet and air outlet. This enthalpy difference is obtained by use of the dry bulb temperatures and the specific heat capacities at the air inlet and outlet, taking into account the vapour content.The latent cooling capacity is obtained by measuring the flow rate of water condensate directly and multiplying it by the specific water vaporization heat minus the enthalpy of the condensate.b) Where the latent capacity is not required, the air side capacity can be obtained by measuring the air mass flow rate directly and multiplying it by the total difference between specific enthalpies at the air inlet and air outlet. The specific enthalpies are obtained by use of the dry bulb temperature and the dew point or wet bulb temperature.The total air side capacity equals the difference of the enthalpy flow thus obtained, and the enthalpy flow removed by the water, condensed on the air side.



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8.1.4 Air flow rate

The air flow rate may be measured, for example, through static pressure difference measurement between two points, located upstream and downstream of a standardized restriction, according to ISO 5221.

Any other method is acceptable provided it gives the same accuracy.

For the purpose of this standard, the influence of the moisture content of the air on the air flow measurement shall be ignored.

In the following, the measured air mass flow rate shall be considered as the dry air mass flow rate.

8.2 Equipment

8.2.1 General requirements

The testing equipment shall be designed in such a way that:

— at the inlet of the coil the velocities and temperatures of the air can be maintained within the specified limits;— the temperature and pressure measuring devices do not influence the turbulence of the airflow at the inlet of the coil significantly;— the heat exchange of the duct and coil with the ambient air between the temperature measuring planes is below ±0,5 % of the measured capacity;— no measurable air leakage of the ductwork between the air flow meter and the coil occurs;— steady state conditions can be maintained;— there shall be a straight and unrestricted section of duct, having the same cross-section as the coil face area, of not less than twenty times the equivalent diameter of measuring devices in the duct or one equivalent hydraulic diameter of the coil face area, whichever is the greater, between the measuring planes and the coil.

8.2.2 Operation with liquid

Venting facilities shall be provided to ensure that the liquid is free from entrained air which would result in inaccurate measurements.NOTE The system should preferably be pressurized with automatic venting of air.

8.2.3 Operation with refrigerant

8.2.3.1 Air heating coils

The test equipment shall guarantee free drainage of the refrigerant from the coil outlet connection to a liquid receiver, which is positioned below the level of the outlet connection, ensuring that there is no restriction involved.

All refrigerant vapour shall be trapped in this !receiver".

A sight glass will enable the liquid level and thus also constant refrigerant flow to be checked during the test period.

The !receiver" and the connecting pipe shall be well insulated in order to ensure that the heat loss is less than 0,5 % of the measured coil capacity.

8.2.3.2 Air cooling coils

As the specific enthalpy of the refrigerant entering the coil is defined by the specific enthalpy of the liquid refrigerant at the inlet of the expansion device, the refrigerant shall be sufficiently subcooled and without flashgas. In order to check this, a sight glass shall be placed immediately in front of the expansion device.

8.2.4 Air cooling coils with dehumidification

If droplets of the condensed water are carried away by the air flow leaving the coil, care shall be taken that it does not affect the measurement of the humidity content and the measurement of the condensed water flow rate as well as the pressure measurement.

!8.2.5 Liquid receiver

For high glide refrigerants the internal volume of the liquid receiver shall be less than 4 % of the total system volume."



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9 Test procedures

9.1 Physical arrangement

9.1.1 The coil shall be installed in accordance with the manufacturer’s specifications.

All components supplied by the manufacturer as a part of the coil shall be included in the test set-up and used in accordance with the instructions.

9.1.2 The liquid shall be free from entrained air.

9.2 Permissible deviations

9.2.1 Air heating coils

The permissible deviations are chosen such that the conversion method gives a maximum error of ±3 %.

If the set conditions are the standard ones, the uncertainty given in Table 3 shall apply.

Table 3 — Uncertainty for set conditions for air heating coils

9.2.2 Air cooling coils

The permissible deviations are chosen such that the conversion method gives a maximum error of ±3 %.

If the set conditions are the standard ones, the conditions given in Table 4 shall apply.

Table 4 — Uncertainty for set conditions for air cooling coils

Quantity Uncertainty

qma ±1,0 %tA1 ±2,0 K

Fluid Liquid Refrigerant

∆t1 ±0,5 K ±0,5 K∆tL ±0,2 K —∆tsup — ±0,5 K∆tsub — k3 K

Quantity Uncertainty

qma ±1,0 %tA1 ±2,0 Ktdp1 ±0,3 K∆t1 0,2 K

Fluid Liquid Refrigerant

∆tL ±0,2 K —∆tRO — ±0,3 K∆tsup — ±1,0 K

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9.3 Steady state conditions

The measurement of the capacity shall be carried out under steady state conditions. Steady state shall be reached a minimum of 30 min before testing commences.

Steady state conditions are assumed to exist when all changes and periodic fluctuations remain within the following:

9.4 Test duration

The test duration shall be chosen such that any deviation from steady state conditions will not influence the uncertainty of the test results by more than ±0,5 %.

The test duration shall be a minimum of 30 min.

During the test period at least five sets of measurements shall be taken at regular intervals, sufficiently small to identify all significant fluctuations.

9.5 Data to be recorded

The data specified in 9.5.1, 9.5.2, 9.5.3, 9.5.4 and 9.5.5 shall be recorded during the test.

9.5.1 Air side

tA1, tA2, qmA, %pA

additional for air cooling coils:

tWb1 or tdp1, tW, qmW, tWb2 or tdp2 when the total air side capacity is obtained by use of the air enthalpy difference.

tW may be approximated to tdp2 and then does not need to be recorded.

9.5.2 Cooling and heating fluid side for liquid operation

tL1, tL2, qmL, %pL or pL1 or pL2

9.5.3 Cooling fluid side for refrigerant operation

pe, tRO, tR2, qmR, tmR, pRO

the refrigerant used and the oil content.

9.5.4 Heating fluid side for refrigerant operation

pc, tR1, tR2, qmR, tmR, pR2

the refrigerant used and the oil content.

9.5.5 Test duration: Z (mins)

10 Capacity calculation

10.1 Fluid side heating capacity

10.1.1 General

The fluid side heating capacity shall be calculated in accordance with 10.1.2 or 10.1.3 as appropriate.

— flow rates ±2 %;— a) for heating coils:

— air inlet temperature ±1 K;— subcooling ±1 K;— superheated vapour temperature ±3 K;— inlet temperature difference ±0,5 K;

— b) for cooling coils:— air inlet temperature (dry bulb, dew point) ±2 K;— superheating ±1 K;— subcooled liquid temperature ±2 K;— inlet temperature difference ±0,5 K.



EN 1216:1998


10.1.2 For liquid operation

10.1.3 For refrigerant operation

10.2 Air side heating capacity

The air side heating capacity shall be calculated in accordance with the following:

10.3 Fluid side cooling capacity

10.3.1 General

The fluid side cooling capacity shall be calculated in accordance with 10.3.2 or 10.3.3 as appropriate.

10.3.2 For liquid operation

10.3.3 For refrigerant operation

10.4 Air side cooling capacity

10.4.1 General

The air side cooling capacity shall be calculated in accordance with 10.4.2, 10.4.3 and 10.4.4, and the enthalpy flow of the air-side condensates in accordance with 10.4.5.

10.4.2 Sensible cooling capacity

10.4.3 Latent cooling capacity

10.4.4 Air side total cooling capacity

10.4.5 Enthalpy flow of the air-side condensates

10.5 Relative deviation

The relative deviation rd between the results of the primary and confirming method is:

PtotL = qmL (hL1 p hL2) (1)

PtotR = qmR (hR1 p hR2) (2)

PtotA = qmA (hA2 p hA1) (3)

PtotL = qmL (hL2 p hL1) (4)

PtotR = qmR (hR2 p hR0) (5)

Psens = qmA (cpA1 × tA1 p cpA2 × tA2) (6)cpA = 1,006 + 1,835 X (7)

Plat = qmW × (∆hW) (8)

1) PtotA = Psens + Plat; (9)2) PtotA = qmA (hA1 p hA2) p qmW × cpW × tW. (10)

PW = qmW × cpW × tW (11)

rd = 100 × in % (12)PtotA Pv PtotF–+

PtotF----------------------------------------------



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11 Conversion to standard conditions

11.1 Correction for standard barometric pressure

The influence of barometric pressure on sensible heating or cooling capacity can be neglected.

The influence on latent cooling capacity is very complex, and cannot be corrected without the help of a coil calculation model. Therefore, no correction shall be made.

11.2 Conversion to standard capacity

11.2.1 For air heating coils, liquid and refrigerant operation

11.2.2 For air cooling coils, liquid and refrigerant operation

11.3 Conversion to standard air side pressure drop

NOTE 1,8 is an empirical value, considering that the exponent normally lies between 1,5 and 2. Therefore, for a single set of tests, the accuracy is sufficient.

11.4 Conversion to liquid side pressure drop

NOTE 1 1,8 is an empirical value considering that the exponent normally lies between 1,5 and 2. Therefore, for a single set of tests, the accuracy is sufficient.

NOTE 2 Standard refrigerant side pressure drop is not relevant for the user.

12 Test report

The test report shall be in accordance with EN 45001.

P(st) = PtotF × (13)

P(st) = PtotF × (14)

shf(st) = (15)

Plat(st) = P(st) × shf(st) (16)

Plat(st) = P(st) × [1 p shf(st)] (17)

%pA(st) = %pA × (18)

qmL(st) = (19)

%pL(st) = %pL × (20)

%t1(st)

%t1--------------

%t2(st)

%t2--------------

PsensPtot--------------

pmA(st)

qmA------------------

1,8

p(st)

hL1(st) hL2

(st)–----------------------------------------

qmL(st)

qmL------------------

1,8



EN 1216:1998


Annex A (normative)Circuit diagrams

Key

1 liquid flowmeter

2 air heating/cooling coil

3 air flowmeter

Figure A.1 — Heating/cooling with liquid

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Key

1 sight glass

2 refrigerant flowmeter

3 to evaporator

4 from compressor

5 air heating coil

6 liquid receiver

7 air flowmeter

Figure A.2 — Heating with refrigerant



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Key
1 to compressor

2 expanision device

3 sight glass

4 refrigerant flowmeter

5 from condenser

6 air cooling coil

7 air flowmeter

Figure A.3 — Cooling with refrigerant by direct expansion



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Annex B (informative)Oil content measurement procedure

The oil content should be measured under steady state conditions, immediately after the capacity test has been finished.

The following method for measuring the oil content is recommended. Any other method can be used, provided that it has the same accuracy:

a) evacuate the pressure vessel for the oil/refrigerant mixture sample having a volume of 100 cm3 to 200 cm3;

b) weigh the empty vessel with an accuracy of ±0,1 g;

c) connect this vessel to the liquid line at the appropriate position;

d) weigh the vessel filled with the test sample with an accuracy of ±0,1 g;

e) evaporate the refrigerant carefully in order to prevent any escape of oil with the refrigerant and evacuate the vessel. The refrigerant should be recovered.

The refrigerant should be recovered:

f) add a solvent to the remaining oil (e.g. methylchloroform) in the vessel. Shake the mixture carefully and put it into an evaporating pan which has been weighed accurately to ±1 mg. Following this, rinse the vessel twice with the solvent and put this mixture also into the pan;

g) evaporate the solvent by means of a boiling water bath;

h) weigh the evaporation pan with the oil accurately to ±1 mg;

i) the oil content is obtained by dividing the difference of the masses of the evaporating pan with and without remaining oil by the difference of the masses of the pressure vessel with and without the “refrigerant + oil” test sample.

Annex C (informative)Bibliography

EN 247, Heat exchangers — Terminology.

EN 305, Heat exchangers — Definitions of performance of heat exchangers and the general test procedure for establishing performance of all heat exchangers.

EN 306, Heat exchangers — Methods of measuring the parameters necessary for establishing the performance.

EN 307, Heat exchangers — Guidelines to prepare installation, operation and maintenance instructions required to maintain the performance of each type of heat exchangers.




blanks Institution license with BSI - Uncontrolled Copy


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BS EN 1216:1999

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