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IS 13687 (1993): Internal combustion engines - Radiators -Heat dissipation performance - Method of test [TED 2:Automotive Primemovers]

IS 13687 : 1993

Indian Standard

INTERNAL COMBUSTION ENGINES - RADIATORS - HEAT DISSIPATION

PERFORMANCE - METHOD OF TEST

UDC 621’43 : 629’113

0 BIS 1993

BUREAU OF INDIAN STANDARDS y MANAK BHAVAN, 9 BAHADUR SHAH ZAFAR MARC

NEW DELHI 110002

December 1993 Price Group 4

Automotive Primemovers Sectional Committee. TED 2

FOREWORD

This Indian Standard was adopted by the Bureau of Indian Standards, after the draft finalized by the Automotive Primemovers Sectional Committee had been approved by the Transport Engineering Division Council.

This Indian Standard specifies the method of test for assessing the heat transfer efficiency of radiators used in road vehicles. The efficiency of cooling arrangement of an internal combustion engine when fitted with a radiator may be judged mainly by its heat transfer performance. The principle adopted for assessment makes use of a wind tunnel arrangement with provisions for measuring the pressure and temperatures of air, coolant and flow rate in front and rear of the radiator. Typical performance curves and recording of test results are given in Annex B and Annex C. This standard is an important adjunct to IS 761 I : 1993 ‘Internal combustion engines - Radiators - Specification (first revision )’ and IS 13686 : 1993 ‘Internal combustion engines - Radiators - Methods of test’.

In the preparation of this Indian Standard considerable assistance has been derived from:

JIS D 1614-1970 ‘Heat dissipation test code of radiators for automobiles’ issued by the Japanese Jndustrial Standards Committee.

In reporting the results of a test or analysis made in accordance with this standard, if the final value, observed or calculated, is to be rounded off, it shall be done in accordance with 1s 2 : 1960 ‘Rules for rounding off numerical values ( revised )‘.

P

Indian Standard

IS 13687 : 1993

INTERNAL COMBUSTION ENGINES- RADIATORS- HEAT DISSIPATION

PERFORMANCE- METHOD OF TEST

1 SCOPE

This Indian Standard specifiesthe method of test for assessing heat dissipation performance of automotive radiators.

2 REFERENCES

The followingIndian Standards are necessary adjuncts to this standard:

ZS No. Title

7611 : 1993 Internal combustion engines - Radiators - Specification (first revision)

13686 : 1993 Internal combustion engines - Radiators - Methods of test

3 TERMINOI,OGY

3.0 For the purpose of this standard, the following definitions shall apply.

3.1 Converted Heat Dissipation Rate

The heat dissipation rate of the cooling water (hereinafter referred to as “waterside”), which is converted to the state where inlet temperature difference between water and air is 60°C, and is expressed by the unit of kilocalorie per hour (kcal/h).

3.2 Heat Dissipation Rate on Waterside

The heat dissipation rate under test conditions, expressed as the quantity of heat which water loses under, and is expressed by the unit of kilocalories per hour (kcal/h).

3.3 Heat Reception Rate on Airside

The heat rate which the cooling air (hereinafter, referred to as “air” receives under test conditions and is expressed by the unit of kilocalories per hour (kcal/h).

3.4 Inlet Temperature Difference

The difference between the inlet temperatures ofwater and air expressed by the unit of degree Celsius (“C).

3.5 Water Flow Rate

The flow rate of water which passes through the radiator expressed in litres per minute (l/mm).

3.6 Air Velocity at Frontal Area

The flow rate of air passing through the radiator divided by the frontal area and is expressed in metre per second (m/s).

3.7 Pressure Loss of Waterside

The difference of static pressure between the water side inlet and outlet of the radiator which is measured at the test state and is expressed by the unit of mercury column height of millimetre (mm Hg).

3.8 Pressure Loss of Airside

The difference of static pressure between the airside inlet and outlet of the radiator, measured at the test state and is expressed by height of water column in millimetre (mm Aq).

3.9 Upstream End

Area before the radiator which permits entry of air into the radiator.

3.10 Downstre+n End

Area after the radiator which permits exit of air away from the radiator.

4 TEST REQUIREMENTS

4.1 The radiator shall comply with IS 7611 : 1993.

4.2 The test room conditions shall be steady and at normal ambient temperature and humidity. The air flow shall be steady without large fluctuations.

4.3 Unless otherwise specified the water used for test purposes shall be clear without suspended impurities and the radiator inlet water temperature maintained at 85 + 5OC at the dissipation state. The temperature shall- be recorded at steady state conditions and a variation of 2 2OC in the water inlet temperature is permissible between successive readings.

4.4 The measuring equipment shall be calibrated before start of test.

4.5 The test room shall be maintained ,at steady atmospheric condition.

5 TESTING AND MEASURING- ARRANGE- MENTS ,

5.1 The test apparatus is broadly divided into waterside

IS 13687 : 1993

circuits and airside (wind tumlel) circuits. The typical testing arrangement is shown in Fig. 1.

5.2 Waterside Circuit

5.2.1 The waterside circuit shall be equipped with separators in order to prevent mixing of air and vapour in the waterside circuit of the radiator. The hot water tank shall be so designed as to prevent air and vapour locking.

5.2.2 The water pump may be connected, to either side of the inlet pipe or the outlet pipe of the radiator. Care shall be taken to avoid any cavitation.

5.2.3 The rate of heat generation by hot water tank shall be enough to maintain heat dissipation rate and shall be adjustable in all ranges of heat dissipation.

5.3 Airside (Wind Tunnel) Circuit

5.3.1 Wind Tunnel

The air flow passing through radiator shall. be adjustable. The arrangement shall include fan, throttle devices such as orifice, shutter, cone. The comiecting tube between the main body of the wind tunnel and the radiator shall be interchangeable to take care of variations in size and shape of radiator:The shape of the connecting tube shall be such that the front of the radiator receives a uniform parallel flow,of air. All joints shall be totally airtight.

5.3.2 An alternate suction type arrangement with wind tunnel is also permissible when mutually agreed between the manufacturer and the purchaser. The details of such arrangement are given in Annex A.

5.4 Measuring Equipments

5.4.1 Water Flowmeter

The water flowmeter used shall have an accuracy of + 2% of maximum scale.

5.4.2 Air Flowmeter

The air flowmeter used shall be based on Pitot tube or Orifice or Nozzle. The minimum scale for liquid column shall be 1 mm on 30’ inclined type manometer or that having a vertical column.

5.4.3 Pressure Gauges

For waterside the liquid mercury column gauge shall have a minimum one mm accuracy. For the airside to measure pressure loss, the liquid column gauge shall have at least 1 mm accuracy. For measuring atmospheric pressure, a Fortin’s barometer is recommended.

5.4.4 Thermometers

For measuring the temperatures the thermometers used shall have at least t O.l°C accuracy for waterside and l°C accuracy airside. For room temperature and humidity, a wet and dry bulb thermometer shall be used.

6 TESTS

6.1 The airside circuit is completed by connecting the radiator and wind tmmelwith the connecting tube. The waterside circuit of the test apparatus is connected to the inlet and outlet pipes of the radiator. When the radiator (see Fig. 1) reaches stable conditions with specified rate of air and water flow, the heat tratifer and pressure loss tests shall be conducted.

6.2 The following are measured:

a) Atmospheric pressure and humidity b) Inlet and outlet water temperatures c) Inlet and outlet air temperatures d) Rate of air and water flow e) Wind velocity f) Pressure loss -Water and air sides.

6.3 Flow measurements shall be made after stable conditions are reached. When Pitot tube is used for air flow, only the control air velocity may be measured and the ratio of mean to centre velocity shall be used for computing the rate of airflow. The airflow is to be measured in the air inlet side.

6.4 Pressure Loss Measurements

The pressure loss measurement of waterside is to be made’ at the position as near as possible to the end of inlet and outlet pipe of radiator.

The pressure loss measurement of airside is to be near the radiator at the upstream and down- steam end both locations being equidistant from centre line of radiator core.

6.5 Temperature of water shall be measured as accurately as possible, near the inlet and outlet pipe of radiator. The measurement of air temperatures is to be made at the upstream and downstream end of the radiator. Inlet air temperature may be measured at the centre of core. In the case of outlet air temperature, measurements be made at least at four places covering entire core face and the mean temperature shall be calculated. The point of location of thermometer shall be such that it does not receive radiant heat from the radiator.

7 CAILXJLATIONS

7.1 From the results obtained, the heat dissipated on the waterside shall be calculated and this value shall be judged by heat received on airside simultaneously. The air velocity on the’ upstream side shall also be calculated.

7.2 Heat Dissipation on Waterside shall be calculated by the following formula:

Qw~ = GVV x Cw [T, - T,]

where

QMJ = ;te &heat dissipated on the waterside, ca

2

OUNTER 80 CONNECTNIG .T

. THERMOMETER FOR INLET AIR TEMPER

THERMOMETER FOR THE LET WATER TEMPERATURE

COLUMN GAUGE WATER) FOR THE AIR

PRESSURE LOSS

STREAM END

w METER FOR THE AIR TEMPERATURE

0 COLUMN GAUGE(MERCURY) THE WATER SIDE PRESSURE LOSS - ”

WATER TEMPERATURE

HOT WATER TAN

VOLT METER. / WATER FLOW METER\ \LIQUID COLUMN GAUGE(WATER) .

WATER FLOW ADJbSTING FOR THE AIR FLOW METER

FIG. 1 TYPICAL TESITNG ARHANGEMENT G s

IS 13687 : 1993

Gw =

T, =

Tz =

weight of water circulated through the ra- diator per hour (kg/h)

VWX vx lo-’ x60

volume of water flow per minute in litres weight of water per unit volume (kg/nt3)

specific heat of water, assumed as 1.0 (kcal/kgOC)

inlet water temperature, OC

outlet water temperature, OC

NOTE 1 -The value of weight of water corresponding IO the temperature of water recorded closes1 IO the flowmeter shall be used (sac Fig. 2).

loo-

-960

-

go-=-

80 ; 970

-

70:-

y-980

60-__

so-_

1% 1 40-J (k$-n3)

5 990

FIG. 2 TEMPERATIJRE AND WEIGHT PER UNIT VOLLIME

OF WAXR

NOTE 2 -For validity of test results. heat received on airsidc shall be within -C lO’% OC heat dissipated on waterside.

7.2.1 Hcwt Received on Airside

Qo =

where

Qcr =

Ctr =

Go x Ctr (T, - T,)

heat received ou the airside, (kcal/h)

specific heat ofair, kcal/kgoC(assuuted as 0‘24 kcal/kgV)

T, =

T, =

Gn =

Ga =

where

Vrr =

A =

nieaii outlet air temperature, OC

iiilet air temperature, OC

weight of air passing through per hour,

(kg/h)

Vn xA

rate of air, (nt”/h) (To be determiued by Orifice/Pitot Tube methods)

weight of air per unit voluu~ (kg/n?)

7.3 Method of Calculation for Rate of Air, Va

7.3.1 Pitot Tube Method

where

s =

v,, =

Vtr = 3 600 x S x Vnl

cross-sectional area of wind tunnel at the measuring position, (&)

nmn air velocity in the wind tunnel at the nicasuriug positioii (m/s)

.I 2gpd also V,,, = \ 1 -

V A

where

&Y =

pd =

=

A =

acceleratioudue to gravity, m/s’(9.8 m/s*)

dynamic pressure in Pitot Tube (Arithmetic mean of pressure II,, II,, . . . . .

‘L)

l/m (/II + II, . . . . . . . . llm>

weight of air per unit volun~e (kghd)

7.3.2 U,sing the OriJicc

Vr1=3600xtrxBxmx

where

c1 =

B =

m =

px =

K =

fz =

tlow coefficient

correction coefficient by expansion of air

arca of opcniug of Orifice (n$)

pressure difference inuuediately in front altd behind the Orifice (nun Act)

weight of air per unit volume inme- diately in front of Orifice (kg/m”)

accelerationduc togravity, nt/s’(9.8 m/s?)

7.4 Air Velocity of Frontside Area (!htf)

Vrr vc1’1‘ =

Fx3600

where

Vwf = frontside area air velocity, (m/s)

Vf7 = rate of air (Same connotation as in 7.3.1 and 7.3.2)

F = frout side area, (II?)

7.5 Weight of Air per IJnit Volume (A) shall be Calculated from the Equation

1.293xH A

= (1 + 0.003 67 x r(l) 760

H = atmospheric pressure, nm of mercury (Room condition)

(mm l-tfg )

IS 13687 : 1993

where tn = atmospheric temperature, OC (obtainable

from Fig. 3).

7.6 The dissipated heat shall be corrected by multiplying the rate of heat dissipated on the waterside (Qw) with the ratio of60 divided by difference in inlet temperatures of water (T,) and air (T,) respectively. T,, 7’, and Q,,. have sanle connotation as in 7.2.

8 TEST RESULTS

8.1 The heat dissipation performance curves shall be plotted as in Amex B.

8.2 The results shall be recorded in accordance with Annex C.

t

0

( Wm3)

FIG. 3 MONOGRAPH OF ‘A’

ANNEX A (Clause 5.3.2)

SIICTION TYPE WIND TUNNEI, AI<HANGEMEN’I

A-l TEST APPARATUS

A-1.1 The test apparatus comprises 21 typical suctiorl tYPe wind tumrl arrangement with coiiiiecting tube and arrangenic tit for nicasureiiieiit for velocity and pressure. The arraogement is show11 in Fig. 4 aud 5.

EXPANDING TUBE

A-l.2 Connecting Tube

When the connecting tube transits from iI circular shape to a circular shape, from a rectangular shape to a circular shape or from a circular shape to a rectaiigul;ir shape, the rules dcscribcd below ShillI be observed :

3o”rrlax.

REDUCING TUBE

FIG. 4 CONNECTXVC; TL’ruzs

5

IS 13687 :

a)

b)

where

L

D

AREA RATIO

- TRANSITION FROM RECTANGLE TO CIRCLE --- - TRANSITION FROM CIRCLE TO RECTANGLE

FIG. 5 LENGTH OF CONNJZCIING TUBE

The angle between the connecting tube and the axial line in the case of the transition from a circular shape to a circular shape shall be not more than 14O for the expanding tube, and not more than 300 for the reducing tube c)

(see Fig. 4).

In the case of the transition from a rectangular

shape to a circular shape (see Fig. S), the rule described in thefollowing equation (discharge side) applies:

In the case of the transition from a circular shape to a rectangular shape (see Fig. 5), the rule described in the following equation (suction side) applies:

For reducing tube (m s 1) : L/D r 1.8

For expanding tube (m r 1) : L/D r 4

For reducing tube (m r 1) : L/D r 1.8

For expanding tube (m s 1) : iiD L 4 L J

m=

= length of connecting tube a =

= inside diameter of measuring duct b =

9t.D area ratio = -

4ab

length of long side of rectangle

length of short side of rectangle

6

IS 13687 : 1993

ANNEX B (Foreword, and Clause 8.1)

HEAT DISSIPATION PERFORMANCE OF RADIATOR

S1 No.

Batch No.

Name of manufacturer

Type Grade

Manufacturer part number

Date of test

Room temperature

Humidity

Atmospheric pressure

Test apparatus

Tested by

oC

percent

mm Hg

HEAT DISSIPATION ‘QUANTITY 1 1

0 5 10 15 20 25

AIR VELOCITY OF THE FRONTAL AREA vaf (m/s)

0 100 200

WATER FLOW VOLUME Vw(l/minI

AN EXAMPLE OF HEAT DISSIPATION PERFORMANCE CURVE

NOTE-The heat dissipation rate in this table is to be corrected for the inlet temperature difference achieved for a difference of 6OT between inlet water temperature and upstream air temperature.

7

/I I , , , I

I- I

I

I I

=I=

t-

t-

I I

=I=

I I

I Standard Mark

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Dot : No. TED 2 (5213 )

Amendments Issued Since Publication

Amend No. Date of Issue Text Affected

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