AT2255-LM

Department of Automobile Engineering, REC / 2010-11

RAJALKSHMI ENGINEERING COLLEGETHANDALAM

DEPARTMENT OF AUTOMOBILE ENGINEERING

AT 2255 – ENGINE PERFORMANCE AND EMISSION TESTING LABORATORY

LAB MANUAL

Cycle I

1. Study of dynamometers

2. Study of emission measuring instruments

3. Valve timing diagram of multi-cylinder engine

a. Multi-cylinder SI engine

b. Multi-cylinder CI engine

4. a. Port timing diagram of two stroke engine

b. Valve timing diagram of single cylinder engine

5. Performance and emissions test on multi-cylinder SI engine

6. Heat balance test on multi-cylinder SI engine

7. Morse test on multi-cylinder SI engine

Cycle II

1. Performance and emissions test on multi-cylinder CI engine

2. Heat balance test on multi-cylinder CI engine

3. Performance and emission test on two-wheeler SI engine

4. Retardation test on IC engine

5. P-θ and P-V diagram of single cylinder diesel engine

1


Cycle I

Ex.No:1 Date:

STUDY OF DYNAMOMETERS USED FOR ENGINE TESTING

Aim:

To study about dynamometers used for finding the engine brake power

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Ex.No:2 Date:STUDY OF EMISSION MEASURING INSTRUMENTS

Aim:

To study about emission measuring instruments

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2


Ex.No:3 Date:

VALVE TIMING DIAGRAM OF MULTI-CYLINDER ENGINE

AIM:To draw the valve timing diagram for the given multi-cylinder engine.

EQUIPMENTS REQUIRED:

1. Measuring tape2. Scale3. Feeler gauge

FORMULA:

Required angle =

Where,L = Distance of the valve opening or closing position marked on flywheel with

respect to their dead centre.C = Circumference of the flywheel

PROCEDURE:

1. First the Inlet and Exhaust valves are identified.

2 The TDC and BDC positions of the piston are found as follows. The flywheel is rotated and when the piston reaches an arbitrarily chosen location in the cylinder a mark is made on the flywheel against a fixed mark on the frame. The flywheel is rotated and when the piston comes to the same mark in its downward stroke a mark is made on the flywheel against the fixed mark chosen. The mid point of these two marks gives the TDC position of the piston and the diametrically opposite position gives the BDC.

3. The correct direction of rotation is found from the sequence of opening and closing of the inlet and exhaust valves.

4. The circumference of the flywheel is determined using the measuring tape.

5. The flywheel is rotated and the point at which the inlet valve starts opening is found out and its position is marked on the flywheel against the fixed mark.

6. Similarly the position at which it closes is also found out.

7. The same procedure is repeated for the exhaust valve.

8. The distances of the opening and closing of the two valves are measured with respect to the dead centre and converted into angles using the relation given above.

3


OBSERVATION:

EventDistance from their

respective dead centres in “cm”

Valve opening period in degrees

Position w.r.to dead

centre

Inlet valve opens

Inlet valve closes

Exhaust valve opens

Exhaust valve closes

RESULT:

The valve timing of the given four stroke engine is found out and the diagram is drawn.

Duration of suction stroke =

Duration of compression stroke =

Duration of expansion stroke =

Duration of exhaust stroke =

Duration of valve overlap =

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4


Ex.No:4 Date:

4a. PORT TIMING DIAGRAM OF TWO STROKE ENGINE

AIM:

To draw the port timing diagram for the given two stroke engine.

TOOLS REQUIRED:

1. Measuring tape2. Scale

FIXING THE DEAD CENTRES:

The flywheel is rotated and when the piston reaches an arbitrarily chosen location in the cylinder a mark is made on the flywheel against a fixed mark on the frame. The flywheel is rotated and when the piston comes to the same mark in its downward stroke a mark is made on the flywheel against the fixed mark chosen. The midpoint of these two marks gives the TDC position of the piston and the diametrically opposite position gives the BDC

IDENTIFICATION OF POSTS:

The port which has more area and is nearer to the TDC is the exhaust port and the other one is the inlet port. Normally the export port is the bigger than the inlet port.

DIRECTION OF ROTATION:

As the port opening and closing are symmetrical about the dead centre any arbitrary direction of rotation may be selected.

FORMULA:

Required angle =



PROCEDURE:

1. The flywheel is turned in any arbitrary direction.2. During the downward traverse position when it just uncovers a port it is marked as the

opening of the port on the flywheel.3. The rotation is further continued until the piston covers the port during its upward

travel.

5


4. A mark is made on the flywheel against the fixed mark. This gives the closing of the port.

5. The same procedure is repeated for other ports also.

OBSERVATION:

EventDistance(L) from their

respective dead centres in “cm”

Valve opening period in degrees

Position w.t.to dead

centre

Exhaust port opens

Exhaust port closes

Transfer port opens

Transfer port closes

RESULT:

Thus the port time for the given two stroke engine is found out and the port timing diagram is drawn.





Scavenging period =

4b. VALVE TIMING DIAGRAM OF SINGLE CYLINDER CI ENGINE

AIM:To draw the valve timing diagram for the given single cylinder diesel engine.

EQUIPMENTS REQUIRED:

1. Measuring tape2. Scale3. Feeler gauge

FORMULA:

6


Required angle =



PROCEDURE:

1. The Inlet and Exhaust valves are identified first.

2 The TDC and BDC positions of the piston are found as follows. The flywheel is rotated and when the piston reaches an arbitrarily chosen location in the cylinder a mark is made on the flywheel against a fixed mark on the frame. The flywheel is rotated and when the piston comes to the same mark in its downward stroke a mark is made on the flywheel against the fixed mark chosen. The mid point of these two marks gives the TDC position of the piston and the diametrically opposite position gives the BDC.

3. The correct direction of rotation is found from the sequence of opening and closing of the inlet and exhaust valves.

4. The circumference of the flywheel is determined using the measuring tape.

5. The flywheel is rotated and the point at which the inlet valve starts opening is found out and its position is marked on the flywheel against the fixed mark.

6. Similarly the position at which it closes is also found out.

7. The same procedure is repeated for the exhaust valve.

8. The distances of the opening and closing of the two valves are measured with respect to the dead centre and converted into angles using the relation given above.

OBSERVATION:

EventDistance from their respective

dead centers in “cm”Valve opening period in

degrees

Inlet valve opens

Inlet valve closes

Exhaust valve opens

Exhaust valve closes

RESULT:

7


The valve timing of the given four stroke engine is found out and the diagram is drawn.





Duration of valve overlap =

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8


Ex.No:5 Date:

PERFORMANCE AND EMISSION TEST ON MULTI-CYLINDER PETROL ENGINE

AIM:To find the load and emission characteristics of the four stroke four cylinder petrol

engine.

APPARATUS REQUIRED:Engine test rig, Tachometer, Stop watch, and emission analyzer

ENGINE DETAILS:Brake Power : P in kW

Bore diameter : D mm

Stroke : L mm

Calorific value : CV kJ / kg

Density of fuel : ρf grams / cc

Orifice Area : A m2

FORMULAE:1. Brake power:

BP = 2πNT / (60 x 1000) kWWhere,N = Number of revolutions of Brake Drum per min

T = Load torque in Nm

2. Total Fuel consumption:

TFC = ( / tf) x ρf x (3600/1000) kg / hr

Where,tf = Time taken to consume cc of fuel in secondsρf = Density of fuel in Grams per cc

3. Specific fuel consumption per hour:

SFC = TFC / BP kg / kW hr

4. Brake thermal efficiency

bth = BP x 3600 x 100 / (TFC x CV) %

5. Brake mean effective pressure:BMEP = BP x 60 /(100 x LAnk) bar

9


Where,n = cycles per minute = N/2 for four stroke enginesk = Number of cylindersL = Stroke length, mA = Area = /4 D2

DESCRIPTION:

The engine is a four stroke, four cylinder, water cooled petrol engine connected with

hydraulic dynamometer. Petrol and air mixture is led through carburetor. Performance test is

done to find the fuel consumption and thermal efficiency at various loading conditions. Engine

emissions are measured with a five gas analyzer which gives the volume % of CO, CO 2 O2, and

the ppm of NOx and UBHC.

PROCEDURE:

1. Engine is started by rotating the crank by means of a crank lever. Engine is allowed to

pick up speed and cooling water is supplied to the engine.

2. Rated load of the engine is calculated.

3. Load is applied gradually in steps till 10% over load is reached.

4. Note down the time taken for 10cc of fuel consumption.

5. Repeat the experiment for different loads.

OBSERVATION:

S.noSpeedrpm

TorqueN-m

Time taken for x cc of

fuel consumption

(Sec)

Exhaust Emissions

CO(%)

CO2

(%)NOx(ppm)

UHBC(ppm)

12345

RESULT:

10


S.no

Brake Power(kW)

TFC(kg/hr)

SFC(kg/kWhr)

Brake thermal efficiency (bth %)

BMEP (bar)

12345

GRAPH:Performance characteristics:

1. Speed vs. Torque2. Speed vs. TFC3. Speed vs. SFC4. Speed vs. bth

5. Speed vs. BMEP

Emission characteristics:1. Speed vs. CO2. Speed vs. CO2

3. Speed vs. NOx4. Speed vs. UHBC

Thus the load test on single cylinder four-stroke vertical diesel engine is performed and

its performance characteristics are plotted.

INFERENCE:

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Ex.No:6 Date:

11


HEAT BALANCE TEST ON MULTI - CYLINDER PETROL ENGINE

AIM:To prepare the heat balance sheet for a four cylinder four stroke, petrol engine.

APPARATUS REQUIRED:

Tachometer, Stop watch, Thermometer, Water flow meter.ENGINE DETAILS:

Brake Power : P in kW

Bore : D mm

Stroke : L mm



Orifice Area : A m2

FORMULAE:


TFC = ( / tf) x ρf x (3600/1000) kg / hr


2. Total heat input:

i =Tfc x CV / 60 kJ / min

Where,

CV = Calorific value of fuel

3. Heat equivalent of brake output:

o = P x 60 kJ/min

Where,

P = Brake power in kilo watts

= 2 NT / 60000 kWWhere,

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N = Speed in rpm

T = Torque in Nm

4. Heat carried by cooling water:

cw = x Cpw (T2 – T1) kJ / min

Where, = cooling water flow rate in kg/min

= (Vw/tw) x ρw x 60

Where, Vw = volume of cooling water measured in litres

tw = time for volume of water measured in seconds

Cpw = Specific heat capacity of water in kJ/kg K

ρw = Density of water = 1 kg/litre

T1 & T2 = temperature of cooling water at inlet and outlet

5. Heat carried by exhaust gas kJ/min

Ex = x Cpg (TEx – TR) kJ / min

Where, TR – Temperature of air inlet

TEx – Temperature of Exhaust gas

Cpg – Specific heat of Exhaust gas in kJ/kg K

= Mass of exhaust gas= + TFC / 60 kg / min

= mass flow rate of air

= Cd x A ( 2g ha ) 0.5 a x 60 kg / min

Where,

Cd - Coefficient of discharge of orifice

A - Orifice area in m2

g - Acceleration due to gravity in m / sec2

ha - head difference in m of air = ( ) x (m / a)

13


h m - manometric difference in centimeters of manometric fluid

m - Density of manometric fluid in kg / m3

a -Density of air in kg / m3

6. Unaccounted heat loss:

Un = i – ( o + cw + Ex)

7. Air / fuel ratio:

= / (TFC/60)

Where,

- Mass of air per min

DESCRIPTION:

The engine is a four stroke Four cylinder in-line petrol engine connected with Hydraulic

dynamometer. The water flow meter is connected to measure the mass flow rate of water. Fuel

consumption can be measured by a burette connected in a three way cock from fuel tank. The

exhaust gas temperature and the cooling water inlet and outlet temperatures can be measured by

the thermocouple provided. An orifice meter is provided in the air inlet tank to measure the

flow rate of air to the engine.

PROCEDURE:

1. Check the cooling water supply and fuel line for air lock.

2. Release the entire load on the engine, Start the engine

3. Take the measurements at various loads and calculate the various quantities.

4. Draw the pie-chart at any two loads.

14


OBSERVATION:

Temperature of air inlet = TR

s.no

Tor

que

(Nm

)

Spe

ed (

rpm

)Manometer Difference

CmTime for cc of

fuel consumption

tf sec

Time for Vw litres of

watertw sec

Exhaust gas

temp TEx

Cooling water to engine

hm

=(h1-h2)

Inlet

T1

Outlet

T2

1

2

RESULT:S.

no

Brake

Power

kW

(P)

Air -

fuel

ratio

Heat input Heat equivalent

of brake output

Heat carried

by cooling

water

Heat carried

by Exhaust

gas

Un-

accounted

losses

i

kJ/min

%o

kJ/min

%cw

kJ/min

%Ex

kJ/min

%Un

kJ/min

%

1

2

Thus the heat balance sheet for the four stroke single cylinder vertical diesel engine is drawn and distribution of heat can be seen from pie chart.

INFERENCE:

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15


Ex.No:7 Date:

MORSE TEST ON MULTI-CYLINDER SI ENGINE

AIM:

To perform the Morse test on the given multi cylinder petrol engine and to find the

mechanical efficiency at given load.

APPARATUS REQUIRED:

Morse test apparatus.

ENGINE DETAILS:

Make : ISUZU

Power :

Speed :

Bore :

Stroke :

Number of cylinders : 4

FORMULAE:

1. Brake power:

BPn = 2 NTn / 60000 kWWhere,

N = Speed in rpm

Tn = Torque in Nm

Brake Power when,

I st cylinder cut off:

BP n-1 = 2 NT n-1 / 60000 kWII nd cylinder cut off:

BPn-2 = 2 NT n-2 / 60000 kWIII rd cylinder cut off:

16


BP n-3 = 2 NT n-3 / 60000 kWIV th cylinder cut off:

BP n-4 = 2 NT n-4 / 60000 kW

Indicated power of

I st cylinderIP1 = BPn – B.P n-1

IInd cylinder

IP2 = BPn – B.P n-2

IIIrd cylinder


IVth cylinder


Total indicated Power

IP = IP1 + IP 2 +IP 3 + IP 4

Total frictional power [F.P]:

FP = IP – BPn

Mechanical efficiency mech:

Mech = BP / IP x 100

Air / fuel ratio:

= / (TFC/60)

Where, = mass flow rate of air

= Cd x A ( 2g ha ) 0.5 a x 60 kg / min

Where, Cd - Coefficient of discharge of orifice



17



h m - manometer difference in centimeters of manometer fluid

m - Density of manometer fluid in kg / m3


DESCRIPTION:

The four stroke four cylinder in-line petrol engine connected with hydraulic

dynamometer air and fuel mixture through the carburetor.

PROCEDURE:

1. Start the engine using the starter.

2. Adjust the speed and load to the given value.

3. Note down the time for 10 cc of fuel consumption and inlet manometer depression.

4. Cut-off the cylinders one by one in-turn, and reduce the load to get the same speed.

Note down the load value.

5. Calculate the A/F ratio, Indicated thermal efficiency and Mechanical efficiency.

OBSERVATION:

Manometer Difference = cm

S.no Cylinder Speedrpm

Torque Nm

1 All firing 25002 1st Cut off 25003 2nd Cut off 25004 3rd Cut off 25005 4th Cut off 2500

RESULT:

The Morse test on given four stroke four cylinder petrol engine is performed and the

Mechanical efficiency is found to be ………….. %

Indicated power is found to be ……………… kW

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18


Cycle II

Ex.No:1 Date:

PERFORMANCE AND EMISSION TEST ON MULTI-CYLINDER DIESEL ENGINE

AIM:To find the load and emission characteristics of the four stroke four-cylinder CI engine.

APPARATUS REQUIRED:

Engine test rig, Tachometer, Stop watch, and emission analyzer

ENGINE DETAILS:


Bore diameter : D mm

Stroke : L mm



Orifice Area : A m2

FORMULAE:1. Brake power:

BP = 2πNT / (60 x 1000) kWWhere,N = Number of revolutions of Brake Drum per min

T = Load torque in Nm


TFC = ( / tf) x ρf x (3600/1000) kg / hr


3. Specific fuel consumption per hour:

SFC = TFC / BP kg / kW hr

19


4. Brake thermal efficiency:

bth = BP x 3600 x 100 / (TFC x CV) %

5. Brake mean effective pressure:

BMEP = BP x 60 /(100 x LAnk) bar

Where,n = cycles per minute = N/2 for four stroke enginesk = Number of cylindersL = Stroke length, mA = Area = /4 D2

DESCRIPTION:The engine is a four-stroke, four-cylinder, water cooled diesel engine connected with

eddy current dynamometer. Performance test is done to find the fuel consumption and thermal

efficiency at various loading conditions. Engine emissions are measured with a five gas

analyzer which gives the volume % of CO, CO2 O2, and the ppm of NOx and UBHC.

PROCEDURE:

1. Engine is started by rotating the crank by means of a crank lever. Engine is allowed

to pick up speed and cooling water is supplied to the engine.

2. Rated load of the engine is calculated.

3. Load is applied gradually in steps till 10% over load is reached.

4. Note down the time taken for 10cc of fuel consumption.

5. Note the emission readings, from five gas analyzer for CO, CO2, NOx and UBHC.

6. Repeat the experiment for different loads and speeds.

OBSERVATION:

S.noSpeedrpm

TorqueN-m

Time taken for x cc of

fuel consumption

(Sec)

Exhaust Emissions

CO(%)

CO2

(%)NOx(ppm)

UHBC(ppm)

12345

20


RESULT:

S.no

Brake Power(kW)

TFC(kg/hr)

SFC(kg/kWhr)

Brake thermal efficiency (bth %)

BMEP (bar)

12345

GRAPH:Performance characteristics:

6. Speed vs. Torque7. Speed vs. TFC8. Speed vs. SFC9. Speed vs. bth

10. Speed vs. BMEP

Emission characteristics:5. Speed vs. CO6. Speed vs. CO2

7. Speed vs. NOx8. Speed vs. UHBC

Thus the load test on single cylinder four-stroke vertical diesel engine is performed and

its performance characteristics are plotted.

INFERENCE:

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21


Ex.No:2 Date:

HEAT BALANCE TEST ON MULTI - CYLINDER PETROL ENGINE

AIM:To prepare the heat balance sheet for a four cylinder four stroke, petrol engine.

APPARATUS REQUIRED:

Tachometer, Stop watch, Thermometer, Water flow meter.

ENGINE DETAILS:


Bore : D mm

Stroke : L mm



Orifice Area : A m2

FORMULAE:


TFC = ( / tf) x ρf x (3600/1000) kg / hr


2. Total heat input:

i =Tfc x CV / 60 kJ / min

Where,

CV = Calorific value of fuel

3. Heat equivalent of brake output:

o = P x 60 kJ/min

Where,

P = Brake power in kilo watts

22


= 2 NT / 60000 kWWhere,

N = Speed in rpm

T = Torque in Nm

4. Heat carried by cooling water:

cw = x Cpw (T2 – T1) kJ / min

Where, = cooling water flow rate in kg/min

= (Vw/tw) x ρw x 60

Where, Vw = volume of cooling water measured in litres

tw = time for volume of water measured in seconds

Cpw = Specific heat capacity of water in kJ/kg K

ρw = Density of water = 1 kg/litre

T1 & T2 = temperature of cooling water at inlet and outlet

5. Heat carried by exhaust gas kJ/min

Ex = x Cpg (TEx – TR) kJ / min

Where, TR – Temperature of air inlet

TEx – Temperature of Exhaust gas

Cpg – Specific heat of Exhaust gas in kJ/kg K

= Mass of exhaust gas= + TFC / 60 kg / min

= mass flow rate of air

= Cd x A ( 2g ha ) 0.5 a x 60 kg / min

Where,

Cd - Coefficient of discharge of orifice


23




h m - manometric difference in centimeters of manometric fluid

m - Density of manometric fluid in kg / m3


6. Unaccounted heat loss:

Un = i – ( o + cw + Ex)

7. Air / fuel ratio:

= / (TFC/60)

Where,

- Mass of air per min

DESCRIPTION:The engine is a four stroke Four cylinder in-line petrol engine connected with Hydraulic

dynamometer. The water flow meter is connected to measure the mass flow rate of water. Fuel

consumption can be measured by a burette connected in a three way cock from fuel tank. The

exhaust gas temperature and the cooling water inlet and outlet temperatures can be measured by

the thermocouple provided. An orifice meter is provided in the air inlet tank to measure the

flow rate of air to the engine.

PROCEDURE:

1. Check the cooling water supply and fuel line for air lock.

2. Release the entire load on the engine, Start the engine

3. Take the measurements at various loads and calculate the various quantities.

4. Draw the pie-chart at any two loads.

24


OBSERVATION:

Temperature of air inlet = TR

s.no

Tor

que

(Nm

)

Spe

ed (

rpm

)

Manometer Difference

cmTime for cc of

fuel consumption

tf sec

Time for Vw litres of

watertw sec

Exhaust gas

temp TEx

Cooling water to engine

hm

=(h1-h2)

Inlet

T1

Outlet

T2

1

2

RESULT:

S.

no

Brake

Power

kW

(P)

Air -

fuel

ratio

Heat input Heat equivalent

of brake output

Heat carried

by cooling

water

Heat carried

by Exhaust

gas

Un-

accounted

losses

i

kJ/min

%o

kJ/min

%cw

kJ/min

%Ex

kJ/min

%Un

kJ/min

%

1

2

Thus the heat balance sheet for the four stroke single cylinder vertical diesel engine is drawn and distribution of heat can be seen from pie chart.

INFERENCE:

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25


Ex.No:3 Date:

PERFORMANCE AND EMISSION TEST ON TWO WHEELER PETROL ENGINE

………………………will be given at the during the lab course……………………………..

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26


Ex.No:4 Date:

RETARDATION TEST ON SINGLE CYLINDER CI ENGINE

AIM:To perform retardation test on the given single cylinder CI engine

APPARATUS REQUIRED:

1. Single cylinder CI engine coupled with dynamometer

2. Tachometer

3. Stop watch

PROCEDURE:

1. Engine is started and allowed to run at rated rpm in no loading conditions.

2. Fuel supply is cut off.

3. Time taken for the speed to decrease to various values is noted down.

4. Again fuel supply is given and engine is brought back to rated speed.

5. The engine load is adjusted using dynamometer to some known value

6. Fuel supply is cut-off and time taken for the speed to decrease to various values is noted down as in the no load condition

7. Curves are plotted b/w Speed and Time on no load as well as load condition

CALCULATION OF FRICTION POWER:

At no load condition, the torque is only due to friction

Tf α ΔN/t1 ………1

At load condition, the torque is the sum of torque due to load and friction torque

27


( TL + Tf ) α ΔN/t2 ...…….2

Where,

Tf - Friction torque

TL - Load torque

t1 & t2 are times for decrease in Speed of ΔN from the Speed Vs Time curves

on no load and on load respectively.

From equation 1 & 2,

Solving,

Therefore, Frictional Power FP =

RESULT

Thus the retardation test is conducted, the results are plotted and the frictional power of

the engine is found.

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28


Ex.No:5 Date:

P-θ AND P-V DIAGRAM ON SINGLE CYLINDER CI ENGINE

29

Documents

AT2255-LM