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Laboratory Manual
THERMALLABORATORY
DEPARTMENT OF MECHANICALENGINEERING
Prepared by:Deepak paliwal
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LIST OF EXPERIMENTS
SERIAL
NO.
NAME OF EXPERIMENT HOURS
1 STUDY OF 2 STROKE/4STROKE PETROL ENGINE 2
2 STUDY OF 2 STROKE/4 STROKE DIESEL ENGINE 2
3 PORT TIMING DIAGRAM OF SINGLE CYLINDER
TWO STROKE SPARK IGNITION ENGINE
2
4 VALVE TIMING DIAGRAM OF A SINGLE
CYLINDER FOUR STROKE COMPRESSION
IGNITION ENGINE
2
5 PERFORMANCE TEST ON RECIPROCATING
AIR COMPRESSOR
2
6 PERFORMANCE TEST ON FOUR STROKE FOUR
CYLINDER PETROL ENGINE
2
7 PERFORMANCE TEST ON FOUR STROKE FOUR
CYLINDER DEISEL ENGINE
2
8 HEAT BALANCE TEST ON FOUR CYLINDER
FOUR STROKE SPARK IGNITION
ENGINE
2
9 HEAT BALANCE TEST ON FOUR CYLINDER
FOUR STROKE COMPRESSION IGNITION
ENGINE
2
10 TO FIND INDICATED HOURSE POWER ON
MULTICYLINDER PETRIL ENGINE BY MORSE TEST
2
11 FLASH AND FIRE POINT TEST BY
CLEAVE LAND OPEN CUP APPARATUS
2
12 STUDY OF WATER TUBE AND FIRE TUBE BOILER 2
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EXPERIMENT NO.1
Aim: - To Study the construction details & working principal of 2-Stroke / 4-Stroke
Petrol Engine.
Apparatus : - Models of 2-Stroke / 4-Stroke Engines.
Theory:- The working Principle of Engines.
2-Stroke (S.I) EnginesIn a 2-Stroke engine, the filling process is accompanied by the change compressed in a
crank case or by a blower. The induction of compressed charge moves out the product
of combustion through exhaust ports. Therefore, no piston stroke is required. Out ofthese 2-strokes, one stroke is for compression of fresh charge and second for power
stroke.
The charge conducted into the crank case through the spring loaded valve when thepressure in the crank case is reduced due to upward motion of piston during the
compression stroke. After the compression & ignition expansion takes place in usual
way.
During the expansion stroke the charge in crankcase is compressed. Near the end of theexpansion stroke, the piston uncovers the exhaust ports and the cylinder pressure drops
to atmosphere pressure as combustion produced leave the cylinder.
Four Stroke (S.I) EngineIn a four stroke engine, the cycles of operations is completed in 4 strokes of piston or 2revolution of crank shaft. Each stroke consists of 180 & hence the fuel cycle consists
of 720 of crank rotation. The 4-Strokes are: -Suction or Intake Stroke : - It starts at, when the piston is at top dead centre & about to
move downwards. The inlet valve is open at that time and exhaust valve is closed due
to suction created by the motion of the piston towards the bottom dead centre, thecharge containing air fuel mixture is drawn into the cylinder. When the piston reaches
BDC the suction stroke ends and inlet valve is closed.
Compression Stroke : - The charge taken into the cylinder during suction stroke iscompressed by return stroke of piston. During this stroke both the valves are closed.
The mixture which fills the entire cylinder volume is now compressed into the
clearance volume. At the end, the mixture is ignited with the help of electrode of sparkplug. During the burning process the chemical energy of fuel is converted to heat
energy. The pressure is increased in the end due to heat release.Expansion Stroke : - The burnt gases escape out and the exhaust valve opens but inlet
valve remaining closed the piston moves from BDC to TDC and sweeps the burnt gasesout at almost atmospheric pressure. The exhaust valve gets closed at the end of this
stroke. Thus, for one complete cycle of engine, there is only one power stroke while
crank shaft makes 2 revolutions.
Exhaust Stroke : - During the upward motion of the piston, the exhaust valve is openand inlet valve is closed. The piston moves up in cylinder pushing out the burnt gases
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through the exhaust valve. As the piston reaches the TDC, again the inlet valve opens
and fresh charge is taken in during next downward movement of the piston and thecycle is repeated.
Construction Details
Cylinder : - It is a cylindrical vessel or space in which the piston makes areciprocating produces.
Piston: - It is a cylindrical component fitted into the cylinder forming the movingboundary of combustion system. It fits in cylinder perfectly.
Combustion Chamber : - It is the space enclosed in the upper part of cylinder, by thecylinder head & the piston top during combustion process.
Inlet Manifold : - The pipe which connects the intake system to the inlet valve ofengine.
Exhaust Manifold : - The pipe which connects the exhaust system to the exhaustvalve of engine.
Inlet / Exhaust Valves : - They are provided on the cylinder head to head to regulatethe charge coming into or going out of the chamber.Spark Plug : - It is used to initiate the combustion process in S.I engines.Connected Rod : - It connects piston & the crank shaft.Crank shaft : - It converts the reciprocating motion of the piston into useful rotary
motion of output shaft.
Gudgeon pins : - It forms a link between connection rod and the piston.Cam shaft : - It controls the opening & closing of the valves.Cam : - They open the valves at the correct tunes.Carburetor : - Used in S.I engine for atomizing & vaporizing and mixture it with air
in varying proportion.
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EXPERIMENT NO.2
Aim : - To study the constructional details & working principles involved in a2-
Stroke & 4-Stroke Diesel Engines.
Apparatus : - Model of 2-Stroke / 4-Stroke Diesel Engine.
Theory : -
Two Stroke (C.I.) EngineIn two stroke engines, the cycle is completed in one revolution of the crankshaft.In 2-stroke engine, the filling process is accomplished by the charge compressed
in crankcase or by a blower. The induction of compressed charge moves out of
the exhaust ports. Therefore, no piston strokes are required for these 2 operations.
Two strokes are sufficient to complete the cycle one for compressing the freshcharge and other for expansion or power stroke.
1. Compression: - The air or charge is inducted into the crankcase through the springloaded inlet valve when the pressure in crankcase is reduced due to upward
motion of piston.
2. Expansion : -During this, the charge in the crankcase is compressed. At the end the piston
uncovers the exhaust ports and cylinder pressure drops to the atmospheric
pressure. Further movement of piston opens the transfer ports, permitting the
slightest compressed charge in the crankcase to enter the engine cylinder.
Construction Details
1. Cylinder : - In it the piston makes a reciprocating process motion.
2. Piston: - It is a cylindrical component fitted into the cylinder forming the
moving boundary of the combustion system. It fits into cylinder.3. Combustion Chamber : - The space enclosed in the upper part of the cylinder,
by the head and the piston top during the combustion process.
4. Inlet/ Outlet ports : - They are provided on the side of cylinder to regulate thecharge coming in and out of cylinder.
5. Fuel Injector : - It injects the fuel in combustion chamber to initiate
combustion process for power stroke.
6. Connecting Rod : - It interconnects crank shaft and the piston.
7. Fly Wheel : - The net torque imparted to the crankshaft during one completecycle of operation of the engine fluctuates cow sing change in angular velocity
of shaft. In order to achiever uniform torque an internal mass is attached to the
output shaft & this is called as fly wheel. Four Stroke (C.I.) Engine
In four strokes C.I. Engine compression ratio is from 16 to 20. During suctionstroke air is inducted. In C.I. engines high pressure. Fuel pump and injectors are
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provided to inject the fuel into combustion chamber and ignition chamber system
is not necessary.
1. Suction : - During suction stroke, air is inducted through inlet valve.2. Compression : - The air inducted is compressed into the clearance volume.3. Expansion : - Fuel injection starts nearly at the end of the compression stroke.
The rate of injection is such that the combustion maintains the pressure constantinspired of piston movement on its expansion stroke increasing the volume. After
injection of fuel, the products of combustion chamber expand.
4. Exhaust : - The piston traveling from BQC to TDC pushes out the products ofcombustion out of cylinder.
Construction Details
1. Cylinder: It is a cylindrical vessel in which a piston makes up and down motion.
2. Piston: It is a cylindrical component making up and down movement in thecylinder.3. Combustion Chamber: It is the portion above the cylinder in which the
combustion of the Fuel-air mixture takes place.
4. Inlet and Exhaust valves: The inlet valves allow the fresh fuel-air mixture toenter the combustion chamber and the exhaust valve discharges the products ofcombustion.
5. Crank Shaft: It is a shaft which converts the reciprocating motion of piston intothe rotary motion.
6. Connecting Rod: The connecting rod connects the Piston with the crankshaft.7. Cam shaft: The cam shaft controls the opening and closing of inlet and Exhaust
valves.8. Fuel Injector: It is located at the top of head to inject the fuel into the combustionchamber.
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EXPERIMENT NO. 3
AIM :-To draw the port timing diagram of a two stroke spark ignition engine.
APPARATUS REQUIRED:
1. A two stroke petrol engine2. Measuring tape
3. Chalk
BRIEF THEORY OF THE EXPERIMENT:The port timing diagram gives an idea about how various operations are taking place in
an engine cycle. The two stroke engines have inlet and transfer ports to transfer thecombustible air fuel mixture and an exhaust port to transfer exhaust gas after combustion.
The sequence of events such as opening and closing of ports are controlled by the
movements of piston as it moves from TDC to BDC and vice versa. As the cycle of
operation is completed in two strokes, one power stroke is obtained for every crankshaft
revolution. Two operations are performed for each stroke both above the piston (in thecylinder) and below the piston (crank case). When compression is going on top side of
the piston, the charge enters to the crank case through inlet port. During the downwardmotion, power stroke takes place in the cylinder and at the same time, charge in the crank
case is compressed and taken to the cylinder through the transfer port. During this period
exhaust port is also opened and the fresh charge drives away the exhaust which is known
scavenging. As the timing plays major role in exhaust and transfer of the charge, it isimportant to study the events in detail. The pictorial representation of the timing enables
us to know the duration and instants of opening and closing of all the ports. Since one
cycle is completed in one revolution i.e. 360 degrees of crank revolution, variouspositions are shown in a single circle of suitable diameter.
PROCEDURE1.Mark the direction of rotation of the flywheel. Always rotate only in clockwise
direction when viewing in front of the flywheel.
2.Mark the Bottom Dead Center (BDC) position on the flywheel with the referencepoint when the piston reaches the lowermost position during rotation of the
flywheel.
3.Mark the Top Dead Center (TDC) position on the flywheel with the referencepoint when the piston reaches the top most position during the rotation of flywheel.
4.Mark the IPO, IPC, EPO, EPC, TPO, and TPC on the flywheel observing thefollowing conditions.
5.Inlet port open (IPO) when the bottom edge of the piston skirt just opens thelower most part of the inlet port during its upward movement.
6.Inlet port close (IPC) when the bottom edge of the piston fully reaches the lowermost part of the inlet port during its downward movement.
7.Transfer port open (TPO) when the top edge of the piston just open the top mostpart of the transfer port during its downward movement.
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8.Transfer port close (TPC) when the top edge of the piston fully reaches the uppermost part of the transfer port during its upward movement
9.Exhaust port open (EPO) when the top edge of the piston just opens the top mostpart of the exhaust port during its downward movement.
10.Exhaust port close (EPC) when the top edge of the piston fully reaches the uppermost part of the exhaust port during its up ward movement
11.Measure the circumferential distance of the above events either from TDC orfrom BDC whichever is nearer and calculate their respective angles.
12.Draw a circle and mark the angles.
OBSERVATION TABLE:
Circumference of flywheel (L) = mm
Sl.No. Description Distance in mm Angle in Degrees1. IPO before TDC
2. IPC after TDC
3. EPO before BDC
4. EPC after BDC
5. TPO before BDC
6. TPC after BDC
FORMULA:
L
Angle = ----- 360
X
Where, LDistance from nearest dead center in mmX- Circumference of the Flywheel in mm
RESULT:
The given two-stroke petrol engine is studied and the Port timing diagram is drawn for
the present set of values.
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EXPERIMENT NO. 4
AIM:-To draw the valve timing diagram of the four stroke compression ignitionengine.
APPAATUS REQUIRED:
1. Experimental engine
2. Measuring tape
3. Chalks
BRIEF THEORY OF THE EXPERIMENT:
The valve timing diagram gives an idea about how various operations are taking place in
an engine cycle. The four stroke diesel engines have inlet valve to supply air inside the
cylinder during suction stroke and an exhaust valve to transfer exhaust gas after
combustion to the atmosphere. The fuel is injected directly inside the cylinder with the
help of a fuel injector.
The sequence of events such as opening and closing of valves which are performed by
cam- follower-rocker arm mechanism in relation to the movements of the piston as it
moves from TDC to BDC and vice versa. As the cycle of operation is completed in four
strokes, one power stroke is obtained for every two revolution of the crankshaft. The
suction, compression, power and exhaust processes are expected to complete in the
respective individual strokes. Valves do not open or close exactly at the two dead centers
in order to transfer the intake charge and the exhaust gas effectively. The timing is set in
such a way that the inlet valve opens before TDC and closes after BDC and the exhaust
valve opens before BDC and closes after TDC. Since one cycle is completed in two
revolutions i.e 720 degrees of crank rotations, various events are shown by drawing
spirals of suitable diameters. As the timing plays major role in transfer of the charge,
which reflects on the engine performance, it is important to study these events in detail.
PROCEDURE:1.Mark the direction of rotation of the flywheel. Always rotate only in clockwise
direction when viewing in front of the flywheel.2.Mark the Bottom Dead Center (BDC) position on the flywheel with the reference
point when the piston reaches the lowermost position during rotation of the
flywheel.
3.Mark the Top Dead Center (TDC) position on the flywheel with the referencepoint when the piston reaches the top most position during the rotation of
flywheel.
4.Identify the four strokes by the rotation of the flywheel and observe themovement of inlet and exhaust valves.
5. Mark the opening and closing events of the inlet and exhaust valves on the
flywheel.
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6. Measure the circumferential distance of the above events either from TDC or
from BDC whichever is nearer and calculate their respective angles.7. Draw the valve timing diagram and indicate the valve opening and closing
periods.
FORMULA:L
Angle = ----- 3600
X
Where,
L - Distance from nearest dead center in mm
X - Circumference of the Flywheel in mm
OBSERVATIONS:
Sl. No. Description Distance in mm Angles in
Degrees
1. IVO Before TDC
2. IVC After BDC
3. EVO Before BDC
4. EVC After TDC
RESULT:The given four-stroke compressed ignition engine is studied and the valve timing diagram
is drawn for the present set of values.
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EXPERIMENT NO. 5
AIM:To conduct a performance test on the two stage reciprocating air compressorand to determine the volumetric efficiency and isothermal efficiencies at
various delivery pressures.
APPARATUS REQUIRED:
1. Reciprocating air compressor test rig.
2. Manometer3. Tachometer
SPECIFICATIONS:Power :
Type : Two stage reciprocating
Cooling Medium : Air
Capacity :
Maximum Pressure :Speed :
BRIEF THEORY OF THE EXPERIMENT:
The two stage reciprocating compressor consists of a cylinder, piston, inlet and exit
valves which is powered by a motor. Air is sucked from atmosphere and compressed inthe first cylinder (Low pressure) and passed to the second cylinder (High pressure)
through an inter cooler. In the second cylinder, air is compressed to high pressure and
stored in the air tank. During the downward motion of the piston, the pressure inside thecylinder drops below the atmospheric pressure and the inlet valve is opened due to the
pressure difference. Air enters into the cylinder till the piston reaches the bottom dead
center and as the piston starts moving upwards, the inlet valve is closed and the pressure
starts increasing continuously until the pressure inside the cylinder above the pressure ofthe delivery side which is connected to the receiver tank. Then the delivery valve opens
and air is delivered to the air tank till the TDC is reached. At the end of the delivery
stroke a small volume of high pressure air is left in the clearance volume. Air at highpressure in the clearance volume starts expanding as the piston starts moving downwards
up to the atmospheric pressure and falls below as piston moves downward. Thus the
cycle is repeated. The suction, compression and delivery of air take place in two strokes /one revolution of the crank
PRECAUTIONS:
1. The orifice should never be closed so as to prevent the manometer fluid beingsucked in to the tank.
2. At the end of the experiment the outlet valve of the reservoir should be opened asthe compressor is to be started against at low pressures so as to prevent excess
strain on the piston.
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EXPERIMENTAL SETUP:
The two-stage air compressor consists of two cylinders of v type. The compressor isdriven by an AC motor. Air is first sucked into the low pressure (LP) cylinder and it is
compressed and delivered at some intermediate pressure. The compressed air is then
cooled in the intercooler and the same is then sucked by the high pressure (HP) cylinder.
Compressed air is the finally discharged to the receiver tank.An orifice plate is mounted on one side of the air tank and which is connected with a
manometer for the measurement of air flow rate. One side of the air tank is attached with
a flexible rubber sheet to prevent damage due to pulsating air flow. A pressure gauge ismounted on the air tank to measure the air tank pressure. The tank pressure can be
regulated by adjusting the delivery valve. A pressure switch is mounted on the air tank to
switch off the motor power supply automatically when the pressure inside the tank raisesto the higher limit and to avoids explosion.
PROCEDURE:
1. The manometer is checked for water level in the limbs.
2. The delivery valve in the receiver tank is closed.3. The compressor is started and allowed to build up pressure in the receiver tank.
4. Open and adjust the outlet valve slowly to maintain the receiver tank pressure constant.5. The dynamometer is adjusted so that the circular balance reads zero when the points at
the motor pedestal coincide. This can be done by operating the hand wheel.
6. Note down the readings as per the observation table.
7. Repeat the experiment for various delivery pressures. This can be done by closing thedelivery valve and running the compressor to build up higher pressure. Ensure the tank
pressure is maintained constant by adjusting the outlet valve before taking the readings.
8. Tabulate the values and calculate the volumetric efficiency and isothermal efficiency.
OBSERVATION TABLE:
Sl.No Deliverypressure
(Kgf /cm2)
Manometer Reading(mm)
Speed TorqueKg.m
h1 h2 h1 - h2 Motor Comp.
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CALCULATION:
h1- h2 w1. Hair = ------------ ------- m
100 air
Where,
Hair = Air head causing the flow, m
h1, h2 = Manometer reading, mmw = Density of water = 1000kg/m
3
air = Density of air, kg/m3
Paair = ---------------- kg/m
3
RT
Where,
Pa = Atmospheric pressure
R = Gas constant for air = 0.287 KJ/Kg.KT = Room temperature K
2. Va = Cd A (2gHair) m3/s
Where,
Va = Actual volume of air compressed m3/s
Cd = Coefficient of discharge =
A = area of orifice = (/4) d2
d = diameter of orifice = m
Va
3. V1 = ------------ TNTP m3/s
TRTPWhere,
V1 = Actual volume of air compressed at NTP m3/s
Va = Actual volume of air compressed m3/sTNTP = 273 K
TRTP = 273 + Room temperature in K
D2 L Nc
4. V2 = ---------------------------- m3/s4 60
Where,
V2 = Theoretical volume of air compressed m3/s
D = Diameter of cylinder = mL = Stroke length = m
NC = Speed of the compressor
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V15. V.E. = ----------- 100 %
V2Where,
V.E = Volumetric efficiencyV1 = Actual volume of air compressed at NTP m3/s
V2 = Theoretical volume of air compressed m3/s
ln (r) Pa Va
6. I.P. = ------------------------------ KW1000
Where,
Iso.P = Isothermal Power
Pa + Pg
r = -------------------Pa
r = Compression ratioPa = Atmospheric pressure N/m2 ( 1.01325 x 105 N/m2)
Pg = Pressure in the tank N/m2 (Pressure gauge reading x 105)
35 2 Nm ( T 9.81)7. I.P. = ------ ------------------------------ motor KW
30 60000Where,
I.P. = Input Power
Nm = Motor speed rpm
T = Torque on the motor Kg.mmotor =
Iso. P.
8. I.E = ---------------- 100
I.P.
Where,I.E. = Isothermal Efficiency
Iso.P. = Isothermal Power
I.P. = Input Power
GRAPH:
1. Gauge pressure Vs Volumetric efficiency
2. Gauge pressure Vs Isothermal efficiency
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RESULT:
The performance test on the given air compressor test rig is conducted and the volumetricand isothermal efficiencies are determined at various delivery pressures and the
characteristic curves are drawn.
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EXPERIMENT NO. 6
AIM:- To prepare variable speed performances test on a four-Stroke, four-
Cylinder Petrol Engine and prepare the curves: (i) BP, BSFC, BMEP,
Torque Vs Speed and (ii) Volumetric Efficiency & A/F Ratio Vs Speed.
APPARATUS USED :-
Four-Stroke, four-Cylinder Petrol Engine Test Rig, Stop Watch, and Digital
Tachometer.
THEORY :-
S.I. Engines are often used for automotive purposes. It is important to know thetorque, brake mean effective pressure, and specific fuel consumption over the
engine working speed range. For this purpose variable speed test at full load and
part load is conducted. To test the park ignition engine at full load the throttle valve
is kept wide open and the brake load is adjusted to obtain the lowest desired speed.
The ignition timing may be set to obtain maximum output at this speed. Rate of fuelconsumption, dynamometer load reading and speed are recorded.
FORMULE USED:-
(i) Torque,
T = 9.81 x W x Reffective N-m.; Where Reffective= (D + d)/2 or (D + t)/2 m, and
W (Load) = ( S1- S2) Kg,
(ii) Brake Power,B P = ( 2N T ) / 60, 000 KW
; Where N = rpm, T= Torque N-m,
(iii)Indicated Power,
IP = n (Pm Lstroke A N ) / 60,000 KW
; Pm = Mean effective pressure N/m2
Lstroke = stroke m, A( cross section of the cylinder) = D2 /4 m2
N = N/2 (four stroke)
(i) Fuel Consumption,
mf= ( 50 ml x 10-6 x fuel) / ( t ) kg/s
Here; 1 ml = 10-3
liters, and 1000 liters = 1 m3
So 1 ml = 10-6
m3
(V) Brake Mean Effective Pressure,BMEP = ( BP x 60,000)/ Lstrokex A x N N/m
2
Lstroke= stroke m, A( cross section of the cylinder) = D2 /4 m2
N = N/2 (four stroke)
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(vi) Brake Specific Fuel Consumption,BSFC = ( mfx 3600 ) / B P Kg/ KW . hr
(vii) Indicated Specific Fuel Consumption,ISFC = ( mfx 3600 ) / I P Kg/ KW .hr
(viii) Indicated Thermal Efficiency,= ( I P x 100 ) / (mfx C.V. ) %
(ix) Brake Thermal Efficiency,
= ( B P x 100 ) / (mfx C.V. ) %
(X) Mass of the air, mair = Cd x Ao g h airwater kg/sWhere Cd(coefficient of discharge) = , air = (pa x 10
2)/ (R x Ta ) kg/m
3,
Ao(area of orifice) = ( do2)/4 m
2, P1 = 1.10325 bar , R = 0.287 KJ/Kg.K,
Ta = ( ta + 273 ) K, ta = Ambient temperatureoC
(XI) Air fuel ratio, A/F = (mair / mfuel ) Kg/Kg of fuel
(XII) Volumetric efficiency, = (Vair x 100 )/ Vs %; where Vair ( volume of air inhaled/sec) = ( mair/air ) m
3/sec.
Vs (swept volume /sec) = n. (Lstroke A N) /60 m3/sec
(XIII) Mechanical efficiency , BP/IP
PROCEDURE:-
1. Before starting the engine check the fuel supply, lubrication oil.
2. Set the dynamometer to zero load.3. Run the engine till it attains the working temperature and steady state condition.
4. Adjust the dynamometer load to obtain the desired engine speed. Note down the fuelconsumption rate.
5. Adjust the dynamometer to the new value of the desired speed. Note and record the
data as in step 4
6. Repeat the experiment for various speeds up to the rated speed of the engine.7. Do the necessary calculations.
OBSERVATIONS:-
No. of Cylinders, n =Brake Drum Diameter, D =
Rope Diameter, d =
Bore, Dbore =Stroke, Lstroke =Engine Displacement, Vswept =
Engine Horse Power, BHP =
Density of fuel (Petrol), fuel =Density of Manometer fluid, water =Calorific value of fuel (Petrol), C.V. = KJ/ Kg
Orifice Diameter, do =
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Co-efficient of Discharge, Cd =
Ambient Temperature, ta =Atmospheric Pressure, Pa = 1.01325 Bar
OBSERVATIONS TABLE :-
Sl.
No.
Engine speed
,
N(rpm)
Dynamometer spring
balance
Reading, (Kg)
Time taken for 50
ml
Fuel , t (sec)
Manometer
Reading
S1 (kg) S2 (kg)
CALCULATION:
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RESULT TABLE:
Sl.
No.
Engine
speed,
N(rpm)
Torque
(N-m)
Brake
Power,
BP
(KW)
Air
consumption
Rate, mair
(kg/hr)
Fuel
Consumption
Rate, mf
(kg/hr)
BSFC
(kg/KW.hr)
BMEP
(N/m2)
A/F
ratio
Mecha.
Efficien
%age
1.
2.
3.
4.
RESULTS:-
Performance curves are plotted and they are similar to the standard performance Curves
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EXPERIMENT NO. 7
AIM:- To prepare variable speed performances test on a four-Stroke, four-
Cylinder Diesel Engine and prepare the curves: (i) BP, BSFC, BMEP,
Torque Vs Speed and (ii) Volumetric Efficiency & A/F Ratio Vs Speed.
APPARATUS USED :-
Four-Stroke, four-Cylinder Diesel Engine Test Rig, Stop Watch, and Digital
Tachometer.
THEORY :-
In the diesel engine, air is compressed adiabatically with a compression ratio typicallybetween 15 and 20. This compression raises the temperature to the ignition temperature
of the fuel mixture which is formed by injecting fuel once the air is compressed.
Diesel fuel is used in C.I engines which is less volatile than gasoline, and will only ignite
under severe pressure and/or very high temperatures. That makes diesel fuel safer to
handle, and reduces the chance of a fire or explosion should the fuel tank rupture in acrash.
Diesels produce large amounts of torque (pulling power) at low engine speeds; a smallfour-cylinder diesel can easily produce as much torque as a larger six-cylinder gasoline
engine. This strong mid-range torque gives diesel cars excellent passing power.
Horsepower ratings for diesels tend to be lower, because horsepower is a function of
speed and diesels tend to have a lower redline (maximum operating speed) than gasolineengines.
FORMULE USED:-
(i) Torque,T = 9.81 x W x R
effectiveN-m.
; Where Reffective= (D + d)/2 or (D + t)/2 m, andW (Load) = ( S1- S2) Kg,
(ii) Brake Power,B P = ( 2N T ) / 60, 000 KW
; Where N = rpm, T= Torque N-m,(iv)Indicated Power,
IP = n (Pm Lstroke A N ) / 60,000 KW
; Pm = Mean effective pressure N/m2
Lstroke = stroke m, A( cross section of the cylinder) = D2 /4 m2
N = N/2 (four stroke)
(ii)Fuel Consumption,mf= ( 50 ml x 10
-6 x fuel) / ( t ) kg/s
Here; 1 ml = 10-3
liters, and 1000 liters = 1 m3
So 1 ml = 10-6 m3
(V) Brake Mean Effective Pressure,
BMEP = ( BP x 60,000)/ Lstrokex A x N N/m2
Lstroke= stroke m, A( cross section of the cylinder) = D2 /4 m2
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N = N/2 (four stroke)
(vi) Brake Specific Fuel Consumption,BSFC = ( mfx 3600 ) / B P Kg/ KW . hr
(vii) Indicated Specific Fuel Consumption,ISFC = ( mfx 3600 ) / I P Kg/ KW .hr
(viii) Indicated Thermal Efficiency,= ( I P x 100 ) / (mfx C.V. ) %
(ix) Brake Thermal Efficiency,= ( B P x 100 ) / (mfx C.V. ) %
(X) Mass of the air, mair = Cd x Ao g h airwater kg/sWhere Cd(coefficient of discharge) = , air = (pa x 10
2 )/ (R x Ta ) kg/m3,
Ao(area of orifice) = ( do2)/4 m2, P1 = 1.10325 bar , R = 0.287 KJ/Kg.K,
Ta = ( ta + 273 ) K, ta = Ambient temperatureoC
(XI) Air fuel ratio, A/F = (mair / mfuel ) Kg/Kg of fuel
(XII) Volumetric efficiency, = (Vair x 100 )/ Vs %
; where Vair ( volume of air inhaled/sec) = ( mair/air ) m3/sec.
Vs (swept volume /sec) = n. (Lstroke A N) /60 m3/sec
(XIII) Mechanical efficiency , BP/IP
PROCEDURE:-1. Before starting the engine check the fuel supply, lubrication oil.
2. Set the dynamometer to zero load.3. Run the engine till it attains the working temperature and steady state condition.4. Adjust the dynamometer load to obtain the desired engine speed. Note down the fuel
consumption rate.
5. Adjust the dynamometer to the new value of the desired speed. Note and record the
data as in step 46. Repeat the experiment for various speeds up to the rated speed of the engine.
7. Do the necessary calculations.
OBSERVATIONS:-No. of Cylinders, n =
Brake Drum Diameter, D =Rope Diameter, d =Bore, Dbore =
Stroke, Lstroke =
Engine Displacement, Vswept =Engine Horse Power, BHP =
Density of fuel (Petrol), fuel =Density of Manometer fluid, water =
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Calorific value of fuel (Petrol), C.V. = KJ/ Kg
Orifice Diameter, do =Co-efficient of Discharge, Cd =
Ambient Temperature, ta =
Atmospheric Pressure, Pa = 1.01325 Bar
OBSERVATIONS TABLE :-
Sl.
No.
Engine speed
,
N(rpm)
Dynamometer spring
balance
Reading, (Kg)
Time taken for 50
ml
Fuel , t (sec)
Manometer
Reading
S1 (kg) S2 (kg)
CALCULATION:
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RESULT TABLE:
Sl.
No.
Engine
speed,
N(rpm)
Torque
(N-m)
Brake
Power,
BP
(KW)
Air
consumption
Rate, mair
(kg/hr)
Fuel
Consumption
Rate, mf
(kg/hr)
BSFC
(kg/KW.hr)
BMEP
(N/m2)
A/F
ratio
Mecha.
Efficien
%age
1.
2.
3.
4.
RESULTS:-
Performance curves are plotted and they are similar to the standard performance Curves
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EXPERIMENT NO. 8
AIM:- To prepare heat balance sheet on four-Cylinder petrol Engine.
APPARATUS USED :-
1.
Multi-Cylinder Petrol Engine Test Rig2. Rig, Stop Watch and Digital Tachometer.
THEORY:-
The thermal energy produced by the combustion of fuel in an engine is not completely
utilized for the production of the mechanical power. The thermal efficiency of I. C.Engines is about 33 %. Of the available heat energy in the fuel, about 1/3 is lost through
the exhaust system, and 1/3 is absorbed and dissipated by the cooling system.
It is the purpose of heat balance sheet to know the heat energy distribution, that is, how
and where the input energy from the fuel is is distributed. The heat balance sheet of an I.C. Engine includes the following heat distributions:
a. Heat energy available from the fuel brunt.b. Heat energy equivalent to output brake power.
c. Heat energy lost to engine cooling water.
d. Heat energy carried away by the exhaust gases.
e. Unaccounted heat energy loss.
FORMULE USED :-
(i) Torque,
T = 9.81 x W x Reffective N-m.; Where Reffective= (D + d)/2 or (D + t)/2 m, and
W (Load) = ( S1- S2) Kg,
(ii) Brake Power,B P = ( 2N T ) / 60, 000 KW
; Where N = rpm, T= Torque N-m,
(iii)Fuel Consumption,
mf= ( 50 ml x 10-6 x fuel) / ( t ) kg/s
Here; 1 ml = 10-3 liters, and 1000 liters = 1 m3
So 1 ml = 10-6 m3
(iv) Heat energy available from the fuel brunt,
Qs = mfx C. V. x 3600 KJ/hr
(v) Heat energy equivalent to output brake power,
QBP = BP x 3600 KJ/hr
(vi) Heat energy lost to engine cooling water,
QCW = mW x CW (tWOtWI ) x 3600 KJ/hr
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(vii) Heat energy carried away by the exhaust gases,
QEG = mfg x Cfg (tfgtair )x 3600 KJ/hr
; where mfg = ( mf+ mair ) kg/s, and mair = Cd Ao g h airwater kg/s
Where Cd(coefficient of discharge) = 0.6, air = (pa x 102 )/ (R x Ta ) kg/m
3,
Ao(area of orifice) = ( do2)/4 m
2, P1 = 1.10325 bar , R = 0.287 KJ/Kg.K,
Ta = ( ta + 273 ) K, ta = Ambient temperatureoC
(viii) Unaccounted heat energy loss
Qunaccounted = Qs{ QBP + QCW + QEG } KJ/hr
PROCEDURE :-
1. Before starting the engine check the fuel supply, lubrication oil, and availability
of cooling water.2. Set the dynamometer to zero load and run the engine till it attain the working
temperature and steady state condition.
3. Note down the fuel consumption rate, Engine cooling water flow rate, inlet and
outlet temperature of the engine cooling water, Exhaust gases cooling water flow
rate, Air flow rate, and Air inlet temperature.
4. Set the dynamometer to 20 % of the full load, till it attains the steady state
condition. Note down the fuel consumption rate, Engine cooling water flow rate,
inlet and outlet temperature of the engine cooling water, Exhaust gases cooling
water flow rate, Air flow rate, and Air inlet temperature.
5. Repeat the experiment at 40 %, 60 %, and 80 % of the full load at constant
speed.
6. Disengage the dynamometer and stop the engine.
7. Do the necessary calculation and prepare th e heat balance sheet.
OBSERVATIONS:-
Engine Speed, N = rpm
No. of Cylinders, n = four
Calorific Value of Fuel, C.V. = KJ/Kg
Specific Heat of Water, C = 4.187 KJ/Kg . K wSpecific Heat of Exhaust Flue Gases, Cfg = 2.1 KJ/Kg . K
Gas Constant, R = 0.287 KJ/Kg . K
Ambient Temperature, ta =oC
Atmospheric Pressure, Pa = 1.01325 Bar
Orifice Diameter, do = m
Co-efficient of Discharge, C =
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Density of fuel (diesel) , fuel = kg/m3
Density of water , water = kg/m3
Brake drum diameter, D = m
Rope diameter ,d = m
Belt thickness, tbelt= m
OBSERVATIONS TABLE :-
Sl.
No.
Engine
speed
N
(rpm)
Dynamometer
Spring
Balance Readings,
(Kg)
Time
taken for
50 ml
fuel,
t (sec)
Engine
cooling
Water
Flow
rate,
mw
(kg/hr)
Engine cooling
Water tem (oC)
Exhaust
Gas
Temp
tfg (o
C)
Mano
meter
Readi
ngtwi
(0C)
Two
(oC)
S1 (kg) S2 (kg)
1.
2.
3.
4.
CALCULATIONS:-
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RESULT TABLE:
SL.
No.
Engine
speed
Brake
power
BP(KW)
Fuel
consumption,
mf( kg/ hr)
Air flow
rate
mair (kg/hr)
Exhaust gas flow
rate,
mfg (kg/hr)
1.
2.
3.
4.
HEAT BALANCE SHEET:
Heat
energy
supplied
KJ/hr %
age
Heat energy consumed
( Distribution)
KJ/hr % age
Heat
energy
Available
From the
fuel
Burnt
(a)Heat energy equivalentto output brake power
(b)Heat energy lost toengine cooling water
(c)Heat energy carriedaway
By the exhaust gases.
(d)Unaccounted heatEnergy loss.
Total --------- 100% Total ------------ 100%
RESULT:
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EXPERIMENT NO. 9
AIM:- To prepare heat balance sheet on four-Cylinder diesel Engine.
APPARATUS USED :-
1.
Multi-Cylinder diesel Engine Test Rig2. Rig, Stop Watch and Digital Tachometer.
THEORY:-
The thermal energy produced by the combustion of fuel in an engine is not completely
utilized for the production of the mechanical power. The thermal efficiency of I. C.Engines is about 33 %. Of the available heat energy in the fuel, about 1/3 is lost through
the exhaust system, and 1/3 is absorbed and dissipated by the cooling system.
It is the purpose of heat balance sheet to know the heat energy distribution, that is, how
and where the input energy from the fuel is is distributed. The heat balance sheet of an I.C. Engine includes the following heat distributions:
a. Heat energy available from the fuel brunt.b. Heat energy equivalent to output brake power.
c. Heat energy lost to engine cooling water.
d. Heat energy carried away by the exhaust gases.
e. Unaccounted heat energy loss.
FORMULE USED :-
(i) Torque,
T = 9.81 x W x Reffective N-m.; Where Reffective= (D + d)/2 or (D + t)/2 m, and
W (Load) = ( S1- S2) Kg,
(ii) Brake Power,B P = ( 2N T ) / 60, 000 KW
; Where N = rpm, T= Torque N-m,
(iv)Fuel Consumption,
mf= ( 50 ml x 10-6 x fuel) / ( t ) kg/s
Here; 1 ml = 10-3 liters, and 1000 liters = 1 m3
So 1 ml = 10-6 m3
(iv) Heat energy available from the fuel brunt,
Qs = mfx C. V. x 3600 KJ/hr
(v) Heat energy equivalent to output brake power,
QBP = BP x 3600 KJ/hr
(vi) Heat energy lost to engine cooling water,
QCW = mW x CW (tWOtWI ) x 3600 KJ/hr
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(vii) Heat energy carried away by the exhaust gases,
QEG = mfg x Cfg (tfgtair )x 3600 KJ/hr
; where mfg = ( mf+ mair ) kg/s, and mair = Cd Ao g h airwater kg/s
Where Cd (coefficient of discharge) = , air = (pa x 102 )/ (R x Ta )
kg/m3,
Ao(area of orifice) = ( do2)/4 m2, P1 = 1.10325 bar , R = 0.287
KJ/Kg.K,
Ta = ( ta + 273 ) K, ta = Ambient temperatureoC
(viii) Unaccounted heat energy loss
Qunaccounted = Qs{ QBP + QCW + QEG } KJ/hr
PROCEDURE :-
1. Before starting the engine check the fuel supply, lubrication oil, and availability
of cooling water.
2. Set the dynamometer to zero load and run the engine till it attain the working
temperature and steady state condition.
3. Note down the fuel consumption rate, Engine cooling water flow rate, inlet and
outlet temperature of the engine cooling water, Exhaust gases cooling water flow
rate, Air flow rate, and Air inlet temperature.
4. Set the dynamometer to 20 % of the full load, till it attains the steady state
condition. Note down the fuel consumption rate, Engine cooling water flow rate,
inlet and outlet temperature of the engine cooling water, Exhaust gases cooling
water flow rate, Air flow rate, and Air inlet temperature.
5. Repeat the experiment at 40 %, 60 %, and 80 % of the full load at constant speed.
6. Disengage the dynamometer and stop the engine.
7. Do the necessary calculation and prepare th e heat balance sheet.
OBSERVATIONS:-
Engine Speed, N = rpm
No. of Cylinders, n = four
Calorific Value of Fuel, C.V. = KJ/KgSpecific Heat of Water, C = 4.187 KJ/Kg . K w
Specific Heat of Exhaust Flue Gases, Cfg = 2.1 KJ/Kg . K
Gas Constant, R = 0.287 KJ/Kg . K
Ambient Temperature, ta =oC
Atmospheric Pressure, Pa = 1.01325 Bar
Orifice Diameter, do = m
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Co-efficient of Discharge, C =
Density of fuel (diesel) , fuel = kg/m3
Density of water , water = kg/m3
Brake drum diameter, D = m
Rope diameter ,d = m
Belt thickness, tbelt= m
OBSERVATIONS TABLE :-
Sl.
No.
Engine
speed
N
(rpm)
Dynamometer
Spring
Balance Readings,
(Kg)
Time
taken for
50 ml
fuel,
t (sec)
Engine
cooling
Water
Flow
rate,
mw
(kg/hr)
Engine cooling
Water tem (oC)
Exhaust
Gas
Temp
tfg (o
C)
Manom
eter
Readingtwi
(0C)
Two
(oC)
S1 (kg) S2 (kg)
1.
2.
3.
4.
CALCULATIONS:-
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RESULT TABLE:
SL.
No.
Engine
speed
Brake
power
BP(KW)
Fuel
consumption,
mf( kg/ hr)
Air flow
rate
mair (kg/hr)
Exhaust gas flow
rate,
mfg (kg/hr)
1.
2.
3.
4.
HEAT BALANCE SHEET:
Heat
energy
supplied
KJ/hr %
age
Heat energy consumed
( Distribution)
KJ/hr % age
Heat
energy
Available
From the
fuel
Burnt
(e)Heat energy equivalentto output brake power
(f) Heat energy lost toengine cooling water
(g)Heat energy carriedaway
By the exhaust gases.
(h)Unaccounted heatEnergy loss.
Total --------- 100% Total ------------ 100%
RESULT:
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EXPERIMENT NO. 10
AIM: To find the indicated power (IP) on Multi-Cylinder Petrol Engine by Morse
test.
APPARATUS USED: -
1. Multi-Cylinder Petrol Engine Test Rig2. Stop Watch,3. Hand Gloves4. Digital Tachometer.
THEORY :-
The purpose of Morse Test is to obtain the approximate Indicated Power of a Multi-
cylinder Engine. It consists of running the engine against a dynamometer at a particularspeed, cutting out the firing of each cylinder in turn and noting the fall in BP each time
while maintaining the speed constant. When one cylinder is cut off, power developed isreduced and speed of engine falls.Accordingly the load on the dynamometer is adjusted so as to restore the engine speed.
This is done to maintain FP constant, which is considered to be independent of the load
and proportional to the engine speed. The observed difference in BP between all
cylinders firing and with one cylinder cut off is the IP of the cut off cylinder. Summationof IP of all the cylinders would then give the total IP of the engine under test.
FORMULE USED :-
(v)Brake Power, BP = WN/ C KW; Where W =Load on the Dynamometer Kg, N = rpm of the Engine,and C =Dynamometer Constant.
(ii) Indicated Power ( IP ) of each Cylinders:IP1 = ( BPTBP234) KWIP2= (BPTBP134) KWIP3 = (BPTBP124) KWIP4 = (BPTBP123) KW
(iii) Total IP of the Engine,
IP = (IP1 +IP2 + IP3 + IP4 ) KW(iv) Mechanical efficiency,
= BPT / IPT
PROCEDURE:-
1. Before starting the engine check the fuel supply, lubrication oil, and availability of
cooling water.
2. Set the dynamometer to zero load.
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3. Run the engine till it attains the working temperature and steady state condition. Adjust
the dynamometer load to obtain the desired engine speed. Record this engine speedand dynamometer reading for the BP calculation.
4. Now cut off one cylinder. Short-circuiting its spark plug can do this.
5. Reduce the dynamo meter load so as to restore the engine speed as at step 3. Record
the dynamometer reading for BP calculation.6. Connect the cut off cylinder and run the engine on all cylinders for a short time. This
is necessary for the steady state conditions.
7. Repeat steps 4, 5, and 6 for other remaining cylinders turn by turn and record thedynamometer readings for each cylinder.
8. Bring the dynamometer load to zero, disengage the dynamometer and stop the engine.
9. Do the necessary calculations.
OBSERVATIONS:-
Engine Speed, N = rpm
No. of Cylinders, n = Four
Calorific Value of Fuel, C.V. = KJ/Kg
OBSERVATIONS TABLE :-
Sl. No. Cylinders
Working
Dynamometer
Reading, (KW)
Brake
Power, BP
(KW)
IP of the cut
off
cylinder,
(KW)
1. 1-2-3-4 ------------------- BPT =
2. 2-3-4 BP234= IP1=
3. 1-3-4 BP134= IP2=
4. 1-2-4 BP124= IP3=
5. 1-2-3 BP123= IP4=
CALCULATIONS:-
RESULT:-
Total IP of the Multi-Cylinder Petrol Engine by Morse Test, IPT = KW
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EXPERIMENT NO. 11
AIM: To find the flash and fire point of the given fuel / oil by cleave land open cup
apparatus.
APPARATUS REQUIRED:
1. Open cup tester
2. Thermometer (0300C)3. Sample of fuel / oil
4. Splinter sticks
DESCRIPTION OF THE EQUIPMENT:
This apparatus consists of a cylindrical cup of standard size. It is held in place in themetallic holder that is placed on a wire gauge and is heated by means of an electric heater
housed inside the metallic holder.
A provision is made on the top edge of the cup to hold the thermometer in position. A
standard filling mark has been scribed on the inner side of the cup and the sample oil isfilled up to this mark. This apparatus is more accurate than Pensky Martons closed cupand it gives sufficiently proclaimed accurate result for most of the practical purposes.
PROCEDURE:
1. Fill the cleaned open cup with the given sample of oil up to the standard fillingmark of the cup.
2. Insert the thermometer in the holder on the top edge of the cup. Make sure thatthe bulb of the thermometer is immersed in the oil and should not touch the
metallic part.3. Heat the sample of fuel / oil by means of an electric heater so that the sample of
oil gives out vapour at the rate of 10 C per minute.
4. When the oil gives out vapours, start to introducing the glowing splinter ( theflame should not touch the oil ) and watch for any flash with flickering sound.
5. Blow out or expel the burnt vapour before introducing the next glowing splinter.This ensures that always fresh vapours alone is left over the surface of the oil and
the test is carried out accurately.
6. Continue the process of heating and placing the glowing splinter at every tendegree of rise in temperature from the first flash till you hear the peak flickering
sound and note the corresponding temperature as the flash point.
7. Continue the heating further after retaining the flash point and watch the firepoint, which is noted when the body of the oil vapour ignites and continue to burn
at least for five seconds.
8. Repeat the test twice or thrice with fresh sample of the same oil until the resultsare equal.
9. Tabulate the observations.
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OBSERVATION TABLE:
Sl.No. Temperature( C ) Observations
RESULT:The flash and fire point test is carried out and the following oil / fuel properties
are found.
The flash point of the given sample fuel / oil is =
The fire point of the given sample fuel / oil is =
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EXPERIMENT No.-12
AIM :-To study the Locomotive Boilers and Babcock & Wilcox Boilers.
APPARATUS USED :- Model of Locomotive and Babcock & Wilcox Boilers.
THEORY :-
A closed vessel in which steam is produced from water by combustion of fuel. According
to A.S.M.E, combustion of apparatus for producing or recovering heat together with theapparatus for transferring the heat so made available to the fluid being heated and
vaporized.The primary requirements of steam generator or boiler are:1. Water
2. Water drum
3. Fuel for heating
TYPES OF BOILERS :-a. Water tube boiler b. Fire tube boiler
In the water tube boilers, the water are inside the tube & hot gases surrounds the tubes.The various water tube boiler are following :
(i) Babcock & Wilcox boiler
(ii) Sterling boiler
(iii) Lamont boiler(iv) Loeffler boiler
(v) Benson boiler
(vi) Velox boilerThe various fire tube boiler are following :
(i) Lancashire boiler
(ii) Locomotive boiler
(iii) Scotch marine(iv) Cochran boiler
LOCOMOTIVE BOILERS
Locomotive boiler is a horizontal multi tubular, natural circulation, artificial draft, internally
fired, fire tube boiler; Locomotive boilers are manufactured in both portable or mobile and
stationary types. A locomotive boiler produces steam upto to pressure of 25 bar and the steaming
rate as high as 55 to 75 kg per square meter of the heating surface per hour upto 7000 kg per hour.
Locomotive boilers are designed to meet the sudden and fluctuating demands of steam due tovariation in power output. Locomotive boilers are used in railway engines, road rollers and
haulage engines. They are also used in stationary service power plants where semi portability is
desired.
CONSTRUCTION OF LOCOMOTIVE BOILERS
The main parts of the Locomotive Boiler are fire box, boiler shell and smoke box. The firebox
which forms the furnace is constructed by extending the boiler shell downward from the sides at
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its rear end. The annular space left in between the furnace wall and downward extension of the
boiler shell is also connected with the water space in the barrel. The grate over which the fuel
burns is mounted sloping downwards in the furnace. Beneath the grate there is an ash pit for
collecting the ashes. The hot gases rising from the grate are deflected by the fire brick arch which
ensures more uniform and proper heating because the deflected hot gases come in contact with
the entire heating surface of the fire box.
The boiler barrel is a cylindrical shell and it accommodates a large number of flue tubes which
connect the furnace with the smoke box. The flue tubes are made of two sizes. Super heater tubes
are inserted into the large diameter flue tubes. The steam dome located at the top of the
cylindrical shell is meant to collect the dry steam. The smoke box is connected to the boiler barrel
at its front end. A super heater header which distributes the steam to the super heater tube is
mounted inside the smoke box. The chimney located at the top of the smoke box is made very
short in order to avoid its striking with the tunnels and under bridge when the locomotive passes
through the tunnels and below the under bridge. Since the chimney is short, its reduces the
draught. But the motion of the locomotive creates a strong artificial forced draft. In some
locomotive boilers artificial draught is also created by passing the exhaust steam from the engine
cylinder into the smoke box. Since the exhaust steam will be at low pressure, a pressure
differential will be set up between the smoke box and the fire box which causes the drawl of the
hot gases through the fire tubes and make their exit through the chimney. This causes the drawl of
air through the grate. The smoke box door provided at its front end facilitates cleaning inside the
smoke box.
WORKING OF LOCOMOTIVE BOILER
Water is filled nearly to three fourth of the barrel space so as to submerge completely the fire box
and the flue tubes, and also to fill the annular space left in between the furnace wall and the
downward extension of the boiler shell. The coil is charged into the furnace through the fire doorand burnt over the grate. The hot gases rising from the grate are deflected by the fire brick arch so
as to heat the entire fire box more uniformly, and then pass through the flue tubes from the
furnace to the smoke box. The heat is transferred from hot gases through the walls of the furnace
and also through the walls of the flue tubes. From the smoke box the hot gases escape through the
chimney. The steam evolving from the surface of the water is accumulated in the steam space and
also in the steam dome. Inside this steam dome there is a throttle valve connected to the main
steam pipe. This throttle valve is regulated by the regulating rod to allow the required quantity of
the steam to pass. For superheating the steam so as increase the thermal energy, the steam is
passed from the main steam pipe to the super heater header and then through the super heater
tubes which are in the bigger flue tubes. The steam passing through the super heater a tube is
further heated by the hot gases passing in the flue tubes and gets superheated. The superheated
steam from the super heater tubes are returned to the super heater header from there it is passed to
the steam engine cylinders.
BABCOCK & WILCOX BOILER :-
The water tube boilers are used exclusively, when pressure above 10bar and capacity inexcess of 7000kg./hr. is required.
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DIMENSION & SPECIFICATIONS :
Diameter of the drumLength of the drum
Size of the water tubes
Size of the super heater tubes
Working pressureSteaming capacity
Efficiency
CONSTRUCTION & WORKING :- Babcock & Wilcox boiler with longitudinal
drum
It consists of a drum connected to a series of front end and rear end header by short risertubes. To these headers are connected a series of inclined water tubes of solid drawn mild
steel. The inclination of tubes to the horizontal is about 15 degree or more. A hand hole is
provided in the header in front of each tube for cleaning & inspection of tubes. A feed
valve is provided to fill the drum and level of water indicates by water level indicator.
Fire is burnt on the grate. The hot gases are forced to move upwards between the tubes bybaffle plates provided. The water from the drum flows through the inclined tubes via
down take header & goes back into the steam the steam space of the drum. The steamthen enters through the anti- priming pipe and flows in the super heater tubes where it is
further heated and is finally taken out through the main stop valve and supplied to the
engine when needed.
In the cross drum there is no limitation of the number of connecting tubes. In case ofcross drum:
Pressure --------------------------
Steaming capacity --------------
APPLICATIONS :-
The steam generated is employed for the following purpose :
1. For generating power in steam engines or steam turbines.2. In the textile industries for sizing & bleaching etc. and many other industries like
sugar mills, chemical industries.
3. For heating the building in cold weather & for producing hot water supply.4. Steam turbine propelled ships and other marine vessels.
5. Agriculture field machineries, saw mills etc.
6. Steam locomotive.7. To study steam to the steam engine for driving industries hoists, road rollers, in road
constructions, pumps in coal mine.
PRECAUTIONS :-
Do not feed water fully the drum. Water level should be checked properly. Pressure should not be over the rating pressure. Clean the boiler time to time. Boiler operator should be present there.