1. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 –
6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 4, July - August (2013) © IAEME
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THEORETICAL ANALYSIS OF COMPRESSION IGNITION ENGINE
PERFORMANCE FUELLED WITH HONGE OIL AND ITS BLENDS WITH
ETHANOL
Sanjay Patil
Associate Professor, Department of Automobile Engineering, Guru Nanak Dev Engineering College,
Bidar- Karnataka
ABSTRACT
In this work, a simulation model based on first law of thermodynamics is used for analyzing
the performance of compression ignition engine fuelled with diesel, straight honge oil and its blends
with ethanol. A Double wiebe’s function is used for computing heat release rate (premixed and
diffusive phase of combustion separately). A Range-kutta fourth order algorithm is used to calculate
temperature at every crank angle during combustion phenomenon. In present investigation, neat
honge oil and its different blends with ethanol namely straight honge oil (H100), HE80 (80% honge
oil and 20% ethanol), HE70 (70% honge oil and 30% ethanol) and HE60 (60% honge and 40%
ethanol) are used as test fuels. It is observed that brake thermal efficiency with HE70 is higher than
other test fuels, however it is lower than diesel at all load conditions. Results of model (BTE & EGT)
for HE70 are validated by conducting experiments and it is found that the simulated values are in
closer approximation with experimental results.
Key words: simulation, compression ignition engine, honge oil, oxides of nitrogen.
1. INTRODUCTION
The demand for energy around the world is continuously increasing due to rapid industrial
and automotive growth. Provisional estimate indicates that the crude oil consumption in India in
2007-08 was about 156 million tones and Indian domestic crude oil production meets about 23% of
the demand, while the rest is met by import [1]. Soaring oil prices and increase in petroleum oil
demand puts heavy financial burden on economies of oil deficient countries due to import of huge
amount of crude oil. This has prompted many researchers worldwide to search for alternative energy
sources which can reduce the dependency on fossil fuel. Great focus is made on use of bio-fuels, as
they are renewable and less polluting due to their closed carbon dioxide cycle. The straight vegetable
oils have high viscosity and poor volatility which results in lower thermal efficiency and higher
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2. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 –
6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 4, July - August (2013) © IAEME
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hydrocarbon, carbon monoxide and smoke emissions, etc [2]. The problem of high viscosity and
poor volatility of straight vegetable oil can be overcome by converting it to a fuel with properties
very close to diesel fuel. Pre- heating, blending the vegetable oil with diesel or alcohol and
converting it to biodiesel by trans-esterification etc. can be used to reduce the viscosity of vegetable
oils. [3] used diesel- biodiesel- ethanol blend for operating diesel engine and they found that the
calorific value, cetane number and flash point blend was lower than diesel. Significant reduction in
emissions like CO and HC and increase in NOx at high engine load were observed compared to
diesel. [4] conducted performance and emissions test on four stroke, four cylinder indirect diesel
engine fuelled with emulsion of diesel with 10% and 15% ethanol and propanol was used as
emulsifier to avoid phase separation. This investigation shows that ethanol addition to diesel reduces
the carbon monoxide, soot and SO2 emissions and increases the NOx emissions. [5] Studied the
effect of addition of water containing ethanol in blend of ethanol-biodiesel and diesel. In this study, 4
v% water containing ethanol is mixed with (65-90%) diesel using (95-30%) biodiesel and 1 v %
butanol as stabilizer and co-solvent respectively. These fuels were tested against those of bio-diesel–
diesel fuel blends to investigate effect of addition of water containing ethanol on performance and
emission characteristics of diesel engine operated generator set. Addition of water containing ethanol
resulted in slight increase in brake specific fuel consumption and reduction in oxides of nitrogen. [6]
Investigated use diesel- ethanol blend for running diesel engine. Palm stearin methyl ester was added
to ethanol in diesel blend to improve the solubility. Addition of ethanol upto 30% shows lower brake
specific fuel consumption and higher brake thermal efficiency as compared to diesel. Higher HC and
CO emissions and lower nitric oxide and smoke emissions were observed with blends as compared
to diesel. [7] conducted performance and emission tests on diesel engine to evaluate the effects of
addition of ethanol to diesel. During their investigations, various blends of diesel and ethanol (5%
and 10% ethanol and remaining diesel) were used for operating the engine. They observed that
increase in proportion of ethanol in blend increases the specific fuel consumption and slight increase
in brake thermal efficiency. With ethanol- diesel blends, Smoke density, NOx and CO emissions
were reduced as compared to diesel, this reduction being higher the higher the percentage of ethanol
in blend. However hydrocarbon emissions were increased with increase in ethanol percentage in
blend.
In present investigation, the concept of ethanol addition to vegetable oil to reduce the
viscosity of honge oil is considered. Neat honge oil (H100), various blends of honge oil and ethanol
namely HE80 (20% ethanol and 80% honge oil), HE70 (30% ethanol and 70% honge oil) and 30%
ethanol and HE60 (40% ethanol and 60% honge oil) used in the present investigation. As Simulation
analysis can yield valuable information about the effect of fuel type and engine operating conditions
on the combustion process, engine performance and emissions, a theoretical model based on first
law of thermodynamics developed by the author of this paper is used[9].
2. SIMULATION AND EXPERIMENTAL PROCEDURE
2.1 Simulation
Simulation model is based on First law of thermodynamics and programmed in MATLAB for
numerical solution of the equations. This model simulates the compression and expansion process
with ideal gas equation and polytropic process. An ignition delay is computed using an empirical
formula developed by Hardenberg and Hase[10]. A Double wiebe function is used for predicting the
rate of heat release during premixed and diffusion phase of combustion separately [11]. The heat
transfer is calculated based on Hohenberg’s equation [12]. The model predicts peak cylinder
pressure, brake thermal efficiency, brake specific fuel consumption, exhaust gas temperature and
emissions like NOx and soot density etc., for all the test fuels.

3. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 –
6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 4, July - August (2013) © IAEME
368
2.2 Experimental setup
Experimental results with TV-1, stationary, single cylinder, water cooled, variable
compression ratio diesel engine developing 3.5 kW at 1500 rpm are used for model validation. The
engine is coupled to a water cooled eddy current dynamometer for loading. Thermocouples are used
for measurement of coolant and exhaust gas temperature. An air box with water manometer is used
to measure air flow rate. A differential pressure transmitter is used for measurement of fuel
consumption. The cylinder pressure data is recorded by using piezoelectric transducer. The engine
specifications and fuel properties used for present analysis are shown in table 1 and 2 respectively.
Table 1. Engine Specifications
Table 2. Fuel Properties
Parameter Specification
Type Four stroke direct injection
single cylinder VCR diesel
engine
Software used Engine soft
Injector opening
pressure
200 bar
Rated power 3.5 kW @1500 rpm
Cylinder diameter 87.5 mm
Stroke 110 mm
Compression ratio 17.5:1
Injection timing 23 degree before TDC
Properties Diesel
(D0)
Honge
(H100)
Ethanol
Viscosity in
Cst (at 30°C)
4.25 40.25 1.2
Flash point(°C) 79 40 21
Fire point(°C) 85 47 25
Calorific value
(kJ/kg)
42000 37200 27569
Specific gravity 0.830 0.925 0.78

4. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 –
6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 4, July - August (2013) © IAEME
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3. RESULTS AND DISCUSSION
Figure.1 BTE v/s Load Figure.2 BSEC v/s Load
Figure.3 EGT v/s Load Figure.4 NOx v/sLoad
Figure.5 Soot v/s Load
0.00E+00
2.00E-07
4.00E-07
6.00E-07
8.00E-07
1.00E-06
1.20E-06
1.40E-06
1.60E-06
1.80E-06
0 25 50 75 100
soot(gm/m^3)
Load (%)
D0
H100
HE80
HE70
HE60
0
5
10
15
20
25
30
0 25 50 75 100
BrakeSpecificEnergy
Consumption(MJ/kW-hr)
Load (%)
D0
H100
HE80
HE70
HE600
5
10
15
20
25
30
0 25 50 75 100
BrakeThermalEfficiency(%)
Load (%)
D0
H100
HE80
HE70
HE60
0
200
400
600
800
1000
1200
0 25 50 75 100
NOx(ppm)
Load (%)
D0
H100
HE80
HE70
HE60
0
50
100
150
200
250
300
350
400
0 25 50 75 100
ExhaustGasTemperature(°c)
Load(%)
D0
H100
H80
H70
H60

5. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 –
6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 4, July - August (2013) © IAEME
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Figure 1 shows the comparison of brake thermal efficiency (BTE) with load for different test
fuels. For all test fuels, the brake thermal efficiency increases with increase in load due to lower heat
losses at higher loads. It is noticed that at full load the brake thermal efficiency with H100, HE80,
HE70, HE60 and diesel is about 21.15%, 22.47%, 23.23%, 21.35% and 24.98% respectively. The
reason for lower thermal efficiency with H100 is due to its higher viscosity, lower calorific value and
poor volatility which results in injection of larger droplets which in turn results in poor combustion
and lower thermal efficiency. The addition of ethanol to vegetable oil reduces the viscosity of the
fuel, increases volatility and the inherent oxygen in ethanol improves the combustion phenomenon.
HE80 and HE70 shows higher brake thermal efficiency as compared to HE100. Further increase of
percentage of ethanol in blend reduces the calorific valve of fuel, takes more amount of fuel to
develop same power, and hence the brake thermal efficiency with HE60 is reduced.
Figure 2 shows variation of brake specific energy consumption with load for various test
fuels. The brake specific energy consumption (BSEC) decreases with increase in load with all the
test fuels due to better combustion and lower heat losses. It is observed that the BSEC with neat
vegetable oil (H100) at full load is 16.23 MJ/kW-hr which is highest among all the test fuels. This
may be due to lower calorific value, higher viscosity and poor atomization of H100. With HE70, at
full load, the BSEC is 14.70 MJ/kW-hr which is lower as compared to H100. At full load HE60
shows BSEC of 15.85 MJ/kW-hr which is higher than HE70. This increase in BSEC with HE60 due
to reduction in calorific value of the blend, lower heat release rate and more energy consumption.
Figure 3 indicates variation in exhaust gas temperature for various test fuels with load. The
exhaust gas temperature (EGT) increases with increase in load for all the tested fuels. This increase
in EGT is due the fact that at higher load, extra amount of fuel is injected to develop more power.
H100 shows highest exhaust gas temperature as compared to diesel and various honge-ethanol
blends. The reason for higher EGT is poor atomization of vegetable oil due to higher viscosity
which causes slow combustion and part of the oil supplied may burn late in cycle. Lower exhaust gas
temperature with blends is due to the better combustion and lower heat losses in exhaust gases.
Figure 4 indicates variation in oxides of nitrogen emissions for various test fuels with load.
A lower oxide of nitrogen emission with H100 is observed due to poor combustion. Addition of
ethanol (upto 30%) to honge oil results in improvement in combustion phenomenon which causes
slight increase in NOx emissions. Dilution of honge oil with 40% ethanol results in lower NOx
emissions as compared to HE70 due to net reduction in heat release because of lower calorific value
of the blend.
Figure 5 shows comparison of smoke density for various test fuels with load. Highest smoke
density is observed with H100 as compared to other test fuels. Lower smoke density with honge oil–
ethanol blends is observed due to improvement in combustion process and reduction in fuel rich
regions in combustible mixture.
4. MODEL VALIDATION
The theoretical results predicted with simulation model for brake thermal efficiency and
exhaust gas temperature for HE70 at various loads is validated by conducting experimental
investigation. It is observed that the predicted results are in closer agreement with experimental
results (Figure 6 and 7)

6. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 –
6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 4, July - August (2013) © IAEME
371
Figure.6 comparison of experimental and Figure.7 comparison of experimental and
simulated brake thermal efficiency for HE70 simulated exhaust gas temperature for HE70
5. CONCLUSION
Based on the results and discussions following conclusions are drawn
• Use of neat honge oil results in inferior engine performance as compared to its blends with
ethanol.
• Among all blends, highest brake thermal efficiency is observed with HE70.
• Reduction in brake thermal efficiency with HE60 as compared to HE70 is observed due
reduction in calorific value.
• Increase in percentage of ethanol in the blend reduces the exhaust gas temperature.
• Increase in NOx and reduction in soot emissions are observed with honge – ethanol blends as
compared to neat honge oil.
ACKNOWLEDGEMENT
I would like to express my gratitude to my guide Dr. M. M. Akarte, National Institute of
Industrial Engineering Mumbai-India for his valuable advice and guidance throughout this work. I
would also like to thank my daughters Shreya patil and Tanvi patil for supporting me during this
work.
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