comprehensive study of biodiesel fuel for hsdi engine
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IC engines using diesel as fuel are used mostly in heavy vehicles
These engines are producing lots polluting gases like CO2,CO,NOX etc. in combustion process which are responsible for global
warming
The fossil fuels are going to exhaust in near future
As result, the research effort in the field of alternative fuel isincreased to face the above problems
Several studies have shown that vegetable oils( bio-diesel) can
be used as alternative fuels in conventional diesel engine
because they have low CO2 emission and the future will be
independent of fossil fuel
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Vegetable oils cant be used in diesel engines directly
because its low temperature fluid properties. By
converting this oil to ester by transesterificationprocess which reduces its viscosity and density its
property will become nearly similar to that of diesel.
The main objective of this research is study of
combustion characteristic of biodiesel in DI enginewhich can be attained by comparing biodiesel with
diesel in wide range of operating conditions
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Bio diesel diesel
Lower heating value [MJ/kg] 36.79 42.84
Stoich A/F ratio 12.6 14.56
Density @ 15 C [kg/m3] 882.5 843.0
Viscosity @ 40 C [mm2/s] 4.304 2.847
Cetane number 52.9 51.0
Acid value [mgKOH/g] 0.29 -
Total glycerol [%] 0.1 -
Free glycerol [%]
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this methodology based on experimental test performed in single
cylinder diesel engines since this type of facility generate more
accurate data compared to multi cylinder engines.
Test engine is peugeot 1.6 lit single cylinder diesel engine which is
equipped with second generation common rail injection system
Bore(mm) 88
Stroke(mm) 76
Displacement volume(mm) 0.399
Connecting rod length(mm) 123.8
Eccentricity (mm) 1
Compression ratio 17:1
Maximum speed(rpm) 4500
Injection system Common rail 160mpa
with solenoid control
Characteristics of single cylinder engine
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Scheme of single cylinder research engine and
complete test cell
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In cylinder pressure
By kistler 6043A
Pressure measured per 25 cycles
quantity of pollutants
Un burned hydrocarbons(UHC). Nox,CO,CO2
By horiba7100
Smoke emission
measurement of soot emissionby AVL smoke meter
unitfilter smoke number
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EGR system is used in this system
While evaluating dilution level EGR rate can be used as a parameter . But
it is different value depending on the chemical composition of the fuel.
The most appropriate parameter to quantify the dilution between the
fresh air and exhaust is the YO2intake
Dilution level
Load level
The oxygen mass consumed during the combustion has been
considered as the most suitable parameter to quantify the load level
The consumed oxygen should be quantified in the following way:
YO2intakeYO2exhaust
YO2 intake = YO2atm(1-EGR)+YO2exhaust.EGR
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ENGINE OPERATING CONDITIONS
Operating
conditions
Injection
pressure(mpa)
Injection
strategy
Injection
timingp /m(BTDC)
A 61 Pilot injection+Main injection
24/14
B 61 Pilot injection +Main injection
16/6
C 61 Main injection -/6
D 100 Pilot injection +Main injection 24/14
All the operating conditions are centered in condition A . Only one
parameter is was modified while moving to any other operating
conditions
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Sample maps for comparison
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Result and discussion
The analysis of the experimental results obtained withconventional diesel and neat biodiesel have been divided
into two progressive and complementary steps
1. Description of combustion performance
2. Insight physical biodiesel combustion phenomena
1.Description of combustion performance
Main parameters to be checked
1. End of combustion angle
2. Indicated efficiency3. Exhaust gas temperature
4. Combustion induced noise
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1.End of combustion angle
The end of combustion angle
defined as the crank angle at which
total heat has been released
The map confirm an early EOC for
biodiesel than that for diesel fuel.
Start of ignition is same for all test
so shorter combustion process
Map comparing EOC observed
using neat biodiesel and diesel fuel
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Ratio maps of CO, UHC,density and adiabatic
temperature
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3. Exhaust gas temperature
Higher indicated efficiency indicates
better conversion of thermal energyinto mechanical energy.
So the thermal energy remaining in
the exhaust gases should be lower
Its results in low exhaust
temperatureIn the low pressure combustion
region the exhaust temperature is
critical even for diesel fuel due to its
negative effects of turbocharger
performance. So the lower exhaust
temperature observed for biodiesel
could be a major draw back for its
applicability in future diesel engines
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4. Combustion induced noise
In case of biodiesel fuel the
combustion noise is slighted
reduced compared to the diesel
fuel.
It takes place during the pre-
mixed combustion stage
It is directly linked with thepressure gradient and it is
estimated by instantaneous
pressure signal
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Physical biodiesel combustion phenomena
Due to complexity of combustion process this analysis is divided into
three phases
1. Ignition delay
2. Premixed combustion
3. Mixing controlled combustion
Ignition delay and premixed combustion isanalyzed in the operating condition C(only main
injection)
mixing controlled combustion is analyzed in the
operating condition A
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1 . Ignition delay and premixed combustion stage
Ignition delay corresponds to beginning of the fuel injection
until the cylinder rise in pressure i.e the start of combustion
ID= SOC - ( SOI + Hydraulic time delay)
This reduction of ignition delay is mainly caused due to
different in physical composition and chemical properties of the
fluid
Higher cetane number also responsible for the shorter ignitiondelay
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Comparison of ignition delay and premised combustion parameters
between biodiesel and diesel in operating condition C
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Neat biodiesel reduces the premixed combustion
period and also the mass of the fuel burnt in premixed
condition
The effect of dilution is evident in this premixed
combustion stage
Because the premixed combustion duration increases
as YO2intake is reducedAs biodiesel shortens the ignition delay it is more
difficult to attain a highly premixed combustion for
reducing NOx emission
Premixed combustion directly related to the ignitiondelay
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From the first hypothesis
Where
FL=flame length
Considering the profile velocity along the axial direction of
gaseous jet
Mixing time=
Integrating this equation we will get
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From this equation two opposite effects has been detected
Stoichiometric air/fuel ratio is higher than the density
ratio and the ST ratio is squared but the density ratio is
square rooted
So mixing time of biodiesel is shorter than that of diesel
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The apparent time of combustion (ACT) for biodiesel is shorter than
that of diesel engine
The lower heating value of diesel requires longer injection duration to
introduce same quantity of energyRelation between the injection time of the two fuels
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The experimental value obtained is 0.87It signifies that it have shorter combustion period
It justifies the early end of combustion
Two situation has been observed i.e for tmixing and
for tinjection
Shorter combustion
periodLonger combustion
period
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conclusionUniversal methodology used based on practical and robust
parameter which includes broad range of operating condition
Biodiesel have faster combustion process and slight increase
in indicated efficiency
Lower emission of CO2 , CO and UHC. But NOx emission
increased for bio diesel
Mixing time shorter and faster combustion , these results
are valid for conventional and low pressure combustionconditions
It is a promising fuel for HSDI diesel engines operating with
current and future contents
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reference
Comprehensive study of biodiesel fuel for HSDI engines
in conventional andlow temperature combustion
conditions
Authors
Bernardo Tormos*, Ricardo Novella, Antonio Garca,
Kevin Gargar
CMT-Motores Termicos, Universidad Politecnica de Valencia, Valencia, ES, Campus de Vera, s/n, Edificio 6D.
Camino de Vera s/n, 46022 Valencia, Espana
Collected from journal ELSEVIER
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