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http://www.scirp.org/journal/wjet ISSN Online: 2331-4249

ISSN Print: 2331-4222

Investigation of Performance and Combustion

Characteristics of DI Diesel Engine Fuelled

with Ternary Fuel Blend at Different

Injection Pressure

Pani Sharanappa, Mallinath C. Navindgi

Department of Mechanical Engineering, PDA College of Engineering, Kalburgi, India

Abstract

The depletion of fossil diesel fuels, global warming concerns and strict limits on regulated pollutant emissions are encouraging the use of renewable fuels. Biodiesel is the most used renewable fuel in compression ignition (CI) engine. The majority of literature agrees that the particulate matter (PM), unburnt total hydrocarbons (THC) and carbon dioxide (CO) emission from biodiesel are lower than from conventional diesel fuel. One of the most important rea-sons for this is the oxygen content of the biodiesel. This induces a more com-plete and cleaner combustion process. In addition to this the absence of aro-matic compounds in biodiesel leads to particulate matter reduction with re-spect to diesel fuel. The potential emission benefits induced by the presence of oxygen in fuel molecules has increased the interest in using the bio-alcohols fuel blends in CI engines such as ethanol. Although alcohols are more suitable for blending with diesel fuel, properties like lubricity, viscosity, stability, heat-ing value and cetane number of diesel-alcohol (Diesohol) still require im-provement. One of the techniques is addition of biodiesel which can improve all of these properties forming diesel-biodiesel-alcohol (ternary) blends. The blends of diesel-biodiesel-ethanol can be used in the existing CI engines without any major modifications and most significant result of using this blend is the lower emission with almost the same performance as of diesel fuel alone. The present study focused on investigation of performance and com-bustion characteristics of ternary fuel blend in DI diesel engine operating at different injection opening pressure (IOP). The different injection opening pressures are: 180 bar, 200 bar and 220 bar.

Keywords

Diesohol, Ternary Fuel Blends, Aromatic Compounds, Injection

How to cite this paper: Sharanappa, P. and Navindgi, M.C. (2017) Investigation of Performance and Combustion Characteris-tics of DI Diesel Engine Fuelled with Ter-nary Fuel Blend at Different Injection Pres-sure. World Journal of Engineering and Technology, 5, 125-138.

https://doi.org/10.4236/wjet.2017.51011

Received: January 9, 2017 Accepted: February 25, 2017 Published: February 28, 2017

Copyright © 2017 by authors and Scientific Research Publishing Inc. This work is licensed under the Creative Commons Attribution International License (CC BY 4.0).

http://creativecommons.org/licenses/by/4.0/

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Opening Pressure, CI Engines

1. Introduction

The ongoing investigations and the already found analysis about the fractional replacement of fossil diesel fuel with the combination of biodiesel and ethanol in compression ignition engines found to be successful as this blend has the similar fuel properties like the commercial diesel fuel with high bio fuel content. Many scientists and investigators have studied this blend with different proportions of diesel, biodiesel and ethanol to study its suitability as a fuel in existing CI en-gines [1]. It was found from the detailed literature survey that a maximum of 20% biodiesel and 10% of ethanol can be added to the diesel fuel effectively. Many investigators have used soybean, rapeseed oil, Pongamia oil and waste cooking oil as an emulsifier in diesohol blend [2]. Little literature is available on the use of methyl esters of Rice bran oil and Mahuva oil blend with diesohol, hence these two biodiesels are chosen for analysis. However a detailed analysis of performance, combustion characteristics of diesel-biodiesel-ethanol blend in di-esel engines appears to be scarce. Thus the aim of this work is to investigate the optimum engine parameters at which the ternary blends can be used effectively. The engine is also tested at different injection opening pressure. A lot of work has been carried on optimization of ternary blend using soybean, palm, rape seed, Jatropha biodiesels, but a very little information is available using mahuva biodiesel. So in this work an effort is done to determine experimentally the per-formance and combustion characteristics of the direct injection diesel engine fu-elled with diesel-mahuva biodiesel blend with ethanol as an additive. The engine is also tested at different injection opening pressure.

1.1. Scope of Biodiesel as an Alternative Fuel

Biodiesels can be defined as “the mono alkyl esters of long chain fatty acids de-rived from lipid feed stock, such as vegetables and animal fats, for its use in di-esel engines” [3]. Neat vegetable oils are not ideally suitable for compression ig-nition engines as a fuel because of durability and operational problems. The du-rability problems such as deposit formation, lubrication oil dilution and choking of injector tip. The Operational problems such as ignition, combustion and abil-ity to start may restrict the use of neat vegetable oils [4]. These problems are mainly due to higher viscosity and density, which leads to poor atomization, bigger droplets, longer jet spray penetration, and low volatilities. Many efforts have been carried out to reduce the viscosity of the vegetable oils. Two different methods are used to reduce the viscosity of the oils:

1) Engine modification: Heating the fuel line, injection system modification, duel fuelling.

2) Fuel modification: Blending, Pyrolysis and micro emulsion.

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any ratio. It emits no sulphur oxides, a pollutant that causes acid rain and burns the lungs, eyes and throat. Global warming can be reduced by reducing the emission of carbon dioxide by using the biodiesel. Some of the advantages of using biodiesel are, absence of sulphur, absence of aromatics, lower hydrocarbon emissions, reduction of smoke and soot and reduction i carbon monoxide [5].

Biodiesel can be mixed with diesel fuels in any proportion; the blend can sta-ble even at low temperatures. It is advisasta-ble that biodiesels can’t be stored more than six months, similar to fossil diesel fuel. It can be stored in a closed contain-er with air tight heading protecting from direct sun light, moisture and cold weather. Biodiesel separates from diesel fuel at lower temperatures and it can clog the fuel flow line, but as it warms up it liquidates [6].

Even though it has got many more advantages, it cannot be used as a sole fuel for compression ignition engine, because of its lower heating value, higher den-sity and higher emission of NOx. The higher emission of NOx is due to higher exhaust gas temperature. Due to lower heating value of biodiesel the efficiency of the engine reduces.

1.2. Scope of Alcohols as an Alternative Fuel

Alcohol is a bio-product extracted with the help of chemical process. Raw ma-terial for alcohol is; grains, agricultural wastes, starch, sugar and wood. Ethanol and methanol are two important alcohols. Ethanol has been used in Germany and France as early as 1894 and Brazil has utilized ethanol as a fuel since 1925 [7].

Ethanol consists of carbon, hydrogen and oxygen, since it consists of oxygen ethanol burns cleaner than fossil fuels. Emissions from ethanol are very less, particularly NOx emission which is not possible with biodiesel. Ethanol can be produced from agricultural wastes, grains, dated soda, cheese whey, grains or any other material which contains starch or sugar. Ethanol can be called as re-newable fuel as it is produced from crops. Use of ethanol in the compression ig-nition may cause some problems such as:

1) More amount of ethanol is required to produce the rated power. 2) Low boiling point and high vapour pressure may cause vapour lock. 3) High latent heat of ethanol leads to poor mixing with air, hence need heat-ing of intake manifold.

4) Low cetane number leads to poor combustion.

The above problems can be overcome by blending the ethanol with diesel fuel. The blend of diesel and ethanol is called as diesohol, which is the best alternative fuel for dual fuel engines. Anhydrous ethanol makes homogeneous mixture with diesel fuel but hydrous ethanol with diesel makes phase separation. This can be solved by adding emulsifier or surfactants. The maximum percentage of ethanol in the diesel fuel blend is around 15% [8].

2. Experimental Work

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and combustion parameters. The performance parameters like brake thermal ef-ficiency (BTE), brake specific fuel consumption (BSFC), exhaust gas temperature (EGT) were determined. The combustion parameters like, cylinder pressure, mass fraction burn, cumulative heat release rate and net heat release were de-termined. The engine was run at different injection opening pressure. Different injection opening pressure: 180 bar, 200 bar and 220 bar, injection opening pressure was set by adjusting the compression of the spring and calibrated. Ta-ble 1 gives detailed Engine specifications:

3. Materials and Methodology

The various materials used for conducting experiment are, pure diesel fuel (D100), pure biodiesel (B100), ternary fuel blends; ternary fuel blends were pre-pared by blending different proportion of diesel fuel, Mahuva biodiesel and ethanol by volume. The different prepared ternary fuel blends are: D70B20E10 (B20), D60B30E10 (B30) and D50B40E10 (B40). E10 indicates 10% of ethanol is used as an additive in the blend. The basic fuel properties of fuels were deter-mined according to ASTM standards in Bangalore test house, Bangalore and IISC, Bangalore. The engine was run with different injection pressure (IOP) 180 bar, 200 bar and 220 bar; IOP was set by adjusting the spring pressure and was calibrated in the lab.

4. Results and Discussions

4.1. Performance Characteristics

The performance characteristics discussed in this section are brake thermal effi-ciency (BTE), brake specific fuel consumption (BSFC) and exhaust gas tempera-ture (EGT).

4.1.1. Brake Thermal Efficiency

[image:4.595.208.538.538.733.2]

Figure 1 shows the variation of brake thermal efficiency of pure diesel (D100),

Table 1. Engine specifications.

Specifications Details Engine type, model Kirloskar, TV-1

Number of strokes 4

Power output 5.2 kW/7BHP Bore x Stroke 87.5 mm × 110 mm Number of cylinders One

Constant speed 1500 RPM

Orifice diameter 20 mm

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[image:5.595.209.536.73.215.2]

Figure 1. Brake thermal efficiency with BP.

biodiesel (BD100), and ternary fuel blends (B20, B30, B40) with brake power. BTE increases with increase in load it’s due to better combustion at higher loads. BTE of the fuels follow the same trend at all loads. The BTE of D100, BD100, B20, B30 and B40 at full load are 28%, 25%, 26%, 27% and 25% respectively. The BTE of the ternary fuel blends is almost same as that of pure diesel fuel; it may be due to leaner combustion and higher ignition delay of biodiesel and ethanol. Further increase of biodiesel proportion in the ternary blend decreases the BTE; it may be due to lower heating value, higher density and viscosity of the biodie-sel. Hence ternary fuel blends with limited biodiesel proportion in the blend can be effectively used as an alternative fuel.

Figure 2 shows the variation of brake thermal efficiency of different fuels at different injection opening pressures (IOP) at full load. The brake thermal effi-ciency increases when the IOP increases from 180 bar to 200 bar, it is because of increased IOP leads to better atomization and complete combustion of the fuel, further increase of IOP to 220 bar leads to decrease in brake thermal efficiency, it may be due to higher IOP leads to more vaporization of the fuel and sudden rise of combustion temperature which leads to more heat loss. Hence ternary fuel blends with 200 bar IOP has better thermal efficiency. B30 at 200 bar IOP has same BTE as diesel fuel.

4.1.2. Brake Specific Fuel Consumption

Figure 3 shows the variation of brake specific fuel consumption (BSFC) of pure diesel fuel (D100), biodiesel (B100), ternary fuel blends (B20, B30, B40) with BP. BSFC decreases with increase in load it’s due to better combustion at higher loads. BSFC of the fuels follow the same trend at all loads. The BSFC of the ter-nary fuel blends is slightly more than that of the diesel fuel and mahuva biodiesel it is because of lower heating value of the biodiesel and ethanol in the ternary fuel blends. Among the ternary fuel blends B30 has lowest fuel consumption.

Figure 4 shows the BSFC of various fuels and fuel blends at different Injection pressures. Figure shows that BSFC decreases with increase in IOP; it is due to higher IOP leads to better atomization and through mixing of fuels, which leads to complete combustion and hence lower fuel consumption. At 220 bar IOP the BSFC is 1 kg/kW-hr less than at 180 bar IOP for modes of fuel. Hence

0 5 10 15 20 25 30 35

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BP (kW)

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[image:6.595.210.538.75.245.2] [image:6.595.204.542.115.660.2]

Figure 2. Brake thermal efficiency with IOP at full load.

Figure 3. Brake specific fuel consumption with BP.

Figure 4. Brake specific fuel consumption at different IOP.

ternary fuel blends at higher IOP are suitable for engines.

4.1.3 Exhaust Gas Temperature

Figure 5 shows the variation of EGT of pure diesel fuel (D100), biodiesel

22

23

24

25

26

27

28

29

30

D100

BD100

B20

B30

B40

Br

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Fuel blend

180

200

220

0 0.5 1 1.5 2 2.5 3 3.5 4

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D100 BD100 B20 B30 B40

0 0.1 0.2 0.3 0.4 0.5 0.6

D100 BD100 B20 B30 B40

BS

FC

(kg

/kW

h)

FUEL BLENDS

[image:6.595.208.537.276.471.2] [image:6.595.209.534.504.646.2]
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(BD100), ternary fuel blends (B20, B30, B40). It is observed from the graph that exhaust gas temperature increases with increase in load; it is due to higher com-bustion temperature. EGT of ternary fuel blends are almost same as of diesel fuel at all load conditions; it is due to presence of ethanol which has high evaporative heat and low heating values, which takes off the heat from combustion chamber. At full load the EGT of all modes of fuel is around 450˚C.

Figure 6 shows the variation of EGT of various fuels at different IOP at full load. It shows that EGT reduces with increase in IOP; it is due to better atomiza-tion, complete combustion of the fuel and effective heat conversion, which leads to less heat escape in to the exhaust gas. Hence higher IOP are preferable for ternary fuel blends concerned to EGT.

4.2. Combustion Characteristics

The combustion characteristic discussed in this section is cylinder pressure, mass fraction burn rate, cumulative heat release and net heat release.

[image:7.595.213.536.367.716.2]

4.2.1. Cylinder Pressure

Figure 7 shows the peak cylinder pressure of the engine with respective crank angle.

Figure 5. Exhaust gas temperature with BP.

Figure 6. Exhaust gas temperature at different IOP. 0

50 100 150 200 250 300 350 400 450 500

0 1 2 3 4 5.2

EX

HA

U

ST

G

AS T

EM

P.

(o

C)

BP (kW)

D100 BD100 B20 B30 B40

0 100 200 300 400 500

D100 BD100 B20 B30 B40

Ex

ha

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t g

as

te

mp

era

tu

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(d

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Fuel blend

[image:7.595.208.537.368.540.2]
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For D100, BD100, B20, B30 and B40 the peak cylinder pressure is 68.48, 70.20, 68.18, 68.46 and 68.40 bar respectively and occurs at the same crank angle 370 deg. The peak cylinder pressure of the ternary fuel blends is same as D100; it is due to the presence of ethanol in the ternary blend leads to superior fuel mixing and atomization which leads to lower ignition delay (ID) of the ternary fuel blends. It shows that, peak cylinder pressure increases with increase in biodiesel proportion in the ternary fuel blend; it is due to higher cetane number and lean-er combustion of biodiesel.

Figures 8-10 show the peak cylinder pressure at different injection opening pressure (IOP), 180 bar, 200 bar and 220 bar respectively. As IOP increases peak pressure decreases, it is due to higher IOP leads to shorter ignition delay, which in turn causes incomplete combustion and hence combustion efficiency falls down. B100 has highest peak pressure of 70.20 bar at 180 bar. It is due to leaner

Figure 7. Cylinder pressure with crank angle.

[image:8.595.205.540.282.759.2]

Figure 8. Cylinder pressure with CA at 180 bar IOP.

Figure 9. Cylinder pressure with CA at 200 bar IOP. 0

20 40 60 80

1 39 77 115 153 191 229 267 305 343 381 419 457 495 533 571 609 647 685

PR

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D100 BD100 B20 B30 B40

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PR

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CYLINDER PRESSURE AT 180 BAR IOP

D100 BD100 B20 B30 B40

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PR

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CYLINDER PRESSURE AT 200 BAR IOP

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[image:9.595.212.538.74.199.2]

Figure 10. Cylinder pressure with CA at 220 bar IOP.

combustion and higher cetane number of the biodiesel. Among the ternary fuel blends B30 at 180 bar IOP has highest peak cylinder pressure which is almost same as D100.

4.2.2. Mass Fraction Burn

Figure 11 shows the variation of mass fraction burn in percentage with crank angle of various test fuels; D100, BD100, B20, B30 and B40. MFB curves follow the S-shape and all the fuels follow the same trend. MFB curves of D100, B20 and B30 coincides, it means both the fuels have same CD and heat release rate of D100. The MFB curves for B100 and B40 are distinct from that of D100, which means they have higher CD. So B20 and B30 are the better blends as compared to B100 and B30, the similar results were obtained by B. K. Venkanna, et al.

Figures 12-14 show variation of MFB with crank angle at 180 bar, 200 bar and 220 bar IOP respectively. All the graphs follow the same trend at 180 and 200 bar IOP but little deviation is found at 220 bar IOP. At 200 bar IOP the MFB curve of B30 coincides with D100, which means B30 has similar burning rate as that of pure diesel fuel. Hence B30 is suitable ternary fuel at 200 bar IOP com-pared with other fuels.

4.2.3. Cumulative Heat Release

Figure 15 shows the variation of cumulative heat release of D100, BD100, B20, B30 and B40 with crank angle at 180 bar injection pressure. The graph shows all the modes of fuels fallow the same trend of heat release, and the maximum cu-mulative heat release for all the fuels is around 1.3 kJ. The maximum crank angle at which the maximum cumulative heat is released is around 480 deg. Hence the cumulative heat release of ternary fuel blend is almost same as that of pure diesel fuel; it may be due to leaner combustion of the biodiesel fuel and higher latent heat of ethanol.

Figures 16-18 show the cumulative heat release (CHR) at different injection pressure, 180 bar, 200 bar and 220 bar. The graph shows CHR increases with in-crease in injection pressure it may be due to higher IOP, which leads to more atomization and ensures complete combustion.

4.3.4. Net Heat Release Rate

Figures 19-21 show variation of net heat release at different injection pressure 0

20 40 60 80

1 41 81 121 161 201 241 281 321 361 401 441 481 521 561 601 641 681

PR

ES

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CYLINDER PRESSURE AT 220 BAR IOP

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[image:10.595.224.524.75.189.2] [image:10.595.228.524.220.361.2]

Figure 11. Variation of mass fraction burn with CA of various fuels.

Figure 12. Variation of mass fraction burn with crank angle at 180 bar.

Figure 13. Variation of mass fraction burn with crank angle at 200 bar.

Figure 14. Variation of mass fraction burn with crank angle at 220 bar. -20 0 20 40 60 80 100 120

-10 -7 -4 -1 2 5 8 11 14 17 20 23 26 29

M ASS F RA CT IO N B UR N (% ) CRANK ANGLE D100 BD100 B20 B30 B40 -20 0 20 40 60 80 100 120

-12 -9 -6 -3 0 3 6 9 12 15 18 21 24 27

M ASS F RA CT IO N B UR N (% ) CRANK ANGLE

MASS FRACTION BURN RATE AT 180 BAR IOP

D100 BD100 B20 B30 B40 -200 20 40 60 80 100 120

-11 -7 -3 1 5 9 13 17 21 25 29 33 37

M ASS F RA CT IO N BU RN (% ) CRANK ANGLE

MASS FRACTION BURN RATE AT 200 BAR IOP

D100 BD100 B20 B30 B40 -20 0 20 40 60 80 100 120

-9 -6 -3 0 3 6 9 12 15 18 21 24 27 30 33

M ASS F RA CT IO N B U RN (% ) CRANK ANGLE

MASS FRACTION BURN RATE AT 220 BAR IOP

[image:10.595.225.523.392.519.2] [image:10.595.229.520.553.710.2]
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[image:11.595.203.538.47.666.2] [image:11.595.207.537.74.237.2] [image:11.595.207.471.281.442.2]

Figure 15. Variation of cumulative heat release with crank angle.

Figure 16. Cumulative heat release at 180 bar IOP.

Figure 17. Cumulative heat release at 200 bar IOP.

(IOP), 180 bar, 200 bar and 220 bar respectively. Max. NHR occurs at 355 - 367 CA, for different tested fuels. It can observe that as IOP increases NHR increas-es; it is due to when injection pressure increases the diameter of fuel particles small, and air fuel mixture becomes better during ignition period. But, higher

0 0.2 0.4 0.6 0.8 1 1.2 1.4

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HEA

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D100 BD100 B20 B30 B40

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D100 BD100 B20 B30 B40

0 0.2 0.4 0.6 0.81 1.2 1.4 1.6

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CUMULATIVE HEAT RELEASE AT 200 BAR IOP

[image:11.595.209.522.474.644.2]
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[image:12.595.231.516.77.242.2] [image:12.595.233.515.280.455.2]

Figure 18. Cumulative heat release at 220 bar IOP.

Figure 19. Net heat with CA at 180 bar IOP.

Figure 20. Net heat with CA at 200 bar IOP.

injection pressure leads shorter ignition delay, which in turn decreases the pos-sibilities of homogeneous mixture and causes the incomplete combustion. Maxi-mum NHR can be obtained at higher injection pressure. B30 releases maxiMaxi-mum NHR, 28.83 at 200 bar IOP.

0 0.2 0.4 0.6 0.81 1.2 1.4 1.6

1 53

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HEA

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CUMULATIVE HEAT RELEASE AT 220 BAR IOP

D100 BD100 B20 B30 B40

-15 -10 -5 0 5 10 15 20 25 30

1 49 97 145 193 241 289 337 385 433 481 529 577 625 673

H

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NET HEAT RELEASE AT 180 BAR IOP

D100 BD100 B20 B30 B40

-20 -10 0 10 20 30

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NET HEAT RELEASE AT 200 BAR IOP

[image:12.595.233.517.490.638.2]
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[image:13.595.229.523.74.246.2]

Figure 21. Net heat with CA at 220 bar IOP.

5. Conclusions

Brake thermal efficiency of the ternary fuel blends is slightly less than the pure diesel fuel. Among the ternary fuel blends, B30 has higher BTE of 27%. BTE increases with increase in IOP.

Brake specific fuel consumption of the ternary fuel blends is greater than the pure diesel fuel and pure mahuva biodiesel. B30 gives lowest fuel consump-tion of 0.3 kg/kW-h. BSFC reduces with increase in IOP.

Exhaust gas temperature reduces with increase in IOP; B20 has lowest EGT. At 180 bar B20 has 450 deg C. whereas at 220 bar it is 430 deg C.

Peak cylinder pressure for pure Mahuva biodiesel is greater than diesel and ternary fuel blend. Peak cylinder pressure reduces as IOP increases.

B30 has the similar mass fraction burn as that of diesel fuel.

Cumulative heat release is more for biodiesel and ternary fuel blends as compared with diesel fuel. Cumulative heat release is more at higher injec-tion opening pressures. CHR increased by 1.5% to 2% when IOP increased from 180 bar to 220 bar.

Net heat release rate increases with increase in IOP. Maximum net heat oc-curs at 355 - 357 CA. B30 has maximum net heat of 28.83 at 200 bar IOP.

References

[1] Ajay, E.A., et al. (2002) A Study of Some Fuel Properties of Local Ethanol Blended

with Diesel Fuel. Agricultural Engineering International: CIGR Journal of Scientific

Research and Development, Manuscript EE 01, Vol. IV.

[2] Agarwal, A.K. (2007) Bio Fuels (Alcohols and Biodiesel) Applications as Fuels for

Internal Combustion Engines. Progress in Energy and Combustion Science, 33,

233-271. https://doi.org/10.1016/j.pecs.2006.08.003

[3] Ajav, E.A., Sing, B., et al. (1998) Performance of a Stationary Diesel Engine Using

Vaporised Ethanol as Supplementary Fuel. Biomass Bio Energy, 15, 493-502.

https://doi.org/10.1016/S0961-9534(98)00055-5

[4] Hansen, A.C., et al. (2005) Ethanol-Diesel Fuel Blends—A Review. Bio Resource

Technology, 96, 277-285. https://doi.org/10.1016/j.biortech.2004.04.007

-15 -10 -5 0 5 10 15 20 25 30 35

1 46 91 136 181 226 271 316 361 406 451 496 541 586 631 676

HEA

T R

EL

EA

SE

(J/

de

g)

CRANK ANGLE

NET HEAT RELEASE AT 220 BAR IOP

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[5] Cheenkachorn, K., et al. (2010) An Investigation on Diesel-Ethanol-Biodiesel Blends

for Diesel Engines: Part Imulsion Stability and Fuel Properties. Energy Sources, Part

A: Recovery, Utilization, and Environmental Effects, 32, 637-644.

https://doi.org/10.1080/15567030903059608

[6] Hulwan, D.B., et al. (2011) Performance, Emission and Combustion Characteristics

of a Multicylinder DI Diesel Engine Running on Diesel-Ethanol-Bio Diesel Blends

of High Ethanol Content. Applied Energy, 88, 5042-5055.

https://doi.org/10.1016/j.apenergy.2011.07.008

[7] Barabas, I., et al. (2010) Performance and Emission Characteristics of a CI Engine

Fuelled with Diesel-Biodiesel Bio Ethanol Blends. Fuel, 89, 3827-3832.

https://doi.org/10.1016/j.fuel.2010.07.011

[8] Venkata Subbaiah, G., et al. (2010) Rice Bran Oil Biodiesel as an Additive in

Di-esel-Ethanol Blends for Diesel Engines. IJRRAS, 3, 334-342.

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Figure

Table 1. Engine specifications.
Figure 1. Brake thermal efficiency with BP.
Figure 2. Brake thermal efficiency with IOP at full load.
Figure 5. Exhaust gas temperature with BP.
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References

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