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Research Papers: Gas Turbines: Combustion, Fuels, and Emissions

Quasidimensional Modeling of Diesel Combustion Using Detailed Chemical Kinetics

[+] Author and Article Information
Aron P. Dobos

Department of Mechanical Engineering,
Colorado State University,
Fort Collins, CO 80523
e-mail: adobos@engr.colostate.edu

Allan T. Kirkpatrick

Department of Mechanical Engineering,
Colorado State University,
Fort Collins, CO 80523
e-mail: allan@engr.colostate.edu

1Corresponding author.

Contributed by the Combustion and Fuels Committee of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received July 25, 2016; final manuscript received December 30, 2016; published online March 21, 2017. Assoc. Editor: Nadir Yilmaz.

J. Eng. Gas Turbines Power 139(8), 081502 (Mar 21, 2017) (14 pages) Paper No: GTP-16-1363; doi: 10.1115/1.4035820 History: Received July 25, 2016; Revised December 30, 2016

This paper presents an efficient approach to diesel engine combustion simulation that integrates detailed chemical kinetics into a quasidimensional fuel spray model. The model combines a discrete spray parcel concept to calculate fuel-air mixing with a detailed primary reference fuel chemical kinetic mechanism to determine species concentrations and heat release in time. Comparison of predicted pressure, heat release, and emissions with data from diesel engine experiments reported in the literature shows good agreement overall, and suggests that spray combustion processes can be predictively modeled without calibration of empirical burn rate constants at a significantly lower computational cost than standard multidimensional (CFD) tools.

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References

Figures

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Fig. 1

Transformation of a thermodynamic zone (“parcel”) from liquid fuel to combustion products

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Fig. 2

Spray parcel concept

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Fig. 3

Influence of swirl ratio on spray tip penetration length

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Fig. 4

Instantaneous swirl ratio as a function of piston geometry

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Fig. 5

Turbulence intensity and squish velocity as a function of piston geometry

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Fig. 6

χ2 volume distribution function for droplets

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Fig. 7

Block diagram of solution procedure to advance one time step

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Fig. 8

Engine 1, 50% load @ 1800 rpm, pressure and AHRR

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Fig. 9

Engine 1, 900 rpm, pressure and AHRR. θi = −11, θd = 5, and PBDC = 1.2 bar

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Fig. 10

Injected, vaporized, fuel burned, and hydrocarbon burned mass fractions for the baseline case

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Fig. 11

Instantaneous fractions of injected, vaporized, and burned fuel mass

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Fig. 12

Predicted zone temperatures for engine 1, baseline

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Fig. 13

Predicted total and radiative heat transfer for engine 1, baseline

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Fig. 14

Predicted NOx and soot emissions for engine 1, baseline case

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Fig. 15

Engine 1, spray liquid mass fraction and temperature distribution

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Fig. 16

Engine 1, NOx and soot locations

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Fig. 17

Engine 1, ϕ versus temperature @ 1800 rpm: (a) 25% load, (b) 50% load, and (c) 75% load

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Fig. 18

Engine 1, AHRR with and without parcel mixing model

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Fig. 19

Engine 1, sensitivity to chemical kinetic mechanism, baseline conditions

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Fig. 20

Engine 1, swirl ratio sensitivity

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Fig. 21

Engine 1, piston bowl size sensitivity for swirl ratio of2

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Fig. 22

Engine 2, 80% load, 1600 rpm, pressure and AHRR

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Fig. 23

Engine 2, modeled soot versus NOx tradeoff curve, resulting from changing the start of injection timing, θi

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