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Research Papers: Micro/Nanoscale Heat Transfer

Multi-Objective Optimization of Laminar Heat Transfer and Friction Factor in Rectangular Microchannel With Rectangular Vortex Generators: An Application of NSGA-II With Gene Expression Programing Metamodel

[+] Author and Article Information
Aparesh Datta

Department of Mechanical Engineering,
National Institute of Technology Agartala,
Jirania, Tripura 799046, India
e-mail: adatta96@gmail.com

Ajoy Kumar Das

Department of Mechanical Engineering,
National Institute of Technology Agartala,
Jirania, Tripura 799046, India
e-mail: akdas_72@yahoo.com

Prasenjit Dey

Department of Mechanical Engineering,
National Institute of Technology Agartala,
Jirania, Tripura 799046, India
e-mail: prasenjitmit1@gmail.com

Dipankar Sanyal

Department of Mechanical Engineering,
Jadavpur University,
Kolkata, West Bengal 700032, India
e-mail: dipans26@gmail.com

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received August 31, 2016; final manuscript received January 24, 2017; published online March 21, 2017. Assoc. Editor: Guihua Tang.

J. Heat Transfer 139(7), 072401 (Mar 21, 2017) (12 pages) Paper No: HT-16-1545; doi: 10.1115/1.4035890 History: Received August 31, 2016; Revised January 24, 2017

Improvement of the effectiveness of heat exchanger is the demand of compact and efficient cooling devices. In that respect, a numerical study of fluid flow and heat transfer has been conducted with different arrangements of simple vortex generator (VG) in a rectangular microchannel Reynolds number (Re) in the range between 200 and 1100. The combined effect of spanwise and pitchwise distance of VG on heat transfer is investigated rigorously to observe the dependence of heat transfer on both. By processing the numerical predictions through gene expression programing and genetic algorithm optimization, the output variations in heat transfer, or Nusselt number, and friction factor with Re and locations of VGs in the channel are predicted in the form of explicit equations. The predicted monotonic increase of the outputs with Re shows heat transfer enhancement of 40–135% at the cost of increased pressure drop by 62–186.7% with respect to channels without VGs.

Copyright © 2017 by ASME
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References

Figures

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Fig. 1

Schematic diagram of channel

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Fig. 2

Flowchart of numerical simulation by computational fluid dynamics (CFD)

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Fig. 3

Comparison of present numerical results with experiment by Liu et al. [36]

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Fig. 4

Flowchart of algorithm of NSGA-II technique

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Fig. 5

Computational time of NSGA-II technique

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Fig. 6

Flowchart of GEP model

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Fig. 7

Linear-fit model of CFD and optimizer predicted (a) Nusselt number and (b) friction factor

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Fig. 8

Pareto-optimal solutions using the NSGA-II

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Fig. 11

Variation in relative friction factor f/f0 for different channels

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Fig. 12

Velocity contour at Re 400 for C1, C2, C3, and C4 channels at Z = 0.5H

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Fig. 13

Velocity contour at Re 1000 for C1, C2, C3, and C4 channels at Z = 0.5H

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Fig. 14

Temperature contour on cross sections along the flow direction

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Fig. 15

Temperature contour and limiting streamline at the top surface of C1 and C4 channels at Re 600: C1—S = 100 μm, P = 0.005 m, and Re = 600; C4—S = 350 μm, P = 0.005 m, and Re = 600

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Fig. 16

Temperature contour and limiting streamline at the top surface of C2 and C4 channels at Re 1000: C2—S = 200 μm, P = 0.005 m, and Re = 1000; C4—S = 350 μm, P = 0.005 m, and Re = 1000

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Fig. 17

Temperature contour and limiting streamline at the top surface of C2 and C6 channels at Re 600: C2—S = 200 μm, P = 0.005 m, and Re = 600; C6—S = 200 μm, P = 0.00285 m, and Re = 600

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Fig. 18

Temperature contour and limiting streamline at the top surface of C4 and C12 channels at Re 1000: C4—S = 350 μm, P = 0.005 m, and Re = 1000; C12—S = 350 μm, P = 0.002 m, and Re = 1000

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Fig. 10

Thermal performance of different channels

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Fig. 9

Variation in relative Nusselt number Nu/Nu0 for different channels

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