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Research Papers: Micro/Nanoscale Heat Transfer

A New Approach for the Mitigating of Flow Maldistribution in Parallel Microchannel Heat Sink

[+] Author and Article Information
Ritunesh Kumar

Mechanical Engineering Department,
Indian Institute of Technology Indore,
Khandwa Road,
Simrol 453552, India
e-mail: ritunesh@iiti.ac.in

Gurjeet Singh

Mechanical Engineering Department,
Indian Institute of Technology Indore,
Khandwa Road,
Simrol 453552, India

Dariusz Mikielewicz

Faculty of Mechanical Engineering,
Gdansk University of Technology,
ul. Narutowicza 11/12,
Gdansk 80-233, Poland

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received June 5, 2017; final manuscript received November 14, 2017; published online March 30, 2018. Assoc. Editor: Ali Khounsary.

J. Heat Transfer 140(7), 072401 (Mar 30, 2018) (10 pages) Paper No: HT-17-1326; doi: 10.1115/1.4038830 History: Received June 05, 2017; Revised November 14, 2017

The problem of flow maldistribution is very critical in microchannel heat sinks (MCHS). It induces temperature nonuniformity, which may ultimately lead to the breakdown of associated system. In the present communication, a novel approach for the mitigation of flow maldistribution problem in parallel MCHS has been proposed using variable width microchannels. Numerical simulation of copper made parallel MCHS consisting of 25 channels has been carried out for the conventional design (CD) and the proposed design (PD). It is observed that the PD reduces flow maldistribution by 93.7%, which facilitated in effective uniform cooling across the entire projected area of MCHS. Temperature fluctuation at fluid–solid interface is reduced by 4.3 °C, whereas maximum and average temperatures of microchannels projected area are reduced by 2.3 °C and 1.1 °C, respectively. PD is suitable in alleviating flow maldistribution problem for the extended range of off design conditions.

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Figures

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Fig. 1

Flow configurations reported in literature: (a) I type, (b) N type, (c) Z type, (d) D type, (e) L type, (f) L′ type, (g) U type, (h) U′ type, (i) V type, and (j) V′ type

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Fig. 2

Geometry of the conventional MCHS (a) top view and (b) 3D view

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Fig. 3

Comparison of average friction factor

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Fig. 4

Comparison of local Nusselt number at Rein = 1200

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Fig. 5

Variation of mass flow rate in channels for different iteration at Rein = 1200

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Fig. 6

Velocity vectors diagram at z = 0.3 mm (a) CD and (b) PD at Rein = 1200

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Fig. 7

Effect of Reynolds number on ϕ

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Fig. 8

Effect of Reynolds number on mass flow distribution: (a) 800, (b) 1000, (c) 1400, and (d) 1600

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Fig. 9

Comparison of average interface temperature for channels at Rein = 1200

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Fig. 10

Temperature contours at MCHS base (a) CD and (b) PD at Rein = 1200

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Fig. 11

Effect of Reynolds number on (a) maximum base temperature, (b) average base temperature, and (c) base temperature fluctuations

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Fig. 12

Comparison of heat removal from channels at Rein = 1200

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Fig. 13

Comparison of Nusselt number

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Fig. 14

Comparison of pressure drop in channels at Rein = 1200

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Fig. 15

Comparison of overall thermal performance factor

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