Research Papers: Micro/Nanoscale Heat Transfer

Experimental Study on the Effect of Low Acute Side Angles on Heat Transfer in Rhombic Shaped Microchannel

[+] Author and Article Information
Sunil K. Dwivedi

Department of Mechanical Engineering,
Indian Institute of Technology Bombay,
Mumbai 400076, India
e-mail: hgarbha@gmail.com

Sandip K. Saha

Department of Mechanical Engineering,
Indian Institute of Technology Bombay,
Mumbai 400076, India
e-mail: sandip.saha@iitb.ac.in

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received July 7, 2017; final manuscript received November 28, 2018; published online December 19, 2018. Assoc. Editor: George S. Dulikravich.

J. Heat Transfer 141(2), 022404 (Dec 19, 2018) (12 pages) Paper No: HT-17-1401; doi: 10.1115/1.4042148 History: Received July 07, 2017; Revised November 28, 2018

This experimental study on rhombic shaped microchannels was conducted to understand the effect of a low acute side angle on the Nusselt number and compare the results with the published numerical results for H1 (axially constant heat flux and circumferentially constant temperature) and H2 (constant axial and circumferential wall heat flux) boundary conditions. The hydraulic and heat transfer characteristics of the rhombic geometry with a side angle of 30 deg for different mass flow rates and heat flux inputs are obtained using a three-dimensional (3D) conjugate heat transfer model, which is validated with the experimental results. It is found that the average Nusselt number obtained from the experimental and numerical results can be approximated closely with that computed using the H1 boundary condition. The local Nusselt number of hydrodynamically and thermally developed regions obtained from the numerical analysis is compared with a correlation for the H1 boundary condition. These results will be useful in design and optimization of a rhombic shaped microchannel for electronic cooling applications.

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Fig. 1

Schematic of the experimental setup

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Fig. 2

(a) Copper block with thermocouple locations, (b) thermocouple locations, (c) exploded view, and (d) photograph of the microchannel heat sink test section

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Fig. 3

Cross-sectional view of the machined channel and its profile measurement (α1=28∘40′38″ and α2=29∘38′43″)

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Fig. 4

Schematic of the computational domain (a) top view, (b) side view, (c) section A-A, and (d) detail of B with α1=28∘40′38″ and α2=29∘38′43″ (all dimensions are in mm)

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Fig. 5

Validation of pressure drop at different flow rates

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Fig. 6

Validation of temperature at same flow rates and different heat inputs

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Fig. 7

Variation of temperature measured experimentally along the nondimensional length for 32 W and different flow rates

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Fig. 8

Contour plots for 22 W and 12.34 ml/min flow rate (a) nondimensional velocity profile, (b) nondimensional temperature profile, (c) microchannel wall temperature, and (d) velocity contours

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Fig. 9

Numerical results for temperature variation at different flow rates and (a) 42 W, (b) 32 W, and (c) 7.5 W

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Fig. 10

Variation of the Poiseuille number (fReDh) along the nondimensional channel length

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Fig. 11

Comparison of the local Nusselt number from numerical results and published correlation (Saha et al. [7]) for the H1 boundary condition for different Reynolds numbers based on (a) hydraulic diameter (Dh) and (b) square root of area (√A)



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