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Research Papers

Lattice Boltzmann Simulation of Heat Transfer Enhancement in a Cold Plate Using Porous Medium

[+] Author and Article Information
Abbasali Abouei Mehrizi

e-mail: abbasabouei@gmail.com

Mousa Farhadi

e-mail: mfarhadi@nit.ac.ir

Kurosh Sedighi

e-mail: ksedighi@nit.ac.ir

Amir Latif Aghili

e-mail: amir_latifaghili@yahoo.com

Faculty of Mechanical Engineering,
Babol University of Technology,
P.O. Box 484,
Babol 47148-71167, Iran

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the Journal of Heat Transfer. Manuscript received April 22, 2012; final manuscript received February 14, 2013; published online September 23, 2013. Assoc. Editor Sujoy Kumar Saha.

J. Heat Transfer 135(11), 111006 (Sep 23, 2013) (9 pages) Paper No: HT-12-1180; doi: 10.1115/1.4024611 History: Received April 22, 2012; Revised February 14, 2013

The computational study of heat transfer and fluid flow in a porous media cold plate was investigated using lattice Boltzmann method. The study was carried out on a heat exchanger including two adiabatic inlet and outlet conduit and three hot fins with constant temperature. The porous medium is positioned between the fins to enhance heat transfer rate. The local thermal equilibrium assumption between the fluid and solid phases and the Brinkman–Forchheimer extended Darcy equation was used to simulate the porous domain. The effect of porosity on heat transfer from the fins surfaces was studied at different Reynolds and Prandtl numbers. Results show that by decreasing the porosity, the heat transfer rate increases and the fluid bulk temperature grows at less time for different Reynolds and Prandtl numbers.

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Figures

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Fig. 1

Computational domain and boundary condition. (a) 3D physical model and (b) 2D simulative model.

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Fig. 2

Temperature distribution at the middle of: (a) clear zone and (b) porous zone

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Fig. 3

Dimensionless velocity profiles for: (a) full porous channel at various Reynolds number, (b) full porous channel at various Darcy number, and (c) the interface between porous medium and fluid layer

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Fig. 4

Streamlines and temperature contours with different Reynolds numbers and porosities

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Fig. 5

Temperature contours for different Reynolds numbers and porosities

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Fig. 6

Nondimensional bulk mean temperature versus the (a) Reynolds number for different porosities at Pr = 0.7, (b) Prandtl number for different porosities at Re = 40

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Fig. 7

Variation of dimensionless time to reach the steady state versus: (a) Reynolds number when Pr = 0.7 and (b) Prandtl number when Re = 40

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Fig. 8

Variation of average Nusselt number in the fins versus the porosity. (a) Re = 10, (b) Re = 20, (c) Re = 40, and (d) Re = 60.

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Fig. 9

Variation of average Nusselt number in the fins for different values of porosity when Pr = 0.7 versus the Reynolds number. (a) Inlet fin, (b) central fin, and (c) outlet fin.

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Fig. 10

Variation of average Nusselt number in the fins, with different Prandtl numbers versus the porosity. (a) Pr=0.5, (b) Pr=0.7, (c) Pr = 1, and (d) Pr = 5.

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