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RESEARCH PAPERS: SPECIAL ISSUE ON BOILING AND INTERFACIAL PHENOMENA: Porous Media

Heat Transfer Analysis in Metal Foams With Low-Conductivity Fluids

[+] Author and Article Information
Nihad Dukhan

Department of Mechanical Engineering,  University of Detroit Mercy, 4001 W. McNichols Rd., Detroit, MI 48221nihad.dukhan@udmercy.edu

Rubén Picón-Feliciano

Department of Mechanical Engineering,  University of Puerto Rico-Mayagüez, Mayagüez, Puerto Rico 00681

Ángel R. Álvarez-Hernández

 NASA Johnson Space Center, Houston, TX 77058

J. Heat Transfer 128(8), 784-792 (Feb 06, 2006) (9 pages) doi:10.1115/1.2217750 History: Received May 08, 2005; Revised February 06, 2006

The use of open-cell metal foam in contemporary technologies is increasing rapidly. Certain simplifying assumptions for the combined conduction∕convection heat transfer analysis in metal foam have not been exploited. Solving the complete, and coupled, fluid flow and heat transfer governing equations numerically is time consuming. A simplified analytical model for the heat transfer in open-cell metal foam cooled by a low-conductivity fluid is presented. The model assumes local thermal equilibrium between the solid and fluid phases in the foam, and neglects the conduction in the fluid. The local thermal equilibrium assumption is supported by previous studies performed by other workers. The velocity profile in the foam is taken as non-Darcean slug flow. An approximate solution for the temperature profile in the foam is obtained using a similarity transform. The solution for the temperature profile is represented by the error function, which decays in what looks like an exponential fashion as the distance from the heat base increases. The model along with the simplifying assumptions were verified by direct experiment using air and several aluminum foam samples heated from below, for a range of Reynolds numbers and pore densities. The foam samples were either 5.08- or 20.32cm-thick in the flow direction. Reasonably good agreement was found between the analytical and the experimental results for a considerable range of Reynolds numbers, with the agreement being generally better for higher Reynolds numbers, and for foam with higher surface area density.

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Copyright © 2006 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Schematic and nomenclature of a foam block

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Figure 2

Schematic of the experimental setup

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Figure 3

Temperature distribution for 10ppi thin foam sample: (a) Rek=165.4, (b) Rek=192.9, (c) Rek=216.3

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Figure 4

Temperature distribution for 20ppi thin foam sample: (a) Rek=134.6, (b) Rek=157.4, (c) Rek=180.9

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Figure 5

Temperature distribution for 10‐ppi-thick foam sample: (a) Rek=47.1, (b) Rek=51.2, (c) Rek=55.3

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Figure 6

Temperature distribution for 20‐ppi-thick foam sample: (a) Rek=29.1, (b) Rek=32.8, (c) Rek=63.9

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Figure 7

Temperature distribution for 40‐ppi-thick foam sample: (a) Rek=20.1, (b) Rek=29.8, (c) Rek=43.9

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