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Research Papers: Jets, Wakes, and Impingement Cooling

Computational Study of Heat Transfer in a Conjugate Turbulent Wall Jet Flow at High Reynolds Number

[+] Author and Article Information
E. Vishnuvardhanarao

Department of Mechanical Engineering,  Indian Institute of Technology Guwahati, Guwahati 781 039, Indiaelaprolu@iitg.ernet.in

Manab Kumar Das1

Department of Mechanical Engineering,  Indian Institute of Technology Guwahati, Guwahati 781 039, Indiamanab@mech.iitkgp.ernet.in

1

Corresponding author. Present address: Associate Professor, Department of Mechanical Engineering, Indian Institute of Technology Kharagpur, West Bengal 721302, India.

J. Heat Transfer 130(7), 072201 (May 16, 2008) (7 pages) doi:10.1115/1.2908429 History: Received March 07, 2007; Revised October 23, 2007; Published May 16, 2008

In the present case, the conjugate heat transfer involving the cooling of a heated slab by a turbulent plane wall jet has been numerically solved. The bottom of the solid slab is maintained at a hot uniform temperature, whereas the wall jet temperature, is equal to the ambient temperature. The Reynolds number considered is 15,000 because it has already been experimentally found and reported that the flow becomes fully turbulent and is independent of the Reynolds number. The high Reynolds number two-equation model (κϵ) has been used for the turbulence modeling. The parameters chosen for the study are the conductivity ratio of the solid-fluid (K), the solid slab thickness (S), and the Prandtl number (Pr). The ranges of parameters are K=11000, S=110, and Pr=0.01100. Results for the solid-fluid interface temperature, local Nusselt number, local heat flux, average Nusselt number, and average heat transfer are presented and discussed.

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Copyright © 2008 by American Society of Mechanical Engineers
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Figures

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Figure 1

Schematic and computational domain of the wall jet flow

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Figure 2

Interface temperature distribution (θi) distribution for S=10 and K=1000 at various Prandtl numbers

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Figure 3

Interface temperature distribution (θi) distribution for Pr=1 and S=10 at various thermal conductivity ratios (K)

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Figure 4

Interface temperature distribution (θi) distribution for Pr=1 and K=1000 at solid thickness ratios (S)

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Figure 5

Local Nusselt number (Nux) distribution for S=10 and K=1000 at various Prandtl numbers

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Figure 6

Local Nusselt number (Nux) distribution for Pr=1 and S=10 at various thermal conductivity ratios (K)

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Figure 7

Local Nusselt number (Nux) distribution for Pr=1 and K=1000 at various solid thickness ratios (S)

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Figure 8

Heat flux (Qx) distribution for S=10 and K=1000 at various Prandtl numbers

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Figure 9

Heat flux (Qx) distribution for Pr=1 and S=10 at various various thermal conductivity ratios (K)

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Figure 10

Heat flux (Qx) distribution for Pr=1 and K=1000 at various various solid thickness ratios (S)

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