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Research Papers: Jets, Wakes, and Impingement Cooling

# Modeling of Convective Cooling of a Rotating Disk by Partially Confined Liquid Jet Impingement

[+] Author and Article Information
Jorge C. Lallave, Muhammad M. Rahman

Department of Mechanical Engineering, University of South Florida, Tampa, FL 33620

J. Heat Transfer 130(10), 102201 (Aug 06, 2008) (10 pages) doi:10.1115/1.2945898 History: Received April 18, 2007; Revised January 08, 2008; Published August 06, 2008

## Abstract

This paper presents the results of the numerical simulation of conjugate heat transfer during a semiconfined liquid jet impingement on a uniformly heated spinning solid disk of finite thickness and radius. This study considered various disk materials, namely, aluminum, copper, silver, Constantan, and silicon; covering a range of Reynolds number (220–900), Ekman number $(7.08×10−5–∞)$, nozzle-to-target spacing $(β=0.25–1.0)$, disk thicknesses to nozzle diameter ratio $(b∕dn=0.25–1.67)$, and Prandtl number (1.29–124.44) using ammonia $(NH3)$, water $(H2O)$, flouroinert (FC-77), and oil (MIL-7808) as working fluids. The solid to fluid thermal conductivity ratio was 36.91–2222. A higher thermal conductivity plate material maintained a more uniform interface temperature distribution. A higher Reynolds number increased the local heat transfer coefficient. The rotational rate also increased the local heat transfer coefficient under most conditions.

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## Figures

Figure 1

3D schematic of axisymmetric semiconfined liquid jet impingement on a uniformly heated spinning disk

Figure 2

Velocity vector distribution for a semiconfined jet impingement on a silicon disk with water as the cooling fluid (Re=475, Ek=4.25×10−4, rp∕rd=0.5, β=0.5, and b∕dn=0.5)

Figure 3

Free surface height distribution for different plate-to-disk confinement ratios with water as the cooling fluid (Re=450, Ek=4.25×10−4, β=0.5, and b∕dn=0.5)

Figure 4

Local Nusselt number and dimensionless interface temperature distributions for a silicon disk with water as the cooling fluid for different Reynolds numbers (Ek=4.25×10−4, β=0.5, b∕dn=0.5, and rp∕rd=0.667)

Figure 5

Average Nusselt number variations with Reynolds number at different Ekman numbers for a silicon disk with water as the cooling fluid (β=0.5, b∕dn=0.5, and rp∕rd=0.667)

Figure 6

Local Nusselt number and dimensionless interface temperature distributions for a silicon disk with water as the cooling f1uid at different Ekman numbers (Re=540, β=0.25, b∕dn=0.5, and rp∕rd=0.667)

Figure 7

Local Nusselt number and dimensionless interface temperature distributions for different silicon disk thicknesses with water as the cooling fluid (Re=450, Ek=4.25×10−4, β=0.5, and rp∕rd=0.667)

Figure 8

Local Nusselt number and dimensionless interface temperature distributions for a silicon disk with water as the cooling fluid for different nozzle-to-target spacing (Re=750, Ek=4.25×10−4, b∕dn=0.5, and rp∕rd=0.667)

Figure 9

Local Nusselt number and dimensionless interface temperature distributions for different cooling fluids for silicon as the disk material (Re=750, β=0.5, b∕dn=0.5, and rp∕rd=0.667)

Figure 10

Local Nusselt number and dimensionless interface temperature distributions for different solid materials with water as the cooling fluid (Re=875, Ek=4.25×10−4, β=0.5, b∕dn=0.5, and rp∕rd=0.667)

Figure 11

Local Nusselt number and dimensionless interface temperature distributions for different plate-to-disk confinement ratios (Re=450, Ek=4.25×10−4, β=0.5, and b∕dn=0.5)

Figure 12

Comparison of the predicted average Nusselt number (Eq. 17) with numerical data

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