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RESEARCH PAPERS

Experimental Measurements of the Flow and Heat Transfer of a Square Jet Impinging on an Array of Square Pin Fins

[+] Author and Article Information
Johnny S. Issa

Experimental and Computational Heat Transfer Laboratory, Department of Aerospace and Mechanical Engineering,  The University of Arizona, Tucson, AZ 85721jissa@email.arizona.edu

Alfonso Ortega

Experimental and Computational Heat Transfer Laboratory, Department of Aerospace and Mechanical Engineering,  The University of Arizona, Tucson, AZ 85721ortega@u.arizona.edu

J. Electron. Packag 128(1), 61-70 (Jun 14, 2005) (10 pages) doi:10.1115/1.2160513 History: Received December 13, 2004; Revised June 14, 2005

The flow behavior and heat transfer due to free air jet impingement on pin fin heat sinks was experimentally studied. Flow velocities and tip clearance ratios were varied from 2to20ms and 0 to 1, respectively. The stagnation pressure recovered at the center of the heat sink was higher for tall pins than for short pins. The pressure loss coefficient showed little dependence on Re, increased with increasing pin density and pin diameter, and decreased with increasing pin height and clearance ratio. The overall base-to-ambient thermal resistance decreased with increasing Re number, pin density, and pin diameter.

Copyright © 2006 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Flow behavior in jet impingement on pins with tip clearance

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Figure 2

Schematic of the experimental set-up

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Figure 3

Schematic of the hydraulics test plate: (a) side view; (b) top view

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Figure 4

Illustration of the pressure tap locations for the various heat sink families

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Figure 5

Schematic of the heat transfer plate

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Figure 6

Pressure loss coefficient at fixed pin height H∕W=0.9 and h∕H=0 for different pin arrays with a∕H=0.12

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Figure 7

Pressure loss coefficient at fixed pin height H∕W=0.9 and h∕H=0 for heat sinks 4C, 6C, and 7C with varying pin thickness

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Figure 8

Pressure loss coefficient vs aspect ratio (H∕W) for three different pin densities at Re=30,600, h∕H=0

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Figure 9

Dependence of pressure loss coefficient on Reynolds number for heat sinks of different heights 1A, 1B, and 1C (8×8) at h∕H=0

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Figure 10

Pressure loss coefficient for 1C (H∕W=0.9) at various clearance ratios

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Figure 11

Effect of tip clearance on overall pressure loss coefficient for 1A, 1B, and 1C (8×8) at various Re

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Figure 12

Pressure mapping for 1A and 1C (8×8) at different clearance ratios along the lateral direction of the heat sink at Re=7650

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Figure 13

Pressure mapping for 1A and 1C (8×8) at different clearance ratios along the diagonal direction of the heat sink at Re=7650

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Figure 14

Pressure mapping for 1B and 5B at different clearance ratios along the diagonal direction of the heat sink at Re=7650 and H∕W=0.7

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Figure 15

Heat sink base-to-ambient resistance dependence on Reynolds number and pin density for a∕H=0.12 at fixed pin height H∕W=0.9 and h∕H=0

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Figure 16

Heat sink base-to-ambient resistance at fixed pin heightH∕W=0.9 and h∕H=0 for heat sinks (5×5 arrays) with varying pin thickness

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Figure 17

Heat sink base-to-ambient resistance vs Re number at h∕H=0 for 1A, 1B, and 1C (8×8)

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Figure 18

Heat sink base-to-ambient resistance vs aspect ratio at high Re=30,600 and low Re=3,000h∕H=0 for three different pin densities

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Figure 19

Normalized heat sink base-to-ambient resistance vs Re for 1C at different clearance ratios

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Figure 20

Overall thermal resistance vs clearance ratio at high Re (30,600) and low Re (3,000) for an 8×8 heat sink

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