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RESEARCH PAPERS

# An Experimental Study of the Enhancement of Air-Cooling Limits for Telecom/Datacom Heat Sink Applications Using an Impinging Air Jet

[+] Author and Article Information
Eric Sansoucy

University of Ottawa, Department of Mechanical Engineering, Ottawa, Ontario, Canada K1N 6N5sansoucy@genie.uottawa.ca

Patrick H. Oosthuizen

Queen's University, Department of Mechanical Engineering, Kingston, Ontario, Canada K7L 3N6oosthuiz@me.queensu.ca

Gamal Refai-Ahmed

ATI Technologies Inc., 1 Commerce Valley Drive East, Markham, Ontario, Canada L3T 7X6gahmed@ati.com

J. Electron. Packag 128(2), 166-171 (Aug 24, 2005) (6 pages) doi:10.1115/1.2164848 History: Received November 13, 2004; Revised August 24, 2005

## Abstract

An experimental study was conducted to investigate the heat transfer from a parallel flat plate heat sink under a turbulent impinging air jet. A horizontal nozzle plate confined the target surface. The jet was discharged from a sharp-edged nozzle in the nozzle plate. Average Nusselt numbers are reported for $Pr=0.7$, $5000⩽Re⩽30,000$, $L∕d=2.5$, and 0.833 at $H∕d=3$ where $L$, $H$, and $d$ define the length of the square heat source, nozzle-to-target spacing, and nozzle diameter, respectively. Tests were also conducted for an impinging flow over a flat plate, flush with the top surface of the target plate. The average Nusselt numbers from the heat sink were compared to those for a flat plate to determine the overall performance of the heat sink in a confined impingement arrangement. The experimental results were compared with the numerical predictions obtained in an earlier study. Although the average Nusselt numbers obtained from numerical simulations differed from the experimental measurements by 18%, the disagreement is much less significant when related to the junction temperature. Under typical conditions, it was shown that such discrepancy in the Nusselt number lead to an error of 6% in the prediction of the junction temperature of the device.

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## Figures

Figure 1

Parallel flat plate heat sink under a confined impinging jet

Figure 2

Schematic of the experimental setup

Figure 3

Details of the test section

Figure 4

Details of the heater assemblies for an impinging flow over (a) a flat plate and (b) a heat sink

Figure 5

Details of the flat plate and of the flat plate heat sink (dimensions in millimeters)

Figure 6

Comparison of experimentally determined average Nusselt numbers with numerical results of Sansoucy (8) for an impinging flow over a flat plate at L∕d=2.5, H∕d=3, and various Reynolds numbers

Figure 7

Comparison of experimentally determined average Nusselt numbers with numerical results of Sansoucy (8) for an impinging flow over a flat plate at L∕d=0.833, H∕d=3, and various Reynolds numbers

Figure 8

Comparison of experimentally determined average Nusselt numbers with numerical results of Sansoucy (8) for an impinging flow over a heat sink at L∕d=2.5, H∕d=3, and various Reynolds numbers

Figure 9

Comparison of experimentally determined average Nusselt numbers with numerical results of Sansoucy (8) for an impinging flow over a heat sink at L∕d=0.833, H∕d=3, and various Reynolds numbers

Figure 10

Comparison of experimentally determined COE with numerical results of Sansoucy (8) at L∕d=2.5, H∕d=3, and various Reynolds numbers

Figure 11

Comparison of experimentally determined COE with numerical results of Sansoucy (8) at L∕d=0.833, H∕d=3, and various Reynolds numbers

Figure 12

Thermal resistance circuit of a heat sink mounted on an electronic device

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