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RESEARCH PAPERS

Jet Impingement Cooling of Chips Equipped With Cylindrical Pedestal Profile Fins

[+] Author and Article Information
Y. S. Chung

Samsung Electronics Co., Ltd., 416, Maetan3-dong, Paldal-gu, Suwon, Gyeonggi-do, 442-742 Korea

D. H. Lee

School of Mechanical and Automotive Engineering, Inje University, 607 Obang-dong, Gimhae, Gyongnam 621-749 Korea

P. M. Ligrani

Convective Heat Transfer Laboratory, Department of Mechanical Engineering, University of Utah. Salt Lake City, Utah 84112-9208 USA

J. Electron. Packag 127(2), 106-112 (Jun 03, 2005) (7 pages) doi:10.1115/1.1849235 History: Received September 03, 2003; Revised July 07, 2004; Online June 03, 2005
Copyright © 2005 by ASME
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References

Fedorov,  A. G., and Viskanta,  A., 1997, “A Numerical Simulation of Conjugate Heat Transfer in an Electronic Package Formed by Embedded Discrete Heat Sources in Contact With Porous Heat Sink,” ASME Trans. J. Electron. Packag., 119, pp. 8–16.
Weiss,  J., Fortner,  P., Pearson,  B., Watson,  K., and Monroe,  T., 1989, “Modeling Air Flow in Electronic Package,”Mech. Eng. (Am. Soc. Mech. Eng.), pp. 56–58.
Copeland,  D., 1996, “Single-Phase and Boiling Cooling of Small Pin Fin Arrays of Multiple Nozzle Jet Impingement,” ASME Trans. J. Electron. Packag., 118, pp. 21–26.
Sparrow,  E. M., and Larson,  E. D., 1982, “Heat Transfer From Pin-Fins Situated in an Oncoming Longitudinal Flow Which Turns to Crossflow,” Int. J. Heat Mass Transfer, 25(5), pp. 603–614.
Wadsworth, D. C., 1989, “Cooling of a Multichip Electronic Module by Means of Confined Two-Dimensional Jets of Dielectric Liquid,” M.S. thesis, Purdue University, IN.
Sullivan, P. F., Ramadhyani, S., and Incropera, F. P., 1992, “Extended Surfaces to Enhanced Impingement Cooling With Single Circular Liquid Jets,” ASME paper no. EEP-1-1, Proceedings of the ASME/JSME Joint Conference on Electronic Packaging, San Jose, CA, pp. 207–216.
Sullivan, P. F., Ramadhyani, S., and Incropera, F. P., 1992, “Use of Smooth and Roughened Spreader Plates to Enhance Impingement Cooling With Single Circular Liquid Jets,” ASME paper no. HTD-206-2, National Heat Transfer Conference, San Diego, CA, pp. 103–110.
Teuscher, K. L., 1992, “Packaging Methods for Jet Impingement Cooling of an Array of Discrete Heat Sources,” M.S. thesis, Purdue University, IN.
Baughn,  J. W., Mesbah,  M., and Yan,  X., 1993, “Measurements of Local Heat Transfer for an Impinging Jet on a Cylindrical Pedestal,” ASME-Turbulent Enhancement Heat Transf.,HTD-239, pp. 57–62.
Parneix,  S., Behnia,  M., and Durbin,  P. A., 1999, “Predictions of Turbulent Heat Transfer in an Axisymmetric Jet Impinging on a Heated Pedestal,” ASME Trans. J. Heat Transfer, 121, pp. 43–49.
Dunne, S. T., 1983, “A Study of Flow and Heat Transfer in Gas Turbine Cooling Passages,” Ph.D. thesis, Oxford University, UK.
Kline,  S. J., and McKlintock,  F. A., 1953, “Describing Uncertainties in Single Sample Experiments,” Mech. Eng. (Am. Soc. Mech. Eng.), 75, pp. 3–8.
Rajaratnam, N., 1976, Turbulent Jet, Elsevier Scientific Publishing Corporation, The Netherlands.
Lee,  D. H., Song,  J., and Jo,  M. C., 2004, “The Effects of Nozzle Diameter on Impinging Jet Heat Transfer and Fluid Flow,” ASME J. Heat Transfer,126, pp. 554–557.
Baughn,  J. W., and Shimizu,  S., 1989, “Heat Transfer Measurement From a Surface With Uniform Heat Flux and an Impinging Jet,” ASME Trans. J. Heat Transfer, 111, pp. 1096–1098.
Gardon, R., and Cobonpue, J., 1962, “Heat Transfer Between a Flat Plate and Jets in Air Impinging on It,” Int. Development Heat Transfer, pp. 454–459.

Figures

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Schematic diagram of the experimental apparatus
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(a) Schematic diagram of the test model. (b) Test model geometric parameters.
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Test apparatus including devices used for preheating the test model
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Variation of wall pressure coefficients along the flat plate with no pedestal employed for Re=23,000, H/D=0, and L/d=2–10
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Variation of wall pressure coefficients along the flat plate with a H/D=0.5 pedestal for Re=23,000, and L/d=2–10
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Variation of wall pressure coefficients along the flat plate with a H/D=1.0 pedestal for Re=23,000, and L/d=2–10
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Variation of wall pressure coefficients along the flat plate with a H/D=1.5 pedestal for Re=23,000, and L/d=2–10
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Visualizations of flow patterns along the flat surface for H/D=0,L/d=2, and Re=2300
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Visualizations of flow patterns along the flat surface and around the pedestal for H/D=0.5,L/d=2, and Re=2300
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Visualizations of flow patterns along the flat surface and around the pedestal for H/D=1.0,L/d=2, and Re=2300
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Comparison between local Nusselt number data from Baughn et al. 9 and those by the present study for Re=23,000, H/D=1.0, and L/d=2
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Local Nusselt number distributions on the upper surface of the pedestal and along the flat plate for Re=23,000, L/d=2–10, and H/D=0
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Local Nusselt number distributions on the upper surface of the pedestal and along the flat plate for Re=23,000, L/d=2–10, and H/D=0.5
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Local Nusselt number distributions on the upper surface of the pedestal and along the flat plate for Re=23,000, L/d=2–10, and H/D=1.0
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Local Nusselt number distributions on the upper surface of the pedestal and along the flat plate for Re=23,000, L/d=2–10, and H/D=1.5
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Globally averaged Nusselt numbers as they depend upon the H/D and L/d parameters

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