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Research Papers

Liquid Jet Impingement With an Angled Confining Wall for Spent Flow Management for Power Electronics Cooling With Local Thermal Measurements

[+] Author and Article Information
John F. Maddox

Department of Mechanical Engineering,
Auburn University,
Auburn, AL 36849
Department of Mechanical Engineering,
University of Kentucky,
Paducah, KY 42002
e-mail: john.maddox@uky.edu

Roy W. Knight, Sushil H. Bhavnani

Department of Mechanical Engineering,
Auburn University,
Auburn, AL 36849

1Corresponding author.

Contributed by the Electronic and Photonic Packaging Division of ASME for publication in the JOURNAL OF ELECTRONIC PACKAGING. Manuscript received April 27, 2015; final manuscript received June 25, 2015; published online July 14, 2015. Assoc. Editor: Xiaobing Luo.

J. Electron. Packag 137(3), 031015 (Sep 01, 2015) (9 pages) Paper No: EP-15-1041; doi: 10.1115/1.4030953 History: Received April 27, 2015; Revised June 25, 2015; Online July 14, 2015

The local surface temperature, heat flux, heat transfer coefficient, and Nusselt number were measured for an inline array of circular, normal jets of single-phase, liquid water impinging on a copper block with a common outlet for spent flow, and an experimental two-dimensional (2D) surface map was obtained by translating the jet array relative to the sensors. The effects of variation in jet height, jet pitch, confining wall angle, and average jet Reynolds number were investigated. A strong interaction between the effects of the geometric parameters was observed, and a 5 deg confining wall was seen to be an effective method of managing the spent flow for jet impingement cooling of power electronics. The maximum average heat transfer coefficient of 13,100 W/m2 K and average Nusselt number of 67.7 were measured at an average jet Reynolds number of 14,000.

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References

Figures

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Fig. 1

Regions of an impinging jet in an array with a common outlet

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Fig. 2

Spatial arrangement of jet array, where the shaded region represents the area of interest for the central jet

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Fig. 3

Cross-sectional view of jet array

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Fig. 4

Jet impingement flow chamber

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Fig. 5

Jet impingement flow loop

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Fig. 6

Sectioned view of insulation, heater block, TIM, and measurement block

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Fig. 7

Extrapolated surface map layout

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Fig. 8

Measured local values upstream and downstream of central jet along y* = 0, for γ = 0 deg, P* = 6, H* = 1, and L*n =2

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Fig. 9

Measured local values transverse to the direction of flow from central jet along x* = 0, for γ = 0 deg, P* = 6, H* = 1, and L*n =2

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Fig. 10

Increasing the Reynolds number, with all other parameters being constant, increases the intensity of the local heat transfer at all locations

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Fig. 11

Variation in average heat transfer for orifice and nozzle plates with parallel confining walls at P* = 6

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Fig. 12

Comparison of best case average heat transfer for orifice and nozzle plates with parallel confining walls at P* = 6

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Fig. 13

Comparison of best case local heat transfer for orifice and nozzle plates with parallel confining walls at P* = 6 and ReDn=14,000

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Fig. 14

Increasing the confining wall angle, with all other parameters being constant, enhances the stagnation region heat transfer and degrades the wall jet region heat transfer

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Fig. 15

Variation in heat transfer with Reynolds number for orifice plates, γ = 0 deg and Ln*=0

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Fig. 16

Variation in heat transfer with Reynolds number for angled confining wall, γ = 5 deg

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Fig. 17

Variation in heat transfer with jet height

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