Research Papers

A Numerical Model of a Reciprocating-Mechanism Driven Heat Loop for Two-Phase High Heat Flux Cooling

[+] Author and Article Information
Olubunmi Popoola, Ayobami Bamgbade, Yiding Cao

Department of Mechanical and
Materials Engineering,
Florida International University,
Miami, FL 33174

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF THERMAL SCIENCE AND ENGINEERING APPLICATIONS. Manuscript received January 29, 2016; final manuscript received May 23, 2016; published online July 27, 2016. Assoc. Editor: Amir Jokar.

J. Thermal Sci. Eng. Appl 8(4), 041006 (Jul 27, 2016) (12 pages) Paper No: TSEA-16-1027; doi: 10.1115/1.4034059 History: Received January 29, 2016; Revised May 23, 2016

An effective design option for a cooling system is to use a two-phase pumped cooling loop to simultaneously satisfy the temperature uniformity and high heat flux requirements. A reciprocating-mechanism driven heat loop (RMDHL) is a novel heat transfer device that could attain a high heat transfer rate through a reciprocating flow of the two-phase working fluid inside the heat transfer device. Although the device has been tested and validated experimentally, analytical or numerical study has not been undertaken to understand its working mechanism and provide guidance for the device design. The objective of this paper is to develop a numerical model for the RMDHL to predict its operational performance under different working conditions. The developed numerical model has been successfully validated by the existing experimental data and will provide a powerful tool for the design and performance optimization of future RMDHLs. The study also reveals that the maximum velocity in the flow occurs near the wall rather than at the center of the pipe, as in the case of unidirectional steady flow. This higher velocity near the wall may help to explain the enhanced heat transfer of an RMDHL.

Copyright © 2016 by ASME
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Fig. 1

Schematic of an RMDHL

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Fig. 2

The geometry and boundary conditions for this study

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Fig. 3

The experimental setup for RMDHL study [8]

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Fig. 4

A photograph of the fabricated RMDHL [8]

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Fig. 5

(a) Open-loop geometry configuration for numerical model of the RMDHL, (b) location of the planes for data analysis of the RMDHL, and (c) grid distribution for numerical simulations of the RMDHL

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Fig. 6

Comparison of numerical and experimental temperature distributions along the heat loop at different heat inputs for a coolant inlet temperature of 313 °C

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Fig. 7

Comparison of numerical and experimental temperature distributions along the heat loop at different heat inputs for a coolant inlet temperature of 338 °C

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Fig. 8

Temperature contours of the working fluid for (a) 313 K condenser with 166 W at 715.4 s, (b) 338 K condenser with 162 W at 474.8 s, and (c) 323 K condenser with 171 W at 624.8 s

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Fig. 9

Plot of fluid temperature versus distance from the heater location

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Fig. 10

Velocity profile of cooling liquid in the evaporator over plane 2 with 313 K condenser: (a) 166 W at 474.8 s, (b) 166 W at 624.8 s, and (c) 166 W at 715.4 s

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Fig. 11

Temperature contours of the heat loop showing surface temperature uniformity for 323 K condenser inlet temperature with heat flux at (a) 75.9 W, (b) 126.9 W, (c) 156 W, and (d) 171 W

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Fig. 12

Regression analysis for the SD of the of the cold plate static temperature for operating conditions




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