Research Papers: Max Jakob Award Paper

Review and Advances in Heat Pipe Science and Technology

[+] Author and Article Information
Amir Faghri

Department of Mechanical Engineering,
University of Connecticut,
Storrs, CT 06269
e-mail: faghri@engr.uconn.edu

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received July 16, 2012; final manuscript received August 6, 2012; published online October 10, 2012. Editor: Terrence W. Simon.

J. Heat Transfer 134(12), 123001 (Oct 10, 2012) (18 pages) doi:10.1115/1.4007407 History: Received July 16, 2012; Revised August 06, 2012

Over the last several decades, several factors have contributed to a major transformation in heat pipe science and technology applications. The first major contribution was the development and advances of new heat pipes, such as loop heat pipes (LHPs), micro and miniature heat pipes, and pulsating heat pipes (PHPs). In addition, there are now many commercial applications that have helped contribute to the recent interest in heat pipes. For example, several million heat pipes are manufactured each month for applications in CPU cooling and laptop computers. Numerical modeling, analysis, and experimental simulation of heat pipes have significantly progressed due to a much greater understanding of various physical phenomena in heat pipes as well as advances in computational and experimental methodologies. A review is presented hereafter concerning the types of heat pipes, heat pipe analysis, and simulations.

Copyright © 2012 by ASME
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Fig. 1

(a) Axial variation of the liquid–vapor interface and the vapor and (b) liquid pressures along the heat pipe at moderate vapor flow rates

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Fig. 2

Thermal resistance model of a typical heat pipe

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Fig. 4

Pulsating heat pipe (a) unlooped and (b) looped

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Fig. 5

Schematic of an inverted meniscus type evaporator with the triangular fin: (a) with low heat fluxes and (b) with high heat fluxes

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Fig. 6

Conceptual design of a leading edge heat pipe

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Fig. 7

The axial interface temperature profile along the sodium heat pipe with Q = 560 W, Rv = 0.007 m, Le = 0.1 m, La = 0.05 m, kl = 66.2 W/m2 K, ks = 19.0 W/m2 K, δl = 0.0005 m, δw = 0.001 m [38]

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Fig. 8

Heat pipe wall and vapor temperature versus axial location for (a) single evaporator and (b) two evaporators [40]

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Fig. 9

Centerline vapor temperature for transient response to heat input pulse: (a) convective boundary condition and (b) radiative boundary condition [50]

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Fig. 10

Leading edge heat pipe outer wall temperature distribution [53]

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Fig. 11

Wall temperature prediction for frozen start up by Cao and Faghri [60] compared with the experimental data of (a) Faghri et al. [52] and (b) Ponnappan [61]

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Fig. 12

Analytical wall temperature prediction for frozen startup by Cao and Faghri [62] compared with experimental data of (a) Faghri et al. [52] and (b) Ponnappan [61]

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Fig. 13

Comparison of the model predictions with experimental data ((symbols) experimental data from Hopkins et al. [22] and (lines) numerical simulation results from the Do et al. [68] model): (a) maximum heat transport rate and (b) wall temperature. (Adopted from Do et al. [68].)

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Fig. 14

Comparison of LHP modeling predictions [100] with experimental results of (a) Chuang [96] for ammonia as the working fluid and (b) Boo and Chung [108] for acetone as the working fluid

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Fig. 15

Heat transfer rate: (a) sensible heat and (b) evaporative heat [142]




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