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Research Papers

Parametric Study of the Effect of the Vapor Chamber Characteristics on Its Performance

[+] Author and Article Information
Hamdy Hassan

UVHC,
TEMPO-DF2T,
F-59313 Valenciennes, France;
Mechanical Engineering Department,
Assuit University,
71515 Assiut, Egypt
e-mail: hamdyaboali@yahoo.com

Souad Harmand

UVHC,
TEMPO-DF2T,
F-59313 Valenciennes, France;
Université Lille Nord de France,
F-59000 Lille, France
e-mail: souad.harmand@univ-valenciennes.fr

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the Journal of Heat Transfer. Manuscript received April 24, 2012; final manuscript received December 20, 2012; published online September 23, 2013. Assoc. Editor: Sujoy Kumar Saha.

J. Heat Transfer 135(11), 111008 (Sep 23, 2013) (13 pages) Paper No: HT-12-1185; doi: 10.1115/1.4024613 History: Received April 24, 2012; Revised December 20, 2012

In this work, the effect of vapor chamber characteristics, the properties of its working fluid and the operating parameters on the vapor chamber performance are studied. Also, the effects of these parameters on the cooling process are considered. A three dimensional hydrodynamic model is used for solving the fluid flow through the liquid and vapor regions of the vapor chamber. The hydrodynamic model is coupled with a three dimensional thermal model to calculate the model temperature. The hydrodynamic model takes into consideration the circulation of liquid between the two wick regions. An implicit finite difference method is used to solve the numerical model and a validation of the numerical model is presented. The effect of porosity of the wick material, wick structure, solid wall material, working fluid, wick region thickness, vapor region thickness, power input, and heat transfer coefficient of the cooling fluid are taken in the study. Their effects on the heat pipe temperature, pressure difference of the heat pipe, liquid and vapor velocities and mass evaporated are studied. The results show that, to increase the cooling performance of the heat pipe, the porosity, wick thickness, power input, and vapor region thickness should be decreased and the heat transfer coefficient should be increased. To minimize the maximum pressure difference of the heat pipe, increase porosity, wick thickness, and vapor thickness and decrease heat transfer coefficient and power input. The study shows that the increase of wick thickness by a factor of four decreases the maximum pressure difference by about 75% and increases the maximum vapor chamber temperature 30%. It also shows that the vapor region thickness has an insignificant effect on the vapor chamber temperature and pressure. The increase of the heat transfer coefficient of the cooling liquid decreases its effect on heat pipe performance.

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References

Figures

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Fig. 1

Model used in the study (dimensions mm)

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Fig. 2

Comparison between the numerical results and the results of Ranjan et al. [24] for the temperature of the heat pipe on the top surface (evaporator side) and the bottom surface (condenser side)

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Fig. 3

Comparison between the numerical results and the results of Ranjan et al. [24] for the evaporated and condensed mass flux

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Fig. 4

Effect of wick thickness on the maximum heat pipe temperature

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Fig. 5

Effect of wick thickness on the (a) maximum pressure difference, (b) maximum mass flux evaporated, (c) maximum vapor velocity, and (d) maximum liquid velocity

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Fig. 8

Effect of power input on the maximum heat pipe temperature

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Fig. 9

Effect of power input on the (a) maximum pressure difference, (b) maximum mass flux evaporated, (c) maximum vapor velocity, and (d) maximum liquid velocity

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Fig. 10

Effect of heat transfer coefficient of the cooling fluid on the maximum heat pipe temperature

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Fig. 11

Effect of heat transfer coefficient of cooling fluid on the (a) maximum pressure difference, (b) maximum mass flux evaporated, (c) maximum vapor velocity, and (d) maximum liquid velocity

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Fig. 6

Effect of vapor thickness on the maximum heat pipe temperature

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Fig. 7

Effect of vapor thickness on the (a) maximum pressure difference, (b) maximum mass flux evaporated, (c) maximum vapor velocity, and (d) maximum liquid velocity

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Fig. 12

Effect of wick porosity on the maximum heat pipe temperature for different working fluid of the wrapped screen wick

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Fig. 13

Effect of working fluid construction at different porosities on the (a) maximum pressure difference, (b) maximum mass flux evaporated, (c) maximum vapor velocity, and (d) maximum liquid velocity for wrapped screen wick

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Fig. 14

Effect of wick porosity on the maximum heat pipe temperature for different working fluid of the packed sphere wick

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Fig. 15

Effect of working fluid construction at different porosities on the (a) maximum pressure difference, (b) maximum mass flux evaporated, (c) maximum vapor velocity, and (d) maximum liquid velocity for packed sphere wick

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Fig. 16

Effect of wick porosity on the maximum heat pipe temperature for different working fluid of the packed sphere wick

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Fig. 17

Effect of working fluid construction at different porosities on the (a) maximum pressure difference, (b) maximum mass flux evaporated, (c) maximum vapor velocity and (d) maximum liquid velocity for packed sphere wick

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