Research Papers: Two-Phase Flow and Heat Transfer

Cavitation Bubble Collapse Near a Heated Wall and Its Effect on the Heat Transfer

[+] Author and Article Information
Bin Liu

Institute of Engineering Thermophysics,
Chinese Academy of Sciences,
Beijing 100190, China
University of Chinese Academy of Sciences,
Beijing 100080, China

Jun Cai

e-mail: caijun@mail.etp.ac.cn

Fengchao Li

Institute of Engineering Thermophysics,
Chinese Academy of Sciences,
Beijing 100190, China

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received October 7, 2012; final manuscript received March 14, 2013; published online November 5, 2013. Assoc. Editor: W. Q. Tao.

J. Heat Transfer 136(2), 022901 (Nov 05, 2013) (7 pages) Paper No: HT-12-1546; doi: 10.1115/1.4024071 History: Received October 07, 2012; Revised March 14, 2013

In the present work, a numerical investigation on the mechanism of heat transfer enhancement by a cavitation bubble collapsing near a heated wall has been presented. The Navier–Stokes equations and volume of fluid (VOF) model are employed to predict the flow state and capture the liquid-gas interface. The model was validated by comparing with the experimental data. The results show that the microjet violently impinges on the heated wall after the bubble collapses completely. In the meantime, the thickness of the thermal boundary layer and the wall temperature decrease significantly within the active scope of the microjet. The fresh low-temperature liquid and the impingement brought by the microjet should be responsible for the heat transfer reinforcement between the heated wall and the liquid. In addition, it is found that the impingement width of the microjet on the heated wall always keeps 20% of the bubble diameter. And, the enhancement degree of heat transfer significantly depends on such factors as stand-off distance, saturated vapor pressure, and initial bubble radius.

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Fig. 1

Calculation domain

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Fig. 2

Grid independency test

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Fig. 3

The comparison of bubble profiles with the experimental results. (a) Philipp and Lauterborn [12], and (b) present results.

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Fig. 4

Bubble profiles at different t *. (a) t * = 0, (b) t * = 0.8708, (c) t * = 0.9447, (d) t * = 1, (e) t * = 1.0143, (f) t * = 1.0189, (g) t * = 1.0227, and (h) t * = 1.0286.

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Fig. 5

Temperature distributions on the solid wall at different t *

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Fig. 6

The near-wall microjet vector fields at t * = 1.0286

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Fig. 7

The near-wall temperature field at t * = 1.0286

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Fig. 8

Changes of the dimensionless temperature at the central point of the wall for different γ

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Fig. 9

Distributions of the dimensionless temperature on the solid wall under different γ at t* = 1.0286

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Fig. 10

Changes of dimensionless temperature at the central point of the wall under the different saturated vapor pressures

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Fig. 11

Distributions of the dimensionless temperature on the solid wall under the different saturated vapor pressures at t * = 1.0286

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Fig. 12

Changes of the dimensionless temperature at the central point of the wall under the different initial bubble radii

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Fig. 13

Distributions of the dimensionless temperature on the solid wall under the different initial bubble radii at t * = 1.0286

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Fig. 14

The impingement width versus the bubble radius




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