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Research Papers: Evaporation, Boiling, and Condensation

Numerical Simulation of Pool Boiling: A Review

[+] Author and Article Information
Vijay K. Dhir

e-mail: vdhir@seas.ucla.edu

Eduardo Aktinol

Mechanical and Aerospace Engineering Department,
Henry Samueli School of Engineering and Applied Science,
University of California Los Angeles,
420 Westwood Plaza,
Los Angeles, CA 90095

Manuscript received November 18, 2012; final manuscript received January 14, 2013; published online May 16, 2013. Assoc. Editor: Leslie Phinney.

J. Heat Transfer 135(6), 061502 (May 16, 2013) (17 pages) Paper No: HT-12-1614; doi: 10.1115/1.4023576 History: Received November 18, 2012; Revised January 14, 2013

A review of numerical simulation of pool boiling is presented. Details of the numerical models and results obtained for single bubble, multiple bubbles, nucleate boiling, and film boiling are provided. The effect of such parameters such as wall superheat, liquid subcooling, contact angle, gravity level, noncondensables, and conjugate heat transfer are also included. The numerical simulation results have been validated with data from well designed experiments.

Copyright © 2013 by ASME
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References

Figures

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Fig. 1

Predictive model for nucleate boiling

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Fig. 2

Computational domain used in numerical simulations

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Fig. 3

Effect of wall superheat on bubble growth: (a) growth history and (b) bubble shape at departure for saturated water at φ = 38 deg (from [21])

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Fig. 4

(a) Growth rates for water and PF-5060 and (b) normalized departure diameter and growth time (ΔTw = 8 °C, ΔTsub = 0 °C, g /ge = 1.0, from [30])

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Fig. 5

Comparison of numerically predicted bubble growth for water for various contact angles

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Fig. 6

Contributions of the various heat transfer mechanisms (from [30])

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Fig. 7

Variation of heat transfer rate from the wall to liquid and vapor as a function of time (from [30])

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Fig. 8

Comparison of temperature and flow field for (a) pure vapor and (b) with noncondensables (fluid: water, wall superheat = 8.0 °C, liquid subcooling = 5.0 °C, g /ge = 10−4, Cg,0 = 0.2, Cg,l = 2.48 × 10−6, from [33])

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Fig. 9

The dependence of (a) bubble departure diameter and (b) growth period on gravity level

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Fig. 10

Comparison of single bubble growth data with results from numerical simulations (from [39])

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Fig. 11

Comparison of experimental data with results from numerical simulations (from [39])

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Fig. 12

(a) Isotherms for water boiling on stainless steel (0.3 mm thick, qw = 1.1 W/cm2) and (b) comparison of numerical results and experimental correlation for bubble waiting time (copper, 1 mm thick, qw = 0.5 to 2.0 W/cm2, from [44])

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Fig. 13

Comparison of numerical and experimental bubble shapes during vertical merger (fluid: saturated water, ΔTw = 10 °C, g /ge = 1.0, φ = 38 deg, from [46])

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Fig. 14

Comparison of numerical and experimental bubble shapes during lateral merger (fluid: saturated water, ΔTw = 5 °C, g /ge = 1.0, φ = 38 deg, spacing = 1.5 mm, from [47])

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Fig. 15

Comparison of numerically predicted bubble growth with experimental data (from [47])

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Fig. 16

Comparison of single bubble and three inline bubbles (a) bubble growth and (b) forces acting in the vertical direction (fluid: saturated water, ΔTw = 10 °C, g /ge = 1, φ = 54 deg, spacing = 1.25 mm, from [40,48])

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Fig. 17

Effect of spacing (a) dimensionless bubble departure diameter, (b) dimensionless growth time, and (c) Nusselt number (fluid: sat. PF5060, ΔTw = 10 °C, φ = 10 deg, g /ge = 10−2, from [48])

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Fig. 18

Simulated commercial surface (from [48])

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Fig. 19

Comparison of experimental and predicted bubble shapes during nucleate boiling on a simulated commercial surface (a) g /ge = 1 and (b) g /ge = 10−2 (fluid: sat. water, ΔTw = 7 °C, from [48])

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Fig. 20

The variation of wall heat flux with wall superheat for saturated water (a) g /ge = 1 and (b) g /ge = 10−2 (from [48])

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Fig. 21

Bubble growth and merger for ΔTw = 25 °C (from [49])

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Fig. 22

Comparison of the numerical results with experimental data and correlations (from [49])

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Fig. 23

Evolution of liquid-vapor interface at near critical pressures (a) ΔTw = 10 °C, (b) ΔTw = 22 °C, and (c) ΔTw = 30 °C (from [6])

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Fig. 24

Comparison of predicted area-averaged wall Nusselt number with experimental data, for ΔTw = 100 °C and ΔTsub = 0 to 22 °C (from [57,58])

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Fig. 25

Evolution of liquid-vapor interface at g/ge = 1 (a) D = 0.125 mm and (b) D = 12.5 mm (from [7])

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