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Research Papers: Evaporation, Boiling, and Condensation

Numerical Simulation of Dynamics and Heat Transfer Associated With a Single Bubble in Subcooled Boiling and in the Presence of Noncondensables

[+] Author and Article Information
Jinfeng Wu

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

Vijay K. Dhir1

Department of Mechanical and Aerospace Engineering, Henry Samueli School of Engineering and Applied Science, University of California, Los Angeles, Los Angeles, CA 90095vdhir@seas.ucla.edu

1

Corresponding author.

J. Heat Transfer 133(4), 041502 (Jan 10, 2011) (14 pages) doi:10.1115/1.4000979 History: Received July 31, 2009; Revised November 06, 2009; Published January 10, 2011; Online January 10, 2011

During phase change at the bubble-liquid interface, under subcooled boiling conditions, noncondensable gases dissolved in the liquid will be injected into the bubble along with vapor. Due to heat transfer into subcooled liquid, vapor will condense in the upper regions of the bubble while noncondensables will continue to accumulate. Subsequently, thermocapillary convection caused by nonuniform saturation temperature at the interface may occur. The aim of this work is to investigate the effects of noncondensables on heat transfer and bubble dynamics. The numerical results show that the effects of noncondensables on 5°C subcooled boiling of water are minor in terms of the equilibrium bubble diameter and overall Nusselt number. However, induced flow pattern around the bubble is altered, especially under reduced gravity conditions.

Copyright © 2011 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Macro- and microregions in numerical simulation

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Figure 2

Comparison of free surface deformation for Nu=0, Re=Ma=100, and Ca=0.1 and 0.05 between Sasmal and Hochstein (22) and the current study

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Figure 3

Growth history for R−113 at a wall superheat=5°C, liquid subcooling=5°C, contact angle=20 deg, pressure=3.17×105 Pa, and g/ge=10−4

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Figure 4

(a) Growth rate and (b) Nu versus time for wall superheat=8°C, subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, and g/ge=1

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Figure 5

Mass of air inside the bubble for wall superheat=8°C, subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, and g/ge=1

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Figure 6

Isotherms and velocity field for wall superheat=8°C, liquid subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, g/ge=1, Cg,0=0.4, and Cg,l=2.486×10−6 (temperature increment between isotherms is 2.57°C)

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Figure 7

Gas mass fraction distribution for wall superheat=8°C, subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, g/ge=1, Cg,l=2.486×10−6, Cg,0=0.2 (left), and Cg,0=0.4 (right); (a) t=0.01 s and (b) t=0.27 s

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Figure 8

(a) Growth rate and (b) Nu versus time for wall superheat=8°C, subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, and g/ge=10−2

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Figure 9

Interfacial velocity in tangential direction as a function of location along bubble interface for wall superheat=8°C, subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, and g/ge=10−2

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Figure 10

Isotherms and velocity field for wall superheat=8°C, liquid subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, g/ge=10−2, Cg,0=0, and Cg,l=0 (temperature increment between isotherms is 2.57°C)

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Figure 11

Isotherms and velocity field for wall superheat=8°C, liquid subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, g/ge=10−2, Cg,0=0.2, and Cg,l=2.486×10−6 (temperature increment between isotherms is 2.57°C)

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Figure 12

Interferograms for CFC112/CFC12 at t=8.5 s(24)

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Figure 13

(a) Growth rate and (b) Nu versus time for wall superheat=8°C, subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, and g/ge=10−4

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Figure 14

Isotherms and velocity field for wall superheat=8°C, liquid subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, g/ge=10−4, Cg,0=0, and Cg,l=0 (temperature increment between isotherms is 2.57°C)

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Figure 15

Isotherms and velocity field for wall superheat=8°C, liquid subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, g/ge=10−4, Cg,0=0.2, and Cg,l=2.486×10−6 (temperature increment between isotherms is 2.57°C)

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Figure 16

Interferometer picture of thermocapillary jet flow generated from a 1 mm-diameter circular heater at subcooled boiling (8)

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Figure 17

Saturation temperature as a function of location along the bubble interface for wall superheat=8°C, subcooling=5°C, contact angle=38 deg, pressure=1.013×105 Pa, and g/ge=10−4

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