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TECHNICAL PAPERS: Boiling and Condensation

Study of Subcooled Film Boiling on a Horizontal Disc: Part I—Analysis

[+] Author and Article Information
D. Banerjee, V. K. Dhir

Mechanical and Aerospace Engineering Department, University of California, Los Angeles, Los Angeles, CA 90095

J. Heat Transfer 123(2), 271-284 (Oct 31, 2000) (14 pages) doi:10.1115/1.1345889 History: Received January 20, 2000; Revised October 31, 2000
Copyright © 2001 by ASME
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References

Figures

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Plot of crests of the three-dimensional Taylor wave on a circular plate for (m,n) values of (4, 1), (8, 2), (15, 3), (21, 4), and (27, 5). The circular plate, radial rings and wave crests are shown elliptical in the figure.
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Computational domain for solution of fluid side governing equations. In the computations H was set to 15, R was set to 4.34. The value of B changed as the height of the vapor bubble changed with time. The number of grids used in the vapor side was 42×22, with 42 grid points along the radial direction. The number of grids used in the liquid side was 42×42 in simulation runs for saturated film boiling and 42×77 in simulation runs for subcooled film boiling.
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(a) Spatial distribution of velocity vectors for ΔTW=100°C and ΔTsub=10°C at t=5.5. Time is non-dimensionalized with respect to to and velocity is non-dimensionalized with respect to uo. The length of arrows plotted in the figure at the right are 2 times the respective length of arrows in the figure on the left; (b) spatial distribution of isotherms (θ) for ΔTW=100°C and ΔTsub=10°C at t=5.5. Time is non-dimensionalized with respect to to.
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Schematic of the various heat fluxes at the interface and at the wall in subcooled film boiling
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Values of m obtained from solution of Eqs. (60) and (61) for spatial distribution of wave peaks corresponding to wave number knd both in the radial and in the circumferential directions
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Plot of grid locations for film boiling of saturated PF-5060 at Jal*=0.77, and Jav*=0.133, i.e., ΔTW=100°C, and ΔTsub=10°C. The radial and vertical distances are non-dimensionalized with respect to lo. Time t is non-dimensionalized with respect to to.
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Numerical predictions for temporal evolution of the liquid-vapor interface for wall superheat, ΔTW=100°C and ΔTsub=5°C and 10°C. The radial distances and interface heights are non-dimensionalized with respect to lo. Time t is non-dimensionalized with respect to to.
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Comparison of interface shape at bubble departure for wall superheat, ΔTW=100°C, and liquid subcoolings, ΔTsub=0°C, 5°C, and 10°C. The interface height and radius are non-dimensionalized with respect to lo.
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(a) Spatial distribution of velocity vectors for ΔTW=100°C,ΔTsub=10°C and t=3. Time is non-dimensionalized with respect to to and velocity is non-dimensionalized with respect to uo. The length of arrows plotted in the figure at the right are 2 times the respective length of arrows in the figure on the left; (b) spatial distribution of isotherms (θ) for ΔTW=100°C and ΔTsub=10°C at t=3. Time is non- dimensionalized with respect to to.
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Plot of temporal variation of local values of wall Nu for wall superheat, ΔTW=100°C and liquid subcooling, ΔTsub=5°C and 10°C. The radial distances are non-dimensionalized with respect to lo. Time t is non-dimensionalized with respect to to.
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Temporal variation of area averaged Nu at wall for wall superheat, ΔTW=100°C and liquid subcooling, ΔTsub=0°C, 5°C, and 10°C. Time is non-dimensionalized with respect to to.
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Temporal variation of area averaged Nu in the vapor phase for wall siperheat, ΔTW=100°C and liquid subcooling, ΔTsub=0°C, 5°C, and 10°C. Time is non-dimensionalized with respect to to.
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Temporal variation of component of averaged Nu in the liquid phase for wall superheat, ΔTW=100°C and liquid subcooling, ΔTsub=5°C and 10°C. Time is non-dimensionalized with respect to to.
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Plot of local Nu at interface for production of vapor entering the film for t=0, 3, 4.9, and 5.5. Time is non-dimensionalized with respect to to and radial distance is non-dimensionalized with respect to lo.

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