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Research Papers: Evaporation, Boiling, and Condensation

Prediction of PF-5060 Spray Cooling Heat Transfer and Critical Heat Flux

[+] Author and Article Information
Bahman Abbasi

Jungho Kim1

 Department of Mechanical Engineering, University of Maryland, College Park, MD 20742 e-mail:kimjh@umd.edu

1

Corresponding Author.

J. Heat Transfer 133(10), 101504 (Aug 15, 2011) (12 pages) doi:10.1115/1.4004012 History: Received October 20, 2010; Revised April 12, 2011; Published August 15, 2011; Online August 15, 2011

Spray cooling heat transfer measurements of PF-5060 on smooth flat surfaces were obtained using a microheater array operated at constant temperatures using two nozzles (hollow cone and full cone), three nozzle-to-heater standoff distances (3, 5, and 7 mm), four nozzle operating pressures (207 kPa, 345 kPa, 483 kPa, and 689 kPa), and three subcooling levels (11 °C, 21 °C, 31 °C). A separate test setup was used to measure the local normal pressures produced by the sprays. The critical heat flux was found to depend primarily on the local normal pressure and the liquid subcooling. Furthermore, the temperature at which CHF occurred was within a narrow temperature band (about ±5 °C) for smooth flat surfaces over a wide range of spray conditions. The single-phase correlation previously proposed by the authors and the CHF correlation presented in this work were then combined to predict local spray cooling curve within ±25% of the measured values in the spray impingement zone.

Copyright © 2011 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Photographs of spray produced by the hollow (left) and full cone (right) nozzles operated at 345 kPa

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Figure 2

Pressure measurement apparatus

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Figure 3

Schematic of the pressure plate and pressure tap geometry

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Figure 4

Photograph of the microheater array used to measure heat flux distribution

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Figure 5

Heat transfer measurement apparatus

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Figure 6

Heat flux distribution for the hollow cone (right) and full cone (left) sprays at 90 °C wall temperature and 689 kPa spray pressure

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Figure 7

Radially averaged boiling curves for hollow cone sprays operated at various nozzle pressures and standoff distances; the CHF location is designated using a solid symbol

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Figure 8

Radially averaged boiling curves for full cone sprays operated at various nozzle pressures and standoff distances; the CHF location is designated using a solid symbol

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Figure 9

CHF magnitude versus and occurrence temperatures at different wall temperatures

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Figure 10

CHF versus impingement pressure for hollow cone and full cone sprays at various liquid temperatures

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Figure 11

Sample spray cooling curve

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Figure 12

Measured and predicted hollow cone spray cooling curves in the impingement zone for different subcoolings, standoff distances, spray nozzle pressures, and radii

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Figure 13

Measured and predicted cone spray cooling curves in the impingement zone for different subcoolings, standoff distances, spray nozzle pressures, and radii

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Figure 14

Measured versus predicted heat flux for all the data in the impingement zone for various sprays labeled according to subcooling and standoff distances (a) and radii and heat transfer regime (b)

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Figure 15

Comparison of area-averaged CHF predictions of the present model and that of Visaria and Mudawar [27]

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