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Evaporation, Boiling, and Condensation

Critical Heat Flux in Submerged Jet Impingement Boiling of Water Under Subatmospheric Conditions

[+] Author and Article Information
Ruander Cardenas

School of Mechanical, Industrial, and Manufacturing Engineering,  Oregon State University, 204 Rogers Hall, Corvallis, OR 97331-6001

Vinod Narayanan1

School of Mechanical, Industrial, and Manufacturing Engineering,  Oregon State University, 204 Rogers Hall, Corvallis, OR 97331-6001vinod.narayanan@oregonstate.edu

1

Corresponding author.

J. Heat Transfer 134(8), 081502 (Jun 05, 2012) (10 pages) doi:10.1115/1.4006206 History: Received March 24, 2011; Revised February 01, 2012; Published June 05, 2012; Online June 05, 2012

Critical heat flux (CHF) characteristics in submerged jet impingement boiling of water on a heated copper surface are investigated at subatmospheric conditions. Data are reported at a fixed surface-to-nozzle diameter ratio of 23.8 and a fixed surface-to-nozzle height of 6 nozzle diameters. Three subatmospheric pressures of 0.176 bars, 0.276 bars, and 0.477 bars are considered, corresponding to fluid saturation temperatures of 57.3 °C, 67.2 °C, and 80.2 °C and liquid-to-vapor density ratios of 8502, 5544, and 3295, respectively. At each pressure, CHF for varying jet Reynolds numbers (Re) in the range 0–14,000 are compared for two different surface finishes of roughness average values of 123 nm and 33 nm. The CHF enhancement observed with increasing Re is depicted in a nondimensional CHF map. Existing correlations available in the literature, which are out of range of the current experimental conditions, are found to poorly predict the obtained CHF data. A CHF correlation that captures the entire experimental data set within an average error of ±3% and a maximum error of ±13% is developed. The effect of fluid subcooling on submerged jet CHF is studied at the lowest pressure of 0.176 bars. Subcooled jet CHF is found to be well predicted from saturated jet CHF by using a typical subcooled pool boiling CHF correction factor.

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Copyright © 2012 by American Society of Mechanical Engineers
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Figures

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Figure 1

Simplified schematic of the experimental facility

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Figure 2

Schematic of test section

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Figure 3

Effect of surface roughness on surface wetting—Surface roughness profile sample over a 73 × 73 μm2 area (50 × 50 pixels) for (a) a 123 nm Ra surface and (b) a 33 nm Ra surface. Static contact angles on (c) a 123 nm surface and (d) a 33 nm surface

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Figure 4

Comparison of saturated pool boiling CHF with Kutateladze’s correlation

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Figure 5

Critical heat flux data as a function of Re for: (a) 123 nm Ra surface and (b) 33 nm Ra surface

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Figure 6

Inverse effectiveness as a function of Re for a 33 nm Ra surface

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Figure 7

CHF map for submerged jet impingement boiling

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Figure 8

Realized jet enhancement over the total enhancement potential for water on a 33 nm Ra surface

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Figure 9

Comparison of experimental data with correlations at P = 0.276 bars. □, C.1; ▷, C.2; ◁, C.3; ◯, C.4; + , C.5; >, C.6; <, C.7; ▪, 123 nm Ra surface; ▲, 33 nm Ra surface

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Figure 10

Comparison of developed correlation (Eqs. 4,5) with experimental data for the 33 nm Ra surface

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Figure 11

Effect of fluid subcooling on submerged jet CHF on a 33 nm Ra surface for P = 0.176 bars

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