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Research Papers

Analytical Modeling of Annular Flow Boiling Heat Transfer in Mini- and Microchannel Heat Sinks

[+] Author and Article Information
A. Megahed

Department of Mechanical and Industrial Engineering, Concordia University, Montreal, QC, H3G 1M8, Canada

I. Hassan1

Department of Mechanical and Industrial Engineering, Concordia University, Montreal, QC, H3G 1M8, Canadaibrahimh@alcor.concordia.ca

1

Corresponding author.

J. Heat Transfer 132(4), 041012 (Feb 22, 2010) (11 pages) doi:10.1115/1.4000887 History: Received April 06, 2009; Revised November 11, 2009; Published February 22, 2010; Online February 22, 2010

An analytical model is proposed to predict the flow boiling heat transfer coefficient in the annular flow regime in mini- and microchannel heat sinks based on the separated model. The modeling procedure includes a formulation for determining the heat transfer coefficient based on the wall shear stress and the local thermophysical characteristics of the fluid based on the Reynolds’ analogy. The frictional and acceleration pressure gradients within the channel are incorporated into the present model to provide a better representation of the flow conditions. The model is validated against collected data sets from the literature produced by different authors under different experimental conditions, different fluids, and with mini- and microchannels of hydraulic diameters falling within the range of 921440μm. The accuracy between the experimental and predicted results is achieved with a mean absolute error of 10%. The present analytical model can correctly predict the different trends of the heat transfer coefficient reported in the literature as a function of the exit quality. The predicted two-phase heat transfer coefficient is found to be very sensitive to changes in mass flux and saturation temperature. However, it is found to be mildly sensitive to the change in heat flux.

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Figures

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Figure 1

(a) Parameters in the annular flow for force balance on the liquid film; (b) control volume analysis of the vapor differential element in the annular flow

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Figure 2

Revellin and Thome (20) flow regime map for diabatic two-phase flow in microchannels

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Figure 3

(a) Liquid-phase Reynolds number as a function of the exit quality (b) vapor-phase Reynolds number as a function of the exit quality

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Figure 4

Predicted and experimentally determined two-phase heat transfer coefficients

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Figure 5

Comparison of heat transfer coefficient at constant mass flux: (a) Lee and Lee (2) (R113, G=208 kg/m2 s, and q=5 kW/m2); (b) Yun (3) (R410A, G=400 kg/m2 s, and q=20 kW/m2)

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Figure 6

Heat transfer coefficient predictions by the analytical model compared with (a) Dong (5) (R141b, G=500 kg/m2 s, and q=100 kW/m2) and (b) Yen (7) (R123, G=400 kg/m2 s, and q=25.32 kW/m2)

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Figure 7

Two-phase heat transfer coefficient as a function of the exit quality predicted by the analytical model compared with the data of Agostini (18) (R236fa and G=984 kg/m2 s)

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Figure 8

The effect of mass flux on the experimental and predicted heat transfer coefficient: experimental data of (a) Dong (5)(q=100 kW/m2) and (b) Agostini (18)(q=236 kW/m2)

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Figure 9

Predicted influence of heat flux on two-phase heat transfer coefficient as a function of the exit quality, compared with experimental data of (a) Dong (5) for the variation in the heat flux for G=500 kg/m2 s, and (b) Agonstini (18) (G=810 kg/m2 s)

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Figure 10

Effect of the saturation temperature on the two-phase heat transfer coefficient: experimental data of Agostini (18) (G=810 kg/m2 s and q=18.6 kW/m2)

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