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Research Papers: Evaporation, Boiling, and Condensation

Modeling and Analysis of Supercritical Startup of a Cryogenic Loop Heat Pipe

[+] Author and Article Information
Lizhan Bai1

School of Aeronautical Science and Engineering,  Beihang University, Beijing 100191, P.R. Chinabailizhan@sina.com

Guiping Lin

School of Aeronautical Science and Engineering,  Beihang University, Beijing 100191, P.R. Chinabailizhan@sina.com

G. P. Peterson

Woodruff School of Mechanical Engineering,  Georgia Institute of Technology, Atlanta, GA 30318

Dongsheng Wen

School of Engineering and Materials Science,  Queen Mary University of London, London E1 4NS, UK

1

Corresponding author.

J. Heat Transfer 133(12), 121501 (Oct 03, 2011) (9 pages) doi:10.1115/1.4004595 History: Received January 13, 2011; Revised June 28, 2011; Published October 03, 2011; Online October 03, 2011

Supercritical startup of cryogenic loop heat pipes (CLHPs) has been investigated both analytically and experimentally. Mathematical model of the supercritical startup has been established using the nodal network method, and parametric study is conducted where the effects of working fluid charged pressure, parasitic heat load from the ambient, etc., on the supercritical startup characteristics are incorporated and evaluated. The result improves understanding of the effects of these parameters on supercritical startup and identification of those conditions under which supercritical startup can and will occur. In addition, the modeling effort has led to an enhanced understanding of supercritical startup performance.

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Copyright © 2011 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Schematic of a cryogenic loop heat pipe

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Figure 2

The nodal network of the transport/condenser lines

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Figure 3

Schematic of the primary evaporator and primary CC at stages 1 and 2

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Figure 4

The nodal network of the primary evaporator and primary CC at stages 1 and 2

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Figure 5

Schematic of the primary evaporator and primary CC at stage 3

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Figure 6

The nodal network of the primary evaporator and primary CC at stage 3

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Figure 7

Schematic of the secondary evaporator and the secondary CC at stage 1

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Figure 8

The nodal network of the secondary evaporator and the secondary CC at stage 1

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Figure 9

Schematic of the secondary evaporator and the secondary CC at stages 2 and 3

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Figure 10

The nodal network of the secondary evaporator and the secondary CC at stages 2 and 3

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Figure 11

Comparison of modeling results with experimental data

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Figure 12

Temperature variation of working fluid in the secondary evaporator for different charged pressures

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Figure 13

Vapor quality variation of working fluid in the secondary evaporator for different charged pressures

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Figure 14

Temperature variation of working fluid in the secondary evaporator for different thermal conductance between the secondary CC and heat sink

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Figure 15

Vapor quality variation of working fluid in the secondary evaporator for different thermal conductance between the secondary CC and heat sink

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Figure 16

Temperature drop of working fluid in the primary evaporator for different heat loads applied to the secondary evaporator

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Figure 17

Vapor quality variation of working fluid in the primary evaporator for different heat loads applied to the secondary evaporator

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Figure 18

Temperature drop of working fluid in the primary evaporator for different parasitic heat loads

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Figure 19

Vapor quality variation of working fluid in the primary evaporator for different parasitic heat loads

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Figure 20

Temperature variation of the primary evaporator wall for different parasitic heat loads

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Figure 21

Temperature variation of the primary evaporator wall for different startup heat loads

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