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Research Papers

Entropy Analysis of Mixed Convective Condensation by Evaluating Fan Velocity With a New Approach

[+] Author and Article Information
Dipanka Bhuyan, Pradip Lingfa

Department of Mechanical Engineering,
North Eastern Regional Institute
of Science and Technology,
Itanagar 791109, India

Asis Giri

Department of Mechanical Engineering,
North Eastern Regional Institute
of Science and Technology,
Itanagar 791109, India
e-mail: measisgiri@gmail.com

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF THERMAL SCIENCE AND ENGINEERING APPLICATIONS. Manuscript received October 15, 2017; final manuscript received January 18, 2018; published online May 8, 2018. Assoc. Editor: Wei Li.

J. Thermal Sci. Eng. Appl 10(5), 051003 (May 08, 2018) (9 pages) Paper No: TSEA-17-1391; doi: 10.1115/1.4039355 History: Received October 15, 2017; Revised January 18, 2018

Present paper conducts an extensive numerical study on entropy analysis of mixed convective condensation inside a vertical parallel plate channel. A new approach is proposed to separate pump velocity component/Reynolds number from inlet mixed convection velocity. Influence of inlet governing parameters on condensation heat and mass transfer at different inlet pressure, velocity, channel length, and width are widely studied. The central focus of this paper is to study entropy generation under mixed convective condensation. Variation of local as well as overall entropy generation and second law efficiency for different geometric and environmental conditions are presented. For effective condenser design, present study provides two important correlations of overall volumetric entropy generation due to thermal transport and overall volumetric entropy generation due to mass transport.

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References

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Figures

Grahic Jump Location
Fig. 5

Contour of local volumetric rate of entropy generation due to pure thermal transport at (a) pin = 0.75 bar, H = 0.005 m, Uin,mix = 1000, Tin = 60 °C, L = 0.75 m, (b) pin = 0.75 bar, H = 0.005 m, Uin,mix = 2000, Tin = 60 °C, L = 0.75 m, (c) pin = 3 bar, H = 0.005 m, Uin,mix = 1000, Tin = 60 °C, L = 0.75 m, and (d) pin = 3 bar, H = 0.005 m, Uin,mix = 2000, Tin = 60 °C, L = 0.75 m

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Fig. 6

Isotherm contours at pin = 0.75 bar and pin = 3.0 bar

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Fig. 3

Axial developments of dimensionless local average pressure defect for (a) Pin = 1.5 bar and (b) Pin = 3.0 bar

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Fig. 7

Contour of local volumetric rate of entropy generation due to mass transport at (a) pin = 0.75 bar, H = 0.005 m, Uin,mix = 1000, Tin = 60 °C, L = 0.75 m, (b) pin = 0.75 bar, H = 0.005 m, Uin,mix = 2000, Tin = 60 °C, L = 0.75 m, (c) pin = 3 bar, H = 0.005 m, Uin,mix = 1000, Tin = 60 °C, L = 0.75 m, and (d) pin = 3 bar, H = 0.005 m, Uin,mix = 2000, Tin = 60 °C, L = 0.75 m

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Fig. 4

Variation of natural convection velocity with Reynolds number at (a) H = 0.005 m and (b) H = 0.01 m

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Fig. 8

(a) Variation of overall volumetric entropy generation due to pure thermal transport with inlet mixed convection velocity and (b) variation of overall entropy generation due to mass transfer with inlet mixed convection velocity: (a) Tin = 60 °C, Twall = 30 °C and (b) Tin = 60 °C, Twall = 30 °C

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Fig. 9

(a) Plot of computed and correlated data of overall entropy generation due to pure thermal transport and (b) due to pure mass transfer

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Fig. 2

Validation with results of Lebedev et al. [15], Rao et al. [16], and Hammami et al. [17]

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Fig. 10

Variation of second law efficiency with inlet mixed convection velocity

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Fig. 11

Variation of Carnot available work with inlet mixed convection velocity

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