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TECHNICAL PAPERS

Second Law Analysis in a Partly Porous Double Pipe Heat Exchanger

[+] Author and Article Information
Nadia Allouache

 Universite des Sciences et de la Technologie Houari Boumediene, B. P. 32, El Alia, Bab Ezzouar 16111, Algeria

Salah Chikh1

 Universite des Sciences et de la Technologie Houari Boumediene, B. P. 32, El Alia, Bab Ezzouar 16111, Algeriasalahchikh@yahoo.fr

1

To whom correspondence should be addressed.

J. Appl. Mech 73(1), 60-65 (Apr 27, 2005) (6 pages) doi:10.1115/1.1991865 History: Received June 22, 2004; Revised April 27, 2005

A combination of the first and second laws of thermodynamics has been utilized in analyzing the performance of a double pipe heat exchanger with a porous medium attached over the inner pipe. The goal of this work is to find the best conditions that allow the lowest rate of entropy generation due to fluid friction and heat transfer with respect to the considered parameters. Results show that the minimization of the rate of entropy generation depends on the porous layer thickness, its permeability, the inlet temperature difference between the two fluids, and the effective thermal conductivity of the porous substrate. An increase in the effective thermal conductivity of the porous medium seems to be thermodynamically advantageous. Unexpectedly, the fully porous annular gap yields the best results in terms of the rate of total entropy generation.

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Copyright © 2005 by American Society of Mechanical Engineers
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Figures

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Figure 1

Schematic of physical domain

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Figure 2

Mean temperature along the heat exchanger (Rce=1, cold side, e=0.6, Da=10−3)

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Figure 3

Rate of entropy generation due to fluid friction at the exit of heat exchanger (Rce=1, cold side)

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Figure 4

Rate of entropy generation due to temperature gradient at the exit of heat exchanger (Rce=1, cold side)

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Figure 5

Difference between the wall temperature and the mean temperature of the cold fluid

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Figure 6

Rate of total entropy generation as function of β parameter

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Figure 7

Rate of total entropy generation at the exit of heat exchanger (Rce=1, cold side, 10°C<ΔTin<20°C)

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Figure 12

Rate of total entropy generation as function of thermal conductivity ratio (β=105)

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Figure 11

(a) rate of total entropy generation at the exit of the heat exchanger (cold fluid, β=105, Da=10−2). (b) Rate of total entropy generation at the exit of the heat exchanger (cold fluid, β=105, Da=10−6).

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Figure 10

Rate of total entropy generation at the exit of heat exchanger (Rce=1, cold fluid, Da=10−6, case of water)

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Figure 9

Rate of total entropy generation at the exit of heat exchanger (Rce=1, cold side, ΔTin⩾20°C)

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Figure 8

Bejan number (Rce=1, cold side, 10°C<ΔTin<20°C)

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