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TECHNICAL PAPERS: Heat and Mass Transfer

Numerical Evaluation of Fin Performance Under Dehumidifying Conditions

[+] Author and Article Information
G. Comini

Department of Energy Technologies, University of Udine, Via delle Scienze 208, 33100 Udine, Italygianni.comini@uniud.it

C. Nonino, S. Savino

Department of Energy Technologies, University of Udine, Via delle Scienze 208, 33100 Udine, Italy

J. Heat Transfer 129(10), 1395-1402 (Feb 13, 2007) (8 pages) doi:10.1115/1.2755012 History: Received October 24, 2006; Revised February 13, 2007

A numerical model of moist air cooling in compact heat exchangers is presented. The model requires the solution of a coupled problem, since interface temperatures, obtained from the solution of the energy equation in adjacent fluid and solid regions, are used to set the appropriate boundary conditions for the transport equation of water vapor in moist air. The approach is completely general, even if the finite-element method is used for the simulations reported in the paper. The numerical results are favorably compared with the corresponding experimental results concerning the rectangular and wavy fins under dehumidifying conditions.

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Copyright © 2007 by American Society of Mechanical Engineers
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Figures

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Figure 1

Rectangular fins: (a) geometry (not to scale) and location of thermocouples and (b) computational domain

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Figure 2

Rectangular fins in wet conditions at ϕi=50% with three different frontal velocities uf: (a) temperature distributions and (b) mass flow rates of vapor condensing per unit area of the fin surfaces

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Figure 3

Rectangular fins in wet conditions at ϕi=70% with three different frontal velocities uf: (a) temperature distributions and (b) mass flow rates of vapor condensing per unit area of the fin surfaces

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Figure 4

Rectangular fins in wet conditions at ϕi=50%: experimentally (6) and numerically determined values of dimensionless temperatures for (a) uf=0.5m∕s and (b) uf=4.0m∕s

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Figure 5

Rectangular fins in wet conditions at ϕi=70%: experimentally (6) and numerically determined values of dimensionless temperatures for (a) uf=0.5m∕s and (b) uf=4.0m∕s

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Figure 6

Rectangular fins in wet conditions at ϕi=90%: experimentally (6) and numerically determined values of dimensionless temperatures for (a) uf=0.5m∕s and (b) uf=4.0m∕s

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Figure 7

Rectangular fins: experimentally (6) and numerically determined values of dry (ϕi=40%) and wet (ϕi=70%) fin efficiencies

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Figure 8

Wavy fins: (a) geometry (not to scale) and (b) computational domain

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Figure 9

Streamlines in the corner regions on the horizontal midplane z∕H=0.5 of wavy fins for two different values of the frontal velocity uf

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Figure 10

Wavy fins in wet conditions at ϕi=85% and uf=4m∕s: (a) temperature distribution and (b) mass flow rate of vapor condensing per unit area of the fin surface

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Figure 11

Wavy fins: experimentally (7) and numerically determined values of dry (ϕi=40%) and wet (ϕi=85%) heat transfer coefficients

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