Heat Transfer, Pressure Loss and Flow Field Measurements Downstream of Staggered Two-Row Circular and Elliptical Pin Fin Arrays

[+] Author and Article Information
Oguz Uzol, Cengiz Camci

Turbomachinery Heat Transfer Laboratory, Pennsylvania State University, University Park, PA 16802

J. Heat Transfer 127(5), 458-471 (May 25, 2005) (14 pages) doi:10.1115/1.1860563 History: Received January 28, 2004; Revised September 02, 2004; Online May 25, 2005
Copyright © 2005 by ASME
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Grahic Jump Location
Average relative convective heat transfer coefficient variation with Reynolds number
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Average Nusselt number versus Reynolds number comparisons of (a) current measurements with previously reported correlations for staggered circular pin fin arrays, and (b) circular, SEF, and N fin arrays with previously reported measurements for various pin fin shapes. Empty tunnel results are the current measured data with no pin fins.
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(a) A sample liquid crystal image for the empty tunnel case obtained at ReDh=75,000(Dh=0.126 m) and (b) the corresponding measured h distribution on the heater strip
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(a) Low Speed Heat Transfer Research Facility at Pennsylvania State University and (b) the layout and the dimensions of the acrylic test section shown in (a)
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The shapes and relative dimensions of the circular fin, Standard Elliptical Fin (SEF), and the N fin (D=0.0508 m)
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(a) Layout of the two-row staggered pin fin configuration within the test section, and the end wall heat transfer measurement setup using Liquid Crystal Thermography and (b) sample images of the liquid crystal sprayed heater strip for empty tunnel (left) and with circular fin array (right) cases
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A comparison of current baseline empty tunnel measurements with (a) fully developed turbulent duct flow (Eq. (10)) and (b) flat plate with unheated starting length [Eqs. (11) and (12)] correlations as given in Incropera and DeWitt 34
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Relative convective heat transfer coefficient distribution on the endwall for circular (○), SEF (▵) and N (+) fin arrays, 2D downstream (h0: baseline empty tunnel value). ReD is calculated using the maximum velocity and the circular fin diameter, D=0.0508 m (or SEF/N fin minor axis length that is equal to D).
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Friction coefficient distributions inside the wakes of circular (○), SEF (▵), and N (+) fin arrays, 2D downstream
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Average friction coefficient versus Reynolds number for circular, SEF, and N fin arrays. (a) A comparison with previously published circular fin data. Error bars show ±15% range given for the correlation given by Metzger et al. 35, Eq. (17). (b) A comparison with previously published pressure loss data for various other pin fin shapes.
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Relative Nusselt number variation with relative total pressure loss. Nu0 is the baseline empty tunnel Nusselt number obtained using the estimated h0 values from Eq. (13) and modified using the pin fin diameter instead of hydraulic diameter; f0 is calculated using the Blasius power-law correlation (Kays and Crawford 32), Eq. (22).
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(a) Reynolds analogy performance index and (b) Thermal performance (TP) parameter variation with Reynolds number for circular, SEF, and N fin arrays
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Ensemble-averaged (a) velocity magnitude, (b) vorticity, and (c) turbulent kinetic energy distributions within the wakes of circular, SEF, and N fin arrays (from top to bottom) for ReD=18 000 and at the midplane. y/D=0 is on the centerline of the channel and x/D=0 is on the centers of the circular cylinders in the first row.



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