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TECHNICAL PAPERS: Gas Turbines: Heat Transfer

Effects of Pore Size Variations on Regenerative Wheel Performance

[+] Author and Article Information
Wei Shang, Robert W. Besant

Department of Mechanical Engineering, University of Saskatchewan, 57 Campus Drive, Saskatoon SK S7N 5A9, Canada

J. Eng. Gas Turbines Power 127(1), 121-135 (Feb 09, 2005) (15 pages) doi:10.1115/1.1804539 History: Received April 02, 2003; Revised September 01, 2003; Online February 09, 2005
Copyright © 2005 by ASME
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References

Shang,  W., and Besant,  R. W., 2001, “Energy Wheel Effectiveness Evaluation, Part I: Outlet Airflow Property Distributions Adjacent to an Energy Wheel; Part II: Testing and Monitoring Energy Wheels in HVAC Applications,” ASHRAE Trans., 107, pp. 266–280.
Mahbub-Uddin, A. K. M., and Bell, K. J., 1988, “Effect of Uncertainties on the Design and Operation of Systems of Heat Exchangers,” Heat Transfer Equipment Design, R. K. Shah, E. C. Subbarao, and R. A. Meshelkar, eds., Hemisphere, New York, pp. 39–47.
Fraas, A. P., 1989, Heat Exchanger Design, Wiley, New York.
Kuppan, T., 2000, Heat Exchanger Design Handbook, Marcel Dekker, New York.
London,  A. L., 1970, “Laminar Flow Gas Turbine Regenerators—The Influence of Manufacturing Tolerances,” ASME J. Eng. Power, 92, pp. 46–56.
Mondt,  J. R., 1977, “Effects of Nonuniform Passages on Deepfold Heat Exchanger Performance,” ASME J. Eng. Power, 99, pp. 657–663.
London,  A. L., 1980, “Discussion on the Paper by Mondt 6—Effects of Nonuniform Passages on Deepfold Heat Exchanger Performance,” ASME J. Eng. Power, 102, pp. 510–511.
Rohsenow, W. M., 1981, “Why Laminar Flow Heat Exchangers Can Perform Poorly,” Heat Exchangers: Thermal-Hydraulic Fundamentals and Design, S. Kakac, A. E. Bergles, and F. Mayinger, eds., McGraw-Hill, New York, pp. 1057–1071.
Shah,  R. K., and London,  A. L., 1980, “Effects of Nonuniform Passages on Compact Heat Exchanger Performance,” ASME J. Eng. Power, 102, pp. 653–659.
Simonson,  C. J., and Besant,  R. W., 1997, “Heat and Moisture Transfer in Desiccant Coated Rotary Energy Exchangers, Part I: Numerical Model; Part II: Validation and Sensitivity Studies,” Int. J. HVAC&R Research,3, pp. 325–368.
Stiesch,  G., Klein,  S. A., and Mitchell,  J. W., 1995, “Performance of Rotary Heat and Mass Exchangers,” Int. J. HVAC&R Research,1, pp. 308–323.
Nimmo,  B. G., Collier,  R. K., and Rengarajan,  R., 1993, “DEAC: Desiccant Enhancement of Cooling-Based Dehumidification,” ASHRAE Trans., 99, pp. 842–848.
Zheng,  W., Worek,  W. M., and Novosel,  D., 1993, “Control and Optimization of Rotational Speeds for Rotary Dehumidifiers,” ASHRAE Trans., 99, pp. 825–833.
Simonson,  C. J., Ciepliski,  D. L., and Besant,  R. W., 1999, “Determining the Performance of Energy Wheels, Part I: Experimental and Numerical Methods; Part II: Experimental Data and Numerical Validation,” ASHRAE Trans., 105, pp. 174–205.
ASHRAE, 1991, ANSI/ASHRAE Standard 84-1991R: Method of Testing Air-to-Air Heat Exchangers, American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc., Atlanta.
Shah, R. K., and London, A. L., 1978, Laminar Flow Forced Convection in Ducts, Supplement 1 to Advances in Heat Transfer, Academic, New York.
Simonson,  C. J., and Besant,  R. W., 1999, “Energy Wheel Effectiveness, Part I: Development of Dimensionless Groups; Part II: Correlations,” Int. J. Heat Mass Transfer, 42, pp. 2161–2185.
ARI, 2001, ARI Standard 1060: Rating Air-to-Air Energy Recovery Ventilation Equipment, Air-Conditioning & Refrigeration Institute, Arlington, Virginia.
Bejan, A., 1984, Convection Heat Transfer, Wiley, New York.
Taylor, J. R., 1982, An Introduction to Error Analysis, University Science Books, Mill Valley, CA.

Figures

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Schematic of airflow for air-to-air heat/energy exchangers
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(a) A typical energy wheel with desiccant coating, (b) corrugated channels for the same energy wheel with flow through each pore
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Number of wheel matrix pores versus pore hydraulic diameter for a Guassian distribution of diameters
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Pressure drop ratio for parallel surface wheel with random variations in pore sizes to one without versus the standard deviation in pore hydraulic diameters with respect to the mean value
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Effectiveness versus mass flow rate under the ARI Std 1060 test conditions based on the correlations of Simonson and Besant (see Ref. 17) for a desiccant coated energy wheel for ventilation air heat and moisture exchange (wheel width 229.5 mm, wheel diameter 638.5 mm, wheel rotational speed 27.6 rpm, and silica gel desiccant coating)
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Ratio of effectiveness for a parallel surface wheel with a random variation in pore sizes to one without versus standard deviation in pore hydraulic diameters with respect to the mean value
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Pressure drop ratio for a regenerative wheel with a matrix containing symmetrical cylinder pores with random variations in pore sizes to one without versus the standard deviation in pore hydraulic diameters with respect to the mean value
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Ratio of effectiveness for a regenerative wheel with a matrix containing symmetrical cylinder pores with a random variation in pore sizes to one without versus standard deviation in pore hydraulic diameters with respect to the mean value
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Schematic of a corrugated shaped matrix channel for a regenerative wheel
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Kf versus aspect ratio η for a corrugated channel
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Kp versus aspect ratio η for a corrugated channel
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K versus Δη/η0 for a corrugated pore geometry with η0 as a parameter
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D/2a versus aspect ratio η for a corrugated channel
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Modified pressure drop ratio for a corrugated matrix energy wheel versus standard deviation divided by mean value of hydraulic diameter
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Modified effectiveness ratio for a corrugated matrix energy wheel versus standard deviation divided by mean value of hydraulic diameter
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Modified effectiveness ratio for a corrugated matrix energy wheel versus standard deviation divided by mean value of hydraulic diameter ∂εm=−0.3
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A schematic of the optical system used to measure pore geometries
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Photos of the matrices for four different energy wheels
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A schematic diagram showing the optical measure position Pij on an energy wheel face
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A chi squared analysis of the characteristic dimension distributions of the four wheels; (a) parallel surface wheel (D/2), (b) hexagonal honeycomb wheel (D), (c) corrugated aluminum wheel (2b), and (d) corrugated paper wheel (2b) each compared with a Gaussian distribution line

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