Research Papers: Heat Exchangers

Effect of Plate Characteristics on Axial Dispersion and Heat Transfer in Plate Heat Exchangers

[+] Author and Article Information
K. Shaji

Department of Mechanical Engineering,
Indian Institute of Technology Madras,
Chennai 600036, India

Sarit K. Das

Heat Transfer and Thermal Power Laboratory,
Department of Mechanical Engineering,
Indian Institute of Technology Madras,
Chennai 600036, India
e-mail: skdas@iitm.ac.in

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the Journal of Heat Transfer. Manuscript received August 2, 2010; final manuscript received October 20, 2012; published online March 20, 2013. Assoc. Editor: Phillip M. Ligrani.

J. Heat Transfer 135(4), 041801 (Mar 20, 2013) (10 pages) Paper No: HT-10-1339; doi: 10.1115/1.4022993 History: Received August 02, 2010; Revised October 20, 2012

A new mathematical model of single-blow transient testing technique is proposed for the determination of heat transfer and dispersion coefficients in plate heat exchangers (PHEs) in which the flow maldisrtibution effects are separated from the fluid back-mixing. The fluid axial dispersion is used to characterize the back-mixing and other deviations from plug flow. Single-blow experiments are carried out with different number of plates for various flow rates with three different plate geometries of 30 deg, 60 deg, and mixed (30 deg/60 deg) chevron angles. The outlet temperature response to an exponential inlet temperature variation is solved numerically using finite difference method. In the present work, the whole curve matching technique is used to determine the values of Nusselt number and dispersive Peclet number. Since the maldistribution effects are separated, these data are independent of test conditions and hence using a regression analysis, general correlations are developed for Nusselt number and Peclet number of the present plate heat exchangers. The applicability of the single-blow test data is validated using a two-fluid experiment. Two-fluid experiments are conducted on the same plate heat exchanger with smaller and larger number of plates and the results have been compared with its simulation which used the Nusselt number and Peclet number correlations developed by the new model of single-blow test as the inputs.

Copyright © 2013 by ASME
Your Session has timed out. Please sign back in to continue.


Heggs, P. J., and Burns, D., 1988, “Single-Blow Experimental Prediction of Heat Transfer Coefficients—A Comparison of Four Commonly Used Techniques,” Exp. Therm. Fluid Sci., 1, pp. 243–251. [CrossRef]
Wolf, J., 1964, “General Solutions of the Equations of the Parallel Flow Multi-Channel Heat Exchangers,” Int. J. Heat Mass Transfer, 7, pp. 901–919. [CrossRef]
Jackson, B. W., and Troupe, R. A., 1966, “Plate Heat Exchanger Design byɛ-NTU Method,” Chem. Eng. Prog., Symp. Ser., 62(64), pp. 185–190.
Das, S. K., Spang, B., and Roetzel, W., 1995, “Dynamic Behaviour of Plate Heat Exchangers—Experiments and Modeling,” ASME J. Heat Transfer, 117(4), pp. 859–864. [CrossRef]
Roetzel, W., and Luo, X., 1997, “Extended Temperature Oscillation Measurement Technique for Heat Transfer and Axial Dispersion Coefficients,” Proceedings of the International Conference on Compact Heat Exchangers for the Process Industries, pp. 381–388.
Balzereit, F., and Roetzel, W., 1997, “Determination of Axial dispersion Coefficients in Plate Heat Exchangers Using Residence Time Measurements,” Proceedings of the International Conference on Compact Heat Exchangers for the Process Industries, pp. 389–400.
Roetzel, W., and Na Ranong, C., 1999, “Consideration of Maldistribution in Heat Exchangers Using the Hyperbolic Dispersion Model,” Chem. Eng. Process, 38, pp. 675–681. [CrossRef]
Bassiouny, M. K., and Martin, H., 1984, “Flow Distribution and Pressure Drop in Plate Heat Exchangers-I, U-Type Arrangement,” Chem. Eng. Sci., 39, pp. 693–700. [CrossRef]
Tereda, F. A., Srihari, N., Sunden, B., and Das, S. K., 2007, “Experimental Investigation on Port to Channel Flow Maldistribution in Plate Heat Exchangers,” Heat Transfer Eng., 28(5), pp. 435–442. [CrossRef]
Muley, A., and Manglik, R. M., 1999, “Experimental Study of Turbulent Flow Heat Transfer and Pressure Drop in a Plate Heat Exchanger With Chevron Plates,” ASME J. Heat Transfer, 121(1), pp. 110–117. [CrossRef]
Srihari, N., and Das, S. K., 2008, “Experimental and Theoretical Analysis of Transient Response of Plate Heat Exchanger in Presence of Nonuniform Flow Distribution,” ASME J. Heat Transfer, 130(5), p. 051801. [CrossRef]
Kakac, S., and Liu, H., 2002, Heat Exchangers—Selection, Rating, and Thermal Design, 2nd ed., CRC Press, New York.
Moffat, R. J., 1988, “Describing the Uncertainties in Experimental Results,” Exp. Therm. Fluid Sci., 1, pp. 3–17. [CrossRef]
Danckwerts, P. V., 1953, “Continuous Flow Systems: Distribution of Residence Times,” Chem. Eng. Sci., 2, pp. 1–13. [CrossRef]


Grahic Jump Location
Fig. 3

Schematic view of two-fluid experimental setup

Grahic Jump Location
Fig. 4

Flow friction characteristics of the chevron plates

Grahic Jump Location
Fig. 2

Schematic view of single-blow experimental setup

Grahic Jump Location
Fig. 1

Photographic view of the corrugated plates

Grahic Jump Location
Fig. 5

Channel and flow configuration for single-pass PHE

Grahic Jump Location
Fig. 6

The outlet temperature response within the channels of a plate heat exchanger: (a) 81 plates of 30 deg chevron angle (m2 = 2.35) and (b) 57 plates of 60 deg chevron angle (m2 = 0.49)

Grahic Jump Location
Fig. 7

Curve matching between experimental values and the model for different types of plates: (a) 81 plates (m2 = 2.35) at Re = 2053 (30 deg plates), and (b) 57 plate (m2 = 0.49) at Re = 2555 (60 deg plates)

Grahic Jump Location
Fig. 8

Variation of Nusselt number with Reynolds number for different chevron angle plates

Grahic Jump Location
Fig. 9

Variation of Peclet number with Reynolds number for different chevron angle plates

Grahic Jump Location
Fig. 10

Comparison of the experimental temperature responses with theoretical model at: (a) Re = 1470, N = 20, NTU = 0.741, Rg2 = 1.0 under uniform flow distribution (m2 = 0.15, 30 deg plates), and (b) Re = 920, N = 80, NTU = 1.023, Rg2 = 1.12 under nonuniform flow distribution (m2= 2.1, 30 deg plates)



Some tools below are only available to our subscribers or users with an online account.

Related Content

Customize your page view by dragging and repositioning the boxes below.

Related Journal Articles
Related eBook Content
Topic Collections

Sorry! You do not have access to this content. For assistance or to subscribe, please contact us:

  • TELEPHONE: 1-800-843-2763 (Toll-free in the USA)
  • EMAIL: asmedigitalcollection@asme.org
Sign In