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Research Papers

# Transient Heat Exchanger Response With Pressure Regulated Outflow

[+] Author and Article Information

Faculty of Engineering and Applied Science,  University of Ontario Institute of Technology, 2000 Simcoe Street North, Oshawa, ON, L1H 7K4, CanadaPrashant.Regulagadda@uoit.ca

G. F. Naterer

Faculty of Engineering and Applied Science,  University of Ontario Institute of Technology, 2000 Simcoe Street North, Oshawa, ON, L1H 7K4, CanadaGreg.Naterer@uoit.ca

I. Dincer

Faculty of Engineering and Applied Science,  University of Ontario Institute of Technology, 2000 Simcoe Street North, Oshawa, ON, L1H 7K4, CanadaIbrahim.Dincer@uoit.ca

J. Thermal Sci. Eng. Appl 3(2), 021008 (Jul 29, 2011) (8 pages) doi:10.1115/1.4004009 History: Received November 23, 2010; Revised April 01, 2011; Published July 29, 2011; Online July 29, 2011

## Abstract

This paper analyzes the thermal performance of a co-current flow heat exchanger with transient gas outflow. The temperature distributions of the working fluid, heating fluid, and the wall over the length of the heat exchanger are predicted by an integral formulation. The heat transfer rates are determined at various stages of the heat exchanger operation. An integral formulation of the nondimensionalized governing equations is solved numerically, using a time-marching algorithm. The temperature distributions of the working fluid and the wall have an exponential increase from the inlet to the outlet of the heat exchanger. The heating fluid shows an initial decrease and subsequent increase of temperature. A base model for the step change in the mass flow of the working fluid is developed and compared against past data for purposes of validation. In addition, results are presented and discussed for the time-varying performance, during pressure regulated gas outflow from the heat exchanger.

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## Figures

Figure 1

Schematic of the heat exchanger

Figure 2

Schematic for the analytical model of the heat exchanger

Figure 3

Validation results for (a) Tf*vs.x*forN1=700,N20=10,N30=1.0,γ=0.4 and (b) Tw* vs. x*forN1=700,N20=10,N30=1.0,γ=0.4

Figure 4

Laminar flow results for (a) Tf*vs.x*forN1=300,N20=6.0,N30=6.0,γ=0.4, (b) Tw* vs. x*forN1=300,N20=6.0,N30=6.0,γ=0.4, and (c) Th* vs. x*forN1=300,N20=6.0,N30=6.0,γ=0.4

Figure 5

Turbulent flow results for (a) Tf* vs. x*forN1=300,N20=6.0,N30=6.0,γ=0.4 (b) Tw* vs. x*forN1=300,N20=6.0,N30=6.0,γ=0.4, and (c) Th* vs. x*forN1=300,N20=6.0,30=6.0,γ=0.4

Figure 6

Laminar flow results for (a) Tf* vs. x*forN1=300,N20=9.0,N30=9.0,γ=0.4, (b) Tw* vs. x*forN1=300,N20=9.0,N30=9.0,γ=0.4, and (c) Th* vs. x*forN1=300,N20=9.0,N30=9.0,γ=0.4

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