0
Journal of Thermal Science and Engineering Applications | Volume 3 | Issue 2 | Research Paper
Research Papers

Transient Heat Exchanger Response With Pressure Regulated Outflow

[+] Author and Article Information
P. Regulagadda

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
Article
References
Figures

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.
FIGURES IN THIS ARTICLE
<>
Copyright © 2011 by American Society of Mechanical Engineers
Your Session has timed out. Please sign back in to continue.

References

Figures

Grahic Jump Location
+Schematic of the heat exchanger
View Large  |  Save Figure  |  Download Slide (.ppt)
Schematic of the heat exchanger
Figure 1

Schematic of the heat exchanger

Grahic Jump Location
+Schematic for the analytical model of the heat exchanger
View Large  |  Save Figure  |  Download Slide (.ppt)
Schematic for the analytical model of the heat exchanger
Figure 2

Schematic for the analytical model of the heat exchanger

Grahic Jump Location
+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
View Large  |  Save Figure  |  Download Slide (.ppt)
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 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

Grahic Jump Location
+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
View Large  |  Save Figure  |  Download Slide (.ppt)
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 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

Grahic Jump Location
+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
View Large  |  Save Figure  |  Download Slide (.ppt)
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 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

Grahic Jump Location
+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
View Large  |  Save Figure  |  Download Slide (.ppt)
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
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

Tables

Errata

Discussions

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
Completing the Picture
Air Engines> Chapter 11
Thermodynamic Performance
Closed-Cycle Gas Turbines> Chapter 6
Scope of Section I, Organization, and Service Limits
Power Boilers> Chapter 1
Pool Boiling
Thermal Management of Microelectronic Equipment, Second Edition
Natural Gas Transmission
Pipeline Design & Construction: A Practical Approach, Third Edition> Chapter 3
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