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Research Papers

Experimental and Numerical Investigation on Effect of Convergent Angle and Cold Orifice Diameter on Thermal Performance of Convergent Vortex Tube

[+] Author and Article Information
Seyed Ehsan Rafiee

Department of Mechanical Engineering,
Urmia University of Technology,
Urmia 57166-17165, Iran e-mail: s.e.rafiee@mee.uut.ac.ir

M. M. Sadeghiazad

Department of Mechanical Engineering,
Urmia University of Technology,
Urmia 57166-17165, Iran e-mail: rez.saeed@yahoo.com

Nasser Mostafavinia

Young Researchers and Elite Club,
Mahabad Branch,
Islamic Azad University,
Mahabad 59139-33137, Iran e-mail: n.geramian@mee.uut.ac.ir

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF THERMAL SCIENCE AND ENGINEERING APPLICATIONS. Manuscript received September 15, 2014; final manuscript received March 10, 2015; published online June 16, 2015. Assoc. Editor: Mehmet Arik.

J. Thermal Sci. Eng. Appl 7(4), 041006 (Jun 16, 2015) (13 pages) Paper No: TSEA-14-1214; doi: 10.1115/1.4030639 History: Received September 15, 2014

The vortex tube (VT) air separator is an invaluable tool which has the ability to separate a high-pressure fluid into the cold and hot fluid streams. The hot tube is a main part of the air separator VT which the energy separation procedure happens along this part. This research has been done to analyze the effect of the convergent angle and cold orifice diameter on the thermal efficiency of a convergent vortex tube (CVT). The CVT is linked to an air pipeline with the fixed pressure of 6.5 bar. The convergent hot tube angle is varied over the range of 1 deg to 9 deg. The consideration of the main angle effect denotes that the highest thermal ability could be achieved at β = 5 deg. The laboratory setup results show this subject that the optimization of the hot tube convergent angle elevates the cooling and heating effectiveness around 32.03% and 26.21%, respectively. Experiments denoted that both cooling capability and heating effectiveness reach the highest magnitudes when the DCold is around 9 mm. After these two stages, the optimized CVT was capable of decreasing and rising air temperatures at the cold and the hot sides up to 9.05 K (42.89%) and 10.48 K (44.74%), respectively. A computational fluid dynamics (CFD) model was employed to predict the performance of the air flow inside the CVT. The numerical investigation was done by full 3D steady-state CFD-simulation using fluent6.3.26. The results show that the agreement between computation predictions and laboratory measurements is fairly good.

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References

“JOTSE,” www.jotse.org
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Figures

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Fig. 1

A schematic drawing of (a) RHVT [1] and (b) PVT

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Fig. 2

A schematic drawing of the CVT

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Fig. 3

Schematic drawing of the experimental setup: 1, inlet pressure gauge; 2, thermocouple; 3, vortex chamber; 4, working tube; 5, inlet nozzle; 6, rotameter; 7, cold outlet digital manometer; and 8, hot outlet digital manometer

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Fig. 4

Schematic plot of boundary conditions

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Fig. 5

Schematic demonstration of mesh domain: (a) convergent VT, (b) straight VT, (c) control valve position, and (d) nozzle injectors position

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Fig. 6

Model validation for different convergent hot tubes

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Fig. 7

Effect of convergent hot tube angle on hot temperature drop

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Fig. 8

Effect of convergent hot tube angle on cold temperature drop

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Fig. 9

Effect of convergent hot tube angle on convergent VT efficiency

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Fig. 10

Temperature fields for (a) convergent VTs and (b) straight one in comparison form

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Fig. 11

Velocity fields for (a) convergent VTs and (b) straight one in comparison form

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Fig. 12

Pressure fields for (a) convergent VTs and (b) straight one in comparison form (Pa)

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Fig. 13

Effect of cold orifice diameter on hot temperature drop

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Fig. 14

Effect of cold orifice diameter on cold temperature drop

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Fig. 15

Effect of cold orifice diameter on convergent VT efficiency

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