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Research Papers

Investigation of Temperature Separation Inside Various Models of Ranque–Hilsch Vortex Tube: Convergent, Straight, and Divergent With the Help of Computational Fluid Dynamic Approach

[+] Author and Article Information
Adib Bazgir

Department of Chemical Engineering,
Petroleum University of Technology,
Behbahani Highway, Room 1,
P.O. Box 6818958688,
Ahwaz, Iran
e-mail: adib.bazgir@afp.put.ac.ir

Nader Nabhani

Department of Mechanical Engineering,
Petroleum University of Technology,
P.O. Box 6198144471,
Ahwaz, Iran
e-mail: nabhani@put.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 18, 2017; final manuscript received April 1, 2018; published online May 22, 2018. Assoc. Editor: Sandip Mazumder.

J. Thermal Sci. Eng. Appl 10(5), 051013 (May 22, 2018) (15 pages) Paper No: TSEA-17-1359; doi: 10.1115/1.4039966 History: Received September 18, 2017; Revised April 01, 2018

In this paper, a Ranque–Hilsch vortex tube (RHVT) has been optimized utilizing convergent (φ), straight, and divergent (θ) axial angles for hot-tube. Effects of divergent (θ) and convergent (φ) angles on the flow behavior have been investigated by computational fluid dynamic (CFD) techniques. By using a renormalization group (RNG) k–ε turbulence model based on finite volume method, all the computations have been carried out. The isentropic efficiency (ηis) and coefficient of performance (COP) of machine was studied under five different divergent angles (θ), namely 1 deg, 2 deg, 3 deg, 4 deg, and 6 deg, two different convergent (φ) angles (φ) namely 1 deg and 2 deg adjusted to the hot-tube. Furthermore, some geometrical and operational parameters including cold outlet diameter, hot-tube length, and different inlet pressures and mass flow rates have been analyzed in detail (spanwisely) in order to optimize the cooling efficiency of vortex tube (straight). The results show that utilizing the divergent hot-tubes increases the isentropic efficiency (ηis) and COP of device for most values of inlet pressures, and helps to become more efficient than the other shape of vortex tubes (straight and convergent). Finally, some results of the CFD models have been validated by the available experimental and numerical data, which show reasonable agreement, and others are compared qualitatively.

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Figures

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Fig. 1

Flow structure in a counter-flow vortex tube

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Fig. 2

The schematic diagram of the straight, divergent, and convergent models (a)–(d)

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Fig. 3

Pressures at the face of a pressure outlet boundary

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Fig. 4

The grids of the 3D model of vortex tubes

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Fig. 5

The variations of temperature difference (ΔTc) versus different (a) number of cells and (b) volume of a mesh for the case Pin=0.3 MPa

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Fig. 6

Experimental and numerical variation of total (ΔT = Th−TC) temperature difference with pressure loss ratio (λ)

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Fig. 7

The distributions of the total, tangential and axial velocities of (a) 2 deg convergent (φ = 2 deg), (b) straight, and (c) 2 deg divergent (θ = 2 deg) vortex tubes at Pin = 0.3 MPa (absolute)

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Fig. 8

Radial profiles of (a) axial and (b) tangential velocities for 2 deg convergent, straight, and 2 deg divergent vortex tubes at different cross section locations of Z = −15, 0, 50, and 110 mm with the absolute total pressure of Pin = 0.3 MPa

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Fig. 9

Streamlines in 2 deg convergent (φ = 2 deg), straight, and 2 deg divergent (θ = 2 deg) vortex tubes

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Fig. 10

Contours of density and total pressure for (a) 2 deg convergent (φ = 2 deg), (b) straight, and (c) 2 deg divergent (θ = 2 deg) vortex tubes at Pin = 0.3 MPa (absolute)

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Fig. 11

Contours of total and static temperature, respectively, for (a) 2 deg convergent (φ = 2 deg), (b) straight, and (c) 2 deg divergent (θ = 2 deg) vortex tubes at Pin=0.3 MPa (absolute)

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Fig. 12

Cold temperature difference (ΔTc) versus pressure loss ratio (λ) for different vortex tubes at (a) Pin = 0.3 and (b) Pin = 0.4 MPa

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Fig. 13

Isentropic efficiency versus pressure loss ratios (λ) for different vortex tubes at (a) Pin = 0.3 and (b) Pin = 0.4 MPa

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Fig. 14

Coefficient of performance versus pressure loss ratios (λ) for different vortex tubes at (a) Pin = 0.3 and (b) Pin = 0.4 MPa

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Fig. 15

Temperature distribution of straight vortex tube with different cold outlet diameters

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Fig. 16

The diagram of temperature distribution along vortex tube length with different cold outlet diameters

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Fig. 17

The diagrams of (a) cold and (b) hot temperature difference, (c) isentropic efficiency, and (d) COP versus different cold outlet diameters

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Fig. 20

The variation of temperature versus nondimensional parameter of axial distance along to the length of vortex tube

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Fig. 19

The stream lines of swirling velocity for different lengths of vortex tube

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Fig. 18

The diagrams of (a) cold and (b) hot temperature difference, (c) isentropic efficiency, and (d) COP versus different lengths of hot tube (mm)

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