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Numerical CFD analysis and experimental investigation of the geometric performance parameter influences on the counter-flow Ranque-Hilsch vortex tube (C-RHVT) by using optimized turbulence model

  • Adib BazgirEmail author
  • Mohammadreza Khosravi-Nikou
  • Ali Heydari
Original
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Abstract

This research article demonstrates how using different turbulence models may affect the temperature detachment (the temperature diminution of cold air (∆Tc = Ti − Tc)) inside straight counter-flow Ranque-Hilsch Vortex Tube (RHVT). The code is utilized to find the optimized turbulence model for energy separation by comparison with the experimental data of the setup. To obtain the results with a minimum error, various turbulence models have been investigated in steady state and transient time-dependence modes. Results show that RNG k-ε turbulence model has the best correspondence with the obtained experimental data from the setup; therefore, by using a RNG k-ε turbulence model with respect to Finite Volume Method (FVM), all the computations have been carried out. Moreover, some geometric parameters are focused on the length of hot tube and number of nozzle intakes within divergent and convergent hot-tube. Numerical results present that there is an optimum angle for obtaining the highest refrigeration performance, and 2ο divergence is the optimal candidate under our numerical analysis conditions. Length of hot tube which exceeds a critical length has slight effect on the refrigeration capacity. The critical length is L = 166 mm in our study. Temperature reduction sensitivity can be reduced by increasing number of nozzles and maximum temperature reduction can be obtained.

Nomenclature

ANN

Artificial neural network

CFD

Computational fluid dynamic

FVM

Finite volume method

RANS

Reynolds average navier stokes

RNG

Renormalized group

RHVT

Ranque-Hilsch vortex tube

RH

Ranque-Hilsch

RHE

Ranque-Hilsch effect

LES

Large eddy simulation

VT

Vortex tube

∆Tc = ( Tin − TC)

Temperature difference between inlet and cold outlet

ΔT = ( TH − TC)

Temperature difference between hot and cold outlets

Cp

Specific heat at constant absolute pressure (J.kg−1.K−1)

Cεi

Coefficients (i = 1, 2) used in ε equation

Cμ

Constants in Eq. 14

Cυ

Constants in Eq. 13

D

Diameter of vortex tube (mm)

\( \overset{\cdot }{m} \)

Mass flow rate (kg.s−1)

dn

Diameter of inlet nozzle (mm)

E

Total energy (kJ)

Gk

Generation of turbulence kinetic energy

k

Turbulence kinetic energy (m2.s−2)

Ke

Thermal conductivity (W.m−1.K−1)

L

Length (mm)

N

Number of inlet nozzle

P

Absolute pressure (pa)

Qc

Cooling rate

Prt

Turbulent Prandtl number

R

Specific constant of an ideal gas (J/kgmol-K)

S

Twice the strain rate tensor (s−1)

T

Temperature (K)

ui

Absolute fluid velocity component in i-direction (m/s)

YM

Contribution of the fluctuating dilatation

Ma

Mach number

W

Mechanical energy

Greek symbols

αk

Inverse effective Prandtl numbers in Eq. 11

αε

Inverse effective Prandtl numbers in Eq. 12

δij

Kronecker delta

τ

Shear stress (N.m−2)

(τij)eff

Deviatoric stress tensor (N.m−2)

ε

Turbulence dissipation rate (m−2.s−3)

α

Cold mass fraction

μ

Dynamic viscosity (kg.m−1.s−1)

υ

Kinematic viscosity (m2.s−1)

\( \widehat{\upsilon} \)

Ratio of effective viscosity to the dynamic viscosity

γ

Specific heat ratio

ρ

Density (kg.m−3)

λ

Pressure Loss Ratio

η0, β, η

Coefficients in RNG k- ε model

ηis

Isentropic efficiency

Subscripts

c

Cold gas

eff

Effective

h

Hot gas

in

Inlet gas

is

isentropic

i, j, k

Cartesian indicates

n

nozzle

t

turbulent

st

static

a

Atmospheric

Notes

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Copyright information

© Springer-Verlag GmbH Germany, part of Springer Nature 2019

Authors and Affiliations

  • Adib Bazgir
    • 1
    Email author
  • Mohammadreza Khosravi-Nikou
    • 1
  • Ali Heydari
    • 1
  1. 1.Ahvaz Faculty of PetroleumPetroleum University of Technology (PUT)AhvazIran

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