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Frontiers in Energy

ISSN 2095-1701

ISSN 2095-1698(Online)

CN 11-6017/TK

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Front. Energy    2014, Vol. 8 Issue (2) : 201-211    https://doi.org/10.1007/s11708-014-0297-7
RESEARCH ARTICLE
Heat transfer and fluid flow analysis of an artificially roughened solar air heater: a CFD based investigation
Anil Singh YADAV1,*(),J. L. BHAGORIA2
1. Mechanical Engineering Department, Technocrats Institute of Technology-Excellence, Bhopal, MP 462021; Mechanical Engineering Department, Maulana Azad National Institute of Technology, Bhopal, MP 462051, India
2. Mechanical Engineering Department, Maulana Azad National Institute of Technology, Bhopal, MP 462051, India
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Abstract

In this paper, the effect of rib (circular sectioned) spacing on average Nusselt number and friction factor in an artificially roughened solar air heater (duct aspect ratio, AR= 5:1) is studied by adopting the computational fluid dynamics (CFD) approach. Numerical solutions are obtained using commercial software ANSYS FLUENT v12.1. The computations based on the finite volume method with the semi-implicit method for pressure-linked equations (SIMPLE) algorithm have been conducted. Circular sectioned transverse ribs are applied at the underside of the top of the duct, i.e., on the absorber plate. The rib-height-to-hydraulic diameter ratio (e/D) is 0.042. The rib-pitch-to-rib-height (P/e) ratios studied are 7.14, 10.71, 14.29 and 17.86. For each rib spacing simulations are executed at six different relevant Reynolds numbers from 3800 to 18000. The thermo-hydraulic performance parameter for P/e = 10.71 is found to be the best for the investigated range of parameters at a Reynolds number of 15000.
Keywords heat transfer      pressure drop      thermo-hydraulic performance parameter     
Corresponding Author(s): Anil Singh YADAV   
Issue Date: 19 May 2014
 Cite this article:   
Anil Singh YADAV,J. L. BHAGORIA. Heat transfer and fluid flow analysis of an artificially roughened solar air heater: a CFD based investigation[J]. Front. Energy, 2014, 8(2): 201-211.
 URL:  
https://academic.hep.com.cn/fie/EN/10.1007/s11708-014-0297-7
https://academic.hep.com.cn/fie/EN/Y2014/V8/I2/201
Fig.1  Schematic of two-dimensional computational domain
Fig.2  Roughened absorber plate with different arrangement of circular sectioned transverse rib
Geometrical and operating parametersRange
Entrance length of duct (L1)/mm245
Test length of duct (L2)/mm280
Exit length of duct (L3)/mm115
Width of duct (W)/mm100
Depth of duct (H)/mm20
Hydraulic diameter of duct (D)/mm33.33
Duct aspect ratio (W/H)5
Rib height (e)/mm1.4
Rib Pitch (P)/mm10-25 (4 values)
Reynolds number (Re)3800-18000 (6 values)
Prandtl number (Pr)0.7
Relative roughness pitch (P/e)7.14-17.86 (4 values)
Relative roughness height (e/D)0.042 (fixed value)
Tab.1  Range of geometrical and operating parameters for CFD analysis
Fig.3  Two-dimensional non-uniform meshing
RegionUsed boundary condition
InletVelocity inlet
OutletOutflow
Duct top wallWall
Duct bottom wallWall
Tab.2  Boundary conditions for the present geometry
PropertyAirAbsorber plate (Aluminum)
Density (ρ)/(kg·m-3)1.1172719
Specific heat (Cp)/(J·kg-1·K-1)1007871
Viscosity (μ)/(N·s.m-2)1.857e-05-
Thermal conductivity (k)/(W·m-1·K-1)0.0262202.4
Tab.3  Thermo-physical properties of air and absorber plate for CFD analysis
Number of cellsNusselt numberDifference/%Friction factorDifference/%
10323179.88-0.0218-
11878182.833.690.02274.15
13691083.590.920.02291.07
16156883.880.350.02310.94
19797784.970.110.02320.57
Tab.4  Grid independence test
Fig.4  Nusselt number versus Reynolds number
Fig.5  Contour map of turbulence intensity for relative roughness pitch, P/e = 7.14 and Reynolds number, Re = 15000
Fig.6  Nusselt number ratio versus Reynolds number
Fig.7  Friction factor versus Reynolds number
Fig.8  Contour map of pressure for relative roughness pitch, P/e = 7.14 and Reynolds number, Re = 15000
Fig.9  Friction factor ratio versus Reynolds number
Fig.10  Thermo-hydraulic performance parameter versus Reynolds number
Fig.11  Comparison of Nusselt number predicted by present CFD investigation with the correlation developed by Verma and Prasad [30]
Fig.12  Comparison of friction factor predicted by present CFD investigation with the correlation developed by Verma and Prasad [30]
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