Abstract
This paper aims at showing that to prescribe a flow rate at the inlet section of a vertical channel with heated walls leads to surprising and counterintuitive physical solutions, especially when the problem is modeled as elliptical. Such an approach can give rise to the onset of recirculation cells in the entry region while the heat transfer is slightly increased under the influence of the buoyancy force. We suggest an alternative model based on more realistic boundary conditions based on a prescribed total pressure at the inlet and a fixed pressure at the outlet sections. In this case, the pressure and buoyancy forces act effectively in the same direction and, the concept of buoyancy aiding convection makes sense. The numerical results emphasize the large differences between solutions based on prescribed inlet velocity and those obtained with the present pressure-based boundary conditions.
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Abbreviations
- a :
-
Thermal diffusivity (m2 s−1)
- A :
-
Aspect ratio, A = H/D
- c p :
-
Specific heat (J K−1 kg−1)
- c x , c z :
-
Stretching parameters, Eq. 13
- D :
-
Plate spacing (m)
- D h :
-
Hydraulic diameter, D h = 2D (m)
- g :
-
Gravitational acceleration (m s−2)
- Gr H :
-
Grashof number based on H, Gr H = gβ 0ΔTH 3/ν 20
- h :
-
Heat transfer coefficient (W m−2 K−1)
- H :
-
Channel height (m)
- k :
-
Thermal conductivity (W m−1 K−1)
- L :
-
Channel length in the spanwise direction (m)
- \( \dot{m} \) :
-
Mass flow rate (kg s−1)
- n x , n z :
-
Numbers of grid points in x- and z-directions
- p :
-
Pressure (Pa)
- p s :
-
Pressure at the outlet section (Pa)
- Pr :
-
Prandtl number, Pr = ν0/a 0
- Q :
-
Heat flux (W)
- Q en :
-
Enthalpy heat flux (W)
- Q 2w :
-
Convective heat flux along the two channel walls (W)
- Re :
-
Reynolds number based on D h , Re = w 0 D h /ν0
- Ri :
-
Richardson number, Ri = Gr/Re 2
- S c :
-
Area of the channel cross section, S c = DL (m2)
- t :
-
Time (s)
- T :
-
Temperature (K)
- u, w :
-
Velocity components (m s−1)
- x, z :
-
Coordinates (m)
- β :
-
Coefficient of thermal expansion, β = 1/T 0 (K−1)
- ΔT :
-
Temperature difference, ΔT = (T h − T 0) (K)
- μ :
-
Dynamic viscosity (Pa s)
- ν :
-
Kinematic viscosity (m2 s−1)
- ρ :
-
Density (kg m−3)
- θ :
-
Dimensionless temperature ratio, θ = (T − T 0)/ΔT
- τ :
-
Dimensionless time
- a, b :
-
Analytical solutions
- h :
-
Hot wall
- H :
-
Quantity based on channel height
- nc :
-
Natural convection
- 0:
-
Inlet section
- −:
-
Averaged quantity
- *:
-
Dimensionless quantity
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Sun, H., Li, R., Chénier, E. et al. On the modeling of aiding mixed convection in vertical channels. Heat Mass Transfer 48, 1125–1134 (2012). https://doi.org/10.1007/s00231-011-0964-8
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DOI: https://doi.org/10.1007/s00231-011-0964-8