Effects of the Form Factor and the Force of the Gravity on the Thermal Exchanges by Natural Convection in a Rectangular Cavity Filled with Nanofluid

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1. Introduction

The improvement of the heat transfer by natural convection is the main object of several studies; many researchers have conducted a series of tests numerical and experimental of the description of the phenomena of convection: the manager of fact, the nature of the systems (in particular the geometry) and the properties of fluids involved (physico-chemical properties).

Bairi et al. [1] have conducted a study on the natural convection for a Rayleigh number high to the assistance of a technical numerical and experimental in a rectangular cavity tilted. They have obtained a correlation giving the Nusselt number in function of Rayleigh of this study; the Nusselt number minimum is obtained for Φ = 270˚. Hakan F. Ozrop Eiyad Abu-Nada [2] conducted numerical studies to analyze the effect of the use of different nanofluids on the distribution of fields of high temperatures in a cavity of height H and length W filled with a mixture of water and of nanoparticles (Cu, Al_{2}O_{3} and TiO_{2}). The left wall is maintained at a constant temperature higher than the temperature of the right wall. They have shown that the value of the Rayleigh number, the size of the heating device and the volume fraction of the nanofluids effect on the strength of heat transfer. Kamal Raj Kumar Tiwari and ManabDas [3] have conducted numerical studies to analyze the effect of nanofluids on the distribution of the temperature field, the flow lines in a cavity filled with a mixture of water and type of nanoparticles of copper and for different volumetric fractions. They showed that the coefficient of heat exchange is influenced by the Reynolds number and the volume fraction of nanofluid. Nanotechnology has been widely used in industry as materials with nanometer sizes possess unique chemical and physical properties. The nanoscale fluids added are called nanofluids which are used for the first time by Choi [4] . Khanafer et al. [5] have studied the improvement of heat transfer in an enclosure to two dimensions by using the nanofluids for various relevant parameters. They have tested different models from the density of the nanofluid, viscosity and thermal expansion coefficients. They found that nanoparticles in suspension significantly increase the rate of transfer of heat to all number of Grashof.

G. de Vahl Davis et al. [6] have used the method of finite differences to resolve the problem of natural convection in a square cavity differentially heated. These studies have had the merit to launch an international competition on the subject. They have shown that the temperature distribution at mid-height of the cavity is almost linear and the gradient vertical heat tends toward zero for the values of the Rayleigh number inferior than 10^{4}. G. de Vahl Davis [7] has proposed a standard solution known as the benchmark for the case of the square cavity differentially heated in laminar regime. The formulation of the problem done by Davis is the formulation stream function-vorticity. The modified equations by the interaction of a transitional term are discretized by the method of finite differences. The system of an algebraic equation resulting from the operation of discretization is solved by the algorithm ADI (Alternating direction implicit). Zaydan et al. [8] they studied numerically the laminar natural convection of a nanofluid confined in a square cavity. The vertical walls are supposed to be isolated, non-conductor and impervious to the transfer of mass. The horizontal walls are differentially heated, the low wall is maintained to a warm temperature (sine) and the high wall is cold. His study is to develop a new method of accurate resolution of height to solve the equations of heat transfer. The new method is a compact of the fourth order (F.O.C). His work aims to show the interest of the method and to understand the effect of the presence of nanofluids in closed systems squares on the mechanism of the natural convection. The numerical simulations are carried out for a Prandtl number (Pr = 6.2), for the different volume fractions φ Varies between 0% and 10% for the nanofluid (water + Cu) and the Rayleigh numbers between Ra = 10^{3} and Ra = 10^{5}. Markatos and Pericleous [9] have studied numerically, the phenomenon of natural convection in a square cavity filled with air and differentially heated for values of the Rayleigh number included in the interval 10^{3} ≤ Ra ≤ 10^{6}. Jou and Tzeng [10] use of nanofluids to improve the heat transfer by natural convection in a rectangular enclosure. They conducted a numerical study using the model Khanafer. They indicated that the volume fraction of nanofluid causes an increase in the coefficient of thermal transfer medium. Barakos et al. [11] have analyzed numerically the natural convection in a square cavity using an approach of volume of the control. Their calculations were made for laminar flows and turbulent with and without functions of logarithmic walls for a series of functions for Rayleigh up to 10^{10}. The solution captures very well all flow and heat transfer phenomena, especially near the walls where dense, non-uniform grids are used in the thin boundary layers constituted there. Elsherbiny [12] an experimental study conducted from June to pay Studying heat transfer by natural convection in an inclined rectangular cavity. In this work we are interested in the study of the code thermal transfer digital in inclined cavity in relation to the horizontal, in order to study the influence of the inclination angle, the form factor and the volume fraction on the transfer of heat. The main objective of this study is to examine the heat transfer by natural convection in inclined enclosure fully heated filled with nanofluids. In this context, we have established our own code in solving the problem discretized by the method ADI (alternating direction implicit).

2. Mathematical Description of the Problem

The configuration has studied is show in Figure 1. It is a square cavity tilted in relation to the horizontal axis filled with a mixture of water and of nanoparticles of Al_{2}O_{3}, including two walls are maintained at the respective temperatures T_{H} hot and cold T_{C}, the other walls are supposed, adiabatic. The form factor of the cavity is defined as R = H/W.

The nanofluid in the cavity is considered incompressible and Newtonian, the flow is assumed to be laminar and two-dimensional; the liquid phase and nanoparticles are in a state of thermal equilibrium. According to the approximations Boussinesq, the variation of density is negligible everywhere except in the term of buoyancy.

The thermophysical properties with which we will work are described in Table 1.

Figure 1. Physical model and coordinate system.

Table 1. Thermophysical properties of different phases.

Under the assumption of thermal properties constants, the Navier-Stokes equations for an incompressible fluid, unsteady, two-dimensional and are:

・ Continuity equation:

$\frac{\partial u}{\partial x}+\frac{\partial v}{\partial y}=0$ (1)

・ x-momentum equation:

${\rho}_{nf}\left(u\frac{\partial u}{\partial x}+v\frac{\partial u}{\partial y}\right)=-\frac{\partial P}{\partial x}+{\mu}_{nf}{\Delta}_{2}u\left({\rho}_{s}{\beta}_{s}\phi +\left(1-\phi \right){\beta}_{f}{\rho}_{f}\right)\cdot T\cdot g\cdot \mathrm{sin}\left(\varphi \right)$ (2)

・ y-momentum equation:

${\rho}_{nf}\left(u\frac{\partial v}{\partial x}+v\frac{\partial v}{\partial y}\right)=-\frac{\partial P}{\partial y}+{\mu}_{nf}{\Delta}_{2}v\left({\rho}_{s}{\beta}_{s}\phi +\left(1-\phi \right){\beta}_{f}{\rho}_{f}\right)\cdot T\cdot g\cdot \mathrm{cos}\left(\varphi \right)$ (3)

・ Energy equation:

$u\frac{\partial T}{\partial x}+v\frac{\partial T}{\partial y}={\alpha}_{nf}\left[\frac{{\partial}^{2}T}{\partial {x}^{2}}+\frac{{\partial}^{2}T}{\partial {y}^{2}}\right]$ (4)

・ Kinematics equation:

$\frac{{\partial}^{2}\psi}{\partial {x}^{2}}+\frac{{\partial}^{2}\psi}{\partial {y}^{2}}=-\omega $ (5)

where ${\alpha}_{nf}=\frac{{k}_{nf}}{{\left(\rho \cdot {c}_{p}\right)}_{nf}}$

・ The effective viscosity of the fluid containing a dilute suspension of small particles rigid spherical is given by Brinkman:

${\mu}_{nf}=\frac{{\mu}_{f}}{{\left(1-\phi \right)}^{2.5}}$ (6)

・ The effective density of the nanofluids:

${\rho}_{nf}=\left(1-\phi \right){\rho}_{f}+\phi {\rho}_{s}$ (7)

・ The heat capacity of the nanofluids is given as follows:

${\left(\rho {c}_{p}\right)}_{nf}=\phi {\left(\rho {c}_{p}\right)}_{s}+\left(1-\phi \right){\left(\rho {c}_{p}\right)}_{f}$ (8)

・ The thermal conductivity of the actual nanofluids is determined by the model Maxwel-Garnetts:

$\frac{{k}_{nf}}{{k}_{f}}=\frac{{k}_{s}+\left(n-1\right){k}_{f}-\left(n-1\right)\left({k}_{f}-{k}_{s}\right)\phi}{{k}_{s}+\left(n-1\right){k}_{f}-\left({k}_{f}-{k}_{s}\right)\phi}$ (9)

・ The dimensionless parameters are:

$X=\frac{x}{H};Y=\frac{y}{H};\Omega =\frac{\omega {H}^{2}}{{\alpha}_{f}};\Psi =\frac{\psi}{{\alpha}_{f}};V=\frac{vH}{{\alpha}_{f}};U=\frac{uH}{{\alpha}_{f}};\theta =\frac{T-{T}_{h}}{{T}_{c}-{T}_{h}}$ (10)

・ The equations can be written in the form dimensionless below

$\begin{array}{l}\frac{\partial \left(U\Omega \right)}{\partial X}+\frac{\partial \left(V\Omega \right)}{\partial Y}\\ =Gr\cdot P{r}^{2}\cdot A\cdot \left[\mathrm{cos}\left(\varphi \right)\frac{\partial \theta}{\partial X}-\mathrm{sin}\left(\varphi \right)\frac{\partial \theta}{\partial Y}\right]+B\cdot Pr\cdot \left[\frac{{\partial}^{2}\Omega}{\partial {X}^{2}}+\frac{{\partial}^{2}\Omega}{\partial {Y}^{2}}\right]\end{array}$ (11)

where: $A=\frac{1}{\frac{\left(1-\phi \right)}{\phi}.\frac{{\rho}_{f}}{{\rho}_{s}}+1}\frac{{\beta}_{s}}{{\beta}_{f}}+\frac{1}{\frac{\phi}{\left(1-\phi \right)}.\frac{{\rho}_{s}}{{\rho}_{f}}+1}$ ; $B=\frac{1}{{\left(1-\phi \right)}^{2.5}\left[\left(1-\phi \right)+\phi \frac{{\rho}_{s}}{{\rho}_{f}}\right]}$

$U=\frac{\partial \psi}{\partial Y};V=\frac{\partial \psi}{\partial X}$ (12)

$\frac{\partial}{\partial X}\left(\theta \cdot \frac{\partial \psi}{\partial Y}\right)-\frac{\partial}{\partial Y}\left(\theta \cdot \frac{\partial \psi}{\partial X}\right)=\frac{{\alpha}_{nf}}{{\alpha}_{f}}\left(\frac{{\partial}^{2}\theta}{\partial {X}^{2}}+\frac{{\partial}^{2}\theta}{\partial {Y}^{2}}\right)$ (13)

$\frac{{\partial}^{2}\psi}{\partial {X}^{2}}+\frac{{\partial}^{2}\psi}{\partial {Y}^{2}}=-\Omega $ (14)

The Rayleigh number, Prandtl and Grashof are given respectively:

$Pr=\frac{{\nu}_{f}}{{\alpha}_{f}};Ra=\frac{g\beta {H}^{3}\left({T}_{h}-{T}_{c}\right)}{{\nu}_{f}\alpha};Gr=\frac{g\beta {H}^{3}\left({T}_{h}-{T}_{c}\right)}{{\nu}_{f}^{2}}$

The boundary conditions no dimensional are written as:

$\begin{array}{l}\text{On the left wall}:X=0;\Psi =0;\Omega =-\frac{{\partial}^{2}\Psi}{\partial {X}^{2}};\theta =1\\ \text{On the Right wall}:X=1;\Psi =0;\Omega =-\frac{{\partial}^{2}\Psi}{\partial {X}^{2}};\theta =0\\ \text{On the wall stop and bottom}:\Psi =0;\Omega =-\frac{{\partial}^{2}\Psi}{\partial {Y}^{2}};\frac{\partial \theta}{\partial Y}=0\end{array}\}$ (15)

The Nusselt number can be expressed as:

$Nu=\frac{hH}{{k}_{f}}$ (16)

The coefficient of heat transfer is given by the Equation (17):

$h=\frac{{q}_{w}}{{T}_{h}-{T}_{c}}$ (17)

The thermal conductivity is expressed as:

${k}_{nf}=\frac{{q}_{w}}{\frac{\partial T}{\partial x}}$ (18)

Substituting Equations ((17), (18)) and Equation (9) in Equation (16), and using the settings dimensionless, the Nusselt number is given by the equation below:

$Nu=-\left(\frac{{k}_{nf}}{{k}_{f}}\right)\cdot \frac{\partial \theta}{\partial X}$ (19)

The average Nusselt number is:

$\stackrel{\xaf}{Nu}={\displaystyle \underset{0}{\overset{1}{\int}}Nu\left(Y\right)\cdot \text{d}Y}$ (20)

3. Numerical Method

The procedure of discretization of the equations (Guidelines Equations (11), (13), (14)) and the boundary conditions described by the Equation (15) have solved numerically using a finite difference technique. The equations of vorticity and energy are resolved using the method ADI (alternating direction implicit) and the equation of the function of current is resolved by the method SOR (successively over relaxation) while the difference in the near is used for the convective terms. The application line by line of the TDMA method (Tri-Diagonal Matrix Algorithm) (21) is applied to the equations of vorticity and energy until the sum of the residues becomes lower than 10^{−6}. The developed algorithm has been implemented in the Fortran program.

The convergence criterion is defined by the following expression:

$\epsilon =\frac{{\displaystyle {\sum}_{j=1}^{j=M}{\displaystyle {\sum}_{i=1}^{i=N}\left|{\Phi}^{n+1}-{\Phi}^{n}\right|}}}{{\displaystyle {\sum}_{j=1}^{j=M}{\displaystyle {\sum}_{i=1}^{i=N}\left|{\Phi}^{n+1}\right|}}}<{10}^{-6}$ (21)

where ε is the tolerance; M and N are the number of grid points in the x and y directions respectively.

4. Grid Testing and Code Validation

The test of the mesh size is carried out in the case of Ra = 10^{5}, Pr = 6.2, φ = 10%, Φ = 0˚ and R = 1. The temperature and vertical speed calculated at half height of the cavity are presented in Figure 2 and Figure 3 for the sizes of mesh size 61 × 61, 81 × 81, 162 × 162 and 324 × 324. We can see that the differences in the calculated temperature and the speed are very low between the four meshes used and the size of the mesh size 81 × 81 is sufficient for R = 1. Consequently, a uniform mesh size of 324 × 81, 81 × 162, 81 × 81 and 324 × 324 is used respectively for R = 0.25, 0.5, 1, and 4.

Figure 2. Temperature profiles at middle of hot wall cavity for various sizes of meshes (Ra = 10^{5}, Pr = 6.2, φ = 10%, Φ = 0˚ and R = 1).

Figure 3. Velocity profiles at middle of hot wall for various mesh sizes (Ra = 10^{5}, Pr = 6.2, φ = 10%, Φ = 0˚and R = 1).

In order to validate our code of calculation, we made a comparison with the previous results (Figure 4 and Figure 5), in the case of a square cavity without horizontal nanofluids. From this comparison, we see that there is a qualitative agreement between the results obtained by our code of calculation and those of previous work; this strengthens in the choice of our mathematical models and digital.

5. Results and Discussion

Once the code of calculation has been validated, we studied the influence of different

Figure 4. Comparison of the temperature distribution at mid-height of the cavity with previous work for (Ra = 10^{5}, Pr = 0.7, Φ = 0˚).

Figure 5. Variation of average Nusselt number Rayleigh numbers and comparison with other published works on the left wall (Ra = 10^{5}, Pr = 0.7, Φ = 0˚, R = 1).

parameters on the thermal transfer. The results will be given in the form of the streamlines, and isotherms, average Nusselt as a function of correlation of the Rayleigh number between 10^{3} ≤ Ra ≤ 10^{5}, for different volume fractions of 0% ≤ φ ≤ 10% and different angles of tilt angle 0˚ ≤ f ≤ 90˚. For the form factor (R = 0.25, 0.5, 1 and 4), the results are presented as the streamlines and isotherms, the Nusselt number, temperature and velocity profiles.

For a horizontal cavity without nanofluid and R = 1, being observed in Figure 6 a convective scheme for Ra = 10^{4} and Ra = 10^{5} but a conductive schema for Ra = 10^{3}.

For a Rayleigh number (Ra = 10^{4}), the isotherms become more deflected by report to the waves of Ra = 10^{3}, and the volume fractions higher always cause a slight deviation of the current lines and the isotherms between the nanofluid and the pure fluid. For a Rayleigh number Ra = 10^{5}, the isotherms become deflected by report to the curves of the two previous cases. The increase of the volume fractions entails a significant deviation of the isotherms and of the streamlines between the nanofluid and the pure fluid. The flow passes to a type of boundary layer (Figure 7).

Figure 8 shows the lines of current to the left and the isotherms to the right

Figure 6. Temperature and velocity profiles in the middle hot of the cavity for Pr = 6.2, Φ = 0˚, R = 1.

Figure 7. Streamlines (left) and isotherms (right) at various volume fractions for (Pr = 6.2; Φ = 0˚, R = 1).

Figure 8. Streamlines (left) and isotherms (right) at different angles for ( Ra = 10^{5}, Pr = 6.2, φ = 10%, R = 1).

for different angles of inclinations. It is observed that the shape of the main cell is sensitive to the inclination angle. For Φ = 90˚, the flow of Rayleigh-Bénard type is formed for the inner cavity because of the existence of the gravity in the enclosure. Figure shows that the transfer of heat is more pronounced for Φ = 30˚ and low for Φ = 90˚.

Figure 9 illustrates the isotherms and the streamlines at various angles of inclinations (Φ = 0˚, 15˚, 30˚, 45˚, 60˚, 75˚ and 90˚) for Ra = 10^{5}, Pr = 6.2, φ = 10% and the form factor equal to 0.5. It is observed that the shape of the main cell of the streamlines decreases with the increase of angle of tilt and deflected to the left. Small cells of recirculation in the lower right corner and in the upper left corner for Φ = 90˚. Figure 12(b) shows that the transfer of heat is higher for Φ = 15 ˚ is low for Φ = 90˚.

Figure 10 shows the streamlines and the isotherms to different angles of inclinations (Φ = 0˚, 15˚, 30˚, 45˚, 60˚, 75˚ and 90˚) for Ra = 10^{5}, Pr = 6.2, φ = 10% and R = 0.25.It is noticed that the shape of the cell is reduced with the increase of the inclination angle. It is observed a change in the cell structure of cells for Φ = 90˚. That is why the transfer of heat is low, as shown in Figure 12(c) to Φ = 90˚.

Figure 9. Streamlines contours (left) and isotherms (right) at various angles for ( Ra = 10^{5}, Pr = 6.2, φ = 10%, R = 0.5).

Figure 10. Streamlines contours (left) and isotherms (right) at various angles for ( Ra = 10^{5}, Pr = 6.2, φ = 10%, R = 0.25).

Figure 11 shows the lines of the streamlines and the isotherms for different inclination angle (Φ = 0˚, 15˚, 30˚, 45˚, 60˚, 75˚ and 90˚) for Ra = 10^{5}, Pr = 6.2, φ = 10% and the form factor equal to 4. We see that the isotherms are insensitive to the inclination angle with the exception of the angle Φ = 90˚ to the cause of the decline in heat transfer, as shown in Figure 12(d).

6. Conclusions

In this work, it has been demonstrated the influence of the inclination angle

Figure 11. Streamlines (left) and isotherms (right) at various angles for ( Ra = 10^{5}, Pr = 6.2, φ = 10%, R = 4) and Φ = 0˚ (a); Φ = 15˚ (b); Φ = 30˚ (c); Φ = 45˚ (d); Φ = 60˚ (e); Φ = 75˚ (f); Φ = 90˚ (g).

Figure 12. Variation of the average Nusselt number with different inclination angles for φ = 10% and the form factor (a) = 1, (b) = 0.5, (c) = 0.25, (d) = 4.

as well as the volume fraction of nanoparticles and the form factor in cavity. The results have indicated that the addition of the nanoparticles of Al_{2}O_{3} has produced a remarkable enhancement on heat transfer with respect to that of the pure fluid. The heat transfer increases with the increase of Rayleigh, but the effect of the concentration of nanoparticles on the the Nusselt number is more pronounced at low Rayleigh number than at high Rayleigh number. Inclination angle of the cavity is considered as a control parameter of the fluid flow and heat transfer. It has been seen that the heat transfer is more low to Φ = 90˚. But the increase of the values of the volume fraction becomes insignificant flow of fluid from this angle. Finally, the angle of tilt is a good parameter of control in the two cases of a cavity filled with pure fluid and nanofluid.

It was concluded that inclination angle where the heat transfer minimal has developed to a close relationship with the structure of the flow of transition. For the form factor of 1 and 0.5, the secondary flow which occurs in the corners of the cavities was found to cause a decrease in the transfer of heat. For the form factor of 0.25, a decrease of heat has occurred at the transformation of a unique cellular structure in a cell to seven cells. The transfer of heat is incremented for form factor equal to 4.

Nomenclature

C_{p} Specific heat capacity [J∙kg^{−1}∙K^{−1}]

$g$ Gravitational acceleration [m∙s^{−2}]

Gr Grashof number $Gr=\left({\beta}_{f}{H}^{3}g\left({T}_{h}-{T}_{c}\right)\right)/\left({\nu}_{f}^{2}\right)$

H Height of the cavity [m]

k Thermal conductivity [W/m∙K]

$\stackrel{\xaf}{Nu}$ Average Nusselt number

Nu Local Nusselt number

p Pressure [Pa]

P The dimensionless pressure

Pr

R Prandtl number Pr = α_{f}/ν_{f}

Form factor

Ra Rayleigh number $Ra=\left({\beta}_{f}g{H}^{3}\left({T}_{h}-{T}_{c}\right)\right)/\left({\nu}_{f}\alpha \right)$

T Temperature [K]

W Width of the cavity [m]

(x, y) Cartesian coordinates-dimensional [m]

(X, Y) Cartesian coordinates dimensionless

u, v Velocity components in the directions x, y [m∙s^{−1}]

U, V Dimensionless velocity components

Greek symbols

α Thermal diffusivity [m^{2}∙s^{−1})

β Thermal expansion coefficient [K^{−1}]

φ Solid volume fraction [%]

µ Dynamic viscosity [N∙s∙m^{−2}]

n Kinematic viscosity [m²∙s^{−1}]

r Density [kg∙m^{−3}]

Ω Dimensionless vorticity

Φ Inclination angle [˚]

Ψ Dimensionless stream function

q Dimensionless temperature

Indices

c Cold

eff Effective

h Hot

s Solid

f Fluid

Operators

D Laplacian

References

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[2] Oztop, H.F. and Abu-Nada, E. (2008) Numerical Study of Natural Convection in Partially Heated Rectangular Enclosure Filled with Nanofluids. International Journal of Heat and Fluid Flow, 29, 1326-1336.

https://doi.org/10.1016/j.ijheatfluidflow.2008.04.009

[3] Tiwari, R.K. and Das, K. (2007) Heat Transfer Increase in a Two-Sided Lid-Driven Differentially Heated Square Cavity Utilizing Nanofluids. International Journal of Heat and Mass Transfer, 50, 2002-2018.

https://doi.org/10.1016/j.ijheatmasstransfer.2006.09.034

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[5] Khanafer, K., Vafai, K. and Lightstone, M. (2003) Buoyancy-Driven Heat Transfer Enhancement in a Two-Dimensional Enclosure Utilizing Nanofluids. International Journal of Heat and Mass Transfer, 46, 3639-3653.

https://doi.org/10.1016/S0017-9310(03)00156-X

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https://doi.org/10.1002/fld.1650030305

[8] Zaydan, M., Yadil, N., Boulahia, Z., Wakif, A. and Sehaqui, R. (2016) Compact Fourth-Order Formulation for the Resolution of Heat Transfer in Natural convection of Water-Cu Nanofluid in a Square Cavity with a Sinusoidal Thermal Boundary condition. World Journal of Nano Science and Engineering, 6, Article ID: 67550.

https://doi.org/10.4236/wjnse.2016.62009

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https://doi.org/10.1016/0017-9310(84)90145-5

[10] Jou, R.-Y. and Tzeng, S.-C. (2006) Numerical Research of Nature Convective Heat Transfer Enhancement Filled with Nanofluids in Rectangular Enclosures. International Communications in Heat and Mass Transfer, 33, 727-736.

https://doi.org/10.1016/j.icheatmasstransfer.2006.02.016

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