3D Buoyancy-Induced Flow and Entropy Generation of Nanofluid-Filled Open Cavities Having Adiabatic Diamond Shaped Obstacles

Abstract

A three dimensional computational solution has been obtained to investigate the natural convection and entropy generation of nanofluid-filled open cavities with an adiabatic diamond shaped obstacle. In the model, the finite volume technique was used to solve the governing equations. Based on the configuration, the cavity is heated from the left vertical wall and the diamond shape was chosen as adiabatic. Effects of nanoparticle volume fraction, Rayleigh number (10³ ≤ Ra ≤ 10⁶) and width of diamond shape were studied as governing parameters. It was found that the geometry of the partition is a control parameter for heat and fluid flow inside the open enclosure.

1. Introduction

The work on open systems is vital in the design of electronic cooling, heating and cooling of building, ventilation, food industry and solar applications. Bilgen and Öztop [1] solved via a finite volume method the two-dimensional governing equations of 2D natural convection in partially open inclined cavities. Prakash et al. [2] studied different heat transfer areas using Fluent. A buoyancy-induced flow loss is observed to increase with increasing opening ratio. This increment in buoyancy-induced flow loss for different inclination angles is found to range between 30%–80% when the opening ratio is increased from 1/4 to 1/2 for all closed space shapes. Zamora and Kaiser [3] solved the convective flows in cubical open cavities. They investigated the influence of an internal wall (adiabatic or isothermal) as well as the slope of an external heated wall on flow structure and heat transfer.

The number of studies on buoyancy-induced flow in nanofluid-filled open cavities, has increased recently. In this context, buoyancy-induced flow of a SWCNT-nanofluid (single-walled carbon nanotube nanofluids) in an open enclosure was studied by Jafari et al. using a lattice Boltzmann simulation [4]. It is mainly a square closed space heated with an isothermal vertical wall. They observed that the aspect ratio of the closed space plays an important role in buoyancy-induced flow and an increase of this parameter leads to heat transfer reduction in the target problem. Sheremet et al. [5] applied the curvilinear boundary conditions on a nanofluid-filled wavy walled closed space and they found that both waviness and nanoparticle volume rate are effective parameters in buoyancy-induced flow and heat transfer.

Using the lattice Boltzmann approach, Kefayati [6] studied the entropy generation due to laminar buoyancy induced flow in a square closed space filled with non-Newtonian nanofluid. He observed that total entropy production rises with the Ra number and the increase in volume fraction enhances entropy generation due to heat and fluid flow in different power-law indexes. Later, Kefayati [7] employed the lattice Boltzmann method to investigate the free convection in an open cavity in the presence of MHD flow using alumina/water nanofluid. Mejri and Mahmoudi [8] applied a magnetic field on buoyancy-induced flow heat transfer in a nanofluid-filled open enclosure.

Öztop and Salem [9] performed a review to present on entropy-related work with energy systems including buoyancy-induced flow. There are few works on three-dimensional analysis of entropy generation. Öztop et al. [10] numerically studied the three-dimensional heat transfer and entropy generation due to combined buoyancy and thermocapillary convection in a cubic cavity. Their results elucidated that at low Rayleigh numbers, the Marangoni number influence on the total entropy generation rises. Entropy generation for buoyancy-induced flow in a partitioned closed space, with adiabatic horizontal and isothermally cooled vertical walls, is studied numerically by Famouri and Hooman [11]. They presented the effects of fluid friction on entropy production is weak and the heat transfer irreversibility increases almost linearly with the Nu number and the temperature difference.

Mehrez et al. [12] exploited the finite-volume method to study the MHD flow effect on the entropy generation due to the use of Cu–water nanofluids in an open cavity where the bottom side was heated. They concluded that the average Nusselt number and entropy generation were enhanced with particle loading. Furthermore, it was found that the amount of increase in the Nusselt number and entropy generation depends on the intensity of the magnetic field (Hartmann number), and the angle at which the magnetic field is applied.

Heat transport can be controlled by installing differently shaped passive elements in open or closed cavities. In this context, conjugate heat transfer in a partially open square closed space with a vertical heat source has been simulated by Koca [13]. In this case, the closed space had an opening on the top side where the position and size of opening was changed. It was found that ventilation location has a significant influence on the heat transfer rate. Nasrin [14] concluded that obstacles could be used as effective tools to control the heat transfer in cavities where MHD flow is considered in the problem.

Hussein et al. [15] solved the three-dimensional buoyancy-induced flow and entropy generation in a trapezoidal closed space with different slopes filled with air for Rayleigh numbers in the range of 10³ and 10⁵. The closed space was heated from the bottom wall while the left and right sides were kept at a lower temperature compared to the bottom. They found that at low Rayleigh numbers, the slope of the closed space has no effect on the total entropy generation.

This literature review indicates that most studies on buoyancy-induced flow in open cavities have been considered as 2D dimensional problems. The main aim of this paper was to perform a 3D analysis of heat transport of nanofluids in an open cavity with a diamond shaped obstacle in the middle of a closed space.

2. Definition of the Physical Model

Figure 1 displays a schematic of the present problem. As shown, the left side of the closed space has a higher temperature than the right side that is considered as the opening. Other walls are assumed to be adiabatic. A diamond shaped obstacle with a side size of Ld and insulated walls is inserted in the middle of the closed space. The space between the closed space and the obstacle is filled with Al₂O₃/water nanofluid.

Figure 1. Physical model with boundary conditions.

The nanofluid is assumed to be incompressible and the flow is considered laminar. The base fluid and nanoparticles are assumed to be at thermal equilibrium. Table 1 presents the thermo-physical properties of the base fluid (water) and the nanoparticles.

Table 1. Thermo-physical properties of nanoparticles and base fluid.

Properties	Al2O3	Water
Cp (J·kg−1·°C−1)	765	4179
ρ (kg·m−3)	3970	997.1
k (W·m−1·°C−1)	40	0.613
α × 107 (m2·s−1)	131.7	1.47
$\beta$ × 10−5 (K−1)	0.85	21

2.1. Governing Equations

Equations governing the studied configuration were written using the 3D vorticity-vector potential formalism $(\overrightarrow{\psi }-\overrightarrow{\omega })$. This formalism allows the elimination of the pressure which is delicate to treat. Vorticity and vector potential are defined respectively by the following two relations:

$$\overrightarrow{\omega }\prime =\overrightarrow{\nabla }\times \overrightarrow{V}\prime$$

(1a)

and

$$\overrightarrow{V}\prime =\overrightarrow{\nabla }\times \overrightarrow{\psi }\prime$$

(1b)

Using the dimensionless variables the governing equations are written in the following form:

$$-\overrightarrow{\omega }={\nabla }^2\overrightarrow{\psi }$$

(2)

$$\frac{\partial \overrightarrow{\omega }}{\partial t}+(\overrightarrow{V}\cdot \nabla )\overrightarrow{\omega }=(\overrightarrow{\omega }\cdot \nabla )\overrightarrow{V}+\frac{{\nu }_{nf}}{{\nu }_f}\mathrm{Pr}\cdot {\nabla }^2\overrightarrow{\omega }-\frac{{\beta }_{nf}}{{\beta }_f}Ra\mathrm{Pr}\nabla \times T\overrightarrow{g}$$

(3)

$$\frac{\partial T}{\partial t}+\overrightarrow{V}\cdot \nabla T=\frac{{\alpha }_{nf}}{{\alpha }_f}{\nabla }^{2}T$$

(4)

The velocity ($\overrightarrow{V}\prime$), time ($t\prime$), vector potential ($\overrightarrow{\psi }\prime$) and vorticity ($\overrightarrow{\omega }\prime$), are put respectively in the dimensionless forms by $\alpha /l$, $l^2/\alpha$, $\alpha$ and $l^2/\alpha$ and the dimensionless temperature is written as:

$$T=(T\prime -T_c\prime )/(T_h\prime -T_c\prime )$$

(5)

In these equations, the dimensionless Pr and Ra numbers are respectively defined as:

$$\mathrm{Pr}=\frac{\nu }{\alpha }\text{ and Ra}=\frac{g\cdot \beta \cdot \Delta T\cdot l^3}{\nu \cdot \alpha }$$

(6)

The effective density, the specific heat, the effective thermal conductivity (Maxwell–Garnetts model) and the effective dynamic viscosity (Brinkman model) of the nanofluid are given respectively as [16,17]:

$${\rho }_{nf}=\left(1-\varphi \right){\rho }_f+\varphi {\rho }_s$$

(7)

$${\left(\rho C_p\right)}_{nf}=\left(1-\varphi \right){\left(\rho C_p\right)}_f+\varphi {\left(\rho C_p\right)}_s$$

(8)

$$\frac{k_{nf}}{k_f}=\frac{k_s+2k_f-2\varphi \left(k_f-k_s\right)}{k_s+2k_f+\varphi \left(k_f-k_s\right)}$$

(9)

$${\mu }_{nf}=\frac{{\mu }_f}{{\left(1-\varphi \right)}^{2.5}}$$

(10)

2.2. Boundary Conditions

For the considered configuration, the boundary conditions are:

Temperature:

$$T=1\text{ for }x=0$$

(11)

$$\frac{\partial T}{\partial n}=0\text{ on adiabatic walls}$$

(12)

$$T_{in}=Tc\text{ if }n.V<0$$

(13a)

and

$${\frac{\partial T}{\partial n}|}_{out}=0\text{ if }n.V\ge 0\text{ At open boundary}$$

(13b)

Vorticity:

$${\omega }_x=0,{\omega }_y=-\frac{\partial V_z}{\partial x}\text{ and }{\omega }_z=\frac{\partial V_y}{\partial x}\text{ at }x=0$$

(14)

$${\omega }_x=\frac{\partial V_z}{\partial y},{\omega }_y=0\text{ and }{\omega }_z=-\frac{\partial V_x}{\partial y}\text{ at }y=0\text{ and }1$$

(15)

$${\omega }_x=-\frac{\partial V_y}{\partial z},{\omega }_y=\frac{\partial V_x}{\partial z}\text{ and }{\omega }_z=0\text{ at }z=0\text{ and }1$$

(16)

Vector potential:

$$\frac{\partial {\psi }_x}{\partial x}={\psi }_y={\psi }_z=0\text{ at }x=0$$

(17)

$${\psi }_x=\frac{\partial {\psi }_y}{\partial y}={\psi }_z=0\text{ at }y=0\text{ and }1$$

(18)

$${\psi }_x={\psi }_y=\frac{\partial {\psi }_z}{\partial z}=0\text{ at }z=0\text{ and }1$$

(19)

Velocity:

$$V_x=V_y=V_z=0\text{ on all walls}$$

(20)

$$\frac{\partial V_x}{\partial x}=\frac{\partial V_y}{\partial x}=\frac{\partial V_z}{\partial x}=0\text{ at open boundary}$$

(21)

The expression of the dimensional generated entropy ($S{\prime }_{gen}$) is presented by Equation (22):

$$\begin{array}{l}S{\prime }_{gen}=\left\{\frac{k_{nf}}{T_0^2}\left[{\left(\frac{\partial T\prime }{\partial x\prime }\right)}^2+{\left(\frac{\partial T\prime }{\partial y\prime }\right)}^2+{\left(\frac{\partial T\prime }{\partial z\prime }\right)}^2\right]\right\}+\hfill \\ \frac{{\mu }_{nf}}{T_0^{}}\left\{2\left[{\left(\frac{\partial V{\prime }_x}{\partial x\prime }\right)}^2+{\left(\frac{\partial V{\prime }_y}{\partial y\prime }\right)}^2+{\left(\frac{\partial V{\prime }_z}{\partial z\prime }\right)}^2\right]+{\left(\frac{\partial V{\prime }_y}{\partial x\prime }+\frac{\partial V{\prime }_x}{\partial y\prime }\right)}^2+{\left(\frac{\partial V{\prime }_z}{\partial y\prime }+\frac{\partial V{\prime }_y}{\partial z\prime }\right)}^2+{\left(\frac{\partial V{\prime }_x}{\partial z\prime }+\frac{\partial V{\prime }_z}{\partial x\prime }\right)}^2\right\}\hfill \end{array}$$

(22)

Put in its dimensionless form, the local generated entropy ($N_s$) is written as:

$$\begin{array}{l}{N}_s=\frac{k_{nf}}{k_f}\left[{\left(\frac{\partial T}{\partial x}\right)}^2+{\left(\frac{\partial T}{\partial y}\right)}^2+{\left(\frac{\partial T}{\partial z}\right)}^2\right]\hfill \\ +{\varphi }_S\frac{{\mu }_{nf}}{{\mu }_f}\left\{2\left[{\left(\frac{\partial V_x}{\partial x}\right)}^2+{\left(\frac{\partial V_y}{\partial y}\right)}^2+{\left(\frac{\partial V_z}{\partial z}\right)}^2\right]+\left[{\left(\frac{\partial V_y}{\partial x}+\frac{\partial V_x}{\partial y}\right)}^2+{\left(\frac{\partial V_z}{\partial y}+\frac{\partial V_y}{\partial z}\right)}^2+{\left(\frac{\partial V_x}{\partial z}+\frac{\partial V_z}{\partial x}\right)}^2\right]\right\}\hfill \end{array}$$

(23)

In this equation another dimensionless parameter appears, this number is the irreversibility coefficient defined by:

$${\varphi }_S={\left(\frac{\alpha }{l\Delta T}\right)}^2{T}_0$$

(24)

The local generated entropy is the sum of two types of entropies; the first one is due to temperature gradients (N_s–th) and the second is due to viscous effects (N_s-fr).

The total generated entropy ($S_{tot}$) is given by:

$$S_{tot}={\displaystyle \underset{v}{\int }{N}_s}dv={\displaystyle \underset{v}{\int }\left(N_{s-th}+N_{s-fr}\right)}dv=S_{th}+S_{fr}$$

(25)

The Bejan number (Be) is the ratio of heat transfer irreversibility to the total irreversibility due to the heat transfer and the fluid friction as:

$$Be=\frac{S_{th}}{S_{th}+S_{fr}}$$

(26)

The local Nusselt number (Nu) is defined as follows:

$$Nu={\left(\frac{k_{nf}}{k_f}\right){\frac{\partial T}{\partial x}}_{}|}_{x=0,1}$$

(27)

The average Nusselt number on the hot wall ($N{u}_{av}$), is expressed by:

$$N{u}_{av}={\displaystyle \underset{0}{\overset{1}{\int }}{\displaystyle \underset{0}{\overset{1}{\int }}Nu\cdot dy\cdot dz}}$$

(28)

The FORTRAN language was used to write the numerical program allowing to solve the mathematical model described above. Governing Equations (2)–(4) and (23) were discretized using the control volume method based on the central-difference scheme and solved using the successive relaxation iteration scheme. Although grids are uniform in all directions, additional nodes are added on boundaries. For all numerical tests, the time step and spatial mesh are fixed respectively at (10⁻⁴) and (81³) and the convergence criterion for each step of time is chosen as:

$${\displaystyle \sum _i^{1,2,3}\frac{\max \left|{\psi }_i^n-{\psi }_i^{n-1}\right|}{\max \left|{\psi }_i^n\right|}}+\max \left|T_i^n-T_i^{n-1}\right|\le {10}^{-5}$$

(29)

3. Validation of the Code and Grid Dimension

For 3D analysis, the findings of Wakashima and Saitoh [18] and Fusegi et al. [19] on buoyancy- induced flow are validated with Pr = 0.71 and shown in Table 2. The present results are in excellent agreement with the previously reported results. After a grid sensivity test, the 81 × 81 × 81 grid distribution with additional nodes in boundaries was retained. For nanofluids buoyancy-induced flow, the code was validated by comparing with the studies of Öztop and Abu-Nada [20] (Figure 2) and of Jahanshahi et al. [21] (Figure 3). It can be said from this comparison that there is good agreement.

Table 2. Comparison of present results with the 3D results of (Wakashima and Saitho [18]) and (Fusegi et al. [19]) for differentially heated cubic closed space and Pr = 0.71.

Ra	Authors	${\psi }_z$ (Center)	${\omega }_z$ (Center)	$V_{x\max }$ (y)	$V_{y\max }$ (x)	$N{u}_{av}$
104	Present work	0.05528	1.1063	0.199 (0.826)	0.221 (0.112)	2.062
	Wakashima and Saitho [18]	0.05492	1.1018	0.198 (0.825)	0.222 (0.117)	2.062
	Fusegi et al. [19]	-	-	0.201 (0.817)	0.225 (0.117)	2.1
105	Present work	0.034	0.262	0.143 (0.847)	0.245 (0.064)	4.378
	Wakashima and Saitoh [18]	0.03403	0.2573	0.147 (0.85)	0.246 (0.068)	4.366
	Fusegi et al. [19]	-	-	0.147 (0.855)	0.247 (0.065)	4.361
106	Present work	0.01972	0.1284	0.0832 (0.847)	0.254 (0.032)	8.618
	Wakashima and Saitho [18]	0.01976	0.1366	0.0811 (0.86)	0.2583 (0.032)	8.6097
	Fusegi et al. [19]	-	-	0.0841 (0.856)	0.259 (0.033)	8.77

Figure 2. Nusselt number versus ϕ for Ra = 10⁴; comparison with results of Öztop and Abu-Nada [20].

Figure 3. Comparison of the temperature on axial midline between the present results (cubic closed space; z = 0.5 plan) and results of Jahanshahi et al. [21] (Pr = 6.2, ϕ = 0.1 and Ra = 6.2 × 10⁴).

4. Results and Discussion

A computational work has been done to solve the equations of buoyancy-induced flow in a 3D open cavity with a diamond shaped obstacle. The working fluid is chosen as a nanofluid and entropy generation is also analyzed for different governing parameters such as nanoparticle volume fraction, Ra number and length of the diamond obstacle.

Streamlines and velocity vector projection at z = 0.5 plan for different Ra numbers and nanoparticle fractions are presented in Figure 4 and Figure 5, respectively, at Ld = 0.3. The flow enters the closed space from the bottom side and goes to the top side by surrounding the partition. Also, a small part of the fluid comes into the closed space and impinges on the inserted body and goes back. It shows small differences between nanofluid and pure fluid. Vena contracta shaped flow is formed around the inserted body. With increasing flow velocity and Ra number, a circulation cell is formed on the corner of the inserted body. This circulation cell becomes bigger with nanoparticle addition. Its dimension also increases with increasing Ra number.

Figure 4. Streamlines for Ld = 0.3 and different Ra; (Left) ϕ = 0; and (Right) ϕ = 0.15.

Figure 5. Velocity vector projection at z = 0.5 plan for Ld = 0.3 and different Ra; (Left) ϕ = 0; and (Right) ϕ = 0.15.

Figure 6, presents the iso-surfaces of temperature for Ld = 0.3 at different Ra numbers for both nanofluid and water. For higher values of Ra number, the thermal boundary layer becomes thinner. Thus, insertion of the body becomes more effective for the lower values of Ra number. It is noticed that the inserted body has adiabatic boundary conditions. Thus, heat is captured under the left bottom side of the partition.

Figure 6. Iso-surfaces of temperature for Ld = 0.3 and different Ra; Dark (ϕ = 0.15) clear (ϕ = 0).

Figure 7 illustrates the isotherms for different Ra numbers and nanoparticle volume fraction at z = 0.5. As seen from the figure, distances among isotherms are almost same due to the domination of the conduction mode of heat transfer at low Ra numbers. Thus, isotherms are distributed diagonally due to the inserted insulated material. The effects of the inserted body become less due to thinner thermal boundary layer at higher Ra number. Local thermal entropy generation is displayed for different Ra number. In Figure 8, gray lines show values for pure fluid and black ones are given for nanofluids. S_th value becomes effective at the corners of the inserted body due to increases in kinetic energy. It is also cumulated mostly at the bottom side of the left vertical wall due to heat transport way. The inserted body behaves as an insulated wall. When values of Ra number increase the thermal boundary layer becomes thinner and the inserted body becomes insignificant on S_th value. Figure 9 illustrates the entropy generation due to fluid friction. Again, the edge of the inserted body becomes significant in entropy generation. Also, boundaries are effective for entropy generation. Especially, the top outlet edge becomes effective in entropy generation due to fluid friction, because friction is increased at that part of the flow.

Figure 7. Isotherms at z = 0.5 plan for Ld = 0.3 and different Ra; (gray) ϕ = 0; (black) ϕ = 0.15.

Figure 8. Local thermal entropy generation (S_th) at z = 0.5 plan for Ld = 0.3 and different Ra; (gray) ϕ = 0; (black) ϕ = 0.15.

Figure 9. Local entropy generation due to friction (S_fr) at z = 0.5 plan for Ld = 0.3 and different Ra; (gray) ϕ = 0; (black) ϕ = 0.15.

Total entropy generation is presented in Figure 10 for the same parameters as Figure 8 and Figure 9. Figure 11 shows the variation of average Nusselt number along the hot wall as a function of nanoparticle volume fraction at different Ra numbers. For Ra = 10³ and 10⁴, heat transport becomes constant with volume fraction, due to the domination of conduction mode. For higher Ra, heat transfer increases by increasing the nanoparticle volume fraction.

Figure 10. Local total entropy generation (S_tot) at z = 0.5 plan for Ld = 0.3 and different Ra; (gray) ϕ = 0; (black) ϕ = 0.15.

Figure 11. Average Nusselt number at hot wall as function of ϕ for Ld = 0.3 and different Ra.

Geometric effects of the inserted body are presented in Figure 12 for the highest value of Ra number. As seen from the figure, the dimension of the partition is the main effective parameter in the flow structure inside the closed space. In any case, a circulation cell occurs due to flow separation of the corner of the partition. Also, another mini-circulation cell is formed under this circulation cell. For the biggest partition, the flow is obstructed from the outside. Nanoparticle addition has less effect on flow structure.

Figure 12. Velocity vector projection at z = 0.5 plan for Ra = 10⁶ and different Ld = 0.3.

In the same manner, isotherms are given in Figure 13 for different nanoparticle volume fraction at z = 0.5 for Ra = 10⁶. The small partition size becomes insignificant in the temperature distribution. However, temperature distribution is affected by the partition and the high temperature penetrates into the cavity.

Figure 13. Isotherms at z = 0.5 plan for Ra = 10⁶ and different Ld (gray) ϕ = 0; (black) ϕ = 0.15.

Average Nusselt number is illustrated for the considered parameters in Figure 14. As seen from the figure, the general trend with geometrical parameter is a small decrease. However, higher heat transfer is obtained with the addition of nanoparticles into the base fluid. Variation of S_th value with geometrical parameter is plotted in Figure 15 at different Ra numbers. As given in the figure, entropy generation becomes almost constant with geometrical parameters for lower Ra numbers. However, it is increased with the increase of geometrical parameter at higher values of the Ra number due to increase in heat transfer. Entropy generation due to friction as a function of geometrical parameter for different nanoparticle volume fraction is shown in Figure 16(a) for lower Ra numbers and Figure 16b for higher Ra numbers. It is an interesting result that heat transfer is decreased for Ld > 0.3 due to the obstruction effect of the inserted body. Entropy generation due to fluid friction becomes constant for different geometrical parameters at Ra = 10⁵ for both nanofluid and pure fluid. It is increased with geometrical parameter for Ra = 10⁶ and higher heat transfer occurs for nanofluids.

Figure 14. Average Nusselt number at hot wall for ϕ = 0 and ϕ = 0.15 and different Ra.

Figure 15. Thermal entropy generation as function of Ld for ϕ = 0 and ϕ = 0.15 and different Ra.

Figure 16. Entropy generation due to friction as a function of Ld for ϕ = 0 and ϕ = 0.15 and different Ra; (a) Ra = 10³ and 10⁴; (b) Ra = 10⁵ and 10⁶.

Figure 17 illustrates the total entropy generation for the chosen parameters. Total entropy generation becomes almost constant for Ra = 10⁵ with Ld values and higher values are formed for nanofluids. However, entropy generation is increased almost linearly with Ld values for Ra = 10⁶. On the contrary, entropy generation decreases with Ld values due to obstruction of the inserted body. Finally, Figure 18 presents the variation of Bejan number with Ld values at different Ra number and nanoparticle volume fraction. This value becomes almost constant for the highest value of Ra number for all values of geometrical parameters. On the contrary, Bejan number is decreased with increasing the geometrical parameter but in any cases, higher values are formed for the case of nanofluids. This decreasing trend is also valid for Ra = 10⁴.

Figure 17. Total entropy generation as function of Ld for ϕ = 0 and ϕ = 0.15 and different Ra; (a) Ra = 10³ and 10⁴; (b) Ra = 10⁵ and 10⁶.

Figure 18. Bejan number as function of Ld for ϕ = 0 and ϕ = 0.15 and different Ra.

5. Conclusions

A computational study has been done in this work to obtain the heat transfer, fluid flow and entropy generation for different parameters such as nanofluids, geometrical parameter and Ra numbers. An inserted body can be used to control heat transfer, fluid flow and energy efficiency inside the closed space. Thus, Bejan number becomes almost fixed for the highest value of Ra number and it decreases with increasing geometrical value, but it decreases for lower values of Ra numbers. In any case both heat transfer and entropy generation augment with addition of nanoparticle. The increase of geometrical parameter enhances the total entropy generation due to the enhancement of entropy generation with heat transfer. Circulation cells inside the enclosure are a function of the geometrical parameters of the inserted body.