Research Article | Open Access
Said Bouchta, M’barek Feddaoui, Abdellatif Dayf, "Numerical Simulation of Free Convection in a Partially Heated Three-Dimensional Enclosure Filled with Ionanofluid ([C4mim][NTf2]-Cu)", Mathematical Problems in Engineering, vol. 2021, Article ID 6696119, 11 pages, 2021. https://doi.org/10.1155/2021/6696119
Numerical Simulation of Free Convection in a Partially Heated Three-Dimensional Enclosure Filled with Ionanofluid ([C4mim][NTf2]-Cu)
A numerical analysis was performed to study free convection in a stationary laminar regime in a partially heated cube filled with ionanofluid. To numerically solve the dimensionless equations, we applied the finite volume method using the SIMPLEC algorithm for pressure correction. All walls are adiabatic, except for the left and right side walls which are partially heated differently. At the end of this simulation, several results are given in the form of current lines, isotherms, and variations in the Nusselt number. These results are obtained by analyzing the effect of a set of factors such as Rayleigh number, particle volume fraction, cold and source position on the dynamic and thermal fields, and heat transfer. It has been shown that the percentage of nanoparticles and high Rayleigh numbers significantly increase heat transfer by ionanofluid. Two comparisons have been made, between ionic fluid and ionanofluid at isotherms and streamlines, and between nanofluid and ionanofluid at Nusselt number, which show the advantage of using ionanofluid in heat transfer.
The low thermal conductivity of conventional fluids used in free convection has led physicists to replace them with another, that is, with a high thermal conductivity called nanofluid. This new fluid invented by Choi and Eastman  is a colloidal solution composed of nanoparticles suspended in a base fluid. A summary was prepared by Yu and Xie  on the progress of the study of nanofluids, such as preparation methods, methods of assessing the stability of nanofluids, and ways to improve the stability of nanofluids, the stability mechanisms of nanofluids, and their current and future applications in various fields. Nanofluids have shown great progress in convection  in various applications such as heat exchangers, automotive parts, and cooling of electronic and electrical components.
Several works have been published on nanofluids. Putra et al.  conducted an experiment to analyze the behavior of water-Al2O3 and water-CuO nanofluids in a horizontal cylinder subjected to constant temperatures. Mohebbi et al.  studied the natural convection of a nanofluid. They analyzed the effect of the existence of a heat source and its location on the flow rate of a C-shaped enclosure. Mehryan et al.  numerically analyzed the free convection inside porous enclosures filled with water/Ag-MgO nanofluids with Darcy and LTNE conditions. The results indicate that the dissipation of MgO-Ag in the base fluid significantly reduces heat transfer. They found that increasing the concentration of the nanoparticles significantly improves the heat transfer for the nanofluid CuO-water. Khanafer et al.  have numerically processed nanofluids in free convection. Their findings show that at any Grashof number, the added nanoparticles remarkably increase the rate of heat transfer.
Other studies [8–13] have shown the effect of increasing the concentration of nanoparticles on improving heat transfer. A number of researchers studied magnetohydrodynamics (MHD). Mansour et al.  performed a numerical study of the natural convection of the nanofluid MHD in a square cavity under thermal boundary conditions. Ahmed et al.  digitally studied two heating systems inside triangular chambers filled with nanofluid under the Lorentz force. They showed that the thermal transfer improves with the increase in the height of the fins and also improves with the increase in the percentage of nanoparticles and the parameter heat production/absorption while the presence of magnetic force slows the movement of fluids and decreases the rate of heat transfer.
Alsabery et al.  studied free convection in a cavity with elastic walls; it was observed that the elastic walls affect the fluid flow and heat transfer characteristics. In the presence of a uniform magnetic field, a numerical study was carried out by Selimefendigil and Öztop  of the laminar flow of nanofluid on a corrugated plate. They showed that the pulsed flow improves the heat transfer rate compared to the case of a constant flow. Selimefendigil and Öztop proposed the use of nanofluid jets for cooling an isothermal surface under the influence of a rotating cylinder , which affects the fluid flow and heat transfer characteristics. The same researchers  used the same technique for cooling an isothermal surface in a partially porous medium under the impact of an inclined magnetic field. They observed that the characteristics of the magnetic field and the porous medium have significant impacts on the variation of the flux and thermal patterns for the thermal configuration.
The free convection of nanofluids in 3D cavities has been addressed by few researchers. Ravnik et al.  have analyzed the free convection of nanofluids in a cube with the boundary element method (BEM). Zhou et al. , using the Boltzmann method, have created a 3D model to analyze the heat transfer and flow dynamics of the mixed convection of the nanofluid water-Al2O3 in a cube in the existence of a magnetic field. Different parameters were considered in this study of nanofluid flow and heat transfer, such as Rayleigh, Hartmann, and Richardson numbers and volume fraction of nanoparticles. The conclusions show that a low Ra and the addition of particles to water can improve the heat transfer effect. However, at high Rayleigh numbers, this improvement in heat transfer may be weakened or even reversed. In addition, the findings show that the external magnetic field applied has the effect of removing the convection state of heat transfer within the enclosure.
El Moutaouakil et al.  studied the influence of thermal radiation on free convection of various nanofluids in a partially heated cubic cavitation. They studied the impact on the dynamic and thermal fields and also the heat transfer of several parameters, the volume fraction, the radiation components, the aspect ratio of the heated elements, and the angle of inclination of these elements (0°, 45°, and 90°). Selimefendigil and Öztop  treated convective heat transfer in a 3D enclosure separated by a conductive partition and having an internal rotating adiabatic circular cylinder. The cavity is filled with nanofluid (carbon/water nanotubes). They analyzed the impact on the heat transfer of various parameters, Richardson number, the angular rotation velocity of the inner cylinder, the thickness, and the solid fraction φ. Atashafrooz  studied numerically in 3D the circulation of nanofluid in an inclined step. He showed that the nanoparticle volume fraction acts more on the temperature distribution than on the velocity distribution and increases the coefficient of friction, temperature, and Nusselt number.
A three-dimensional simulation of the mesoscopic scale of natural magnetohydrodynamic convection using the Lattice Boltzmann method has been examined by Sajjadi et al. . The findings show that increasing the Hartmann number considerably weakens the heat transfer. In addition, the influence of the Ha increases with the improvement of the Grashof number, such as the reduction of the average number of Nusselt. Bouchta and Feddaoui  have also studied the effect of the presence of a magnetic field on the flow and heat transfer of a nanofluid in a three-dimensional cavity. Different parameters were considered in this study such as Rayleigh and Hartmann numbers and the volume fraction of nanoparticles. The findings show that the applied magnetic field has the influence to make the convection state of heat transfer in the cavity disappear. Al-Sayegh  has numerically analyzed the free convection of a carbon nanotube (CNT) nanofluid within an open trapezoidal enclosure under the action of an inclination of the outside magnetic field by the finite volume method. The analysis took into account several factors, noting the Rayleigh and Hartmann numbers, the solid fraction, and the angle of inclination of the magnetic force. It has been found that, for high values of Ra, the heat transfer rate decreases when the Hartmann number is increased, while this heat transfer rate improves with increasing volume fraction of the nanoparticles regardless of the angle of inclination of the magnetic field.
A numerical investigation of the free convection of CNT nanofluids based on finite volumes is carried by Al-Rashed et al. ; they analyzed the influence of adequate factors, such as the Rayleigh number, the nanoparticles volume fraction, angle of inclination of the outer magnetic field, and the Hartmann number. They show that heat transfer improves with the addition of particles (CNT) and Rayleigh number. When Ha goes from 50 to 100, magnetic repulsion inhibits heat transfer by 50%.
A new class of heat transfer fluids proposed by Ribeiro et al.  called ionanofluid, which is today a hot research topic, has its fascinating thermophysical properties proven by several papers [30–33].
According to the literature review, the use of nanofluids and their derivatives to improve free convection heat transfer performance is an important and interesting topic. To my knowledge, there are few studies on the numerical investigation of the impact of ionanofluid on heat transfer performance. The objective of this work is to study the flow of an ionanofluid (Cu/ionic fluid) through a cube, as well as to quantify the convective exchanges. The effects of ionanofluid and Rayleigh number as well as the influence of the concentration of nanoparticles on the thermal performance of the cavity are analyzed in this study.
2. Mathematical Modeling
The study geometry (Figure 1) is a three-dimensional enclosure that is full of an ionic liquid and copper nanoparticles. The side walls are partially heated according to the four cases illustrated in Figure 1 (Th > Tc). The other walls are assumed adiabatic.
All thermophysical properties (at 300 K) listed in Table 1 are considered constant.
For the modeling of the physical problem described in Figure 1, we will adopt the following simplifying hypotheses: the flow is laminar, and the fluid is incompressible and Newtonian, apart from the density that evolves according to the Boussinesq approximation of Bejan .
Our system of equations, in steady state, of conservation of mass and conservation of momentum and energy that governs the configuration studied in its dimensionless form is given by 
The dimensionless parameters of the previous equations are
Table 2 shows the thermophysical properties of ionanofluid ([C4mim][NTf2]-Cu).
The calculation of the average Nusselt number is based on the following relation:
3. Grid Dependency
This numerical simulation was tested for the independence of the uniform mesh on the cubic enclosure for the bottom-bottom case with two Rayleigh values (Ra = 105, 106) and φ = 0.05. The well-known Richardson extrapolation technique was used [38–40]. The relation is given by , where the ratio of the spacing between the coarse and fine grid is represented by r = 1.5 and the accuracy of the extrapolation by = 2.
The evolution of the mean Nusselt number with the refinement of the grid for Rayleigh values Ra = 105 and Ra = 106 has been given in Table 3. The “percentage numerical error” for the two average Nusselt numbers is also given in Table 3. The results are seen to be in good agreement between grid sizes 603 and 903. In addition, the percentage error decreases as the grid size increases. Therefore, grid size 603 was chosen in this work for good accuracy and computing time.
4. Numerical Method
We use the finite volume method to discretize the equations of the mathematical model. The obtained equations are solved by the usual iterative method TDMA . The iterative process takes into account the pressure correction by implementing the SIMPLEC algorithm  and reaches convergence when the variation of the dependent variables (U, V, W, P, or θ) is no longer significant. A test for stopping the iterative process at convergence is established at each stretch according to the following criterion:where is one of the field variables (U, V, W, T, and P) and i, j, and k are the grid positions. n represents the time step number.
To verify the numerical program, the results obtained are confronted with the results already available in the literature. The first comparison is a three-dimensional numerical simulation of free convection of air and water (Pr = 0.71) at Rayleigh number values varying from 103 to 106. Table 4 shows comparisons between our results and those of the literature. After consultation, we see that our numerical results are fully consistent with those of the reference.
The second test is still free convection in a three-dimensional cavity but with a Cu-water nanofluid. Our results are compared with those of Ravnik et al. . Figure 2 shows that there is a very clear agreement between the average number of Nusselt obtained by this simulation and that obtained by Ravnik et al. .
A numerical analysis was realized using a finite volume method to analyze the heat transfer by free convection and fluid flow in a cubic cavity, using [C4mim][NTf2]-Cu ionanofluid. The isotherms, streamlines, and variation of the average Nusselt number are shown for the four study cases and with different values of Ra (103 to 106), and φ (0 to 0.05).
Figure 3 illustrates the 3D distribution of the temperature in the cube for two Rayleigh numbers 103 and 106. The fluid moves from the hot wall to the cold wall so that the rate of heat transfer is continuously maintained in the cube. At Ra = 106, the thermal field is marked by strong gradients on the active parts, which means that the heat transfer is large by convection.
In order to have a better view of the temperature profile within the cube, and for reasons of symmetry, the plane Y = 0.5 was considered as the study plane to represent the isotherms and current lines (Figures 4 and 5 ) with Ra = 103 and 106 for the cases of an ionic and ionanofluid liquid of φ = 5%.
Figures 4 and 5 illustrate the structures of the isotherms and streamlines for the four case studies with Ra = 103 and 106. Figures are given for ionic fluid (φ = 0) and ionanofluid (φ = 0.05). It is noted that for low Rayleigh numbers Ra = 103, where viscous forces are more dominant than buoyancy forces and diffusion is the main mode of heat transfer, cells are formed occupying the entire cavity with the nucleus located in the center and rotating clockwise. It should also be noted that for a lower Rayleigh number, the current lines of the ionic liquid and the ionanofluid are almost identical. The temperature field is vertically stratified, and the thermal gradients are low near the active parts. As the Rayleigh number increases Ra = 106, the intensity of recirculation in the enclosure increases and the streamlines become distorted. The thermal boundary layers become thinner and the isotherms stratify horizontally in the cavity. It is concluded that with increasing Rayleigh number, the temperature gradients become more important near the heated part of the left wall, and the intensity of the ionanofluid flow ([C4mim] [NTf2]/Cu) becomes stronger compared to that of the pure fluid ([C4mim] [NTf2]).
Comparing the four case studies, it is clear that the ionic liquid and the ionanofluid behave in the same way regardless of the Rayleigh value.
Figure 6 shows the isosurfaces of ionanofluid ([C4mim] [NTf2]) in 3D with two Rayleigh numbers Ra = 103 and Ra = 106 and a volume fraction φ = 5%. We notice that the shape of the isosurfaces highlights the change of the heat transfer mode when the Rayleigh number increases. Indeed, for Ra = 103, the isosurfaces are almost vertical due to the dominance of the conduction mode in heat transfer. With increasing Rayleigh, the dominance of heat transfer shifts from conduction to convection. For Ra = 106, the isosurfaces are marked by an almost horizontal stratification within the cube. Figure 6 also shows that the increase in Rayleigh number naturally leads to an increase in the energy supplied to the system. The result is an increase in the convective effect and heat transfer that increases with Ra.
The evolution of the average Nusselt number of ionanofluid for the four cases as a function of the Rayleigh number (Ra from 103 to 106) and the volume fraction of nanoparticles (φ from 0 to 5%) is illustrated in Figure 7. We can observe that the average number of Nusselt increases as the number of Rayleigh increases. Similarly, the Nuavg increases with the increasing percentage of nanoparticles for all Rayleigh numbers. This is due to the increased conductivity of the ionanofluid [C4mim][NTf2]-Cu which increases the heat transfer through the active parts of the walls. According to Figure 7, we notice that the bottom-bottom case represents the best Nuavg values, which is the best heat transfer situation.
The variation in the number of local Nusselt along the warm part for the four case studies is shown in Figure 8, with φ = 5% and Ra = 105. For the top-top and top-bottom cases, the values of the local Nusselt number are higher at the beginning of the heating (near the warm part at the level of the left vertical wall) and lower at the top of the cavity. The figure shows again that the highest values of the local Nusselt number are relative to the top-top case.
For the bottom-top and bottom-bottom cases, the local Nusselt number values start to drop from the beginning of the heating and increase again to reach a maximum value in the middle of the cavity. The figure also shows that the highest values of the local Nusselt number are relative to the bottom-bottom case.
A comparison of the variation of the average Nusselt number as a function of the volume fraction of nanoparticles between ionanofluid ([C4mim][NTf2]-Cu) and nanofluid (water-Cu) is shown in Figure 9. The curves are given for the bottom-bottom configuration since this is the one that gives the best Nuavg values. It can be seen that the number of the mean Nusselt increases with the volume fraction φ and that heat transfer is favored for the ionanofluid over the nanofluid. This result is due to the increased conductivity of the ionanofluid compared to the nanofluid, which improves the heat transfer to the cavity.
The comparison of the variations in the number of local Nusselt along the warm part of the nanofluid and ionanofluid for the bottom-bottom case is shown in Figure 10, with φ = 5% and Ra = 105. The figure shows that the highest values of the local Nusselt number are relative to the ionanofluid, while the lowest values of the local Nusselt number are relative to the nanofluid.
In this work, the free convection of ionanofluid in a partially heated cubic enclosure is studied numerically. We compared the dynamic, thermal, and thermal fields of ionanofluid to those of the pure ionic liquid, and then we analyzed the effect of relevant factors such as Rayleigh number, volume fraction, and also the position of the hot and cold plate. And finally, we made a comparison of the heat transfer between the nanofluid and the ionanofluid in terms of the average Nusselt number.
Based on the results of this analysis, the following conclusions are drawn:(i)The addition of nanoparticles to the ionic fluid improves the thermal properties of the fluid(ii)The average Nusselt number increases as the volume fraction of nanomaterials increases(iii)The average Nusselt number increases with the increase in Rayleigh number(iv)Heat transfer is improved by the use of an ionanofluid compared to pure ionic fluid(v)The bottom-bottom case gives the highest Nusselt numbers compared to the other cases and subsequently the best heat transfer(vi)Heat transfer is improved by the use of ionanofluid compared to nanofluid
This work can be extended by further studies to better understand the phenomenon of natural convection in a cubic cavity filled with ionanofluid; for this, we suggest the following:(i)The influence of the shape and size of nanoparticles(ii)The effect of Brownian motion and thermophoresis(iii)Hydromagnetic study
|h:||Local heat transfer coefficient,|
|H:||Width of the enclosure, m|
|:||Nusselt number average|
|:||Nusselt number local|
|T:||Dimensional temperature, °C|
|u, , :||Dimensional velocity components,|
|U, V, W:||Dimensionless velocity components|
|x, y, z:||Dimensional coordinates, m|
|X, Y, Z:||Dimensionless coordinates|
|:||Thermal expansion coefficient,|
|φ:||Solid volume fraction|
The data used to support the findings of this study are included within the article.
Conflicts of Interest
The authors declare that they have no conflicts of interest.
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