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Numerical Study on Convective Heat Transfer Enhancement in Horizontal Rectangle Enclosures Filled with AgGa Nanofluid
Nanoscale Research Lettersvolume 12, Article number: 326 (2017)
Abstract
The natural convection heat transfer of horizontal rectangle enclosures with different aspect ratios (A = 2:1 and A = 4:1) filled with AgGa nanofluid (different nanoparticle volume fractions φ = 0.01, φ = 0.03, φ = 0.05 and radiuses r = 20 nm, r = 40 nm, r = 80 nm) at different Rayleigh numbers (Ra = 1 × 10^{3} and Ra = 1 × 10^{5}) is investigated by a twophase lattice Boltzmann model. It is found that the Nusselt number enhancement ratios of two enclosures (A = 2:1 and A = 4:1) filled with AgGa nanofluid (r = 20 nm) are the same compared with those of the water at the corresponding aspect ratio enclosure. The more flat horizontal rectangular enclosure (A = 4:1) has the higher Nusselt number than the less flat horizontal rectangular enclosure (A = 2:1). It is also found that Nusselt number increases with the decreasing nanoparticle radius. Nusselt number enhancement ratios for every nanoparticle radius reducing by half at high Rayleigh number are higher than those at low Rayleigh number in most cases. The interaction forces between particles are also investigated in this paper. It is found that the Brownian force F _{B} is about two magnitudes greater than that of drag force F _{D}, and the value of driving force F _{S} in A = 4:1 enclosure is about twice the value of driving force F _{S} in A = 2:1 enclosure while other forces are almost the same.
Background
Heat transfer enhancement attracts more and more people’s attention. One method is to improve the structure of the heat exchanger, and another method is to find new fluid with higher heat transfer performance instead of the common fluid. People have studied the structures of the heat exchangers for many years. About the heat transfer medium, since the nanofluid with high thermal conductivity is prepared, the thermal properties [1,2,3] and heat transfer performance [4,5,6,7,8,9] of nanofluid are studied by more and more researchers.
Natural convection heat transfer is an important heat transfer process. The natural convection heat transfer characteristics of nanofluid have been widely investigated by experimental and numerical methods respectively.
Natural convection heat transfer characteristics of nanofluid are experimentally investigated by many researchers. Ho et al. [10] experimentally investigated the natural convection heat transfer of Al_{2}O_{3}water nanofluid in different size enclosures respectively, and the effects of nanoparticle volume fraction and Rayleigh number on the natural convection heat transfer of nanofluid are discussed. Heris et al. [11,12,13] experimentally investigated the laminar flow convective heat transfer of CuOwater, Al_{2}O_{3}water, and Cuwater nanofluid in a circular tube respectively. Hu et al. [14] experimentally investigated the natural convection heat transfer of TiO_{2}water nanofluid with different nanoparticle mass fractions, and the effects of Rayleigh number on natural convection heat transfer are discussed. Sommers et al. [15] experimentally investigated the convection heat transfer of Al_{2}O_{3}propanol nanofluid through a copper pipe, and the effects of heat rate on the convection heat transfer are discussed.
In addition to the experimental method, numerical simulation is also an important method to study the natural convection heat transfer of nanofluid. Many researchers have investigated the natural convection heat transfer of nanofluid by various numerical methods. He et al. [16] investigated the convection heat transfer of TiO_{2}water nanofluid flowing through a straight tube by a singlephase method and a combined Euler and Lagrange method respectively. The effects of nanoparticle fraction, Reynolds number, and nanoparticle aggregated size on the convection heat transfer are discussed. Bianco et al. [17,18,19] investigated the convection flow of a circular tube filled with Al_{2}O_{3}water nanofluid under different conditions respectively. Akbarinia et al. [20,21,22] investigated the mixed convection of Al_{2}O_{3}water nanofluid in a horizontal curved tube, annulus and elliptic ducts respectively. Sheikholeslami et al. [23,24,25,26,27] investigated the natural convection heat transfer of various kinds of nanofluid under magnetic field and revealed the heat transfer enhancement mechanism of nanofluid. Qi et al. [28,29,30] investigated the natural convection heat transfer of Cu/Al_{2}O_{3}water, Al_{2}O_{3}water, and Cugallium in an enclosure by a lattice Boltzmann method respectively.
The above literatures made a great contribution to the researches on the effects of macrofactors (nanoparticle volume fraction, kinds of nanofluid, and so on) on the heat transfer of nanofluid. The effects of microfactors (nanoparticle radius) on the heat transfer of nanofluid are needed to be studied. Hence, in our previous published paper [31], the natural convection heat transfer of a vertical rectangle enclosure (the left and the right walls are hot and cold walls, respectively, and other walls are adiabatic) filled with CuGa nanofluid with various radius nanoparticles is investigated. In order to reveal the effects of different laying forms of the rectangle enclosure and different boundary conditions in the natural convection heat transfer of nanofluid with different nanoparticle radiuses, the natural convection of a horizontal rectangle enclosure (the left and right walls are all hot walls, and other walls are all cold walls) filled with AgGa nanofluid with various radius nanoparticles is investigated in this paper.
Methods
The natural convection of the horizontal rectangle enclosure filled with AgGa nanofluid with various radiuses of nanoparticles is simulated by a twophase lattice Boltzmann model. The twophase lattice Boltzmann model for nanofluid has been developed by us in the previous published paper [31]. The main basic equations of the twophase lattice Boltzmann model are given as follows:
The evolution equations and equilibrium distribution functions for velocity and temperature fields are given respectively as follows:
The interaction forces including gravity and buoyancy force F _{H}, drag force F _{D}, interaction potential force F _{A}, and Brownian force F _{B} are presented respectively as follows:
All units in the simulation adopt the lattice units. The transformation relationships between lattice units and international units are as follows:
where the physical quantities with the superscript “^{'}” represent the lattice units and the physical quantities without the superscript “^{'}” represent the international units.
The other details of this model can be seen in the previous published paper [31].
Results and Discussion
Figure 1 presents the horizontal rectangular enclosure filled with AgGa nanofluid in the simulation. The aspect ratio between width and height is defined as A = W/H. The thermophysical parameters of liquid metal gallium (Ga) and silver (Ag) nanoparticles are given in Table 1. Because the temperature change has a great effect on the specific heat of Ga while a mall effect on the specific heat of Ag, in order to simplify the calculation, the specific heat of Ga considers the effect of temperature, and the specific heat of Ag keeps a constant. The left and right walls of the horizontal rectangular enclosure are all hot wall T _{H}, and the top and bottom walls are all cold wall T _{C}. The initialization conditions of the four walls are shown as follows:
Before the study in AgGa nanofluid, a grid independence test is analyzed. Five kinds of grids (78 × 39, 128 × 64, 198 × 99, 256 × 128, and 300 × 150) are chosen to be tested in this paper. The results under different grids are showed in Table 2. It can be seen from Table 2 that there are noticeable differences in the results from 78 × 39 to 256 × 128 but few differences from 256 × 128 to 300 × 150. In order to accelerate the numerical simulation velocity, the grid 256 × 128 is adopted for A = 2:1 enclosure in this numerical simulation. Correspondingly, the grid 256 × 64 is adopted for A = 4:1 enclosure.
The reliability and accuracy of the twophase lattice Boltzmann model have been verified in the previous published paper [31].
Figure 2 shows the temperature nephogram and streamlines of AgGa nanofluid (r = 20 nm, φ = 0.01) in the horizontal rectangular enclosure (A = 2:1 and A = 4:1) at different Rayleigh numbers (Ra = 1 × 10^{3} and Ra = 1 × 10^{5}) respectively. It can be seen that the isotherm becomes more and more crooked with the Rayleigh number. The number of vortexes in the enclosure increases with the Rayleigh number. The vortexes can disturb the laminar boundary layer and enhance the heat transfer. The main heat transfer form is heat conduction at low Rayleigh number Ra = 1 × 10^{3}, while the main heat transfer form changes from heat conduction to convection heat transfer at high Rayleigh number Ra = 1 × 10^{5}. High Rayleigh number causes a big temperature difference driving force which disturbs the laminar boundary layer and improves the heat transfer compared with the low Rayleigh number.
Figure 3 presents the nanoparticle volume fraction distributions of AgGa nanofluid (r = 20 nm, φ = 0.01) in the horizontal rectangular enclosure at different Rayleigh numbers (Ra = 1 × 10^{3} and Ra = 1 × 10^{5}) respectively. It can be seen from Fig. 3 that the high nanoparticle volume fraction mainly distributes in the left and right sides (the center of the vortexes) of the enclosure. The velocity in the center of the vortex is smaller than that outside of vortexes. Due to the smaller velocity of nanoparticles compared with water, the nanoparticles mainly fall into the center of the two big vortexes in the left and right sides of the enclosure.
There are driving force F _{S} and interaction forces between particles including gravity and buoyancy force F _{H}, drag force (Stokes force) F _{D}, interaction potential force F _{A}, and Brownian force F _{B} for nanofluid. For Ra = 10^{5} and φ = 0.01, the ranges of interaction forces between particles in enclosure with A = 2:1 and A = 4:1 are given in Tables 3 and 4 respectively. It can be seen from these two tables that the driving force F _{S} is the biggest force, and among the interaction forces between particles, Brownian force F _{B} is the biggest force, followed by the drag force F _{D}. It can be also seen that Brownian force F _{B} is about two magnitudes greater than drag force F _{D}, which is another reason for the enhancement of nanofluid in addition to the high thermal conductivity of nanofluid. In addition, it can be obtained a conclusion that the values of the driving force F _{S} in enclosure (A = 4:1) are about twice the values of F _{S} in enclosure (A = 2:1) while those of the other forces are almost the same, which causes a higher heat transfer enhancement ratio in enclosure with A = 4:1 compared with that in enclosure with A = 2:1.
Figure 4 shows the biggest advantageous force F _{S} and the biggest disadvantageous force F _{D} distributions at high Rayleigh number Ra = 1 × 10^{5} (A = 2:1, r = 20 nm). It can be seen that the driving force F _{S} distribution is similar to the temperature distribution. This is because the driving force F _{S} is the biggest force and plays a main role in the temperature distribution. The drag force F _{D} mainly surrounds the border of the vortex in the enclosure. This is because the velocity of nanofluid and the corresponding velocity difference between nanoparticle and gallium surrounding the border of the vortex are all bigger than that in other places.
Take the nanoparticle radius r = 20 nm and the aspect ratio of enclosure A = 2:1, for example, Figs. 5 and 6 give the Nusselt number distributions and average Nusselt numbers of AgGa nanofluid with different nanoparticle volume fractions along with the left hot wall at different Rayleigh numbers respectively. It can be seen from Fig. 5 that Nusselt number increases with the nanoparticle volume fraction. High nanoparticle volume fraction can enhance the whole thermal conductivity of nanofluid and improve the natural convection heat transfer. It can be also seen from Fig. 5 that the Nusselt number firstly decreases with Y and then increases with Y, and there is only one Nusselt number valley at low Rayleigh number. However, there are two Nusselt number valleys at high Rayleigh number. At low Rayleigh number, there are no obvious vortexes between the two big vortexes (Fig. 2c), and the velocity in the place between the two big vortexes is small, which causes small Nusselt numbers. At high Rayleigh number, there are two small vortexes between the two big vortexes (Fig. 2d), which disturb the laminar boundary layer and enhance the Nusselt number. Hence, there are two Nusselt number valleys at high Rayleigh number, while there is only one Nusselt number valley at low Rayleigh number, and it shows a more fluctuation in the Nusselt number distributions along with the left hot wall in Fig. 5b compared with that in Fig. 5a. It can be seen from Fig. 6 that Nusselt number increases with the decrease of the nanoparticle radius. For A = 2:1, AgGa nanofluid with the smallest nanoparticle radius (r = 20 nm) can enhance the heat transfer by 3.1 and 2.1% compared with water at Ra = 10^{3} and Ra = 10^{5} respectively.
The similar conclusions can be obtained from Figs. 7 and 8 compared with Figs. 5 and 6. For A = 4:1, AgGa nanofluid with the smallest nanoparticle radius (r = 20 nm) can enhance the heat transfer by 3.1 and 2.1% compared with water at Ra = 10^{3} and Ra = 10^{5} respectively. The enhancement ratios of the two enclosures (A = 4:1 and A = 2:1) filled with AgGa nanofluid (r = 20 nm) are the same.
Figure 9 shows the average Nusselt numbers of AgGa nanofluid with different nanoparticle radiuses along with the left hot wall. Based on these data in Fig. 9, a mathematic correlation between average Nusselt number and nanoparticle volume fraction is given in Eq. (11). The simulation results and the results in Eq. (11) are all shown in Fig. 9. They have a good agreement with each other. It is found that the more flat horizontal rectangular enclosure (aspect ratio A = 4:1) has the higher Nusselt number than the less flat horizontal rectangular enclosure (aspect ratio A = 2:1). For every nanoparticle volume fraction, Nusselt numbers of AgGa nanofluid with the smallest nanoparticle radius (r = 20 nm) in enclosure (A = 4:1) are all 1.5% higher than that in enclosure (A = 2:1) at low Rayleigh number Ra = 10^{3}. Nusselt numbers of nanofluid (r = 20 nm) in enclosure (A = 4:1) are 1.6, 1.1, and 1.0% higher than that in enclosure (A = 2:1) for φ = 5%, φ = 3%, and φ = 1% at high Rayleigh number Ra = 10^{5} respectively. Big aspect ratio of the horizontal rectangular enclosure in this paper is advantageous to the heat transfer enhancement.
where 0 ≤ φ ≤ 0.05 and the constants a, b, c, and d are all shown in the Table 5.
Table 6 shows the Nusselt number enhancement ratios for every nanoparticle radius reducing by half. It can be seen that Nusselt number enhancement ratios for every nanoparticle radius reducing by half are all about 0.3% for two enclosures (A = 2:1 and A = 4:1) at Ra = 10^{3}. This is because the heat conduction plays a major role in the heat transfer, and the Nusselt number enhancement ratios mainly depend on the heat transfer area increment at the same nanoparticle volume fraction. The heat transfer area increment for every nanoparticle radius reducing by half are almost the same, which causes the same Nusselt number enhancement ratios at Ra = 10^{3}. For Ra = 10^{5}, Nusselt number enhancement ratios from the nanoparticle radius r = 80 nm to r = 40 nm for nanofluid (φ = 0.1%) in enclosure (A = 2:1 and A = 4:1) are smaller than those in other conditions. At high Rayleigh number Ra = 10^{5}, the convection heat transfer plays a major role in the heat transfer, due to the low nanoparticle volume fraction (φ = 1%) and the small heat transfer area for r = 80 nm and r = 40 nm; the Nusselt number enhancement ratios are smaller compared with those of the others. Except above two conditions, the Nusselt number enhancement ratios at Ra = 10^{5} are all higher than those at Ra = 10^{3}. High Rayleigh number can enhance the disturbance and improve the heat transfer.
Conclusions
The natural convection heat transfer of AgGa nanofluid with different nanoparticle radiuses in horizontal rectangle enclosures with different aspect ratios is simulated based on a twophase lattice Boltzmann model. Some conclusions are obtained as follows:

1.
Nusselt number increases with the decrease of the nanoparticle radius. The Nusselt number enhancement ratios of two enclosures (A = 4:1 and A = 2:1) filled with AgGa nanofluid (r = 20 nm) are the same compared with those of the water at the corresponding enclosure. For both A = 4:1 and A = 2:1, AgGa nanofluid with the smallest nanoparticle radius (r = 20 nm) can enhance the heat transfer by 3.1 and 2.1% at best compared with water at Ra = 10^{3} and Ra = 10^{5} respectively.

2.
The more flat horizontal rectangular enclosure (A = 4:1) has the higher Nusselt number than the less flat horizontal rectangular enclosure (A = 2:1). Nusselt numbers of AgGa nanofluid (r = 20 nm) in the enclosure (A = 4:1) are all 1.5% higher than those in enclosure (A = 2:1) for every nanoparticle volume fraction at Ra = 10^{3}. For Ra = 10^{5}, Nusselt numbers of the enclosure (A = 4:1) are 1.0, 1.1, and 1.6% higher than those in enclosure (A = 2:1) for φ = 1%, φ = 3%, and φ = 5% respectively.

3.
Nusselt number enhancement ratios for every nanoparticle radius reducing by half at high Rayleigh number are higher than those at low Rayleigh number in most cases. For the two enclosures (A = 2:1 and A = 4:1), Nusselt number enhancement ratios for every nanoparticle radius reducing by half are all about 0.3% at Ra = 10^{3}, and most of them are 0.35 to 1.0% at Ra = 10^{5}.

4.
The Brownian force F _{B} is about two magnitudes greater than the drag force F _{ D }. The value of driving force F _{S} in A = 4:1 enclosure is about twice the value of driving force F _{S} in A = 2:1 enclosure while other forces are almost the same.
References
 1.
Li H, Wang L, He Y, Hu Y, Zhu J, Jiang B (2015) Experimental investigation of thermal conductivity and viscosity of ethylene glycol based ZnO nanofluids. Appl Therm Eng 88:363–368
 2.
Chen M, He Y, Zhu J, Shuai Y, Jiang B, Huang Y (2015) An experimental investigation on sunlight absorption characteristics of silver nanofluids. Sol Energy 115:85–94
 3.
Yang JC, Li FC, Zhou WW, He Y, Jiang B (2012) Experimental investigation on the thermal conductivity and shear viscosity of viscoelasticfluidbased nanofluids. Int J Heat Mass Transfer 55(11):3160–3166
 4.
Yang JC, Li FC, He YR, Huang YM, Jiang BC (2013) Experimental study on the characteristics of heat transfer and flow resistance in turbulent pipe flows of viscoelasticfluidbased Cu nanofluid. Int J Heat Mass Transfer 62:303–313
 5.
Yang JC, Li FC, Cai WH, Zhang HN, Yu B (2014) On the mechanism of convective heat transfer enhancement in a turbulent flow of nanofluid investigated by DNS and analyses of POD and FSP. Int J Heat Mass Transfer 78:277–288
 6.
Li H, He Y, Hu Y, Jiang B, Huang Y (2015) Thermophysical and natural convection characteristics of ethylene glycol and water mixture based ZnO nanofluids. Int J Heat Mass Transfer 91:385–389
 7.
He Y, Li H, Hu Y, Hu Y, Wang X, Zhu J (2016) Boiling heat transfer characteristics of ethylene glycol and water mixture based ZnO nanofluids in a cylindrical vessel. Int J Heat Mass Transfer 98:611–615
 8.
Ho CJ, Chang CY, Cheng CY, Cheng SJ, Guo YW, Hsu ST, Yan WM (2016) Laminar forced convection effectiveness of Al_{2}O_{3}–water nanofluid flow in a circular tube at various operation temperatures: effects of temperaturedependent properties. Int J Heat Mass Transfer 100:464–481
 9.
He Y, Qi C, Hu Y, Qin B, Ding Y (2011) Lattice Boltzmann simulation of aluminawater nanofluid in a square cavity. Nanoscale Res Lett 6(1):184–191
 10.
Ho CJ, Liu WK, Chang YS, Lin CC (2010) Natural convection heat transfer of aluminawater nanofluid in vertical square enclosures: an experimental study. Int J Therm Sci 49(8):1345–1353
 11.
Heris SZ, Etemad SG, Esfahany MN (2006) Experimental investigation of oxide nanofluids laminar flow convective heat transfer. Int Commun Heat Mass Transfer 33(4):529–535
 12.
Heris SZ, Esfahany MN, Etemad SG (2007) Experimental investigation of convective heat transfer of Al_{2}O_{3}/water nanofluid in circular tube. Int J Heat Fluid Flow 28(2):203–210
 13.
Heris SZ, Etemad SG, Esfahany MN (2009) Convective heat transfer of a Cu/water nanofluid flowing through a circular tube. Exp heat transfer 22(4):217–227
 14.
Hu Y, He Y, Wang S, Wang Q, Schlaberg HI (2014) Experimental and numerical investigation on natural convection heat transfer of TiO_{2}–water nanofluids in a square enclosure. J Heat Transfer 136(2):022502
 15.
Sommers AD, Yerkes KL (2010) Experimental investigation into the convective heat transfer and systemlevel effects of Al_{2}O_{3}propanol nanofluid. J Nanopart Res 12(3):1003–1014
 16.
He Y, Men Y, Zhao Y, Lu H, Ding Y (2009) Numerical investigation into the convective heat transfer of TiO_{2} nanofluids flowing through a straight tube under the laminar flow conditions. Appl Therm Eng 29(10):1965–1972
 17.
Bianco V, Chiacchio F, Manca O, Nardini S (2009) Numerical investigation of nanofluids forced convection in circular tubes. Appl Therm Eng 29(17):3632–3642
 18.
Bianco V, Manca O, Nardini S (2011) Numerical investigation on nanofluids turbulent convection heat transfer inside a circular tube. Int J Therm Sci 50(3):341–349
 19.
Bianco V, Manca O, Nardini S (2014) Performance analysis of turbulent convection heat transfer of Al_{2}O_{3} waternanofluid in circular tubes at constant wall temperature. Energy 77:403–413
 20.
Akbarinia A, Behzadmehr A (2007) Numerical study of laminar mixed convection of a nanofluid in horizontal curved tubes. Appl Therm Eng 27(8):1327–1337
 21.
Moghari RM, Akbarinia A, Shariat M, Talebi F, Laur R (2011) Two phase mixed convection Al_{2}O_{3}–water nanofluid flow in an annulus. Int J Multiphase Flow 37(6):585–595
 22.
Shariat M, Akbarinia A, Nezhad AH, Behzadmehr A, Laur R (2011) Numerical study of two phase laminar mixed convection nanofluid in elliptic ducts. Appl Therm Eng 31(14):2348–2359
 23.
Sheikholeslami M, GorjiBandpy M, Vajravelu K (2015) Lattice Boltzmann simulation of magnetohydrodynamic natural convection heat transfer of Al_{2}O_{3}–water nanofluid in a horizontal cylindrical enclosure with an inner triangular cylinder. Int J Heat Mass Transfer 80:16–25
 24.
Sheikholeslami M, Ellahi R (2015) Three dimensional mesoscopic simulation of magnetic field effect on natural convection of nanofluid. Int J Heat Mass Transfer 89:799–808
 25.
Sheikholeslami M, Vajravelu K, Rashidi MM (2016) Forced convection heat transfer in a semi annulus under the influence of a variable magnetic field. Int J Heat Mass Transfer 92:339–348
 26.
Sheikholeslami M, Chamkha AJ (2016) Flow and convective heat transfer of a ferronanofluid in a doublesided liddriven cavity with a wavy wall in the presence of a variable magnetic field. Numer Heat Transfer, Part A: Appl 69(10):1186–1200
 27.
Sheikholeslami M, Rashidi MM (2015) Ferrofluid heat transfer treatment in the presence of variable magnetic field. Eur Phys J Plus 130(6):1–12
 28.
Qi C, He G, Li Y, He Y (2015) Numerical simulation of natural convection of square enclosure filled with Cu/Al_{2}O_{3}–water mixed nanofluid based on lattice Boltzmann method. Acta Phys Sin 64(2):024703 (in Chinease)
 29.
Qi C, He Y, Yan S, Tian F, Hu Y (2013) Numerical simulation of natural convection in a square enclosure filled with nanofluid using the twophase lattice Boltzmann method. Nanoscale Res Lett 8(1):1–16
 30.
Qi C, He Y, Hu Y, Yang J, Li F, Ding Y (2011) Natural convection of Cugallium nanofluid in enclosures. J Heat Transfer 133(12):122504
 31.
Qi C, Liang L, Rao Z (2016) Study on the flow and heat transfer of liquid metal based nanofluid with different nanoparticle radiuses using twophase lattice Boltzmann method. Int J Heat Mass Transfer 94:316–326
 32.
Vajravelu K, Prasad KV, Lee J, Lee C, Pop I, Gorder RAV (2011) Convective heat transfer in the flow of viscous Ag–water and Cu–water nanofluids over a stretching surface. Int J Therm Sci 50(5):843–851
Acknowledgements
This work is financially supported by the “National Natural Science Foundation of China” (Grant No. 51606214) and “the Fundamental Research Funds for the Central Universities” (Grant No. 2015XKMS063).
Authors’ Contributions
CQ participated in the design of the program, carried out the numerical simulation of the nanofluid, and drafted the manuscript. LYY and GQW participated in the design of the program. All authors read and approved the final manuscript.
Competing Interests
The authors declare that they have no competing interests.
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Keywords
 Nanofluid
 Natural convection
 Heat transfer enhancement
 Twophase lattice Boltzmann method