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Research Papers: Natural and Mixed Convection

Lattice Boltzmann Simulation of Mixed Convection Heat Transfer in a Lid-Driven Square Cavity Filled With Nanofluid: A Revisit

[+] Author and Article Information
Özgür Ekici

Department of Mechanical Engineering,
Hacettepe University,
Ankara 06800, Turkey

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received December 5, 2016; final manuscript received February 14, 2018; published online March 23, 2018. Editor: Portonovo S. Ayyaswamy.

J. Heat Transfer 140(7), 072501 (Mar 23, 2018) (9 pages) Paper No: HT-16-1785; doi: 10.1115/1.4039490 History: Received December 05, 2016; Revised February 14, 2018

Mixed convection heat transfer of Al2O3 nanofluid in a lid-driven square cavity with differentially heated vertical walls is studied numerically with lattice Boltzmann method (LBM). In order to understand the reasons for the conflicting results on heat transfer enhancement in cavity problems, formulation of nondimensional properties and modeling thermophysical properties, in accordance with the relative effects of natural and forced convection flows, are examined. In addition to gain more insight into the physics, one of the goals of the study is to identify the reasons of existing contradictory findings; therefore, a single-phase formulation is adopted as has been the case in the majority of related literature to date. To isolate the effects of thermophysical properties on the results and to maintain the same natural and forced convection effects, all nondimensional parameters are defined using the corresponding thermophysical properties of the fluid under examination. Two different effective thermal conductivity and viscosity models are tested for a range of Reynolds and Rayleigh numbers to investigate their effects on the nanofluid behavior. Depending on the effective viscosity model, an increase or decrease is obtained in the average Nusselt number. It is also illustrated that the relative magnitudes of effective thermal conductivity values for different models do not translate into the heat transfer enhancement due to convective effects. Moreover, it is shown that thermal behavior of nanofluid approaches to the one of base fluid's as the buoyancy driven flow gets stronger, which is independent of the employed effective property models.

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Figures

Grahic Jump Location
Fig. 1

Problem geometry and the boundary conditions

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Fig. 6

Temperature profiles at three different heights along horizontal axis, for water and Al2O3 nanofluid (Ø = 5%) at various Rayleigh and Reynolds numbers using cond-II for all: (a) Re = 10, Ra = 102, (b) Re = 100, Ra = 102, and (c) Re = 100, Ra = 106

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Fig. 2

Isothermal lid-driven cavity, Re = 100, horizontal (u) and vertical (v) components of velocity through middle vertical and horizontal axes, respectively

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Fig. 3

Streamlines for water (______, Ø = 0%) and Al2O3 nanofluid (········, Ø = 5%) at various Rayleigh and Reynolds numbers using cond-II for all, vis-I (left) and vis-II (right): (a) Re = 10, Ra = 102, (b) Re = 100, Ra = 102, and (c) Re = 100, Ra = 106

Grahic Jump Location
Fig. 4

Horizontal (u) and vertical (v) components of velocity along middle vertical and horizontal axes, respectively, for water and Al2O3 nanofluid (Ø = 5%) at various Rayleigh and Reynolds numbers using cond-II for all: (a) Re = 10, Ra = 102, (b) Re = 100, Ra = 102, and (c) Re = 100, Ra = 106

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Fig. 5

Isotherms for water (______, Ø = 0%) and Al2O3 nanofluid (········, Ø = 5%) at various Rayleigh and Reynolds numbers using cond-II for all, vis-I (left) and vis-II (right): (a) Re = 10, Ra = 102, (b) Re = 100, Ra = 102, and (c) Re = 100, Ra = 106

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Fig. 7

Comparison of: (a) the average Nusselt number for water and Al2O3 nanofluid (Ø = 5%) and (b) percentage difference in the average Nusselt number for thermal conductivity models, cond-I and cond-II; all with the effective viscosity model, vis-I

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Fig. 8

Comparison of: (a) the average Nusselt number for water and Al2O3 nanofluid (Ø = 5%) and (b) percentage difference in the average Nusselt number for thermal conductivity models, cond-I and cond-II; all with the effective viscosity model, vis-II

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Fig. 9

The average Nusselt number for Al2O3 nanofluid (Ø = 5%) with two different viscosity models compared to that of water in percentage change

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Fig. 10

The average convective heat transfer coefficient for Al2O3 nanofluid (Ø = 5%) with two different viscosity models compared to that of water

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