Natural convection in a differentially heated square cavity with a horizontal partition plate on the hot wall

Nag, Arijit; Sarkar, A.; Sastri, V. M. K.

doi:10.1016/0045-7825(93)90025-s

Cited by 105 publications

(62 citation statements)

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“…Khashan (2006) have used this model for numerical simulation of thermal non-equilibrium natural convection in a porous cavity, heated from below. The study of natural convection heat transfer, in an enclosure filled with fluid due to attaching partitions and fins at the wall, has been carried out by several authors in the recent years (Shakerin et al 1988;Frederick 1989a;Frederick and Valenica 1989b;Nag et al 1993;Shi and Khodadahi 2003;Bilgen 2005). Shakerin et al (1988) have demonstrated natural convection in a differentially heated rectangular enclosure with discrete roughness elements on a vertical heated wall numerically and verified experimentally.…”

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confidence: 99%

Control of Flow and Heat Transfer in a Porous Enclosure due to an Adiabatic Thin fin on the Hot Wall

Sathiyamoorthy

Narasimman

2011

Transp Porous Med

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Natural convection flow in a differentially heated square enclosure filled with porous matrix with a solid adiabatic thin fin attached at the hot left wall is studied numerically. The Brinkman-Forchheimer-extended Darcy model is used to solve the momentum equations, in the porous medium. The numerical investigation is done through streamlines, isotherms, and heat transfer rates. A parametric study is carried out using the following parameters: Darcy number (Da) from 10 −4 to 10 −2 , dimensionless thin fin lengths (L p ) 0.3, 0.5, and 0.7, dimensionless positions (S p ) 0.25, 0.5, and 0.75 with Prandtl numbers (Pr) 0.7 and 100 for Ra = 10 6 . For Da = 10 −3 and Pr = 0.7, it is observed that there is a counter clock-wise secondary flow formation around the tip of the fin for S p = 0.5 for all lengths of L p . Moreover when Da = 10 −2 the secondary circulation behavior has been observed for S p = 0.25 and 0.75 and there is another circulation between the top wall and the fin that is separated from the primary circulation. However, these secondary circulations features are not observed for Pr = 100. It is also found that the average Nusselt number decreases as the length of the fin increases for all locations. However, the rate of decrease of average Nusselt number becomes slower as the location of fin moves from the bottom wall to the top wall. The overall heat transfer rate can be controlled with a suitable selection of the fin location and length.

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confidence: 99%

Control of Flow and Heat Transfer in a Porous Enclosure due to an Adiabatic Thin fin on the Hot Wall

Sathiyamoorthy

Narasimman

2011

Transp Porous Med

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“…This goal guides the design through choosing the relevant parameters appropriately. Winters [1] and Sathiyamoorthy and Chamkha [2], for example, considered a vertical divider in the middle of bottom wall; Faces [3] studied two fins on the hot, one on the cold wall in a tall cavity; Nag, et al [4], Shi and Khodadadi [5], and Bilgen [6] investigated a thin fin on the hot wall; and Nada [7] examined multiple fins on the hot wall of a narrow enclosure both horizontal and vertical.…”

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Effect of Fins on the Transition to Oscillating Laminar Natural Convection in an Enclosure

Selamet

2016

MATEC Web Conf.

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Abstract. Flow characteristics and evolution of heat transfer are investigated numerically within a differentially heated square cavity in the presence of thin fins which are either insulated or highly conductive and at the base wall temperature. The transition from steady-state to oscillatory and chaotic convection is observed at certain Rayleigh numbers with varying lengths of fins positioned at different locations.

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“…The hot left wall dimensionless temperature is set to one while the cold right wall dimensionless temperature is set to zero. Table 2 shows a comparison between the mean Nusselt number at the cold surface obtained by the current code and that obtained by De Vahl Davis and Jones, 24 De Vahl Davis, 25 and Nag et al 26 at Ra = 10 Also, Figure 4 shows a comparison of the current code results with the results obtained by Taamneh and Bataineh 27 for the case of a lid driven cavity in which nanofluid particles of Al 2 O 3 is dispersed inside the cavity, f = 0.01 and different Richardson numbers were considered. Where Ri = gb(T 1 -T 2 )L/V 2 .…”

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“…Figure 3 demonstrates that the solution is meshindependent for a grid of 100 3 100 nodes. This grid size is used for all simulations conducted in this research.To verify the numerical code, results of the current code are compared with the results obtained by De Vahl Davis and Jones, 24 De Vahl Davis, 25 and Nag et al 26 for the case of gaseous Boussinesq laminar steady-state air flow inside a square cavity with no fins attached to the hot wall and Pr = 0.71. Boundary conditions considered for this case are as follows: adiabatic upper and lower walls of the cavity.…”

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Numerical study of heat transfer enhancement in the entrance region for low-pressure gaseous laminar pipe flows using Al₂O₃–air nanofluid

Al‐Kouz

Al-Waked

Sari

et al. 2018

Advances in Mechanical Engineering

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The gaseous low-pressure nanofluid flow of a steady-state two-dimensional laminar forced convection heat transfer in the entrance region of pipes is numerically investigated. Such flows are of interest for many engineering applications like the nuclear reactor and electronic equipment cooling, heat exchangers, and many others. Physical parameters considered in this study are Reynolds number (Re), Prandtl number (Pr), nanosolid particles volume fraction (f), Knudsen number (Kn), and the aspect ratio (AR). These parameters ranges are as follows: 500 Re 2000, 0:76 Pr 0:95, 0 f 0:5, 0 Kn 0:1, and 1 AR 10. The outcome of this study shows that by increasing Kn, velocity slip and temperature jump at the solid boundaries increase. In addition, heat transfer is enhanced by dispersing Al 2 O 3 nanoparticles in the base low-pressure gaseous flow. Results show that there is no effect of the nanoparticles volume fraction with values below 0.03 on the average Nusselt number. The average Nusselt number increases (Nu) as the value of the nanoparticles volume fraction exceeds 0.03. For instance, at Re = 1000, results show that when dispersing Al 2 O 3 nanosolid particles with volume fractions of 0.3 and 0.5; there is an enhancement in the average Nusselt number of 30.35% and 136.74%, respectively, when compared to the case of dispersing Al 2 O 3 nanosolid particles of 0.03 volume fraction.. Moreover, it is concluded that the average Nusselt number (Nu) depends directly on Reynolds (Re), Prandtl (Pr) numbers, and the nanoparticles volume fraction (f) and inversely on Knudsen number (Kn) and the aspect ratio (AR) for the investigated range of parameters considered in this study. Finally, a correlation of Nusselt number among all the investigated parameters in this study is proposed as Nu = 0:976AR

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Natural convection in a differentially heated square cavity with a horizontal partition plate on the hot wall

Cited by 105 publications

References 13 publications

Control of Flow and Heat Transfer in a Porous Enclosure due to an Adiabatic Thin fin on the Hot Wall

Control of Flow and Heat Transfer in a Porous Enclosure due to an Adiabatic Thin fin on the Hot Wall

Effect of Fins on the Transition to Oscillating Laminar Natural Convection in an Enclosure

Numerical study of heat transfer enhancement in the entrance region for low-pressure gaseous laminar pipe flows using Al₂O₃–air nanofluid

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Natural convection in a differentially heated square cavity with a horizontal partition plate on the hot wall

Cited by 105 publications

References 13 publications

Control of Flow and Heat Transfer in a Porous Enclosure due to an Adiabatic Thin fin on the Hot Wall

Control of Flow and Heat Transfer in a Porous Enclosure due to an Adiabatic Thin fin on the Hot Wall

Effect of Fins on the Transition to Oscillating Laminar Natural Convection in an Enclosure

Numerical study of heat transfer enhancement in the entrance region for low-pressure gaseous laminar pipe flows using Al2O3–air nanofluid

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Numerical study of heat transfer enhancement in the entrance region for low-pressure gaseous laminar pipe flows using Al₂O₃–air nanofluid