Natural convection heat transfer from a bank of orthogonal heated plates embedded in a porous medium using LTNE model: A comparison between in-line and staggered arrangements

Basher, Noor Moneer; Yousif, Anwar Ahmed

doi:10.1016/j.ijthermalsci.2020.106692

Cited by 20 publications

(14 citation statements)

References 53 publications

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“…The condition of LTNE has been utilized to relate separately with solid and fluid phases and consequently, two conservation of energy are employed 50 . Darcy–Brinkman–Forchheimer model has been used to relate with fluid flow, where the impacts of inertia, viscous shear stress, boundary layer, pressure gradient and body force are implemented 44,56,57 . Boussinesq expression is considered to relate with density variation 14 .…”

Section: Modelmentioning

confidence: 99%

“…The findings confirmed that the considerations of non‐Darcy and LTNE have large impacts on Nusselt number. Then, Alomar et al 44 numerically compared the impacts of orthogonal heated surfaces arrangements on free convective inside porous duct under LTNE and non‐Darcy considerations. The findings confirmed showed that the in‐line arrangement produces better heat transfer than staggered arrangement.…”

Section: Introductionmentioning

confidence: 99%

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Conjugate local thermal nonequilibrium and non‐Darcy flow inside porous enclosure: Analysis of localized heating and cooling arrangements

Basher

Yousif

2023

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This study covers a simulation on conjugate free convective in a porous enclosure containing a side wall thickness and partially heated and cooled from sides under the considerations of local thermal nonequilibrium (LTNE) and non‐Darcy flow. Interest has been focused on how the side wall thickness and the locations of cooled and heated parts affect the effectiveness of the Nusselt number (Nu). Three different cases of localized heating and cooling locations have been implemented for the following ranges: scaled heat transfer coefficient (), wall to fluid thermal conductivity ratio (), modified Rayleigh number (), wall width (), inertial parameter (), and thermal conductivity ratio (). Outcomes show that and the locations of cooled and heated parts have remarkable impacts on all the Nusselt numbers. The intensity of LTNE region considerably relies on , and . The total average NuT is highly dependent on , , , , and as compared to H. The increase in leads to change of the convective mechanism to conductive mode. The rise in guides to increase Nu, where can control the flow strength. The actions of on Nuf is more evident than Nus. For low H and Kr, the size of LTNE zone is considerably affected by H as compared to Kr although Kr has a high influence on Nu. For high Kr and H, the LTNE zone has closely vanished. Findings display that the Case 2 provided the highest Nu for all tested parameters except the case of . Finally, it is evident that for the problems that employed solid conduction wall with localized heating and cooling sections, Case 2 is recommended for future use in the applications that implement a porous medium and depend on free convection.

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Section: Modelmentioning

confidence: 99%

Section: Introductionmentioning

confidence: 99%

Conjugate local thermal nonequilibrium and non‐Darcy flow inside porous enclosure: Analysis of localized heating and cooling arrangements

Basher

Yousif

2023

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“…The variations in density has been considered to follow the Boussinesq approximation 42,43 . By adopting the above assumptions, the set of the governing equations are obtained as follows 43 :

\frac{\partial u}{\partial x} + \frac{\partial v}{\partial y} = 0,

\frac{μ}{K} (][, \frac{\partial u}{\partial y} - \frac{\partial v}{\partial x}) + \frac{ρ b}{K} (][, \frac{\partial}{\partial y} ((∣∣, V) \cdot u) - \frac{\partial}{\partial x} ((∣∣, V) \cdot v)) = - ρ_{f \circ} g β \frac{\partial T_{f}}{\partial x} + μ (][, \frac{\partial}{\partial y} (\frac{\partial^{2} u}{\partial x^{2}} + \frac{\partial^{2} u}{\partial y^{2}}) - \frac{\partial}{\partial x} (\frac{\partial^{2} v}{\partial x^{2}} + \frac{\partial^{2} v}{\partial y^{2}})),

{(ρ C_{p})}_{f} (][, u \frac{\partial T_{f}}{\partial x} + v \frac{\partial T_{f}}{\partial y}) = φ k_{f} (][, \frac{\partial^{2} T_{f}}{\partial x^{2}} + \frac{\partial^{2} T_{f}}{\partial y^{2}}) + h (T_{S} - T_{f}),

…”

Section: Theoretical Modelmentioning

confidence: 99%

“…Based on this, the conservation Equations (1)–(4) can be written in the dimensionless form as follows 42,43 :

\frac{\partial \overset{u}{true}}{\partial \overset{x}{true}} + \frac{\partial \overset{v}{true}}{\partial \overset{y}{true}} = 0,

\frac{\partial^{2} \overset{ψ}{true}}{\partial {\hat{y}}^{2}} + \frac{\partial^{2} \overset{ψ}{true}}{\partial {\hat{x}}^{2}} = \frac{F s}{{italicPr}^{*}} (][, \frac{\partial}{\partial \overset{y}{true}} ((∣∣, \hat{V}) \cdot \overset{u}{true}) - \frac{\partial}{\partial \overset{x}{true}} ((∣∣, \hat{V}) \cdot \overset{v}{true})) + R a^{*} \frac{\partial θ_{f}}{\partial \overset{x}{true}} - D a (][, \frac{\partial^{2} \overset{ω}{true}}{\partial {\hat{y}}^{2}} + \frac{\partial^{2} \overset{ω}{true}}{\partial {\hat{x}}^{2}}),

\frac{\partial \overset{ψ}{true}}{\partial \overset{x}{true}} \cdot \frac{\partial θ_{f}}{\partial \overset{y}{true}} - \frac{\partial \overset{ψ}{true}}{\partial \overset{y}{true}} \cdot \frac{\partial θ_{f}}{\partial \overset{x}{true}} = (\frac{\partial^{2} θ_{f}}{\partial {\hat{x}}^{2}} + \frac{\partial^{2} θ_{f}}{\partial ...})

…”

Section: Theoretical Modelmentioning

confidence: 99%

“…The solutions display that the assumptions of non‐Darcy flow and LTNE model have substantial impacts on the behaviors of flow and rate of heat transfer. Then, Alomar et al 43 presented a comparison study on free convection induced from a bank of orthogonal heated surfaces immersed as inline and staggered arrangements under LTNE and non‐Darcian assumptions. The results show that the performance of staggered arrangement is less than in‐line arrangement.…”

Section: Introductionmentioning

confidence: 99%

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A thermal nonequilibrium model to natural convection inside non‐Darcy porous layer surrounded by horizontal heated plates with periodic boundary temperatures

2021

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This article displays a numerical investigation on natural convection within non‐Darcy porous layer surrounded by two horizontal surfaces having sinusoidal temperature profiles with difference in phase and wave number. The Darcy–Brinkman–Forchheimer model and local thermal nonequilibrium condition have been employed. Simulations have been performed for wide ranges of inertia coefficient (10–4 ≤ Fs/Pr* ≤ 10–2), thermal conductivity ratio (0.1 ≤ K r ≤ 100), phase difference (0 ≤ β ≤ π), modified Rayleigh number (200 ≤ Ra* ≤ 1000), wavelength (3 ≤ k ≤ 12), and nondimensional heat transfer coefficient (0.1 ≤ H ≤ 100). Results demonstrate that Nusselt number highly relies on Fs/Pr*, K r, β, Ra*, and k as compared to H. A considerable enhancement in fluid, solid, and overall Nusselt numbers has been observed with diminishing Fs/Pr* and β and increasing k, K r, and H. The raising in β has a significant impact on Nu for smaller k and this effect is almost ignored when k > 12. The increase in Ra*, K r, β, and H and decrease in Fs/Pr* and k acts to reduce the severity of nonequilibrium zone and increase the size of thermal equilibrium zone. The influence of H on nonequilibrium area is more evident than K r.

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Free convective heat transfer induced inside a vented duct having two aligned hot and cold cylinders: An experimental study

Alomar,

Ali,

Al‐Omar

2024

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Free convective heat transfer created from two aligned cylinders immersed inside a vented air duct is experimentally investigated. The experiments include the measurements of cylinders temperature and the air temperature inside the enclosure under steady, turbulent, and incompressible flow properties by using steady‐state heat equations. The studied parameters include Rayleigh number (), opening sizes at lower and upper enclosure surfaces (), and space size between cylinders () with the constant ratio of enclosure width to cylinder diameter equal to 6. The findings displayed that the average air temperature inside the enclosure for the low values of S and O is low, and it rises as S is raised. The behaviors of Nu differ with changing Ra values. An interaction between hot cylinder and cold cylinder inside the enclosure is observed that depends on O and S values, and hence, they have a large impact on fluid temperature. The data indicated that rises with the for all and values. The value of for each cylinder depends on the values of and . The maximum value has been obtained when and with maximum enhancement between 30% and 50% depending on Ra values as compared with and , whereas the minimum average has been indicated when and . The profiles of reveal that , , and have a considerable influence on heat transfer.

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Natural convection heat transfer from a bank of orthogonal heated plates embedded in a porous medium using LTNE model: A comparison between in-line and staggered arrangements

Cited by 20 publications

References 53 publications

Conjugate local thermal nonequilibrium and non‐Darcy flow inside porous enclosure: Analysis of localized heating and cooling arrangements

Conjugate local thermal nonequilibrium and non‐Darcy flow inside porous enclosure: Analysis of localized heating and cooling arrangements

A thermal nonequilibrium model to natural convection inside non‐Darcy porous layer surrounded by horizontal heated plates with periodic boundary temperatures

Free convective heat transfer induced inside a vented duct having two aligned hot and cold cylinders: An experimental study

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