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Technical Brief

Numerical Solution of Radiative Transfer in a Real-Participating Media

[+] Author and Article Information
Hanene Belhaj Ali

Laboratory of Energy and Thermal Systems (LESTE),
University of Monastir,
Monastir 5019, Tunisia
e-mail: hanene.belhajali@gmail.com

Hajer Grissa

Laboratory of Energy and Thermal Systems (LESTE),
University of Monastir,
Monastir 5019, Tunisia
e-mail: grissahajer@yahoo.fr

Faouzi Askri

Laboratory of Energy and Thermal Systems (LESTE),
University of Monastir,
Monastir 5019, Tunisia;
Faculty of Engineering,
King Khalid University,
Abha 62529, Saudi Arabia
e-mail: Faouzi.askri@enim.rnu.tn

Sassi Ben Nasrallah

Laboratory of Energy and Thermal Systems (LESTE),
University of Monastir,
Monastir 5019, Tunisia
e-mail: Sassi.bennasrallah@enim.rnu.tn

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received March 7, 2016; final manuscript received May 4, 2016; published online May 17, 2016. Assoc. Editor: Zhuomin Zhang.

J. Heat Transfer 138(9), 094503 (May 17, 2016) (6 pages) Paper No: HT-16-1120; doi: 10.1115/1.4033567 History: Received March 07, 2016; Revised May 04, 2016

In this paper, the control volume finite element method (CVFEM) is coupled with the weighted sum of gray gases model (WSGGM) to study the radiative heat transfer in a nongray medium. To the best of our knowledge, the CVFEM–WSGGM is applied for the first time to simulate real-gas. The accuracy of the proposed method is tested through one- and two-dimensional radiative heat transfer within an enclosure filled with a single composition (water vapor or carbon dioxide) or a mixture of H2O, CO2, and N2. Compared to the discrete ordinates method (DOM)–statistical narrow band model (SNBM), the proposed method, using the WSGG model parameters due to Smith or Farag, yields much accurate results than the zonal method (ZM)–WSGGM and DOM–WSGGM. In addition, the present method needs very less control volumes and angles, and consequently computational time, compared to the DOM and ZM coupled with WSGGM.

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References

Figures

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Fig. 2

Angular discretization (control solid angle ΔΩmn)

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Fig. 1

(a) Control volume ΔVP and (b) subvolume δVP

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Fig. 4

Distribution of radiative heat source term for one-dimensional enclosure with a pure water vapor: (a) L = 0.1 m and (b) L = 1 m

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Fig. 5

Distribution of radiative heat source for one-dimensional enclosure with 10% CO2

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Fig. 8

Distribution of radiative heat flux for two-dimensional enclosure with 10% CO2 on (a) wall 1 and (b) wall 2

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Fig. 6

Distribution of radiative heat source for one-dimensional enclosure with H2O–CO2–N2 mixture: (a) L = 1 m and (b) L = 5 m

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Fig. 7

Configuration of a rectangular enclosure

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Fig. 9

Distribution of radiative heat flux for two-dimensional enclosure with 20% H2O on (a) wall 1 and (b) wall 2

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