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Research Papers: Natural and Mixed Convection

Thermosolutal Mixed Convection in an Air Filled Ventilated Enclosure With Slot Wise Embedded Heat and Contaminant Sources

[+] Author and Article Information
K. Venkateshwarlu, V. K. Katiyar, N. Gupta

Department of Mathematics,
Indian Institute of Technology Roorkee,
Roorkee 247667, Uttarakhand, India

A. K. Nayak

Department of Mathematics,
Indian Institute of Technology Roorkee,
Roorkee 247667, Uttarakhand, India
e-mail: ameeyakumar@gmail.com

Bhupinder Singh

Department of Civil Engineering,
Indian Institute of Technology Roorkee,
Roorkee 247667, Uttarakhand, India

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received November 15, 2014; final manuscript received September 12, 2015; published online November 3, 2015. Assoc. Editor: Danesh / D. K. Tafti.

J. Heat Transfer 138(3), 032501 (Nov 03, 2015) (9 pages) Paper No: HT-14-1747; doi: 10.1115/1.4031788 History: Received November 15, 2014; Revised September 12, 2015

Airflow, heat, and contaminant transfer in a mechanically ventilated two-dimensional rectangular enclosure by discrete heat and contaminant sources as well as external forced convection at various inlet and outlet locations is numerically simulated. Two different enclosure configurations are considered. In configuration A, the cold air is injected at the top of the left vertical wall and exited at the bottom of the right vertical wall. In configuration B, the cold air is injected at the lower edge of the left vertical wall and exited at the top of the right vertical wall. The objective of the study is to find the relative locations of inlet and outlet in order to obtain more effective cooling in the core of the enclosure by maximizing the heat and contaminant removal rate and reducing the overall temperature. The developed mathematical model is governed by the two-dimensional continuity, momentum, energy, and concentration equations. The governing equations in Cartesian co-ordinates are solved by finite volume based semi-implicit method for pressure linked-equations (SIMPLE) algorithm based on a staggered grid system. Results are presented for different values of the Reynolds number, Grashof number, Sherwood number, and Buoyancy ratio in the laminar regime. A convective transport visualization technique is used to study the behavior of physical phenomena due to stream function, thermal, and solutal functions. The results indicate that cooling inside the core of the enclosure is most effective when the inlet is kept at the bottom of the left vertical wall.

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References

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Figures

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Fig. 1

Schematic of two-dimensional double-diffusive mixed convection in a displacement ventilated room

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Fig. 2

Influence of grid sizes on the variations of the local Nusselt number at the upper and lower of the square cavity with Moallemi and Jang [21] when Pr = 1.0, Gr = 105, and Re = 500

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Fig. 3

Validation of present code with the previous experimental work of Minaei et al. [10] for a mixed convection flow at Re = 320

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Fig. 4

Streamline for different Richardson numbers and Br = 1 of configuration A

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Fig. 5

Isothermal lines for different Richardson numbers and Br = 1 of configuration A

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Fig. 6

Isoconcentration lines for different Richardson numbers and Br = 1 of configuration A

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Fig. 7

Variations of Nu and Sh against Br with Re = 500 and Gr = 104 for configuration A

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Fig. 8

Variations of Nu and Sh against Gr with Re = 500 and Br = 1 for configuration A

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Fig. 9

Streamlines for different Richardson numbers and Br = 1 of configuration B

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Fig. 10

Isothermal lines for different Richardson numbers and Br = 1 of configuration B

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Fig. 11

Isoconcentration lines for different Richardson numbers and Br = 1 of configuration B

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Fig. 12

Variations of Nu and Sh against Br with Re = 500 and Gr = 104 for configuration B

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Fig. 13

Variations of Nu and Sh against Gr with Re = 500 and Br = 1 for configuration B

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Fig. 14

Effects of Re on heat transfer for different Gr values at Br = 1 for configurations A and B

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Fig. 15

Cooling efficiency for different Ri and Re values at Br = 1 for configurations A and B

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Fig. 16

Comparison of average temperature at Br = 1 for configurations A and B

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