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Research Papers

Dynamic Heat Transfer Study of a Triangular-Shaped Latent Heat Storage Unit for the Attic Space of a Domestic Dwelling

[+] Author and Article Information
Tonny Tabassum

Department of Mining & Materials Engineering,
McGill University,
M. H. Wong Building, 3610 University Street,
Montreal, QC H3A 0C5, Canada
e-mail: Tonny.tabassum@mail.mcgill.ca

Mainul Hasan

Mem. ASME
Department of Mining & Materials Engineering,
McGill University,
M. H. Wong Building, 3610 University Street,
Montreal, QC H3A 0C5, Canada
e-mail: Mainul.hasan@mcgill.ca

Latifa Begum

Department of Mining & Materials Engineering,
McGill University,
M. H. Wong Building, 3610 University Street,
Montreal, QC H3A 0C5, Canada
e-mail: Latifa.begum@mail.mcgill.ca

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF THERMAL SCIENCE AND ENGINEERING APPLICATIONS. Manuscript received November 8, 2017; final manuscript received May 10, 2018; published online September 10, 2018. Assoc. Editor: Amir Jokar.

J. Thermal Sci. Eng. Appl 10(6), 061015 (Sep 10, 2018) (20 pages) Paper No: TSEA-17-1434; doi: 10.1115/1.4040645 History: Received November 08, 2017; Revised May 10, 2018

A two-dimensional (2D) numerical study is carried out to investigate the thermal performance of an impure phase-change material (PCM) in an equilateral triangular-shaped double pipe heat exchanger. To tackle the irregular boundaries, a nonorthogonal body-fitted coordinate (BFC) transformation technique is employed. The nondimensional transformed curvilinear conservation equations for mass, momentum, and energy are written in terms of physical variables and they are solved using a control-volume based finite difference method on a staggered grid arrangement. The developed model is then used to study the effects of the inner tube wall temperature, the initial temperature of the solid PCM, and the shape, as well as the position of the inner tube in the annulus on the melting characteristics, and cumulatively stored energy. Various quantities such as average Nusselt numbers over the inner tube surface, the total and complete melt fractions, and the latent and total stored energies all as a function of the melting time are reported. A correlation for the average Nusselt number on the inner tube wall is also provided. The numerical results show that the shape and the placement of the inner tube are crucial for the efficient design of a latent heat thermal energy storage (LHTES) system. The storage of energy is greatly influenced by the change of the inner tube wall temperature compared to the change of initial solid PCM temperature.

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Figures

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Fig. 1

Schematic views of the proposed physical model where the horizontal double-pipe heat exchangers are presented in a series and in parallel directions

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Fig. 2

Schematic cross-sectional view of an irregular shaped double-pipe heat exchanger. The shaded region (ΔABC) represents the simulation domain.

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Fig. 3

Schematic illustrations of the physical configuration with the boundary conditions. The points D, E, and F on the inner tube are judicially selected for the transformed coordinates.

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Fig. 4

Schematic illustrations of the transformed configuration with the transformed boundary conditions. The points A, B, C, D, E, and F are defined in Fig. 2.

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Fig. 5

Comparison of liquid–solid interface movement of pure gallium inside a rectangular cavity

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Fig. 6

Predicted liquid–solid interface movements of pure gallium inside a rectangular cavity for melting time of (a) 2 min, (b) 5 min, (c) 10 min, and (d) 19 min

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Fig. 7

Two-dimensional temperature contours and velocity fields during melting for the wall temperature of 69.9 °C and the initial temperature of 51.2 °C for six different time instants for case 1: (a) time = 1.86 min, (b) time = 3.72 min, (c) time = 5.58 min, (d) time = 7.44 min, (e) time = 9.30 min, and (f) time = 11.16 min

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Fig. 8

Two-dimensional temperature contours and velocity fields during melting for the wall temperature of 79.9 °C and the initial temperature of 51.2 °C for six different time instants for case 2: (a) time = 1.86 min, (b) time = 3.72 min, (c) time = 5.58 min, (d) time = 7.44 min, (e) time = 9.30 min, and (f) time = 11.16 min

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Fig. 9

Two-dimensional temperature contours and velocity fields during melting for the wall temperature of 89.9 °C and the initial temperature of 51.2 °C for six different time instants for case 3: (a) time = 1.86 min, (b) time = 3.72 min, (c) time = 5.58 min, (d) time = 7.44 min, (e) time = 9.30 min, and (f) time = 11.16 min

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Fig. 10

Two-dimensional temperature contours and velocity fields during melting for the wall temperature of 79.9 °C and the initial temperature of 41.2 °C for six different time instants for case 4: (a) time = 1.86 min, (b) time = 3.72 min, (c) time = 5.58 min, (d) time = 7.44 min, (e) time = 9.30 min, and (f) time = 11.16 min

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Fig. 11

Two-dimensional temperature contours and velocity fields during melting for the wall temperature of 79.9 °C and the initial temperature of 51.2 °C for six different time instants for case 5: (a) time = 1.86 min, (b) time = 3.72 min, (c) time = 5.58 min, (d) time = 7.44 min, (e) time = 9.30 min, and (f) time = 11.16 min

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Fig. 12

Two-dimensional temperature contours and velocity fields during melting for the wall temperature of 79.9 °C and the initial temperature of 51.2 °C for six different time instants for case 6: (a) time = 1.86 min, (b) time = 3.72 min, (c) time = 5.58 min, (d) time = 7.44 min, (e) time = 9.30 min, and (f) time = 11.16 min

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Fig. 13

Two-dimensional temperature contours and velocity fields during melting for the wall temperature of 79.9 °C and the initial temperature of 51.2 °C for six different time instants for case 7: (a) time = 1.86 min, (b) time = 3.72 min, (c) time = 5.58 min, (d) time = 7.44 min, (e) time = 9.30 min, and (f) time = 11.16 min

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Fig. 14

Comparison of the variation with time of the average Nusselt number on the inner circular tube surface for cases (1–3) at Ti = 51.2 °C for three inner tube wall temperatures of 69.9 °C, 79.9 °C, and 89.9 °C

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Fig. 15

Comparison of timewise variation of the (a) cumulative total and complete liquid fraction and (b) cumulatively stored latent energy and total stored energy in the annulus for cases (1–3) at Ti = 51.2 °C for three inner tube wall temperatures of 69.9 °C, 79.9 °C, and 89.9 °C

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Fig. 16

Comparison of timewise variations of the cumulatively stored latent energy and total stored energy in the annulus for (a) cases (2, 5, and 6) and (b) cases (2 and 7)

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