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Research Papers: Micro/Nanoscale Heat Transfer

Hydrodynamic and Thermal Performance of Microchannels With Different In-Line Arrangements of Cylindrical Micropin Fins

[+] Author and Article Information
Ali Mohammadi

Faculty of Engineering and
Natural Sciences (FENS),
Sabanci University,
Orhanli,
Tuzla 34956, Istanbul, Turkey
e-mail: alimohammadi@sabanciuniv.edu

Ali Koşar

Professor
Faculty of Engineering and
Natural Sciences (FENS),
Sabanci University,
Orhanli,
Tuzla 34956, Istanbul, Turkey
e-mail: kosara@sabanciuniv.edu

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received February 11, 2016; final manuscript received July 12, 2016; published online August 16, 2016. Assoc. Editor: Zhuomin Zhang.

J. Heat Transfer 138(12), 122403 (Aug 16, 2016) (17 pages) Paper No: HT-16-1077; doi: 10.1115/1.4034164 History: Received February 11, 2016; Revised July 12, 2016

This study presents results on the hydrodynamic and thermal characteristics of single-phase water flows inside microchannels (MCs) with different micropin fin (MPF) configurations. Different inline arrangements of micropin fins were considered over Reynolds numbers ranging from 20 to 160. The computational studies were performed using the commercial software ansys 14.5. The hydrodynamic performances of the configurations were compared using two parameters, namely, pressure drop and friction factor while the comparison in their thermal and thermal-hydraulic performances were based on Nusselt number and thermal performance index (TPI). Wake-pin fin interactions were carefully analyzed through streamline patterns in different arrangements and under different flow conditions. The results showed strong dependencies of all four evaluated performance parameters on the vertical pitch ratio (ST/D). Weaker dependencies on height over diameter ratio (H/D), horizontal pitch ratio (SL/D), and minimum available area (Amin) were observed. With an increase in the Reynolds number, extension of the wake regions behind MPFs was observed to be the paramount factor in increasing pressure drop and Nusselt number. Regarding TPI, two adverse trends were observed corresponding to different ST/D ratios, while the effect of SL/D ratio was unique. For friction factors, H/D and SL/D ratios of 1 and 1.5, respectively, led to minimum values, while different ST/D ratios are needed for each diameter size for the maximum performance. Moreover, a twofold increase in Reynolds number resulted in about 40% decrease in friction factor in each configuration.

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References

Figures

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Fig. 1

Three-dimensional model of the LVdHd configuration

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Fig. 2

Validation of the numerical model with the results of Koşar et al. [19]—ΔP versus Reynolds number

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Fig. 3

Validation of the numerical model with the results of Koşar et al. [19]—ΔT(ToutTin) versus Reynolds number

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Fig. 4

Velocity and temperature profiles of the validation case at Re = 262 (midheight section)

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Fig. 5

Pressure drop in different configurations (a) with SL/D = 1.5 and (b) with SL/D = 3)

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Fig. 6

Streamlines at the midheight sections of the LVdHd, MVdHd and SVdHd configurations (Re = 80)

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Fig. 7

Streamlines at the 10% (first row) and the 90% (second row) sections of the LVdHd, MVdHd and SVdHd configurations (Re = 80)

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Fig. 8

Streamlines at the midheight sections of the LVdHd and LVdHs configurations (Re = 80)

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Fig. 9

Streamlines at the midheight sections of the MVdHd and MVsHd configurations (Re = 80)

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Fig. 10

Streamlines at the midheight section of the LVdHd configuration at different Reynolds numbers

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Fig. 11

Pressure drop as a function of Reynolds number

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Fig. 12

Friction factor in different configurations at different Reynolds numbers

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Fig. 13

Nusselt number in different configurations (a) with SL/D = 1.5 and (b) with SL/D = 3)

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Fig. 14

Static temperature profiles at the midheight sections of LVdHd, MVdHd and SVdHd configurations (Re = 80)

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Fig. 15

Temperature profiles at the 10% (first row) and the 90% (second row) sections of the LVdHd, MVdHd and SVdHd configurations (Re = 80)

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Fig. 16

Temperature profiles at the midheight sections of the LVdHd and LVdHs configurations (Re = 80)

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Fig. 17

Temperature profiles at the midheight sections of the MVdHd and MVsHd configurations (Re = 80)

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Fig. 18

Nusselt number as a function of Reynolds number

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Fig. 19

Thermal performance index (TPI) as a function of Reynolds number

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