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Research Papers: Heat Exchangers

Thermal Performance of Pulsating Heat Stripes Built With Plastic Materials

[+] Author and Article Information
Oguzhan Der

Laboratory of Technical Physics,
School of Engineering,
University of Liverpool,
Liverpool L69 3GH, UK
e-mail: O.Der@liverpool.ac.uk

Marco Marengo

School of Computing,
Engineering and Mathematics,
University of Brighton,
Brighton BN2 4GJ, UK
e-mail: M.Marengo@brighton.ac.uk

Volfango Bertola

Laboratory of Technical Physics,
School of Engineering,
University of Liverpool,
Liverpool L69 3GH, UK
e-mail: Volfango.Bertola@liverpool.ac.uk

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received September 13, 2018; final manuscript received November 4, 2018; published online July 22, 2019. Assoc. Editor: Fabio Bozzoli.

J. Heat Transfer 141(9), 091808 (Jul 22, 2019) (8 pages) Paper No: HT-18-1600; doi: 10.1115/1.4041952 History: Received September 13, 2018; Revised November 04, 2018

A low-cost, flexible pulsating heat pipe (PHP) was built in a composite polypropylene sheet consisting of three layers joint together by selective laser welding, to address the demand of heat transfer devices characterized by low weight, small unit thickness, low cost, and high mechanical flexibility. A thin, flexible, and lightweight heat pipe is advantageous for various aerospace, aircraft, and portable electronic applications where the device weight, and its mechanical flexibility are essential. The concept is to sandwich a serpentine channel, cut out in a polypropylene sheet and containing a self-propelled mixture of a working fluid with its vapor, between two transparent sheets of the same material; this results into a thin, flat enclosure with parallel channels hence the name “pulsating heat stripes” (PHS). The transient and steady-state thermal response of the device was characterized for different heat input levels and different configurations, either straight or bent at different angles. The equivalent thermal resistance was estimated by measuring the wall temperatures at both the evaporator and the condenser, showing a multifold increase of the equivalent thermal conductance with respect to solid polypropylene.

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References

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Figures

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Fig. 1

Schematic of the PHS assembly and laser welding process (a) and top view of the assembled PHS showing the serpentine channel and the location of surface thermocouples (b)

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Fig. 2

Demonstration of the PHS flexibility (180 deg bending)

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Fig. 3

Schematic of the experimental arrangement to estimate the relaxation stress in the PHS wall

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Fig. 4

Force measured by the sensor sandwiched between the weight and the PHS wall (see Fig. 3). The black line indicates the moving average over 30 min.

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Fig. 5

Pressure variation in the vacuumed PHS (left axis) and corresponding pressure variation (right axis) as a function of time

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Fig. 6

Three-dimensional view of the experimental kit showing the bending mechanism

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Fig. 7

Schematic of the experimental setup: (a) vacuum pump, (b) syringe, (c) data logger and PC, (d) pressure transducer, (e) micrometering valve, (f) thermocouples unit, (g) condenser fans, (h) power supply, and (i) electric heaters

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Fig. 8

Examples of FLIR images of the adiabatic region of PHS in straight vertical arrangement during the heating ramp: (a) Q˙=5.2W, (b) Q˙=16W, and (c) Q˙=31.3W

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Fig. 9

Temperatures measured in the evaporator (TE1TE4) and in the condenser (TC1TC4) zones of the PHS in straight arrangement during the ascending/descending power supply ramp: (a) vertical, (b) inclined at 45 deg, and (c) horizontal

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Fig. 10

Absolute pressure measured in the PHS in straight arrangement during the ascending/descending power supply ramp: (a) vertical, (b) inclined at 45 deg, and (c) horizontal

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Fig. 11

Equivalent thermal resistance of the PHS in straight arrangement, as a function of the heat rate supplied at the evaporator, for different inclination angles; filled symbols: increasing power; open symbols: decreasing power. The standard deviation based on three tests is ≤8%.

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Fig. 12

Temperatures measured in the evaporator (TE1TE4) and in the condenser (TC1TC4) zones of the PHS in bent arrangement during the ascending/descending power supply ramp: (a) 45 deg bending and (b) 90 deg bending

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Fig. 13

Absolute pressure measured in the PHS in bent arrangement during the ascending/descending power supply ramp: (a) 45 deg bending and (b) 90 deg bending

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Fig. 14

Equivalent thermal resistance of the PHS in straight vertical and in bent arrangements, as a function of the heat rate supplied at the evaporator, for different bending angles; filled symbols: increasing power; open symbols: decreasing power. The standard deviation based on three tests is ≤8%.

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