A combined experimental and numerical approach for printed circuit rectangular microchannel J-T cooler using argon

She, Hailong; Cui, Xiaoyu; Weng, Jianhua; Geng, Hong; Chang, Zhihao

doi:10.1016/j.applthermaleng.2020.116107

Cited by 12 publications

(2 citation statements)

References 22 publications

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“…10 Researchers have done some research on micromachined J-T coolers. [11][12][13][14] Most importantly, the microchannel with discontinuous pillars can weaken the axial heat conduction, ensure the pressure capacity, and they can increase the wall surface area, enhance the heat transfer rate. 15 In recent years, a few authors have attempted to use the pin-fins microchannel in the J-T cooler.…”

Section: Introductionmentioning

confidence: 99%

Characterization of a distributed Joule‐Thomson effect cooler with pillars

et al. 2021

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The application of general Joule-Thomson (J-T) coolers in the integrated electronic equipment is limited by its compactness in the heat exchanger and cooling power (a few milliwatts to hundreds of milliwatts). However, the microchannel with pillars has many advantages, such as compact structure, tiny axial thermal conductivity, and large heat transfer area. Besides, when the pressure variation of the fluid is large in the microchannel, the distributed Joule-Thomson effect is generated significantly. Therefore, this study proposed a throttling and heat exchange structure, where heat transfer and throttling coexisted, and fabricated a laminated microchannel distributed J-T cooler with pillars utilizing the processing technology of printed circuit heat exchanger.The refrigeration performance concerning the cold-end temperature, cooling power, and temperature distribution was then investigated through experiments with two refrigerants (argon and nitrogen). The study implies that the temperature difference and cooling power of the cooler both increase with the rise of the inlet pressure with argon, the no-load cold-end temperature is 166.1 K, and the gross cooling power is 3.83 W at 5.20 MPa. The temperature of the cooler increases with the rise of heat load, while the parasitic heat load decreases. The cold-end temperature is 186.0 K, then the parasitic heat load and the gross cooling power are respectively 3.17 W and 7.17 W at 5.20 MPa under the heat load's condition of 4 W. Comparing the refrigeration performance of nitrogen and argon, the cold-end temperature of nitrogen at 5.20 MPa is 235.7 K, which is close to that of argon at 2.98 MPa. Whereas the cooling time of nitrogen is slightly shorter than that of argon, and the cooling power is 3.10 W, higher than that of argon. In addition, this study provides new insight into increasing the cooling power and reducing the application cost of miniature coolers.

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Section: Introductionmentioning

confidence: 99%

Characterization of a distributed Joule‐Thomson effect cooler with pillars

et al. 2021

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“…The heat exchanger is one of the key components of liquid rocket engines. Its main function is to allow full heat exchange between liquid oxygen and high-temperature fuel gas, resulting in the evaporation of the liquid oxygen into gas oxygen, which then enters the storage tank of the rocket oxidizer under the effects of pressure to provide a stable supply of propellant for the engine; therefore, the efficiency of the heat exchanger is one of the key factors affecting the performance of the engine [1][2][3]. At present, the structure of heat exchangers is typically designed in the form of an array-distributed rectangular milling groove structure or a spiral groove structure [4,5], which is formed by tailor-welding a split structure [6,7].…”

Section: Introductionmentioning

confidence: 99%

Analysis of Heat Transfer Characteristics of a Heat Exchanger Based on a Lattice Filling

et al. 2021

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In response to the heat load requirements of the high-thrust liquid rocket engine, a light-weight lattice structure is used to fill traditional a heat exchanger. A parameterized model library of the lattice structure is established, and the relative density of the lattice structure is adjusted by changing the unit cell structure parameters to obtain different filling structures. A comprehensive comparison of heat exchangers with different filling structures performed in terms of weight, heat transfer efficiency, and turbulence intensity. Using the finite difference method, the numerical calculation of the non-steady heat–fluid–solid coupling conjugate heat transfer of the eight-lattice structure is performed, and the dynamic heat transfer process between the lattice structure and liquid oxygen is simulated using the VOF model and the SST k-ω model. The results show that the pressure of the fluid in the heat exchanger increases with increasing relative density, leading to a high outlet temperature and greatly increasing the outlet velocity. The support trusses close to the wall obviously hinder the flow of liquid oxygen, resulting in a sudden change in the flow rate behind the support trusses, driving the high-temperature fluid at the bottom to move upwards. The direction of the support trusses and the unit cell porosity have a greater impact on the liquid oxygen flow rate, which in turn affects the flow and heat transfer performance of the heat exchanger. In consideration of the heat load requirements of the heat exchanger, star-type lattices are used to fill the heat exchanger. When the flow is fully developed, the volume ratio of the heated fluid is 85.60%, and the outlet temperature is 390 K, which meets the design requirements.

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