• Proceedings of the Korean Society for Agricultural Machinery Conference
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• 2002.02a
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• pp.151-157
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• 2002

화석에너지에 대한 경제적 부담과 환경오염문제를 줄이기 위하여 열펌프의 성능계수향상을 위하여 냉온 공기열교환기(HEEVA)를 고안하였고, 이 열교환기의 열특성과 성능계수향상에 미치는 영향을 분석하기 위하여 냉.난방 실험을 수행하였다. HEEVA에 의한 찬 공기와 더운 공기의 온도변화, 전열량 및 냉온 공기열교환기 효율, 총열전달계수등을 측정분석하였고, 냉난방시 외기온에 따른 열펌프의 성능계수, 소비전력, 응축기.증발기 출구 공기토출 온도 변화를 측정 분석함으로서 다음과 같은 결과를 얻을 수 있었다. 1. 외기온이 -4~11$^{\circ}C$로 변할 때 열펌프의 난방과정에서 HEEVA 찬공기 입출구 온도차는 4.5$^{\circ}C$에서 9.$0^{\circ}C$로 증가하였으며, HEEVA에 의한 영향으로 2~6$^{\circ}C$상승된 공기가 증발기 입구로 유입되어 냉매증발을 촉진하였다. 2. 실온이 4~22$^{\circ}C$일 때 HEEVA 더운공기 입출구 온도차는 3$^{\circ}C$에서 7$^{\circ}C$로 증가하였으며, 응축기에 유입되는 공기온도를 3~8$^{\circ}C$낮게 함으로서 압축기 소모전력을 감소시켜 COP 상승 효과를 나타냈다. 3. 외기온과 실온변화에 따라 풍량 346m$^3$/hr의 찬 공기가 받은 열량과 풍량 747m$^3$/hr의 더운 공기가 준 열량간의 차는 50~150kcal/hr로 나타났으며, 더운 공기가 준열량과 찬 공기가 받은 열량의 비가 83~98% 이었으므로 HEEVA의 열 교환율은 91% 을 보였다. 4. 총합열전달계수는 이론값이 실험 값보다 1~3W/m$^2$K 크게 나타났으며, 이 결과는 두 값 사이에 10% 내.외의 편차로서 Nusselt수를 구하기 위한 Petukhov상관식의 자체오차 15%에 비해 크지 않은 오차범주에 속하며, 이론상의 총합열전달계수 유도식의 타당성을 입증한 것이라 하겠다. 5. HEEVA를 작동함으로서 난방시 COP가 HEEVA를 작동하지 않았을 경우보다 0.3~0.5 향상된 것으로 나타났다. 이것은 HEEVA가 겨울철 난방에 효율을 높일수 있는 것으로 판단된다.

• Journal of Energy Engineering
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• v.9 no.3
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• pp.212-220
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• 2000

히트파이프 히트싱크의 라디에이터를 통과하는 공기 유동에 대한 열전달 및 유동 압력 강하를 구하기 위한 연구를 수행하였다. 이 라디에이터는 평판 휜-관 구조이며, 평판휜에 4개의 히트파이프가 유동 방향으로 정격 배열 되어있다. 입구 공기 속도 2.5~4m/s에 대해 열전달 성능실험과 수치해석을 수행하였다. 각 히트파이프의 단위 길이당 열속이 583.3W/m, 입구 공기 속도가 3m/s일때 총합 대류 열전달계수값은 약 32W/$m^2$K, 압력 강하는 8mmAq이었다. 전체속도범위에서 실험결과와 수치 해석 결과 사이에는 약 5%의 미만의 일치를 보였다.

• Proceedings of the KSME Conference
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• 2000.04b
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• pp.13-18
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• 2000

The objective of the Present study is to investigate the performance of electronic scale mitigation unit(ESMU), which reduces the amount of scale in a heat exchanger. A plate heat exchanger with 20 thermal plates is used for the tests. In order to accelerate the rate of fouling in a laboratory test artificial hard water of 2000 ppm(as $CaCO_3$) is recirculated at a flow rate 5L/min throughout the tests. The overall heat trans(or coefficients and fouling factors are examined. Results show that the ESMU technology can significantly reduce the scale deposits.

• Proceedings of the Korean Society of Machine Tool Engineers Conference
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• 1998.10a
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• pp.125-133
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• 1998

Nine tubes with trapezoidal integral-fins having fin densities from 748 to 1654fpm and 10,30 grooves and finned tubes with caves of 0.55 and 0.64mm height respectively are tested. A plain tube having same diameter as the finned tubes is also tested for comparison. In case of condensation CFC-11 condensates at saturation state of 32$^{\circ}C$ on the outside surface cooled by inside cooling water flows. And in case of boiling the refrigerant evaporates at a saturation state of 1bar on the outside tube surface and heat is supplied by hot water which circulates inside of the tube. The tube having fin density of 1299fpm and 30grooves has the best condensation overall heat transfer coefficient. However, as far as boiling heat transfer coefficient concerns, fin tubes with cave show higher value than low fin tube having fin density of 1299fpm and 30 grooves.

• Journal of the Korea Academia-Industrial cooperation Society
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• v.10 no.1
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• pp.46-51
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• 2009

In this work, the experimental investigation was carried out to evaluate the heat transfer performance on the shell side of shell-and-plate finned tube heat exchanger with three different tube numbers(9, 13 and 19). Oil flowing on the shell side was cooled by cold water flowing inside the tubes. A shell-and-tube heat exchanger of an oil cooler consisted of one shell pass and two tube passes with the inner tube diameter of 8.82 mm and the tube length of 575 mm. Mass flow rate was varied from 1.2 to $6.0\;m^3/h$ for oil and from 0.6 to $3.0\;m^3/h$ for cold water, respectively. From the experiment of shell-and-plate finned tube heat exchanger, the overall heat transfer coefficient of heat exchanger with 9 tubes was compared with that of 13 and 19 tubes. It was found that the heat transfer coefficients in shell side of heat exchanger with 9 plate finned tubes showed averagely 1.8 times and 2.3 times higher than those of 13 and 19 tubes, respectively.

• Proceedings of the SAREK Conference
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• 2008.11a
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• pp.250-255
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• 2008

Most high-rise building and large building require a cooling tower. Closed cooling tower is a low noise and the high efficiency. also Closed cooling tower is available for four season. Performance of Closed cooling tower is judged by heat transfer coefficient. In this study, Heat transfer coefficient is compared with air velocity, spray flow, heat exchanger type.

• Solar Energy
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• v.11 no.1
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• pp.69-77
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• 1991

A two-phase closed thermosyphon with circular fins was used as the heat transfer device for storing the thermal energy in paraffin wax. Experiments were carried out for 4, 6 and 8 fins and for various initial temperatures of the wax and power inputs. Heat transfer characteristics along the heat flow path were investigated as well as the overall performance of the system. Some of the important results are as follows:(1) The thermosyphon heat transfer coefficient and the overall heat transfer coefficient increased with the number of fins, whereas the heat transfer coefficient between the fin and the wax decreased; (2) Facilitation of heat transfer by the fins seemed to alleviate the dry-out phenomenon that had been reported to occur in case of bare thermosyphon; and (3) The horizontal fins had adverse effect of subduing a full scale convection in the wax, and the increase of the number of fins delayed the onset of local convection between the fins.

• Proceedings of the SAREK Conference
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• 2008.06a
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• pp.334-339
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• 2008

An closed cooling tower is a device similar to a general cooling tower, but with cooling tower replaced by a heat exchanger. The purpose of this study is to evaluate thermal performance of heat exchanger at various conditions and to provide design datebase. The experimental study regarding heat exchanger for closed cooling tower was conducted. Experimental apparatus consists of constant temperature bath, water pump, spray nozzle, heat exchanger, fan, and date acquisition system. Heat transfer rates at various air velocitys, water flow rates, two different spray modes were measured and heat transfer coefficient were calculated to compare the thermal performances. This study provides that the heat transfer coefficient increases with increasing spray water flow rate and with increasing air velocity. The wet mode was more effective than dry mode for closed cooling tower to this study.

• Transactions of the Korean Society of Mechanical Engineers B
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• v.25 no.9
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• pp.1149-1156
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• 2001

The objective of the present study is to investigate the performance of electronic scale mitigation unit(ESMU), which reduces the amount of scale in a heat exchanger. The circular tube with diameter of 19mm and plate-and-frame heat exchangers with 20 thermal plates were used for the tests. In order to accelerate the rate of scale in a laboratory test, artificial hard water of 1000ppm(as CaCO$_3$) was recirculated at a flow rate of 5 lpm, 7 lpm, and 9 lpm throughout the tests. The effect of ESMU on the scale thickness and overall heat transfer coefficients was examined. The test results showed that the ESMU could reduce the scale deposits even in the acceleated test.

• Journal of the Korea Academia-Industrial cooperation Society
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• v.19 no.4
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• pp.517-524
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• 2018

This purpose of this research is to observe the influence of non-condensable gas (NCG) on a horizontal super-hydrophobic aluminum tube and compare it with a bare aluminum tube. To achieve super-hydrophobic characteristics, an aluminum tube was coated with a Self-Assembled Monolayer (SAM). The overall heat transfer coefficient U was used to represent the condensation performance. The NCG mass fraction was the main variable, and its range was 0.08 to 0.45. The condensation performance of the SAM tube and bare tube increased with decreasing mass fraction of NCG. The SAM tube showed 1.9 to 2.5 times larger dropwise condensation performance than the bare tube. When the mass fraction of NCG decreased in the SAM tube, the rate of increase of the SAM tube was lower because flooded condensation occurred. In addition, filmwise condensation occurred in the SAM tube when more active condensation was generated, and its performance was lower than that of the bare aluminum tube. The flooded and filmwise condensation in the SAM tube is explained by the pinning effect. In conclusion, controlling the condition of the condenser is necessary to improve the condensation performance by surface modification a SAM.