• 한국태양에너지학회 논문집
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• 제32권5호
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• pp.59-67
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• 2012

In this study,the compact type solar thermal and ground coupled heat pump hybrid system for space heating/cooling and hot water supply has been developed. This hybrid system was installed in Zero Energy Solar House(ZeSH) in KIER for the demonstration. The thermal performance and operational characteristics of this hybrid system were analysed especially. The results are as follows. (1) This hybrid system was designed in order to address the existing disadvantages of solar thermal/ground coupled heat pump system. For this design, all parts except solar collector and ground coupled heat pump were integrated into a single product in a factory. The compact type unit includes two buffer tanks, an expansion tank, pumps, valves, a controller, etc. This system has an advantage of easy installation with simple plumbing work even in narrow space. (2) The thermal charging and discharging time of the buffer tanks and its characteristics by ground coupled heat pump, and heat pump COP according to geo-source temperature and buffer storage temperature have been studied. This system was found to meet well to the heat load without any other auxiliary heating equipment. (3) The operating hours of the ground coupled heat pump as a backup device of solar thermal can be reduced significantly by using solar heat. It was also found that the minimum heating water supply setting temperature and maximum cooling water supply setting temperature make an influence on the heat pump COP. The lower heating water and the higher cooling water temperature, the higher COP. In this respect, the hybrid system's performance can be improved in ZeSH than conventional house.

• 한국태양에너지학회 논문집
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• 제35권6호
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• pp.25-33
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• 2015

In this study, heating performance of the air-cooled heat pump with vapor-injection (VI) cycles, re-heater and solar heat storage tank was investigated experimentally. Devices used in the experiment were comprised of a VI compressor, re-heater, economizer, variable evaporator, flat-plate solar collector for hot water, thermal storage tank, etc. As working fluid, refrigerant R410A for heat pump and propylene glycol (PG) for solar collector were used. In this experiment, heating performance was compared by three cycles, A, B and C. In case of Cycle B, heat exchange was conducted between VI suction refrigerant and inlet refrigerant of condenser by re-heater (Re-heater in Fig. 3, No. 3) (Cycle B), and Cycle A was not use re-heater on the same operating conditions. In case of Cycle C, outlet refrigerant from evaporator go to thermal storage tank for getting a thermal energy from solar thermal storage tank while re-heater also used. As a result, Cycle C reached the target temperature of water in a shorter time than Cycle B and Cycle A. In addition, it was founded that, as for the coefficient of heating performance($COP_h$), the performance in Cycle C was improved by 13.6% higher than the performance of Cycle B shown the average $COP_h$ of 3.0 and by 18.9% higher than the performance of Cycle A shown the average $COP_h$ of 2.86. From this results, It was confirmed that the performance of heat pump system with refrigerant re-heater and VI cycle can be improved by applying solar thermal energy as an auxiliary heat source.

• 한국태양에너지학회 논문집
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• 제25권4호
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• pp.37-44
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• 2005

An experimental study was conducted to analyze performance of a heating system with variation of control logic of the system. The system uses a solar as heat source and composed with heat pump that uses R-22 as working fluid. The difference between the developed system and the commercially available heating system is working fluid. The solar assisted heating system which was widely distributed in the market uses water as a working fluid. It could be freezing in case of the temperature drops down under freezing point. The anti-freezing fluids such as methyl-alcohol or ethylene-glycol are mixed with the water to protect the freezing phenomena. However, the system developed in this study uses a refrigerant as a working fluid. It makes the system to run under zero degree temperature conditions. Another difference of the developed system compare with commercial available one is auxiliary heating method. The developed system has removed an auxiliary electric heater that has been used in conventional solar assisted heating system. Instead of the auxiliary electric heater, an air source heat exchanger which generally used as an evaporator of a heat pump was adapted as a backup heating device of the developed system. As results, an efficiency of the developed system is higher than a solar assisted heat pump with auxiliary electric heater. The merit of the developed system is on the performance increment when the system operates at a lower solar energy climate conditions. In case of the developed system operates at a normal condition, COP of the solar collector driven heat pump is higher than the air source heat exchanger driven heat pump's.

• 한국축산시설환경학회지
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• 제10권3호
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• pp.141-154
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• 2004

자연에너지인 태양열을 동력원으로 하여 구동되는 물펌프는 물이 많이 필요한 여름철에 과 열원인 태양에너지가 강하므로 매우 이상적인 장치라 할 수 있다. 본 연구에서는 태양열 물펌프의 자동화운전을 실현하고자 작동물질의 압력변화를 감지하여 자동 운전되도록 하였으며, 이에 필요한 제어논리를 개발하고 회로론 구성하였다. 실험에서는 장치를 제작. 실험, 분석하였고 분석항목은 양수량과 효율, 압력, 온도를 분석하였다. 또한 자동화에 필수적인 응축기 진공을 위한 응축기의 최소 전열면적을 설계하였으며, 그 결과를 정리하면 다음과 같다. 1. 복사에너지를 동력으로 변환하여 물을 양수할 수 있었고, 자동화 제어회로에 의해 사이클을 반복할 수 있었다. 2 양수는 60분 동안에 13사이클을 수행하였으며, 사이클 당 소요시간은 약 4.9분이었다. 총 양수량은 69,200cc, 사이클 당 평균 5,320cc를 양수하였다. 이 과정동안 장치의 열효율은 $0.030\%$로 나타났다. 3. 실험과정에서 기액 분리탱크 내의 작동물질 증기의 온도는 물탱크로 증기를 배출하기 전후에 따라 약 $41\~49^{\circ}C$ 범위에 있었으며, 상당히 균일하게 변동하고 있었다. 물탱크와 공기탱크내의 온도는 약 $30^{\circ}C$ 정도 부근에서 유지되고 있었으며, 응축기 냉각수공급온도는 실험기간 중 $10\~13^{\circ}C$ 범위를 나타내었다. 응축기 출구온도는 $14\~17^{\circ}C$ 정도로서 응축기 냉각수의 입출구 온도차는 실험초기를 제외하면 약 $4^{\circ}C$ 전후로 나타났다 4. 기액 분리탱크 내의 압력은 자동화 프로그램 된 범위인 150$\~$450hPa(gauge)를 매우 정확하게 유지하였으며, 공기탱크내의 압력은 약 1200hPa로 나타났다. 응축기내의 압력은 약 600hPa로서 진공을 잘 유지함으로서 사이클을 반복하는데 문제가 없었다. 5. 한국의 전국 하루 평균 3.488kWh/($m^2{\cdot}day$)의 태양에너지를 기준으로 장치의 열효율이 $0.1\%$를 적용하고 전 양정을 10m로 보면 태양열복사 단위면적 $m^2$ 당 약 128kg의 물을 양수할 수 있을 것으로 예상된다.

• 한국산학기술학회논문지
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• 제21권6호
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• pp.403-410
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• 2020

본 논문은 포항지역 태양광 데이터를 기반으로 태양열을 적용시켜 12kW의 소형 초임계 이산화탄소(s-CO₂) 시험 루프의 설계와 실험 시설의 이론적 연구, 안정화 및 최적화를 통한 이산화탄소의 특성 연구에 초점을 맞추고 있다. 실험 시설의 열역학 사이클은 구성 요소의 한계로 인해 액체, 가스 및 초임계 CO₂가 모두 존재하는 랭킨 사이클(임계점 순환 주기)이며, 펌프, 히터, 레귤레이터, 열교환기, 가스 부스터, 에어 컴프레서 등으로 구성된다. 현재 본 연구에서 제작된 12kW 소형 발전 시스템은 최고압력 12MPa 최고 온도 70℃의 조건에서 6.98%의 효율이 나타나도록 설계되었다. 본 실험 장치를 소형 Brayton cycle과 비교했을 때 약 2% 높은 효율을 가진다는 것을 이론적으로 확인하였고, 사이클 효율을 높이기 위해 최적의 터빈 입구 온도와 압력을 얻었으며, 이 조건에서 IHX(내부 열교환기)의 도입시 18.75%의 최대 효율을 기대할 수 있다는 결론을 도출하였다. 마지막으로, 실험 설비의 태양광 시뮬레이션 결과 5월에는 6.7%, 6월에는 6.26%의 효율로 태양열을 이용할 수 있음을 확인하였다.

• 설비공학논문집
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• 제27권11호
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• pp.581-586
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• 2015

In this study, an analysis was performed on the performance of the solar water heating system with geo-thermal heat pump for a detached house. This system has a flat plate solar collector ($8\;m^2$) and a 3 RT heat pump. The heat pump acts as an auxiliary heater of the solar water heating system. These systems were installed at four individual houses with the same area of $100\;m^2$. The monitoring results for one year are as follows. (1) The average daily operating time of the solar system appeared to be 313 minutes in spring (intermediate season), and 135 minutes and 76 minutes in winter and summer respectively. The reason for the short operating time in summer is the high storage temperature due to low water heating load. The high storage temperature is caused by a decrease in collecting efficiency as well as by overheating. (2) The geothermal heat pump as an auxiliary heater mainly operates on days of poor insolation during the winter season. (3) Despite controlling for total house area, hot water consumption varies greatly according to the number of people in the family, hot water usage habits, etc. (4) The yearly solar fraction was 69.8 to 91.5 percent, which exceeds the maximum value of 80% as recommended by ASHRAE. So the solar collector area of $8\;m^2$ appeared to be somewhat greater for the house with an area of $100\;m^2$. (5) The observed annual efficiency of solar systems was relatively low at 13.5 to 23.6%, which was analyzed to be due to the decrease in thermal efficiency and the overheating caused by a high solar fraction.

• Journal of Biosystems Engineering
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• 제27권4호
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• pp.327-334
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• 2002

In this study, energy conversion from thermal energy to mechanical power by using n-pentane was tested and exergy variation, cycle number, water quantity pumped and thermal efficiency were analyzed. The energy conversion was done and the water head could be ten meters on the experimental conditions. The operating temperature range of cycle was recommended to be around the liquid-vapour saturation temperature of the working fluid on the viewpoint of the maximum work. The cycle diagram was analyzed by the exergy analysis. For the constant water head, the cycle number was decreased and the water quantity per day was increased and thermal efficiency become higher when the water quantity per cycle become increasing. For the constant pumping water quantity per cycle, cycle number and the water quantity per day was decreased and the thermal efficiency become higher because the saturation temperature become higher when the water head become higher.

• 태양에너지
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• 제20권4호
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• pp.17-24
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• 2000

Thermal performance of a SAAHPS (Solar and Ambient-air-assisted Heat Pump System) located in KIER is simulated with TRNSYS 14.2. The SAAHPS is composed of dual evaorators, each of which is used as a solar fluid heat source and an air fluid heat source. Polynomial coefficients data for the SAAHPS is supplied with Frigosoft, a program widely used for heat pump modeling. In general, collector area and storage volume are 2 key parameters in SAAHPS thermal performance. A parametric study is performed in this study to assess sensitivity of collector area and storage volume in SAAHPS. We concluded that firstly collector area and storage volume are the primary variables in SAAHPS thermal performance, secondly COP of SAAHPS is higher than that of conventional heat pumps. Therefore. collector efficiency can be enhanced swith SAAHPS during a heating season.

• 한국축산시설환경학회지
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• 제9권2호
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• pp.69-78
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• 2003

태양열을 동력원으로 하여 열에너지를 동력으로 변환, 물을 양수할 목적으로 저온 상변화물질인 펜탄을 작동물질로 하는 에너지변환장치를 제작하여 실험하였다. 장치는 각부의 크기를 그 기능과 상호작용 원리에 따라 논리에 맞게 최적 설계하였다. 장치의 제작 후 실험을 통하여 그 운전 특성을 분석하여 성능향상에 필요한 자료를 획득하고자 하였다. 작동물질인 펜탄을 가열하는 탱크 내부의 온도는 사이클 경과시간에 따라 약 $40­86^{\circ}C$ 범위에서 변동하고 있었으며, 물탱크내 온도 약 $23­24^{\circ}C$, 공기탱크 내 온도 $22­23.5^{\circ}C$ 범위에서 비교적 일정하게 유지되고 있었다. 응축기내의 온도와 냉각수출구 온도는 냉각수입구 온도수준에 따라 정의 상관관계로 변하고 있는 것을 알 수 있었으며, 또한 열 교환 능력도 냉각수 온도수준이 낮을수록 커진다는 것을 확인하였다. 물탱크 내 온도와 응축기내 온도가 상당히 차이가 나므로 물탱크와 응축기와의 연결거리를 최소화하고 연결파이프 크기를 큰 것으로 하여 내부물질이동 저항을 줄이는 것이 바람직하다는 것을 알 수 있었다. 실험 중 양수량은 1.6­2.4 liter로 나타났으며, 냉각시간의 수준에 따른 물탱크내의 흡입물높이 상승은 차이를 나타내지 않았다. 응축기로부터의 냉각수 배출파이프가 연장되지 않은 경우 냉각수 유량이 5.9 liter/min 이었으나 연장파이프가 있을 때는 2.3 liter/min으로 나타났다. 이러한 현상에서 양수하는 물의 온도가 낮고 유량이 부족한 경우에는 연장파이프를 이용하는 것이 좋고, 냉각수치 양은 풍부하지만 그 온도가 낮지 않은 경우에는 연장파이프를 이용하지 않는 것이 좋다는 사실을 알 수 있다. 실험에서의 응축기내 냉각수의 최대 열교환량은 95.75 kJ/min로 나타났다. 작동물질가열탱크와 기액 분리탱크 내의 압력은 0.13­0.14 MPa.a, 물탱크와 응축기내의 압력은 약 0.11 MPa.a정도로 나타났다.

• Journal of Biosystems Engineering
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• 제29권6호
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• pp.521-530
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• 2004

The solar powered water pump is very ideal equipment because solar power is more intensive when the water is more needed in summer and it is very helpful in the rural area, in which electrical power is not available. The average solar radiation power is $3.488\;kWh/(m^2{\cdot}day)$ in Korea. In this study, the experimental system of the water pump driven by the radiation energy were designed, assembled, tested and analyzed fur realizing the solar powered water pump. Energy conversion ken radiation energy to mechanical energy by using n-pentane as operating material was done and the water pumping cycles were able to be continued. The quantity of the water pumped per cycle ranged from 2 L to 10 L depending on the level of the valve open area far the vapour supply. The average quantity was about 4,366 cc. The thermal efficiency was about $0.018\%$. The pressure level of the n-pentane vapour in flash tank was about $110\~150\;kPa$ and that in the water tank was $93\~130\;kPa$. The pressure in the condenser during cycles was maintained as about 70 kPa. The condensation of the n-pentane vapour in the water tank was increased with the cycles even though the internal and external insulation were done. Air tank performance was better with increasing of the water piston displacement and the water could be pumped with the water piston displacement becoming higher than 6,500 cc.