• Proceedings of the Korean Society of Marine Engineers Conference
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• 2006.06a
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• pp.55-56
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• 2006

냉매 충전량과 이차유체의 입구조건은 $CO_2$용 열펌프시스템의 성능실험에서 중요한 제어변수이다. 따라서, 열펌프사이클의 적용과 난방성능 향상을 위해 제어변수의 특성을 조사하는 것이 필요하다. 본 논문에서, $CO_2$용 열펌프 사이클의 성능 실험은 여러 가지 냉매 충전량에서 이차유체 입구조건에 변화를 주어 수행 되었다. 실험결과, 난방COP는 냉매 충전량이 증가함에 따라 1158g의 냉매 충전량에서 최대가 되었다가 감소하는 경향이 나타나며, 이는 COP가 최대가 되는 냉매충전량이 존재함을 나타낸다. 또한, 난방성능은 가스쿨러내 이차유체의 질량유량의 증가에 따라 증가하였다. 가스냉각기내 2차유체의 입구은도가 $10^{\circ}C$에서 $40^{\circ}C$로 증가하면, 난방용량, 압축일량, 토출압력은 각각 -8.57%, -35.89%, 32.78%로 변화했으며, 증발기 2차유체의 입구 온도가 감소하였을 때 난방COP는 감소하는 경향을 보였다.

• 한국신재생에너지학회:학술대회논문집
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• 2011.05a
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• pp.81-81
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• 2011

본 연구는 $CO_2$를 냉매로 하는 급탕용 히트펌프 성능특성을 평가하는 시험 평가법에 대하여 국내 실정에 맞는 시험평가법을 개발하기 위한 목적으로 기존 $CO_2$ 급탕용 히트펌프의 평가방법을 분석하고자 한다. 현재 $CO_2$ 급탕기 또는 급탕용 히트펌프 제품은 일본에서 2000년 초반부터 에코큐트라는 제품으로 일본 급탕용 난방기기로 판매되고 2009년을 기초로 누적판매 대수가 150만대에 이르고 있다. 국내에는 2008년 후반부터 공기열원 또는 폐열원 등을 이용한 급탕용 히트펌프 제품이 일부 수입되어 목욕탕, 찜질방과 같은 숙박업소용으로 판매되고 있는 추세이다. 국내에서는 급탕용 열펌프의 제품의 정의가 아직 정립되지 않고 이에 대한 시험평가방법이 전무한 실정이기 때문에 현재 일본의 가정용 열펌프 급탕기의 규격을 토대로 실제 급탕용 열펌프의 시험을 수행하여 급탕용 히트펌프의 급탕성능특성을 평가하는 방법을 개발하고자 한다. 시험시료는 일본에서 판매되고 있는 급탕용 히트펌프(D사) 제품을 이용하였으며, 현재 일본에서 사용하고 있는 JRA4050 규격에 의해 급탕성능평가를 진행하고 급탕성능평가 지표 등을 국내 유사조건과 급탕성능특성의 평가방법을 비교분석하였다.

• The Magazine of the Society of Air-Conditioning and Refrigerating Engineers of Korea
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• v.38 no.12
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• pp.73-80
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• 2009

• 기계와재료
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• v.23 no.3
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• pp.126-136
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• 2011

지구 온난화에 따라 이산화탄소를 비롯한 온실가스의 감축은 세계적인 관심사이며 모든 산업 분야의 1차 목표가 되고 있다. IEA는 시스템의 고효율화 기술이 2035년까지 목표 감축량의 50% 이상을 달성할 수 있는 기술로 판단하고 있다. 건조기는 대부분의 산업 분야에서 사용되는 필수기계이고 에너지 다소비 기기이므로 건조기의 에너지 효율을 향상시키는 것을 온실가스 감축에 있어서 중요한 부분이라 할 수 있다. 열펌프 건조기는 건조기 중에서도 가장 높은 효율을 달성할 수 있는 장치로서 산업 분야에 활용된다면 큰 역할을 담당할 것으로판단된다. 특히 산업의 많은 분야에 활용되기 위해서는 고온용 열펌프 건조기의 개발이 매우 중요하다. 최근에 국내외에서 고온용 열펌프에 대한 관심이 증가하고 있고, 개발이 일부 진행되었으나 많은 산업분야에 적용 가능하도록 기술을 성숙시키려면 지속적인 연구개발이 필요하다.

• Korean Journal of Air-Conditioning and Refrigeration Engineering
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• v.15 no.12
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• pp.987-995
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• 2003

The performance of a residential heating and cooling system with $CO_2$ is predicted by using a cycle simulation model. The simulations are conducted by varying design parameters and operating conditions. The efficiency of the transcritical cycle can be improved by utilizing the advantages in heat transfer characteristics of $CO_2$ and developing microchannel indoor and outdoor heat exchangers. For the designed system of this study, the predicted COP of the heat pump system is approximately 3.5 in the heating mode and 3.0 in the cooling mode. The predicted optimal discharge pressure for the heat pump system is approximately 11 MPa in the heating mode and 9 MPa in the cooling mode.

• Korean Journal of Air-Conditioning and Refrigeration Engineering
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• v.23 no.10
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• pp.678-686
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• 2011

Simulation study on the operating characteristics in the solar hybrid R744 heat pump system for residential applications was carried out with heat pump operating temperature, outdoor temperature and solar radiation. As a result, collector operating time is decreased by 1.5 hours due to the increase of water temperature in the heat storage tank when the heat pump operating temperature rises. Heat pump operating time is reduced by 19.4% owing to the high temperature of a heat storage tank. Besides, indoor heating time is decreased from 10.3 to 5.5 hours as the indoor temperature increases from $3^{\circ}C$ to $11^{\circ}C$. In addition to, when the solar radiation rises from 10 to 20 MJ/$m^2$, the maximum outlet temperature of a solar collector is increased from $65^{\circ}C$ to $71^{\circ}C$.

• Transactions of the Korean Society of Automotive Engineers
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• v.17 no.2
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• pp.126-131
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• 2009

A $CO_2$ heat pump system was designed for both cooling and heating in the cabin of electric vehicles, hybrid vehicles or fuel cell vehicles, In this study, the performance characteristics of the heat pump system without any supplementary heating device were analyzed and the heating performance was compared with the cooling performance for various operating conditions. Experiments were carried out by changing the speed of electric drive compressor, the air flow rate of interior heat exchanger and the air inlet temperature and speed of exterior heat exchanger. Therefore, the cooling/heating capacities and the corresponding COPs are quantified. Also, the heat pump system showed an improved performance for the cooling operation and the heating operation. In this study, the experimental results can be used to evaluate the effect of system design changes on system performance as well as the development of a highly efficient heat pump system.

• Journal of Advanced Marine Engineering and Technology
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• v.31 no.5
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• pp.558-566
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• 2007

The performance characteristics of water-chilling heat pump using $CO_2$ with respect to variation of refrigerant charge amount was investigated experimentally. An experimental apparatus is consisted of a compressor, a gas cooler, an expansion valve, an evaporator and a liquid receiver. All heat exchangers used in the test rig are counter-flow-type heat exchangers with concentric dual tubes, which are made of copper. The gas cooler and the evaporator consist of 6 and 4 straight sections respectively arranged in parallel, each has 2400 mm length. The experimental results summarize as the followings : As the refrigerant charge ratio of $CO_2$ heat pump system increases, the discharge pressure and compressor ratio increases, but mass flow rate of refrigerant decreases. Also the compressor work increases with the increase of refrigerant charge ratio. However, the heating and cooling capacity of $CO_2$ heat pump decreases as the refrigerant charge ratio increases. The maximum heating COP of $CO_2$ heat pump system presented at 0.25 refrigerant charge ratio. It is possible to confirm the optimum charge ratio of $CO_2$ heat pump system by the viewpoint of heating COP.

• Journal of Power System Engineering
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• v.11 no.1
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• pp.63-69
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• 2007

The evaporation pressure drop of $CO_2$ (R-744) in a horizontal tube was investigated experimentally. The main components of the refrigerant loop are a receiver, a variable-speed pump, a mass flow meter, a pre-heater and an evaporator (test section). The test section consists of a smooth, horizontal stainless steel tube of 4.57 mm inner diameter. The experiments were conducted at saturation temperature of $-5^{\circ}C\;to\;5^{\circ}C$, and heat flux of 10 to $40kW/m^2$. The test results showed that the evaporation pressure drop of $CO_2$ are highly dependent on the vapor quality, heat flux and saturation temperature. The measured pressure drop during the evaporation process of $CO_2$ increases with increased mass flux, and decreased saturation temperature. The evaporation pressure drop of $CO_2$ is much lower than that of R 22. In comparison with test results and existing correlations, the best fit of the present experimental data is obtained with the previous correlation. But existing correlations failed to predict the evaporation pressure drop of $CO_2$. Therefore, it is necessary to develop reliable and accurate predictions determining the evaporation pressure drop of $CO_2$ in a horizontal tube.

• Journal of Advanced Marine Engineering and Technology
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• v.31 no.5
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• pp.543-551
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• 2007

The performance characteristics of water-chilling heat pump using $CO_2$ with respect to variation of inlet temperature and mass flow rate of secondary fluid was investigated experimentally. An experimental apparatus is consisted of a compressor, a gas cooler, an expansion valve, an evaporator and a liquid receiver. All heat exchangers used in the test rig are counter-flow-type heat exchangers with concentric dual tubes, which ate made of copper. The gas cooler and the evaporator consist of 6 and 4 straight sections respectively arranged in parallel, each has 2.4 m length. The experimental results were summarized as the followings : As inlet temperature of secondary fluid in the gas cooler increases from $10^{\circ}C$ to $40^{\circ}C$, the compressor work, heating capacity and heating COP were varied to 37.8%, -13%, -35.9%, respectively. The heating capacity, compressor work, heating COP were turned into 23.3%, 6.42%, 13.1%, respectively when ass flow rate of secondary fluid in the evaporator increases from 70 g/s to 150 g/s. The above tendency is similar with performance variation with respect to temperature variation of secondary fluid in the conventional vapor compression cycle.