• Journal of the KSME
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• v.30 no.6
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• pp.548-554
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• 1990

대체에너지 기관으로서 요구되는 조건을 갖춘 스터링엔진의 이해를 돕기 위하여 기본원리, 개 발현황, 개발상 문제점 등의 기본사항을 소개하였다. 내연기관과는 달리 외연기관인 스터링엔 진은 작동유체가 밀폐공간 내에서 고. 저온 양 영역을 이동하면서 압력차를 발생시켜 일을 형성 하는 과정을 밟기 때문에 고온. 고압일수록 높은 출력이 예상되며, 전열성능과 작동저항면에서 수소나 헬륨과 같은 저분자량의 가스가 작동체로 채택되기 때문에 작동유체의 누기(leakage) 및 크랑크실의 냉각 윤활유의 작동공간으로의 누유 등은 스터링엔진의 출력 저하에 가장 큰 요인 으로 작용한다. 마찰 등 기계적 손실의 저감기술, 속도제어기술, 용도에 따른 엔진 형식 설계 기술, 구성부품 성능향상을 위한 요소기술 등의 개발이 중요한 과제가 되고 있으며, 이상 소개한 내용이 관심있는 많은 분들의 스터링엔진 연구나 이해에 도움이 될 수 있기를 바란다.

• Cement
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• s.121
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• pp.26-29
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• 1990

• Journal of the korean Society of Automotive Engineers
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• v.9 no.6
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• pp.1-7
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• 1987

스터링 엔진은 1816년 로버트 스터링에 의해 발명된 밀폐형 외연기관이다. 초기에는 왕복형 증기기관과 더불어 구미제국에 널리 보급되었으나, 실용화 기술의 부족으로 인한 잦은 고장과 가솔린 및 디젤엔진의 발명으로 인해 자취를 감추었다. 그 후 1938년 네덜란드의 필립스사(Philips Co.)에 의해 연구가 재개되고, 간헐적으로 진행되다가 최근에 연료의 다양화, 에너지절약, 환경보존 등에로의 강한 요구와 재료기술 및 생산기술의 진보로 인하여 이 엔진이 다시 주목되어 구미, 일본 등에서 연구 개발되고 있다. 미국에서는 1978년부터 정부적 차원에서 개발을 시작하여 일부는 상용화되어 있고, 일본에서는 1982년 이래로 계속 개발을 수행하고 있고, 그 외에도 유럽의 여러 나라들에서도 활발한 연구가 진행되고 있다.

• Journal of Advanced Marine Engineering and Technology
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• v.17 no.4
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• pp.63-72
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• 1993

This paper deals with the determination of the main design parameters on the efficient .betha. type stirling engine for marine use having the rhombic drive mechanism. This studies are performed as following. (1) The characteristics of $\beta$ type stirling engine, (2) The kinds of driving mechanism, (3) The structure of rhombic drive mechanism, (4) The reasons of making choice of the rhombic drive mechanism in $\beta$ type stirling engines, (5) Ultimately the purpose of this paper is to determine the main design parameters of $\beta$ type stirling engines for marine use having the rhombic drive mechanism. Finally, We can adapt the result of this paper in designing of $\beta$ type stirling engine driven by the rhombic drive mechanism.

• 기계와재료
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• v.19 no.3 s.73
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• pp.50-63
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• 2007

• Korea Journal of Geothermal Energy
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• v.8 no.1
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• pp.41-49
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• 2012

• Proceedings of the KSME Conference
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• 2000.04b
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• pp.199-204
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• 2000

A low temperature differential model stirling engine is manufactured, and its operation characteristics are measured and analyzed by SIMPLE analysis model, in which heat transfer processes are simply considered. The heat transfer coefficients between working fluid and heat sources in the analysis are estimated by comparing the P-V diagrams by experiment and by analysis. This result may be very useful for further design and manufacture of model Stilting engines as well as real engines because it provides a comparatively correct predictions of the operation conditions and power output. It will be also conveniently used as an educational material for mechanical engineering students because it can be a nice example of optimal design process to decide the phase angle and compression ratio of engine design with a simple but realistic simulation.

• Korean Journal of Air-Conditioning and Refrigeration Engineering
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• v.3 no.4
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• pp.231-240
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• 1991

A design method has been developed for a Stirling engine with a tubular heater and cooler and a screen type regenerator. This paper provides a design procedure to determine the thermodynamic states and the geometric configurations of the Stirling engine for residential heat pumps. The major design is concerned with the working spaces, i.e. compression and expansion spaces and the heat exchangers such as the heater, the cooler and the regenerator. The Schmidt analysis has been employed to obtain the mass flow rates and heat transfer requirements of the system. The performance analysis of a model Stirling engine was performed by Martini-Weiss program to prove the validity of this design method. The results obtained indicate that this design method is valid for the Stirling engine conceptual design and performance analysis.

• 한국태양에너지학회:학술대회논문집
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• 2008.04a
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• pp.227-232
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• 2008

Stirling engine for solar thermal power is an essential part of Dish-Stirling system which generates electricity by using direct normal irradiation and will go into commercialization in near future. For the Stirling engine used in this study is Solo 161 model the capacity of which is 10 kWe and was already used for the Dish-Stirling system of KIER in Jinhae. The receiver of Stirling engine absorbes concentrated solar radiation and transfer it to working fluid of Hydrogen. The working condition of striling engine is high temperature and high pressure to make high efficiency. Therefore the receiver should stand against high temperature of above 800 $^{\circ}C$ and high pressure of max. 150 bar with good performance of heat transfer. The receiver is composed of 78 Inconel tubes of 1/8" with thickness of 0.71 mm and two reserviors which is connected with two cylinders. In order to know the charaterristics of heat transfer of Stirling engine receiver, simulation on the heat transfer of the receiver of Solo 161 is conducted by using CFD code of Fluent. The heat flux on the receiver surface has a shape of Gaussian distribution so, it is necessary to simulate a whole receiver. However, It is difficult and time consuming to simulate the whole receiver that one tube with different heat flux conditions are considered in this study. From the simulation results, heat transfer charateristics of receiver are observed and tube wall and fluid temperature and heat transfer coefficient are obtained and compared with the calculated results from Dittus-Boelter's correlation.

• 한국태양에너지학회:학술대회논문집
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• 2009.11a
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• pp.62-67
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• 2009

This paper describes the characteristics of scroll type stirling engine receiver. Scroll type stirling engine operated scroll compressor and expander instead of piston. Pass dimension of the receiver was $14(W){\times}14(H)$ mm and total pass length was 5,049 mm. External dimension of the receiver was $300{\times}300mm$. The experimental facility consisted of parabolic dish concentrator, compressor to supply air, triplex air filter, and flowmeter. In this study, basic experimental conditions were set at a inlet pressure of 5 bar and volume flow rate of $25m^3/hr$. As a result, air temperature in receiver at each measuring position of point 1, 2, 3 were $241^{\circ}C$, $465^{\circ}C$, and $542^{\circ}C$ respectively at inlet pressure of 5.5 bar and volume flow rate of $24.6m^3/hr$. As DNI increasing, heat transfer coefficient of the receiver changed from $695W/m^2K$ to $827W/m^2K$. Average heat transfer coefficient of receiver in the experiment was $798W/m^2K$. In addition, receiver efficiency became about 83%.