• 대한조선학회논문집
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• 제31권4호
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• pp.157-166
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• 1994

최근의 배는 에너지절약을 도모하기 위하여 디이젤기관이 대구경 장행정 소수실린더 저속회전화 추세에 있기 때문에 기진력이 커지고 있다. 이와같은 결과로 추진축계에 과잉비틂진동응력이 작용하게 되어 선박운항에 지장을 줄 정도의 플로렐러축의 결손사고가 종종 발생하곤 한다. 현재까지의 추지축계에 대한 설계 및 비틂진동해석은 대부분 축계의 비틂기진력이 확정적이란 가정하에 수행되어 왔다. 이와 관련하여 축계 비틂기진력의 불규칙성의 영향을 고려한 확률적 비틂진동해석에 관한 연구가 이루워지고 있다. 본 연구에서는 기관기진력의 확률변수를 고려하여 추진축계의 강제 비틂진동의 확률적 해석에 대한 새로운 방법을 제시하였다. 확률적 해석에 응답면이론과 Monte Carlo 시뮤레이션 방법이 이용되었다. 본 해석방법의 타당성 여부를 확인하기 위하여 Nikolaidis 등이 사용한 시산대상선에 대한 일련의 수치계산을 수행하고, 그 결과를 Nikolaidis 등의 연구결과와 비교 검토하여 본 결과 비교적 잘 일치하고 있음을 미루어 보아 본 해석방법이 타당성이 확인되었다.

• Journal of Advanced Marine Engineering and Technology
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• 제18권2호
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• pp.113-121
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• 1994

Since two oil shocks in 1970s, all of engine makers have persevered in their efforts to reduce specific fuel consumption and to increase engine power rate as much as possible in marine diesel engines. As a result, the maximum pressure in cylinders of these engines has been continuously increased. It causes direct axial vibration. The axial stiffness of crank shaft is low compared to old types of engine models by increasing the stroke/bore ratio and its major critical speed might occur within engine operation range. An axial damper, therefore, needs to be installed in order to reduce the axial vibration amplitude of the crankshaft. Usually the main critical speed of axial vibration for the propulsion shafting system with a 4-8 cylinder engine exists near the maximum continuous revolution(MCR). In this case, when the damping coefficient of the damper is increased within the allowance of the structural strength, its stiffness coefficient is also increased. Therefore, the main critical speed of axial vibration can be moved beyond the MCR. It has the same function as a conventional detuner. However, in the case of a 9-12 cylinder engine, the main critical speed of axial vibration for the propulsion shafting system exists below the MCR and thus the critical speed cannot be moved beyond the MCR by using an axial damper. In this case, the damping coefficient of an axial damper should be adjusted by considering the range of engine revolution, the location and vibration amplitude of the critical speed, the fore and aft vibration of the hull super structure. It needs to clarify the dynamic characteristics of the axial vibration damper to control the axial vibration appropriately. Therefore authors suggest the calculation method to analyse the dynamic characteristics of axial vibration damper. To confirm the calculation method proposed in this paper, it is applied to the propulsion shafting system of the actual ships and satisfactory results are obtained.

• 한국마린엔지니어링학회:학술대회논문집
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• 한국마린엔지니어링학회 2000년도 춘계학술대회 논문집(Proceeding of the KOSME 2000 Spring Annual Meeting)
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• pp.60-71
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• 2000

When the crankshaft of Diesel engine has more than 3 throws which are arranged in a different plane its vibration induces coupled motions especially the coupled torsional and axial vibration. Nowadays the torsional vibration which is influenced rather weak than axial one can be theoretically calculated fairly accurately but theoretical calculation results of the axial vibration which is influenced strongly from torsional vibration is not so good. To get accurate calculation results of axial vibration coupled axial-torsional vibration must be treated. in this investigation coupled effects of vibration of Diesel engine propulsion shafting are analyzed theoretically and some more simple calculation methods are also studied. On this first report effects of coupling on natural frequencies and their modes are mainly studied setting the each mass in 4 degrees of freedom. later this problem may be studied again by setting each mass as 6 degrees of freedom.

• 한국마린엔지니어링학회:학술대회논문집
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• 한국마린엔지니어링학회 2001년도 춘계학술대회 논문집
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• pp.173-179
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• 2001

The torsional or axial critical vibration of the order coinciding with the number of propeller blades is simultaneously excited by the harmonic tangential or radial forces acting on the crank shaft and by the harmonic of the same order from the propeller. The exciting torque of propeller is relatively small comparing with that of crank side, but the exciting force of propeller rather larger than that of crank shaft. With this situation, the exciting force of propeller cannot neglect if the axial vibration of propulsion shafting is calculated. With the propeller in its optimal angular position, i.e. its excitation effect opposed to that of the engine, the stresses at the critical revolution will largely cancel themselves out. In this paper, a method of optimizing the angular propeller position with regard to torsional and axial vibration is studied. The optimal relative angle is determined theoretically by calculation results of coupled torsional-axial vibration.

• Journal of Advanced Marine Engineering and Technology
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• 제30권7호
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• pp.800-807
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• 2006

This paper introduces the hull deflection analysis method by using the direct measurements. Accordingly, this paper demonstrates how the hull deflection data is obtained by the reverse calculations using the bending moments from the stain gauge and bearing reactions from jack-up method. Where the hull deflection data provided by this research is used for the shafting alignment calculations for identical or similar vessels, shafting failures due to hull deflections can be minimized. It will also save time and expenses associated finite element method to predict hull deflections.

• Journal of Advanced Marine Engineering and Technology
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• 제24권6호
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• pp.7-14
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• 2000

Nowadays, the viscous damper using high viscosity oil was much to be used for engine shafting system to reduce the excessive additional stress by torsional vibration. In general, it was assumed that the viscous damper could be modelled having only damping coefficient, that is to say, whose stiffness be ignored. But it is found that there exists a jump phenomenon, as a kind of non-linear vibration, in the actual engine shafting system with a damper of high viscosity. Therefore the damper ring and the casing are modelled as two mass elastic system with a complex viscosity. Also, to analyze a non-linear phenomenon, it is assumed that the viscous damper has a linear stiffness coefficient in proportion to the angular amplitude and a non-linear stiffness coefficient in proportion to cube of the angular amplitude. For the analysis, Quasi-Newton method with BFGS(Broyden-Fletcher-Goldfarb-Shanno) formula is used. Both calculated and measured values are provided in this paper which confirm the possibility of applying non-linear theory to engine shafting system with viscous damper.

• 한국소음진동공학회:학술대회논문집
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• 한국소음진동공학회 2006년도 추계학술대회논문집
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• pp.776-785
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• 2006

Ship builder's requirement for a higher power output rating has lead to the development of super large two stroke low speed diesel engines. Usually a large-sized bore ranging from 8-14 cylinders, this engine group is capable of delivering power output of more than 100,000 bhp at maximum continuous rating. Other positive aspects of this engine type include higher thermal efficiency, reliability, durability and mobility. This all playa vital role in meeting the propulsion requirement of vessels, specifically for large container ships, of which speed is a primary concern to become more competitive. Consequently, this also resulted in the modification of engine parameters and new component designs to meet the consequential higher mean effective pressure and higher maximum combustion pressure. Even though the fundamental excitation mechanism unchanged, torsional vibration stresses in the propulsion shafting are subsequently perceived to be higher. As such, one important viewpoint in the initial engine design is the resulting vibration characteristic expected to prevail on the propulsion shafting system(PSS). This paper investigated the torsional vibration characteristics of these super large engines. For the two node torsional vibration with a nodal point on the crankshaft, a tuning damper is necessary to reduce the torsional stresses on the crankshaft. Hence, the tuning torsional vibration damper design and compatibility to the shafting system was similarly reviewed and analyzed.

• 수산해양기술연구
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• 제18권1호
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• pp.39-46
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• 1982

박용추진축계의 최적배치상태를 얻기 위해 선형계획법에 의한 최적배치 전산프로그램을 개발했으며, 여기에 필요한 자료들은 삼차모먼트정리를 매트릭스산법으로 전산처리해서 얻어냈고, 이 프로그램의 신속성을 확인하기 위해 모형축의 계산치와 스트레인 게이지에 의한 실측치를 비교하고, 실선축계에 적용한 결과 다음과 같이 요약할 수 있었다. 1. 최적배치의 필수자료인 직선지지상태의 반력 및 반력경향계수를 구하는 전산프로그램을 개발해서, 모형축에 적용한 결과, 실험치와 계산치가 거의 일치했고, 실선축에 대해 계산한 값도 타 프로그램으로 계산한 것과 거의 비슷했다. 2. 본 논문의 스트레인게이지에 의한 축계상태치의 계측방법은 실선축의 배치상태의 조정시에 매우 효과적으로 활용할 수 있을 것이다. 3. 최적배치의 전산프로그램을 실선축에 적용한 결과, 제한조건을 만족하려면, 지지베어링들을 상당량 수직방향으로 조절해야 함을 알 수 있었다. 따라서 최적배치의 관건은 배치계산에 필요한 정확한 자료와 제한조건을 구하는 것이라 할 수 있겠다.

• 해양환경안전학회지
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• 제13권4호
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• pp.119-125
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• 2007

현재 중소형선박의 동력전달용 스테인리스 추진축계가 많이 사용되고 있으나 선미를 통과하는 선미관 패킹부, 베어링이 작용하는 접촉부 등에서 마모, 축의 재질불량이나 설계 불량으로 인하여 축이 절손되는 경우가 많다. 프로펠러축이 과다마모 또는 절손으로 파단시 새로운 축으로 전환하고 있으나 축을 새것으로 구입하려면 주문, 제작 등에 따라 상당한 비용이 소요된다. 또한 축을 육성 용접하는 경우는 해양수산관청의 승인을 득하도록 되어 있으나 지금까지 승인이 된 경우가 없었다. 따라서 이 연구에서는 직접 스테인리스 재료를 육성 용접하면서 모재와 비교하여 용접에 따른 금속조직의 변화, 결함의 계측 등을 규명하여 해양수산관청의 승인에 필요한 용접 절차, 검사에 필요한 사항 등을 검토하였다.

• 한국소음진동공학회:학술대회논문집
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• 한국소음진동공학회 2010년도 춘계학술대회 논문집
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• pp.574-575
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• 2010