• Journal of KSNVE
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• v.9 no.3
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• pp.517-524
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• 1999

Mathematical formulas for multi-dimensional isolation analysis via vibrational power transmission can be derived in a rather simple form when the wave effects of the isolators are completely neglected. With increase of frequency range of interest, however, the wave effects play a very important role and hence cannot be neglected. The formulas get involved accordingly. In this study, a method of equivalent stiffness modeling of the isolators to include the wave effects is proposed in such a way that not only the complexity of the mathematical expressions but also that of experiments of necessity can be reduced. This method is illustratively applied to a two-dimensional vibration isolation system with nonrigid source and base structures.

• Proceedings of the Korean Society for Noise and Vibration Engineering Conference
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• 2008.11a
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• pp.343-347
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• 2008

Design of shape for visco-elastic vibration isolation elements, which are very cost-effective and so popular in many applications is frequently based on experiences, intuitions, or trial and errors. Such traditions in shape design make it difficult for drastic changes or new concepts to come out. In this paper, both topological method and shape optimization method are combined together to find out a most desirable isolator shape efficiently by using two commercial engineering programs. ABAQUS and MATLAB. The procedure is divided into two steps. At the first step, a topology optimization method is employed to find an initial shape. where density of either 0 or 1 for finite elements is used for physical realizability. At the second step, based on the initial shape, finer tuning of the shape is done by boundary movement method. An illustration of the procedure will be presented for a mount of an air-conditioner compressor system and the effectiveness will be discussed.

• Transactions of the Korean Society for Noise and Vibration Engineering
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• v.18 no.12
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• pp.1250-1255
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• 2008

Design of shape fur visco-elastic vibration isolation elements, which are very cost-effective and so popular in many applications is fi?equently based on experiences, intuitions, or trial and errors. Such traditions in shape design make it difficult for drastic changes or new concepts to come out. In this paper, both topological method and shape optimization method are combined together to find out a most desirable isolator shape efficiently by using two commercial engineering programs, ABAQUS and MATLAB. The procedure is divided into two steps. At the first step, a topology optimization method is employed to find an initial shape, where density of either 0 or 1 for finite elements is used fur physical realizability. At the second step, based on the initial shape, finer tuning of the shape is done by boundary movement method. An illustration of the procedure is presented fur a mount of an air-conditioner compressor system and the effectiveness is discussed.

• Journal of Convergence for Information Technology
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• v.11 no.11
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• pp.166-171
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• 2021

An active mount is devised in same geometric constraints with a conventional rubber mount. The proposed mount features the piezoelectric actuator which can be used to reduce the vibration at marine vessels or automotive vehicles. As a first step, a passive rubber mount is adopted and its dynamic characteristics are experimentally evaluated. Based on the geometry of the rubber mount, a rubber element for the active mount is manufactured and integrated with two piezostacks in series, in which the piezostack is operated as an inertial type of actuator. A conventional PID controller featured by the simple and easy implementation, is then designed to attenuate the non-resonant high frequency vibration transmitted from the base excitation. Finally, the control performances of a proposed active mount are evaluated in the wide frequency range and compared with those of the conventional rubber mount.

• Proceedings of the Korean Society of Precision Engineering Conference
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• 2004.05a
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• pp.71-71
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• 2004

일반적으로 동흡진기는 하나의 가진진동수에 의해 진동하는 감쇠가 작은 기계나 구조물에 효과적으로 적용되고 있다 대부분의 동흡진기의 적용 사례는 주 진동이 유발되는 부위, 또는 진동을 억제해야하는 부위에 직접적으로 동흡진기를 부가하여 효과를 얻는 방식을 택하고 있다. 그러나 절연기를 설치 할 수 없는 경우라든지, 절연기로는 한계가 있는 경우, 이미 설치가 완료된 기계 시스템에 절연 변경이 곤란한 경우 또는 국부 진동모드에 대한 진동저감을 할 때는 동흡진기에 대해 보다 일반적인 접근 방법이 필요하며 질량과 스프링계를 부착하기 힘든 경우나 억제시키려는 부위에 설비나 기기의 성능을 저해할 수 있는 경우에는 부득이 그 위치를 변경시켜 줘야 할 경우가 생긴다 할 수 있다.(중략)

• Transactions of the Korean Society for Noise and Vibration Engineering
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• v.13 no.5
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• pp.375-383
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• 2003

For a performance analysis of vibration isolation systems, the concept of vibration power flow can be employed preferably when noise radiated from the supporting structure with finite impedances is of interest. The idea is basically simple to understand and formulas for precise estimation of the vibration power are easy to derive. However, It is often required to simplify the process of experimentation under several assumptions due to instrumental limitations. For an example, rotational degree of freedom has not been well treated in bending vibrations of beam or plate-like structures. Yet, several recent studies showed that the moments and rotations play an important role in power transmission and should be taken into consideration carefully as the frequency range of interest goes to audibly high. Therefore, it is readily agreed that reduction of the noise radiation over the high frequency range can be effectively accomplished by adjusting the rotational stiffness of the isolator without changing the vibration isolator efficiency in low frequency range relevant to the translational stiffness of the isolator In this paper, the vibration power flow approach is applied to an AC motor installed on a finite plate in order to illustrate the contribution of the rotational vibration power to the total vibration power transmission. The effects of rotational stiffness of the isolator on the vibration power transmission are investigated by inserting various shapes of Isolators with different rotational stiffness but with $ame translational stiffness between the motor and the plate. The resultant noise radiation from the plate is presented to verify the proposed approach.

• Proceedings of the Korean Society for Noise and Vibration Engineering Conference
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• 2005.05a
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• pp.231-231
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• 2005

• Journal of KSNVE
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• v.9 no.4
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• pp.795-805
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• 1999

Rubber mounts so called grommets and pipes are two major paths of vibration transmission from a compressor, an important vibration source in an air conditioner, to the whole unit. A procedure of configuring the suction and discharge pipes of the compressor was developed in this paper so as to reduce the vibration transmission through the pipes as well as the grommets. Through investigating the effects of shapes and connecting disrections of pipe elements on vibration transmission, a guideline to configure the pipe layout, which enables to reduce vibration transmission, was proposed. The initial pipe layout by the guideline was optimized with the objective function, minimization of boty vibration transmission and the cost, and with the constraints to yield the final dimensions of the pipes. The procedure not only minimizes the transmitted force to the circumferential devices but enables to eliminate rubber blocks or dampers, which are generally used to avoid resonances of the pipe system.

• Proceedings of the Korean Society of Precision Engineering Conference
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• 2004.05a
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• pp.61-61
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• 2004

벨로우즈는 차량의 배기계나 공장의 덕트 등에 진동 절연을 목적으로 장착되는 부품으로서 제품의 특성상 진동 하중을 많이 받기 때문에 여러 겹으로 설계하는 경우가 많다 또한, 대부분의 제품이 그러하듯이 유한요소해석을 적용하여 제품의 특성을 조기에 평가함으로써 개발의 효율성을 높일 수 있다. 그러나, 여러 겹으로 되어있는 제품의 특성을 그대로 모델링 하였을 때는 유한요소의 수가 지나치게 증가하는 경향이 있기 때문에 해석을 수행하기 어렵다.(중략)

• Proceedings of the Korean Society for Noise and Vibration Engineering Conference
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• 2014.10a
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• pp.208-213
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• 2014

공동주택의 천장구조는 바닥충격음을 변화시키는 영향요소중의 하나이다. 천장구조의 진동응답 특성이 바닥충격음에 영향을 주는 요소를 확인하기 위해 천장구조의 달대를 제거하여 콘크리트 슬래브의 진동이 천장구조에 전달되지 않는 무달대 천장구조를 개발하였다. 달대가 시공된 일반 천장구조와 대비하여 무달대 천장구조의 천장판 가속도와 바닥충격음 레벨을 비교하였다. 무달대 천장구조를 사용함으로서 콘크리트 슬래브의 진동이 천장구조에 전달되는 것을 절연되어 천장구조의 진동응답 증폭을 저감시킬 수 있었으며, 저주파 대역의 바닥 충격음 증폭 또한 저감시킬 수 있었다. 일반 천장구조는 100 Hz 이하에서 천장구조의 진동응답이 증폭되어 저주파 대역 바닥충격음이 증폭되었다.