Application of Elastomeric Components for Noise and Vibration Isolation in the Automotive Industry

Lewitzke, Craig; Lee, Ping

doi:10.4271/2001-01-1447

Cited by 44 publications

(23 citation statements)

References 2 publications

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“…An insulator is a core part which prevents the road surface vibrations and noises from reaching the car body [15,16]. The noise evaluation test method developed in this study quantitatively confirmed the effects of the insulator performance degradation on noises.…”

Section: Effects Of Insulator Performance Degradation On Noises Tsupporting

confidence: 58%

Study on durability and reliability of strut type suspension noise based on experimental methods

et al. 2012

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When cars are released from the factory, strut noises are very small and therefore it is difficult to perceive them. As the use time and travel distance increase, however, strut noises get larger so as to cause users much uneasiness. The noises generated at the field include engine noises and flow noises and therefore it is difficult to clearly discern the noises generated from struts. This study developed a test method which can reproduce field strut noises in the lab. Using the newly developed noise evaluation test, this study analyzed the effects that insulator performance degradation and failure can have on car noises. The study also confirmed that the insulator durability test by the simple back-and-forth motion cannot completely reflect the state of the parts failure in the field. Based on this, the study also confirmed that field noises can be reproduced through a durability test that considers heat aging.

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Section: Effects Of Insulator Performance Degradation On Noises Tsupporting

confidence: 58%

Study on durability and reliability of strut type suspension noise based on experimental methods

et al. 2012

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“…C 10 , C 01 ¼ Mooney-Rivlin material constants d, d min , d max ¼ Time-varying displacement and minimum and maximum values I 1 , I 2 ¼ Strain invariants of the right Green deformation tensor k, n ¼ Material constants of the equivalent strain amplitude parameter N f , N f,max , N f,min ¼ Average fatigue life and maximum and minimum life for a given loading case R ¼ Strain ratio, ε min /ε max R d ¼ Displacement ratio, d min /d max r 2 ¼ Correlation coefficient V ¼ Spatial stretch tensor W ¼ Strain energy density β ¼ Material constant for the equivalent parameter {ε ij } ¼ Logarithmic strain tensor ε, ε min , ε max ¼ Logarithmic normal strain and minimum and maximum strain ε m , ε a ¼ Mean strain and strain amplitude ε À1 ð Þ m ; ε À1 ð Þ a ¼ Mean strain and strain amplitude corresponding to R = À1 ε eq ¼ Equivalent strain parameter, which has the same value as ε Rubbers offer the advantage of withstanding very large strains without permanent deformation or fracture, which makes them ideal for many applications such as tires, vibration isolators, accessory drive belts and so on. 1 Some of the behaviours of the rubbers are comparable with those of commonly used linear elastic materials such as conventional metals. For example, rubbers exhibit limited fatigue strength when subject to tearing energy below a critical value.…”

mentioning

confidence: 80%

“…Rubbers offer the advantage of withstanding very large strains without permanent deformation or fracture, which makes them ideal for many applications such as tires, vibration isolators, accessory drive belts and so on . Some of the behaviours of the rubbers are comparable with those of commonly used linear elastic materials such as conventional metals.…”

Section: Introductionmentioning

confidence: 99%

A method to develop a unified fatigue life prediction model for filled natural rubbers under uniaxial loads

Wang

Shangguan

Rakheja

et al. 2013

Fatigue Fract Eng Mat Struct

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Rubber components are widely used in many fields because of their superior elastic properties. Fatigue failures, commonly encountered in rubber components, however, remain a critical issue. In this study, the effect of strain ratio R on the fatigue life of filled natural rubbers used in automotive mounts is investigated experimentally and numerically. A uniaxial tension/compression fatigue experiment was conducted on dumb‐bell cylindrical rubber specimens subject to loads representing different R ratios. The experimental fatigue data are used to formulate two preliminary fatigue models based on peak strain and strain amplitude as the damage parameters. The deficiencies of these two models in predicting fatigue life over a wide range of R ratios are discussed, and an alternative life prediction model is proposed. The proposed model incorporates the effect of R ratio using an equivalent strain amplitude. It is shown that the proposed model could effectively predict fatigue life over a wide range of R ratios with an improved accuracy.

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“…Elastomeric joints are widely used in vehicle isolation systems and their geometries are shaped to provide favorable properties in certain directions based on the diagonal terms [1,2]. Nonetheless, non-diagonal (coupling) terms are often unknown though they are intrinsic to the design of complex automotive assemblies [3,4].…”

Section: Introductionmentioning

confidence: 99%

Comparative Assessment of Multi-Axis Bushing Properties Using Resonant and Non-Resonant Methods

Noll

Dreyer

Singh

2013

SAE Int. J. Passeng. Cars - Mech. Syst.

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Shaped elastomeric joints such as engine mounts or suspension bushings undergo broadband, multi-axis loading; however, in practice, the elastomeric joint properties are often measured at stepped single frequencies (non-resonant test method). This article helps provide insight into multi-axis properties with new benchmark experiments that are designed to permit direct comparison between system resonant and non-resonant identification methods of the dynamic stiffness matrices of elastomeric joints, including multi-axis (non-diagonal) terms. The joints are constructed with combinations of inclined elastomeric cylinders to control non-diagonal terms in the stiffness matrix. The resonant experiment consists of an elastic metal beam end-supported by elastomeric joints coupling the in-plane transverse and longitudinal beam motion. The dynamic stiffness and loss factors of the elastomeric cylinders are measured in a non-resonant commercial elastomer test machine in shear, compression, and inclined configurations and a coordinate transformation is used to estimate the kinematic non-diagonal stiffness terms. Strong agreement is found for both dynamic stiffness and loss factors between the resonant and non-resonant methods at small displacements.

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Application of Elastomeric Components for Noise and Vibration Isolation in the Automotive Industry

Cited by 44 publications

References 2 publications

Study on durability and reliability of strut type suspension noise based on experimental methods

Study on durability and reliability of strut type suspension noise based on experimental methods

A method to develop a unified fatigue life prediction model for filled natural rubbers under uniaxial loads

Comparative Assessment of Multi-Axis Bushing Properties Using Resonant and Non-Resonant Methods

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