Dynamics of a group of quasi-zero stiffness vibration isolators with slightly different parameters

Valeev, Anvar

doi:10.1177/1461348418756022

Cited by 15 publications

(6 citation statements)

References 23 publications

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“…The spacing washers height should also be 2f [22]. The static force characteristic of a separate Belleville spring is known to be described by the following nonlinear dependence [21,22]…”

Section: Theorymentioning

confidence: 99%

“…Examples of the two static characteristics obtained from (2) are shown in figure 1a. It is known that The separate Belleville spring dimensions s and f are known to be related both to each other and to the coefficient k, on which the stiffness and the slope angle in the center of the spring static characteristic depend, by the ratio [21,22]:…”

Section: Theorymentioning

confidence: 99%

“…Vibration protection systems capable of implementing the quasi-zero stiffness mode [18] provide a wider frequency range of vibration protection compared to the linear vibration isolators and more effective vibration protection against low-frequency vibrations [19]. Passive vibration protection systems based on the Belleville springs [20], which are also able to provide a quasi-zero stiffness mode [21] in the specified movements range [22] are reliable, simple and durable. To expand the range of quasi-zero stiffness, the number of springs is increased and spacing washers or rings are placed between the springs [22].…”

Section: Introductionmentioning

confidence: 99%

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Use of the Belleville spring package in the vibration protection mechanism of the operator’s seat

Корытов

Shcherbakov

Titenko³

et al. 2022

J. Phys.: Conf. Ser.

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Reducing the vibration effects on the operator of a construction, road and other machines is a relevant objective, since its accomplishing improves the efficiency and accuracy of the work performed by machines and reduces the risk of operators’ occupational diseases. Vibration protection systems with the effect of quasi-zero stiffness are promising. To produce this effect, Belleville springs packages can be used. They are a way to create a simple, reliable and inexpensive passive mechanism of the vibration protection system of the operator’s seat. The influence of the static characteristic center slope of two Belleville springs packages on the maximum acceleration of the load under the sinusoidal kinematic excitation of the seat base movements is investigated. The static characteristic center slope of the spring packages was characterized by the coefficient that affects the type of the static characteristic according to the known analytical expressions for the separate spring force. To obtain the chair acceleration values in a fixed coordinate system, we used a simulation mathematical model developed in the Simscape Multibody package for modeling mechanical systems of the MATLAB mathematical system. The model used blocks of a fixed coordinate system, a sliding joint and a rigid body forming a chain. The maximum acceleration of the chair in a fixed coordinate system was defined during a predetermined period of time at the end of the transition process under the steady state oscillations. When conducting the computational experiment, the specified oscillations amplitude of the chair base and the angular frequency of these oscillations varied. For a proper comparison of the experimental results in the form of graphical dependencies of the maximum acceleration on the amplitude and frequency, the ranges of acceptable and unacceptable arguments combinations were selected for the two spring packages. The combinations of amplitude and frequency were considered unacceptable when the maximum deformation of the spring package went beyond the static characteristic maximum. For the two packages of springs, the acceptable regions were different, therefore their intersection used for the comparative analysis, was obtained. The springs package with a relatively high stiffness in the center of the static characteristic is found out to generally provide better vibration protection of the chair in the entire acceptable range of arguments. Simultaneously, a package with lower stiffness in the center of the characteristic dampens vibrations better in the small amplitudes area, i.e. when operating in the quasi-zero stiffness area.

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“…The spacing washers height should also be 2f [22]. The static force characteristic of a separate Belleville spring is known to be described by the following nonlinear dependence [21,22]…”

Section: Theorymentioning

confidence: 99%

Section: Theorymentioning

confidence: 99%

Section: Introductionmentioning

confidence: 99%

See 1 more Smart Citation

Use of the Belleville spring package in the vibration protection mechanism of the operator’s seat

Корытов

Shcherbakov

Titenko³

et al. 2022

J. Phys.: Conf. Ser.

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show abstract

“…Zhou et al designed a pre-compressed cam-roller mechanism for proposing a QZS torsion vibration isolator [15]. Valeev analyzed the dynamics performance of a group of QZS vibration isolators from the manufacturing perspective, and the analysis results indicated that QZS vibration isolators required high precision at manufacturing [16]. Through imitating both multivertebra structure of bird's neck and gazing stability of head, Deng et al analyzed a multi-layer QZS isolator [17].…”

Section: Introductionmentioning

confidence: 99%

Design and performance analysis of a robot flexible connection device based on quasi-zero-stiffness mechanism

Ju,

Ji,

Liu

2024

Preprint

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For suppressing the vibration excitation transmission from the robot to the elastic component during robotic handling, a new type of quasi-zero-stiffness flexible connection device (QZSCD) is designed. By introducing the tilt linkage on the basis of traditional quasi-zero-stiffness isolator with three oblique springs, the QZSCD can actively adapt to varying load conditions. According to the static equilibrium relationship, the conditions that the QZSCD has zero-stiffness at the equilibrium position are obtained. Then, the optimal structure parameters of the QZSCD are determined based on maximizing the system quasi-zero-stiffness interval. And the quantitative relationship between the angle of the tilt linkage and the load mass is investigated. Furthermore, a unified dynamic equation for the QZSCD under varying load conditions is established. The influences of the structural parameters, the tilt linkage angle, and the load mass on the vibration response and displacement transmission characteristics of the QZSCD are analyzed. Simulation and experimental results indicate that by actively adjusting the tilt linkage angle, the QZSCD can ensure good vibration transmission suppression performance under varying load conditions during the robotic handling of the elastic component.

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“…This isolator possesses high-static-low-dynamic stiffness so that it can maintain the load-bearing capacity with a small static displacement and achieve a lower natural frequency to enlarge frequency ranges of vibration isolation. But, it should be noted that isolators with QZS are very sensitive facilities and if something occurs to cause deviation of its characteristic parameters (e.g., mismatch of the load and negative stiffness parameters) and/or change in the non-linearity properties of its forces (e.g., destruction of the symmetry), then the isolation performance will change dramatically [19][20][21][22]. This situation is particularly true when the amplitude of excitation is not relatively small, and the isolator is exposed to a sustained excitation.…”

Section: Introductionmentioning

confidence: 99%

Non-Linear Vibration Isolators with Unknown Excitation and Unmodelled Dynamics: Sliding Mode Active Control

Zhang¹,

Hu²,

Liu³

et al. 2019

Applied Sciences

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For a class of single-degree-of-freedom non-linear passive vibration isolators with unknown excitation and unmodelled dynamics, two sliding mode control methods-a conventional one and the other using a super-twisting algorithm-were proposed to complement and improve the performances and the robustness of the passive isolators. The proposed control methods only require the estimation of the loading and measured velocities of the isolators. Numerical simulations for a non-linear isolator with quasi-zero stiffness demonstrated that both methods were effective and easy to implement, and the one using a super-twisting algorithm was more promising from the perspective of practical application.

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Dynamics of a group of quasi-zero stiffness vibration isolators with slightly different parameters

Cited by 15 publications

References 23 publications

Use of the Belleville spring package in the vibration protection mechanism of the operator’s seat

Use of the Belleville spring package in the vibration protection mechanism of the operator’s seat

Design and performance analysis of a robot flexible connection device based on quasi-zero-stiffness mechanism

Non-Linear Vibration Isolators with Unknown Excitation and Unmodelled Dynamics: Sliding Mode Active Control

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