Abstract

Resonant vibration generators, such as vibratory feeders or ultrasonic sonotrodes, are often employed in manufacturing to generate harmonic vibrations with suitable amplitude, spatial shape, and frequency, in order to meet the process requirements. These underactuated systems are usually excited in open loop by few actuators, and therefore, it is not ensured that the desired response is correctly achieved, since the feasible motions should belong to the subset of the allowable motions. To achieve the closest approximation of the desired vibrations, some new solutions are here proposed. The first strategy is the optimal shaping of the harmonic forces exerted by the actuators, by solving an inverse dynamic problem through a coordinate transformation and the projection of the desired response onto the subspace of the allowable motion. By exploiting the formulation of such a subspace, a second approach that involves concurrently both the force shaping and the modification of the inertial and elastic system parameters is proposed. The idea of this approach is to exploit the modification of the elastic and inertial parameters to properly shape the allowable subspace in such a way that it spans the desired response. A solution method is developed, and analytical sensitivity analysis is proposed to choose the design variables. Validation is proposed through a linear vibratory feeder with a long flexible tray, taken from the literature. The results show the effectiveness of the proposed strategies that lead to a very precise approximation of the desired response.

Highlights

  • Vibration generators are widely employed in manufacturing plants to exert vibrations with prescribed frequency, amplitude, and spatial shape, as required by the process

  • full force shaping (FFS) and partial force shaping (PFS) are here applied to the test case and compared with the results provided by the application of three equal forces, as often done by practitioners in commanding vibratory feeders whenever a uniform response along the tray is wanted [1]

  • It is interesting to notice that elimination of some design variables in PFS-dynamic structural modification” (DSM) 2 leads to a significantly different mix of mode shapes involved in the forced response

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Summary

Motivations

Vibration generators are widely employed in manufacturing plants to exert vibrations with prescribed frequency, amplitude, and spatial shape, as required by the process. Plastic welding and solid-state bonding usually need high uniformity of the tip vibration of the sonotrode to ensure an effective process due to uniform heating and to prevent damage of the sonotrode itself and the products too [8] These examples show that both a proper excitation force and a proper design of the mechanical part should be adopted to achieve the desired behavior. The difficulties in achieving the desired vibration are exacerbated in the presence of large and flexible devices, such as the long tray of linear feeders, which are excited by just few actuators This problem has been up to now tackled in the literature through the optimal design of the elastic and inertial properties of the system, in the frame of the “dynamic structural modification” (DSM), by considering the free response of the system, i.e., without considering the excitation forces. These two situations are typical occurrences in vibration generators, where the response is set to many DOFs that represent different positions of the flexible system, while few actuators are employed

Contributions of this paper
Definitions and statements of the problems
Problem statement
Subspace of the allowable motions
Solving strategy
Subspace of the allowable motions for underactuated systems
Definitions and problem statement
Full FS and dynamic structural modification
Partial FS and dynamic structural modification
Homotopy optimization
Sensitivity analysis on the system displacements
Model of the system
Specifications
Modal analysis
Application of FFS and PFS
FS with structural modification
Sensitivity analysis
Application of FFS-DSM and PFS-DSM
Eigenstructure and modal participation factors in the modified systems
Response of the modified system to three equal forces
Findings
Conclusions
Full Text
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