Resonance Suppression Control Circuit for Drive Train Testing
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Solution Overview
Problem
Existing resonance suppression control circuits for drive train testing systems face instability due to fluctuations in resonance frequency caused by variations in mechanical characteristics and inertial moments, and they struggle to effectively manage multiple vibration modes, leading to spillover issues when applied to actual physical systems.
Innovation Solution
A resonance suppression control circuit designed using the μ design method with a generalized plant model that separates the nominal model into low-order and high-order vibration mode transfer functions, incorporating structured perturbations relative to parameters like spring constants and moments of inertia to ensure robust stability and suppress spillover.
Engineering Contradictions & Design Principles
Engineering Contradiction Analysis
1Device complexity
If a two-inertia system nominal model is used for resonance suppression control design, then the control circuit can be designed with simpler structure, but spillover occurs due to unmodeled high-order vibration modes causing control instability
Solution Approach 1:
The patent segments the nominal model into multiple inertia elements (at least three-inertia system) to represent different vibration modes separately. This segmentation allows the control design to account for both low-order and high-order vibration modes, preventing spillover while maintaining structured control architecture.
Solution Approach 2:
The patent introduces dynamic adjustment mechanisms that adapt the control parameters based on the actual vibration characteristics. The control circuit dynamically adjusts to handle variations in resonance frequency caused by different test pieces, ensuring stability across varying operating conditions.
2Ease of manufacture
If the nominal model parameters are fixed at design stage, then the control circuit design is simplified, but control becomes unstable when resonance frequency fluctuates due to test piece variations
Solution Approach 1:
The patent implements dynamic parameter adjustment mechanisms that allow the control circuit to adapt to varying resonance frequencies. The system monitors actual vibration characteristics and adjusts control parameters in real-time, ensuring stable performance across different test pieces while maintaining a relatively simple base design structure.
Solution Approach 2:
The patent employs parameter variation strategies where the nominal model parameters are designed to accommodate expected ranges of resonance frequency fluctuations. This includes designing the control circuit to handle parameter variations within specified bounds, balancing design simplicity with robustness to parameter changes.
3Reliability
If a multi-inertia system nominal model is used to account for multiple vibration modes, then spillover is suppressed, but the control circuit structure becomes more complex
Solution Approach 1:
The patent segments the system model into distinct inertia elements representing different vibration modes, allowing targeted control strategies for each mode. This segmentation enables the control circuit to address high-order modes specifically without requiring complete redesign of the entire control architecture.
Solution Approach 2:
The patent applies control actions selectively to address specific vibration modes that cause spillover, rather than attempting to control all modes equally. The control circuit focuses computational and control resources on the critical high-order modes that require suppression, reducing overall system complexity while maintaining stability.
Data Source
AI summary
A resonance suppression control circuit provides operation stable for variations with a low order mode of vibration and suppressing spill-over due to high order mode of vibration. This circuit controls a physical system having two or more modes of vibration, and suppresses resonance in a lowest order mode of vibration from among the plurality of modes. The circuit has a controller designed by a μ design method, using a generalized plant with nominal model, and structured perturbation to the generalized plant. The nominal model is represented by the product of a low order vibration mode transfer function having the low order mode of vibration to be suppressed, and a high order vibration mode transfer function having a high order mode of vibration. The structured perturbation includes a first parameter perturbation term which imparts a multiplicative error to a spring constant included in the vibration mode transfer function being suppressed.