Hardware Implementation of High-Speed Active Vibration Control System Based on DSP320C6713 Processor

Macro fiber composite (MFC) has been widely investigated in the active vibration control. Yet, the actuation performance of MFC is a function of temperature. For the active vibration control system using MFC based on the linear piezoelectric equation, if the actuation parameters of MFC are variable, it is easy to cause insufficient control force or control spillover, which degrades the performance of control system. Therefore, an adaptive gain adjustment approach for the active vibration control system is developed, which ensures that the active control system can maintain the expected performance of vibration suppression under the time-varying ambient temperatures. The variation of actuation performance of MFC with temperature is measured by the experiment. The polynomial fitting method is utilized to obtain the functional relationship between the regulator parameters and ambient temperature. The performance of the proposed adaptive gain regulator is verified by the experiment in the temperature environment chamber. In the experiment, a scaled vertical tail model attaching the MFC actuator is as an example, and the fractional order positive position feedback control system is as a representative of the control system without temperature adaptability. When the temperature is −60°C, compared with the control system without regulator, the reduction ratio of response RMS of the control system with adaptive gain regulator is increased by 17.26%.The results indicate that the proposed adaptive gain regulator can avoid the adverse influence of the time.varying ambient temperature on the performance of the control system.

The superior performance of active vibration control systems largely depends on the four‐quadrant controllable execution capability in the available force‐velocity diagram of active actuators. Although semi‐active vibration control systems have the advantages of low energy consumption, simple structure, and high reliability, the system performance is not comparable to active control systems, due to the partial capability in only the first and third quadrants. On the basis of the comprehensive advantages of active and semi‐active actuators, to reform the design philosophy of semi‐active actuators to realize pseudo‐active actuators that have both mechanical properties of active actuators and energy consumption advantages of semi‐active actuators, that is, new semi‐active actuators with four‐quadrant controllable execution capability, will very likely cause a revolution in the related fields of mechanical design and system control. The basic design principle of pseudo‐active actuators that use semi‐active controllable actuators to achieve active actuator performance in the way of conceptual analysis is proposed. The proposed pseudo‐active actuators should consist of two half‐four‐quadrant actuators, that is, one is for the first and third quadrants and the other one for the second and fourth quadrants. This study employs two semi‐active controllable damping actuators and one mechanical compensation mechanism. One of the actuators provides the damping force in the first and third quadrants, and the other one combining with the mechanical compensation mechanism is for the second and fourth quadrants. A global mathematical model of the proposed actuator is established to describe the four different operational modes of the proposed actuator. It is proved that the two operational modes of the proposed actuator can realize active vibration control, and a case study of realizing active control is presented. The other two operational modes are compared with the conventional two‐degree‐of‐freedom model. More specifically, the application cases of the pseudo‐active operational mode of the proposed actuator in the quarter‐car/body‐powertrain suspension system are given, a pseudo‐active suspension named dual‐hook automobile suspension is presented. Furthermore, an equivalent expression of the electrical network is given for the mechanical network under different operational modes of the proposed actuator.

A narrowband active vibration control algorithm with frequency estimator based on lattice notch filter is proposed to suppress the primary signal with multi line spectra. A adaptive iir (infinite impulse response) lattice gradient notch filter was adapted to estimated the frequency of the multi-harmonics buried in the primary signal, then the reference signal is filtered by the adaptive band pass filter. With the reference signal filtered by the adaptive band pass filter, active control algorithm is implemented. Simulations of the frequency estimation of the multi-sinusoidal signal are conducted and simulation results confirm that the proposed algorithm could achieve effective performance when the frequency of the primary disturbance is unknown. Active control of vibration has finds a lot application such as fans, engines, and air conditioners in nowadays. The basic concept of active vibration control is to suppress the primary disturbance with the secondary force which is of same amplitude and opposite phase. Signals generated by the rotating machines such as fans, diesel engines, and air conditioners is characterized with discreet frequency which cause damage to operator in the working environment. Narrowband active vibration control (NAVC) is an effective method to suppress such vibration with multi-line spectra. The application of NAVC has been implemented taken into applications since 1970's. A lot of algorithms have been proposed for suppress the primary disturbance with multi-spectral. There exists two families of algorithm in AVC system, which composed of filtered-X least mean square (FXLMS) algorithm and filtered-X recursive least square algorithm (FXRLS). Due to its simplicity and implementation efficiency, FXLMS algorithm is the most popular adaptive algorithm to suppress the primary disturbance compared to FXRLS algorithms. In the application of NAVC systems, the performance of NAVC systems is directly correlated with the reference signal and the primary signal. NAVC algorithm could not achieve effective performance if the correlation between the primary signal and the reference signal is weak. Frequency estimation of the primary signal is an effective method to adapt to improve the relativity between the reference signal and the primary signal. To estimate the frequency of a sinusoidal signal, a number of algorithm has been proposed to exploit the predictable nature of sinusoidal primary disturbance and characterize the frequency of the sinusoidal primary disturbance, such the Kalman algorithm, music, FFT (fast Fourier transform), etc. such method could be capable of tracking nonstationary or slowly-varyin g primary signals. However, they have some shortcomings in the application of NAVC systems. a lot of Kalman-based algorithms have been proposed for the frequency estimation of the sinusoidal signal in many applications such as the electrical power system, however, it requires much more computation burdens which is much more complicated compared the other algorithms. FFT methods have been proposed in the past to estimated the frequency of the primary signal, but it is has been found that the estimated result could not be accessed effectively in real-time of AVC system. Adaptive notch filter has been proposed for the frequency estimation of the sinusoidal signal in a lot of applications. Adaptive lattice filter shows much more stability and performance compared to the bilinear adaptive notch filter. In this paper, the adaptive lattice notch filter is introduced into an adaptive vibration control system to estimate the frequency of synthesized desired signal. Then, the reference signal is generated to suppress the primary vibration in the active vibration control system.

The dynamic response and active vibration control of flexible composite material barrel under moving projectile are studied in this paper. After analyzing its vibration characteristics, the active vibration control technology is introduced to suppress its vibration. Combining theoretical modeling and experimental developing, some key problems of applying the active vibration control technology to vibration control of flexible composite barrel are discussed, which provides the technology foundation for later developing of flexible smart composite barrel. The coupling vibration model between the moving projectile and flexible composite barrel is established and solved by applying numerical iterative method and simulation experimental study, and many valuable conclusions are made. Besides, the dynamic response model and state space model for active vibration control of barrel under a moving projectile is established. And the adaptive fuzzy control strategy is introduced to suppress the flexible composite material barrel vibration. The testing system of dynamic response and active vibration control for barrel under a moving projectile is designed and developed. The experimental results showed the effectiveness of this kind of control strategy for flexible composite material barrel bonded with piezoelectric self-sensing actuator under a moving projectile, which demonstrated that using the smart material could suppress the time-varying system flexible structure vibration active control.

Considering the problems of model uncertainties, higher harmonics, uncertain boundary conditions, external excitations, and system time delay in practical vibration control system, a novel active vibration control method is proposed to suppress the vibration of a thin plate structure with acceleration sensor and piezoelectric bimorph actuator in this paper. First, a nonlinear extended state observer (NESO)-based controller is designed to ensure the anti-disturbance performance of the structural vibration control system. Then, an enhanced differentiator-based time delay compensation method is introduced to improve the vibration suppression performance of the NESO-based controller. A real time hardware-in-the-loop benchmark for an all-clamped piezoelectric thin plate is designed to verify and compare the performance of the developed controller against conventional ESO-based methods (linear ESO with/without time delay compensation, NESO without time compensation). The best vibration suppression and disturbance rejection performance of the proposed NESO-based controller with an enhanced time delay compensator is verified in the comparative experimental results. This work is able to provide practitioners with vital guidance in designing active vibration control system in the presence of disturbances and time delay.

High-precision in-orbit missions, such as deep space exploration, communication, and Earth observation, have raised higher requirements for spacecraft microvibration suppression (MVS). The complex microvibration environment on spacecraft results in microvibration signals appearing as a combination of broadband random vibration and multiharmonic vibration, posing challenges to MVS. In this article, a new Volterra filtering-based hybrid active vibration control (NVHAVC) system is proposed for suppressing complex microvibrations in spacecraft. In the proposed NVHAVC system, a modified generalized soft-root-sign (MGSRS) adaptive algorithm is used to replace the least-mean-square adaptive algorithm in the filtered-x adaptive controller to address the impact of non-Gaussian or impulse noise on the MVS performance. And the MGSRS and Volterra filtering are introduced into both the broadband subsystem and narrowband subsystem for improving the MVS performance. Meanwhile, a frequency estimation algorithm based on an extended Kalman filter (EKF) is also introduced into the narrowband subsystem to improve the MVS performance of multiharmonic vibration with unknown time-varying frequency and amplitude. In addition, the physical output of the narrowband subsystem is reconstructed in the NVHAVC system framework to reduce the decrease of MVS performance caused by the same error feedback in both the broadband subsystem and the narrowband subsystem of the traditional hybrid active vibration control (AVC) system. Numerical simulation and experimental verification are conducted to validate the effectiveness of the proposed NVHAVC system. The results show that the improved broadband and narrowband subsystems can realize the MVS performance improvements of approximately 5–8 dB and 24–26 dB, respectively, compared with the traditional broadband and narrowband subsystems. The proposed NVHAVC system can achieve microvibration performance improvement of approximately 10 dB compared with the traditional hybrid AVC (HAVC) system.

Active vibration control of large flexible space structure is a challenging topic in the system dynamics and control of spacecraft. This paper proposes a novel approach for vibration control on a large hoop truss structure, typically used as mesh satellite antenna. First, to suppress the first-order bending modal response of the hoop truss structure with an initial disturbance, a piezoelectric bending actuator with excellent bending actuation performance was carefully designed as a key component of an active vibration control system. Then, the actuating characteristics of the actuator and the dynamic equations of the active structure were analyzed and formulated based on a finite element method. In order to improve the vibration-attenuating effect of the control system, a Mamdani-type fuzzy logic algorithm was employed in a closed-loop control system. Finally, simulations and experiments were implemented to validate the effectiveness of the proposed active control approach and structure. The experimental results showed that the decay time of first-order bending modal response (around 0.34 Hz) of control system reduces by 75% compared with that of the uncontrolled system. The results demonstrate that the proposed active vibration control system has good application potential in controlling the bending modes of a large flexible spacecraft.

Commercial active noise and vibration control systems for vehicles are gradually developing, mainly in Japan, for both active noise control of interior sound and active control engine mounts [1]. There have been four Japanese commercial applications: • Active control for booming noise by Nissan in 1991, • Active vibration mount for idle noise and vibration by Toyota in 1997, • Active vibration mount for diesel engines by Nissan in 1998, • Active control for low-frequency road noise by Honda in 2000. Other manufacturers have, of course, developed similar systems, but these have not progressed to production applications. Additionally, active control engine mufflers using cancelling loudspeakers have been successfully demonstrated. A new type of active muffler, using a controlled oscillating butterfly valve in the exhaust line has been developed recently. The future of active control in vehicles is dependent on customers who are willing to pay the higher price for additional noise and vibration control, so that cost reductions are the essential factor in further commercial products. Trends towards fuel efficiency and lighter vehicles run counter to reducing noise and vibration. This has given new interest in active noise control and active control engine mounts as a solution to these conflicting issues.

From a control point of view, active vibration control requires attenuation of unknown and/or time varying multiple narrow band disturbances. Internal Model Principle (IMP) is currently used for building adaptive active vibration control systems. IMP leads to asymptotic suppression of the disturbances but often introduces in the case of multiple narrow band disturbances a strong ”water bed” effect on the output sensitivity function (unwanted amplification). In this paper, an indirect adaptive control methodology for attenuation of multiple unknown time varying narrow-band disturbances is proposed. The method is based on the real time estimation of the frequency of narrow-band disturbances using adaptive notch filters (ANF) followed by the design of a controller using adjustable band-stop filters (BSF) for the appropriate shaping of the output sensitivity function. A Youla-Kucera parametrization of the controller is used for reducing the computation load. This approach is compared on an active vibration control (AVC) system with the direct adaptive control scheme based on the internal model principle (IMP) proposed in [1]. Real time experimental results are provided.

Vibration control strategies strive to reduce the effect of harmful vibrations such as machining chatter. In general, these strategies are classified as passive or active. While passive vibration control techniques are generally less complex, there is a limit to their effectiveness. Active vibration control strategies, which work by providing an additional energy supply to vibration systems, on the other hand, require more complex algorithms but can be very effective. In this work, a novel artificial neural network-based active vibration control system has been developed. The developed system can detect the sinusoidal vibration component with the highest power and suppress it in one control cycle, and in subsequent cycles, sinusoidal signals with the next highest power will be suppressed. With artificial neural networks trained to cover enough frequency and amplitude ranges, most of the original vibration can be suppressed. The efficiency of the proposed methodology has been verified experimentally in the vibration control of a cantilever beam. Artificial neural networks can be trained automatically for updated time delays in the system when necessary. Experimental results show that the developed active vibration control system is real time, adaptable, robust, effective and easy to be implemented. Finally, an experimental setup of chatter suppression for a lathe has been successfully implemented, and the successful techniques used in the previous artificial neural network-based active vibration control system have been utilized for active chatter suppression in turning.

Active vibration control using regenerated vibration energy, i.e., self-powered active control, is proposed. In the self-powered active control system, vibration energy is regenerated by an electric generator, which is called an energy regenerative damper, and is stored in the condenser. An actuator achieves active vibration control using the energy stored in the condenser. The variable-value resistance whose value can be controlled by a computer is utilized to control output force of the actuator. The authors examine the performance of the self-powered active vibration control on experiments and propose to apply this system to cab suspensions of a heavy duty truck. Through experiments, it is shown that the self-powered active vibration control system has better isolation performance than a semi-active and a passive control system. Numerical simulations demonstrate better isolation performance of the self-powered active vibration control in cab suspensions of a heavy duty truck.

SUMMARY Integral resonant control (IRC) has been recently introduced as a simple, robust and high-performance technique for vibration control of smart structures instrumented with collocated piezoelectric actuator–sensor pairs. This work deals with the design and implementation of an active vibration control (AVC) system based on an IRC strategy for the mitigation of human-induced vibrations in light-weight civil engineering structures, such as floors and footbridges, via proof-mass actuators. This work presents a new AVC strategy that combines an approximate inversion of the proof-mass actuator dynamics with an IRC-based strategy. The result is a control scheme with the following desirable characteristics: (i) the closed-loop system exhibits very high stability margins, (ii) the risk of stroke saturation at low frequencies is significantly reduced so that the saturation nonlinearity, which has to be included to keep the system hardware safe, can be designed to account only for force saturation (i.e. the actuator performance is enhanced), (iii) rigorous stability analysis and systematic design can be proposed and (iv) it is not necessary to measure the actuator force. The stability analysis is carried out using the recently developed stability theorem based on the positive feedback interconnection of systems with negative imaginary frequency response. The control scheme is validated on a full-scale prestressed concrete laboratory structure. Excellent vibration reduction performance is reported for frequency-response-function-based tests and for walking excitations. Copyright © 2010 John Wiley & Sons, Ltd.

There have been many reports on the design of active vibration control systems. Most of them have optimized control systems based on the LQ optimal regulator or H∞ control theory. However, there are no answers to the problem whether given passive parameters of plants (e. g., spring constant on damping coefficient) are 'suitable' for the designed controller. In this paper, we consider structure and control simultaneous optimization for an active vibration control system. To provide solutions, several methods have been proposed which are based on tuning the design paramethers existing in the structure and controller. Most of the control laws are those of standard LQ optimal requlators which require full states measurements and estimate performance of a closed-loop control systems in the time domain. From the viewpoint of active vibration control, it is natural to discuss the performance of the control system in the frequency domain. Therefore, we adopt the frequency shaped LQG control law in simultaneous optimization design, which enables output feedback control and frequency shaping.

This work describes a range of issues relating to the implementation of active control for noise and vibration problems. It is important in the commercialization of this technology to consider these and many other factors relating to design of these systems. Many of the concepts required for efficient implementation have not been considered and it is important to begin giving design consideration to these aspects. A design technique based upon the eigenbehavior of feedforward controlled systems is developed and applied to control radiation from structures. Integration of the control system with the physical system dynamics allows the eigenproperties to be defined to meet a prescribed design criteria. Here the technique is demonstrated to implement a structural system that inefficiently couples vibration energy to acoustic energy. In addition, an approach to integrate “knowledge” about actuator configurations into an active control system that reduces spillover effects into structural vibrations is demonstrated. This approach has the advantages that no additional hardware is required while also reducing the order of the control system in terms of degrees of freedom. Finally, some design trade-offs between the passive material properties of an active trim panel and control system performance are examined. Improved performance can be attained but at the cost of additional weight.

<p>Building structures subjected to earthquakes undergo deformations, which may damage structural and non-structural elements. Vibration control systems are an interesting solution to reduce the dynamic response of structures. However, even if this technique is on the research agenda for several decades, there is only a limited number of anti-seismic applications in buildings in Europe. In this paper active, passive and hybrid vibration control systems are designed and analysed numerically in 9 case studies to assess their effectiveness to reduce the inter-storey drift. The investigations are carried out by linear time history analysis at damage limitation state. The results show clearly the advantages and limitations of different vibration control systems for anti-seismic purposes. In the next step the effectiveness and robustness of the most favourable solution will be tested experimentally in a full scale shaking table test of a two storey lightweight steel structure.</p>