By Christopher C. Fuller, S. J. Elliott, P. A. Nelson
This ebook is a significant other textual content to lively keep watch over of Sound by means of P.A. Nelson and S.J. Elliott, additionally released by means of educational Press.
It summarizes the foundations underlying lively vibration regulate and its useful functions by means of combining fabric from vibrations, mechanics, sign processing, acoustics, and keep an eye on concept. The emphasis of the publication is at the lively keep an eye on of waves in buildings, the lively isolation of vibrations, using allotted pressure actuators and sensors, and the lively keep watch over of structurally radiated sound. The feedforward keep an eye on of deterministic disturbances, the lively keep an eye on of structural waves and the lively isolation of vibrations are coated intimately, in addition to the extra traditional paintings on modal suggestions. the rules of the transducers used as actuateors and sensors for such keep an eye on concepts also are given an in-depth description.
The reader will locate fairly fascinating the 2 chapters at the lively keep an eye on of sound radiation from constructions: lively structural acoustic keep an eye on. the cause of controlling excessive frequency vibration is usually to avoid sound radiation, and the foundations and functional software of such strategies are provided the following for either plates and cylinders. the amount is written in textbook variety and is geared toward scholars, working towards engineers, and researchers.
* Combines fabric from vibrations, sign processing, mechanics, and controls
* Summarizes new examine within the box
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Additional resources for Active Control of Vibration
6 Frequency response function and mode shapes of a simply supported beam. 6 shows an example frequency response function (FRF) for a beam of length L = 0 . 3 8 m, bending stiffness E I = 5 . 12). Also shown are the mode shapes corresponding to the peaks, or resonance points in the FRF. 15). An interesting characteristic of beam behaviour is that the resonance frequencies become spaced further apart with increasing mode number. This is also apparent from Fig. 5 and is due to the dispersive nature of flexural waves.
Simultaneously applying the above boundary conditions to an assumed wave field allows determination of both the travelling wave and near-field amplitudes. Let us apply the above approach to the case of a finite beam of length L, simply supported at each end. For the simply supported boundary conditions the flexural near fields can be shown to vanish. The beam response can be then written as the superposition of two travelling waves in the positive and negative directions with unknown coefficients A and B: w(x, t)= A eJ~t-Jkl~ + B eJ°~t+Jklx.
3) by ~Pn= sin knx and integrate over the length of the beam L. We then find an expression for the complex amplitudes Wn given by 2 I L F(x) sin k~x dx. 5) demonstrates that in order to solve for the response of the system, we have conveniently expanded the forcing distribution into a series with the system free mode shapes as the basis functions; the magnitude of the modal amplitudes W, are dictated by the shape of the forcing function. 5) is well-conditioned to determine the global system response and ill-conditioned to predict the near-field effects at say the drive point since the basis functions do not readily model the evanescent motions.