EP0636287B1 - Systeme de regulation de vibrations ameliore au moyen d'un resonateur adaptable - Google Patents

Systeme de regulation de vibrations ameliore au moyen d'un resonateur adaptable Download PDF

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Publication number
EP0636287B1
EP0636287B1 EP92916034A EP92916034A EP0636287B1 EP 0636287 B1 EP0636287 B1 EP 0636287B1 EP 92916034 A EP92916034 A EP 92916034A EP 92916034 A EP92916034 A EP 92916034A EP 0636287 B1 EP0636287 B1 EP 0636287B1
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EP
European Patent Office
Prior art keywords
vibration
control system
resonator
resonator means
frequency
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP92916034A
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German (de)
English (en)
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EP0636287A4 (fr
EP0636287A1 (fr
Inventor
Andrew Langley
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Noise Cancellation Technologies Inc
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Noise Cancellation Technologies Inc
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Priority to AT92916034T priority Critical patent/ATE186614T1/de
Priority claimed from PCT/US1992/003024 external-priority patent/WO1993021687A1/fr
Publication of EP0636287A1 publication Critical patent/EP0636287A1/fr
Publication of EP0636287A4 publication Critical patent/EP0636287A4/fr
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Classifications

    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/175—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using interference effects; Masking sound
    • G10K11/178—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using interference effects; Masking sound by electro-acoustically regenerating the original acoustic waves in anti-phase
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K2210/00—Details of active noise control [ANC] covered by G10K11/178 but not provided for in any of its subgroups
    • G10K2210/10—Applications
    • G10K2210/129—Vibration, e.g. instead of, or in addition to, acoustic noise
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K2210/00—Details of active noise control [ANC] covered by G10K11/178 but not provided for in any of its subgroups
    • G10K2210/30—Means
    • G10K2210/301—Computational
    • G10K2210/3028—Filtering, e.g. Kalman filters or special analogue or digital filters
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K2210/00—Details of active noise control [ANC] covered by G10K11/178 but not provided for in any of its subgroups
    • G10K2210/30—Means
    • G10K2210/301—Computational
    • G10K2210/3045—Multiple acoustic inputs, single acoustic output
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K2210/00—Details of active noise control [ANC] covered by G10K11/178 but not provided for in any of its subgroups
    • G10K2210/30—Means
    • G10K2210/321—Physical
    • G10K2210/3227—Resonators
    • G10K2210/32271—Active resonators
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K2210/00—Details of active noise control [ANC] covered by G10K11/178 but not provided for in any of its subgroups
    • G10K2210/50—Miscellaneous
    • G10K2210/501—Acceleration, e.g. for accelerometers

Definitions

  • the vibration typically comprises a fundamental component whose frequency is, for example, the rotation frequency of the machine (this is called the first harmonic), plus one or more additional harmonics at frequencies that are integer multiples of the first.
  • a tuned damper is a resonant system that is attached to a point where vibration is to be reduced, and it is built to resonate at or close to the frequency of the vibration. Purely passive tuned dampers have fixed characteristics, and will work only close to the frequency for which they are designed.
  • the input impedance of the resonator (defined as the ratio of a generalized force applied by the resonator at the point of attachment to a generalized velocity at the same point) will be exceptionally high (or in some cases, such as a Helmholtz resonator in a duct, exceptionally low: see the description in L E Kinsler, A R Frey, A B Coppens, J V Sanders “Fundamentals of Acoustics” 3rd ed. Wiley and Sons 1982 pp 241-242).
  • a mass suspended on a spring will resonate at a characteristic resonance frequency. If the spring is attached to a structure vibrating at this resonance frequency, the amplitude of vibration of the structure at that point will be reduced (and as a consequence, the suspended mass will vibrate strongly). Similar effects can be described for acoustic resonators (eg. Helmholtz resonators; L E Kinsler, A R Frey, A B Coppens, J V Sanders “Fundamentals of Acoustics” 3rd ed. Wiley and Sons 1982. pp 225-228) where sound pressure is the vibration to be reduced.
  • acoustic resonators eg. Helmholtz resonators; L E Kinsler, A R Frey, A B Coppens, J V Sanders “Fundamentals of Acoustics” 3rd ed. Wiley and Sons 1982. pp 225-228) where sound pressure is the vibration to be reduced.
  • An ideal adaptive-passive system would be able to control components of vibration at several different frequencies (usually the first and subsequent harmonics of a quasi-periodic vibration), whilst maintaining the performance of the system as the frequencies change.
  • the damper is a Helmholtz resonator, and the control systems use the sound pressure level inside the resonator, and just outside it, as inputs. Both control systems aim to adjust the resonators such that the phase shift between the two inputs is 90°, when the resonator will be at resonance.
  • Sato and Matsuhisa use a two-stage control system that estimates the frequency of the sound from the inputs and uses an open-loop control system initially to tune the damper close to that frequency. A second stage of closed-loop control then iterates to tune the damper precisely to the correct frequency, although there is no description of the control algorithm.
  • This system must derive the vibration frequency initially from one of the inputs, which can be difficult if the fundamental period of vibration is changing and the vibration comprises several harmonics all of which will be changing differently. Also, the control system does not allow several tuned dampers to be tuned to reduce several different frequencies in the sound simultaneously.
  • Vibration control via controllable resonators is also known from EP-A-0 300 445 and DE-A-2 905 973.
  • the invention provides for a noise or vibration control system as defined by the appended claim 1.
  • Advantageous embodiments are defined by the dependent claims 2-9.
  • a still further object is to have a vibration control system with sensors attached to the source or the structure (or any other suitable location) that can be used to determine the frequencies of the noise or vibration
  • a still further object is the provision of vibration control with optional additional sensors that are used to monitor other factors that affect the resonators' performances (such as temperature)
  • control system that has as inputs the sensors, and as outputs, signals to change the resonance frequencies of the resonators wherein the control system incorporates an algorithm to tune the resonators close to selected frequencies in the noise or vibration, and to keep them tuned as those frequencies drift.
  • control system incorporates mathematical models of the resonators that are used to enhance the performance of the control system.
  • these models are continuously updated and refined by the control system as it operates.
  • FIG. 2 A very simple example of the invention will be used to illustrate the important features.
  • a structure 1 is excited by a source 2 vibrating at a variable fundamental frequency of f 1 .
  • the spectrum of the vibration contains harmonics at f 1 , 2f 1 , 3f 1 .... etc.
  • a spring-mass-damper resonator 3 is attached at a point on the structure where it is desired to reduce the vibration. It is assumed in this example that the nth harmonic of the fundamental component of the vibration is to be reduced by the damper, so that the aim is to tune the resonator close to nf 1 , and to keep it tuned as f 1 drifts.
  • the “structure” bears the vibration from the source to the resonator, and may be a solid, fluid or gas depending on the application.
  • “Vibration” includes any disturbance in the “structure”, including electromagnetic, as the techniques described here can be equally well applied to mechanical or electrical systems.
  • An accelerometer 4 is attached to the mass of the resonator, and another accelerometer 5 is attached to the structure close to the resonator.
  • the displacement of the mass (as monitored via the accelerometer 4) is denoted x m
  • the displacement of the structure (as monitored via the accelerometer 5) is denoted x s .
  • the frequency responses of the sensors are known so that x m and x s can be derived from the sensor outputs.
  • the frequency response of the sensor can usefully include any other additional filtering (eg analogue bandpass filtering and gain adjustment to improve signal to noise ratios or anti-aliasing).
  • This compensation for the sensor responses can be applied at different points in the system, but it is most efficient to apply the compensation to the coefficients X m and X s described below.
  • the control system will store necessary information about the calibration of the sensors to enable any corrections that are required to be made. In the description below, these corrections are not explicitly stated as it will be obvious to anyone skilled in the art how to compensate for sensor characteristics to derive the quantities needed by the control system.
  • the aim is to maximize the modulus of the input impedance of the resonator at the nth harmonic of the fundamental of vibration, so that the structure will vibrate less at that frequency at the point of attachment of the resonator.
  • the input impedance is defined here to be the ratio of the force applied by the structure to the resonator and the corresponding velocity of the point of attachment, and it is a function of frequency.
  • ⁇ r is the undamped resonance (angular) frequency of the resonator
  • Q is the "quality factor”.
  • a frequency sensor 6 in figure 2 is provided to detect the fundamental frequency of vibration, f 1 .
  • the location and type of sensor is preferably chosen to be reasonably immune to the effects of changing the tuning of the resonator.
  • it could be a tachometer signal from a part of the source of vibration such that the output of the tachometer can be used to determine the current fundamental frequency of the source.
  • it may be sufficient to use one or more of the sensors mounted on the structure and resonators to derive fundamental frequencies, but it is better if the sensor is insensitive to the effects of tuning the resonators.
  • the signal from sensor 6 is used by the control system 7 to help to discriminate those components of x m and x s at the frequency nf 1 in the presence of components at other harmonics of f 1 or any other "noise". This discrimination is crucial if the control system is to be able to alter the resonance frequency of the resonator to coincide with nf 1 and to maintain this condition as f 1 varies.
  • x m and x s will normally contain components at all harmonics of f 1 up to the highest harmonic below the current resonance frequency of the resonator. Unless the unwanted components can be rejected, there is no guarantee that the resonator will be adjusted to the correct frequency.
  • the signal from sensor 6 can be used in several different ways to process the inputs from accelerometers 4 and 5. Three examples are given below.
  • a tracking bandpass filter whose centre frequency is adjusted by the signal from sensor 6 to be close to nf 1 (eg. see K Martin and A S Sedra, IEEE Transactions on Acoutics, Speech and Signal Processing Vol ASSP-29 no. 3 June 1981 pp 736-744).
  • the bandwidth of the filter is chosen to reject all unwanted components in the accelerometer signals.
  • Each accelerometer signal is then filtered through a tracking filter (desirably, these filters would be identical) to leave only the signals at a frequency of nf 1 .
  • One problem with this implementation is that the bandwidth of the filter (expressed in octaves) will have to vary with the number, n, of the harmonic to be controlled. This is because harmonics become more closely spaced (in terms of octaves) as n is increased.
  • the accuracy with which sensor 6 must detect f 1 depends upon the required bandwidth of the filter. If the filter bandwidth must be narrow to remove an unwanted noise component close to nf 1 , then the accuracy with which the filter's centre frequency is set (by the signal from sensor 6) must clearly be such that the pass-band still includes the frequency nf 1 . It is immaterial whether the tracking filter is implemented digitally or with analogue electronics.
  • the output of the bandpass filters will be signals that contain information only at the frequency nf 1 , as required.
  • the low-pass filters described for the harmonic filter can have a bandwidth of up to 2f 1 .
  • a single FFT or DFT is all that should be required to calculate X m and X s as signal averaging will be unnecessary.
  • the outputs of identical bandpass filters are expected to be A
  • the signals x m and x s are then multiplied by sin(2 ⁇ nf 1 t) and cos(2 ⁇ nf 1 t) (giving four signals in total), and each of the results is low-pass filtered by filters whose bandwidths are adjusted to reject all the unwanted components in x m and x s .
  • the bandwidths of the low-pass filters should be less than f 1 .
  • the low-pass filters should have bandwidths that are ideally adjusted by the control system as f 1 changes in order to maintain rejection of unwanted components in the signals (see G P Eatwell, "Control System Using Harmonic Filters”. Copending patent application).
  • the accuracy with which the frequency of the auxiliary signals must match nf 1 depends upon the required bandwidth of the low-pass filters: the difference between the true value of nf 1 and the frequency of the auxiliary signals derived from sensor 6 must be less than the bandwidth of the low-pass filters.
  • y mc and y ms to be the outputs from the process of multiplying x m by cos(2 ⁇ nf 1 t) and sin(2 ⁇ nf 1 t) respectively and then low-pass filtering the results.
  • y sc and y ss for the results of operating on x s .
  • auxiliary signal from sensor 6 Another method of using the auxiliary signal from sensor 6 to discriminate against unwanted components in x m and x s is to use a Fourier transform (D E Newland "An Introduction to Random Vibrations and Spectral Analysis” Longman 1975 pp 33-40). As this would normally be implemented digitally, it is described here in those terms. From the sensor 6 signal, a pulse-train of N pulses per fundamental period of the vibration is derived. (This would be done directly if, for example, sensor 6 were a shaft-encoder giving N pulses per revolution of a shaft in the source rotating at the same frequency as the fundamental frequency of the vibration).
  • This pulse-train is used to trigger analog-to-digital converters (ADC's) sampling x m and x s (after such anti-alias filtering as is necessary).
  • ADC's analog-to-digital converters
  • the pulse-train can be used to select samples from ADC's triggered by a fixed clock running at a frequency considerably higher than Nf 1 (using interpolation/extrapolation if necessary to get the sample value at the occurrence of a pulse, which may lie between two successive samples of the ADC's).
  • the result of this process is a sequence of samples of x m and x s , with N samples per fundamental period of the vibration.
  • N is a suitable number.
  • the "Fast Fourier Transform” algorithm can be used; see D E Newland “An Introduction to Random Vibrations and Spectral Analysis” Longman 1975 pp 150-166). It is also possible to perform a Discrete Fourier Transform (see 6. D E Newland “An Introduction to Random Vibrations and Spectral Analysis” Longman 1975 pp 113-124).
  • the result of this process is one or more "Fourier Coefficients", representing the real and imaginary parts of X m and X s at one or more of the frequencies f 1 , 2f 1 ...nf 1 ... Nf 1 /2.
  • the coefficient at nf 1 will have to be calculated when this is the harmonic of the vibration that is to be reduced).
  • Noise in x m and x s that is not correlated to the pulse-train can also be reduced by averaging corresponding Fourier coefficients from successive blocks of data (this is frequency-domain averaging, another example of a standard technique).
  • the control system must arrange to adjust the tuning of the resonator accordingly.
  • the modulus of the ratio X m /X s is to be maximized, or the phase difference between X m and X s is to be kept at 90° as f 1 varies.
  • a model-based digital control system is described below.
  • a gradient-descent algorithm incorporating a model of the resonator is used.
  • the purpose of the model is to permit rapid and accurate estimation of the derivatives of an error function that determines the current performance of the system.
  • the controller can be configured continuously to update its model of the resonator, and to account for additional variables (such as temperature) that affect the system performance.
  • the aim of the control system is to adjust ⁇ r to minimize
  • ⁇ may be the position of an actuator that changes the stiffness of the spring in the spring-mass-damper resonator.
  • ⁇ k the improved value of ⁇ to be set by the controller ( ⁇ k+1 ) can be calculated by the following equation where ⁇ is a scalar multiplier determined by the control system, and an asterisk indicates the complex conjugate. This is the update equation for a gradient-descent algorithm.
  • equation 3 is of limited use because the derivative of r with respect to ⁇ is not measured (whereas r is). It would be possible to determine the value of this derivative by making small perturbations in ⁇ and observing the results, but it is better to use the model of the resonator to estimate this derivative.
  • equation 2 gives the value of r in terms of the current values of ⁇ r and Q. Therefore, an estimate of the derivative is given by
  • a variable Helmholtz resonator mounted in a duct to prevent transmission of noise at a frequency of nf 1 .
  • This system is very similar to the spring-mass-damper described above, but here the aim is to minimize the input impedance (defined as the ratio of sound pressure in the duct outside the neck of the resonator and the particle velocity of the fluid in the neck) at the frequency nf 1 .
  • ⁇ ⁇ ( ⁇ /Q)/ ⁇ r / ⁇
  • ⁇ is a constant independent of ⁇ and the resonator performance, and the derivative is evaluated at the current value of ⁇ .
  • the best value for ⁇ can be selected by experiment.
  • ⁇ is known from the sensor 6 signal, and an estimate of ⁇ is known from the current value of ⁇ and the relation between ⁇ and ⁇ r which is stored by the controller. Therefore, it is simple to adjust ⁇ in one step to bring ⁇ r much closer to ⁇ .
  • the relation between ⁇ r and ⁇ will in general not be known very accurately since, for example, the relation may depend upon unobserved variables such as temperature.
  • the derivative is evaluated at a value of ⁇ corresponding to a frequency somewhere between ⁇ and ⁇ r , and ⁇ is a positive control parameter that would usually be somewhat less than 1. A value of 1 tries to converge to the correct value of ⁇ in one step.
  • This method relies on the assumption that the gradient ⁇ r / ⁇ is less sensitive to error than the resonance frequency itself.
  • This update equation can be applied iteratively, if necessary, to bring the resonator close enough to resonance for the gradient-descent algorithm to be applied.
  • the relationships between ⁇ , Q and ⁇ can be continually refined and updated by the control system as it operates. For example, when the controller detects that ⁇ and ⁇ r coincide (through a small value of r and/or a small value the second term on the RHS of equation 3) it will be able to update its relationship between ⁇ r and ⁇ , because ⁇ will be known from the sensor 6 signal and ⁇ is a control parameter. Likewise, the minimum value of
  • , from equation 2 will then be 1/Q (if Q>>1, but it is not difficult to derive an exact relation if required) so Q at the current value of ⁇ is also found. As the frequency ⁇ 2 ⁇ nf 1 changes, the relationships between ⁇ r , Q and ⁇ can be continuously updated for the range of ⁇ explored by the change in ⁇ .
  • ⁇ r and Q may also be functions of parameters other than ⁇ .
  • temperature may affect the resonance frequency.
  • the control system can still update these relationships as described above, the only difference being that these relationships now involve ⁇ and the additional variables instead of just ⁇ .
  • more than one harmonic of the vibration will usually be controlled. This is easily performed with the addition of one resonator per harmonic to be controlled, plus at least one additional sensor on each of the resonators. (The sensor 5 on the structure can be used to determine the vibration at all of the harmonics to be controlled, whereas a separate sensor is needed on each of the resonators). With the processing of the signals described above, the control of each resonator is largely independent.
  • the source generates more than one harmonic sequence of vibration.
  • the set of fundamental frequencies, f 1 , f 2 ....f n should be resolved either from a single sensor 6, or preferably from several sensors that measure separately the different fundamentals.
  • the overall control scheme is unchanged, as each additional harmonic sequence can be handled independently by a separate bank of harmonic filters.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)

Claims (10)

  1. Système de régulation de bruit ou de vibration destiné à réguler un bruit ou une vibration provenant d'une ou plusieurs sources de bruit (2), comprenant :
    un ou plusieurs moyens de résonateur adaptatif (3), fixés à un ou plusieurs points sur une structure (1), les fréquences de résonance des moyens de résonateur pouvant être ajustées par des signaux de commande,
    un ou plusieurs moyens de capteur (6) sur la source de vibration (2), la structure (1) ou à la fois ladite source de vibration (2) et ladite structure (1), qui peuvent être utilisés pour obtenir les fréquences des diverses composantes de la vibration,
    caractérisé par
    des moyens de capteur (4, 5) sur ledit moyen de résonateur (3), la structure (1) ou à la fois ledit moyen de résonateur (3) et ladite structure (1) qui sont utilisés pour déterminer l'accord du moyen de résonateur (3),
    un système de régulation (7), qui comporte en tant qu'entrées les signaux de sortie provenant des moyens de capteur (4, 5, 6) utilisés pour déterminer l'accord du moyen de résonateur et utilisés pour obtenir les fréquences des diverses composantes de vibration, et en tant que sorties les signaux de commande destinés à modifier les fréquences de résonance du moyen de résonateur (3),
    dans lequel le système de régulation (7) incorpore un algorithme de commande destiné à accorder les moyens de résonateur (3) à proximité de fréquences choisies du bruit ou de la vibration et à les maintenir accordées lorsque ces fréquences dérivent ou lorsque d'autres facteurs affectant les performances du moyen de résonateur (3) varient.
  2. Système selon la revendication 1, caractérisé par l'incorporation d'une combinaison de filtres suiveurs, de filtres d'harmonique ou de filtres à transformation de Fourier dans le but de réaliser une discrimination vis-à-vis de composantes indésirables dans les entrées du moyen de capteur (6) vers le système de régulation.
  3. Système selon la revendication 1, caractérisé en ce que le système de régulation (7) utilise des modèles du moyen de résonateur (3) dans l'algorithme de régulation.
  4. Système selon la revendication 3, caractérisé en ce que le système de régulation (7) met à jour et affine les modèles du moyen de résonateur (3) lorsqu'il fonctionne.
  5. Système selon la revendication 1, caractérisé en ce que le système de régulation (7) vise soit à minimiser soit à maximiser des quantités qui sont proportionnelles à un module des impédances d'entrée du moyen de résonateur (3).
  6. Système selon la revendication 5, caractérisé en ce que le système de régulation (7) utilise un algorithme de descente par gradients.
  7. Système selon la revendication 3, caractérisé en ce que le système de régulation (7) utilise un algorithme en une étape fondée sur des mesures.
  8. Système selon la revendication 3, caractérisé par des moyens de capteur supplémentaires (8) qui surveillent d'autres paramètres affectant les performances du moyen de résonateur (3) à partir des entrées vers le système de régulation (7).
  9. Système selon l'une des revendications précédentes, caractérisé en ce qu'il comprend en outre un système de régulation actif (plus ses capteurs et ses actionneurs) dont les performances sont conçues pour venir en complément du moyen de résonateur (3) pour la réduction du bruit ou de la vibration dans la structure (1).
  10. Système selon l'une des revendications précédentes, caractérisé en ce que l'accord desdits un ou plusieurs résonateurs (3) n'a raisonnablement aucun effet sur les un ou plusieurs moyens de capteur (6) utilisés pour obtenir les fréquences des diverses composantes de la vibration.
EP92916034A 1992-04-15 1992-04-15 Systeme de regulation de vibrations ameliore au moyen d'un resonateur adaptable Expired - Lifetime EP0636287B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT92916034T ATE186614T1 (de) 1992-04-15 1992-04-15 Verbesserte vibriationsunterdrückungsschaltung mit adaptivem resonator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/US1992/003024 WO1993021687A1 (fr) 1992-04-15 1992-04-15 Systeme de regulation de vibrations ameliore au moyen d'un resonateur adaptable
CA002118210A CA2118210C (fr) 1992-04-15 1992-04-15 Systeme adaptatif de controle des vibrations a resonateurs

Publications (3)

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EP0636287A1 EP0636287A1 (fr) 1995-02-01
EP0636287A4 EP0636287A4 (fr) 1996-02-07
EP0636287B1 true EP0636287B1 (fr) 1999-11-10

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Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2905973A1 (de) * 1979-02-16 1980-08-28 Gauting Gmbh Apparatebau Schwingungstilger
DE3025794C2 (de) * 1980-07-08 1984-09-20 Didier-Werke Ag, 6200 Wiesbaden Einrichtung zum Unterdrücken von bei befeuerten Industrieöfen, insbesondere Winderhitzern, auftretenden Schwingungen
US4742998A (en) * 1985-03-26 1988-05-10 Barry Wright Corporation Active vibration isolation system employing an electro-rheological fluid
IL77057A (en) * 1985-03-26 1990-03-19 Wright Barry Corp Active vibration isolation system
DE3670893D1 (de) * 1985-07-31 1990-06-07 Wright Barry Corp Parametergesteuertes aktives schwingungsdaempfungssystem.
JPH0718470B2 (ja) * 1987-07-20 1995-03-06 日産自動車株式会社 制御型防振装置
US4981309A (en) * 1989-08-31 1991-01-01 Bose Corporation Electromechanical transducing along a path

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EP0636287A4 (fr) 1996-02-07
CA2118210C (fr) 1998-08-04
CA2118210A1 (fr) 1993-10-28
EP0636287A1 (fr) 1995-02-01

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