EP0572492B1 - Procede et appareil servant a affaiblir les vibrations acoustiques dans un milieu - Google Patents

Procede et appareil servant a affaiblir les vibrations acoustiques dans un milieu Download PDF

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Publication number
EP0572492B1
EP0572492B1 EP92905463A EP92905463A EP0572492B1 EP 0572492 B1 EP0572492 B1 EP 0572492B1 EP 92905463 A EP92905463 A EP 92905463A EP 92905463 A EP92905463 A EP 92905463A EP 0572492 B1 EP0572492 B1 EP 0572492B1
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EP
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Prior art keywords
resonator
signal
medium
frequency
selected frequency
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EP92905463A
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German (de)
English (en)
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EP0572492A1 (fr
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Anthony Malcolm Mcdonald
Stephen Mark Hutchins
Ian Stothers
Philip John Crowther
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Lotus Cars Ltd
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Lotus Cars Ltd
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    • 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
    • G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects

Definitions

  • This invention relates to a method and apparatus for attenuating acoustic vibrations in a medium, and more particularly to a method and apparatus to control a tunable acoustic resonator to effect such attenuation.
  • an acoustic resonator can be used to attenuate acoustic vibration in a system (DE 3729765).
  • the resonant frequency of the resonator and hence the frequency of the acoustic vibrations that are attenuated in a system is dependent on the dimensions and structure or type of resonator employed.
  • resonators of fixed structure are employed as disclosed in DE 3729765. This arrangement is however limited in that if the frequency of the acoustic vibration to be attenuated changes, then the efficiency of the resonator as an attenuator decreases as the frequency moves away from the resonant frequency.
  • a resonator is disclosed in EP 0039459 which attempts to overcome this limitation in relation to the use of a resonator to attenuate the noise generated by a turbo machine.
  • Two specific types of resonators are disclosed, one being a quarter wave resonator and the other being a Helmholtz resonator.
  • the resonant frequency of the quarter wave resonator is varied by varying the length of pipe, whilst the resonant frequency of the Helmholtz resonator is varied by varying the volume of the resonant chamber.
  • the resonant frequency is variable to enable attenuation of unwanted variable frequency acoustic vibrations created by the turbo machine. This document does not however address the problem of how such resonators can be accurately controlled.
  • the present invention provides apparatus for attenuating acoustic vibrations in a medium, said apparatus comprising a tunable acoustic resonator with an open end for interfacing with said medium outside of said resonator, at least one transducer to provide a first signal indicative of a dynamic parameter of the medium within said resonator, and a resonator controller operable in response to said first signal to tune said resonator to a selected frequency of said acoustic vibrations.
  • the present invention also provides a method of attenuating acoustic vibrations in a medium comprising the steps of interfacing a tunable acoustic resonator with said medium outside of said resonator, measuring a dynamic parameter of the medium within said resonator to give a first signal, and tuning said resonator to a selected frequency of said acoustic vibrations in response to said first signal.
  • the present invention is applicable to any acoustic resonators such as a quarter wave resonator, a Helmholtz resonator or a mechanical resonator.
  • the first signal can provide a measure of the dynamic pressure at a point within the resonant chamber.
  • the first signal can provide a measure of the motion of the oscillating mass. If an air chamber is used as the spring for a mechanical resonator then the first signal can provide a measure of the dynamic pressure within the chamber.
  • the resonator controller is operative to determine said selected frequency in response to a predetermined characteristic of said first signal and to tune said resonator so as to maximise the amplitude of said first signal at said selected frequency.
  • the present invention can provide for the adaptive control of a resonator without the need for any external signal indicating the frequency of the acoustic vibrations to be attenuated.
  • an algorithm would be performed using digital processing apparatus which had stored the characteristics of the resonator and which could therefore calculate the frequency of the acoustic vibrations reaching the resonator and attenuate the frequency with the largest amplitude for example.
  • the processing apparatus in this instance has knowledge of the dimensions of the resonator for example. This could be obtained from knowledge of for example the position of a piston moveable to vary the resonant volume in a Helmholtz or quarter wave resonator.
  • the processor may alternatively be an analogue processor.
  • a reference means provides a reference signal indicative of said selected frequency and the resonator controller is operative to tune said resonator so as to maximise the amplitude of said first signal at said selected frequency.
  • An arrangement that can accomplish this comprises a filter means to band-pass filter the first signal at the reference signal frequency, wherein said resonator controller is operative to tune said resonator so as to maximise the amplitude of the band-pass filtered first signal.
  • the apparatus includes a second signal indicative of a dynamic parameter of said medium outside of said resonator and reference means providing a reference signal indicative of said selected frequency, wherein said resonator controller is operative to tune said resonator so as to maintain the phase difference between the first and second signals at said selected frequency substantially at 90°.
  • the resonator controller preferably includes a band-pass filter for each of said first and second signals, to band-pass filter each resonator signal at said reference signal frequency, a multiplier to receive the filtered first and second signals and output a combined signal and an integrator or low pass filter to receive the combined signal and output a resonator control signal.
  • a transducer can be provided in the medium to provide the second signal indicative of the dynamic pressure within the medium outside of said resonator.
  • the second transducer provides a measure of the force applied to the resonator whilst the first transducer provides a measure of the response by the resonator to that force.
  • the present invention is applicable for use in the reduction of transmission of acoustic vibrations along a duct, and in particular to the reduction of acoustic vibrations along an exhaust or inlet pipe of an internal combustion engine; although the present invention is by no means limited as such and may be used to reduce unwanted acoustic vibrations in any system.
  • the reference means may comprise either a peak detection filter to detect the frequency of the acoustic vibrations with the largest amplitude, or it can provide a synchronising signal to the rotation rate of the engine.
  • the resonator controller is operative to detect the frequency of the acoustic vibrations with the largest amplitude by utilising its knowledge of the characteristics of the resonator.
  • Figure 1 illustrates three types of resonators that can be employed in cancelling undesired acoustic vibration.
  • the resonators are shown connected to a duct 2, although the present invention is not limited as such.
  • the resonator could be a Helmholtz resonator 1 where the air mass in the neck oscillates on the natural spring created by the air in the bulb. Damping is produced partly by flow effects in the neck, but mainly by sound radiation into the duct.
  • ⁇ o C S lV
  • the resonant frequency of the resonator can be adjusted by adjustinq the neck length, neck area or bulb volume.
  • the resonator could be a quarter wave length resonator 3, which can be viewed as a special case of a Helmholtz resonator, where the neck and the bulb have the same diameter.
  • the effective mass and stiffness are both continuous.
  • the resonant frequency of the quarter wave length resonator can be adjusted by varying the length of the side branch. This can be implemented for example by using a sliding piston.
  • the resonator can also be a mechanical resonator 4 with a piston of mass M on a spring in a side branch.
  • the most simple arrangement is to adjust the spring stiffness. This could be adjusted for example by having a variable rate spring or a compressed gas spring where the spring stiffness is proportional to the gas pressure.
  • any one or more of these three parameters can be measured.
  • accurate control of the resonator can be implemented since the accurate resonant frequency of the resonator is known.
  • the measurement of, for instance, gas pressure within the resonator has the advantage of automatically compensating for any temperature variations that may occur between the medium in which the undesired acoustic vibrations are being transmitted and the medium contained within the resonant cavity.
  • control schemes that can be used to ensure that resonance is obtained at the desired frequency can be based on the three common behavioural characteristics of the resonator at resonance in that:
  • the third control arrangement has the advantage that by measuring the phase, one has direct knowledge of which direction to make adjustments of the resonance frequency of the resonator, thus making adaption very fast and robust.
  • the control system is fully adaptive and can respond to local changes in the environment (sound, speed, temperature, etc.).
  • the required parameters of the resonator can be measured using transducers and the output of these transducers can be filtered so as to be sensitive only to the frequency of interest, i.e. the undesired acoustic vibration frequency. This frequency is selected according to the desired function of the resonator.
  • any of the resonators hereinbefore described are attached to attenuate acoustic vibrations in a medium (e.g. in a duct), sound travelling in the medium (along the duct) will be reflected at the point of fixture. This is how the resonators operate to minimise transmission of acoustic vibrations through the medium.
  • a resonator can be used in the inlet or exhaust of an internal combustion engine to minimise transmitted sound especially at the resonant frequency or frequencies.
  • the resonator can be automatically tuned by adjusting its effective mass or spring parameters.
  • the frequency of interest can be selected in several ways. It can have a fixed relation to one harmonic of the engine and can be obtained from an engine tachometer signal for example. Alternatively, it can automatically be chosen to be the frequency at which attenuation would be the most effective at any given time. This could be achieved by identifying the loudest frequency component from for example a tailpipe or inlet microphone and the resonator could be adapted to that frequency.
  • a resonator controller could have stored in a memory the characteristics of the resonator and could perform an algorithm to ascertain the frequency of the acoustic vibrations impinging on the open end of the resonator having the largest amplitude. The resonator could then be tuned to this frequency.
  • resonators need not be confined to use in ducts.
  • the resonators may be used to control noise in a volume such as a vehicle cabin and to improve the efficiency of acoustic attenuation an array of such resonators may be used.
  • Figure 2 illustrates a quarter wave resonator 3, attached to a duct 2 via an open end 5.
  • the length of the side branch and hence the resonant frequency of the resonator is adjustable using a piston 6 attached to a movable far end wall 7 of the resonator.
  • the piston 6 is driven by a motor 8 which is controlled by a control signal transmitted on line 9.
  • the transducer 11 provides a measure of the dynamic pressure of the gas at the far end wall of the resonator.
  • Signals from the transducer 11 are filtered by a band-pass filter 12, the centre frequency of which is controlled by a signal on line 13 which in this example of this invention is provided from a tachometer 14 of an internal combustion engine.
  • the band-pass filter filters the dynamic pressure signals from the transducer 11 to provide a measure of the dynamic pressure at the selected frequency of the acoustic vibrations to be attenuated.
  • the output signal from the band-pass filter 12 is then input into a maximum signal detector 15 which detects any decrease in the amplitude of the signal at the required frequency. If a decrease is detected then a signal is output via the amplifier 16 on line 9 to the motor to move the piston 6 and the far end wall 7 to adjust the resonant frequency of the resonator.
  • FIG. 3 illustrates a second embodiment of the present invention in which a Helmholtz resonator 1 is connected to a duct 2 via a neck portion 20.
  • the Helmholtz resonator has a resonant chamber 21 the volume of which can be varied by moving a far end wall 22 by the action of a piston 6 driven by a motor 8.
  • a neck insert 25 which is attached to the far end wall 22 and moves therewith in unison.
  • the pressure of the gas within the resonant cavity 21 is measured by a transducer 26 whilst the pressure of the gas in the duct 2 is measured by transducer 27.
  • the signals from these two transducers 26 and 27 are individually filtered by band-pass filters 31 and 32 the centre frequencies of which are controlled by a signal on line 28.
  • the signal on line 28 represents the selected frequency of the acoustic vibrations to be attenuated, and this signal is provided from filter 29 by peak selection filtering of a signal representing the acoustic vibrations at a position in the duct upstream of the resonator as measured by a transducer 30.
  • the selected frequency of the filtered acoustic vibrations that are to be attenuated is decided by selecting the acoustic vibrations in the duct having the largest amplitude.
  • the signals from the transducers 26 and 27 after having been filtered by band-pass filters 31 and 32 are multiplied together by the multiplier 33.
  • the multiplied signal from the multiplier 33 is then applied to an integrator 34 which supplies the resonator control signal on line 35 to the motor 34 to move the piston 23 and far end wall 22 in order to change the resonant cavity volume, and hence the resonant frequency of the resonator.
  • the neck length as well as the volume of the Helmholtz resonator is varied. This provides for extra sensitivity, although only one parameter need be varied.
  • the two filtered pressure signals provided from transducers 26 and 27 after filtering in the band-pass filters 31 and 32, will generally have a phase difference of ⁇ between them.
  • x(t) k/2 (Cos ⁇ - Cos(2w o t+ ⁇ ))
  • the integrator output, y(t) will be approximately y(t) ⁇ k/2 Cos ⁇ (t)
  • a low pass filter could alternatively be used instead of the integrator 34 to provide y(t).
  • FIG. 4 this diagram illustrates the use of a mechanical resonator 4 attached to a duct 2 for a fluid or gas medium.
  • the mechanical resonator comprises a mass 40 suspended at the interface between the resonator 4 and the duct 2 by a diaphragm 41.
  • the diaphragm 41 forms an airtight seal across the interface sealing gas in a cavity 42.
  • the cavity 42 has a preset regulator valve 43 regulating gas provided by a pump 44.
  • the cavity 42 also has a motorised valve 45 to control the pressure there within.
  • a transducer in the form of a microphone 27 is provided within the duct adjacent to the interface with the resonator to provide a measure of the pressure in the duct and hence the force applied to the resonator.
  • a transducer 47 providing signals indicative of the pressure within the cavity 42.
  • the signals from the transducers 27 and 47 are band-pass filtered in filters 31 and 32 with the centre frequency of the filters 31 and 32 controlled by a signal on line 13.
  • the signal on line 13 provides a signal representative of the selected frequency of the acoustic vibrations to be attenuated.
  • such a signal is provided from the tachometer 14 of an internal combustion engine.
  • the filtered signals from the transducers 27 and 47 are then multiplied in the multiplier 33 and the combined signal integrated in integrator 34 to provide the resonator control signal on line 35 which is amplified in amplifier 16 to provide the control signal which controls the motorised valve 45 in order to control the pressure of the gas within the cavity 42.
  • the pump 44 provides a constant head of pressure which can be controlled by the preset regulator valve 43, and the pressure in the resonator cavity 42 is varied by opening or closing the motorised valve 45.
  • ⁇ o 1 2 ⁇ K eff M
  • K eff K 1 + K 2
  • this diagram illustrates a Helmholtz resonator 1 connected to a duct 2 via a neck 20.
  • the volume of the cavity 21 within the resonator is varied by partially filling it with an incompressible fluid 60.
  • the control arrangement illustrated in this diagram is the same as that illustrated in Figure 2 for the quarter wave resonator and like reference numerals denote like components.
  • the resonator control signal produced by the controller controls a positive displacement pump 61 which pumps fluid either from or to the reservoir 62.
  • FIG. 6 this diagram illustrates use of the same control system as described in Figures 2 and 5 to control a mechanical resonator 4.
  • the mass 40 is provided with an accelerometer 46 which measures the motion of the mass 40.
  • the signal provided from the accelerometer is equivalent to that provided by the transducer 47 in Figure 4.
  • the signal from this is then utilised by the control system as described in relation to Figures 2 and 5 to control the motorised valve 45 as described with respect to Figure 4.
  • the resonator controller is different and comprises a digital processing apparatus 70 which has stored characteristics of the resonator to enable it to deconvolve the effects of the resonator on the acoustic vibrations impinging on the open end 5 of the resonator and hence determine the frequency component of the acoustic noise with the largest amplitude.
  • a control signal is then output on line 9 to the motor 8 to tune the resonator to the frequency at which the largest amplitude has been detected.
  • the characteristics of the resonator need be input to the processor only once and the system needs no reference signals. This system could be used where only small changes in the fluid properties (temperature etc.) are expected.
  • a first signal indicative of the vibrations in the resonator 1, 3 or 4 is band-pass filtered with the centre frequency of the band-pass filter 12 being set at the selected frequency of the acoustic vibrations to be attenuated, the centre frequency being controlled by a second signal on the line 13.
  • the amplitude of this filtered signal is then detected by a maximum signal detector 15 and a resonator control signal output to maximise the amplitude of the measured first signal at the selected frequency of the acoustic vibrations to be attenuated.
  • the first signal can either be a measure of the motion of the mass 40 in a mechanical resonator 4 or it can be a measure of the pressure at a point within the resonant cavity 10 or 21 of either a quarter wave or Helmholtz resonator.
  • First signals from the first transducers 26 and 47 and second signals from the second transducers 27 are band-pass filtered at the selected frequency of the acoustic vibration to be attenuated.
  • the filtered signals are then multiplied and integrated or filtered to provide a resonator control signal on line 35.
  • the resonator control signal will be output whenever the phase difference between the signals from the first and second transducers 26 and 27 or from the first and second transducers 47 and 27 strays from a value of approximately 90°. It is a condition of resonance that to a good approximation the phase difference between these two signals should be 90° and therefore any deviation from this phase difference indicates a drift from resonance.
  • This technique has the advantage that the resonator control signal output from the integrator 34 gives an indication of the direction in which to adjust the resonant frequency.
  • a resonator and control system as hereinbefore described is used to cancel undesired acoustic noise in a duct, it may be the case that significant force is transmitted to the resonator housing by the action of the resonator.
  • a symmetric arrangement of resonators, or a resonator of intrinsic axial symmetry can be used.
  • control systems illustrated in Figures 2 to 6 may be implemented either digitally or in an analogue manner.
  • the present invention can thus provide a compact unit comprising a resonator and a control system for use in the attenuation of undesired acoustic vibrations in a system such as a duct.

Abstract

On décrit un appareil servant à affaiblir les vibrations acoustiques dans un milieu, comprenant un résonateur acoustique (3) pouvant être accordé et présentant une extrémité ouverte (5) qui doit être relié au milieu, au moins un transducteur (11) servant à produire un signal de résonateur indiquant un paramètre dynamique du milieu, à l'intérieur du résonateur (3), et un élément de commande de résonateur (8) pouvant être activé en réponse au signal de résonateur pour accorder le résonateur (3) à une fréquence choisie des vibrations acoustiques.

Claims (31)

  1. Appareil pour atténuer les vibrations acoustiques dans un milieu, ledit appareil comprenant un résonateur acoustique pouvant être accordé avec une extrémité ouverte pour réaliser une interface avec ledit milieu à l'extérieur dudit résonateur, au moins un transducteur pour délivrer un premier signal indicatif d'un paramètre dynamique dudit milieu à l'intérieur du résonateur, et un dispositif de commande de résonateur fonctionnant en réponse audit premier signal de façon à accorder ledit résonateur à une fréquence sélectionnée desdites vibrations acoustiques.
  2. Appareil selon la revendication 1, dans lequel ledit dispositif de commande de résonateur fonctionne de façon à déterminer ladite fréquence sélectionnée en réponse à une caractéristique prédéterminée dudit premier signal indicatif du paramètre dynamique dudit milieu et à accorder ledit résonateur de façon à maximiser l'amplitude dudit premier signal à ladite fréquence sélectionnée.
  3. Appareil selon la revendication 1, comprenant des moyens de référence délivrant un signal de référence indicatif de ladite fréquence sélectionnée, dans lequel ledit dispositif de commande de résonateur fonctionne de façon à accorder ledit résonateur de façon à maximiser l'amplitude dudit premier signal indicatif du paramètre dynamique dudit milieu à ladite fréquence sélectionnée.
  4. Appareil selon la revendication 3, dans lequel ledit dispositif de commande de résonateur comprend des moyens formant filtre pour filtrer avec une bande passante ledit premier signal indicatif du paramètre dynamique dudit milieu à ladite fréquence de signal de référence, ledit dispositif de commande de résonateur fonctionnant de façon à accorder ledit résonateur de façon à maximiser l'amplitude du premier signal filtré avec une bande passante.
  5. Appareil selon la revendication 1, comprenant un deuxième transducteur pour délivrer un deuxième signal indicatif d'un paramètre dynamique dudit milieu à l'extérieur dudit résonateur et des moyens de référence délivrant un signal de référence indicatif de ladite fréquence sélectionnée, dans lequel ledit dispositif de commande de résonateur fonctionne de façon à accorder ledit résonateur de façon à maintenir la différence de phase entre les premier et deuxième signaux à ladite fréquence sélectionnée sensiblement à 90°.
  6. Appareil selon la revendication 5, dans lequel ledit dispositif de commande de résonateur comprend un filtre passe-bande pour chacun desdits premier et deuxième signaux, afin de filtrer avec une bande passante chacun desdits signaux à ladite fréquence de signal de référence, un multiplicateur pour recevoir les signaux filtrés et délivrer en sortie un signal combiné et un intégrateur ou filtre passe-bas afin de recevoir le signal combiné et de délivrer en sortie un signal de commande de résonateur.
  7. Appareil selon la revendication 1, dans lequel ledit résonateur comporte une chambre résonante et un premier transducteur monté à l'intérieur de celle-ci de façon à délivrer le premier signal qui est une mesure de la pression dynamique du milieu en un point à l'intérieur de ladite chambre résonante, éloigné de ladite extrémité ouverte dudit résonateur.
  8. Appareil selon l'une quelconque des revendications précédentes, dans lequel ledit résonateur est un résonateur de Helmholtz.
  9. Appareil selon la revendication 7, dans lequel ledit résonateur est un résonateur quart d'onde et ledit premier transducteur est monté sur une paroi d'extrémité éloignée de ladite chambre résonante.
  10. Appareil selon la revendication 8 ou la revendication 9, dans lequel ledit dispositif de commande de résonateur comprend des moyens pour déplacer une paroi d'extrémité éloignée de ladite chambre résonante.
  11. Appareil selon l'une quelconque des revendications 1 à 7, dans lequel ledit résonateur est un résonateur mécanique avec une masse suspendue, ladite masse comportant un transducteur de mouvement qui est fixé à celle-ci afin de délivrer le premier signal qui est une mesure du mouvement de ladite masse.
  12. Appareil selon la revendication 11, dans lequel ledit transducteur de mouvement est un accéléromètre, de façon à délivrer une mesure de l'accélération de ladite masse.
  13. Appareil selon la revendication 11 ou la revendication 12, dans lequel ladite masse est suspendue par un diaphragme voisin de ladite extrémité ouverte dudit résonateur et l'effet de suspension est assuré par un gaz contenu dans une chambre par ledit diaphragme.
  14. Appareil selon la revendication 13, dans lequel la pression du gaz à l'intérieur de la cavité est contrôlée par ledit dispositif de commande de résonateur.
  15. Appareil selon l'une quelconque des revendications 5 à 14, comprenant un deuxième transducteur monté dans ledit milieu à l'extérieur dudit résonateur afin de délivrer ledit deuxième signal qui est indicatif de la pression dynamique à l'intérieur dudit milieu à l'extérieur dudit résonateur.
  16. Appareil selon l'une quelconque des revendications précédentes, adapté pour réduire la transmission de la vibration acoustique indésirable le long d'un conduit.
  17. Appareil selon l'une quelconque des revendications précédentes, adapté pour réduire la transmission de la vibration acoustique le long d'un tuyau d'échappement venant d'un moteur à combustion interne.
  18. Appareil selon l'une quelconque des revendications 3 à 17, dans lequel lesdits moyens de référence comprennent un filtre de détection de pic pour détecter la fréquence des vibrations acoustiques avec la plus grande amplitude et délivrer en sortie ledit signal de référence à ladite fréquence.
  19. Appareil selon la revendication 17, dans lequel lesdits moyens de référence agissent de façon à synchroniser ledit signal de référence à la vitesse de rotation dudit moteur.
  20. Procédé d'atténuation de vibrations acoustiques dans un milieu, comprenant les étapes de mise en interface d'un résonateur acoustique pouvant être accordé avec ledit milieu à l'extérieur dudit résonateur, de mesure d'un paramètre dynamique du milieu à l'intérieur dudit résonateur pour donner un premier signal, et d'accord dudit résonateur à une fréquence sélectionnée desdites vibrations acoustiques en réponse audit premier signal.
  21. Procédé selon la revendication 20, comprenant les étapes de détermination de ladite fréquence sélectionnée en réponse à une caractéristique prédéterminée dudit premier signal indicatif du paramètre dynamique du milieu à l'intérieur du résonateur et d'accord dudit résonateur de façon à maximiser l'amplitude dudit premier signal à ladite fréquence sélectionnée.
  22. Procédé selon la revendication 20, comprenant les étapes de mesure de ladite fréquence sélectionnée afin de délivrer un signal de référence, et d'accord dudit résonateur de façon à maximiser l'amplitude dudit premier signal indicatif du paramètre dynamique du milieu à l'intérieur du résonateur à ladite fréquence sélectionnée.
  23. Procédé selon la revendication 22, comprenant les étapes de filtrage à une bande passante dudit premier signal au moins à ladite fréquence de signal de référence et d'accord dudit résonateur de façon à maximiser l'amplitude du premier signal filtré à une bande passante.
  24. Procédé selon la revendication 20, comprenant les étapes de mesure de ladite fréquence sélectionnée afin de délivrer un signal de référence, de délivrance d'un deuxième signal, et d'accord dudit résonateur de façon à maintenir la différence de phase entre les premier et deuxième signaux à ladite fréquence sélectionnée sensiblement à 90°.
  25. Procédé selon la revendication 24, comprenant l'étape de filtrage à une bande passante de chacun desdits premier et deuxième signaux à ladite fréquence de signal de référence, de multiplication des signaux filtrés et d'intégration des signaux multipliés afin de délivrer un signal de commande de résonateur.
  26. Procédé selon l'une quelconque des revendications 20 à 25, comprenant l'étape de mesure de la pression dynamique du milieu dans le résonateur en un point dans une chambre dudit résonateur, éloigné de l'interface dudit résonateur avec ledit milieu, de façon à délivrer le premier signal.
  27. Procédé selon la revendication 26, dans lequel ladite étape d'accord dudit résonateur comprend l'étape de déplacement d'une paroi d'extrémité éloignée de ladite chambre.
  28. Procédé selon l'une quelconque des revendications 20 à 26, dans lequel ledit résonateur est un résonateur mécanique avec une masse suspendue, ledit procédé comprenant l'étape de mesure du mouvement de ladite masse afin de délivrer le premier signal.
  29. Procédé selon la revendication 28, dans lequel le mouvement de ladite masse est mesuré à l'aide d'un accéléromètre.
  30. Procédé selon la revendication 28 ou la revendication 29, dans lequel ladite masse est suspendue par un diaphragme et est adjacente à ladite interface, et ledit effet de suspension est assuré par une chambre contenant un gaz, ledit procédé comprenant les étapes d'accord dudit résonateur par contrôle de la pression dudit gaz dans ladite chambre.
  31. Procédé selon l'une quelconque des revendications 24 à 30, comprenant l'étape de mesure de la pression dynamique à l'intérieur dudit milieu à l'extérieur dudit résonateur afin de délivrer ledit deuxième signal.
EP92905463A 1991-02-21 1992-02-21 Procede et appareil servant a affaiblir les vibrations acoustiques dans un milieu Expired - Lifetime EP0572492B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB9103689A GB2253076B (en) 1991-02-21 1991-02-21 Method and apparatus for attenuating acoustic vibrations in a medium
GB9103689 1991-02-21
PCT/GB1992/000314 WO1992015088A1 (fr) 1991-02-21 1992-02-21 Procede et appareil servant a affaiblir les vibrations acoustiques dans un milieu

Publications (2)

Publication Number Publication Date
EP0572492A1 EP0572492A1 (fr) 1993-12-08
EP0572492B1 true EP0572492B1 (fr) 1997-11-19

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EP92905463A Expired - Lifetime EP0572492B1 (fr) 1991-02-21 1992-02-21 Procede et appareil servant a affaiblir les vibrations acoustiques dans un milieu

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EP (1) EP0572492B1 (fr)
JP (1) JPH06510870A (fr)
DE (1) DE69223238T2 (fr)
GB (1) GB2253076B (fr)
WO (1) WO1992015088A1 (fr)

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US8077873B2 (en) 2009-05-14 2011-12-13 Harman International Industries, Incorporated System for active noise control with adaptive speaker selection
US8135140B2 (en) 2008-11-20 2012-03-13 Harman International Industries, Incorporated System for active noise control with audio signal compensation
US8189799B2 (en) 2009-04-09 2012-05-29 Harman International Industries, Incorporated System for active noise control based on audio system output
US8199924B2 (en) 2009-04-17 2012-06-12 Harman International Industries, Incorporated System for active noise control with an infinite impulse response filter
US8718289B2 (en) 2009-01-12 2014-05-06 Harman International Industries, Incorporated System for active noise control with parallel adaptive filter configuration
US9020158B2 (en) 2008-11-20 2015-04-28 Harman International Industries, Incorporated Quiet zone control system
CN109654067A (zh) * 2017-10-12 2019-04-19 英业达科技有限公司 静音风扇

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DE4402699C2 (de) * 1994-01-29 1996-01-11 Continental Ag Vorrichtung zur Verminderung des Reifen/Fahrbahngeräusches
US5920173A (en) * 1995-11-15 1999-07-06 Applied Power Inc. Feedback enhanced adaptively tuned vibration absorber
US5710714A (en) * 1995-11-15 1998-01-20 Applied Power Inc. Electronic controller for an adaptively tuned vibration absorber
US5695027A (en) * 1995-11-15 1997-12-09 Applied Power Inc. Adaptively tuned vibration absorber
JPH09212175A (ja) * 1996-01-30 1997-08-15 Ricoh Co Ltd 消音装置
US5930371A (en) * 1997-01-07 1999-07-27 Nelson Industries, Inc. Tunable acoustic system
US6295363B1 (en) 1997-03-20 2001-09-25 Digisonix, Inc. Adaptive passive acoustic attenuation system
DE19743482A1 (de) * 1997-10-01 1999-04-08 Mann & Hummel Filter Schalldämpfer mit einem Nebenschlußresonator
DE19841975B4 (de) * 1998-09-14 2004-02-12 Continental Aktiengesellschaft Schallabsorbierende Platte
DE19861018C2 (de) * 1998-12-15 2001-06-13 Fraunhofer Ges Forschung Gesteuerter akustischer Wellenleiter zur Schalldämpfung
DE10002984C1 (de) 2000-01-24 2001-08-09 Daimler Chrysler Ag Akustischer Absorber und Verfahren zur Schallabsorption
DE10159487C1 (de) * 2001-12-04 2003-02-20 Eberspaecher J Gmbh & Co Aktiver Schalldämpfer für Abgasanlagen
EP1476699B1 (fr) 2002-01-16 2013-11-13 Alstom Technology Ltd Chambre de combustion et dispositif d'amortissement destiné a reduire des pulsations de chambre de combustion dans un système de turbines a gaz
US6998949B2 (en) 2002-05-08 2006-02-14 Koninklijke Philips Electronics N.V. Magnetic resonance imaging (MRI) system comprising acoustic resonators
EP1621042B1 (fr) * 2003-04-28 2008-01-16 Oticon A/S Microphone, appareil de correction auditive dote d'un microphone et structure d'entree pour microphone
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EP3070710A1 (fr) * 2015-03-18 2016-09-21 Plum Sp. z o.o. Procédé de mesure de son dans un guide d'ondes, en particulier dans un système de ventilation et dispositif permettant de mettre en oeuvre le procédé
JP6868571B2 (ja) * 2015-05-06 2021-05-12 エーエスエムエル ネザーランズ ビー．ブイ． リソグラフィ装置
JP6527828B2 (ja) * 2016-02-08 2019-06-05 飛島建設株式会社 汎用型消音器
DE102018103175B3 (de) 2018-02-13 2019-03-21 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Rotoranordnung
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Publication number Priority date Publication date Assignee Title
US8135140B2 (en) 2008-11-20 2012-03-13 Harman International Industries, Incorporated System for active noise control with audio signal compensation
US8270626B2 (en) 2008-11-20 2012-09-18 Harman International Industries, Incorporated System for active noise control with audio signal compensation
US8315404B2 (en) 2008-11-20 2012-11-20 Harman International Industries, Incorporated System for active noise control with audio signal compensation
US9020158B2 (en) 2008-11-20 2015-04-28 Harman International Industries, Incorporated Quiet zone control system
US8718289B2 (en) 2009-01-12 2014-05-06 Harman International Industries, Incorporated System for active noise control with parallel adaptive filter configuration
US8189799B2 (en) 2009-04-09 2012-05-29 Harman International Industries, Incorporated System for active noise control based on audio system output
US8199924B2 (en) 2009-04-17 2012-06-12 Harman International Industries, Incorporated System for active noise control with an infinite impulse response filter
US8077873B2 (en) 2009-05-14 2011-12-13 Harman International Industries, Incorporated System for active noise control with adaptive speaker selection
CN109654067A (zh) * 2017-10-12 2019-04-19 英业达科技有限公司 静音风扇

Also Published As

Publication number Publication date
EP0572492A1 (fr) 1993-12-08
GB9103689D0 (en) 1991-04-10
DE69223238T2 (de) 1998-05-28
GB2253076A (en) 1992-08-26
DE69223238D1 (de) 1998-01-02
JPH06510870A (ja) 1994-12-01
WO1992015088A1 (fr) 1992-09-03
GB2253076B (en) 1994-08-03

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