WO2008101452A1 - Résonateur à large bande pour réduire les vibrations et le bruit de pièces excitées par vibrations, notamment de pièces techniques - Google Patents

Résonateur à large bande pour réduire les vibrations et le bruit de pièces excitées par vibrations, notamment de pièces techniques Download PDF

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Publication number
WO2008101452A1
WO2008101452A1 PCT/DE2007/002073 DE2007002073W WO2008101452A1 WO 2008101452 A1 WO2008101452 A1 WO 2008101452A1 DE 2007002073 W DE2007002073 W DE 2007002073W WO 2008101452 A1 WO2008101452 A1 WO 2008101452A1
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WO
WIPO (PCT)
Prior art keywords
vibration
resonator
resonator element
excited
component
Prior art date
Application number
PCT/DE2007/002073
Other languages
German (de)
English (en)
Inventor
Thomas Borchert
Emilie Debauche
Katharina Kompe
Original Assignee
Fachhochschule Dortmund
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Fachhochschule Dortmund filed Critical Fachhochschule Dortmund
Priority to EP07817795A priority Critical patent/EP2126899A1/fr
Publication of WO2008101452A1 publication Critical patent/WO2008101452A1/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
    • G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects

Definitions

  • the invention relates to a resonator for vibration and noise reduction of technical systems according to the preamble of claim 1.
  • Conventional vibration absorbers such as in US Pat. No. 6,478,110 B1, are also only of limited suitability for vibration and thus noise reduction, since they work only in a monofrequential manner in their block-shaped structure, which is to be considered mechanically as a point mass and is usually mounted on spring elements, ie only are aligned with a frequency and do not calm higher natural vibration orders, bring about a relatively high additional mass and, with the coupling to the component to be soothed, generate new potential resonant frequency positions due to the resulting coupling frequencies of the component / absorber system. For example, by a variable-speed engine, cause new acoustic interference.
  • the object of the present invention is therefore to further develop a generic resonator in such a way that the above-described disadvantages are eliminated and a possible frequency-independent damping of the components over a large frequency range is made possible.
  • the invention relates to a resonator for vibration and noise reduction in particular technical components, comprising at least one substantially bar-shaped resonator element, which is arranged on a portion of the component.
  • a generic resonator is further developed in accordance with the invention by virtue of the fact that at least sections of a damping layer are arranged on or on the resonator element. It has been found that even by only a relatively small-area arrangement of the damping material on the resonator element, a substantial improvement in the damping properties of the entire resonator can be achieved with neither even self-resonator elements alone with a large occupancy of the components to be damped itself To achieve the damping material so. As a result of the geometric variation of the bar-shaped structure of the resonator element, it is possible, in addition to the tuning of the first resonator natural frequency, to be related to the resonator element.
  • the natural resonant frequency of the basic system can also be used to tune the higher resonator natural frequencies to the higher natural frequencies of the fundamental system (broadband effect).
  • Its strip-shaped design is acoustically uncritical due to its low Schallabstrahlgrades and also allows a geometrical in situ integration into the component to be damped about by slot, for example in multi-walled body panels of a vehicle in the inner surfaces, which are usually covered , In this way, additional masses are completely avoided.
  • the coupling frequency positions in which the beam-shaped resonator element carries out large oscillation amplitudes and potentially causes the mounting surface of the component to oscillate due to its bearing coupling are calmed by largely reducing this feedback effect by a damping layer applied locally preferably in the bearing region of the resonator (FIG Broadband effect).
  • a damping layer applied locally preferably in the bearing region of the resonator (FIG Broadband effect).
  • FOG Broadband effect In order not to impair the eradication efficiency, it is also possible to form the damping layer over the entire surface of the resonator element.
  • a resonator is used in the design described here - also in the sense of its multi-eigenfrequential matching to the resonance frequency positions of the component to be damped.
  • the broadband effect of the resonator through the damping layer is ensured even at a low overall height in the design according to the invention.
  • the damping effect is achieved.
  • this makes it possible, in particular for the damping of structural parts such as components on machines or the like, to achieve significant reductions in structure-borne noise and hence in acoustic emission with substantially smaller changes in the components.
  • the damping layer can be formed from a film-like layer with high internal friction.
  • a damping layer dissipates a considerable part of the oscillation energy which is coupled into the resonator element and therefore ensures a corresponding reduction in the oscillation energy of the resonator and via its coupling to the vibration-excited component and the vibration energy of the vibration-excited component.
  • the damping layer may be arranged substantially on one side on the resonator element, for example, the damping layer between the portion of the vibration-excited component on which the resonator is arranged, and the resonator element are arranged.
  • the contact area between the resonator element and the vibration-excited component is decoupled by the damping layer and the damping layer allows only a part of the oscillation energy to pass between the two.
  • the damping layer is arranged at least in sections on the oscillating region of the resonator element. As a result, the oscillation of the resonator element is influenced in a targeted manner.
  • the resonator element is particularly efficient when it is designed as a cantilever beam.
  • the resonator element can be formed as a separate structural unit and mechanically coupled to the vibration-excited component.
  • the resulting additional mass is low and its height relatively flat, since it consists only of a beam.
  • the material of the resonator element is expediently made of a material which can readily vibrate, e.g. in the case of body components, for example, from the material of the vibration-excited component itself. For technical components steel or steel materials because of their good elastic properties.
  • the resonator element with a first end region is fixed on one side mechanically to the vibration-excited component and is freely swinging with its other-side bar-shaped region.
  • the vibration effects between the vibration-excited component and Resonatorelement mechanically securely coupled to each other, while the free-swinging bar-shaped area causes the desired vibration effects, which then by covering with the Attenuation layer does not transmit kinematic feedback effects to the fundamental system.
  • the resonator element is coupled to the vibration-excited component by means of an adapter which has a small area relative to the dimensions of the resonator element.
  • the resonator element is arranged as an additional structural unit, it is to be provided with a relatively small adapter which is to be formed at least to the same extent as the resonator element itself so that the oscillation amplitudes of the beam-shaped section can be freely performed.
  • the connections between resonator element and adapter as well as between adapter and vibration-excited component can be z. B. run with a high strength industrial adhesive.
  • the damping layer is formed in the region of the adapter as a damping foil with a one-sided or two-sided adhesive layer, on the adhesive surfaces of which the resonator element and / or the vibration-excited component are glued.
  • the damping layer on the resonator element can be formed only in the region of the adapter, for example by a damping foil with one-sided or two-sided adhesive surface, which in addition to the damping ability also solves the task of fixing resonator element and vibration-excited component together.
  • the resonator element is formed from the structure of the vibration-excited component itself.
  • the resonator has by its such surface integrative design option no independent and thus possibly disturbing height.
  • As an integrative unit of the vibration-excited component also no additional mass is added, but the resonator element is generated from the vibration-excited component itself.
  • Potential tuning changes with respect to the resonator target frequencies are negligible.
  • the resonator element is integrally formed with the first region from the vibration-excited component and connected to the vibration-excited component and is arranged freely swinging with its opposite bar-shaped region of the vibration-excited component.
  • the resonator element approximately directly connected in one piece with an end portion of its bar-shaped longitudinal extent with the vibration-excited component and separated over essential parts of its circumference by slots of the vibration-excited component such that the free end of the resonator excited by the vibration to be damped vibration of the vibrated component can oscillate substantially free ,
  • the bar-shaped resonator element has a mass between 1/5 and 1/20, preferably 1/10 of the mode-related oscillating mass of the vibration-excited component.
  • the bar-shaped resonator element then has e.g. about 4% of the oscillating mass of each component to be calmed.
  • the dimensions of the resonator element in terms of area achieve a larger surface portion of the vibration-excited component than in the case of a bar-shaped embodiment of the resonator element.
  • the resonator element is tuned to higher natural frequencies of the vibration-excited component, it may be necessary to leave the relatively narrow and long beam dimensions and to provide plate-shaped, spatially significantly larger resonator elements whose sound radiation behavior is likewise uncritical due to the 1/10 modal mass relation.
  • the mounting location of the resonator element is in this case to be positioned between the targeted vibration modes of the vibration-excited component while avoiding layers in vibration node lines.
  • the resonator element tuned to the first resonant oscillation mode is arranged with respect to its arrangement on the vibration-excited component at the location of the fundamental maximum of the respective section of the vibration-excited component. Since the vibrations of the vibration-excited component to be damped are greatest here, the damping effect of the resonator element can best be achieved.
  • the resonator element damps the natural vibration of the vibration-excited component multifrequently.
  • conventional measures for vibration reduction the resonator consistently consistent broadband efficient without additional mass and manufacturing technology is easy to train.
  • the resonator can also be designed from existing vibration-excited components such as chassis elements of vehicles (bifunctionality concept).
  • the damping layer In the case of an integrative embodiment of the resonator, it is advantageous for the damping layer to extend beyond the latter into the vibration-excited component at a level of approximately 10% of the length of the resonator element. To optimize the efficiency of the eradication process, the further application should extend over the entire surface of the resonator element.
  • FIG. 1 shows a schematic representation of the basic construction of a resonator element integrated into the vibration-excited component
  • FIG. 2 shows a schematic representation of the basic construction of a resonator element fixedly mounted on the vibration-excited component via an adapter
  • FIG. 3 shows a resonator element integrated in the vibration-excited component according to FIG. 1 with a damping layer largely applied over its entire area;
  • FIG. 5 shows a plot of the oscillation amplitude versus the frequency of an oscillatory system in the form of a plate without a resonator, with an undamped resonator and with a damped resonator according to the invention.
  • FIGS. 1 to 4 each show very schematic representations of the resonator according to the invention, in which a resonator element 2 is arranged on a vibration-excited component 1 shown as a planar sheet for the sake of simplicity. It goes without saying that both the dimensions and the shape of vibration-excited component 1 and resonator 2 are shown only simplified and are tuned for each case of application of the resonator according to the invention to the respective vibration behavior of the vibration-excited component 1.
  • FIG. 1 shows diagrammatically a beam-shaped longitudinally extended resonator element 2, which is integrally formed from the material of the vibration-excited component 1 in that a contiguous slot 4 is introduced into the material of the component 1 on three sides of the resonator element 2 and the resonance natorelement 2 so that tongue-like projecting from a fixing area 3 of the component 1.
  • the resonator element 2 surrounded by the slot 4 and delimited by the component 1 can oscillate freely, the excitation for this oscillation being due to the externally coupled oscillations of the component 1, which are caused, for example, by a drive motor (not shown), which is typically harmonic Vibration on the component 1 transmits.
  • FIG. 2 shows an alternative embodiment of the resonator with a resonator element 2 applied on the component 1 as a separate structural unit, which is spaced apart and arranged essentially parallel to the plane of the component 1. The distance is produced by an adapter 5, which is arranged at one end between component 2 and resonator element 2 and defines, for example, an adhesive connection between component 1 and resonator element 2 to one another.
  • the resonator element 2 with its cantilevered region can oscillate freely and operate as in the case of the resonator element 2 according to FIG.
  • the resonator elements 2 shown in FIGS. 1 and 2 are each coated with a high internal friction damping layer 6, such as by adhering a film-like damping layer to the resonator element 2, the oscillation behavior of the resonator element 2 is Elementes 2 in the manner described above improved so that the resulting by the resonator-basic system coupling new coupling natural frequencies are advantageously damped and thus a thorough improvement of the generation of sound can be achieved.
  • the damping layer 6 can be arranged wholly or partially on the surface of the resonator element 2, and it is also conceivable to arrange the damping layer 6 at the point of contact between component 1 and resonator 2 between component 1 and resonator 2 and thus component 1 and resonator 2 vibrationally to decouple from one another to a certain extent.
  • FIG. 5 plots an oscillation amplitude of an oscillatory system in the form of a plate over the frequency without a resonator (curve a), with an undamped resonator (curve b) and with a resonator of the invention dampened with different materials (curves c and d) which is intended to illustrate a qualitative assessment and illustration of the achievable with the resonator according to the invention damping.
  • the undamped plate is expected to produce the largest amplitude with a unique maximum at about 122 Hz.
  • the maximum amplitude is already significantly reduced with two maxima at approx. 110 Hz and approx. 140 Hz.
  • the maximum of the amplitude shifts to approx. 135 Hz with a simultaneous significant reduction of the amplitude maximum.
  • the maximum of the amplitude can be further reduced and, at the same time, a large smearing of the amplitude values over a larger frequency range can be achieved, whereby the acoustic emission can be further reduced.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne un résonateur pour réduire les vibrations et le bruit de pièces (1) excitées par vibrations, notamment de pièces techniques (1), présentant au moins un élément résonateur (2) essentiellement en forme de barre qui est disposé sur une partie (3) de la pièce (1) excitée par vibrations, une couche d'amortissement (6) étant disposée au moins par endroits sur le bord ou sur le dessus de l'élément résonateur (2). On a constaté avec étonnement que le simple fait de disposer le matériau d'amortissement (6) sur l'élément résonateur (2) uniquement sur une surface relativement petit permet d'ores et déjà d'obtenir une amélioration importante des propriétés d'amortissement de l'ensemble du résonateur.
PCT/DE2007/002073 2007-02-21 2007-11-16 Résonateur à large bande pour réduire les vibrations et le bruit de pièces excitées par vibrations, notamment de pièces techniques WO2008101452A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07817795A EP2126899A1 (fr) 2007-02-21 2007-11-16 Résonateur à large bande pour réduire les vibrations et le bruit de pièces excitées par vibrations, notamment de pièces techniques

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007009071.6 2007-02-21
DE102007009071 2007-02-21

Publications (1)

Publication Number Publication Date
WO2008101452A1 true WO2008101452A1 (fr) 2008-08-28

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WO (1) WO2008101452A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022117383A1 (de) 2022-07-12 2024-01-18 Bayerische Motoren Werke Aktiengesellschaft Fahrzeugbauteil, Kraftfahrzeug, computerimplementiertes Verfahren, Computerprogramm und/oder computerlesbares Medium

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE864178C (de) * 1949-09-03 1953-01-22 Ferdinand Dr-Ing Marguerre Einrichtung zur Verminderung mechanischer Schwingungen
DE1071364B (fr) * 1959-12-17
DE2163798A1 (de) * 1971-12-22 1973-07-05 Messerschmitt Boelkow Blohm Resonanzabsorber fuer periodische und aperiodische schwingungen
US4373608A (en) * 1979-12-20 1983-02-15 General Electric Company Tuned sound barriers
US5240221A (en) * 1988-06-03 1993-08-31 Delta Tech Research, Inc. Viscoelastic damping system
DE4343008C1 (de) * 1993-12-16 1995-01-12 Deutsche Aerospace Resonanzabsorber
DE19707123C1 (de) * 1997-02-22 1998-04-16 Eurocopter Deutschland Zellenstruktur
US20020046901A1 (en) * 2000-08-25 2002-04-25 Zapfe Jeffrey A. Noise cancellation using a mechanical oscillator
DE10125190A1 (de) * 2001-05-23 2002-11-28 Poroton Gmbh Fuer Werbung Und Verfahren und Anordnung zur Schalldämmung von Gebäudesegmenten
WO2006103291A1 (fr) * 2005-03-31 2006-10-05 Universita' Degli Studi Di Roma 'la Sapienza' Dispositif d'amortissement des vibrations

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1071364B (fr) * 1959-12-17
DE864178C (de) * 1949-09-03 1953-01-22 Ferdinand Dr-Ing Marguerre Einrichtung zur Verminderung mechanischer Schwingungen
DE2163798A1 (de) * 1971-12-22 1973-07-05 Messerschmitt Boelkow Blohm Resonanzabsorber fuer periodische und aperiodische schwingungen
US4373608A (en) * 1979-12-20 1983-02-15 General Electric Company Tuned sound barriers
US5240221A (en) * 1988-06-03 1993-08-31 Delta Tech Research, Inc. Viscoelastic damping system
DE4343008C1 (de) * 1993-12-16 1995-01-12 Deutsche Aerospace Resonanzabsorber
DE19707123C1 (de) * 1997-02-22 1998-04-16 Eurocopter Deutschland Zellenstruktur
US20020046901A1 (en) * 2000-08-25 2002-04-25 Zapfe Jeffrey A. Noise cancellation using a mechanical oscillator
DE10125190A1 (de) * 2001-05-23 2002-11-28 Poroton Gmbh Fuer Werbung Und Verfahren und Anordnung zur Schalldämmung von Gebäudesegmenten
WO2006103291A1 (fr) * 2005-03-31 2006-10-05 Universita' Degli Studi Di Roma 'la Sapienza' Dispositif d'amortissement des vibrations

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022117383A1 (de) 2022-07-12 2024-01-18 Bayerische Motoren Werke Aktiengesellschaft Fahrzeugbauteil, Kraftfahrzeug, computerimplementiertes Verfahren, Computerprogramm und/oder computerlesbares Medium

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