• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention relates to a non-linear dynamic absorber (9) comprising: - a blade (1) with two end parts (2a) and an intermediate part (2b) with a non-linear spring function, a fixed mass (3) at the intermediate part (2b) with non-linear spring function of the blade, - a fixing means (4) for fixing the two end portions (2a) of the blade (1) on a solid support in a manner the intermediate portion (2b) with a non-linear spring function can oscillate about its equilibrium position or its equilibrium positions. It also relates to a construction element containing such an absorber and the use of such an absorber or construction element to reduce the acoustic transparency of a wall.
    公开号:FR3027082A1
    申请号:FR1459688
    申请日:2014-10-09
    公开日:2016-04-15
    发明作者:Pierre-Olivier Mattei；Sergio Bellizzi；Marc Pachebat；Remi Poncot；Sylvain Berger
    申请人:Saint Gobain Isover SA France；Centre National de la Recherche Scientifique CNRS；Saint Gobain Placo SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a non-linear dynamic absorber and its use to improve the acoustic insulation between two spaces separated by a wall. The sound insulation between two parts, separated by a wall, is typically provided either by increasing the surface density of the wall, or by doubling said wall. In the case of double-walled partitions, an acoustic insulating material, typically a mineral wool mattress or an elastic foam, may be inserted into the air gap between the two plates. From an acoustic point of view, such a double-walled partition, whether or not it is lined with an insulating material, behaves at low frequency like a mass-spring-mass system where the air gap or the lining of insulating material plays the role of the spring coupling the two plates together. FIG. 1 shows the evolution of the weakening index (NF EN ISO 140-3) of such a double-walled partition, with and without insulating lining, as a function of the frequency of the sound.
    [0002] There is a first characteristic weakness (fo) at low frequencies (about 100-150 Hz), called "breathing" frequency, corresponding to a phase-opposition of the system, and a second characteristic weakness (fa) at high frequencies ( between 2000 and 3000 Hz), called the coincidence frequency, where the wavelength of the acoustic incident wave "coincides" with the wavelength of the bending waves in the plates. The present invention aims to reduce the acoustic transparency of walls, in particular double-walled partitions, in the low frequency range, that is to say at frequencies between about 50 and 150 Hz, without adding a additional acoustic insulation layer or increase the overall thickness of the partition. This objective is achieved by means of a device, of a modest size, fixed on the wall at an appropriate place thereof, and which is capable of attenuating or even suppressing the resonance of the wall at its end. breathing frequency by adapting to the intrinsic variations thereof. The physical phenomenon underlying this attenuation of plate resonance is known as energy pumping or non-linear targeted energy transfer (see, for example, O. Gendelman et al., Energy Pumping). in non-linear mechanical oscillators, Part I and II, J. Appl., Mech, 68 (2001) 34-48).
    [0003] Energy pumping is the irreversible transfer of vibratory energy from a main structure, usually a linear oscillator, to an auxiliary structure formed by a substantially non-linear oscillator. The auxiliary structure, composed of a mass coupled to the main structure via a non-linear spring and, possibly, a damper, has no resonance frequency of its own and can oscillate at any frequency. From a vibratory energy threshold of the main structure, the vibratory energy of the latter is transferred to the auxiliary structure, thereby attenuating the amplitude of the vibrations of the main structure. The auxiliary structure, referred to as the non-linear energy sink (abbreviated to NES), is preferably significantly smaller in size than the main structure. Energy pumping is already widely used in various applications such as the seismic protection of buildings and engineering structures, the improvement of the dynamic performance of vehicles 25 or the stabilization of ships. To the knowledge of the Applicant, it has not been envisaged so far to use energy pumping to reduce the acoustic transparency of walls separating two spaces of a building or the interior of a building from the outside .
    [0004] It is the merit of the Applicant to have developed such a nonlinear dynamic absorber that is simple, robust and lightweight which can be easily attached to a plate intended to act as a wall or a wall. partition, such as an element of a suspended ceiling, a floor slab, a wall of a single or double wall, a doubling element, etc. The non-linear dynamic absorber of the present invention comprises, as an essential element, a blade whose two ends are embedded in a support (non-free ends) and on which a small mass is fixed. In the case of dynamic loading, this blade behaves like a non-linear spring oscillating around its equilibrium position - or its equilibrium positions - in a frequency range encompassing the bias frequency, thus allowing the irreversible transfer of The vibratory energy of the main resonator, namely the plate on which the non-linear absorber is fixed, to the nonlinear dynamic absorber. The subject of the present invention is therefore a non-linear dynamic absorber comprising: a blade with two end parts and an intermediate non-linear spring function part; a mass fixed to the non-linear spring function intermediate part; linear blade, - a fixing means for fixing the two end portions of the blade on a solid support so that the intermediate portion 20 with non-linear spring function can oscillate around its position of balance or its equilibrium positions. The nonlinear dynamic absorber of the present invention therefore comprises three essential means: a means for fixing the blade to the main structure whose vibration is to be attenuated, a blade with two non-free ends, embedded in the fastening means and - a small mass fixed on the "free" intermediate portion of the blade located between the two recessed end portions.
    [0005] When this absorber is subjected to a vibratory stress of sufficient energy and a suitable frequency, the small mass will oscillate in a plane perpendicular to the main plane of the blade, at a frequency different from the excitation frequency, the part The intermediate blade then comprises as a non-linear spring coupling the mass to the fastening means and to the main structure on which the absorber is attached. The blade may be any rigid elastic material with a high Young's modulus, typically greater than 50 GPa, preferably greater than 60 and in particular greater than 70 GPa. It is preferably a metal blade. The mass is preferably fixed in the central part - more precisely one-third in the center - of the intermediate part with a non-linear spring function of the blade, but this position is not the only one that can be envisaged and the mass could all be has an off-center position. The mass may be of a material identical to or different from that of the blade. As for the blade, it is preferably a metallic material. For example, the mass and the blade could be formed in one piece, the mass then corresponding to a bulge of the intermediate portion of the blade. The blade is preferably stressed, particularly a compressive or torsional stress. This constraint results in a decrease in the stiffness of the spring formed by the thin blade. The tests carried out by the Applicant have shown that this constraint also has the advantageous consequence of lowering the triggering threshold of the energy pumping phenomenon and increasing the efficiency of the dynamic absorber. The blade is preferably not subjected to a tensile stress capable of reducing or even eliminating the effectiveness of the nonlinear dynamic absorber (probably by increasing the spring stiffness and the triggering threshold). The compressive or torsional stress is preferably sufficiently large to impose on the blade an elastic buckling, ie a reversible buckling which disappears with the relaxation of the stress. In a preferred embodiment of the nonlinear dynamic absorber of the present invention, the blade is subjected to compressive stress imposing an elastic buckling. A flamed blade, that is to say, subjected to compression stress in the plane of the blade, has two points of stable equilibrium, as opposed to a non-compressive stress blade which presents a single point of stable equilibrium.
    [0006] The elastic buckling of the blade should not be too great. Indeed, when the value of the buckling exceeds a certain value, the transition between the two stable equilibrium positions becomes too difficult and the nonlinear spring will oscillate while around a single stable equilibrium position.
    [0007] The elastic buckling is advantageously less than 10%, preferably less than 6%, in particular less than 4%, this percentage being expressed relative to the length of the nonlinear spring function intermediate part. The buckling of the blade can also be expressed by indicating the ratio of the deformation to the thickness of the blade. In the nonlinear dynamic absorber of the present invention this ratio is preferably less than 100, especially less than 50 and most preferably less than 30. In a preferred embodiment of the nonlinear dynamic absorber of the present invention the fixing means consists of a single piece having two means for embedding the end portions of the blade. This embodiment is particularly advantageous when using a flamed blade, because it allows to adjust the compressive stress of the blade without the attachment means is attached to the main structure.
    [0008] In principle, the fastening means could, however, consist of two separate parts, each of these parts having a means of embedding one end of the blade. This embodiment would require the adjustment of the blade stress after the non-linear dynamic absorber is attached to the main structure whose vibrations it must attenuate. The fastening means must be of a sufficiently rigid material to transmit the vibrations of the main structure to the non-linear spring 3027082 - 6 - that forms the blade. It is preferably a relatively high modulus of elastic polymer material, typically greater than 1.5 GPa. The means for fixing the non-linear absorber used in the tests carried out by the Applicant was ABS (acrylonitrile-butadiene-styrene). ABS is a two-phase complex material with a thermoplastic matrix (acrylonitrile-styrene) in which elastomer (butadiene) nodules are dispersed. These nodules could play an important role in the dissipation of the vibratory energy of the nonlinear dynamic absorber. Another two-phase material of this type which may be particularly suitable for forming the fixing means is high impact polystyrene, a poly (styrene-b-butadiene) block copolymer with elastomeric polybutadiene nodules dispersed in a polystyrene matrix. In an advantageous embodiment of the invention, the fixing means is thus formed of a two-phase polymeric material comprising a rigid thermoplastic matrix (high Young's modulus) and an elastomeric phase (low Young's modulus). dispersed in the thermoplastic matrix. The dynamic absorber of the present invention preferably has a plane of symmetry perpendicular to the longitudinal axis of the blade. In a particularly preferred embodiment of the dynamic absorber, the fixing means comprises two branches extending symmetrically from a common base. The two means 25 of embedding the end portions of the blade are then located respectively on the two branches, preferably at the end or near the end of each of the branches, in two symmetrical positions relative to each other. to the other. The nonlinear dynamic absorber may have, for example, an overall shape in U, Y, or V, allowing attachment to the support at the base of the U, Y, or V. In a advantageous embodiment, the two embedding means are two jaws. The weight fixed on the intermediate portion advantageously has a weight of between 1 and 200 g, preferably between 2 and 100 g, in particular between 3 and 50 g and ideally between 5 and 30 g. The length of the intermediate portion of the blade is advantageously between 1 and 50 cm, preferably between 3 and 30 cm and in particular between 5 and 20 cm. The thickness of the intermediate portion of the blade is advantageously between 0.05 mm and 5 mm, preferably between 0.1 and 3 mm, in particular between 0.5 and 2 mm. Finally, the width of the intermediate portion of the blade is advantageously between 1 mm and 50 mm, preferably between 2 mm and 30 mm, in particular between 5 and 20 mm.
    [0009] The non-linear dynamic absorber constructed and tested by the Applicant and described in more detail below, comprises a blade whose intermediate portion is 12 cm long, 0.1 mm thick and 0.5 cm wide, in the center of which is fixed a mass of 3 g. As explained in the introduction, the nonlinear dynamic absorber 20 of the present invention is used to improve the acoustic insulation between two spaces separated by a wall comprising at least one plate. This wall can separate the interior of a building from the outside, or it can separate two rooms of a building, or a means of rail, naval, automobile or aeronautical.
    [0010] This wall may be a plate-shaped building element, or it may comprise a plurality of building elements each comprising at least one plate. The non-linear dynamic absorber is in all cases fixed, via the fastening means, directly to the plate (s) of the construction element.
    [0011] The present application therefore also relates to a construction element comprising - at least one plate made of a rigid material, and at least one non-linear dynamic absorber as described above, fixed in a rigid manner. on the plate by means of the attachment means of the dynamic absorber. The Young's modulus of the plate forming material is typically greater than 0.1 GPa, preferably greater than 1 GPa, in particular greater than or equal to 3 GPa. The plate may be of a material selected for example from glass, concrete, metals, plaster, plastics, wood or composite materials.
    [0012] In a preferred embodiment, the construction element will comprise at least one gypsum board. In another preferred embodiment, the construction element is part of a double-walled partition, that is to say it comprises two plates parallel to one another and separated by an intermediate space, also 15 called air gap. It is indeed these double partitions comprising two plates coupled by an air gap, which pose problems of a fairly high acoustic transparency in the low frequency range corresponding to the "breathing" frequency of the system. This problem of acoustic transparency is particularly pronounced when the two plates are plasterboard, generally fixed to a frame of rails and / or uprights, preferably metal. The intermediate space defined between the two plates is preferably at least partially filled with an acoustic insulation material.
    [0013] In general, the nonlinear dynamic absorber is preferably fixed to the plate so that the plane of the absorber plate is substantially parallel to the plane of the plate. The building element may comprise one or more nonlinear dynamic absorbers. For obvious aesthetic reasons, when the building element is part of a double-walled partition, the non-linear dynamic absorber is preferably attached to at least one of the inward faces of the double wall. 3027082 - 9 - In the case of an acoustic insulation project for an existing wall, the acoustic absorber can however be fixed on a visible face, easily accessible from the wall. To optimize the efficiency of the non-linear dynamic absorber, it must be installed at a location on the plate where the amplitude of the vibrations of the plate is maximum. Indeed, the energy pumping is only initiated from a certain level of vibratory energy and the main difficulty of the use of a non-linear dynamic absorber for acoustic insulation is to lower as much as possible this trigger threshold. It is therefore advisable to install the nonlinear dynamic absorber at the point of the plate where it vibrates the most strongly. This place will most often be in half of the surface of the plate farthest from the fixed edges. When the intermediate space of the double wall is filled with an insulating material, the nonlinear dynamic absorber can be housed in a recess dug on the inner face of the plate or in a recess dug in the insulating material so as to it does not come into contact with it. In another variant, the filling of the intermediate space by the insulating material could be only partial and the nonlinear dynamic absorber could be installed in the unfilled part. Finally, the subject of the present invention is the use of a non-linear dynamic absorber as described below or of a construction element containing such a nonlinear dynamic absorber to reduce the acoustic transparency of a wall.
    [0014] This use includes, for example, a method for reducing the acoustic transparency of a wall separating two rooms of a building or the interior of a building from the outside, which comprises fixing on said wall, preferably on a wall. plate of said wall, a non-linear dynamic absorber according to the present invention.
    [0015] Of course, all of the embodiments mentioned above with respect to the non-linear dynamic absorber or the building element comprising it also apply to the use of these objects for the reduction of the acoustic transparency of a wall. The present invention is now described in more detail with reference to the accompanying figures, in which FIG. 1 is a graph showing the evolution of the index of weakening of a double partition as a function of the frequency of the sound it this is to prevent passing through the wall; FIG. 2 is a perspective view of a nonlinear dynamic absorber according to the invention, FIG. 3 is a view from above of the dynamic absorber according to the invention of FIG. 2 showing the two positions of FIG. stable balance of the non-linear spring function blade; Figure 4 shows a cross section of a double wall comprising a non-linear dynamic absorber according to the invention.
    [0016] Figure 1 has already been discussed in the introduction. It shows the technical problem that the present invention proposes to solve, namely the increased acoustic transparency (fo) of a double wall at low frequencies (about 100 - 150 Hz), called "breathing" frequency, corresponding to a resonance in opposite phase of the two plates 20 of a double wall. The non-linear dynamic absorber 9 of the present invention, shown in Figure 2, comprises a fixing means 4 in the form of Y flattened. This fixing means is composed of a base 7 from which extend symmetrically two branches 6. At the end of each branch 6 is a mounting means 5 whose clamping is adjustable by means of a screw. The two embedding means 5 hold the two end portions (not visible) of a metal blade 1. The intermediate portion 2b of the blade can vibrate freely when activated by the vibration of the main resonator (not shown) on which the non-linear dynamic absorber 9 will be fixed. In the center of the blade 1 is fixed a small mass 3.
    [0017] 3 shows the same non-linear dynamic absorber whose blade 1 is subjected to a compressive stress which is exerted along the longitudinal axis of symmetry of the blade. This compression stress is generated by the fact that the intermediate portion 2b of the blade 5 between the two end portions 2a, embedded in the embedding means 5 is longer than the distance separating the two embedding means. This compression stress imposes a buckling on the blade 1. Each of the two representations shows a stable equilibrium position of the blade 1 flambé. During operation, that is to say when the non-linear dynamic absorber according to the invention is fixed rigidly on a plate subjected to a sufficient vibration, the blade can move from a stable equilibrium position to the other. Finally, FIG. 4 very schematically represents the nonlinear dynamic absorber 9 according to the invention, fixed in a recess of a plate 11 which forms part of an element of constructions according to the invention. This building element is here a double wall wall formed of two plates 11 between which is defined an intermediate space 8 filled with an insulating material 10. The nonlinear dynamic absorber is fixed on the plate so that the plane the blade (not visible) is substantially parallel to the general plane of the plate 11.
    权利要求:
    Claims (15)
    [0001]
    REVENDICATIONS1. Non-linear dynamic absorber (9) comprising - a blade (1) with two end parts (2a) and an intermediate part (2b) with a non-linear spring function, - a mass (3) fixed to the intermediate part (2b) a non-linear spring function of the blade, - a fixing means (4) for fixing the two end portions (2a) of the blade (1) on a solid support so that the intermediate part (2b) with non-linear spring function can oscillate around its equilibrium position or its equilibrium positions.
    [0002]
    2. Dynamic non-linear absorber according to claim 1, characterized in that the blade is stressed, preferably a compression or torsion stress.
    [0003]
    3. Dynamic non-linear absorber according to claim 2, characterized in that the blade is subjected to a stress imposing an elastic buckling, preferably a compression stress imposing an elastic buckling.
    [0004]
    4. non-linear dynamic absorber according to claim 3, characterized in that the elastic buckling is less than 10%, preferably less than 6%, in particular less than 4%, this percentage being expressed relative to the length of the intermediate part with non-linear spring function.
    [0005]
    5. Dynamic non-linear absorber according to one of the preceding claims, characterized in that the mass (3) is fixed in the central portion of the intermediate portion (2b) non-linear spring function of the blade.
    [0006]
    6. Dynamic non-linear absorber according to any one of the preceding claims, characterized in that the blade is a metal blade.
    [0007]
    7. non-linear dynamic absorber according to any one of the preceding claims, characterized in that the fastening means (4) consists of a single piece comprising two recessing means 3027082 - 13 - (5) parts end (2a) of the blade.
    [0008]
    8. Dynamic non-linear absorber according to any one of the preceding claims, characterized in that the fixing means (4) comprises two branches (6) extending symmetrically from a common base (7), the two embedding means (5) being respectively located on the two branches, preferably at the end or near the end of each of the branches.
    [0009]
    9. Construction element comprising - at least one plate (11) made of a rigid material, and
    [0010]
    At least one non-linear dynamic absorber (9) according to any one of the preceding claims, rigidly fixed to the plate (11) via the fixing means (4). 10. Construction element according to claim 9, characterized in that the nonlinear dynamic absorber is fixed on the plate so that the plane of the blade (1) of the absorber is substantially parallel to the plane of the plate.
    [0011]
    11. Building element according to one of claims 9 and 10, characterized in that the plate (11), or at least one of the plates, is a plasterboard.
    [0012]
    12. Construction element according to one of claims 9 to 11, characterized in that it comprises two plates (11) parallel to one another and separated by an intermediate space (8).
    [0013]
    13. Building element according to claim 12, characterized in that the two plates (11) are gypsum board, preferably fixed on a frame of rails and / or uprights.
    [0014]
    14. Building element according to claim 12 or 13, characterized in that the intermediate space (8) between the two plates (11) is filled with an acoustic insulation material (10). 30
    [0015]
    15. Use of a non-linear dynamic absorber according to any one of claims 1 to 8 or a construction element according to one of claims 9 to 14 for reducing the acoustic transparency of a wall.
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    同族专利:
    公开号 | 公开日
    EP3204566A1|2017-08-16|
    KR20170066398A|2017-06-14|
    US20170307041A1|2017-10-26|
    RU2693218C2|2019-07-01|
    EP3204566B1|2020-03-04|
    US10738464B2|2020-08-11|
    FR3027082B1|2017-04-28|
    WO2016055733A1|2016-04-14|
    JP2017530278A|2017-10-12|
    TW201617497A|2016-05-16|
    AR102210A1|2017-02-08|
    RU2017115480A|2018-11-13|
    CN106795713B|2020-02-07|
    CN106795713A|2017-05-31|
    RU2017115480A3|2019-04-29|
    BR112017005728A2|2018-01-30|
    CA2962613A1|2016-04-14|
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    法律状态:
    2015-10-22| PLFP| Fee payment|Year of fee payment: 2 |
    2016-04-15| PLSC| Search report ready|Effective date: 20160415 |
    2016-10-21| PLFP| Fee payment|Year of fee payment: 3 |
    2017-10-26| PLFP| Fee payment|Year of fee payment: 4 |
    2018-10-15| PLFP| Fee payment|Year of fee payment: 5 |
    2019-10-25| PLFP| Fee payment|Year of fee payment: 6 |
    2021-07-09| ST| Notification of lapse|Effective date: 20210605 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1459688A|FR3027082B1|2014-10-09|2014-10-09|NON-LINEAR DYNAMIC ABSORBER AND USE THEREOF FOR ACOUSTIC INSULATION|FR1459688A| FR3027082B1|2014-10-09|2014-10-09|NON-LINEAR DYNAMIC ABSORBER AND USE THEREOF FOR ACOUSTIC INSULATION|
    TW104132157A| TW201617497A|2014-10-09|2015-09-30|Nonlinear energy sink and use of same in sound insulation|
    US15/517,190| US10738464B2|2014-10-09|2015-10-07|Non-linear dynamic absorber and use thereof for acoustic insulation|
    RU2017115480A| RU2693218C2|2014-10-09|2015-10-07|Nonlinear dynamic vibration damper and its application for sound insulation|
    PCT/FR2015/052690| WO2016055733A1|2014-10-09|2015-10-07|Non-linear dynamic absorber and use thereof for acoustic insulation|
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