• 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 invention relates to a system for passive damping of mechanical vibrations generated by a vibrating structure supported by a support, the system comprising a transducer interposed between the vibrating structure and the support for transforming the mechanical energy of the vibrations into electrical energy, characterized by the fact that: - the transducer comprises: ○ a flextensional structure having a first axis (and a second axis perpendicular to each other, ○ a stack of piezoelectric elements adapted to produce electrical energy when it is constrained, which stack is constrained in compression by the flextensional structure along the first axis so that a deformation of said structure modifies the compressive stress applied on said stack, - two peripheral fasteners are integral with the flextensional structure, each of the fastenings being arranged according to the second axis, ▪ a first fixa tion for the attachment of the flextensional structure to the vibrating structure, ▪ a second attachment for the attachment of the flextensional structure to the support, ▪ at least one of the attachments incorporates an elastic suspension, - a shunt is connected to the piezoelectric stack so dissipating all or part of the electrical energy produced by the stress applied to said piezoelectric stack.
    公开号:FR3082258A1
    申请号:FR1854917
    申请日:2018-06-06
    公开日:2019-12-13
    发明作者:Gilles Grosso；Frederic Mosca
    申请人:Pytheas Tech；
    IPC主号:
    专利说明:

    SYSTEM AND METHOD FOR PASSIVE AMORTIZATION OF
    MECHANICAL VIBRATIONS
    Description
    Technical field of the invention.
    The invention relates to a system and a method for passive damping of mechanical vibrations.
    It concerns the technical field of passive vibratory isolators, that is to say which do not function as actuators transforming electrical vibrations into mechanical vibrations acting in phase opposition with the vibrations to be attenuated.
    State of the art.
    Vibratory isolators are generally mounted between, on one side a structure producing vibrations and, on the other side, a part potentially susceptible to receive these vibrations. They absorb vibrations from the vibrating structure and thus prevent them from being transmitted to the receiving part. For example, a vibration isolator can be interposed between the support part of a rotating machine and the rotating machine itself so that the vibrations generated by the rotating machine are not transmitted to the supporting part.
    There are different types of vibration isolators based on different techniques. Insulators with a fluid chamber and orifice or elastomeric or metallic suspensions are known in particular. These purely mechanical insulators transform the mechanical energy of vibrations into thermal energy (heat). These technologies are mature and proven but can present a certain number of limitations in terms of performance and adaptability to operating conditions (temperature, operating regime of the vibrating structure, transmission of static force, ...).
    Electromagnetic, magnetostrictive or piezoelectric suspensions are also known which use electroactive materials to convert the mechanical energy of vibrations into electrical energy. These technologies are efficient and allow better adaptability to the context of use. However, they are not widespread and are sometimes perceived as less robust than the aforementioned purely mechanical insulators. In addition, these solutions, when they are used in passive assemblies (the suspension not having an actuator role), do not allow effective damping at low frequency due to the relative rigidity of the electro- assets used.
    FIG. 1 is a diagram illustrating the attenuation capable of being obtained with a piezoelectric stack. The abscissae correspond to the frequency in Hertz of the vibrations and the ordinates correspond to the transmissibility in Decibels (ratio of the transmitted force to the excitation force). Up to around 100 Hz, it is found that the transmissibility is zero, that is to say that the piezoelectric stack lets through all the vibrations, without producing any attenuation. A positive transmissibility peak of around 20 dB appears around 500 Hz, this rejection means that the piezoelectric stack amplifies the vibrational phenomenon rather than attenuating it. It is only from this peak frequency that transmissibility becomes negative. The piezoelectric stack attenuates vibrations by around 40 dB / decade over a range of
    -3 frequencies ranging from around 500 Hz to around 20 KHz, this frequency range (Z) corresponding to noise pollution which it is particularly advantageous to reduce.
    Faced with this state of affairs, an objective of the invention is to provide a vibratory isolator having increased performance compared to that of the vibratory isolators of the aforementioned prior art.
    Another objective of the invention is to propose a vibratory isolator making it possible to optimize the adaptability to the operating conditions.
    Yet another objective of the invention is to provide a robust vibratory isolator, the design of which is simple, robust and inexpensive.
    An additional objective of the invention is to propose a vibratory isolator allowing effective damping of vibrations, over a wide frequency band, in particular at low frequencies and with increased attenuation on the frequency band ranging from approximately 500 Hz to approximately 20 KHz.
    Disclosure of the invention.
    The solution proposed by the invention is a system for passive damping of mechanical vibrations generated by a vibrating structure supported by a support, the system comprising:
    - a transducer interposed between the vibrating structure and the support to transform the mechanical energy of the vibrations into electrical energy and comprising:
    a flextensional structure having a first axis and a second axis perpendicular to each other,
    -4o a stack of piezoelectric elements adapted to produce electrical energy when it is constrained, which stack is constrained in compression by the flextensional structure along the first axis so that a deformation of said structure modifies the compressive stress applied to said stack,
    - two peripheral fasteners are secured to the flextensional structure, each of the fastenings being arranged along the second axis, o a first fastening for securing the flextensional structure to the vibrating structure, o a second fastening for securing the flextensional structure to the support , o at least one of the bindings preferably incorporates an elastic suspension,
    - A shunt is connected to the piezoelectric stack so as to dissipate all or part of the electrical energy produced by the stress applied to said piezoelectric stack.
    This damping system, or vibratory isolator, comprises a flextensional type piezoelectric transducer advantageously combined with an elastic suspension placed in series with said transducer. The Applicant has found that this particularly robust vibratory isolator has increased performance compared to that of the aforementioned prior art vibratory isolators. It allows in particular an effective damping of vibrations over a frequency range from about 50 Hz to 20 KHz, with an attenuation from 40 dB / decade to 60 dB / decade on the frequency band from about 500 Hz to about 20 KHz. The shunt can also be easily controlled to modify the stiffness of the piezoelectric stack according to the operating conditions, and in fact, further improve the attenuation of vibrations.
    Other advantageous features of the invention are listed below. Each of these characteristics can be considered alone or in combination
    -5combination with the remarkable characteristics defined above, and be the subject, if necessary, of one or more divisional patent applications:
    Advantageously, the elastic suspension is integrated in the attachment which is furthest from the vibrating structure.
    - The elastic suspension can be an elastomeric suspension, or a metallic or pneumatic or hydraulic suspension.
    - The shunt may consist of an electrical resistance connected to the terminals of the piezoelectric stack so as to thermally dissipate all or part of the electrical energy produced by the stress applied to said piezoelectric stack.
    - According to an alternative embodiment, the shunt consists of an electrical resistance and an inductance connected to the terminals of the piezoelectric stack so as to form an RLC resonant electronic circuit tuned over a frequency band to be attenuated.
    Advantageously, an electronic management unit is connected to an accelerometer placed so as to pick up the vibrations of the support and / or to an accelerometer placed so as to pick up the vibrations of the vibrating structure, which electronic management unit controls the shunt to modify the electrical stiffness of said piezoelectric stack as a function of the signals emitted by the accelerometer.
    Advantageously, part of the electrical energy produced by the stress applied to the piezoelectric stack, and which is not dissipated by the shunt, supplies one or more electronic components.
    - Advantageously, the flextensional structure has: - two opposite lateral ends, arranged perpendicular to the first axis and symmetrically on either side of the second axis; - two opposite transverse flanges, arranged perpendicular to the second axis and symmetrically on either side of the first axis; - identical longitudinal arms which extend along the first axis and which connect the lateral end caps to the transverse soles.
    - The connections between on the one hand the longitudinal arms and on the other hand the lateral end caps and the transverse flanges, advantageously consist of articulations, which articulations are formed by zones of lesser thickness forming a hinge arranged at the ends of each arm .
    Advantageously, an elastomer pad is interposed between the transverse flanges so as to limit the movement of the flextensional structure along the second axis.
    Advantageously, the piezoelectric stack is prestressed, the prestressing force applied to said stack being produced: - by the cooperation of a rod installed along the first axis and on which the piezoelectric stack is mounted, with fasteners installed in the flextensional structure; - or directly by the flextensional structure.
    Another aspect of the invention relates to a method for damping mechanical vibrations of a wiper motor of a motor vehicle, which motor is supported by a support, said method consisting in using the damping system according to the invention. one of the preceding characteristics, by interposing the transducer between said wiper motor and said support.
    Yet another aspect of the invention relates to a method for damping mechanical vibrations over a frequency band of 50 Hz ± 10 HZ to 20 KHz ± 100 HZ, which vibrations are generated by a vibrating structure supported by a support, said method consisting to use the damping system according to one of the preceding characteristics, by interposing the transducer between said vibrating structure and said support.
    Yet another aspect of the invention relates to a method for damping mechanical vibrations, with attenuation from 40 dB / decade ± 10 dB / decade to 60 dB / decade ± 10 dB / decade, over a frequency band ranging from 500 Hz ± 100 HZ at 20 KHz ± 100 HZ, which vibrations are generated by a vibrating structure supported by a support, said method consisting in using
    -7the damping system according to one of the preceding characteristics, by interposing the transducer between said vibrating structure and said support.
    Description of the figures.
    Other advantages and characteristics of the invention will appear better on reading the description of a preferred embodiment which will follow, with reference to the appended drawings, produced by way of indicative and nonlimiting examples and in which:
    - Figure 1 above is a diagram illustrating the attenuation likely to be obtained with a piezoelectric stack,
    FIG. 2 is a perspective view of a transducer according to the invention showing a flextensional structure,
    FIG. 3 is a side view of the transducer of FIG. 2,
    FIG. 4a is a sectional view along A-A of the transducer of FIG. 3,
    - Figure 4b is a sectional view along AA of the transducer of Figure 3, according to an alternative embodiment, Figure 5 illustrates the transducer of Figures 2 to 4a-4b interposed between a vibrating structure and a support, the piezoelectric stack being connected to a shunt,
    - Figure 6 is a diagram illustrating the attenuation likely to be obtained with a damping system according to the invention.
    Preferred embodiments of the invention.
    The terms right / left, upper / lower, up / down, horizontal / vertical which may be used in the present description essentially refer to the position of the elements illustrated in the accompanying drawings. They are used only as indicative and non-limiting examples.
    -8 In Figure 5, the damping system object of the invention comprises a transducer 1 interposed between a vibrating structure 2 and a support 3 supporting said vibrating structure. This vibrating structure 2 is for example a rotating machine or a wiper motor of a motor vehicle. In the latter case, the support 3 may correspond to the linkage which supports the wiper or to a chassis element of the vehicle.
    The function of the transducer 1 is to transform the mechanical energy of the vibrations generated by the vibrating structure 2 into electrical energy, so that these vibrations are not or little transmitted to the support 3.
    Referring to Figures 2 to 5, the transducer 1 has a flextensional structure 10. By "flextensional structure" means a structure in combined bending and tension. This mechanical structure is deformable and forms a mechanical amplifier, transmitting and amplifying the vibrational forces of the vibrating structure 2 towards a piezoelectric stack 4.
    The structure 10 has a first axis A-A and a second axis B-B perpendicular to each other. In the attached figures, the axis A-A is horizontal and the axis B-B vertical. The structure 10 has a general octagonal shape, elongated along the first axis A-A. It can be inscribed in an envelope whose length is between 5 cm and 30 cm, the width between 2 cm and 10 cm and the height between 2 cm and 10 cm.
    The structure 10 preferably has:
    - two short sides or side ends 12a, 12b identical (or not) opposite, arranged perpendicular to the first axis A-A and symmetrically on either side of the second axis B-B; these tips have a generally parallelepiped or cylindrical shape,
    - two small transverse flanges 13a, 13b identical (or not) opposite, arranged perpendicular to the second axis B-B and symmetrically on either side of the first axis A-A; these soles have a generally parallelepiped or cylindrical shape;
    - identical longitudinal arms 14a, 14b, 15a, 15b which extend along the first axis A-A and which connect the end pieces 12a, 12b to the transverse flanges 13a, 13b; these arms can be square, rectangular, round, oval, etc.
    More particularly, the structure 10 has:
    - a pair of upper arms 14a which connect the upper sole 13a to an upper edge of the left lateral end piece 12b,
    - a pair of lower arms 14b which connect the upper sole 13a to a lower edge of the left lateral end piece 12b,
    - a pair of upper arms 15a which connect the upper sole 13a to an upper edge of the right lateral end piece 12a,
    - a pair of lower arms 15b which connect the upper sole 13a to a lower edge of the right lateral end piece 12a.
    In an alternative embodiment not shown, each pair of arms 14a, 14b, 15a, 15b is replaced by a single arm. The use of pairs of arms however makes it possible to better distribute the mechanical stresses in said arms. In another alternative embodiment, not shown, each pair of arms 14a, 14b, 15a, 15b is replaced by a combination of three or more arms.
    The end pieces 12a, 12b, the soles 13a, 13b and the arms 14a, 14b, 15a, 15b preferably form a rigid monobloc piece made of steel, stainless steel, aluminum, or composite and obtained by machining or injection. These elements may however be in the form of separate parts assembled together for example by welding, screwing or bolting.
    - 10The connections between on the one hand the arms 14a, 14b, 15a, 15b and on the other hand the end pieces 12a, 12b and the soles 13a, 13b, advantageously consist of joints. To simplify the design of the structure 10, these joints consist of thinner zones 140, 150 forming a hinge which are arranged at the ends of each arm 14a, 14b, 15a, 15b. This limits the number of mechanical parts, which offers significantly improved maintenance of the transducer.
    The mechanical structure 10 is thus elastically deformable. When it is subjected to a compressive stress (bending) along the axis B-B, the flanges 13a, 13b tend to approach. This bringing together of the soles 13a, 13b increases the distance separating the end pieces 12a, 12b. Conversely, when the compression stress along the axis B-B reverses (extension), the flanges 13a, 13b move away, and the distance between the end pieces 12a, 12b decreases. It is understood that these compression stresses are generated by the vibrations of the vibrating structure 2.
    To limit the movement of the structure 10 along the axis B-B, an elastomer pad 8 can be provided interposed between the two flanges 13a, 13b. This pad 8 avoids excessive movement of the structure 10 which may damage it.
    A stack 4 of piezoelectric elements is installed in the structure
    10. It is suitable for producing electrical energy when it is forced. The piezoelectric elements of the stack 4 are advantageously in the form of washers or piezoceramic or piezocomposite discs suitable for being electrically polarized under the action of mechanical stress. The number of washers can vary from 3 to 20 depending on the length of the structure 10. For example, 8 hard ceramic PZT (Titano-Zirconate of Lead) washers are used, the stack 4 having a stiffness of 16 MN / m
    -11 and a Young module of approximately 50 GPa. This stack 4 is capable of delivering a voltage of 73 Volts under a force of 100 Newtons.
    In FIGS. 2 to 5, the stack 4 is installed along the first axis A-A, between the end pieces 12a, 12b, so that a deformation of the structure 10 modifies the compressive stress applied to said stack. More particularly, and as explained in the previous paragraph, when the vibrating structure 2 vibrates, the structure 10 deforms along the axis BB, By pinching effect, a compressive stress is applied to the stack 4. The structure 10 thus plays the role of mechanical amplifier, transmitting and amplifying the vibrational forces from the vibrating structure 2 towards the stack 4.
    The stack 4 is advantageously prestressed to improve the mechanical tensile strength of the transducer 1. In FIG. 4a, the stack 4 is mounted on a rod 40 installed along the first axis A-A. Fasteners 40a, 40b, installed in the end pieces 12a, 12b, are engaged with the threaded ends of the rod 40. The cooperation of the fasteners 40a, 40b with the rod 40 allows to apply a preload on the stacking 4.
    In FIG. 4b, it is the structure 10 which directly produces the prestressing force applied to the stack 4. The structure 10 is elastically deformed to allow the establishment of the stack 4. In practice, a stress of compression along the axis BB is applied to the soles 13a, 13b so that the end pieces 12a, 12b move away so as to allow the insertion of the stack 4. By releasing the soles 13a, 13b, the end pieces 12a, 12b come together and compress the stack 4 which is thus prestressed. To facilitate the insertion of the stack 4, it is mounted on a guide rod 400 held in position along the axis A-A by fastening elements 400a, 400b installed in the end pieces 12a, 12b.
    - 12 The mounting of the transducer 1 is carried out very simply and very quickly in the following manner: the rod 40 is inserted into the stack 4; the stack 4 is installed in the structure 10, between the end pieces 12a, 12b; the fastening elements 40a, 40b are positioned in the end pieces 12a, 12b so that said elements come into engagement with the threaded ends of the rod 40; the fastening elements 40a, 40b are screwed with a dedicated tool (eg torque wrench) so as to pre-constrain the stack 4 according to a desired prestressing force. To facilitate the installation of the stack 4 inside the structure 10, the upper sole 13a and / or the lower sole 13b can be produced in two parts so as to provide a changeover day.
    Two peripheral attachments 5a, 5b are secured to the structure 10. The upper attachment 5a is secured to the upper sole 13a and the lower attachment 5b to the lower sole 13b. The fasteners 5a, 5b are thus arranged along the second axis B, B. The fastening of the fasteners 5a, 5b on the flanges 13a, 13b can for example be obtained by welding, screwing or bolting. The shape of the fasteners 5a, 5b is complementary to that of the soles 13a, 13b. In FIGS. 2 to 5, the fasteners 5a, 5b are in the form of flat parallelepipedic and rigid flanges, made of steel, stainless steel, aluminum, or composite, obtained for example by machining. Their dimensions in length and width correspond to those of the soles 13a, 13b. Their thickness can vary from 1 cm to 10 cm.
    In Figure 5, the upper attachment 5a is used to secure the structure 10 to the vibrating structure 2, by screwing or bolting. And the lower attachment 5b is used to secure the structure 10, also by screwing or bolting.
    According to an advantageous characteristic of the invention, at least one of the fasteners 5a and / or 5b includes an elastic suspension. By “integrating”, it is meant that the fixing 5b and the suspension 6 can be two separate pieces assembled together or on the contrary formed one and the same piece.
    - 13 In Figures 2 to 5, it is the lower attachment 5b which incorporates this suspension 6. This acts as an interface between the lower attachment 5b and the support 3. The lower attachment 5b may be constituted by this single suspension
    6. The suspension 6 can however be integrated only in the upper attachment 5a, between the vibrating structure 2 and said attachment. The two fasteners 5a and 5b could also each incorporate an elastic suspension. The best results in terms of damping are however obtained when the elastic suspension is integrated in the attachment 5b which is furthest from the vibrating structure 2.
    To simplify the design, improve the robustness and overcome complex and costly solutions, this suspension 6 is preferably in the form of an elastomer sole, for example made of natural or synthetic rubber, the shape of which is complementary to that of fixing 5b. In FIGS. 2 to 5, it is in the form of a parallelepiped sole, the dimensions of which in length and in width correspond to those of the lower attachment 5b. Its thickness can vary from 1 cm to 10 cm. For example, a natural rubber sole with a stiffness of 250 kN / m and a Young's modulus of around 1.5 MPa are used. In practice, the stiffness of the suspension 6 is chosen as a function of the frequency band of the vibrations to be attenuated. The elastomeric sole 6 is assembled on the sole 5b by gluing, screwing or bolting.
    The suspension 6 can also be in the form of one or more pads made of elastomers assembled between the lower attachment 5b and the support 3. The suspension 6 can also be in the form of a metal suspension, for example a helical spring or blades, or a pneumatic or hydraulic suspension.
    Referring to FIG. 5, a shunt 7 is connected to the piezoelectric stack 4. This shunt 7 makes it possible to dissipate all or part of the electrical energy produced by the stress applied to the stack 4 during the deformation of the structure 10. The stack 4 produces an electrical signal transmitted to the shunt 7. On reception of the signal, the shunt 7 provides resistance to the electrical signal. Following this resistance, the stack 4 resists deformation of the structure 10, so that its electrical stiffness is modified. The stack 4 then acts as a shock absorber.
    The shunt 7 may consist of an electrical resistance connected in parallel or in series across the terminals of the stack 4, dissipating thermally (that is to say in the form of heat) all or part of the electrical energy. Knowing that the piezoelectric stack 4 is equivalent to an electrical capacitor, an electronic circuit RC is obtained making it possible to produce a low-pass or high-pass filter tuned to the frequency band to be attenuated.
    The shunt 7 may also consist of an electrical resistance and an inductor (coil) connected to the terminals of the stack 4 so as to form an electronic resonant RLC circuit, parallel or series, tuned to the frequency band to be attenuated. This type of shunt 7 (resistive or resistive-inductive) is passive, stable, simple and compact.
    In an alternative embodiment, a shunt 7 with negative capacity is used. This shunt 7 comprises a resistor and a synthetic negative capacitor having a real and imaginary impedance. The electrical impedance of the negative capacitance modifies the stiffness of the piezoelectric stack 4 to increase the damping.
    In FIG. 5, an electronic management unit 70 is connected to an accelerometer 71 placed so as to pick up the vibrations of the support 3 and / or to an accelerometer placed so as to pick up the vibrations of the vibrating structure 2.
    The management unit 70 is then adapted to control the shunt 7 so as to modify the electrical stiffness of the stack 4 as a function of the signals emitted by the accelerometer 71. For example, the shunt 7 can integrate a variable resistance or a variable impedance, the value of which is modified by the management unit 70 as a function of the signals emitted by the accelerometer 71.
    Part of the electrical energy produced by the stress applied to the piezoelectric stack 4, and which is not dissipated by the shunt 7, can be used to power one or more electronic components. This electrical energy can, for example, be used to power the management unit 70 and / or the accelerometer 71.
    FIG. 6 is a diagram illustrating the attenuation capable of being obtained with a damping system according to the invention. The abscissae correspond to the frequency in Hertz of the vibrations and the ordinates correspond to the transmissibility in Decibels. Curve 1 in dotted lines repeats the attenuation curve of FIG. 1 (piezoelectric stack only). Curve 2 in solid lines is the attenuation curve obtained with the piezoelectric stack 4 combined with the elastic suspension. Up to around 50 Hz (± 10 HZ), the transmissibility remains almost zero. Compared to curve 1, the system according to the invention enables the inflection point of the attenuation curve to be moved back by approximately 50 dB ± 10 HZ. From this frequency zone, the transmissibility becomes negative, with an attenuation of 40 dB / decade (± 10 dB / decade) up to a frequency of 500 Hz (± 100 HZ). At around this frequency, a transmissibility peak of around 20 dB appears, with less vibration attenuation. Adjusting the shunt 7 (for example the value of the resistance, the inductance or the negative capacitance) nevertheless makes it possible to process and attenuate this rejection. From this peak, the attenuation is 40 dB / decade ± 10 dB / decade to 60 dB / decade ± 10 dB / decade over the frequency range z from 500 Hz ± 100 HZ to 20 KHz ± 100 HZ. In summary, the system according to the invention allows vibration damping over a wider frequency range (50 Hz - 20 KHz) than that obtained by a piezoelectric stack alone (100
    - 16Hz - 20 KHz). In addition, the attenuation of noise pollution is better (greater than 40 dB / decade).
    The arrangement of the various elements and / or means and / or steps of the invention, in the embodiments described above, should not be understood as requiring such an arrangement in all implementations. In any event, it will be understood that various modifications can be made to these elements and / or means and / or stages, without departing from the spirit and scope of the invention.
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    claims
    1. System for passive damping of mechanical vibrations generated by a vibrating structure (2) supported by a support (3), the system comprising a transducer (1) interposed between the vibrating structure and the support to transform the mechanical energy of the vibrations in electrical energy, characterized by the fact that:
    - the transducer (1) comprises:
    o a flextensional structure (10) having a first axis (AA) and a second axis (BB) perpendicular to each other, o a stack (4) of piezoelectric elements adapted to produce electrical energy when it is constrained, which stack is constrained in compression by the flextensional structure along the first axis (AA) so that a deformation of said structure modifies the compressive stress applied to said stack,
    - two peripheral fasteners (5a, 5b) are integral with the flextensional structure (10), each of the fastenings being arranged along the second axis (B, B), a first fastening (5a) for securing the flextensional structure (10) to the vibrating structure (2), a second attachment (5b) for securing the flextensional structure (10) to the support (3), at least one of the attachments (5b) incorporates an elastic suspension (6),
    - A shunt (7) is connected to the piezoelectric stack (4) so as to dissipate all or part of the electrical energy produced by the stress applied to said piezoelectric stack.
    [2" id="c-fr-0002]
    2. System according to claim 1, in which the elastic suspension is integrated in the fixing (5b) which is furthest from the vibrating structure (2).
    [3" id="c-fr-0003]
    3. System according to one of claims 1 or 2, wherein the elastic suspension (6) is an elastomeric suspension.
    [4" id="c-fr-0004]
    4. System according to one of claims 1 or 2, wherein the elastic suspension (6) is a metal or pneumatic or hydraulic suspension.
    [5" id="c-fr-0005]
    5. System according to one of claims 1 to 4, wherein the shunt (7) consists of an electrical resistor connected to the terminals of the piezoelectric stack (4) so as to thermally dissipate all or part of the electrical energy produced by the stress applied to said piezoelectric stack.
    [6" id="c-fr-0006]
    6. System according to one of claims 1 to 4, in which the shunt (7) consists of an electrical resistance and an inductance connected to the terminals of the piezoelectric stack (4) so as to form an RLC resonant electronic circuit tuned to a frequency band to be attenuated.
    [7" id="c-fr-0007]
    7. System according to one of claims 1 to 6, in which an electronic management unit (70) is connected to an accelerometer (71) placed so as to pick up the vibrations of the support and / or to an accelerometer placed so as to capturing the vibrations of the vibrating structure, which electronic management unit controls the shunt (7) to modify the electrical stiffness of said piezoelectric stack as a function of the signals emitted by the accelerometer (71).
    [8" id="c-fr-0008]
    8. System according to one of claims 1 to 7, in which part of the electrical energy produced by the stress applied to the stack
    - 19piezoelectric (4), and which is not dissipated by the shunt (7), supplies one or more electronic components (70, 71).
    [9" id="c-fr-0009]
    9. System according to one of claims 1 to 8, in which the flextensional structure (10) has:
    - two opposite lateral ends (12a, 12b), arranged perpendicular to the first axis (A-A) and symmetrically on either side of the second axis (B-B),
    - two opposite transverse flanges (13a, 13b), arranged perpendicular to the second axis (B-B) and symmetrically on either side of the first axis (A-A);
    - identical longitudinal arms (14a, 14b, 15a, 15b) which extend along the first axis (A-A) and which connect the lateral end caps (12a, 12b) to the transverse flanges (13a, 13b).
    [10" id="c-fr-0010]
    10. System according to claim 9, in which the connections between on the one hand the longitudinal arms (14a, 14b, 15a, 15b) and on the other hand the lateral end pieces (12a, 12b) and the transverse flanges (13a, 13b ), consist of joints, which joints are formed by zones of reduced thickness (140, 150) forming a hinge arranged at the ends of each arm.
    [11" id="c-fr-0011]
    11. System according to one of claims 9 or 10, in which an elastomer pad (8) is interposed between the transverse flanges (13a, 13b) so as to limit the movement of the flextensional structure (10) along the second axis. (BB).
    [12" id="c-fr-0012]
    12. System according to one of claims 9 to 11, in which the piezoelectric stack (4) is prestressed, the prestressing force applied to said stack being produced:
    - By the cooperation of a rod (40) installed along the first axis (AA) and on which is mounted the piezoelectric stack (4), with fasteners (40a, 40b) installed in the flextensional structure (10) , or
    - directly by the flextensional structure (10).
    [13" id="c-fr-0013]
    13. Method for damping mechanical vibrations of a wiper motor (2) of a motor vehicle, which motor is supported by a support (3), said method consisting in using the damping system according to claim 1 in interposing the transducer (1) between said wiper motor and said support.
    [14" id="c-fr-0014]
    14. Method for damping mechanical vibrations over a frequency band of 50 Hz ± 10 HZ to 20 KHz ± 100 HZ, which vibrations are generated by a vibrating structure (2) supported by a support (3), said method consisting in using the damping system according to claim 1 by interposing the transducer (1) between said vibrating structure and said support.
    [15" id="c-fr-0015]
    15. Method for damping mechanical vibrations, with an attenuation of 40 dB / decade ± 10 dB / decade to 60 dB / decade ± 10 dB / decade, over a frequency band ranging from 500 Hz ± 100 HZ to 20 KHz ± 100 HZ, which vibrations are generated by a vibrating structure (2) supported by a support (3), said method consisting in using the damping system according to claim 1 by interposing the transducer (1) between said vibrating structure and said support.
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    FR2966085A1|2012-04-20|Vehicle i.e. motor vehicle, has axle engaged with damping device to permanently exert radial traction force on intermediate turn of helical spring for damping lateral oscillations of helical spring
    FR2966774A1|2012-05-04|Motor vehicle, has vibration damping device whose central portion is arranged in support against part of intermediate coil of suspension spring in non-sliding manner to permanently exert radial thrust on intermediate coil
    EP3189248B1|2021-09-01|Vibration insulating device, associated shock absorber and use of said shock absorber
    BE1013240A6|2001-11-06|Device support for rail rail.
    EP1319862A2|2003-06-18|Damping mechanism
    FR2838173A1|2003-10-10|Non-structural damping element for structure subject to vibrations has at least one metal honeycomb layer
    FR3082073A1|2019-12-06|VIBRATORY ENERGY RECOVERY
    FR2761311A1|1998-10-02|Suspension device for vehicle seat
    WO2019229310A1|2019-12-05|Vibrating torsion trap device
    FR3062403A1|2018-08-03|RAIL ATTACHMENT FOR FIXING ON A RAILWAY TRAVERSE
    FR2858380A1|2005-02-04|Vibration amplitude filtering and attenuating method for e.g. automobile frame, involves transferring vibration energy generated by elastic blade and dissipated by damping device for assuring filtering and attenuation of pressure wave
    FR2897130A1|2007-08-10|DEVICE FOR REDUCING THE VIBRATION OF A STRUCTURE
    FR2587950A1|1987-04-03|MOTOR SUPPORT HAVING IMPROVED AND LOW-DIMENSIONAL DAMPING PROPERTIES
    同族专利:
    公开号 | 公开日
    EP3803152A1|2021-04-14|
    FR3082258B1|2021-11-05|
    WO2019234366A1|2019-12-12|
    US20210226116A1|2021-07-22|
    JP2021527782A|2021-10-14|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US5783898A|1996-02-26|1998-07-21|Mcdonnell Douglas Corporation|Piezoelectric shunts for simultaneous vibration reduction and damping of multiple vibration modes|
    US20050134149A1|2003-07-11|2005-06-23|Deng Ken K.|Piezoelectric vibration energy harvesting device|
    JP3790255B1|2005-03-07|2006-06-28|太平洋セメント株式会社|ENERGY CONVERSION DEVICE, MOBILE BODY HAVING THE SAME, AND ENERGY CONVERSION SYSTEM|
    US20070164189A1|2005-10-07|2007-07-19|Corsaro Robert D|Tri-axial Hybrid Vibration Isolator|
    US8912710B2|2011-02-20|2014-12-16|Omnitek Partners Llc|Energy harvesting from input impulse with motion doubling mechanism for generating power from mortar tube firing impulses and other inputs|
    WO2017048906A1|2015-09-15|2017-03-23|The Regents Of The University Of Michigan|Energy harvesting for leadless pacemakers|
    WO2017051133A1|2015-09-25|2017-03-30|Pytheas Technology|System using a piezoelectric generator to produce electrical power|
    CN111043215A|2019-12-09|2020-04-21|南京航空航天大学|Piezoelectric type intelligent dynamic vibration absorber|
    CN112532108B|2020-12-07|2022-02-22|上海大学|Vibration energy collecting device based on piezoelectric stack and electromagnetic induction|
    法律状态:
    2019-06-28| PLFP| Fee payment|Year of fee payment: 2 |
    2019-12-13| PLSC| Publication of the preliminary search report|Effective date: 20191213 |
    2019-12-13| EXTE| Extension to a french territory|Extension state: PF |
    2020-06-30| PLFP| Fee payment|Year of fee payment: 3 |
    2021-06-28| PLFP| Fee payment|Year of fee payment: 4 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1854917|2018-06-06|
    FR1854917A|FR3082258B1|2018-06-06|2018-06-06|SYSTEM AND METHOD FOR PASSIVE AMORTIZATION OF MECHANICAL VIBRATIONS|FR1854917A| FR3082258B1|2018-06-06|2018-06-06|SYSTEM AND METHOD FOR PASSIVE AMORTIZATION OF MECHANICAL VIBRATIONS|
    JP2020568288A| JP2021527782A|2018-06-06|2019-06-06|System and method of passive damping of mechanical vibration|
    US16/972,213| US20210226116A1|2018-06-06|2019-06-06|System and method for passive damping of mechanical vibrations|
    PCT/FR2019/051368| WO2019234366A1|2018-06-06|2019-06-06|System and method for passive damping of mechanical vibrations|
    EP19742849.3A| EP3803152A1|2018-06-06|2019-06-06|System and method for passive damping of mechanical vibrations|
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