EP1135624A2 - Dispositif comprenant un composant aux vibrations amorties, notamment un frein - Google Patents

Dispositif comprenant un composant aux vibrations amorties, notamment un frein

Info

Publication number
EP1135624A2
EP1135624A2 EP99965409A EP99965409A EP1135624A2 EP 1135624 A2 EP1135624 A2 EP 1135624A2 EP 99965409 A EP99965409 A EP 99965409A EP 99965409 A EP99965409 A EP 99965409A EP 1135624 A2 EP1135624 A2 EP 1135624A2
Authority
EP
European Patent Office
Prior art keywords
brake
piezoelectric element
component
damping
piezoelectric
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP99965409A
Other languages
German (de)
English (en)
Inventor
Torsten Treyde
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF International UK Ltd
Original Assignee
Lucas Industries Ltd
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 Lucas Industries Ltd filed Critical Lucas Industries Ltd
Publication of EP1135624A2 publication Critical patent/EP1135624A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/005—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion using electro- or magnetostrictive actuation means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/0006—Noise or vibration control
    • F16D65/0012—Active vibration dampers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/08—Bands, shoes or pads; Pivots or supporting members therefor for internally-engaging brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2129/00—Type of operation source for auxiliary mechanisms
    • F16D2129/06—Electric or magnetic
    • F16D2129/12—Electrostrictive or magnetostrictive elements, e.g. piezoelectric

Definitions

  • the invention relates to a device with a component that can vibrate mechanically, wherein the mechanical vibration is undesirable and should therefore be damped.
  • Brakes are an example of such a device. Although the invention is explained below with a view to brakes, the invention can also be used in other devices. Mechanical vibrations occur in particular in devices in which moving parts rub against one another and put the system in undesirable vibration states.
  • US Patent 1572680 aims to reduce noise in a drum brake by providing the anchor plate in a certain area with recesses or openings which are filled with a certain material that is selected so that it inhibits vibrations of the anchor plate.
  • British patent specification 1381589 wants to prevent unwanted noise formation in a fixed-disc brake by shifting the center of gravity by means of a ground coupling.
  • the U.S. Patent 4445594 wants to avoid vibrations in that the outer brake pad of a floating caliper partial pad disc brake is attached and stored via rubber elements in the bridge fingers.
  • JP-A 59-200819 also teaches to provide the bridge fingers of a disc brake with vibration dampers.
  • the vibration dampers are made of rubber or a plastic and steel masses are also specifically attached. Different natural frequencies of the bridge, on the one hand, and the masses mentioned, on the other hand, attempt to counter vibration of the system or its components.
  • EP-A 0 592 290 wants to dampen vibrations in disc brakes in that a clamping wedge is braced on the one hand with a side wall of the housing of the disc brake and on the other hand with a flange of the axle to which the disc brake is attached.
  • an elastomeric layer can be provided between the clamping wedge and the side wall.
  • EP 0 470 064 A2 discloses a device with a piezoelectric sensor element that detects structure-borne noise. conditions detected and an actuator element that generates antiphase structure-borne vibrations. In this case, signals from the sensor elements are fed to the actuator element via an electronic regulating and control device, which also contains an amplifier stage for supplying external energy.
  • the invention has for its object to provide simple, inexpensive and reliable means with which the mechanical vibration of a component of a device can be effectively prevented.
  • the invention proposes a device or a brake with the features of claims 1, 2, 4, 16 or 17.
  • piezoelectric elements can deform when a voltage is applied and thus carry out a mechanical oscillation when a periodic voltage is applied. B. periodically deform.
  • this mechanical vibration of the piezoelectric element is now used in such a way that it counteracts the vibration of the component of the device to be damped.
  • This can be done according to the basic rules of physics e.g. B. happen that a suitable phase relationship is established between the mechanical vibration of the component to be damped and the deformation vibration of the piezoelectric element.
  • the oscillation of the component and the oscillation of the piezoelectric element do not necessarily have to have the same frequency, rather a relationship between the frequencies according to integer multiples ("harmonics") is usually sufficient to achieve a damping effect.
  • a piezoelectric element is used to generate by means of the mechanical vibration of the component to be damped the electrical voltage with which another piezoelectric element (or even the same piezoelectric element, see below) is applied to the mechanical vibration of the piezoelectric see element ("electrostriction") and thus dampen the unwanted vibration of the component.
  • electroelectric the mechanical vibration of the piezoelectric see element
  • Such a system is self-regulating in the sense that the vibration-damping periodic vibration of one piezoelectric element only occurs by generating voltage on the other piezoelectric element if the component of the device which is at risk of vibration actually vibrates (which need not always be the case) .
  • the periodic electrical excitation of the vibration-damping piezoelectric element is reduced (ie the applied voltage becomes lower) or completely interrupted when the mechanical vibration of the component to be damped becomes lower or ceases.
  • the system does not even need external energy (electrical voltage) to be effective, although the use of external additional electrical energy sources can be provided for reinforcement in more complex systems.
  • the piezoelectric element vibrates in two states (modes): on the one hand, it is periodically deformed by the mechanical vibration of the component that is to be damped and thus periodically generates a voltage due to the piezoelectric effect, and on the other hand, this becomes Voltage itself, possibly after a suitable phase shift and / or modulation, is again applied to the same piezoelectric element for electrical excitation in order to put it into an electrostrictive periodic mechanical oscillation state, which causes the mechanical oscillation of the component of the device is steamed.
  • modes two states
  • the damping is self-regulating: If no component of the device vibrates, no piezoelectric voltage is generated and, conversely, no electrostriction oscillation is generated for damping (which also prevents an undesired vibration caused by the piezoelectric crystal itself).
  • This self-regulation of the system is proportional, ie the quantity of the damping oscillation of the crystal depends on the quantity of the undesired mechanical oscillation of the component of the device to be damped.
  • a phase relationship between the periodic electrical voltage generated and the voltage applied for damping is set by means of an inductor.
  • Another preferred embodiment of the invention provides that at least one piezoelectric element is connected as a capacitive element in at least one electrical resonant circuit, and that this resonant circuit has a resonance frequency that is matched to the mechanical vibration frequency to be damped.
  • At least two piezoelectric elements are preferably connected either in parallel or in series in a resonant circuit with an inductor such that the resonance frequency of this resonant circuit is essentially matched to the mechanical vibration frequency of the component to be damped.
  • the one piezoelectric element in the sense explained above can generate a voltage due to the piezoelectric effect, which is applied to the other piezoelectric element in order to generate a mechanical oscillation of this piezoelectric element due to the electrostriction (i.e. the reverse piezoelectric effect) and thus a damping of the oscillation of the To effect component of the device.
  • the piezo elements are therefore effective alternately (crosswise) and have the same functions.
  • the invention relates not only to devices of the type in question here, but also to methods for damping components in devices, the method realizing the teachings explained above.
  • the invention is particularly preferably used for brakes, in particular for disc brakes, such as floating caliper or frame brakes, or also for drum brakes.
  • the brake is a floating caliper or floating frame brake and that the component that can generate noise is a lining carrier and / or part of the caliper, such as a bridge finger.
  • At least one piezoelectric element acts between the lining carrier and part of the caliper or frame of the brake.
  • At least two piezoelectric elements are preferably arranged in such a way that they are at a distance from one another in the circumferential direction of the brake (that is, the direction of rotation of the brake disc; i.e. tangentially).
  • a piezoelectric element can therefore preferably be arranged on the inlet side and another piezoelectric element on the outlet side of the brake. Measurements have shown that a particularly effective damping of the mechanical vibrations of the system can be achieved with such an arrangement in a disc brake.
  • the piezoelectric element or the piezoelectric elements are connected in an electrical circuit in order to transmit voltages and to effect the explained feedback effect.
  • an inductance can be provided in the circuit, ie a component with an induction effect.
  • the inductance can directly in a component of the brake, for. B. the component to be damped, integrated or mounted on such a component of the brake, z. B. in the immediate vicinity of the piezoelectric element, so that it can be assembled together with this.
  • piezoelectric elements are used in an oscillating circuit, this is preferably tuned in such a way that the damping effect of at least one of the piezoelectric elements is at a maximum in the range of a mechanical oscillation frequency of the component of the device that is to be damped mainly.
  • the at least one piezoelectric element is preferably arranged in the force flow of an application force of the brake, because the vibrations generated by friction arise in this force flow path and can therefore also be effectively damped there.
  • the invention can be implemented not only in general in devices and in particular brakes of the type described, but also in individual parts of such devices or brakes, such as the following:
  • a brake lining for a disc brake can have a piezoelectric element for damping vibrations.
  • the piezoelectric element or the elements can be attached to the support plate of the brake pad or integrated into it. It is even possible to design the entire support plate of the brake pad as a piezoelectric element or to design part of the support plate as a piezoelectric element.
  • At least one piezoelectric element is arranged near an antinode of the mechanically vibrating component.
  • An antinode in this sense is a point at which the mechanically vibrating component vibrates with maximum amplitude.
  • An anti-periodically oscillating piezoelectric element effective at this point has a particularly high damping effect.
  • Figure 1 is a disc brake with a measuring arrangement to explain the basics of the invention
  • Figure 2 with a measuring arrangement according to Figure 1 measured accelerations of the inlet and outlet side bridge fingers of a floating caliper partial pad disc brake;
  • FIG. 3 shows forces measured with an arrangement according to FIG. 1 on the inlet-side and outlet-side bridge fingers of the disc brake
  • FIG. 5 shows the time course of the electrical voltage of one of the two piezoelectric elements in a measurement corresponding to FIG. 4;
  • 6A and 6B show two basic circuit diagrams for circuits with two piezoelectric elements and one inductor
  • FIG. 7 measurements of the coupling behavior of two piezoelectric elements as a function of the oscillation frequency
  • FIG. 8 shows a floating caliper partial lining disc brake with piezoelectric elements for damping
  • FIG. 9 shows an axial top view of a brake lining of a brake according to FIG. 8 with piezoelectric elements
  • FIG. 10 shows a section through the brake lining according to FIG. 9;
  • Figure 11 shows another embodiment of a brake pad with piezoelectric elements in plan view
  • FIG. 12 shows a section through the brake lining according to FIG. 11.
  • FIG. 1 shows, as an exemplary embodiment of a device in which the mechanical vibration of a component is damped, a floating caliper partial-pad disc brake 10 with a brake disk 12 and a caliper 14.
  • the brake disk 12 is clamped between two brake pads 14a, 16a during braking .
  • the brake pads 14a, 16a are on pad Carrier plates 16, 18 attached from metal.
  • An actuating piston (cf. FIGS. 8, 20a) is moved axially in a cylinder 20 when braking.
  • the saddle 14 overlaps or engages behind the indirectly actuated lining carrier 16 in a known manner with two bridge fingers 22, 24.
  • two force sensors 26, 28 are arranged between the bridge fingers 22, 24 and the lining carrier plate 16, each of which acts in the axial direction (in the usual designation, axially with respect to the axis of the disc brake or the direction of the application force) Strength measurement.
  • Acceleration sensors 30, 32 are arranged on the outside of the bridge fingers 22, 24.
  • the arrangement described above is used for measurement purposes.
  • An exemplary embodiment of a device designed according to the invention is obtained if, in the arrangement described above, the two force sensors 26, 28 are replaced by piezoelectric elements. This is explained below.
  • the measured values of the two acceleration sensors 30, 32 are input via a (charge) amplifier 34, 36 and a low-pass filter 42 into a computer 44 for evaluation.
  • measured values of the two force sensors 26, 28 are also entered into the computer 44 for evaluation via the low-pass filter 42.
  • FIG. 2 shows the results measured with the acceleration sensors 30, 32 during braking.
  • the time in milliseconds is plotted on the abscissa and the measured acceleration a is plotted on the ordinate.
  • Figure 2 shows with thick line A the acceleration on the exit-side bridge finger and with thinner curve E the acceleration on the entry-side bridge finger. If the brake disc 12 moves from right to left in FIG. re the bridge finger 22 on the inlet side and the bridge finger 24 on the outlet side.
  • the acceleration a in FIG. 2 shows a periodic oscillation at 2500 Hz, ie clearly in the range audible to the human ear.
  • the two bridge fingers show oscillations of the same frequency, which are out of phase by 180 °.
  • FIG. 3 shows the forces F acting on the bridge fingers and measured with the force sensors 26, 28 over the same time scale.
  • the curve A shown with a strong line again shows the measurement results on the outlet-side bridge finger and the finer curve E shows the measurement results for the inlet-side bridge finger.
  • Figures 2 and 3 thus show the mechanical vibration of components of the "brake” system, which must be damped.
  • the two force sensors 26, 28 are replaced by piezoelectric elements in the arrangement according to FIG. This is explained by way of example in FIGS. 8 to 10.
  • the piezoelectric elements 46, 52 shown there replace the force sensors 26, 28. Further details of the disc brake according to FIG. 8 are explained further below.
  • FIG. 6B shows the basic circuit diagram (switch 38 still having to be considered in the circuit).
  • FIG. 4 shows measurement results when using the piezoelectric elements explained above.
  • the accelerations on the bridge fingers 22, 24 are again measured with the acceleration sensors 30, 32.
  • the inductance L is 61 mH.
  • the piezoelectric elements 46, 52 have a damping effect, as shown in FIG.
  • a piezoelectric element is periodically compressed by the mechanical vibration between the lining carrier plate 16 and the bridge fingers 22, 24 and thus generates a periodic voltage of the same frequency piezoelectrically.
  • This periodic voltage is applied to the other piezoelectric element, so that it starts to vibrate mechanically due to the reverse piezoelectric effect, i. H. periodically expands and contracts.
  • the vibration of the system of the backing plate 16 and bridge fingers is damped.
  • FIG. 4 shows, the shrinkage drops practically completely in less than 0.1 seconds.
  • FIG. 5 shows the measured piezoelectric voltage U. As soon as the switch 38 is closed at the time “0”, the voltage U at the two piezoelectric elements 46, 52 also drops to negligibly small values in significantly less than 0.1 seconds, which indicates that the self-damping effect of the two cross-connected and effective piezoelectric elements is highly effective.
  • FIGS. 6A and 6B show basic circuit diagrams for possible circuits according to which two piezoelectric elements with the capacitances C 1 and C 2 and the inductance L (40) can be switched; the total capacitance and also the resonance frequency f 0 are given in the figure.
  • the capacitances and inductors are preferably chosen so that the resonant frequency of the resonant circuit corresponds to the mechanical vibration to be damped or is at least in an integral relationship to it.
  • FIG. 7 shows the advantage of such a tuning of the electrical resonance frequency of the resonant circuit with the piezoelectric elements to the frequency of the mechanical vibration of the system that is to be damped.
  • a coupling factor k is plotted on the ordinate and the frequency on the abscissa.
  • the coupling factor k is a measure of how strong the coupling of the two piezoelectric elements and thus their damping effect is.
  • the lower curve which runs essentially at the value 0.3, shows the case in which the two piezoelectric elements 46, 52 are connected directly to one another without the interposition of an inductor.
  • the upper curve with a maximum at approximately 600 Hz shows the case in which an inductance of 900 mH is switched on and an oscillating circuit is thus formed, the resonance frequency of which is approximately 600 Hz.
  • the coupling factor rises sharply in the case of resonance (to values of approximately 2).
  • FIG. 8 shows details of a floating caliper partial lining disc brake 10, which has already been explained above with regard to its conventional structure.
  • two piezoelectric elements 46, 52 are arranged between the indirectly actuated pad carrier plate 16 and the bridge fingers 22, 24, in such a way that the flow of force from the bridge fingers is transmitted to the pad carrier plate via the piezoelectric elements.
  • the piezoelectric elements are clamped between metal plates 48, 50, which in turn engage concavely on the outside in corresponding convex depressions in the bridge finger or the lining carrier plate.
  • FIG. 10 shows an example of two troughs 54, 56 in the lining carrier plate 16.
  • the engagement between the piezoelectric element and the component whose vibration is to be damped can also take place indirectly.
  • the two piezoelectric elements 46, 52 are arranged approximately at the effective center of the clamping force (corresponding to the axis A according to FIG. 8) such that one piezoelectric element on the inlet side and the other piezoelectric element on the other side, that is, the outlet side.
  • FIGS. 11 and 12 show modifications of the embodiment according to FIGS. 9 and 10.
  • the piezoelectric elements 46 ′ and 52 ′ are arranged in cylindrical recesses in the lining carrier plate 16 ′.
  • Inductors 58, 60 are also mounted directly on the base plate 16 ', with the help of bearing washers 62, 64, which in the illustrated embodiment made of plastic, for. B. Polyoxy ethylene exist.
  • the inductors 58, 60 are designed as spiral windings.
  • FIGS. 8 to 12 The arrangements of piezoelectric elements shown in FIGS. 8 to 12 can be switched in different ways.
  • Each of the piezoelectric elements can be switched as an individual assembly with an inductance to form an independent resonant circuit, the mechanical vibration of the brake acting on the piezoelectric element generating an electrical voltage which reacts on the piezoelectric element by means of the inductance in such a way that the reverse piezoelectric element Effect (ie the mechanical vibration of the piezoelectric element due to the applied voltage) causes a damping in the sense described above.
  • the two (or more) piezoelectric elements can also belong to a common resonant circuit, as described above.
  • the resonant circuits with the piezoelectric elements do not require any external energy. However, it is also possible to amplify the piezoelectric voltages using electronic aids.
  • inductances and capacitances used in the circuits are adjustable in order to adapt them to the respective system at hand.
  • the performance data, in particular capacities, of the piezoelectric elements to be used and the inductors are experimentally optimized with an arrangement according to FIG. 1 and then used accordingly for the given system.
  • the frequencies and optimization of the damping it may be necessary to provide additional capacitances and / or inductances and / or resistances in the resonant circuits.
  • Coupling losses between the piezoelectric elements can be compensated for by external energy.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Braking Arrangements (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne l'amortissement vibrations mécaniques de composants de dispositifs. L'invention concerne notamment l'amortissement de composants de freins (10). A cet effet, au moins un élément piézoélectrique est relié par engrenage au composant vibrant (16, 22, 24) et excité électriquement de telle façon qu'il amortit les vibrations du composant.
EP99965409A 1998-12-01 1999-11-26 Dispositif comprenant un composant aux vibrations amorties, notamment un frein Withdrawn EP1135624A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19855467 1998-12-01
DE19855467A DE19855467A1 (de) 1998-12-01 1998-12-01 Vorrichtung mit schwingungsgedämpftem Bauteil, insbesondere eine Bremse
PCT/EP1999/009214 WO2000032958A2 (fr) 1998-12-01 1999-11-26 Dispositif comprenant un composant aux vibrations amorties, notamment un frein

Publications (1)

Publication Number Publication Date
EP1135624A2 true EP1135624A2 (fr) 2001-09-26

Family

ID=7889663

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99965409A Withdrawn EP1135624A2 (fr) 1998-12-01 1999-11-26 Dispositif comprenant un composant aux vibrations amorties, notamment un frein

Country Status (9)

Country Link
US (1) US6742632B2 (fr)
EP (1) EP1135624A2 (fr)
JP (1) JP4059630B2 (fr)
CN (1) CN100416129C (fr)
AU (1) AU2093900A (fr)
BR (1) BR9915834A (fr)
DE (1) DE19855467A1 (fr)
WO (1) WO2000032958A2 (fr)
ZA (1) ZA200104392B (fr)

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CN1333863A (zh) 2002-01-30
US20010042661A1 (en) 2001-11-22
WO2000032958A3 (fr) 2000-10-12
WO2000032958A2 (fr) 2000-06-08
JP4059630B2 (ja) 2008-03-12
US6742632B2 (en) 2004-06-01
BR9915834A (pt) 2001-08-21
ZA200104392B (en) 2002-01-15
CN100416129C (zh) 2008-09-03
DE19855467A1 (de) 2000-06-08
AU2093900A (en) 2000-06-19
JP2002531783A (ja) 2002-09-24

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