EP2076689A1 - Vorrichtung zur reduktion von schwingungen einer struktur - Google Patents
Vorrichtung zur reduktion von schwingungen einer strukturInfo
- Publication number
- EP2076689A1 EP2076689A1 EP07818542A EP07818542A EP2076689A1 EP 2076689 A1 EP2076689 A1 EP 2076689A1 EP 07818542 A EP07818542 A EP 07818542A EP 07818542 A EP07818542 A EP 07818542A EP 2076689 A1 EP2076689 A1 EP 2076689A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- actuator
- resonant circuit
- signal
- electrical
- controller
- 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- Withdrawn
Links
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- 230000004044 response Effects 0.000 claims description 5
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- 230000004913 activation Effects 0.000 abstract description 5
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- 238000013016 damping Methods 0.000 description 11
- 230000009467 reduction Effects 0.000 description 11
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- 239000010410 layer Substances 0.000 description 7
- 238000006073 displacement reaction Methods 0.000 description 6
- 230000006978 adaptation Effects 0.000 description 5
- 230000010349 pulsation Effects 0.000 description 5
- 230000008901 benefit Effects 0.000 description 4
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
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- 230000008033 biological extinction Effects 0.000 description 1
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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
- 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
- F16F15/002—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion characterised by the control method or circuitry
-
- 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
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D19/00—Control of mechanical oscillations, e.g. of amplitude, of frequency, of phase
- G05D19/02—Control of mechanical oscillations, e.g. of amplitude, of frequency, of phase characterised by the use of electric means
Definitions
- the invention relates to a device for reducing vibrations of a structure having the features of the preamble of patent claim 1.
- passive vibration absorber To reduce vibrations of a structure, the use of so-called passive vibration absorber is known. These have a mechanical structure with a damping mass, which is coupled via a Tilgersteifmaschine, ie a spring, elastically to the structure whose vibrations are to be reduced. Due to the vibrations of the structure of the absorber mass is excited due to the coupling in turn to vibrate.
- the reaction forces exerted on the structure by the vibration absorber cause the structure to be kept at rest by the vibration absorber at its natural frequency.
- this ideal effect of a vibration absorber is given exclusively for the case in which the natural absorption frequency is equal to the frequency of the structure's vibrations to be reduced.
- the structure has several natural frequencies or at least one variable natural frequency, or is excited to vibrate with a variable-frequency external periodic force
- conventional, purely passive vibration dampers quickly reach their limits. If natural frequencies of the structure are to be reduced in order to reduce vibration, several vibration absorbers must be provided, with the resulting larger number of absorbers representing an undesirable increase in the total mass of the system. Frequency-variable excitation of the structure can also be counteracted with a plurality of vibration modes only if the frequency bandwidth remains small.
- the usable frequency range can be widened by the actual Tilgereigenfrequenz a passive vibration absorber by damping the movements of the absorber mass in the frequency space.
- damping With the introduction of damping, the ability of a passive vibration absorber to keep the structure at rest at its natural frequency is reduced. It is then only a reduction of the vibrations of the structure at the Tilgereigenfrequenz reachable.
- This function fulfills a vibration damper with integrated damping but over a wider frequency range. The greater the attenuation, the less the structure is ideally kept at rest at the self-sustaining frequency, but the wider the frequency range in which the vibration absorber provides a still usable reduction in vibrations of the structure.
- a device for reducing vibrations of a structure having the features of the preamble of patent claim 1 uses a passive electrical resonant circuit, which is connected via a piezoelectric element serving as both sensor and actuator, or a sensor and a separate actuator to the structure whose vibrations are to be reduced.
- a passive electrical resonant circuit which may be formed by a resistor and an inductance, a resistance and a capacitance, an inductance and a capacitance or a resistance, an inductance and a capacitance, a mechanical vibration damper is electrically modeled.
- EP 1 291 551 A1 also proposes active systems in which no resonant circuit is provided and which actively counteract the oscillations of the structure either with an open control loop, a closed control loop or a hybrid system which combines both control concepts ,
- the invention has for its object to provide a device for reducing vibrations of a structure having the features of the preamble of independent claim 1, in which the control for the control of the actuator is designed in the simplest possible way to the hitherto existing disadvantages of an active vibration reduction as far as possible to eliminate as compared to a passive vibration damper, without losing the fundamental frequency variability of the active vibration reduction.
- the controller has an analog to a mechanical absorber constructed electrical resonant circuit, which determines the course of a transfer function of the control between the signal of the vibration sensor and the control of the actuator. It is therefore not a question that the controller according to the invention has somewhere any electrical resonant circuit, which may already be the case with a control of a device from the prior art. Rather, it is important that the course of the transfer function of the controller between the signal of the vibration sensor and the control of the actuator, so the response of the controller in the form of driving the actuator to the signal of the vibration sensor is determined by magnitude and phase by the electrical resonant circuit.
- the present invention is based on the concept to replace the mechanical resonant circuit of a passive vibration absorber by an analogously constructed electrical resonant circuit and analog with the vibration sensor on the one hand and the actuator on the other hand, the relevant couplings of a mechanical vibration absorber with the structure whose vibrations are to be reduced. Except for adjustments between the electrical resonant circuit and the mechanical structure, which may require the supply of electrical power, the new device works as a mechanical vibration absorber passive insofar as the response to vibrations of the structure is determined by the passive electrical resonant circuit and than that at least Part of the power needed to reduce the vibration of the structure is available as reactive power. As a result, a high susceptibility to interference and energy-saving operation of the new device are guaranteed.
- the adaptation of the electrical resonant circuit to the energy of the vibrations of a structure to be reduced can be achieved by a larger dimensioning of the electrical resonant circuit, ie larger electrical components. In this case, it comes with little externally supplied electrical power for adaptation between the electrical resonant circuit and the mechanical structure. It is also in principle sufficient to provide the adaptation to the energy of the vibrations to be reduced in the region of the interface between the electrical resonant circuit and the mechanical structure.
- the resonant circuit is composed of operational amplifiers. At least two operational amplifiers are provided. Preferably, these are at least three operational amplifiers. Of the operational amplifiers, a first is used as a differential amplifier and each other as an integrator for the output of the preceding operational amplifier, and at least from the last integrator in the series, the output is fed back to the differential amplifier.
- the electrical resonant circuit of the new device basically has a fixed natural frequency. However, it is readily possible to intervene in this electrical resonant circuit, for example, by changing its electrical variables to change its natural frequency. Thus, this natural frequency can easily be tuned to a relevant frequency component of the vibrations of the structure or this tracked. Due to the slight variability of the electrical variables of the electrical resonant circuit, in addition to its natural frequency, as far as this is desired, for. B. also changes its attenuation and be optimized with respect to the current operating conditions of the device.
- the tuning of the natural frequency and possibly also the attenuation of the electrical resonant circuit by changing its electrical variables is preferably carried out as a function of a dominant frequency component of the signal of the vibration sensor or another sensor.
- Several other sensors can also be used in determining the currently ideal electrical variables of the electrical resonant circuit.
- the control In order to use the vibration sensor to simulate the coupling of a mechanical vibration absorber to the structure, the control generates from the signal of the vibration sensor a path-proportional voltage signal, which is fed back into the resonant circuit.
- a path-proportional voltage signal is provided directly by a displacement sensor. But it can also be generated from the signal of a speed sensor or an acceleration sensor by one or two times integration. In principle, it is also possible that directly a speed or acceleration proportional voltage signal is fed back into the resonant circuit of the new controller.
- the controller controls the actuator with a difference between a feedback voltage signal of the electrical resonant circuit and the off-proportional voltage signal received at the mechanical structure.
- Control is typically via a power amplifier.
- Voltage signal of the electrical resonant circuit corresponds to the oscillation path of
- Absorber mass which, depending on its position relative to the structure, acts on the structure via the absorber stiffness simulated in the electrical oscillating circuit.
- the electrical resonant circuit of the control of the new device can be realized analog or digitally simulated.
- the electrical resonant circuit may be constructed of integrated circuits, wherein then the adaptation to the power level of the mechanical structure may be more complex.
- a digitally simulated electrical resonant circuit facilitates the change in the electrical variables of the resonant circuit in order to change its natural frequency and / or attenuation as needed.
- the actuator with which the control acts on the mechanical structure is preferably one which is supported exclusively on the structure itself, ie. H. acts on at least two points of the structure and is effective between them. Changes in the position of the structure in relation to an external support of the actuator do not have to be considered.
- the actuator may have a layer structure of two surface electrodes and a piezoelectric layer arranged between the surface electrodes, which stretches in its main plane of extension when a voltage is applied between the surface electrodes.
- a planar element of the structure, with which this actuator is connected flat claimed bending.
- frequently occurring bending vibrations of a wall or of another planar element of a structure can be counteracted very effectively.
- the natural frequency of the electrical resonant circuit of the new device is easily changeable.
- the electrical resonant circuit can also be readily configured so that it has a plurality of natural frequencies and thus determines the response behavior, ie the transfer function of the controller to vibrations of the mechanical structure at several frequencies in an ideal manner.
- Fig. 1 shows a schematic diagram of an elastic structure attached thereto mechanical vibration absorber.
- Fig. 2 shows a schematic diagram of a first embodiment of the present invention
- FIG. 1 Invention in which the mechanical vibration absorber according to FIG. 1 is simulated by an electrical resonant circuit.
- Fig. 3 shows a comparison with FIG. 1 to a damping of the absorber mass of the mechanical vibration absorber supplemented schematic diagram.
- Fig. 5 shows the arrangement of an actuator on a structure in the application of the new device
- FIG. 6 shows details of the actuator according to FIG. 5.
- a mechanical structure 1 is shown, which is shown here, that it is coupled via a structural rigidity 2 to a stationary base 3 in order to reproduce their elasticity.
- a mechanical vibration damper 4 is coupled from a Tilgersteiftechnik 5 and a damping mass 6, wherein the Tilgersteiftechnik 5 binds the absorber mass 6 to the structure 1.
- ⁇ is the matching natural frequency expressed as angular frequency
- c ⁇ is the value of the absorber stiffness 5
- m ⁇ is the value of the absorber mass 6
- K is the value of the modal structural stiffness 2
- M is the value of the modal mass of the structure 1, reduces the vibration damper 4 vibrations of the structure 1 with the matching natural frequency to zero.
- x is the displacement of the structure 1
- x ⁇ is the displacement of the absorber mass 6
- x is the acceleration of the structure 1.
- the structure 1 "sees" the vibration absorber 4 exclusively in the form of a force component -c r (x -x ⁇ ) in this case.
- a vibration sensor 8 which emits a signal 10 to a control 9 is arranged on the structure 1.
- the controller 9 controls an actuator 11 acting on the structure 1 with a drive signal 12.
- the drive signal 12 is proportional to (x -x ⁇ ), where x is a path-proportional voltage signal, the control 9 from the signal 10 of the vibration sensor. 9 generated, and x ⁇ here a feedback voltage signal 13 of an electrical
- Resonant circuit 14 of the controller 9 is. In this way, with the controller 9 and the actuator 11, the influence of a vibration absorber on the structure 1 is simulated analogously.
- the feedback from the structure 1 to the vibration damper is simulated via the vibration sensor 9, in which the controller feeds back into the electric oscillating circuit 14 the out-of-band voltage signal 15 generated from its signal 10, which also enters the drive signal 12.
- the electrical resonant circuit 14 may be formed in different ways. Here it is constructed by three operational amplifiers, a differential amplifier 16 which amplifies the difference between the voltage signals 13 and 15, and two integrators 17 and 18.
- a transition signal 19 from the differential amplifier 16 to the integrator 17 corresponds to the acceleration of the absorber mass of a mechanical vibration absorber simulated by the resonant circuit 14, while a transition signal 20 between the two integrators 17 and 18 corresponds to a speed of this absorber mass.
- the fed back voltage signal 13 is as well as the voltage signal 15 away proportional.
- the voltage signal 15 reflects the displacement x of the structure 1, the voltage signal 13 corresponds to the displacement x ⁇ of the absorber mass 6.
- a conditioner 21 of the controller 9 serves to make the signal 10 of the vibration sensor 8 the path-proportional voltage signal 15 and from the Signal 10 and the voltage signal 15 and the voltage signal 13 to generate the drive signal 12.
- the vibration sensor 8 is a displacement sensor and no integration of the signal 10 for the generation of the voltage signal 15 is required, essentially to a level adjustment between the vibration sensor 8 and the electrical resonant circuit 14 on the one hand and the electrical resonant circuit 14 and the actuator 11 on the other hand.
- the controller 9 operates passively based on the electrical oscillating circuit 14. That is, a substantial portion of the electric power for driving the actuator 11 is provided by the electric oscillation circuit 14 in the form of reactive power. On this basis, the entire device 7 is very economical with respect to the electric power to be externally supplied thereto.
- a not yet mentioned advantage of the device 7 over the attachment of a mechanical vibration absorber 4 according to FIG. 1 to the structure 1 is that the entire control 9 can be arranged away from the structure. It has already been suggested that, especially with higher-energy vibrations of structure 1, the required Mass m ⁇ the absorber mass 6 is often very large with adequate design of a vibration absorber 4 of FIG. 1, because the available for the absorber mass 6 ways x ⁇ are practically limited. This limitation does not occur with respect to the amplitudes of the voltage signals in the electric oscillation circuit 14. Moreover, its electrical variables can be changed and, in particular, increased without this having the same influence on the mass of the controller 9 as in a mechanical vibration absorber 4 according to FIG. 1.
- a damper 22 between the structure 1 and the absorber mass 6 is reproduced.
- the associated with the damper 22 damping the movement of the absorber mass 6 is often not only real available, but quite desirable.
- this attenuation is also reproduced in the control 9, in which not only the voltage signal 13, but also the transition signal 19 between the two integrators 17 and 18 with negative sign to the differential amplifier 16 in the electrical resonant circuit 14 is fed back.
- This transition signal 20 corresponds to a speed x T of the absorber mass of the simulated mechanical vibration absorber.
- the degree of damping is adjustable by an actuator 23.
- actuators 24 to 26 point to further intervention possibilities in the resonant circuit 14 in order to modify it if necessary.
- dashed lines is further indicated in Fig. 4 that also the transition signal 19 can be fed back into the differential amplifier 16 and that also the transition signals 19 and 20 can also be supplied to the conditioner 21 to enter the drive signal 12.
- the actuators 23 to 26 and also an actuator 27 for a feedback signal if any gurgekoppeltes 19 are not limited to potentiometers for adjustable attenuation of the respective input voltage. It can also be adjustable amplifiers or even adjustable inverters for the input voltage. Thus, a negative stiffness or a negative damping of a vibration absorber can be simulated analogously.
- an additional vibration sensor 38 on the structure 1 is indicated in FIG.
- FIG. 5 shows how a flat actuator 11 is arranged on a planar element 28 of the structure 1 by being connected to it in a planar manner.
- the controller 9 is shown here only as a "black box" which, depending on the signal 10 of the vibration sensor 8 on the structure 1 controls the actuator 8 with the drive signal 12 and the electrical power 28 is added from the outside.
- Fig. 6 shows a possible structure of the actuator 11.
- a sheath 29 which serves both for electrical insulation and for mechanical stabilization, a two-dimensionally extended piezoelectric layer 30 is arranged.
- the piezoelectric layer 30 is interposed between two surface electrodes 31 and 32.
- the surface electrode 31 is here formed by a copper cloth 33, while the surface electrode 32 is a coating 34 of the copper cloth 33 facing away from the surface of the piezoelectric layer 20.
- the drive signal 12 is applied between the surface electrodes 31 and 32 via electrical contacts 35 and 36.
- As a result of a voltage between the surface electrodes 31 and 32 there is an extension of the piezoelectric layer 30 in its main plane of extension, which transfers to the envelope 29.
- this extension of the actuator 8 acts in a curvature of the planar element 28 of the structure 1.
- the new device can be used wherever mechanical vibration absorbers have hitherto been used. Due to the variability in terms of their operating point, many other applications are possible in which a vibration problem does not occur or not only at a fixed frequency.
- a special application of the new device is the reduction of pressure pulsations in a hydraulic line between a pump, which is often the cause of the pressure pulsations, and a consumer.
- the actuator of the device can act directly on the pulsating hydraulic medium, so that it reduces the pressure oscillations .
- a part of the wall of the hydraulic line, in particular a rigid hydraulic line, in which the pressure pulsations occur are formed by the actuator, which is controlled orthogonally to the course of the wall.
- the actuator may also act on the hydraulic line to primarily reduce its deformation by the pressure pulsations. Even so, it has a reducing effect on the pressure pulsations of the hydraulic medium in the hydraulic line. LIST OF REFERENCE NUMBERS
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006046593A DE102006046593B4 (de) | 2006-09-30 | 2006-09-30 | Vorrichtung zur Reduktion von Schwingungen einer Struktur |
PCT/EP2007/008460 WO2008037487A1 (de) | 2006-09-30 | 2007-09-28 | Vorrichtung zur reduktion von schwingungen einer struktur |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2076689A1 true EP2076689A1 (de) | 2009-07-08 |
Family
ID=38728873
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07818542A Withdrawn EP2076689A1 (de) | 2006-09-30 | 2007-09-28 | Vorrichtung zur reduktion von schwingungen einer struktur |
Country Status (4)
Country | Link |
---|---|
US (1) | US20090248209A1 (de) |
EP (1) | EP2076689A1 (de) |
DE (1) | DE102006046593B4 (de) |
WO (1) | WO2008037487A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010003400B4 (de) | 2010-03-29 | 2013-11-21 | Deutsches Zentrum für Luft- und Raumfahrt e.V. | Verfahren und Vorrichtung zum Abmindern von Schwingungen einer Struktur |
KR101525741B1 (ko) * | 2014-07-29 | 2015-06-04 | 단국대학교 산학협력단 | 능동질량감쇠장치의 최적제어력 산정 및 제어방법 |
DE102016115369A1 (de) * | 2016-08-18 | 2018-02-22 | Automotive Lighting Reutlingen Gmbh | Lichtmodul eines Kraftfahrzeugscheinwerfers mit Schwingungsdämpfer, Kraftfahrzeugscheinwerfer und Verfahren zum Dämpfen von auf das Lichtmodul wirkenden Schwingungen |
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US4099211A (en) * | 1976-09-13 | 1978-07-04 | Ampex Corporation | Positionable transducing mounting structure and driving system therefor |
US4565940A (en) * | 1984-08-14 | 1986-01-21 | Massachusetts Institute Of Technology | Method and apparatus using a piezoelectric film for active control of vibrations |
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DE10051784C1 (de) * | 2000-10-19 | 2002-08-14 | Deutsch Zentr Luft & Raumfahrt | Elektromechanisches Funktionsmodul |
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-
2006
- 2006-09-30 DE DE102006046593A patent/DE102006046593B4/de not_active Expired - Fee Related
-
2007
- 2007-09-28 EP EP07818542A patent/EP2076689A1/de not_active Withdrawn
- 2007-09-28 WO PCT/EP2007/008460 patent/WO2008037487A1/de active Application Filing
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2009
- 2009-03-27 US US12/412,505 patent/US20090248209A1/en not_active Abandoned
Non-Patent Citations (1)
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See references of WO2008037487A1 * |
Also Published As
Publication number | Publication date |
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DE102006046593B4 (de) | 2009-12-10 |
WO2008037487A1 (de) | 2008-04-03 |
US20090248209A1 (en) | 2009-10-01 |
DE102006046593A1 (de) | 2008-04-03 |
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