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EP3449149A1 - Absorbeur de vibrations adaptatif à action mono-directionnelle - Google Patents

Absorbeur de vibrations adaptatif à action mono-directionnelle

Info

Publication number
EP3449149A1
EP3449149A1 EP17722369.0A EP17722369A EP3449149A1 EP 3449149 A1 EP3449149 A1 EP 3449149A1 EP 17722369 A EP17722369 A EP 17722369A EP 3449149 A1 EP3449149 A1 EP 3449149A1
Authority
EP
European Patent Office
Prior art keywords
leaf spring
vibration
vibration damper
damper according
mass
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.)
Pending
Application number
EP17722369.0A
Other languages
German (de)
English (en)
Inventor
Franz Mitsch
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.)
FM Energie GmbH and Co KG
Original Assignee
FM Energie GmbH and Co KG
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 FM Energie GmbH and Co KG filed Critical FM Energie GmbH and Co KG
Publication of EP3449149A1 publication Critical patent/EP3449149A1/fr
Pending 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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • 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
    • F16F15/04—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 using elastic means
    • F16F15/06—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 using elastic means with metal springs
    • F16F15/073—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 using elastic means with metal springs using only leaf springs
    • 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
    • F16F2238/00—Type of springs or dampers
    • F16F2238/02—Springs
    • F16F2238/022—Springs leaf-like, e.g. of thin, planar-like metal
    • 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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/1022—Vibration-dampers; Shock-absorbers using inertia effect the linear oscillation movement being converted into a rotational movement of the inertia member, e.g. using a pivoted mass

Definitions

  • the invention relates to a vibration damper or damper, which can be adapted over a certain range to the unidirectional disturbing sequences of a component to be damped or the machine or system to be damped with the aid of a leaf spring whose physically effective length is variable , the position of the
  • the invention relates to a vibration damper which itself is largely undamped, so that larger amplitudes and thus greater forces can be achieved here.
  • the damper according to the invention is particularly suitable for systems and machines which are subject to frequent speed changes, which often
  • Interference frequencies are generated, which are noticeable in particular by the occurrence of structure-borne noise.
  • Vibration dampers for reducing unwanted vibrations in machines, systems or their components are generally known in the art. For this purpose, numerous solutions have been proposed. Most of these solutions come with one
  • rotating systems with varying speeds tend, inter alia, to increased or increased structure-borne noise, which is undesirable in particular in wind turbines.
  • the absorber according to the invention consists essentially of a vibratory leaf spring (2.1), which directly or indirectly with the machine unit to be damped or Annex (4) (10.1) is connected.
  • the leaf spring is pressed with its flat side by means of an attached to the absorber mass (1) (10.2) biasing element (5, 5.1) to a roller unit (7), which in turn is in contact with the absorber mass, whereby the
  • Roller unit (7) by means of a displacement device (6) is shortened or lengthened according to the natural frequency to be set of the oscillating perpendicular to the leaf spring system.
  • the construction according to the invention is designed so that the absorber mass (1) (10.2) is not moved, which is a great advantage in view of the sometimes high absorber masses. In order to influence the frequency of this construction so that the effective length of the leaf spring must be variable.
  • the absorber according to the invention is designed in particular for a frequency range between approximately 50 Hz and approximately 200 Hz, but in principle exceeding frequency ranges are possible.
  • the invention is thus an adaptable to interference frequencies, effective in one direction adaptive vibration absorber for a machine unit or system which is exposed to the said and to be damped interference frequencies, essentially comprising a vibration mass (1) (10.2), and a vibratory leaf spring (2.1 ) with a first and an opposite second side, which is fixedly connected at its non-resilient end directly or indirectly with said machine unit or system, wherein on the first side of the leaf spring (2.1) a biasing element (5) (5.1) is arranged, which with the vibration mass (1) (10.2) is connected, and on the second side of the leaf spring (2.1) a roller unit (7) is arranged, which between the leaf spring and a facing surface of the vibration mass by a
  • Vibration mass can be moved back and forth and at a selected position on the leaf spring to the vibration mass (1) by the biasing member (5) (5.1) is pressed and fixed,
  • Leaf spring (2.1) determines, whereby the frequency of the oscillating perpendicular to the leaf spring machine unit or system can be variably changed and adjusted at locally unchanged vibration mass (1).
  • the mode of action of the absorber according to the invention is based on the fact that the natural frequency of the system equipped with a absorber according to the invention to be damped a
  • the roller unit (7) can now be moved accurately and with repeated accuracy to the correct position on the leaf spring (2.1), which corresponds to a natural frequency of the system, which in turn counteracts the disturbing frequency to be eliminated.
  • This interference frequency is usually associated with the rotational speed of the rotating component of the system or machine.
  • the reel unit (7) may have one or more juxtaposed rollers, which is moved by means of a displacement device (6), in one
  • Embodiment of the invention also in a plain bearing guide (8), so that the roller or rollers can not deviate from the tread on the leaf spring.
  • the rollers themselves may be hard or elastic, made of plastic or of metal or of a composite material, or be present as a corresponding hollow role. A certain role property can also influence the frequency to be set.
  • the leaf spring (2.1) is connected either directly to an attachment point (2.3) for the machine to be damped or via a connecting or holding element (2.2).
  • the entire mounting structure can also be understood as a combination of parts (2.3) and (2.2).
  • the leaf spring (2.1) is in the simplest embodiment of rectangular shape, preferably over its entire length. But it can also have other geometric shapes, whereby a specific vibration behavior can be generated. In a special
  • Embodiment it may also be trapezoidal, as shown in Fig. 4.
  • a trapezoidal leaf spring the narrow side of the trapezoid is either at the free end of the leaf spring or at the end, which is connected to the plant or machine to be damped
  • the required displacement of the roller (7) for varying the frequency is lower
  • a rectangular leaf spring requires a larger displacement, which usually has an advantageous effect on the accuracy of the frequency adjustment and adaptation.
  • a trapezoidal spring, as shown in Fig. 4 has an even longer adjustment path and thus an even higher accuracy.
  • Leaf springs of any shape for example, where critical frequency ranges can be set very precisely. Also leaf springs with different thickness over the length are suitable.
  • the biasing element (5) consists of one or more, preferably two compression springs which can be pressurized by corresponding tensioning devices in such a way that from one side of the leaf spring (2.1) against the roller unit (7) on the other side of Press leaf spring and thus also the mass (1) at the point of contact of roller (7) and leaf spring (1).
  • the absorber according to the invention with one or more, preferably two, elastic link elements (3), in particular
  • the handlebar springs have the task of preventing the mass (1) from twisting due to the spring forces arising from the biasing element (5) when the roller (7) is outside the
  • the handlebar springs can either at the
  • the forces are also higher at higher frequencies, as these higher frequencies occur in the range of rated power with high torques.
  • Higher frequencies have greater acceleration forces at the same amplitudes, so that they can be reduced with relatively small amplitude amplitudes.
  • the damping is lower, so that the vibration damper according to the invention can work optimally, without causing large vibration paths, which too
  • Vibration damper construction transmits the vibration path to a greater length at lower frequencies, the small frequencies are not critical with larger vibration ranges, which is a significant advantage of the absorber according to the invention. Due to the slightly damped structure, the region in which the vibration absorber according to the invention operates optimally is relatively narrow, so that it is expedient to set the respective absorber frequency with the greatest possible precision to a value dependent on the interference frequency, ie a corresponding fine adjustment of the position of the roller unit (7) to make the leaf spring (2.1). But as excited by the spurious frequency, as described, high
  • the displacement device (6) which also includes a drive to arrange in the area (6.5), occur in the much smaller accelerations. This area is in the immediate vicinity of the attachment point (2.3).
  • displacing rollers (6.1) (6.2) can not transmit high accelerations occurring on the mechanical elements of the displacement device (6).
  • Fig. 3 - 5 show such a belt drive. With such a drive, the desired frequency accuracy in the range of 0.25 to 0.5 Hz can be achieved according to the invention.
  • roller unit by a pull rope (9.1), which rolls up on a cable drum (9.2), pulled along the leaf spring with the force F1 in the direction of the position of the pulley and brought to the required position on the leaf spring.
  • the movement or return of the reel unit in the opposite direction by a force F0 is effected here by the clamping force of the biasing element (5), which presses on the leaf spring.
  • the natural frequency of the equipped with a Tilger according to the invention to be damped system is, as already mentioned, according to the invention a function of the axial
  • Roller device adapted exactly to the interference frequency.
  • the characteristic curve can then be used to set the servomotor control of the drive as a function of the frequency.
  • the drive now has the task, by means of the displacement device (6), the roller unit (7) exactly and repeat the exact position on the leaf spring (2.1) approach, which gives a natural frequency of the system, the frequency to be canceled, depending on the engine speed, counteracts.
  • Stepper motor although only in rare cases, "forget" its respective position, this moves at certain intervals, for example, once per hour, in an end position and recalibrates.
  • a linear motor which is controlled via a ruler scale, which measures exactly the respective position of the rollers.
  • the use of optical measuring methods, including lasers is conceivable.
  • the control units are programmed to move the rollers to the correct height depending on the disturbance frequency. This frequency deviations of ⁇ 0.1 Hz can be realized.
  • Interference frequency to an associated position along the path of the leaf spring (2.1) using the displacement device (6) driven.
  • the noise frequency usually is proportional to the engine speed, it is sufficient to detect only the speed as a function of the exciter frequency. This is done according to the prior art.
  • the electrical speed signal is applied to the structure and geometry of the
  • Vibration absorber adapted.
  • the natural frequency of the vibration absorber is determined as a function of the position of the reel unit in small steps by means of spline interpolation. This makes it possible to create a characteristic curve of the vibration damper with respect to frequency ⁇ - -> position roller on the leaf spring.
  • the adjustment of the speed-generating drive motor via measurement of the motor pulses as a function of the frequency to obtain a characteristic curve After this relationship, the motor of the drive is driven according to the required frequency. By manipulating the characteristic curve, it is now possible to vary the frequency required for attenuation in order to optimally set the absorber over a large range.
  • the invention thus also relates to a suitably equipped vibration absorber, which comprises a path adjustment system for tuning the absorber to the disturbance frequency in dependence on the position of the roller unit on the leaf spring.
  • Machine or system occur, for example, by speed changes, influence can be taken.
  • an active leaf spring length of for example 150 to 300 mm, frequencies between 50 Hz and 250 Hz, preferably between 100 Hz and 200 Hz, can be damped.
  • the leaf spring as already mentioned, be changed in their length or shape. Furthermore, it is possible to shift the frequency range to smaller frequencies by installing additional springs.
  • Vibration damper can be used particularly advantageously in conjunction with dampening absorbers of the prior art.
  • the vibration damper according to the invention is thus, as described, thus suitable for reducing or eliminating interference frequencies that occur in a machine or plant or parts of a machine or plant as a result of rotating components,
  • Fig. 1 shows a typical but illustrative simplified embodiment in plan view of the vibration damper according to the invention.
  • the leaf spring (2.1) is with a fixed, preferably not or little oscillatory holding element (2.2) firmly connected, which is connected in this case via a fastening device (2.3) with the machine part to be damped (4).
  • the vibration mass (1) is connected to the holding element (2.2) and to the biasing element (5).
  • the roller unit (7) is located as well as the leaf spring (2.1) in a recess of the absorber mass (1), which is formed as a plate or bundle of plates.
  • the absorber mass is pressed over the roller unit on one side and the biasing device (5) on the other side to the leaf spring, which then their vibration effective length between their attachment point to the element (2.2) or possibly directly to (2.3 ) and the point of contact with the roller (7).
  • the roller unit position 7 is moved in position so that the effective leaf spring (2.1) becomes longer or shorter effective according to the required frequency. Since the mass (1) does not voluntarily contact the roller unit (7), it must be pressed with a force. This force comes from the biasing springs (5) (5.1).
  • the leaf spring position 2.1 has a small spring constant (10 kN per 20
  • Tilgermasse (1) is connected.
  • Another link spring (3.2) connects the free end of the leaf spring (2.1) also with the oscillating mass (1).
  • this handlebar spring (3.2) are connected.
  • Holes are provided so that they can be penetrated by the biasing springs (5) to act directly on the leaf spring (2.1).
  • Fig. 2 shows a further embodiment of the vibration damper shown in Fig. 1.
  • an additional damping of the vibration mass is provided by a magnetic exciter, comprising an electromagnet actuator and a solenoid stator, which are separated by an air gap in the idle state are.
  • the magnet exciter serves mainly to compensate for the natural dispersion of the damping despite the exact setting of the reel unit along the length of the leaf spring.
  • damping dampers For use in wind turbines or other machines, it is often desirable or necessary to install additional damping dampers as known in the art (not shown).
  • Fig. 3 is a 3-D view of the vibration damper of Fig. 1. It can be seen particularly well the connection of the displacement device (6) with the drive (6.6).
  • the attachment point (2.3) which is connected to the machine part (4) to be damped is arranged on the side facing away from the absorber construction.
  • Fig. 4 is a section through the narrow side of the absorber according to the invention, in which one still recognizes on the bottom of the displacement device with toothed belt (6), as well as the biasing device with compression springs (5) and the roller unit (7).
  • Fig. 5 (a) (b) is a section through the long side of the absorber construction (5a) according to the invention and a 3-D view thereof (5b) is shown, in which the roller unit and the
  • Fig. 6 (a) shows a further embodiment of the vibration absorber according to the invention, which instead of a toothed belt drive (6.3) of the displacement element a
  • a pull rope (9.1) is mounted centrally on the reel unit (7).
  • the cable is guided longitudinally to the leaf spring and rolled up in the direction of the cable drum (9.2), which is driven by the drive unit (6.6).
  • the drive unit is mounted on the holding part (2.2) in the region of the small accelerations (6.5) in the vicinity of the fastening element (2.3).
  • the traction cable is rolled up with the force F1.
  • the counterforce F0 is provided by the biasing member (5) and causes the reel unit (7) to be urged in the opposite direction to F1, provided a correspondingly aligned angle (9.3) between the leaf spring (2.1) and the opposite running surface of the reel unit of the
  • the angle (9.3) can be achieved for example by an oblique arrangement of the leaf spring.
  • the angle should be at least 1 °, but not more than 4 ° in order to achieve an optimal effect.
  • the angle opened in the direction of the force F0 should be 1.5-2 °.
  • the spring force FO corresponds to the force multiplied by the tangent of the angle.
  • the tensile force (9.4) corresponds to about 2.6% of the spring force originating from the pretensioning element (5).
  • the roller unit (7) is advanced and tensioned the tension cable (9.1). About the cable drum (9.2), the exact location of
  • Pretension is, so that the teeth of the transmission always rest on the same side of the flank.
  • the exact position determination is thus carried out over the existing in the engine Drehwinkelaufêt, so that an additional way adjustment system is not necessary here to achieve the precision required for the exact way determination.
  • the figure shows the rope drum (9.2) with a small diameter and several rope layers. It has proven to be advantageous that a more precise travel control is possible with a single-layer cable drum with a correspondingly larger diameter.
  • Fig. 7 shows a modified embodiment of an inventive
  • Vibration damper which is intended for the vibration-calming of large rotating machines.
  • Inner ring (10.2) and outer ring (10.1) are radially connected in their circumference by means of several control springs (10.3).
  • control springs (10.3) about several also arranged in the circumference of the rings biasing springs (5) of the inner ring, which has the same number, correspondingly arranged flywheel (10.4), including these mass segments with the necessary bias against the roller unit (7) pressed.
  • the actual spring element (2.1) is thus connected via the roller (7) with the flywheel (101.4) of the inner ring 10.2.
  • the system is hereby described for the inner ring as Tilger flywheel.
  • the outer ring is the component to be soothed by the absorber. With the same function and the outer ring can be used as a damper to calm the inner ring.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne un absorbeur de vibrations ou un amortisseur à masse accordée, apte à s'adapter dans une plage déterminée, aux séquences perturbatrices, agissant dans une direction définie, d'un élément à amortir ou de la machine ou installation à amortir, à l'aide d'un ressort à lames, dont la longueur physique est de conception variable. L'invention concerne en particulier un absorbeur de vibrations, qui est lui-même largement non amorti, de manière à pouvoir atteindre de plus grandes amplitudes et ainsi de plus grandes forces. L'amortisseur selon l'invention est approprié, notamment à la réduction des bruits d'impact dans des installations et machines, de préférence des éoliennes, qui sont soumises à de fréquentes variations de vitesses et donc qui entrent en oscillations.
EP17722369.0A 2016-04-28 2017-04-24 Absorbeur de vibrations adaptatif à action mono-directionnelle Pending EP3449149A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP16000959 2016-04-28
PCT/EP2017/000506 WO2017186343A1 (fr) 2016-04-28 2017-04-24 Absorbeur de vibrations adaptatif à action mono-directionnelle

Publications (1)

Publication Number Publication Date
EP3449149A1 true EP3449149A1 (fr) 2019-03-06

Family

ID=55862502

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17722369.0A Pending EP3449149A1 (fr) 2016-04-28 2017-04-24 Absorbeur de vibrations adaptatif à action mono-directionnelle

Country Status (2)

Country Link
EP (1) EP3449149A1 (fr)
WO (1) WO2017186343A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108591334B (zh) * 2018-05-12 2019-11-05 王快乐 一种下压力减震器
US20230296155A1 (en) 2020-03-03 2023-09-21 Fm Energie Gmbh & Co.Kg Frequency-adaptive leaf-spring tuned mass damper

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19741627B4 (de) * 1997-09-20 2006-04-13 Volkswagen Ag Schwingungstilger
DE19856500B4 (de) 1998-12-08 2005-12-08 Franz Mitsch Schwingungstilger
ATE342410T1 (de) 2002-01-03 2006-11-15 Franz Mitsch Einstellbarer schwingungstilger
FI119519B (fi) * 2007-06-27 2008-12-15 Metso Paper Inc Paperikoneen tela ja värähtelyn vaimennin
FI126119B (fi) * 2011-01-31 2016-06-30 Waertsilae Finland Oy Massavaimennin
DE102012205797A1 (de) * 2012-04-10 2013-10-10 Zf Friedrichshafen Ag Drehschwingungsdämpfungsanordnung
EP2816177B1 (fr) 2013-05-08 2017-09-06 FM Energie GmbH & Co. KG Amortisseurs de vibrations pour des tours d'éoliennes

Also Published As

Publication number Publication date
WO2017186343A1 (fr) 2017-11-02

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