WO2012065796A1 - Dispositif de réduction active d'une vibration mécanique - Google Patents

Dispositif de réduction active d'une vibration mécanique Download PDF

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Publication number
WO2012065796A1
WO2012065796A1 PCT/EP2011/068082 EP2011068082W WO2012065796A1 WO 2012065796 A1 WO2012065796 A1 WO 2012065796A1 EP 2011068082 W EP2011068082 W EP 2011068082W WO 2012065796 A1 WO2012065796 A1 WO 2012065796A1
Authority
WO
WIPO (PCT)
Prior art keywords
vibration
cam
oscillation
machine structure
primary
Prior art date
Application number
PCT/EP2011/068082
Other languages
German (de)
English (en)
Inventor
Mark Mohr
Michael Wechs
Bastian Volpert
Gerhard Gumpoltsberger
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2012065796A1 publication Critical patent/WO2012065796A1/fr

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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
    • F16F15/22—Compensation of inertia forces
    • F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
    • F16F15/261—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system where masses move linearly
    • 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
    • F16F15/043—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 acting on a cam follower

Definitions

  • the invention relates to a device for actively reducing a mechanical vibration in a machine structure according to the preamble of patent claim 1.
  • the spurious vibration of a structure is detected by means of a suitable vibration sensor, and the sensor signals are used to control a separate vibration source, which generates the counter-vibration and initiates the structure.
  • Such devices are also used in the automotive industry, for example to compensate for vibrations of an internal combustion engine relative to the vehicle body or vibrations in the drive train of a motor vehicle, where previously used systems such as torsion damper, dual mass flywheels and windings thereof (dual mass flywheel with centrifugal pendulum), crankshaft starter generators, etc. are not sufficient or do not detect the desired vibration bandwidth.
  • the invention has for its object to provide a device referred to in the preamble of claim 1, which is structurally and control technology simple, and which is able to effectively suppress or mitigate at least regular oscillations of any strength.
  • the invention is based on the finding that, in particular for compensating for regular oscillations, it is also possible to serve a mass moved by means of a cam gear when the gear curve corresponds to the oscillation to be compensated.
  • the invention is based on a device for active reduction of a mechanical, introduced by a drive unit in a connected thereto machine structure primary vibration, wherein the vibration is superimposed by means of a separate, connected to the machine structure vibration source counter-vibration.
  • the separate vibration source comprises at least one arranged on one of the primary vibration part of the machine assembly, driven by a cam gear to a lifting movement, working at a Aus detailhub against a bias of an energy storage piston element or the like, wherein the Cam mechanism is drive-connected to the drive unit.
  • the term "piston element or the like” is understood to mean any component driven by the cam mechanism for its stroke movement, which is capable of delivering energy to any energy store whose influence influences the characteristics of a stroke movement referred to here as an outward stroke to the shape of the generated counter-vibration, as will be explained.
  • the arrangement of the separate vibration source on one of the primary vibration subjected part of the machine assembly, the counter-vibration is introduced directly into the machine assembly. Since the separate vibration source is also drivingly connected to the drive generating the primary vibration, the primary vibration on the one hand and the counter-vibration on the other hand always change in the same direction at a speed change of the drive unit, so that at least for a particular speed range complete or at least partial eradication of the vibrations is guaranteed.
  • the frequency of the countervibration depends on the speed and the formation of the transmission curves.
  • the extinction of the primary vibration is achieved by a superposition of the countervibration.
  • the amplitude of the countervibration can be changed according to a preferred embodiment of the invention, for example, by changing the bias of the respective energy storage. According to a further embodiment of the invention it is provided that for this purpose, the stroke of the piston element or the like is adjustable. Also, a complete shutdown of the countervibration can be made, for example, to facilitate the start of the engine.
  • a torsional vibration damper is known from DE 10 2009 038 189 A1, in which of a separate drive unit driven cams several energy storage depending on the angle of rotation can be stretched or relaxed. In this case, the bias of the energy storage can be changed from the outside and thus adapted to certain operating conditions.
  • this known damper is based on the principle that is stored in a non-uniform drive (eg by a piston engine) during the power stroke and discharged again in the intake stroke, whereby a smoothing of the drive torque is achieved. Accordingly, this known damper does not work according to the principle of vibration cancellation by a counter-vibration.
  • a preferred further embodiment of the invention provides that the energy accumulator is designed as a hydropneumatic accumulator with a hydraulic fluid volume acted upon by the piston element or the like and a gas volume separated therefrom by means of a membrane or the like.
  • the pressure in the gas volume determines the bias of the energy storage.
  • the internal pressure of the gas volume is adjustable according to the invention, so that the bias of the energy storage is variable.
  • a further embodiment of the invention provides that a hydraulic oil is provided as the hydraulic fluid, and that this hydraulic fluid volume is connected to one or more hydraulic oil consumers.
  • the separate vibration source according to the invention can be used simultaneously for an oil supply of the machine structure, i. be used for example for a pressurized oil or lubricating oil supply.
  • conventional, normally provided for this purpose devices such as gear pumps, vane pumps, cam pumps and the like may be unnecessary.
  • the energy store is a mechanical spring whose bias can be changed.
  • the energy store comprises an electric linear motor linear generator with a movable armature formed by the piston element or the like and a stator cooperating therewith, as well as an electrical capacitor connected thereto.
  • This capacitor represents the actual energy storage, which is charged by the linear motor linear generator in the generator mode.
  • the bias of the energy storage corresponds to the respective state of charge of the capacitor.
  • the energy storage is formed by a magnetic field between a movable magnet formed by the piston member or the like and a fixed magnet opposite same polar orientation.
  • the bias of this energy storage corresponds to the respective repulsive force of the two magnets.
  • at least one of the magnets is designed as an electromagnet with variable magnetic field strength.
  • the cam mechanism via which the respective piston element or the like is actuated comprises, according to a preferred embodiment of the invention, a cam correspondingly shaped to the desired countershaft and drive-connected with the drive unit and a cam follower element cooperating therewith and connected to the piston element or the like.
  • the bias applied by the energy storage ensures that the cam follower is held in contact with the cam.
  • the contour of the cam is variable. This change can be made either steplessly by changing the shape of the cam itself or stepped by switching between cams of different contour.
  • the means for producing be formed switched off a counter-vibration, so that no counter-vibration is transmitted to the subject of the primary vibration part of the machine structure.
  • the amplitude of the countervibration may be generated in dependence on the load acting on the part of the machine structure subjected to the primary vibration.
  • the countervibration of the load can be adjusted.
  • the load can be detected, for example, based on the displacement of two masses, which are connected to each other via a spring means.
  • two masses could be comprised of a dual mass flywheel.
  • a sensor can detect this shift and adjust the energy store accordingly, for example, via a servomotor or the like.
  • a spring element can be biased accordingly, the pressure of a hydraulic fluid volume or volume of gas to be changed accordingly, but also a capacitor are pre-charged.
  • sensors can also possible as sensors to use pressure sensors, such as piezoelectric elements, which detect the transmitted pressure.
  • FIG. 2 schematically shows a vibration source for generating a counter-vibration with a hydropneumatic energy storage
  • Fig. 3 shows schematically a vibration source with a mechanical
  • Coil spring as energy storage 4 shows schematically a vibration source with a mechanical spiral spring as energy storage
  • Fig. 5 shows schematically a vibration source with an electrical
  • Linear motor / generator and a capacitor as energy storage
  • Fig. 6 shows schematically a vibration source with a magnetic field formed between two homopolar magnets as energy storage.
  • FIG. 1 shows on its left side a diagram 2 in which the course of a primary vibration 4 introduced into a machine structure, for example into the drive train of a motor vehicle, is plotted over the time t or the phase angle ⁇ .
  • a separate vibration source 6 Disposed on a part of the machine structure subjected to the primary vibration 4 is a separate vibration source 6 capable of producing a counter vibration 8 opposed to the primary vibration 4, which is introduced directly into the machine structure and releases the primary vibration 4, as in FIG the diagram 10 shown on the right side in FIG. 1 by the fully smoothed line 12 is shown.
  • the oscillation source 6 comprises a mechanical cam mechanism 14 preferably designed as a cam drive, which drives a piston element or the like to a lifting movement, wherein the piston element or the like works in an outward stroke against a bias voltage of an energy accumulator 16, as will be explained in detail.
  • the cam mechanism 14 is preferably also drive-connected to the drive unit, which induces the primary oscillation, so that the primary 4 vibration and the counter-vibration 8 are always synchronized with each other.
  • the energy store is designed as a hydropneumatic accumulator 18 with a hydraulic fluid volume 22 acted on by a piston element 20 and a gas volume 26 separated from it by a membrane 24.
  • hydraulic fluid volume oil is provided in the present case.
  • the pressure energy in the gas 26 is increased via the incompressible oil volume 22 and the membrane 24 under a bias pressure gas volume 26 in response to the shape of the piston member 20 moving cam 28 and that with the piston member 20 connected cam follower element 30 held in contact with the cam 28.
  • the desired countervibration is generated and the machine structure is initiated.
  • the pressure bias in the gas volume 26 can be varied via a control valve 32 connected to a gas pressure vessel, not shown, or the like.
  • FIG. 2 additionally offers the possibility of supplying a hydraulic fluid consumer 34 with a desired oil pressure or oil volume by branching off an oil flow from the hydraulic fluid volume 22.
  • a hydraulic fluid consumer 34 for this purpose, starting from the hydropneumatic accumulator 18, an oil line, a switching valve (not further described) and a gas pressure-loaded oil reservoir are present.
  • Fig. 3 shows an arrangement similar to that of Fig. 2, but wherein the energy storage is a mechanical spring 36 which is compressed by the piston member 38 in its Ausfacthub.
  • the action of the mechanical spring 36 designed as a helical spring can be varied by means of a piston 40 arranged on the side opposite the piston element 38, which in turn can be hydraulically adjusted with respect to its position via a control valve 44 connected to a hydraulic fluid pump 42.
  • the hydraulic fluid pump 42 and / or the control valve 44 in response to the load applied to the piston member 28 or a component connected thereto, are controlled.
  • an elastic member rotatably connected, which transmits the force to another rigid element.
  • the rigid element with respect to the piston element 28 move. This shift is detected by a sensor and forwarded to the control unit of the control valve 44 and / or the hydraulic pump 42.
  • the energy store 46 is also a mechanical spring, which in this case, however, is designed as a helical spring 48.
  • the coil spring 48 is arranged radially within the cam contour of the cam 50.
  • the rotating cam 50 displaces a piston element 52, which in this case is designed as a toothed rack, into a lifting movement, which in turn drives a crank rocker assembly 54 whose end link 56, which is connected to the spiral spring 48, periodically tensions it.
  • a change in the spring preload can be achieved, for example, by displacement of the articulation point 57 of the coil spring 48 on the end link 56.
  • Fig. 5 shows an embodiment in which the energy storage a linear electric motor linear generator with a piston member 58 forming a movable armature and a cooperating Stator 60 and an associated electrical capacitor 62 summarized.
  • the electrical energy generated during the lifting movement of the armature 58 is stored in the capacitor 62 and released again.
  • the armature 58 is driven in the manner already described with reference to Figures 1 to 4 by means of a rotating cam 64 to its lifting movement.
  • the energy store is formed by a magnetic field between a movable magnet forming the piston element 66 and a magnet 68 which is fixedly arranged opposite this and has the same positive pole orientation in the present case.
  • the movable magnet 66 is driven via a rotating cam 70 to its lifting movement. As the two magnets 66, 68 approach, the magnetic field located between them and thus the energy stored in this energy storage increases.
  • At least one of the magnets may be designed as an electromagnet with a variable magnetic field strength, so that in this way the bias of the energy storage can be changed.
  • the cam gear can be arranged directly in the power flow between the drive unit and the machine structure or parallel to the power flow.
  • a drive train of a motor vehicle there is the possibility of arranging, for example, on the primary side or on the secondary side on a dual mass flywheel, between a dual mass flywheel and a transmission, on or within the transmission, on or in the control drive of the internal combustion engine, on the camshaft or the crankshaft or the like.
  • the drive of the cam gear can be done directly from the crankshaft of the engine, the transmission input shaft or indirectly via gears, chain or belt.
  • the energy store could deviate from the illustrated embodiments, an electric battery, a galvanic cell, a redox flow cell, a flywheel, a heat storage or the like.
  • energy to be stored e.g. also a chemical potential, a kinetic energy, a potential energy or the like in question.
  • the cam gear can be regulated or connected and disconnected by means of a phase adjuster (cam phaser), a planetary gear, a hydrostatic or a friction wheel or belt drive.
  • the cam shape can also vary in the direction of the depth in the circumferential direction, the movement excited by the cam can be, for example, radial, tangential or axial.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne un dispositif de réduction active d'une vibration primaire (4) mécanique induite par un système d'entraînement dans une structure de machine reliée à celui-ci, la vibration primaire (4) étant superposée à une contre-vibration (8) au moyen d'une source de vibration (6) séparée reliée à la structure de machine. La source de vibration (6) séparée comprend au moins un élément piston ou similaire agencé sur une partie de la structure de machine soumise à la vibration primaire, entraîné dans sa course par une commande à cames (14) et agissant à l'encontre d'une précontrainte d'un accumulateur d'énergie (16) lors d'une course vers l'extérieur, la commande à cames étant elle-même également reliée par entraînement au système d'entraînement. La source de vibration (6) séparée produit une contre-vibration opposée à la vibration primaire (4). Etant donné que la source de vibration (6) séparée est également reliée par entraînement au système d'entraînement, la vibration primaire (4) et la contre-vibration (8) varient de manière toujours synchrone lors d'un changement de vitesse.
PCT/EP2011/068082 2010-11-16 2011-10-17 Dispositif de réduction active d'une vibration mécanique WO2012065796A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010043952A DE102010043952A1 (de) 2010-11-16 2010-11-16 Einrichtung zur aktiven Reduzierung einer mechanischen Schwingung
DE102010043952.5 2010-11-16

Publications (1)

Publication Number Publication Date
WO2012065796A1 true WO2012065796A1 (fr) 2012-05-24

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PCT/EP2011/068082 WO2012065796A1 (fr) 2010-11-16 2011-10-17 Dispositif de réduction active d'une vibration mécanique

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WO (1) WO2012065796A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3014515B1 (fr) * 2013-12-09 2016-07-01 Renault Sa Dispositif de regulation de la rotation d'un arbre, notamment dans le domaine automobile
EP3088578B1 (fr) * 2015-04-27 2017-03-22 Karl Mayer Textilmaschinenfabrik GmbH Métier à tricoter à chaîne

Citations (8)

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Publication number Priority date Publication date Assignee Title
DE3607133A1 (de) * 1986-03-05 1987-09-10 Kloeckner Humboldt Deutz Ag Einrichtung zum ausgleich von massenkraeften und massenmomenten
DE4141637A1 (de) 1991-12-17 1993-06-24 Metzeler Gimetall Ag Aktives, elastisches lager
DE4441798A1 (de) * 1993-12-01 1995-06-08 Fev Motorentech Gmbh & Co Kg Hubkolbenmaschine mit Massenausgleich
DE4410495A1 (de) * 1994-03-27 1995-09-28 Schrick Gmbh Dr Kolbenmaschine mit Ausgleich freier Massenkräfte
EP0800021A2 (fr) * 1996-04-01 1997-10-08 Sankyo Seisakusho Co. Mécanisme de transformation d'un mouvement avec compensation de couple
FR2802264A1 (fr) * 1999-12-10 2001-06-15 Renault Dispositif d'equilibrage d'un moteur thermique
WO2004083611A1 (fr) * 2003-03-21 2004-09-30 Audi Ag Commande de soupape d'un moteur a combustion interne presentant une culasse
DE102009038189A1 (de) 2008-09-04 2010-04-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehschwingungsdämpfer

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4013500C2 (de) * 1990-04-27 1993-12-02 Audi Ag Vorrichtung zur Verbesserung des Massenausgleichs des Ventiltriebes einer Achtzylinder-Viertakt-Brennkraftmaschine
DE29614589U1 (de) * 1996-08-22 1997-12-18 Fev Motorentech Gmbh & Co Kg Hubkolbenmaschine mit veränderbar einstellbarem Massenausgleich
DE102007020050A1 (de) * 2007-04-27 2008-10-30 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Vorrichtung zur Schwingungstilgung

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3607133A1 (de) * 1986-03-05 1987-09-10 Kloeckner Humboldt Deutz Ag Einrichtung zum ausgleich von massenkraeften und massenmomenten
DE4141637A1 (de) 1991-12-17 1993-06-24 Metzeler Gimetall Ag Aktives, elastisches lager
DE4441798A1 (de) * 1993-12-01 1995-06-08 Fev Motorentech Gmbh & Co Kg Hubkolbenmaschine mit Massenausgleich
DE4410495A1 (de) * 1994-03-27 1995-09-28 Schrick Gmbh Dr Kolbenmaschine mit Ausgleich freier Massenkräfte
EP0800021A2 (fr) * 1996-04-01 1997-10-08 Sankyo Seisakusho Co. Mécanisme de transformation d'un mouvement avec compensation de couple
FR2802264A1 (fr) * 1999-12-10 2001-06-15 Renault Dispositif d'equilibrage d'un moteur thermique
WO2004083611A1 (fr) * 2003-03-21 2004-09-30 Audi Ag Commande de soupape d'un moteur a combustion interne presentant une culasse
DE102009038189A1 (de) 2008-09-04 2010-04-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehschwingungsdämpfer

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