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WO2011060752A1 - Embrayage à friction équipé d'un disque d'embrayage pour transférer des couples - Google Patents

Embrayage à friction équipé d'un disque d'embrayage pour transférer des couples Download PDF

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Publication number
WO2011060752A1
WO2011060752A1 PCT/DE2010/001255 DE2010001255W WO2011060752A1 WO 2011060752 A1 WO2011060752 A1 WO 2011060752A1 DE 2010001255 W DE2010001255 W DE 2010001255W WO 2011060752 A1 WO2011060752 A1 WO 2011060752A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction
absorber mass
disc
energy storage
rotation
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.)
Ceased
Application number
PCT/DE2010/001255
Other languages
German (de)
English (en)
Inventor
Markus Hausner
Steffen Lehmann
Martin HÄSSLER
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG 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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to CN201080052034.5A priority Critical patent/CN102612613B/zh
Priority to DE112010004468.6T priority patent/DE112010004468B4/de
Publication of WO2011060752A1 publication Critical patent/WO2011060752A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1421—Metallic springs, e.g. coil or spiral springs
    • F16F15/1428—Metallic springs, e.g. coil or spiral springs with a single mass
    • 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
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
    • F16F15/1292—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means characterised by arrangements for axially clamping or positioning or otherwise influencing the frictional plates
    • 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
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
    • F16F15/1297—Overload protection, i.e. means for limiting torque
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/0052—Physically guiding or influencing
    • F16F2230/0064—Physically guiding or influencing using a cam

Definitions

  • the invention relates to a friction clutch with a clutch disc for transmitting torque with a friction device.
  • Friction clutches with such clutch plates have long been known and are used for example as separation or starting clutches in motor vehicles between the internal combustion engine and the transmission.
  • the power transmission between the internal combustion engine such as diesel or gasoline engine and transmission as manual transmission, automated manual transmission, dual-clutch transmission is provided with frictional friction clutches, which is controlled by a complete separation over a slipping to complete operation continuously controlled by an actuating system.
  • the mean friction torque can be superimposed on an alternating torque, which can lead to disturbing vibrations in the drive train or to disturbing vibrations on the motor vehicle.
  • torsional vibration dampers with integrated into the power flow energy storage such as coil springs
  • torsional vibration dampers which are designed for the problematic frequency range of the torsional vibrations.
  • a known technique for this purpose is a parallel to the drive train, for example on the clutch disc, coupled via an energy storage device and a friction absorber mass, the possible occurring vibrations compensated by a counter-torque in the correct phase. This is known, for example, from DE 10 2008 028 570 A1, the disclosure content of which with regard to the construction is hereby expressly integrated.
  • the height of the possible occurring alternating moments for the design must be estimated or fixed.
  • the friction is then optimized for the selected alternating torque and executed constructively as a constant friction torque.
  • This vibration damping system achieves its optimum effect during operation when the actual alternating torque occurring during operation corresponds to the assumption in the design. If, on the other hand, the alternating moment occurring during operation is smaller than the assumption, the spring-mass system tends to adhere to the mass to be occupied, thereby possibly losing its effect.
  • the critical frequency is better attenuated, the amplitudes increase before and after the original critical frequency, which may also increase the risk of disturbing vibrations.
  • the object of the invention is therefore an advantageous development of a friction clutch with a clutch disc, which allows at least largely independently of the amplitudes of the torque to be transmitted superimposed torsional vibrations an efficient elimination of torsional vibrations.
  • a friction clutch with a clutch disc for transmitting torques, wherein, forming a torsional vibration damper, a friction device integrated in the clutch disc is provided with a frictional torque dependent on the relative angle of rotation between the absorber mass and the mass to be engaged.
  • the proposed friction clutch for example, in the drive train of motor vehicles regardless of the vehicle type such as passenger cars, commercial vehicles, motorized two-wheelers and the like and transmissions regardless of the type of transmission such as manual, automated manual, double clutch and the like may be provided as a frictional friction clutch, preferably as a dry clutch.
  • the proposed friction clutch avoids or at least reduces torsional vibrations, in particular in the drive train of a motor vehicle, preferably also for reducing possible torsional vibrations due to periodic torque fluctuations in friction clutch systems such as a motor vehicle clutch, which have a substantially constant excitation frequency but different amplitudes. These torque fluctuations can arise both from external excitation and from self-excitation (instability). According to the invention, the proposed solution can also be used for all other torsional vibration problems with a critical frequency range.
  • the theoretical degree of reduction in the case of forced excitation may advantageously be greater than or equal to 50%, preferably greater than or equal to 60%, that is, the residual vibrations when using the proposed torsional vibration damper in the clutch disc are less than 50% and 40% compared to a system without torsional vibration damper.
  • the torsional vibration damper can therefore also be used alternatively to increase the permissible alternating torques at a constant vibration level. Self-excitation by negative overall damping of the drive train is avoided when using such a torsional vibration damper.
  • the torsional vibration damper offers due to its positive damping properties, for example, in addition to use alternative covering materials for the friction linings of the clutch disc, such as the use of ceramic-based pads instead of organic-based pads in a dry friction clutch, for example, by their large friction coefficients and low padding suspension the excitation of the clutch disc and the subsequent drive train is particularly high, but these can be eliminated by the proposed torsional vibration damper in an improved form.
  • a torsional vibration damper is proposed with absorber mass energy storage friction device system arranged in parallel, which attenuates possible vibrations in a critical frequency range of a torsional vibration excitation and whose effectiveness is independent of the amplitude of an exciting alternating torque.
  • a friction device is provided with a friction torque dependent on the predetermined relative angle of rotation between the absorber mass and the mass to be used. This dependence can be carried out with angular proportionality but also according to any law. This achieves a degree of reduction independent of the excitation amplitude.
  • the entire energy storage / friction unit is designed so that a flexible characteristic design is possible.
  • the friction can be realized with and without basic friction, as well as with play.
  • the first energy storage can also be realized with or without bias, as well as with game.
  • a friction clutch for this purpose, in which the clutch disc contains a disc part and a counter to the action of a first energy storage relative to the disc part by a predetermined angle of rotation relatively rotatable absorber mass and the first energy storage, the friction device is connected in parallel with verfwinkelinem friction torque.
  • the friction torque which can be set via the angle of rotation can be provided by the friction device comprising a ramp device with a first ramp part provided with rotation in the circumferential direction with ramps arranged in the circumferential direction and a second ramp part provided with the drive part with counter ramps complementary to the ramps and one of the two ramp parts a friction surface against the action of an axially effective, axially firmly received second energy storage acted upon.
  • the configuration of the slopes of the ramps and complementary counter ramps to these can be adapted to the requirements of the provided over the angle of rotation friction torque.
  • ramps and counter ramps in a central position of the absorber mass relative to the disc part over a twist angle smaller than a maximum angle of rotation have a slope zero.
  • a constant for example, from an additional and / or the ramps having friction pair or only the physically not excludable Störreibungsmoment is applied.
  • the pitch profile over at least a portion of the predetermined angle of rotation may be linear, progressive, degressive or formed in free form.
  • the second energy storage can generate a basic friction by corresponding bias against the friction surface of the friction disc provided for this purpose.
  • the friction device may include a further friction disc for providing a basic friction.
  • the friction surfaces of the variable friction friction device may be provided, for example, between a friction plate and the absorber mass be, wherein the friction disc and the absorber mass have the corresponding ramps and counter ramps.
  • the second energy storage have counter-ramps, which are applied to ramps of the absorber mass or connected to this friction disc.
  • the second energy store can be arranged on the absorber mass and apply a friction disk fixedly connected to the disk part. It is understood that the enumeration of the execution options of ramps, counter ramps in connection with the application of these by the second energy storage are not restrictive compared to the spirit of the invention to understand.
  • the clutch disc of the first energy storage can be formed in a spring cage, effective in the circumferential direction helical compression springs, wherein the absorber mass is rotatably mounted on the spring cage and the coil springs in the direction of action in each case on one side on the spring cage and radially in the spring cage extended cam support.
  • the spring cage may have radially expanded, in recesses of the absorber mass at least in the amount of the angle of rotation play engaging cam.
  • the cams of the spring cage abut on the peripheral boundaries of the recesses.
  • the twist angle can be made soft, for example by interposing buffers such as spring elements or rubber buffers.
  • the angle of rotation can be determined by a block position of the coil springs, hard attacks can be avoided by partial Gölaglagem the spring coils of the coil springs.
  • a slip clutch is provided.
  • the slip clutch is preferably arranged between the disc part and the absorber mass effectively.
  • the spring cage with the helical springs relative to the disc part against the action of a third energy storage for example, a plate spring can be rotated biased.
  • a frictional torque between the disc part and the spring cage is formed, which is overcome upon reaching a predetermined torque between absorber mass and disc part, so that the absorber mass relative to the disc part over the predetermined angle of rotation can be twisted out and therefore avoid hard attacks.
  • the interpretation of this friction torque depending on the torsional stiffness of the first energy storage controls whether the absorber mass slips against the disc part before or upon reaching a hard stop, for example when reaching the block position or striking the absorber masses on a component of the disc part.
  • the clutch disc with torsional vibration damper with spring cage can advantageously provide the spring cage axially between an axially supported on the disk part, third energy storage and a relative to the disk part axially spaced and firmly recorded cover sheet to be braced.
  • the third energy storage and the cover plate additionally a friction disc and the second energy storage be braced.
  • the friction clutch can according to the inventive idea continue to include a torsional vibration damper in addition to the proposed torsional vibration damper.
  • the disk part is divided into an input and output part, between which a fourth energy store, which is effective in the circumferential direction, is connected, for example helical springs distributed over the circumference.
  • a friction device can be connected in parallel with this fourth energy store.
  • FIG 2 is a partial section through one of the clutch disc of Figure 1 similar
  • FIG. 3a shows a partial view of a friction device with variable over the angle of rotation friction torque in the middle position in a schematic representation
  • FIG. 3b shows the friction device of FIG. 3a in a twisted state
  • Figure 5 is a torque / angle of rotation characteristic of the proposed torsional vibration damper
  • FIG. 6 shows a detailed view of the torsional vibration damper of FIGS. 1 and 2.
  • Figure 1 shows the housed in a friction clutch, not shown, clutch disc 1, which is arranged about the rotation axis 2 and is rotationally connected by means of the hub 3 with a transmission input shaft.
  • clutch disc 1 With the hub 3, the friction linings, not shown, to form the friction engagement with the friction clutch receiving disc part 4 is firmly connected, for example - as shown here - caulked.
  • the torsional vibration damper 5 is also arranged, which contains the spring cage 6 formed from the cage parts 7, the first energy accumulator 8 received therein in the form of the coil springs 9, the absorber mass 10 and the friction device 11.
  • the torsional vibration damper 5 is rotatably received on the hub 3 and under formation of the slip clutch 12 between the disc part 4 and connected to the hub 3, for example - as shown here - caulked cover plate 13 axially braced.
  • a cage part 7 is applied to the cover plate 13 and the other cage part 7 of the split to accommodate the coil springs 9 spring cage 6 with the second energy storage 14 of the friction device 11.
  • the designed as a plate spring 15 second energy storage 14 serves as a contact for the friction disc 16 of the slip clutch 12, which is acted upon axially by the third energy storage 17 in the form of the disk part 4 axially supporting plate spring 18 and the friction torque of the slip clutch 12 determines.
  • the absorber mass 10 is limited to the spring cage 6 against the action of the coil springs 9 rotatable.
  • cam 19 and the absorber mass 10 radially inwardly extended provided in the spring cage 6 radially engaging cam 20, which act on the circumference and inserted into the spring cage 6 coil springs 9 each act on the front side.
  • the absorber mass 10 can be adjusted relative to the spring cage 6 and thereby the angle of rotation between them are specified. Before or upon reaching a stop, the slip clutch 12 can be effective.
  • the effect of the first energy store 8 can be connected in parallel at least over a predetermined angle of rotation range, the friction device 11.
  • the friction device 11 has the ramp device 21, which is formed from the two mutually relatively rotated ramp parts 22, 23 with the circumferentially formed ramps 24 and counter-ramps 25 complementary thereto.
  • the ramp part 22 is preferably integrated in the absorber mass 10, for which purpose the ramps 24 can be stamped into the absorber mass or inserted as a ramp ring.
  • the ramp portion 23 is preferably formed of plastic and firmly connected to the plate spring 15, for example, hung or - as shown - melted by means of the warts 26.
  • the frictionally engaged by the frictional contact with the slip clutch 12 with the disk part 4 plate spring 15 sets the frictional engagement of ramps 24 and counter ramp 25.
  • disc part 4 Upon entry of torque fluctuations such as torque peaks in the frequency range of the tuned torsional vibration damper 5 in the rotating at a predetermined speed disc part 4 attempts the absorber mass 10 due to the action of the first energy storage 8, the set on the friction device 11 friction torque and the moment of inertia of the absorber mass 10 in a stable To remain rotational position, whereby a twist angle between disc part 4 and absorber mass 10 sets.
  • the setting of this angle of rotation causes the eradication effect and is dependent inter alia on the set on the friction device 11 friction torque.
  • FIG 2 shows a relation to the clutch disc 1 of Figure 1 slightly modified clutch disc 1a with the disc part 4a with friction linings 27, the torsional vibration absorber 5a and the slip clutch 12a.
  • the torsional vibration damper 5a is formed of the spring cage 6a, the absorber mass 10a, the first energy storage 8a, and the friction device 11a.
  • the ramp device 21a and the energy storage 8a, 14a, 17a and the cover plate 13a received on the hub 3a and the friction disk 16a for forming the friction torque of the slip clutch 12a are formed corresponding to the clutch disk 1 of FIG.
  • the ramp part 23a is provided with axial projections 29 which are hooked into corresponding openings of the plate spring 15a.
  • the axial securing of the ramp part 23a with respect to the plate spring 15a takes place by means of at least slight pretensioning with respect to the ramp part 22a of the absorber mass 10a.
  • FIGS. 3a and 3b schematically show a section of the friction device 11 of FIG. 1 (reference numerals not referenced to FIG. 1) with the ramp device 21 formed by the ramp parts 22, 23.
  • the ramp part 22 is received axially fixedly on the absorber mass 10.
  • the ramp part 23 axially against the action of the second, on the disc part 4 supporting energy storage 14 is arranged axially displaced.
  • the ramp portions 22, 23 have circumferentially aligned ramps 24, and counter ramps 25, which in the representation of the approximate center position shown in Figure 3 with not mutually rotated disc part 4 and absorber mass 10 are approximately opposite, so that the second energy storage 14 this under the set bias tensioned. If disk part 4 and absorber mass 10 are rotated against one another, as shown in FIG.
  • ramp parts 22, 23 are increasingly spaced with increasing compression angle with further compression of second energy accumulator 14 along ramps 24 and counter ramps 25, so that the frictional torque is dependent thereon increased by the angle of rotation.
  • ramps 24 and counter ramps 25 also have, in the region of the central position, a plateau 30 extending over a slight angle of rotation range without an incline, so that a constant basic friction is ensured at small angles of rotation.
  • FIG. 4 a shows a basic sequence of individual diagrams of a torque amplitude over the frequency in a resonance region with an amplitude increasing from left to right of a torsional vibration damper according to the prior art.
  • FIG. 4b shows a basic sequence of individual diagrams of a torque amplitude over the frequency in a resonance range with amplitude increasing from left to right of the torsional vibration absorber 5 of FIG. 1 or 5a of FIG. 2.
  • the setting of the friction torque depends largely on the amplitude Moment fluctuation, a substantially equal proportion of erased surface portion 31a and uncoated surface portion 32a without further training additional torque amplitudes, which usually have a disturbing effect achieved.
  • FIG. 5 shows a principal characteristic curve 33 of the torsional vibration absorbers 5, 5a of FIGS. 1 and 2 with the moment M over the angle of rotation a.
  • the torque lines 34, 35 are loaded at positive and negative angle of rotation ⁇ with in each case the same magnitude friction moment equal pitch.
  • FIG. 6 shows a detailed view of the torsional vibration damper 5 of FIG. 1 accommodated on the hub 3 and secured axially by means of the cover plate 13.
  • the absorber mass 10 is centered on the spring cage 6 and rotatable against the action of the coil springs 9. outsourced.
  • the coil springs 9 are received in recesses 36 of the spring cage 6 and are acted upon at the end faces of the radial boundaries 37 of the recesses 36 in the circumferential direction. On the opposite side, the coil springs 9 are acted upon by radially engaging in the recesses 36 cam 20 of the absorber mass 10.
  • the absorber mass 10 also has recesses 38 into which the radially expanded cams 19 of the spring cage 6 engage and with the circumferentially provided stops 39 of the recesses 38 form the Vercardwinkelbegrenzung the absorber mass 10 relative to the spring cage 6.
  • the slip clutch 12 ( Figure 1) is activated at the latest.
  • the slip clutch 12 by setting the slip torque smaller than the friction torque of the friction device 11 ( Figure 1) slip at angles of rotation before reaching the stops 39 through the cam 19 and therefore a hard stop of the cam 19 can be avoided at the stops 39.

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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)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un embrayage à friction équipé d'un disque d'embrayage (1, 1a) pour transférer des couples au moyen d'une unité de friction (11, 11a). L'objectif de l'invention est de permettre de concevoir un amortissement des vibrations torsionnelles superposées au couple à transférer, indépendamment, au moins dans une large mesure, de l'amplitude de ces vibrations torsionnelles. À cet effet, l'unité de friction présente un couple de friction dépendant de l'angle de torsion relatif entre la masse d'amortissement (10, 10a) et la masse à amortir.
PCT/DE2010/001255 2009-11-17 2010-10-28 Embrayage à friction équipé d'un disque d'embrayage pour transférer des couples Ceased WO2011060752A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201080052034.5A CN102612613B (zh) 2009-11-17 2010-10-28 用于传递转矩的具有离合器从动盘的摩擦离合器
DE112010004468.6T DE112010004468B4 (de) 2009-11-17 2010-10-28 Reibungskupplung mit einer Kupplungsscheibe zur Übertragung von Drehmomenten

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102009053435.0 2009-11-17
DE102009053435 2009-11-17
DE102010033833 2010-08-09
DE102010033833.8 2010-08-09

Publications (1)

Publication Number Publication Date
WO2011060752A1 true WO2011060752A1 (fr) 2011-05-26

Family

ID=43759408

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2010/001255 Ceased WO2011060752A1 (fr) 2009-11-17 2010-10-28 Embrayage à friction équipé d'un disque d'embrayage pour transférer des couples

Country Status (3)

Country Link
CN (1) CN102612613B (fr)
DE (2) DE102010049929A1 (fr)
WO (1) WO2011060752A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2711586A2 (fr) 2012-09-24 2014-03-26 Aisin Seiki Kabushiki Kaisha Absorbeur de fluctuation de couple
FR3026451A1 (fr) * 2014-09-30 2016-04-01 Valeo Embrayages Disque de friction pour embrayage
WO2016066507A1 (fr) 2014-10-31 2016-05-06 Valeo Embrayages Dispositif d'amortissement des vibrations de type batteur inertiel
EP3073148A1 (fr) 2015-03-27 2016-09-28 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
EP3073146A1 (fr) 2015-03-27 2016-09-28 Valeo Embrayages Composant pour systeme de transmission, notamment disque d'embrayage
FR3036761A1 (fr) * 2015-05-26 2016-12-02 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
DE102016111077A1 (de) 2015-06-24 2016-12-29 Valeo Embrayages Zusätzliche Trägheitskomponente für einen Antriebsstrang eines Fahrzeugs
DE102016120193A1 (de) 2015-10-27 2017-04-27 Valeo Embrayages Dämpfungsvorrichtung
DE102017101550A1 (de) 2016-03-04 2017-09-07 Valeo Embrayages Dämpfungsvorrichtung
FR3102105A1 (fr) 2019-10-21 2021-04-23 Valeo Embrayages Chaîne de transmission pour véhicule hybride ou électrique équipée d’un batteur inertiel

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DE102011080447A1 (de) * 2011-08-04 2013-02-07 Zf Friedrichshafen Ag Massenelement für einen Rupftilger
CN103917801B (zh) * 2011-09-09 2015-12-09 舍弗勒技术股份两合公司 离心摆和具有该离心摆的离合器盘
DE102012214825B4 (de) 2011-09-16 2022-05-05 Schaeffler Technologies AG & Co. KG Kupplungsvorrichtung mit flexibler Schwingungsdämpfung
DE102012223751A1 (de) 2012-12-19 2014-06-26 Schaeffler Technologies Gmbh & Co. Kg Drehschwingungstilgereinrichtung
FR3000155B1 (fr) 2012-12-21 2015-09-25 Valeo Embrayages Amortisseur de torsion pour un dispositif de transmission de couple d'un vehicule automobile
DE102014223308A1 (de) 2013-11-27 2015-05-28 Schaeffler Technologies AG & Co. KG Kupplungsscheibe mit Tilgereinheit
DE102013226053B4 (de) 2013-12-16 2016-03-03 Volkswagen Aktiengesellschaft Verbindungselement eines Antriebsstranges umfassend ein Federelement und einen Rampenmechanismus
FR3024759B1 (fr) 2014-08-08 2020-01-03 Valeo Embrayages Amortisseur, notamment pour un embrayage d'automobile
DE102014219255B4 (de) 2014-09-24 2022-06-30 Schaeffler Technologies AG & Co. KG Drehschwingungstilger
FR3027642B1 (fr) * 2014-10-27 2020-02-21 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
FR3036757B1 (fr) * 2015-06-01 2017-06-02 Valeo Embrayages Disque d'embrayage
FR3043155B1 (fr) * 2015-10-30 2017-12-08 Valeo Embrayages Absorbeur de vibration, mecanisme d'amortissement et ensemble de propulsion associes
FR3047529A1 (fr) * 2016-02-04 2017-08-11 Valeo Embrayages Dispositif d'amortissement pendulaire
DE102016205594A1 (de) * 2016-04-05 2017-10-05 Zf Friedrichshafen Ag Schwingungsdämpfungsanordnung, insbesondere für einen Antriebsstrang eines Fahrzeugs
FR3051859B1 (fr) * 2016-05-24 2020-04-17 Valeo Embrayages Dispositif d'amortissement pendulaire
DE102016221550A1 (de) * 2016-11-03 2018-05-03 Zf Friedrichshafen Ag Torsionsdämpfer für ein Kraftfahrzeug
CN110621906B (zh) * 2017-05-17 2021-07-30 舍弗勒技术股份两合公司 具有离心力摆的无盖的双质量飞轮
FR3072434B1 (fr) * 2017-10-16 2019-09-27 Valeo Embrayages Dispositif de transmission de couple comportant un absorbeur dynamique de vibrations
CN112443586A (zh) * 2019-08-30 2021-03-05 舍弗勒技术股份两合公司 离合器从动盘及离合器
DE102020110889B4 (de) * 2020-04-22 2022-01-05 Schaeffler Technologies AG & Co. KG Torsionsschwingungsdämpfer mit koppelbarem Tilgersystem, sowie Antriebsstrang mit Torsionsschwingungsdämpfer
DE102022110201B4 (de) 2022-04-27 2024-02-08 Karlsruher Institut für Technologie, Körperschaft des öffentlichen Rechts Schwingungsdämpfer

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Publication number Priority date Publication date Assignee Title
EP2711586A2 (fr) 2012-09-24 2014-03-26 Aisin Seiki Kabushiki Kaisha Absorbeur de fluctuation de couple
US8998728B2 (en) 2012-09-24 2015-04-07 Aisin Seiki Kabushiki Kaisha Torque fluctuation absorber
EP2711586A3 (fr) * 2012-09-24 2015-08-26 Aisin Seiki Kabushiki Kaisha Absorbeur de fluctuation de couple
FR3026451A1 (fr) * 2014-09-30 2016-04-01 Valeo Embrayages Disque de friction pour embrayage
WO2016050569A1 (fr) * 2014-09-30 2016-04-07 Valeo Embrayages Disque de friction pour embrayage
WO2016066507A1 (fr) 2014-10-31 2016-05-06 Valeo Embrayages Dispositif d'amortissement des vibrations de type batteur inertiel
EP3073148A1 (fr) 2015-03-27 2016-09-28 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
EP3073146A1 (fr) 2015-03-27 2016-09-28 Valeo Embrayages Composant pour systeme de transmission, notamment disque d'embrayage
FR3034156A1 (fr) * 2015-03-27 2016-09-30 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
FR3036761A1 (fr) * 2015-05-26 2016-12-02 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
DE102016111077A1 (de) 2015-06-24 2016-12-29 Valeo Embrayages Zusätzliche Trägheitskomponente für einen Antriebsstrang eines Fahrzeugs
DE102016120193A1 (de) 2015-10-27 2017-04-27 Valeo Embrayages Dämpfungsvorrichtung
DE102017101550A1 (de) 2016-03-04 2017-09-07 Valeo Embrayages Dämpfungsvorrichtung
FR3102105A1 (fr) 2019-10-21 2021-04-23 Valeo Embrayages Chaîne de transmission pour véhicule hybride ou électrique équipée d’un batteur inertiel
WO2021078755A1 (fr) 2019-10-21 2021-04-29 Valeo Embrayages Chaîne de transmission pour véhicule hybride ou électrique équipée d'un batteur inertiel
DE112020005091T5 (de) 2019-10-21 2022-08-04 Valeo Embrayages Antriebsstrang für hybrid- oder elektrofahrzeug mit einer inertialen schwingungsdämpfungsmasse

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DE102010049929A1 (de) 2011-05-19

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