WO2018219397A1 - Amortisseur de vibrations de torsion - Google Patents

Amortisseur de vibrations de torsion Download PDF

Info

Publication number
WO2018219397A1
WO2018219397A1 PCT/DE2018/100461 DE2018100461W WO2018219397A1 WO 2018219397 A1 WO2018219397 A1 WO 2018219397A1 DE 2018100461 W DE2018100461 W DE 2018100461W WO 2018219397 A1 WO2018219397 A1 WO 2018219397A1
Authority
WO
WIPO (PCT)
Prior art keywords
flange
energy storage
storage element
additional
torsional vibration
Prior art date
Application number
PCT/DE2018/100461
Other languages
German (de)
English (en)
Inventor
Benjamin Stober
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112018002746.5T priority Critical patent/DE112018002746A5/de
Priority to CN201880034699.XA priority patent/CN110662910B/zh
Publication of WO2018219397A1 publication Critical patent/WO2018219397A1/fr

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
    • F16F15/12—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
    • F16F15/131—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 the rotating system comprising two or more gyratory masses
    • F16F15/133—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 the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/13469—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/13476—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/13484—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs

Definitions

  • the invention relates to a torsional vibration damper, in particular two-mass flywheel pulley decoupler or disk damper, with the aid of which torsional vibrations can be damped in a drive train of a motor vehicle.
  • a torsional vibration damper in particular two-mass flywheel pulley decoupler or disk damper, with the aid of which torsional vibrations can be damped in a drive train of a motor vehicle.
  • a torsional vibration damper for damping of Torsional vibrations in a drive train of a motor vehicle provided with a peripheral receiving channel forming a primary mass and a limited energy storage element, in particular bow spring, limited relative to the primary mass rotatable secondary mass, wherein the secondary mass has a protruding into the receiving channel output flange for tangential striking the energy storage element wherein the output flange has a tangentially applied to the energy storage element transmission flange and a torque-coupled via an additional damper with the transmission flange connection flange, in particular between the transmission flange and the connecting flange, a toothing is formed and the additional damper is positioned in the toothing.
  • the addition of the energy storage element provided additional damper it is possible to provide a desired clearance angle in the additional damper, so that the additional damper from another angle between the primary mass and the secondary mass is effective than is provided in the energy storage element. As a result, it is easy to achieve a damping behavior that changes over the angle of rotation.
  • it is possible with a slight relative rotation of the primary mass to the secondary mass when a rotation angle range is swept with only small Drehwin- no, determined only by the energy storage element to provide spring characteristic, while above a rotation angle at which provided in additional damper clearance angle exceeded and the Damping function of the pre-damper is activated, automatically provided by the energy storage element and the additional damper spring characteristic is provided.
  • a spring characteristic with a sectionally different overall spring constant can be set.
  • a comparatively soft damping can be achieved over a sufficiently large rotation angle range, which is perceived as particularly comfortable.
  • a clearance angle in the region of the energy storage element can be reduced or even completely avoided, so that more space remains in the circumferential direction for the energy storage element. This allows a larger extent of the energy storage element in the circumferential direction and so with a longer distance around which the energy storage element can be compressed.
  • a softer spring characteristic for the energy storage element can be realized.
  • the additional damper spaced to the energy storage element of the additional damper is not arranged coaxially to the energy storage element and therefore easily operated independently of the energy storage element. This makes it easier to operate the additional damper in a different rotation angle range from the energy storage element and to realize a total spring characteristic curve with regions of different spring constants.
  • the energy storage element with the softer spring characteristic is already maximally compressed and goes to block, so that in a further increase in the angle of rotation, only the additional damper or only the energy storage element with the stiffer spring characteristic is still effective , This makes it possible to set a particularly large blocking moment, in which the maximum possible angle of rotation of the primary mass to the secondary mass is reached.
  • the output flange of the secondary exhaust mass Due to the at least two-part design of the output flange of the secondary exhaust mass, it is easily possible to provide a clearance angle for the additional damper via the torque-transmitting coupling of the transmission flange to the connecting flange of the multi-part output flange.
  • a relative rotation of the transmission flange to the connection flange can take place within the output flange of the secondary mass substantially uninfluenced by a compression of the energy storage element, so that the relative rotation of the transmission flange to the connection flange is not restricted by the energy storage element.
  • the additional damper can be connected in series to the energy storage element and for this purpose be integrated in the multi-part output flange.
  • the additional damper is coupled via the transmission flange and the energy storage element only indirectly to the primary mass.
  • the auxiliary damper can be easily positioned in the circumferential direction between the teeth of the toothing, wherein a clearance angle for the additional damper over a distance of the teeth of the transmission flange in the circumferential direction to the Teeth of the connection flange can be provided.
  • a separate only of a component circumferentially ausgestaltetes window for receiving the additional damper is not required. Instead, in the circumferential direction, subsequent teeth can form a tooth space which is open towards a radial direction for receiving the additional damper, wherein the side opened in the radial direction can be delimited by the tooth root of the component of the output flange opposite the toothing.
  • the primary mass and the secondary mass arranged rotatably on the primary mass limited by the energy storage element designed in particular as a bow spring can form a spring-mass system which can dampen rotational irregularities in the rotational speed and in the torque of the drive power generated by a motor vehicle engine in a certain frequency range.
  • the mass moment of inertia of the primary mass and / or the secondary mass and the spring characteristic of the energy storage element may be selected such that vibrations in the frequency range of the dominant engine orders of the motor vehicle engine can be damped.
  • the mass moment of inertia of the primary mass and / or the secondary mass can be influenced in particular by an attached additional mass.
  • the primary mass may have a disk, with which a lid may be connected, whereby the substantially annular receiving space for the energy storage element may be limited.
  • the primary mass can strike tangentially on the energy storage element via indentations projecting into the receiving space.
  • the output flange of the secondary mass can protrude, which can strike tangentially at the opposite end of the energy storage element.
  • the turntable vibration damper is part of a dual-mass flywheel, the primary mass can have a couplable with a drive shaft of an automotive engine flywheel.
  • the primary mass can form a pulley on the radially outer surface of the traction means, in particular a V-belt, can engage in torque transmission.
  • the additional damper is designed to block the primary mass at an increasing relative rotation of the secondary mass before the energy storage element is blocked. If the secondary mass is rotated out of a neutral zero position relative to the primary mass in a first circumferential direction or a second circumferential direction opposite to the first circumferential direction, no attenuation can initially be provided, for example as a result of a free angle provided for the energy store and the additional damper, so that particularly high frequencies can be provided low amplitudes in the type of a low-pass filter can be filtered out. But it is also possible that initially only the energy storage element or both the energy storage element and the additional damper are effective with the start of a relative rotation. In particular, the energy storage element has a softer spring characteristic than the additional damper.
  • a soft damping stage at which after the blocking of the additional damper a hard damping stage connects.
  • the soft damping level allows for comfortable cushioning, while the hard cushioning level can dampen a hard impact when reaching the maximum possible rotation angle.
  • the energy storage element can provide such a large clearance angle that at the beginning of the relative rotation only the additional damper is effective until blocking before the energy storage element is effective or vice versa.
  • a spring element of the additional damper designed in particular as a bow spring to cover a longer extent and / or a larger angle range in the circumferential direction than the energy storage element or vice versa.
  • the primary mass and the transmission flange are tangent to the energy storage element, in particular the energy storage element is designed to permanently tangentially abut the primary mass and the transmission flange during operation, in particular the energy storage element between the primary mass and the transmission flange is biased.
  • a clearance angle provided in the radius region of the energy storage element can thereby be avoided, so that more installation space for the energy storage element can be provided in the circumferential direction.
  • the damping effect of the additional damper is switched off via the clearance angle, so that only the damping effect of the energy storage element is effective. Only at the end of the possible range of rotation angle if the additional damper seen free angle is exceeded, the damping effect of the additional damper is effective. In a rotation angle range above the clearance angle up to the maximum possible rotation angle, the spring effects of the energy storage element and the additional damper can overlap.
  • the energy storage element can in this case be designed without clearance angle, so that the damping effect of the energy storage element can be effective from the beginning.
  • the additional damper is provided within the receiving channel.
  • the additional damper can thereby be positioned on a comparatively large radius area, which allows a correspondingly large clearance angle for the additional damper.
  • the additional damper has an additional energy storage element configured in particular as a compression coil spring or bow spring, wherein the auxiliary energy storage element is received in the tangential direction and / or in the circumferential direction at both axial ends biased on the transmission flange and the flange rotatable relative to the transmission flange tangentially via a clearance angle the additional energy storage element can be abutted and / or the additional energy storage element in the tangential direction and / or in the circumferential direction at both axial ends biased is received on the flange and the rotatable relative to the flange connection flange over a clearance angle tangent to the additional energy storage element can be stopped.
  • the additional energy storage element configured in particular as a compression coil spring or bow spring
  • the additional energy storage element is thereby supported not on the one hand on the transmission flange and on the other hand on the connecting flange, but only on one of these components.
  • the additional energy storage element can extend over an entire tooth space of either the transmission flange or the connection flange and support it in a supported manner. If such a strong relative rotation of the transfer flange to the connecting flange takes place that the intended clearance angle is swept over, a part of the respective other component can be moved past the component supporting the additional energy storage element and hit tangentially on the additional energy storage element in order to increase the additional energy. memory element to compress.
  • the additional energy storage element can lift off at the abutting side and be supported on the relatively moving component.
  • the interdental space of the teeth of the connection flange or transmission flange which does not receive the additional energy storage element is in particular so large that two teeth of the transmission flange or connecting flange accommodating the additional energy storage element can be accommodated.
  • the additional energy storage element accommodated in the smaller interdental space can be positioned completely together with the teeth supporting the additional energy storage element in the larger interdental space.
  • one tooth of the larger interdental space can strike tangentially on one side of the additional energy storage element or the other tooth of the larger interdental space on the other side of the additional energy storage element.
  • the teeth of the transfer flange are offset from the teeth of the connecting flange in the axial direction.
  • the teeth of the transfer flange and the teeth of the connecting flange just do not overlap in the circumferential direction. A direct striking the teeth together is avoided. Instead, it is ensured that a torque transmission can only take place via the intermediate additional damper, which can strike it tangentially at different points offset in the axial direction on the teeth of the transmission flange and on the teeth of the connecting flange.
  • a friction device for providing a damping against a resonance-induced rocking of torsional vibrations.
  • the spring-mass system of the torsional vibration damper can be sufficiently damped in order to avoid excessive deflections in the resonance range.
  • the relative movements of the transmission flange can be used for connection flange to produce friction-related relative movements.
  • the friction device can be attached to the transmission flange
  • the first friction partner and a second friction partner fastened to the connection flange, which, for example, are pressed against each other in a frictional manner with the aid of a spring.
  • the friction partners can be represented for example by axial friction rings.
  • the connecting flange has two axially spaced side windows, wherein the transmission flange protrudes in the toothing between the side windows, or the transmission flange has two axially spaced side windows, wherein the connecting flange protrudes in the toothing between the side windows.
  • a tooth root of the transmission flange in the toothing and / or a tooth base of the connecting flange in the toothing to the radially outer guide of the additional damper in the axial direction.
  • the guidance of the additional damper, in particular of the additional energy storage element can thereby be improved, for example in order to avoid buckling of the additional energy storage element under load.
  • the protruding areas may in particular cling to the outer contour of the additional damper or the additional energy storage element.
  • the invention further relates to a pulley arrangement for driving auxiliary units of a motor vehicle with the aid of a traction means, with a pulley for driving the traction means, a hub which can be coupled to a drive shaft of an automobile engine for introducing a torque and a torsional vibration damper, which may be as described above and further educated, wherein the pulley part of the primary mass and the hub are part of the secondary mass of the torsional vibration damper.
  • the additional damper which is provided in particular in a tooth space between the toothing of the multi-part output flange, a torsional vibration damper with a soft spring characteristic is possible with a small installation space.
  • Fig. 1 is a schematic sectional side view of a torsional vibration damper
  • FIG. 2 is a schematic sectional plan view of the torsional vibration damper of FIG. 1.
  • the torsional vibration damper 10 shown in FIGS. 1 and 2 using the example of a pulley decoupler in a belt pulley arrangement for driving auxiliary units of a motor vehicle with the aid of a traction means has a primary mass 12 designed as a pulley, which has an annular receiving channel 14 for a bow spring Energy storage element 16 limited.
  • An outlet flange 18 of a secondary mass 20 projects into the receiving channel 14 from radially inward direction.
  • the energy storage element 16 is clamped at its tangential ends between the primary mass 12 and the output flange 18 without play in the circumferential direction, that is, without clearance angle, with a bias voltage.
  • the secondary mass 20 has an example, two-piece hub 22, with which the output flange 18 is attached.
  • a rubber seal 24 is attached.
  • a fastening means 26 designed as a screw for fastening the rubber sealer 24 also fastens the output flange 18 extending centrally to the energy storage element 16 with the hub 22 and holds the multipart Hub 22 together.
  • the fastening means 26 can be designed, for example, as a screw connection, pinning and / or interference fit. Due to the configuration of the fastening means 26 as a dowel pin, the rubber sealer 24 can be easily positioned on the hub 22.
  • the output flange 18 of the secondary mass 20 has a radially outer transmission flange 28 and a radially inner connecting flange 30, between which a toothing 32 is formed.
  • an additional damper 34 is provided in the toothing 32, which has a configured as a compression coil spring additional energy storage element 36.
  • the auxiliary energy storage element 36 is inserted in a tooth space of two first teeth 38 of the transfer flange 28 with bias.
  • a tooth space between two second teeth 40 of the connection flange 30 is so large that the additional damper 34 composed of the second first teeth 40 and the additional energy storage element 36 can be accommodated.
  • the connecting flange 30 is composed of two side plates 42, which are arranged offset in the axial direction to the transmission flange 28, so that the second teeth 40 can be moved past the first teeth 38 in a relative rotation after overcoming a clearance angle tangentially to the auxiliary energy storage element 36 of the additional damper 34 to strike.
  • the additional energy storage element 36 can be compressed between the transfer flange 28 and the connecting flange 30, and a torque can be transmitted between the transfer flange 28 and the connecting flange 30.
  • wings 44 can protrude which guide the auxiliary energy storage element 36 and / or can support it against kinking. LIST OF REFERENCES

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Pulleys (AREA)

Abstract

L'invention concerne un amortisseur de vibrations de torsion (10), en particulier un double volant amortisseur, un découpleur de poulie ou un amortisseur de poulie, destiné à amortir des vibrations de torsion dans une chaîne cinématique d'un véhicule automobile, comprenant une masse primaire (12) formant un canal de réception (14) périphérique et une masse secondaire (20) pouvant tourner de manière limitée par rapport à la masse primaire (12) par l'intermédiaire d'un élément d'accumulation d'énergie (16), en particulier d'un ressort en arc, la masse secondaire (20) présentant un rebord de sortie (18) faisant saillie dans le canal de réception (14) et destiné à venir en butée tangentielle sur l'élément accumulateur d'énergie (16), le rebord de sortie (18) présentant un rebord de transfert (28) s'appuyant de manière tangentielle sur l'élément accumulateur d'énergie (16) et un rebord de raccordement (30) accouplé au rebord de transfert (28) de manière à pouvoir transmettre un couple de rotation par l'intermédiaire d'un amortisseur supplémentaire (34), une denture (32) étant formée notamment entre le rebord de transfert (28) et le rebord de raccordement (30) et l'amortisseur supplémentaire (34) étant positionné dans la denture (32). Grâce à l'amortisseur supplémentaire (34) qui n'agit qu'à la fin de la plage d'angle de rotation, il est possible d'obtenir un couple de blocage élevé avec un élément accumulateur d'énergie (16) le plus long et le plus souple possible, en présence d'un angle de rotation le plus élevé possible, de façon à permettre l'obtention d'un amortisseur de vibrations de torsion (10) présentant une courbe caractéristique de ressort souple.
PCT/DE2018/100461 2017-06-02 2018-05-15 Amortisseur de vibrations de torsion WO2018219397A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112018002746.5T DE112018002746A5 (de) 2017-06-02 2018-05-15 Drehschwingungsdämpfer
CN201880034699.XA CN110662910B (zh) 2017-06-02 2018-05-15 扭振减振器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017112184.6 2017-06-02
DE102017112184 2017-06-02

Publications (1)

Publication Number Publication Date
WO2018219397A1 true WO2018219397A1 (fr) 2018-12-06

Family

ID=62385962

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2018/100461 WO2018219397A1 (fr) 2017-06-02 2018-05-15 Amortisseur de vibrations de torsion

Country Status (3)

Country Link
CN (1) CN110662910B (fr)
DE (2) DE112018002746A5 (fr)
WO (1) WO2018219397A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110500381A (zh) * 2019-07-18 2019-11-26 佛山科学技术学院 一种复合式曲轴扭转减振器

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2728642A1 (fr) * 1994-11-08 1996-06-28 Valeo Amortisseur de torsion, notamment friction d'embrayage pour vehicule automobile
DE102015221022A1 (de) 2014-11-05 2016-05-12 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer mit abgedichtetem Innenraum
US20160265643A1 (en) * 2013-11-10 2016-09-15 Litens Automotive Partnership Isolator with dual springs

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4128868A1 (de) * 1991-08-30 1993-03-04 Fichtel & Sachs Ag Zweimassenschwungrad mit gleitschuh
DE4417654C2 (de) * 1994-05-20 2001-12-06 Mannesmann Sachs Ag Torsionsschwingungsdämpfeinrichtung mit einem Abstandsring
DE102008015476A1 (de) * 2008-03-25 2009-10-01 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Torsionsschwingungsdämpfer
DE102009015576A1 (de) * 2008-04-17 2009-10-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehschwingungsdämpfer
CN103161836A (zh) * 2011-12-12 2013-06-19 湖北三环离合器有限公司 离合器从动盘总成大转角多级减振器
DE102013200295A1 (de) * 2012-01-27 2013-08-01 Schaeffler Technologies AG & Co. KG Drehzahladaptiver Drehschwingungstilger
DE102013213747A1 (de) * 2012-07-18 2014-01-23 Schaeffler Technologies AG & Co. KG Schwingungsdämpfer
CN203880009U (zh) * 2014-01-08 2014-10-15 郑州宇通客车股份有限公司 一种扭转减振器
JP6252458B2 (ja) * 2014-04-30 2017-12-27 アイシン・エィ・ダブリュ株式会社 ダンパ装置
DE102015222660A1 (de) * 2015-11-17 2017-05-18 Zf Friedrichshafen Ag Federpaket
CN205677999U (zh) * 2016-05-23 2016-11-09 上海萨克斯动力总成部件系统有限公司 集成三个减振器的汽车离合器从动盘

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2728642A1 (fr) * 1994-11-08 1996-06-28 Valeo Amortisseur de torsion, notamment friction d'embrayage pour vehicule automobile
US20160265643A1 (en) * 2013-11-10 2016-09-15 Litens Automotive Partnership Isolator with dual springs
DE102015221022A1 (de) 2014-11-05 2016-05-12 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer mit abgedichtetem Innenraum

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110500381A (zh) * 2019-07-18 2019-11-26 佛山科学技术学院 一种复合式曲轴扭转减振器

Also Published As

Publication number Publication date
DE112018002746A5 (de) 2020-02-20
CN110662910A (zh) 2020-01-07
DE102018111615A1 (de) 2018-12-06
CN110662910B (zh) 2021-11-16

Similar Documents

Publication Publication Date Title
DE10358901C5 (de) Torsionsschwingungsdämpfer
DE19522225B4 (de) Torsionsschwingungsdämpfer
DE102008057648A1 (de) Kraftübertragungsvorrichtung, insbesondere zur Leistungsübertragung zwischen einer Antriebsmaschine und einem Abtrieb
DE102011016577A1 (de) Riemenscheibendämpfer
DE102007026195A1 (de) Torsionsschwingungsdämpfer oder Dekoppler mit gewickelten Drahtfedern in einer Antriebsscheibe
DE102018113585B4 (de) Drehschwingungsdämpfer
DE3411239A1 (de) Einrichtung zum kompensieren von drehstoessen
DE102012214361A1 (de) Torsionsschwingungsdämpfer, Zweimassenschwungrad und leistungsverzweigendes Torsionsschwingungsdämpfersystem
DE112011101594B4 (de) Dämpfungsmechanismus
DE102019118504A1 (de) Drehschwingungsdämpfer
EP2012044A1 (fr) Amortisseur mécanique de vibrations de torsion
DE102010053542A1 (de) Drehschwingungsdämpfer
DE102012214362A1 (de) Torsionsschwingungsdämpfer
DE102018124860A1 (de) Drehschwingungsdämpfer
DE102012214022A1 (de) Drehschwingungsdämpfer
EP2104789A2 (fr) Accouplement de l'arbre élastique à la torsion comprenant un élément élastomère pouvant être ponté
DE102016218670A1 (de) Koppelanordnung zum Ankoppeln eines Drehschwingungsdämpfers
DE102018102373A1 (de) Drehschwingungsdämpfer und Verfahren zum Wuchten eines Drehschwingungsdämpfers
WO2018219397A1 (fr) Amortisseur de vibrations de torsion
DE19913649A1 (de) Dämpfermechanismus
WO2018219396A1 (fr) Amortisseur de vibrations de torsion
DE10210620B4 (de) Dämpfungsvorrichtung
DE102018112326A1 (de) Drehschwingungsdämpfer
DE102017123579A1 (de) Flanschanordnung für ein Zweimassenschwungrad
WO2017194053A1 (fr) Disque de friction pour amortisseur de disque d'embrayage

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18727660

Country of ref document: EP

Kind code of ref document: A1

REG Reference to national code

Ref country code: DE

Ref legal event code: R225

Ref document number: 112018002746

Country of ref document: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18727660

Country of ref document: EP

Kind code of ref document: A1