WO2023030570A1 - Amortisseur de vibrations de torsion - Google Patents

Amortisseur de vibrations de torsion Download PDF

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Publication number
WO2023030570A1
WO2023030570A1 PCT/DE2022/100564 DE2022100564W WO2023030570A1 WO 2023030570 A1 WO2023030570 A1 WO 2023030570A1 DE 2022100564 W DE2022100564 W DE 2022100564W WO 2023030570 A1 WO2023030570 A1 WO 2023030570A1
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WO
WIPO (PCT)
Prior art keywords
friction
friction ring
torsional vibration
vibration damper
input side
Prior art date
Application number
PCT/DE2022/100564
Other languages
German (de)
English (en)
Inventor
László Sarkadi
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
Publication of WO2023030570A1 publication Critical patent/WO2023030570A1/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
    • F16F15/10—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
    • 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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs

Definitions

  • the invention relates to a torsional vibration damper which is used in particular to reduce torsional vibrations in a drive train.
  • the torsional vibration damper can be used as a torque transmission device or as part of a torque transmission device, in particular in a motor vehicle, preferably in the drive train of a motor vehicle, particularly preferably in a hybrid drive train in which z. B. an electric machine and an internal combustion engine can be used to drive the motor vehicle.
  • Torsional vibration dampers are known, for example, from the field of motor vehicles, in order to make rotational irregularities more uniform and thus to reduce torque shocks and/or noise emissions. Torsional vibration dampers can e.g. B. be combined with friction clutches to compact, switchable torque transmission devices.
  • a torsional vibration damper comprises at least one input side, an output side that can be rotated in a circumferential direction relative to the input side, and at least one intermediate element, which is supported on at least one energy storage element and is supported on at least one rolling body so that it can swing on at least one of the input side and output side and reduces rotational irregularities during operation.
  • a torsional vibration damper includes a friction device that can set different hysteresis depending on a rotation of the input side relative to the output side.
  • Hysteresis is the difference between the damping characteristics of the torsional vibration damper when the torsional vibration damper is loaded and unloaded with a torque.
  • the hysteresis thus designates the energy dissipation due to the damping effected by the friction device.
  • the degree of torsion between the input side and the output side can be changed in particular between different damping characteristics and thus different hysteresis.
  • a particularly efficient torsional vibration damper is referred to, for example, as a oscillating rocker damper, which as an intermediate element comprises a plurality of rocker elements connecting the input side with the output side, which are prestressed against one another via spring devices, the input side, output side and rocker elements each having movement paths in which rolling elements are movably arranged, the on the one hand connect the input side and the rocker elements and on the other hand the rocker elements and the output side.
  • a rocker damper is known from DE 10 2019 121 204 A1 and DE 10 2019 121 205 A1.
  • Another torsional vibration damper designed as a pendulum rocker damper is e.g. B. from the subsequently published DE 10 2021 112 758.0 known.
  • the object of the present invention is to at least partially alleviate the problems described at the outset.
  • a torsional vibration damper is to be proposed which has a longer service life.
  • a torsional vibration damper with an axis of rotation is proposed.
  • This is in particular a torque transmission device or a component of a torque transmission device, e.g. B. combined with a friction clutch.
  • the torsional vibration damper comprises at least one input side, an output side that can be rotated in a circumferential direction relative to the input side, and at least one intermediate element, which is supported on at least one energy storage element and is supported on at least one rolling body so that it can swing on at least one of the input side and output side and reduces rotational irregularities during operation, and additionally one Friction device which has at least a first hysteresis and a second hysteresis as a function of a rotation of the input side relative to the output side.
  • the friction device has at least three friction rings, which are each arranged between the input side and the output side and form friction points.
  • the friction rings are ring-shaped, in particular, arranged coaxially to one another and to the axis of rotation, and extend along the circumferential direction around the axis of rotation.
  • the friction device has at least one first cup spring, which has a first contact point, a second contact point and a third contact point arranged one after the other along a radial direction from the inside to the outside and spaced apart from one another.
  • the first plate spring constantly contacts a first friction ring at the innermost first contact point, a second friction ring at the middle second contact point and a third friction ring at the outermost third contact point.
  • the first cup spring contacts the first friction ring and at least the third friction ring, and during the second hysteresis, the first friction ring and additionally only the second friction ring.
  • the contact points are in particular on different radii to the axis of rotation.
  • the second contact point accordingly on an intermediate second radius.
  • the contact points extend, in particular, in a ring shape, in which case they can be present along the circumferential direction, preferably continuously, but possibly also with interruptions.
  • the different hystereses are described by the ratio of the radii of the contact points.
  • the first hysteresis is therefore: first radius of the first contact point / third radius of the third contact point.
  • the second hysteresis is accordingly: first radius of the first contact point / second radius of the second contact point.
  • a ratio between the first, smaller, hysteresis and the second, larger, hysteresis is in particular more than two, preferably approximately three.
  • the first friction ring and the third friction ring consist in particular of a plastic material.
  • the second friction ring consists in particular of a metallic material, in particular of steel.
  • the first friction ring is non-rotatably connected to one of the input side and the output side.
  • the first friction ring is connected to the input side or the output side essentially without play in relation to the circumferential direction.
  • This connection can B. be realized via a pin connected to the corresponding side, which extends through a larger opening of the other side towards the first friction ring.
  • the first friction ring forms a first friction point with the other of the input side and the output side.
  • the first friction ring is also twisted with the input side or output side and rubs with the first friction point on the other of the output side and the input side.
  • the first friction point is arranged in particular at a very small first distance from the axis of rotation.
  • the friction points lie in particular on different radii from one another or are arranged at different distances from the axis of rotation.
  • the first friction point lies at a smallest first distance and the third friction point at a greatest third distance.
  • the second friction point correspondingly at a second distance therebetween.
  • the friction points extend, in particular, in a ring shape, and are preferably present continuously along the circumferential direction.
  • the first friction ring has at least one driver which extends along the axis of rotation and via which the first plate spring is connected to the first friction ring in a rotationally fixed manner.
  • the first plate spring is arranged directly adjacent to the first friction ring, in particular along the axis of rotation.
  • the first disk spring is arranged along the axis of rotation between the first friction ring and the other two friction rings, ie the second friction ring and the third friction ring.
  • the second friction ring and the third friction ring are arranged adjacent to one another along the radial direction and overlapping one another along the axis of rotation.
  • the first friction ring has at least one driver which extends along the axis of rotation and via which the second friction ring is connected in a rotationally fixed manner to the first friction ring.
  • the third friction ring has at least one second driver which extends along the axis of rotation and via which the third friction ring is connected in a rotationally fixed manner to the first cup spring.
  • the friction device has a pressure plate which is non-rotatably connected to the other of the input side and the output side and which forms a second friction point with the second friction ring and a third friction point with the third friction ring.
  • the pressure plate and the third friction ring each have ramps which together form a ramp device by which the first hysteresis or the second hysteresis is set depending on the rotation of the input side relative to the output side.
  • the first disc spring presses either the second friction ring or the third friction ring against the pressure plate.
  • the pressure plate with the other of the input side and output side is directly z. B. connected via screws or rivets.
  • the at least one connection between the pressure plate and the other of the input side and the output side is arranged outside of the friction rings in the radial direction.
  • the friction rings and the disk spring are in particular connected to one another, preferably without play in relation to the circumferential direction.
  • the friction rings and the plate spring z. B. connected to the input side (or to the output side).
  • the pressure plate is then connected to the output side (or to the input side).
  • the friction device additionally has a second cup spring, which has a fourth contact point and a fifth contact point arranged one after the other along the radial direction from the inside to the outside and spaced apart from one another, the fourth contact point and the fifth contact point replacing the second contact point.
  • the second cup spring constantly contacts the first cup spring at the inner fourth contact point and constantly contacts the second friction ring at the outer fifth contact point. As a result of the arrangement of the second plate spring, the first plate spring does not now contact the second friction ring.
  • the second plate spring is arranged in particular along the axis of rotation between the first plate spring and the second friction ring.
  • the second disc spring is arranged in particular inside the third friction ring with respect to the radial direction.
  • the ramp device can be relieved via the second cup spring.
  • the second disc spring exerts a force on the second friction ring at each hysteresis, i. H. the second friction point is also acted upon in the first hysteresis, in addition to the first friction point and the third friction point.
  • the first friction ring has at least one driver which extends along the axis of rotation and via which the second disk spring is connected to the first friction ring in a rotationally fixed manner.
  • the torsional vibration damper is an oscillating rocker damper which, as an intermediate element, comprises a plurality of rocker elements connecting the input side with the output side, which are preloaded against one another by spring devices, the input side, output side and rocker elements each having movement paths in which rolling elements are movably arranged, on the one hand the input side and the rocker elements and on the other hand connect the rocker elements and the output side with each other.
  • the torsional vibration damper can be used or used as a torque transmission device or as a component of a torque transmission device, in particular in a motor vehicle, preferably in the drive train of a motor vehicle.
  • indefinite articles (“a”, “an”, “an” and “an”), particularly in the claims and the description reflecting them, is to be understood as such and not as a numeral.
  • indefinite articles (“a”, “an”, “an” and “an”), particularly in the claims and the description reflecting them, is to be understood as such and not as a numeral.
  • Correspondingly introduced terms or components are to be understood in such a way that they are present at least once and in particular can also be present several times.
  • first”, “second”, ... ) primarily (only) serve to distinguish between several similar objects, sizes or processes, i.e. in particular no dependency and/or sequence of these objects, sizes or make processes mandatory for each other. Should a dependency and/or order be necessary, this is explicitly stated here or it is obvious to the person skilled in the art when studying the specifically described embodiment. If a component can occur several times (“at least one”), the description of one of these components can apply equally to all or part of the majority of these components, but this is not mandatory.
  • Fig. 1 a known torsional vibration damper in a perspective
  • Fig. 2 a torsional vibration damper in a perspective view in the
  • FIG. 3 shows a detail of the torsional vibration damper according to FIG. 2 in a perspective view in section
  • FIG. 4 shows the detail according to FIG. 3 in a side view in section
  • FIG. 5 shows part of the torsional vibration damper according to FIG. 2 in a perspective view in section
  • FIG. 6 shows the torsional vibration damper according to FIG. 2 in an exploded illustration in a first perspective view
  • FIG. 7 the torsional vibration damper according to FIG. 2 in an exploded representation in a second perspective view.
  • Fig. 1 shows a known torsional vibration damper 1 in a perspective view in section.
  • Torsional vibration damper 1 with axis of rotation 2 comprises an input side 3, an output side 5 that can be rotated in a circumferential direction 4 relative to input side 3, and at least one intermediate element 6, which is supported on at least one energy storage element 7 (compare FIGS. 6 and 7) and can oscillate on at least one rolling element 8 is mounted on at least one of the input side 3 and the output side 5 and reduces rotational irregularities during operation.
  • the torsional vibration damper 1 includes a friction device 9, which depends on a rotation of the input side 3 relative to the output side te can set 5 different hysteresis. Depending on the extent of the torsion between the input side 3 and the output side 5, you can switch between different damping characteristics and thus different hysteresis.
  • the friction device 9 comprises a first friction ring 10, a first plate spring 16 and a second friction ring 11.
  • the first plate spring 16 is arranged along the axis of rotation 2 between the friction rings 10, 11.
  • the first friction ring 10 is connected to the output side 5 without play in the circumferential direction 4 and forms the first friction point 13 with the input side 3 .
  • the second friction ring 11 forms the second friction point 14 with the pressure plate 23, which is connected to the input side 3 without play.
  • the second friction ring 11 and the pressure plate 23 each have ramps 24 which together form a ramp device 25 by which the first hysteresis or the second hysteresis is set depending on the rotation of the input side 3 relative to the output side 5 .
  • the second friction ring 11 must be able to tilt and is therefore made of plastic, so that the coefficient of friction of the second friction point 14 between the second friction ring 11 and the pressure plate 23 made of a steel material is low.
  • a large contact pressure is therefore required, which generates a high surface pressure between the second friction ring 11 and the pressure plate 23 and thus high wear.
  • the pressure plate 23 must also be sufficiently stiff, resulting in increased manufacturing costs. With the larger hysteresis, the force of the first disk spring is very high, but the characteristic curve is very short. The ramp device 25 is therefore heavily loaded.
  • FIG. 2 shows a torsional vibration damper 1 in a perspective view in section.
  • FIG. 3 shows a detail of the torsional vibration damper 1 according to FIG. 2 in a perspective view in section.
  • FIG. 4 shows the section according to FIG. 3 in a side view in section.
  • FIG. 5 shows part of the torsional vibration damper 1 according to FIG. 2 (here without pressure plate 23) in a perspective view in section.
  • FIG. 6 shows the torsional vibration damper 1 according to FIG. 2 in an exploded view in a first perspective view.
  • FIG. 7 shows the torsional vibration damper 1 according to FIG. 2 in an exploded view in a second perspective view. 2 to 7 are described together below. Reference is made to the statements relating to FIG.
  • Torsional vibration damper 1 with axis of rotation 2 comprises an input side 3, an output side 5 that can be rotated relative to input side 3 in a circumferential direction 4, and at least one intermediate element 6, which is supported on at least one energy storage element 7 and can be oscillated on at least one rolling element 8 on at least one of input side 3 and output side 5 is mounted and reduces rotational irregularities during operation.
  • the torsional vibration damper 1 includes a friction device 9 which can set different hysteresis depending on a rotation of the input side 3 relative to the output side 5 .
  • a friction device 9 which can set different hysteresis depending on a rotation of the input side 3 relative to the output side 5 .
  • the input side 3 forms a clutch disk of a friction clutch.
  • a torque can thus be introduced via the clutch disc of the torsional vibration damper 1 and passed on to a hub part 31 via the output side 5 .
  • the hub part 31 is used for.
  • B. the connection of a transmission input shaft.
  • the friction device 9 has three friction rings 10, 11, 12, which are each arranged between the input side 3 and the output side 5 and form friction points 13, 14, 15.
  • the friction device 9 has a first cup spring 16 which has a first contact point 18 , a second contact point 19 (only indicated) and a third contact point 20 arranged one after the other along a radial direction 17 from the inside to the outside and spaced apart from one another.
  • the first plate spring 16 constantly contacts a first friction ring 10 at the innermost first contact point 18, and a second friction ring 11 at the middle second contact point 19 (when the second plate spring
  • the first plate spring 16 contacts the first friction ring 10 and at least the third friction ring 12 during the first hysteresis and the first friction ring 10 and - if the second Disc spring 26 would not be present - only the second friction ring 11 in addition. Due to the second disk spring 26, the second contact point 19 between the first disk spring 16 and the second friction ring 11 is replaced by the fourth contact point 27 and the fifth contact point 28.
  • the contact points 18, 19, 20 are on different radii to the axis of rotation.
  • the first pad 18 at a smallest first radius and the third pad 20 at a largest third radius.
  • the second contact point 19 accordingly on an intermediate second radius.
  • the fifth contact point 28 lies on a fifth radius lying between the fourth radius and the third radius.
  • the first friction ring 10 is non-rotatably connected to the output side 5 .
  • the first friction ring 10 is connected to the output side 5 essentially without play in relation to the circumferential direction 4 .
  • This connection is realized via a bolt 29 which is connected to the output side 5 and which extends through a larger opening in the input side 3 towards the first friction ring 10 .
  • the first friction ring 10 forms a first friction point 13 with the input side 3 .
  • the first friction ring 10 is rotated along with the output side 5 and rubs with the first friction point 13 on the input side 3.
  • the first friction point 13 is at a very small first distance from the other friction points 14, 15 arranged to the axis of rotation 2.
  • the friction points 13 , 14 , 15 lie on different radii from one another or are arranged at different distances from the axis of rotation 2 .
  • the first friction point 13 at a smallest first distance and the third friction point 15 at a greatest third distance.
  • the second friction point 14 correspondingly at a second distance therebetween.
  • the first friction ring 10 has a plurality of first drivers 21 which extend along the axis of rotation 2 and via which the first plate spring 16 is connected to the first friction ring 10 in a rotationally fixed manner.
  • the first disc spring 16 is arranged directly adjacent to the first friction ring 10 along the axis of rotation 2 .
  • the first disc spring 16 is arranged along the axis of rotation 2 between the first friction ring 10 and the other two friction rings 11 , 12 , ie the second friction ring 11 and the third friction ring 12 .
  • the second friction ring 11 and the third friction ring 12 are arranged adjacent to one another along the radial direction 17 and overlapping one another along the axis of rotation 2 .
  • the first friction ring 10 has a plurality of first drivers 21 which extend along the axis of rotation 2 and via which the second friction ring 11 is connected to the first friction ring 10 in a rotationally fixed manner.
  • the third friction ring 12 has a plurality of second drivers 22 which extend along the axis of rotation 2 and via which the third friction ring 12 is connected to the first cup spring 16 in a torque-proof manner.
  • the friction device 9 has a pressure plate 23 which is non-rotatably connected to the output side 5 and which forms a second friction point 14 with the second friction ring 11 and a third friction point 15 with the third friction ring 12 .
  • the pressure plate 23 and the third friction ring 12 each have ramps 24 which together form a ramp device 25 by which the first hysteresis or the second hysteresis is set depending on the rotation of the input side 3 relative to the output side 5 .
  • the first disc spring 16 presses either the second friction ring 11 or the third friction ring 12 against the pressure plate 23.
  • the pressure plate 23 is directly connected to the input side 3 via rivets 32 .
  • the connections between the pressure plate 23 and the input side 3 are arranged outside of the friction rings 10 , 11 , 12 in the radial direction 17 .
  • the friction rings 10, 11, 12 and the disk spring 16 are connected to one another without play in relation to the circumferential direction 4.
  • the friction rings 10, 11, 12 and the plate spring 16 are connected to the output side 5.
  • the pressure plate 23 is connected to the input side 3 without play.
  • the friction device 9 additionally has a second plate spring 26 which has a fourth contact point 27 and a fifth contact point 28 arranged one after the other along the radial direction 17 from the inside to the outside and spaced apart from one another.
  • the second plate spring 26 constantly contacts the first plate spring 16 at the inner fourth contact point 27 and constantly contacts the second friction ring 11 at the outer fifth contact point 28 .
  • the fourth contact point 27 and fifth contact point 28 are located in the radial direction between the first contact point 18 and the third contact point 20.
  • the second plate spring 26 is arranged along the axis of rotation 2 between the first plate spring 16 and the second friction ring 11 .
  • the second plate spring 26 is arranged on the inside of the third friction ring 12 with respect to the radial direction 17 .
  • the ramp device 25 can be relieved via the second plate spring 26 .
  • the second disc spring 26 exerts a force on the second friction ring 11 at each hysteresis, i. H. the second friction point 14 is also acted upon in the first hysteresis, in addition to the first friction point 13 and the third friction point 15 .
  • the first friction ring 10 has a plurality of first drivers 21 which extend along the axis of rotation 2 and via which the second disk spring 26 is connected to the first friction ring 10 in a rotationally fixed manner.
  • Friction ring 11 a higher coefficient of friction can be produced at the second friction point 14 the, so that the pressing force of the first plate spring 16 can be reduced.
  • the surface pressure and thus the wear can be reduced.
  • the plate spring characteristic curve of the first plate spring 16 can also be lengthened.
  • the ramp device 25 is also further relieved due to the third contact point 20 only being present there, so that the wear is reduced.
  • the flange nose 30 shown in FIG. 1 is replaced here by bolts 29 onto which the first friction ring 10 can be pressed. A play-free arrangement of the first friction ring 10 is thus possible.
  • the bolts 29 are also arranged on a larger diameter than the flange nose 30, so that there is less angular play and play in the arrangement with as little play as possible can be further reduced.

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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 amortisseur de vibrations de torsion (1) d'un dispositif de transmission de couple, pourvu d'un axe de rotation (2), ledit amortisseur comportant au moins un côté entrée (3), un côté sortie (5) apte à tourner par rapport au côté entrée (3) dans une direction circonférentielle (4) ainsi qu'au moins un élément intermédiaire (6) qui est monté au niveau d'au moins un côté parmi le côté d'entrée (3) et le côté sortie (5), en appui sur un élément d'accumulation d'énergie (7), de manière à pouvoir osciller sur au moins un corps de roulement (8) et qui, pendant le fonctionnement de l'amortisseur de vibrations de torsion (1), réduit des irrégularités de rotation, ainsi qu'un dispositif de friction (9) qui présente au moins une première hystérésis et une deuxième hystérésis en fonction d'une rotation du côté entrée (3) par rapport au côté sortie (5) ; le dispositif de friction (9) comportant au moins trois anneaux de friction (10, 11, 12) qui sont disposés respectivement entre le côté entrée (3) et le côté sortie (5) et forment des points de friction (13, 14, 15).
PCT/DE2022/100564 2021-09-03 2022-08-05 Amortisseur de vibrations de torsion WO2023030570A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021122870.0 2021-09-03
DE102021122870.0A DE102021122870B3 (de) 2021-09-03 2021-09-03 Torsionsschwingungsdämpfer

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WO2023030570A1 true WO2023030570A1 (fr) 2023-03-09

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Publication number Priority date Publication date Assignee Title
DE102021132417A1 (de) * 2021-12-09 2023-06-15 Schaeffler Technologies AG & Co. KG Pendelwippendämpfer mit einer Drehachse

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Publication number Priority date Publication date Assignee Title
US9739340B2 (en) * 2013-04-25 2017-08-22 Aisin Seiki Kabushiki Kaisha Damper apparatus
EP3006774A1 (fr) * 2014-09-10 2016-04-13 Aisin Seiki Kabushiki Kaisha Appareil amortisseur avec limiteur de couple
WO2019196979A1 (fr) * 2018-04-10 2019-10-17 Schaeffler Technologies AG & Co. KG Amortisseur de vibrations de torsion
DE102019121204A1 (de) 2019-02-27 2020-08-27 Schaeffler Technologies AG & Co. KG Torsionsschwingungsdämpfer mit einer Rotationsachse für einen Antriebsstrang
DE102019121205A1 (de) 2019-02-27 2020-08-27 Schaeffler Technologies AG & Co. KG Torsionsschwingungsdämpfer mit einer Rotationsachse für einen Antriebsstrang
DE102019204366A1 (de) * 2019-03-28 2020-10-01 Zf Friedrichshafen Ag Kupplungsscheibe mit Vorspanneinrichtung
DE102020105144A1 (de) * 2020-02-27 2021-09-02 Schaeffler Technologies AG & Co. KG Torsionsschwingungsdämpfer mit Reibeinrichtung

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