EP3775607A1 - Disque d'embrayage avec amortisseur pendulaire à bascule à un seul sens de déplacement entre ses zones de bride et embrayage à friction - Google Patents

Disque d'embrayage avec amortisseur pendulaire à bascule à un seul sens de déplacement entre ses zones de bride et embrayage à friction

Info

Publication number
EP3775607A1
EP3775607A1 EP19713684.9A EP19713684A EP3775607A1 EP 3775607 A1 EP3775607 A1 EP 3775607A1 EP 19713684 A EP19713684 A EP 19713684A EP 3775607 A1 EP3775607 A1 EP 3775607A1
Authority
EP
European Patent Office
Prior art keywords
rotation
input part
flange
output part
stop
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.)
Withdrawn
Application number
EP19713684.9A
Other languages
German (de)
English (en)
Inventor
Maria Fischer
Gerd Ahnert
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
Publication of EP3775607A1 publication Critical patent/EP3775607A1/fr
Withdrawn legal-status Critical Current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
    • F16F15/12—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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/68—Attachments of plates or lamellae to their supports
    • 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
    • F16F15/1204—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 with a kinematic mechanism or gear system
    • F16F15/1205—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 with a kinematic mechanism or gear system with a kinematic mechanism, i.e. linkages, levers
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/22—Vibration damping
    • 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 clutch disc for a friction clutch of a motor vehicle, such as a car, truck, bus or other commercial vehicle, with an input part rotatable about an axis of rotation and having a friction lining, likewise rotatable about the axis of rotation (preferably with a hub further connected) output part and a pendulum rocker damper which couples the input part to the output part, wherein the pendulum rocker damper has two flange regions which rotate relative to one another about the rotation axis in a limited angular range, cooperate with the input part and the output part and several each via a link device Having a first flange and a second flange area pivotally received intermediate parts and the Kul lissen familiaren are formed such that in a relative rotation of the first flange region to the second flange portion, the intermediate parts each by a spring means are inhibited in their movement (relative to the flange areas).
  • the invention also relates to a friction clutch with this clutch disc.
  • the link mechanisms implemented here are often relatively large-sized and expensive in the position of a finger.
  • the flange areas and / or the intermediate parts are to be made sufficiently large. With a relatively large swivel angle of the intermediate parts / the flange areas and a relatively large spring travel of the spring device, this effect is further enhanced.
  • each flange region is operatively connected to the input part and the output part in such a way that both with a change of a direction of action of a resulting load acting on the input part from a first direction of rotation to one In the first direction of rotation, the second direction of rotation is opposite to the second direction of rotation and, when the direction of action changes from the second direction of rotation to the first direction of rotation, both flange areas are moved relative to one another in a single / common fixed direction of movement.
  • the components of the pendulum rocker damper are therefore produced with significantly less effort. For example, only straight-line slide tracks are required in the respective link device. As a result, the load on the individual components of the pendulum rocker damper during operation is significantly reduced. Impacts / jerky load jumps on the components are thereby avoided. Thus, the individual components can be dimensioned correspondingly smaller and space can be saved or the entire clutch disc can be made more efficient.
  • first flange region can be rotated over a first angular range relative to the input part and / or the output part (limited). Consequently, it is also advantageous if the second flange portion is rotatable relative to the input part and / or the output part over a second angular range.
  • the interface between the pendulum rocker damper and the respective input part and the output part is particularly easy to produce.
  • the first flange region has a first stop, which first stop is matched to the input part (ie cooperates with a (first) counterstop of the input part), that during a rotation of the input part in the first In the first direction of rotation, the input part is non-rotatably in contact with this first stop (of the first flange region) and, with a rotation of the input part in the second rotational direction, the input part can be rotated (limited) relative to the first flange region (limited).
  • the second flange region prefferably has a first stop, which first stop is matched to the input part (ie interacts with a counter-stop of the input part facing the first counter-stop), that during a rotation of the input part in the second direction of rotation, the input part rests in a rotationally fixed manner on this first stop (of the first flange region) and, in the case of a rotation of the input part in the first rotational direction, the input part relative to the second Flange area (limited) rotatable / spaced.
  • first stop is matched to the input part (ie interacts with a counter-stop of the input part facing the first counter-stop)
  • the first flange has a second stop, which second stop is so matched to the output part (ie, with a (first) counter-stop of the output part cooperates) that at a rotation of the Output part in the first direction of rotation, the output part rotatably rests against this second stop and at a rotation of the output part in the second direction of rotation, the output part relative to the first flange (limited) rotatable / spaced.
  • the second flange region has a second stop, which second stop is matched to the output part (ie cooperating with a counter-stop of the output part facing the first counter-stop), that during a rotation of the output part in the second direction of rotation, the output part rests against rotation at this second stop and, upon a rotation of the output part in the first rotational direction, the output part is rotatable (limited) relative to the second flange region.
  • the connection of the respective flange areas by the output part is implemented particularly skilfully.
  • a (first) stop is attached to both the first flange region and the second flange region in such a way that the output part and the input part are in contact with the respective flange region when rotated in the first direction of rotation.
  • a (second) stop is mounted both on the first flange region and on the second flange region in such a way that the output part and the input part are in contact with the respective flange region when rotated in the second rotational direction.
  • the spring device has a changing spring rigidity along its spring travel, a multi-stage torque characteristic of the pendulum rocker damper is implemented in a simple manner.
  • the spring device it is also expedient for the spring device to have a spring unit with a plurality of spring elements acting between the intermediate parts, preferably in parallel arrangement with respect to one another.
  • each intermediate part is coupled to the first flange area by means of a first linear slide track and is coupled to the second flange area by means of a second guide track running obliquely to the first slide track.
  • the invention further relates to a friction clutch for a motor vehicle drive train, with a clutch disk according to the invention used as a first clutch component according to at least one of the previously described embodiments and a frictionally engaged with the clutch disc second clutch component.
  • a clutch disc is realized with pendulum rocker damper, in the input and output flange (first flange and second flange) even when changing the loading direction only in one direction to each other. Only one (even) section of the previous trajectories is required.
  • FIG. 1 shows a schematic representation of a peripheral region of a clutch disc according to the invention, implemented according to a preferred embodiment, wherein a pendulum rocker damper inserted between an input part and an output part of the clutch disc on the part of a coupling a first flange, a second flange and a flange Intermediate part is illustrated
  • FIG. 2 are schematic representations of the clutch disc of Fig. 1, wherein in the central partial view of the pendulum rocker damper, as already in Fig. 1, is arranged in a central position, in the left partial view, the input part in a first direction of rotation relative to the output part rotated and in the right-hand partial view, the input part is rotated in a second direction of rotation relative to the output part,
  • FIG. 3 shows schematic representations of the clutch disk according to FIG. 1, wherein spring elements of the pendulum rocker damper are additionally illustrated, and in which the center position of the pendulum rocker is implemented in an upper partial view, in a central partial view the input part in the first rotational direction relative to FIG the output part is rotated and in a lower partial view, the input part is rotated in the second rotational direction relative to the output part,
  • Fig. 4 is a front view of a clutch disc according to the invention in a preferred embodiment, wherein along the circumference of the clutch disc a total of three intermediate parts according to the in Figs. 1 to 3 are shown used with the flange areas,
  • Fig. 5 is a plan view of an intermediate part used in Fig. 4, and
  • FIGS. 6a and 6b show two diagrams, of which FIG. 6a shows a diagram of the pendulum-type rocker of FIGS. 1 to 4 converted torque curve shows and Fig. 6b in the pendulum rocker damper of Figs. 1 to 4 converted path characteristic of the intermediate part shows.
  • FIG. 4 clearly shows the basic structure of a clutch disk 1 according to the invention.
  • the clutch disk 1 typically has an annular / annular disk-shaped input part 4, which is therefore also referred to as a friction ring.
  • the input part 4 is rotatably arranged about a central axis of rotation 2.
  • the clutch disc 1 is in its operation in a friction clutch, which is not shown here for clarity, used.
  • the friction lining 3 then interacts in a typical manner with a pressure plate and / or counter plate / pressure plate of the friction clutch.
  • the clutch disk 1 is preferably connected with its output part 5 in a rotationally fixed manner to a transmission shaft of a transmission of a motor vehicle drive train and accordingly forms a first clutch component of the friction clutch.
  • a second clutch constituent which in a closed position of the friction clutch is non-rotatably connected to the first clutch component via a clean force connection and is freely rotatable relative to the first clutch component in an open position of the friction clutch, again has the pressure plate and / or the pressure plate on.
  • the input part 4 has two abutment projections 23 on a region lying radially inward with respect to the axis of rotation 2.
  • the stop projections 23 form a first counter-stop 20a and a second counter-stop 20b of the input part 4, which are then shown in FIGS. 1 to 3 are closer to recognize.
  • FIGS. 1 to 3 are closer to recognize.
  • FIG. 4 only one (second) counter-stop 20b of the input part 4 is illustrated.
  • the counter-stops 20a, 20b of the input part 4 are attached to a protruding from the friction lining 3 in the radial direction inwardly nose 24.
  • the two counter strikes 20a, 20b are in a circumferential direction of the input part 4, i. spaced apart along a circular line running around the axis of rotation 2.
  • the output part 5 is arranged concentrically with the input part 4.
  • the output part 5 is therefore also rotatably arranged about the rotation axis 2 rotatably.
  • the output part 5 is shown in FIG. 4 as a ring and, during operation, preferably directly forms a hub rotationally fixed to the transmission shaft.
  • the output part 5 has a plurality of radially outwardly projecting elevations 22.
  • the elevations 22 form a first counter stop 21 a and a second counter stop 21 b of the output part 5, which then in the Fign. 1 to 3 are closer to recognize.
  • the counterstops 21 a, 21 b are spaced apart in the circumferential direction of the output part 5, that is, along the circular line extending around the rotation axis 2.
  • the input part 4 is rotatably connected / coupled via a pendulum rocker damper 6 to the output part 5.
  • the pendulum rocker damper 6 is typically used for damping torsional vibrations that are mainly present on the part of the input part 4 during operation.
  • the input part 4 is thus limited by the formation of the pendulum rocker damper 6 limited by a certain (rotational) angular range relative to the output part 5 rotatable.
  • FIG. 1 schematically illustrates that circumferential region of the clutch disk 1 according to FIG. 4, which illustrates an intermediate part 11 between a first flange region 7 and a second flange region 8.
  • the flange portions 7 and 8 are formed separately from the input and output parts 4, 5 and thus each form a single flange.
  • the input part 4 is shown schematically with its in the circumferential direction opposing counter-attacks 20a, 20b.
  • the output part 5 is shown schematically with its two in the circumferential direction opposing counter-attacks 20a, 20b.
  • the pendulum rocker damper 6 has the two flange areas 7, 8 as well as a plurality of intermediate parts 1 1 arranged distributed in the circumferential direction.
  • the respective intermediate part 1 1 is coupled to the first flange region 7 via a first link device 9 and coupled to the second flange region 8 via a second link device 10. Consequently, the intermediate part 1 1 is displaceably arranged relative to the first flange region 7 via the first slide device 9 and is displaceably arranged relative to the second flange region 8 via the second slide device 10.
  • the first link device 9 has a plurality of first slide tracks 18, which interact with one another via a roller element 25 which is slidably received in them.
  • a first slide track 18 is directly formed in the intermediate part 11, a further first slide track 18 is formed directly in the first flange portion 7.
  • a roller element 25 is inserted in the two first slide tracks 18 and thus serves for coupling / movement coupling of the first flange area 7 with the intermediate part 11 along the runway 25 of the rolling elements 25 defined by the first slide tracks 18.
  • the first slide device 9 points also a plurality of second slide tracks 19 which cooperate with each other via a roller element 25 accommodated in them in a displaceable manner.
  • a second slide track 19 is directly formed in the intermediate part 11, a further second slide track 19 is formed directly in the first flange portion 7.
  • a roller element 25 is inserted into the two second slide tracks 19 and thus serves for the movement coupling of the first flange area 7 with the intermediate part 11 along the runway 25 of the rolling elements 25 defined by the second slide tracks 19.
  • the second slide track 19 introduced in the intermediate part 11 runs obliquely to the first slide track 18, as well visible in Fig. 5 ..
  • the intermediate part 11 is movably coupled to the second flange region 8 via the second link device 10.
  • the second link device 10 has two (third) slide tracks 26, wherein one of the third slide tracks 26 is inserted in the intermediate part 11 and a further second slide track 26 is introduced into the second flange portion 8.
  • a roller element 25 is inserted into the two third cam tracks 26 and thus serves to couple the second flange section 8 to the intermediate part 11 along the roller track 25 defined by the third track 26.
  • the third slide track 26 introduced in the intermediate part 11 runs obliquely both to the first slide track 18 and to the second slide track 19 of the intermediate part 11.
  • All slide tracks 18, 19, 26 each extend exclusively in a straight line, that is implemented as straight slots.
  • the slide mechanisms 9 and 10 are designed so that when shifting the intermediate Part 11, ie in a rocking movement of the intermediate part 11 in the radial direction and in the circumferential direction, the flange portions 7, 8 are pressed apart in the circumferential direction or pushed together again.
  • the intermediate parts 11 are supported by a spring device 12.
  • the spring device 12 acts on each intermediate part 11, the spring device 12 acts.
  • the spring device 12, which can also be clearly seen in FIG. 4, has a spring unit 15 for each intermediate part 11.
  • the spring units 15 are arranged distributed in the circumferential direction. Between each two circumferentially adjacent intermediate parts 11, a spring unit 15 is arranged.
  • the spring unit 15 is used directly for supporting the intermediate parts 11. A first end of the spring unit 15 is in contact with an intermediate part 11, a second end of the spring unit 15 opposite the first end is in contact with another intermediate part 11.
  • the spring units 15 are clamped between the intermediate parts 11 in such a way that a radial biasing of the intermediate parts 11 in the radial direction to the outside occurs.
  • the respective spring unit 15 has a first spring element 16 and a second spring element 17, which is arranged parallel (alternatively in series) with the first spring element 16 on. Both spring elements 16 and 17 are realized in this embodiment as helical compression springs. The second spring element 17 is arranged within the first spring element 16.
  • the slide mechanisms 9, 10 are in principle designed in such a way and each flange portion 7, 8 with the input part 4 and the output part 5 in operative connection, that both at a change of direction of action of acting on the input part 4 resulting load from a first direction of rotation (in the first Circumferential direction) to one, the first rotational direction opposite, the second rotational direction (second circumferential direction) as well as a change of Wirs- From the second direction of rotation to the first direction of rotation, both flange areas 7, 8 are moved relative to one another in a single fixed direction of movement. This can be seen particularly well in the partial views of FIG. 2.
  • the first flange region 7 is rotatable relative to the input part 4 and the output part 5 over a first angular range.
  • the second flange region 8 is also rotatable relative to the input part 4 and the output part 5 over a second angular range.
  • the first stop 13a is formed in this way and the first flange region 7 is designed in principle such that the input part 4, when rotated in the first direction of rotation (relative to the output part 5), rests against this first stop 13a in a rotationally fixed manner and thus carries the first flange region 7 with it twisted.
  • the first stop 13a and the first flange area 7 are designed such that, upon a rotation of the input part 4 in the second direction of rotation (relative to the output part 5), i.
  • the input part 4 is in contact with a first stop 13b of the second flange region 8 via its second counterstop 20b, which is opposite the first counterstop 20a.
  • This first stop 13b of the second flange region 8 is matched to the input part 4 in such a way that the input part 4 rotatably abuts against the first stop 13b when rotated in the second direction of rotation and at a rotation in the first direction of rotation relative to the first flange region 7 is rotatable.
  • the flange portions 7 and 8 act on their second stops 14a, 14b with counter-stops 21 a, 21 b of the output part 5 together.
  • the second flange portion 8 has a with the output part 5, namely the first counter-attack 21 a, cooperating second stop 14a.
  • the second stop 14a is formed in this way and the second flange region 8 is in principle designed such that the output part 5, when twisted in the first direction of rotation (relative to the input part 4), abuts against this second stop 14 a in rotation and thus also twists the second flange region 8. This can be seen in the right part of Fig. 2.
  • the second stop 14a and the second flange area 8 are designed such that upon rotation of the output part 5 in the second direction of rotation (relative to the input part 4), ie opposite to the first direction of rotation, free rotation of the shaft is achieved Output part 5 relative to the second flange 8 in the fixed (first) angle range comes. In this movement in the second direction of rotation, the output part 5 is in contact with a second stop 14b of the second flange area 8 via its second counterstop 21b opposite the first counterstop 21a.
  • This second stop 14b of the second flange area 8 is matched to the output part 5 in such a way that the output part 5 rotatably bears against the second stop 14b during its rotation in the second direction of rotation and relative to the second direction when rotated in the first direction of rotation Flange portion 8 is rotatable.
  • the respective first flange region 7 and the second flange region 8 are rotatable in the circumferential direction in a limited angular range relative to the input part 4 and the output part 5, whereby in this relative rotation the spring device 12 acts in such a way to inhibit the movement of the intermediate parts 11, that a load difference between the input part 4 and the output part 5 is attenuated / weakened.
  • the spring device 12 is shown schematically in FIG. 2 as marked with FF, acting on the intermediate part 11 force arrow.
  • the force applied to the input part 4 force arrow F, the resulting, acting on the input part 4 and the input part 4 for a relative rotation to the output part 5 mandatory load is shown.
  • FIG. 6a illustrates a torque characteristic (profile of the torque MD as a function of the angle of rotation (angle range) y ⁇ ) of the pendulum rocker damper 6.
  • 6b shows a path characteristic (course of the displacement path sw as a function of the angle of rotation (angular range) y ⁇ ) of the intermediate part 11 (according to the spring movement).
  • the two flange parts first and second flange regions 7, 8) are also moved in one direction only relative to one another when changing the loading direction.
  • only one (straight) section of the trajectories is required.
  • the openings (slide tracks 18, 19, 26) in the components (along the curve flanks) can be made considerably smaller, or that the possibility exists of adjusting the pivot angle between the input and output parts 4, 5 relatively larger. This is advantageous for the dimensioning of the components or the entire assembly or for the performance parameters of the clutch disc. In this case, no transition regions of the trajectories 18, 19, 26 are required for the two movement / loading directions. In Fig. 5, the relatively smaller openings for the curve edges 18,19, 26 (space for roller movement) are exemplified for the intermediate part 11 to see. Another advantage is that even when changing the loading direction, the same curved path 18, 19, 26 is used.
  • the torque characteristic curve also has a slope at the "transition point".
  • the contact points of the input part 4 and the output part 5 (respectively to the first flange (first flange portion 7) and the second flange (second flange portion 8)) can be seen.
  • stop bolts (stop projection 23) on the input part 4 or toothings (elevations 22) on the output part 5 are exemplarily designed.

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

Abstract

L'invention concerne un disque d'embrayage (1) destiné à embrayage à friction d'un véhicule automobile et comprenant un élément d'entrée (4) pouvant tourner sur un axe de rotation (2) et comportant une garniture de friction (3), un élément de sortie (5) disposé également de manière à pouvoir tourner sur l'axe de rotation (2) et un amortisseur pendulaire à bascule (6) accouplant l'élément d'entrée (4) à l'élément de sortie (5). L'amortisseur pendulaire à bascule (6) comporte deux zones de bride (7, 8), pouvant tourner l'une par rapport à l'autre sur l'axe de rotation (2) dans une plage angulaire limitée et coopérant avec l'élément d'entrée (4) et l'élément de sortie (5), et une pluralité d'éléments intermédiaires (11) reçus de manière pendulaire au niveau d'une première zone de bride (7) et d'une deuxième zone de bride (8) par le biais d'un dispositif à coulisse (9, 10) et les dispositifs à coulisse (9, 10) sont conçus de manière à ce que, lors d'une rotation relative de la première zone de bride (7) par rapport à la deuxième zone de bride (8) les éléments intermédiaires (11) sont chacun bloqués dans leur mouvement par un dispositif à ressort (12). Les dispositifs à coulisse (9, 10) sont conçus de manière à ce que chaque zone de bride (7, 8) soit en liaison fonctionnelle avec l'élément d'entrée (4) et l'élément de sortie (5) de telle sorte que, lors d'un changement d'un sens d'action d'une charge résultante agissant sur l'élément d'entrée (4) d'un premier sens de rotation à un deuxième sens de rotation opposé au premier sens de rotation, et lors d'un changement de sens d'action du deuxième sens de rotation au premier sens de rotation, les deux zones de bride (7, 8) sont déplacées dans un seul sens de déplacement fixe l'une par rapport à l'autre. L'invention concerne également un embrayage à friction équipé de ce disque d'embrayage (1).
EP19713684.9A 2018-04-06 2019-03-07 Disque d'embrayage avec amortisseur pendulaire à bascule à un seul sens de déplacement entre ses zones de bride et embrayage à friction Withdrawn EP3775607A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018108142.1A DE102018108142A1 (de) 2018-04-06 2018-04-06 Kupplungsscheibe mit Pendelwippendämpfer mit nur einer Bewegungsrichtung zwischen seinen Flanschbereichen; sowie Reibkupplung
PCT/DE2019/100205 WO2019192643A1 (fr) 2018-04-06 2019-03-07 Disque d'embrayage avec amortisseur pendulaire à bascule à un seul sens de déplacement entre ses zones de bride et embrayage à friction

Publications (1)

Publication Number Publication Date
EP3775607A1 true EP3775607A1 (fr) 2021-02-17

Family

ID=65951451

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19713684.9A Withdrawn EP3775607A1 (fr) 2018-04-06 2019-03-07 Disque d'embrayage avec amortisseur pendulaire à bascule à un seul sens de déplacement entre ses zones de bride et embrayage à friction

Country Status (7)

Country Link
US (1) US11255408B2 (fr)
EP (1) EP3775607A1 (fr)
JP (1) JP7052074B2 (fr)
KR (1) KR102714881B1 (fr)
CN (1) CN111742160B (fr)
DE (2) DE102018108142A1 (fr)
WO (1) WO2019192643A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020127459A1 (de) * 2020-08-14 2022-02-17 Schaeffler Technologies AG & Co. KG Pendelwippendämpfer mit mehrteiligem Wippenelement; sowie Hybridantriebsstrang
DE102020127456B4 (de) 2020-08-14 2022-05-25 Schaeffler Technologies AG & Co. KG Pendelwippendämpfer mit Überlastschutz sowie Hybridantriebsstrang
DE102021112758B3 (de) * 2021-05-18 2022-08-11 Schaeffler Technologies AG & Co. KG Pendelwippendämpfer mit radial innenliegenden Anschlägen

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JP5527428B2 (ja) 2010-12-03 2014-06-18 トヨタ自動車株式会社 捩り振動減衰装置
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DE102014210685A1 (de) 2013-06-21 2014-12-24 Schaeffler Technologies Gmbh & Co. Kg Drehmomentübertragungseinrichtung
JP6117722B2 (ja) 2014-01-17 2017-04-19 株式会社Ｎｔｔドコモ 基地局、ユーザ装置、干渉低減制御情報通知方法、及び干渉低減方法
DE102015211899A1 (de) 2015-06-26 2016-12-29 Schaeffler Technologies AG & Co. KG Torsionsschwingungsdämpfer
CN110662908B (zh) 2017-05-23 2021-11-26 舍弗勒技术股份两合公司 具有扭矩限制器的扭振减振器
DE102018108441A1 (de) 2018-04-10 2019-10-10 Schaeffler Technologies AG & Co. KG Torsionsschwingungsdämpfer, Kupplungsscheibe und Kupplung

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CN111742160A (zh) 2020-10-02
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WO2019192643A1 (fr) 2019-10-10
CN111742160B (zh) 2022-06-10
US20210115982A1 (en) 2021-04-22
JP7052074B2 (ja) 2022-04-11
DE112019001804A5 (de) 2020-12-17
KR20200138241A (ko) 2020-12-09
US11255408B2 (en) 2022-02-22
KR102714881B1 (ko) 2024-10-11

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