EP3908764A1 - Disque d'embrayage pourvu d'une unité d'amortissement pour un embrayage à friction - Google Patents

Disque d'embrayage pourvu d'une unité d'amortissement pour un embrayage à friction

Info

Publication number
EP3908764A1
EP3908764A1 EP19836462.2A EP19836462A EP3908764A1 EP 3908764 A1 EP3908764 A1 EP 3908764A1 EP 19836462 A EP19836462 A EP 19836462A EP 3908764 A1 EP3908764 A1 EP 3908764A1
Authority
EP
European Patent Office
Prior art keywords
friction
clutch
disc
torque
damper
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Withdrawn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
EP19836462.2A
Other languages
German (de)
English (en)
Inventor
Julian Mattes
Alain Rusch
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 EP3908764A1 publication Critical patent/EP3908764A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16F15/129—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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/22—Vibration damping

Definitions

  • the invention relates to a clutch disc with a damper unit for a
  • Friction clutch a friction clutch with such a clutch disc
  • This phenomenon is characterized by two
  • Rigidity relates to the bending stiffness of the transmission input shafts at one
  • Measures which detune the coupling of the two natural modes of vibration, for example an adaptation of the lining spring stiffness in the relevant area or a change in the pre-tamping of the countermeasures involved in the area of the friction surface, preferably in the case of the pressure plate which is movable in the axial direction.
  • Measures which change the stiffnesses associated with the natural modes of vibration, for example by introducing a game the bearing arranged between the two coaxial transmission input shafts in double clutch transmissions.
  • a solution is known, for example, from DE 10 2016 208 120 A1 (compare FIGS. 1 to 3).
  • a radially soft friction disc 24 by means of a
  • Fastening area 36 fixedly connected to the output flange 22 and frictionally connected to the input flange 18 by means of a friction ring 34 or vice versa fixedly connected to the input flange 18 and with the
  • the invention relates to a clutch disc with a damper unit for a
  • Friction clutch comprising at least the following components:
  • a friction disc with an axis of rotation for frictionally transmitting a torque about the axis of rotation
  • At least one damper unit which the friction disc and
  • the clutch disc is primarily characterized in that the friction element is axially pressed between the damper flange and the friction disc.
  • the clutch disk proposed here can be used as a damped clutch disk in a friction clutch, for example also in a slip clutch or a torque limiter. Such is preferred
  • the friction disk is set up for torque transmission about its axis of rotation and for this purpose has at least one friction surface, preferably two friction surfaces, the friction surface being formed, for example, by a friction lining.
  • a friction partner for example a pressure plate, preferably pressing the friction disk having two friction surfaces between an axially movable pressure plate and an axially rigid counterplate (often a flywheel)
  • a torque is frictionally locked over the (at least one) friction surface as a result of a pressing force transferable.
  • the torque is passed from the friction disc via a damper unit to a damper flange, the
  • Damper flange torque-transmitting for example by means of teeth, connected to a torque transmission connection.
  • Torque transmission connection is, for example, a hub for connecting a shaft, for example with internal splines.
  • Damper unit is enabled, and the damper unit acts one
  • a damper unit is preferably formed by a helical compression spring, for example with a straight spring axis.
  • a plurality of such damper units for example two, three or four damper units, are preferably arranged distributed over the circumference between the friction disk and the damper flange.
  • the friction disk is thus designed to be oscillatable with respect to the torque transmission connection, for example the friction disk is only on the
  • Torque transmission connection centered and / or held axially.
  • the friction disc is often made in several parts, for example with one or two side discs, also referred to as side plates, a pad spring and one or two circumferentially formed friction linings or a multiplicity of separately formed and individually connected to the friction disk (not circumferentially formed) friction lining elements.
  • a friction element which rests frictionally on the friction disc, so that an opposing frictional torque is generated when there is a relative movement between the friction element and the friction disc.
  • the friction element is (technically) completely stiff. A technically rigid element is ideal in terms of realizability and cost
  • the friction element runs in the circumferential direction with the damper flange with or with the friction disc. Alternatively, that moves
  • the friction is then preferably very different on the two sides, for example by means of friction coefficients, so that one side is usually rigid while the other side carries out a relative torsional vibration.
  • the friction element thus acts as a hysteresis element, because this frictional force opposing the relative torsional vibration movement dissipates on the
  • the friction element is thus in one
  • Circumference twisted in itself around the axis of rotation
  • the friction element is at the same time designed to be soft, that is to say radially soft, in at least one transverse direction, so that the friction element can easily follow a (radial) load applied from the outside transverse to the axis of rotation.
  • a radial load is, for example, frictionally transmitted from the friction disc to the holding element.
  • the friction element is, for example, radially so soft that the force required for the radial deflection corresponds to a maximum of half a circumferential force which is necessary for twisting the friction element.
  • the friction element is therefore significantly more rigid than radially rigid.
  • the friction element is axially pressed between the damper flange and the friction disk.
  • the frictional force between the holding element and the friction disk is generated by means of the installation situation between the damper flange and the friction disk, for example by means of the axial force of a rivet.
  • the friction element is pressed by means of an (additional) hysteresis device, in that it comprises at least one axially acting spring element which is attached to the friction disk and / or to the
  • Torque transmission connection is supported axially.
  • the component connected for torque transmission is radially outside or radially inside a first intermediate mass, which in turn is radially outside or radially inside the frictionally effective one
  • Component is arranged, connected such that a gimbal
  • the friction element comprises a first material level and a second material level, the two material levels being connected in a torque-transmitting manner by means of spring elements, preferably leaf springs.
  • the friction element is formed with two material planes which are spaced apart from one another via an axial gap and are relatively movable with respect to one another in the transverse direction or in the radial direction. These material levels thus have a main extension in a plane with the axis of rotation as the normal. The material levels are thus aligned like the other disc elements of the clutch disc, with the material levels each being axial
  • depth Extend, here referred to as depth, which is considerably smaller than the diameter or a transverse extent in the above-mentioned plane.
  • the two material levels are connected to each other via spring elements, which are stiff and radially soft.
  • spring elements are particularly preferably designed in the manner of one or a plurality of (parallel arranged) leaf springs which have a main extent, here referred to as length, which is in the circumferential direction or tangential to one of the
  • Axis of rotation is aligned concentric circle.
  • the axial extent referred to here as the width, corresponds approximately to the depth of a material plane, for example.
  • the radial extension or transverse extension here referred to as the thickness, is made as small as possible, so that on the one hand a low transverse stiffness, that is to say a large radial softness, and on the other hand a high torque stiffness, that is to say a large circumferential stiffness, is achieved.
  • the friction element is made of metal, for example steel, preferably then in several parts.
  • the elements of the friction element are integrally connected to one another, for example by means of welding or gluing.
  • a metal core is formed, which is coated with a plastic and / or cast around it.
  • the friction element has at least one pressure piece, the at least one pressure piece frictionally on the damper flange or on the
  • the friction element comprises at least one, preferably a plurality of, pressure piece (s).
  • the pressure piece is on the axial side of the friction element, which lies opposite the friction surface of the friction element, as the only axial force-transmitting element of the friction element in frictional or positive contact with the friction disc or with the
  • the pressure pieces are connected as a cantilever beam (with the fixed end) to one of the two material levels and with the free end in
  • Such a pressure piece is designed to be flexible for a radial load, and thus it does not hinder or support the radial softness of the friction element.
  • the pressure pieces are set up to rest against the component of the clutch disc, to which the friction element can optionally carry out no or only a smaller transverse movement, for example the
  • the pressure piece therefore does not stand in the way of a gimbal evasion movement due to its flexibility to an axis parallel to the axis of rotation.
  • a large-area friction surface is preferably formed, which is used for frictional engagement
  • Bearing is set up with the respective other torque-transmitting component of the clutch disc, for example the friction disc.
  • the friction disc With a large friction surface, a large friction force in the radial direction and thus entrainment of the friction element or the relevant material plane in the transverse direction is ensured for most or all operating states.
  • Pressure piece rests frictionally, is arranged and only the second material level with the at least one pressure piece are connected to transmit pressure.
  • the at least one thrust piece or at least one of the thrust pieces protrudes through the first material plane in such a way that, in the event of operational transverse movements, the thrust piece does not come into contact with the first material plane or does not (transversely) transmit force.
  • the fixed end of the pressure piece designed as a cantilever is guided freely towards the friction surface formed by the second material plane, that is to say axially over an axial extension portion
  • the friction element has at least one suspension element which is hooked into the damper flange or into the friction disc, and the friction element is positively entrained in the circumferential direction by means of the hooking element.
  • a suspension element is also provided, by means of which the friction element in the damper flange or in the friction disc
  • Such a suspension element is, for example, a (in the installation situation axial) projection, for example, from an end piece of a spring element, preferably at the (free) end of a leaf spring and only indirectly via the spring element with the rest Friction element, for example a material level, connected.
  • a torque can be transmitted via the spring elements to the friction element, in particular to the second material plane forming the friction surface.
  • the friction element is arranged radially inside the at least one damper unit.
  • the friction element has a slight radial
  • Damper unit arranged.
  • the friction element has, for example, radially outer edges parallel to the damper units.
  • Triangular friction element with four arranged symmetrically
  • Friction elements are arranged parallel to the respective damper unit.
  • the spring elements are preferably radially far out on the friction element
  • Spring elements preferably radially between the component of the friction element, which forms the fluff of the material levels and the at least one
  • the friction element is formed from a plastic, preferably made by injection molding.
  • the friction element is made of a plastic, for example by means of injection molding. This means that low manufacturing costs can be achieved. In addition, due to the flexibility of the plastics in comparison to other materials, for example by means of additives, a frictional property of the friction element can be specifically set. In one embodiment, the material properties differ regionally, for example by means of multi-component injection molding and / or Inserting composite reinforcing agents, for example fibers and / or balls.
  • the friction element is preferably formed from a polyamide or regionally comprises polyamide. Particularly preferred are the polyamides PA46 or PA66, which are reinforced and have an additive for reduced friction, for example PA66CF10TF20 [ten percent carbon fiber, twenty percent
  • Manufacturing from a plastic is particularly advantageous in the case of a construction that is axially longer in comparison to previously known solutions, so that the torsional rigidity is achieved in comparison with a metallic solution with a corresponding material reinforcement.
  • the additional installation space is not available for the previously known solutions, because this means that the additional installation space required for an axial one
  • the friction element is a ceramic component or a ceramic
  • the friction element is formed in one piece. This reduces the manufacturing costs and the assembly effort, as well as increases
  • a friction clutch for a drive train comprising at least the following components:
  • a counter plate which can be connected to a torque input and to which the pressure plate is rotationally fixed;
  • Pressure plate and the counter plate for separable frictional Torque transmission between a torque input and the torque transmission connection is axially compressible.
  • the friction clutch is set up to detachable from a torque
  • Transfer output shaft to a consumer and vice versa This is usually achieved via the (at least one) friction pack, which has an axial
  • a clutch disc with integrated torsional vibration damping Such a torsional vibration is absorbed elastically to the skin-chip part, for example by means of a helical spring, in interaction with at least one flywheel, here the damper flange, and is delayed due to the elastic storage of the vibration energy and thus passed on evenly. This part is (almost) free of
  • Dissipation damped with high efficiency Furthermore, for many applications it is necessary to additionally set a hysteresis property in which a portion of the vibrational energy is dissipated in a frictional manner. In some applications, a different hysteresis property is created depending on the direction of rotation.
  • the function is also a
  • a drive train comprising a drive unit with an output shaft, at least one consumer and a friction clutch according to an embodiment according to the above description, wherein the output shaft for torque transmission is separably connected to the at least one consumer by means of the friction clutch.
  • the drive train is set up to drive a drive unit
  • Example of an energy conversion machine preferably one
  • Torque provided and output via its output shaft, for example crankshaft, can be released, that is to say can be switched on, for at least one consumer
  • An exemplary consumer is at least one
  • Recuperation i.e. for the electrical storage of the braking energy
  • a plurality of drive units are provided, which can be operated in series or in parallel or decoupled from one another by means of the friction clutch, or whose torque can be made available for use in a detachable manner. Examples are hybrid drives from an electric drive machine and an internal combustion engine, but also
  • Multi-cylinder engines in which individual cylinders (groups) can be activated.
  • Clutch disc is simple and inexpensive to manufacture and preferably has a small space requirement by integrating the function of a hysteresis device.
  • the clutch disc can preferably be designed with a reduced moment of inertia due to a reduced radial dimension of the friction element.
  • a motor vehicle comprising at least one drive wheel, which is driven by a drive train according to a
  • Embodiment is drivable according to the above description.
  • Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and performance, whereby this definition is subject to constant change according to the needs of the market.
  • vehicles of the small car and subcompact class are classified according to the European classification of the subcompact car class and in the British market they correspond to the super mini and city car class.
  • Examples of the smallest car class are a Volkswagen up! or a Renault Twingo.
  • Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.
  • Well-known full hybrids in the small car class are the BMW i3, the Audi A3 e-tron or the Toyota Yaris Hybrid.
  • the clutch disc set up for the drive train proposed here is simple and inexpensive to produce and preferably has a low one
  • the clutch disc can preferably be designed with a reduced moment of inertia due to a reduced radial dimension of the friction element.
  • Fig. 1 a damped clutch disc in section
  • Fig. 4 the friction element in a sectional view A-A;
  • a damped clutch disc 1 is axially between one axially
  • Clutch disc 1 comprises a friction disc 4 with a first friction lining 35 (here shown on the left) and a second friction lining 36 (here on the right here), which are connected by means of a lining spring 37 to a first side plate 33 (here shown on the left) about a rotation axis 5 in a torque-transmitting manner, so that when the friction packet formed in this way is pressed, a torque can be frictionally transmitted from the pressure plate 24 and the counter plate 25 to the first side window 33.
  • the first side window 33 is axially rigidly connected to a second side window 34, and both are optionally designed as (cold) formed sheets.
  • the first side window 33 is the second
  • Side window 34 is on a hub 38 with (internal) splines 38
  • the side windows 33, 34 are not immediate
  • damper unit 2 there is at least one damper unit 2, for example four to that
  • Rotation axis 5 symmetrically arranged damper units, here each designed as helical compression springs with a straight spring axis (here the cut one
  • Damper unit 2 pointing out of the image plane) to a damper flange 6 provided which torsional vibrations comparatively a torque entered on the friction lining side to the torque transmission connection 7
  • Damper flange 6 is pressed in a friction element 8, which with the first
  • Side window 33 is in frictional contact and is in pressure-transmitting contact with the damper flange 6 by means of a plurality of pressure pieces, here the first pressure piece 18 can be seen.
  • the friction element 8 has a first here
  • Axial gap 45 are spaced apart.
  • the two material planes 9, 10 are connected to one another in a radially soft manner by means of at least one spring element, here the first spring element 11 can be seen.
  • the first pressure piece 18 is connected to the second material level 10 in a pressure-transmitting manner and projects through the first
  • Material level 9 axially through or past the first material level 9, so that it comes to rest on the damper flange 6.
  • Friction element 8 part of a flysterese device which here on the other side of the damper flange 6 (here on the right in the illustration) has a hysteresis friction lining 40, which is pressed against the damper flange 6 by means of a hysteresis disc spring 41, and an axial disc spring 42 which supports the second side plate 34 and thus the friction plate 4 by means of the axial sliding ring 43 axially to the
  • Torque transmission connection 7 positioned and the friction element 8 pressed with the damper flange 8.
  • the friction element 8 is configured so as to be circumferentially rigid that a torque about the axis of rotation 5, that is to say a force in the direction of rotation 17, can be transmitted to the friction disc 4 by means of the first side disc 33 at least up to a predetermined limit value. At the same time it is
  • the friction element 8 is designed to be radially soft in such a way that a compensating movement 22 across the axis of rotation 5 is possible, that is to say the second material plane 10
  • the friction element 8 is fundamentally also rotated axially, with the pressure pieces against the (first) side window 33, and on the other side (as shown on the right) of the damper flange 6.
  • the friction element 8 is shown in a perspective view from the side of the pressure pieces 18 to 21 in an embodiment as can be used in a clutch disc 1 as shown in FIG. 1 with four damper units 2.
  • the first pressure piece 18 and the third pressure piece 20 protrude past the first material level 9 and the second pressure piece 19 and the fourth
  • Thrust piece 21 protrude through corresponding openings in the first material plane 9 and extend axially from the second material plane 10 beyond the first material plane 9, so that the first material plane 9 does not axially with a
  • Component is pressed, is preferably kept contact-free.
  • Material level 9 is by means of a second spring element 12 with a first
  • Hooking element 15 and connected by means of a fourth spring element 14 to a second hooking element 16 which, in an installation situation as shown in FIG. 1, is hooked into the damper flange 6 for torque-carrying.
  • a fourth spring element 14 to a second hooking element 16 which, in an installation situation as shown in FIG. 1, is hooked into the damper flange 6 for torque-carrying.
  • Torque-transmitting entrainment can be hooked in by means of the second
  • the first material level 9 is connected to the suspension elements 15, 16, that is to say according to FIG. 1, to the damper flange 6 in such a way that the first material levels 9 relative to the suspension elements 15, 16 perform a compensating movement 22 as shown (approximately ) can be moved to the left and right, for example with the axis of rotation 5 as the z direction in the x direction with little resistance.
  • the two material planes 9 and 10 are connected to one another in such a way that the two material planes 9 and 10 perform a compensating movement 22 as shown (approximately) up and down, for example with the axis of rotation 5 as the z direction in y -Direction can be moved with low resistance.
  • a compensating movement 22 as shown (approximately) up and down, for example with the axis of rotation 5 as the z direction in y -Direction can be moved with low resistance.
  • the friction element 8 is, however, sufficient to generate a friction force for a desired flysteresis effect, in the embodiment according to FIG. 1, on the (first) side window 33.
  • FIG. 3 the friction element 8 according to FIG. 2 is shown in a top view from the other side than in FIG. 2.
  • the courses of the sectional planes A-A, B-B and C-C of FIGS. 4, 5 and 6 are also identified there.
  • the first material level 9 is axially spaced from the second material level 10 by means of the axial gap 45 and only by means of the
  • FIG. 6 shows a possible embodiment of the pressure pieces 19, 21, which protrude past or pass through the first material level 9 and protrude axially far into the second material level 10 before they are connected to the second material level 10 by the fixed end.
  • the pressure pieces 19, 21 are very long axially and, with a relatively large radial relative movement to the free end, that is to say in the event of axial tilting, produce only slight resistance forces and internal stresses at the fixed end of the pressure pieces 19, 21 , 20 constructed exactly or similarly and connected to the first material level.
  • a drive train 23 comprising a drive unit 28, here shown as a 3-cylinder internal combustion engine, an output shaft 29, a friction clutch 3 and a torque-transmitting left drive wheel 31 and right drive wheel 32 are shown schematically.
  • the drive train 23 is arranged here in a motor vehicle 30, the drive assembly 28 with its motor axis 46 being arranged transversely to the longitudinal axis 48 in front of the driver's cab 47.
  • the output shaft 29 forms the torque input 26 for the friction clutch 3, which comprises a clutch disc 1, which is shown by means of an axial force device 27, shown here schematically as a concentric central release with a plate spring, between a counter plate 25, which (here directly) is connected to the output shaft 19, and a pressure plate 24 for frictional torque transmission to the
  • Drive wheels 31, 32 is compressible.
  • Friction clutch 31 left drive wheel friction disk 32 right drive wheel rotation axis 33 first side plate damper flange 34 second side plate torque transmission connection 35 first friction lining friction element 36 second friction lining first material level 37 lining spring
  • first thrust piece 46 motor axis second thrust piece 47 driver's cab third thrust piece 48 longitudinal axis fourth thrust piece

Abstract

L'invention concerne un disque d'embrayage (1) pourvu d'une unité d'amortissement (2) pour un embrayage à friction (3), le disque présentant au moins les éléments suivants : - un disque (4) de friction pourvu d'un axe de rotation (5) pour la transmission par friction d'un couple autour de l'axe de rotation (5) ; - un flasque d'amortissement (6) pour l'oscillation en rotation relative par rapport au disque (4) de friction ; - au moins une unité (2) d'amortissement, laquelle relie le disque (4) de friction et le flasque d'amortissement (6) l'un à l'autre avec transmission de couple ; - un raccord de transmission de couple (7) pour la transmission d'un couple du disque (4) de friction sur un arbre ; et - un élément (8) de friction rigide en périphérie et souple radialement destiné à venir en appui par friction sur le disque (4) de friction ou sur le flasque d'amortissement (6). Le disque d'embrayage (1) est caractérisé avant tout par le fait que l'élément (8) de friction est serré axialement entre le flasque d'amortissement (6) et le disque (4) de friction. Le disque d'embrayage selon l'invention permet de mettre au point un élément de friction pouvant être monté de manière simple et peu onéreuse, empêchant un bruit strident.
EP19836462.2A 2019-01-09 2019-12-17 Disque d'embrayage pourvu d'une unité d'amortissement pour un embrayage à friction Withdrawn EP3908764A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019100372.5A DE102019100372A1 (de) 2019-01-09 2019-01-09 Kupplungsscheibe mit einer Dämpfereinheit für eine Reibkupplung
PCT/DE2019/101101 WO2020143868A1 (fr) 2019-01-09 2019-12-17 Disque d'embrayage pourvu d'une unité d'amortissement pour un embrayage à friction

Publications (1)

Publication Number Publication Date
EP3908764A1 true EP3908764A1 (fr) 2021-11-17

Family

ID=69165276

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19836462.2A Withdrawn EP3908764A1 (fr) 2019-01-09 2019-12-17 Disque d'embrayage pourvu d'une unité d'amortissement pour un embrayage à friction

Country Status (4)

Country Link
EP (1) EP3908764A1 (fr)
CN (1) CN113039371B (fr)
DE (1) DE102019100372A1 (fr)
WO (1) WO2020143868A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020124109B4 (de) 2020-09-16 2022-04-21 Schaeffler Technologies AG & Co. KG Reibpad

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EP3069035B1 (fr) * 2013-11-13 2018-03-28 Schaeffler Technologies AG & Co. KG Embrayage à friction
FR3022965B1 (fr) * 2014-06-26 2016-10-21 Valeo Embrayages Disque d'embrayage
DE102014214634A1 (de) * 2014-07-25 2016-01-28 Schaeffler Technologies AG & Co. KG Rotationsbaugruppe für eine Kupplung und/oder Dämpfereinrichtung sowie Drehmomentübertragungseinrichtung
DE102014218549A1 (de) * 2014-09-16 2016-03-17 Schaeffler Technologies AG & Co. KG Reibring und Drehschwingungsdämpfer
DE102014223477A1 (de) * 2014-11-18 2016-05-19 Schaeffler Technologies AG & Co. KG Schwingungsdämpfereinheit
JP6541983B2 (ja) * 2015-02-09 2019-07-10 株式会社エクセディ ダンパーディスク組立体
DE102016207116B3 (de) * 2016-04-27 2017-05-04 Schaeffler Technologies AG & Co. KG Kupplung mit Momentenflussaufteilung zur partiellen Verstärkung
DE102016208120A1 (de) 2016-05-11 2017-11-16 Schaeffler Technologies AG & Co. KG Reibscheibe für einen Kupplungsscheibendämpfer

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CN113039371A (zh) 2021-06-25
CN113039371B (zh) 2023-01-03
WO2020143868A1 (fr) 2020-07-16

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