WO2019170189A1 - Embrayage à friction - Google Patents

Embrayage à friction Download PDF

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Publication number
WO2019170189A1
WO2019170189A1 PCT/DE2019/100167 DE2019100167W WO2019170189A1 WO 2019170189 A1 WO2019170189 A1 WO 2019170189A1 DE 2019100167 W DE2019100167 W DE 2019100167W WO 2019170189 A1 WO2019170189 A1 WO 2019170189A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure plate
support
support ring
friction clutch
actuating element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/DE2019/100167
Other languages
German (de)
English (en)
Inventor
Martin Chambrion
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 WO2019170189A1 publication Critical patent/WO2019170189A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • F16D13/54—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
    • 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
    • F16D13/583—Diaphragm-springs, e.g. Belleville
    • F16D13/585—Arrangements or details relating to the mounting or support of the diaphragm on the clutch on the clutch cover or the pressure plate

Definitions

  • the invention relates to a friction clutch, with the aid of which in a drive train of a motor vehicle optionally a torque can be transmitted.
  • DE 10 2016 213 657 A1 discloses a friction clutch configured as a self-reinforcing multi-plate clutch, in which a disk spring provided for axially displacing a pressure plate is supported so as to be pivotable axially about a circumferential pivot point on a support ring.
  • a part of the torque flow to be transmitted takes place by means of a hub connected to a torque transmitting support disk via leaf springs to the pressure plate, which results in the Aufstell the leaf springs when closing the clutch self-amplification of the pressure applied by the pressure plate pressing force.
  • one end of the leaf spring is riveted to the pressure plate and the other end of the leaf spring is riveted to the support plate.
  • the riveting of the leaf spring with the support disc is used at the same time to fix the support ring with the support disc.
  • a friction clutch for selectively transmitting a torque in a drive train of a motor vehicle is provided with a counter-plate, a relative to the counter-plate axially displaceable pressure plate for frictionally pressing at least one friction lining between the counter-plate and the pressure plate, a torque-transmitting coupling with the friction lining output element, in particular a hub rotatably connected to a transmission input shaft hub, a non-rotatably connected to the output member support plate, at least one connected to the support plate and the pressure plate leaf spring for self-reinforcing a force applied by the pressure plate contact pressure, in particular designed as a plate spring, the actuating element for Displacing the pressure plate at an actuating force acting on the actuating element and a support ring for the pivotable axial support of the actuating
  • the pressure plate When the friction clutch is opened or closed, the pressure plate is axially displaced by a corresponding distance.
  • the leaf spring connected to the axially displaceable pressure plate and to the axially fixed support disk adjusts itself more or less strongly by a corresponding distance. Since the longitudinal extent of the leaf spring does not change, the change in the extent to which the leaf spring is placed, can only be achieved by a relative rotation of the pressure plate relative to the support disk.
  • the relative rotation of the pressure plate during its axial displacement leads to a friction-related relative movement of the pressure plate on the actuating element and / or to a friction-resistant one Relative movement of the actuating element on the support ring.
  • This friction can, in particular in overrun, cause the leaf spring is jammed and exposed to considerable compressive forces, the leaf spring may suffer a component failure due to the applied pressure forces by buckling under certain circumstances.
  • the friction-related relative rotations lead to unnecessarily high wear, which can lead to a reduced service life of the friction clutch.
  • the support ring is not rotationally fixed, but essentially freely rotatable indirectly or directly to the output element and the support member rotatably connected to the output member is connected, the support ring together with the actuator, the relative rotation of the pressure plate in a axial displacement of the pressure plate go along without a friction-related relative rotation takes place on the actuating element. A friction point on the actuating element is thereby avoided.
  • the actuating element is pivoted by a stationary, in particular hydraulic, actuating system in which, for example, a piston is extended out of a cylinder and / or is moved into the cylinder.
  • a release bearing in particular designed as a thrust bearing, is provided anyway between the actuating system and the actuating element, so that a friction point is provided by a relative rotation between the actuating element which is subject to friction and the operating system is avoided anyway.
  • An additional relative rotation of the actuation element together with the pressure plate relative to the counterplate can be easily passed along by the release bearing. Since unnecessary frictional effects are saved, the efficiency of the friction clutch is improved. In addition, the lower friction reduces the amount of hysteresis between the forces required to close the friction clutch and to open the friction clutch, which is felt to be a more comfortable operation of the friction clutch.
  • the support ring is designed to be relatively rotatable relative to the output element
  • the support ring is additionally indirectly or indirectly supported axially on the output element so that the pivot point of the actuating element on the support ring is not axially displaced by the relative movability of the support ring.
  • the kinematics of the movement of the actuating element in particular when the conicity of the operating element designed as a plate spring is changed by the actuating system when the pressure plate is displaced, is not impaired by the rotatability of the support ring. Due to the rotatable but axially supported support ring, unnecessary friction points and unnecessary bending load of the leaf spring can be avoided. so that a good durability of self-reinforcing friction clutches is made possible.
  • the friction clutch can be used in particular for coupling a drive shaft of an automotive engine with a transmission input shaft of a motor vehicle transmission.
  • the friction clutch has a, in particular connected to the counter-plate, torsional vibration damper, which may be configured in particular as a dual-mass flywheel and / or centrifugal pendulum.
  • the friction clutch may, in particular, be designed and developed further as described in DE 10 2016 213 657 A1, the contents of which are hereby incorporated by reference as part of the invention.
  • a torque to be transmitted can be introduced or removed during the pulling operation.
  • the counterplate can be designed, for example, in one piece with the support disk, as a result of which installation space can be saved.
  • the counterplate is supported axially or indirectly on the output element or on an input element of the friction clutch in order to axially support the contact forces introduced via the pressure plate.
  • the friction clutch designed in particular as a multi-disc clutch preferably has an outer disc carrier bearing friction linings or steel discs and an inner disc carrier carrying steel discs or friction linings.
  • the respective slats can be guided in a rotationally fixed but axially displaceable manner on the associated carrier.
  • the outer disk carrier is optionally coupled via a torsional vibration damper to an input element of the friction clutch, while the inner disk carrier is coupled to the output element, or vice versa.
  • the support ring is axially supported on the support disk past the output member.
  • a contact between the support ring and the support disk is thereby avoided, so that a friction point between the support ring and the support disk is saved.
  • a friction-related relative rotation with an axial displacement of the pressure plate is thereby avoided even at a location spaced from the actuating element.
  • the support ring is preferably received in a locking manner in the axial direction between the support disk and an axial stop protruding radially outward from the output element, the axial stop in particular being connected as a separate component, preferably a central nut, to the output element.
  • the support ring can easily be mounted from the side of the actuating element, in particular on the transmission side, without having to reach behind the support disk.
  • the axial stop can be mounted after inserting the support ring, in particular by screwing a central nut which forms the axial stop, which is preferably designed as a shaft nut, onto the starting element.
  • the support ring can easily grip behind the separately executed axial stop to allow for captive installation.
  • the axial stop can remove the expected axial forces during pivoting of the actuating element to the output element.
  • the support disk is further positioned axially spaced apart from the axial stop to the pressure plate.
  • the support disk can thereby be more mo tordrin and the axial stop rather be positioned on the transmission side.
  • the support disc and the axial stop can thereby be easily mounted from the side of the pressure plate and / or the actuating element when the support disc is already mounted. This also facilitates the attachment of the at least one leaf spring to the pressure plate.
  • the support ring has a radially outwardly projecting, in particular annular, support projection for the axial support of the support ring on the output element, wherein in particular the support lug engages behind an axial stop of the output element.
  • the support lug is characterized not radially outward in the direction of attachment point of the leaf spring with the support disk, but radially inward toward the output element. The installation space and the packaging dimensions of the support ring are thereby reduced.
  • the jacking approach can be used to a captive connection, whereby the reliability is increased.
  • the support ring is mounted on the output element via a support bearing. A relative rotation of the support ring to the output element can be realized by the support bearing with minimal friction.
  • the support bearing for example, be designed as angular contact ball bearings, thrust ball bearings, needle bearing or other bearing that is able to support the expected axial forces.
  • the support bearing can also be omitted in order to reduce the number of components and the production costs. Due to the considerably lower friction radius compared to the contact point of the actuating element on the pressure plate, the frictional forces between the support ring and the output element or the axial stop are so low that the frictional torque expected at this contact point can be tolerated without a friction moment to fear significant impairment of the durability of the friction clutch.
  • the actuating element engages with a normal force on the pressure plate, wherein the actuating element with the pressure plate in the circumferential direction is frictionally coupled in a frictionally engaged manner.
  • the actuating element can be biased, for example, and rest against the pressure plate even with a missing attacking actuating force with a certain minimum normal force.
  • the frictional force resulting from this normal force enables frictional coupling of the actuating element with the pressure plate, so that the actuating element can be rotated along with the pressure plate when the pressure plate is axially displaced. A transition from a static friction between the actuating element and the pressure plate to a sliding friction is avoided, so that wear effects are avoided by a frictional relative rotation.
  • a frictional torque prevailing between the actuating element and the pressure plate exceeds a drag torque between the supporting ring and the output element. Even if, during a rotation of the pressure plate, a drag torque should still act on the actuating element, which may occur in particular due to frictional effects between the support ring and the output element, the static friction between the actuating element and the pressure plate te high enough to avoid a frictional relative rotation between the actuating element and the pressure plate can. Any friction between the support ring and the output element which leads to the drag torque takes place at a significantly lower friction radius, so that this friction can not significantly impair the durability of the friction clutch.
  • the actuating element is rotatably coupled to the support ring.
  • a frictional relative rotation of the actuating element to the support ring can be avoided.
  • the actuating element is positively connected to the support ring, wherein in particular the positive coupling essentially blocks only a relative movement in the circumferential direction, but a
  • Pivoting movement around a circumferentially extending pivot point allows.
  • the support ring has through openings for the radial passage of actuation tongues of the actuation element, wherein in particular the actuation tongues are received captively in the axial direction in the axial direction by a safety ring inserted in the support ring.
  • the actuating tongues can abut in the tangential direction on the material of the support ring delimiting the respective passage opening, so that a relative rotation is blocked.
  • the actuation tongues can be pivoted on the axial edge of the passage opening.
  • an actuating system can act on the radially inner edge of the actuating tongues with an actuating force and change the conicity of the actuating element designed as a plate spring in order to pivot a radially outer force edge of the actuating element for axial displacement of the pressure plate with a movement component in the axial direction.
  • the passage openings are open towards an axial direction, so that the actuating tongues can be easily inserted into the passage openings during the assembly of the actuating element by an axial relative movement.
  • An axial slipping out of the actuation tongues from the passage openings can be blocked by a safety ring subsequently inserted into the support ring, which can retain the actuation tongues in the through-openings in a captive manner.
  • FIG. 1 shows a schematic sectional view of a first embodiment of a friction clutch
  • FIG. 2 shows a schematic sectional view of a second embodiment of a friction clutch.
  • the friction clutch 10 designed as a multi-disc clutch shown in FIG. 1 is provided for selectively coupling a drive shaft of an automobile engine with a transmission input shaft of a motor vehicle transmission in a drive train.
  • the friction clutch 10 has an input element 12 designed as a hub, via which the torque of the motor vehicle engine is introduced.
  • the input element 12 is connected via a torsional vibration damper 14 to an outer-plate carrier 16, to which friction linings 18 are fastened in a rotationally fixed but axially displaceable manner.
  • the friction linings 18 can be displaced from a pressure plate 20 to a counter plate 24 fixedly connected to an output element 22 designed as a hub, so that the friction linings 18 with steel laminations 26 arranged alternately with the friction linings frictionally engage between the counterplate 24 and the pressure plate 20 can be pressed to close the friction clutch 10.
  • the steel plates 26 are rotatably but axially slidably mounted with a réellelamel- llen 28, which is riveted in the illustrated embodiment with the counter plate 24.
  • the pressure plate 20 can be axially displaced by an actuating element 30 designed as a partial spring.
  • the actuator 30 is pivotally mounted with radially projecting spring tongues 32 on a support ring 34 about a pivot point extending in the circumferential direction.
  • the actuating element 30 is captive but can be pivoted about the retained spring tongues 32, but is pivotable with the locking ring 36.
  • support ring 34 connected.
  • the securing ring 36 additionally retains a disengaging disk 38, via which an actuating system can introduce an actuating force onto the radially inner ends of the spring tongues 32 via an interposed release bearing 40.
  • leaf springs 42 are riveted, which are secured at the other end with a support member 44 fixed to the output member 22.
  • the leaf springs 42 can move the pressure plate 20 into a defined starting position if no actuating force is introduced.
  • self-amplification of the contact pressure applied by the pressure plate 20 results.
  • the pressure plate 20 performs a slight relative rotation during an axial displacement.
  • the support ring 34 is mounted so as to be relatively rotatable relative to the output element 22 via a support bearing 46 on an axial stop 50 formed by a central nut 48 designed as a shaft nut.
  • the support ring 34 can engage behind the support bearing 46 with a radially projecting annular support projection 52.
  • the support bearing 46 is omitted in comparison to the embodiment of the friction clutch 10 shown in FIG. 1, so that the support projection 52 of the support ring 34 rests against the axial stop 50 of the central nut 48.
  • the frictional contact of the support ring 34 on the central nut 48 takes place on such a small friction radius that a significant impairment of the durability of the friction clutch 10 is not to be feared and the support bearing 46 can be saved.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un embrayage à friction (10) qui est prévu pour transmettre sélectivement un couple dans une transmission d'un véhicule automobile. L'embrayage à friction comprend une contre-plaque (24), une plaque de pression (20) pouvant être déplacée axialement par rapport à la contre-plaque (24) pour presser par friction au moins une garniture de friction (18) entre la contre-plaque (24) et la plaque de pression (20), un élément de sortie (22) pouvant être accouplé en transmission de couple à la garniture de friction (18), un disque de support (44) relié solidairement en rotation à l'élément de sortie (22), au moins un ressort à lame (42) relié au disque de support (44) et à la plaque de pression (20) pour auto-amplifier une force de pression appliquée par la plaque de pression (20), un élément d'actionnement (30) destiné à déplacer la plaque de pression (20) lorsqu'une force d'actionnement agit sur l'élément d'actionnement (30) et une bague de support (34) destinée à supporter axialement de manière pivotante l'élément d'actionnement (30). La bague de support (34) est supportée axialement de manière à pouvoir tourner par rapport à l'élément de sortie (22). Grâce à la bague de support (34) rotative mais supportée axialement, il est possible d'éviter un frottement inutile et une charge de flexion inutile du ressort à lame (42) de manière à permettre une bonne durabilité des embrayages à friction auto-renforçateurs (10).
PCT/DE2019/100167 2018-03-06 2019-02-21 Embrayage à friction Ceased WO2019170189A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018105038.0A DE102018105038A1 (de) 2018-03-06 2018-03-06 Reibungskupplung
DE102018105038.0 2018-03-06

Publications (1)

Publication Number Publication Date
WO2019170189A1 true WO2019170189A1 (fr) 2019-09-12

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ID=66041060

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2019/100167 Ceased WO2019170189A1 (fr) 2018-03-06 2019-02-21 Embrayage à friction

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DE (1) DE102018105038A1 (fr)
WO (1) WO2019170189A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019130851A1 (de) * 2019-11-15 2021-05-20 Schaeffler Technologies AG & Co. KG Reibkupplung mit gezielt eingebrachter Hysterese im Torsionsschwingungsdämpfer

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018119167A1 (de) 2018-08-07 2020-02-13 Schaeffler Technologies AG & Co. KG Selbstverstärkende Lamellenkupplung mit innenlamellendrückender Verstärkungsscheibe und Antriebsstrang mit solcher Lamellenkupplung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015135540A1 (fr) * 2014-03-12 2015-09-17 Schaeffler Technologies AG & Co. KG Embrayage à friction à commande centrifuge
DE102016223769A1 (de) * 2015-12-08 2017-06-08 Schaeffler Technologies AG & Co. KG Kupplungsvorrichtung mit Mittel zum Erzeugen einer die Anpresskraft unterstützenden Federkraft in Abhängigkeit des Drehzustandes
WO2017129178A1 (fr) * 2016-01-27 2017-08-03 Schaeffler Technologies AG & Co. KG Embrayage à friction
DE102016213657A1 (de) 2016-07-26 2018-02-01 Schaeffler Technologies AG & Co. KG Kupplungseinrichtung für einen Antriebsstrang eines Fahrzeuges

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015135540A1 (fr) * 2014-03-12 2015-09-17 Schaeffler Technologies AG & Co. KG Embrayage à friction à commande centrifuge
DE102016223769A1 (de) * 2015-12-08 2017-06-08 Schaeffler Technologies AG & Co. KG Kupplungsvorrichtung mit Mittel zum Erzeugen einer die Anpresskraft unterstützenden Federkraft in Abhängigkeit des Drehzustandes
WO2017129178A1 (fr) * 2016-01-27 2017-08-03 Schaeffler Technologies AG & Co. KG Embrayage à friction
DE102016213657A1 (de) 2016-07-26 2018-02-01 Schaeffler Technologies AG & Co. KG Kupplungseinrichtung für einen Antriebsstrang eines Fahrzeuges

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019130851A1 (de) * 2019-11-15 2021-05-20 Schaeffler Technologies AG & Co. KG Reibkupplung mit gezielt eingebrachter Hysterese im Torsionsschwingungsdämpfer

Also Published As

Publication number Publication date
DE102018105038A1 (de) 2019-09-12

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