WO2011147394A1 - Embrayage à friction présentant une compensation d'usure à commande proportionnelle à la course - Google Patents

Embrayage à friction présentant une compensation d'usure à commande proportionnelle à la course Download PDF

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Publication number
WO2011147394A1
WO2011147394A1 PCT/DE2011/000449 DE2011000449W WO2011147394A1 WO 2011147394 A1 WO2011147394 A1 WO 2011147394A1 DE 2011000449 W DE2011000449 W DE 2011000449W WO 2011147394 A1 WO2011147394 A1 WO 2011147394A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure plate
wear
housing
friction clutch
drive pawl
Prior art date
Application number
PCT/DE2011/000449
Other languages
German (de)
English (en)
Inventor
Michael Schneider
Gerd Ahnert
Original Assignee
Schaeffler Technologies Gmbh & 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 Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Priority to DE112011101755.3T priority Critical patent/DE112011101755B4/de
Priority to CN201180023139.2A priority patent/CN102884333B/zh
Publication of WO2011147394A1 publication Critical patent/WO2011147394A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/75—Features relating to adjustment, e.g. slack adjusters
    • F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate

Definitions

  • the invention relates to a friction clutch at least consisting of a housing arranged around a rotation axis with a rotationally fixed and axially limited against the action of energy storage to this displaceable pressure plate arranged, supported by a plate spring supporting the housing against a fixed housing back pressure plate under tension of friction linings of a clutch disc is axially displaceable, wherein falls below a formed in strained friction linings between the pressure plate and counter-pressure plate a positive connection between a arranged with a spindle of a pressure plate on the spindle drive for rotary drive a arranged between pressure plate and plate spring adjusting ring connected to the pressure plate in the circumferential direction ramps connected pinion and formed on the housing elastically under bias in the direction of pressure plate drive pawl and during a Betrelifactsbew egung of the pressure plate relative to the housing after a rotation of the pinion is released by means of the drive pawl.
  • a generic friction clutch is known for example from DE 10 2008 051 100 A1.
  • a wear compensation occurring over the life of the friction clutch wear of the friction linings in such friction clutches is effected by an adjusting ring is arranged between the pressure plate and this acting lever system having arranged in the circumferential direction ramps arranged with arranged on the pressure plate counter ramps upon rotation of the adjusting ring caused by the axially worn friction linings reduced distance between counter-pressure plate and pressure plate and thus between the counter pressure plate and lever system compensates.
  • a substantially constant angle of attack of the lever system such as a lever spring or disc spring to the housing with associated constant actuating forces of the friction clutch can be achieved.
  • the rotation of the adjusting ring takes place by means of a form fit formed in case of wear between a housing fixedly arranged drive pawl and a spindle mounted on the pressure plate, wherein on the spindle, a pinion is arranged on the outer profile of the drive pawl in the normal state of the friction clutch during the actuation processes, the axial displacement the pressure plate between an open state in which the friction linings of the clutch disc are not in engagement between the counter pressure plate and the pressure plate, and a closed state in which the Friction linings between counter-pressure plate and pressure plate are axially braced and form a frictional engagement with these for transmitting the pending on the friction clutch torque, causing the friction clutch.
  • the distance decreases as wear distance between pressure plate and counter-pressure plate and increases the relative distance between the housing and pressure plate, so that when a predetermined Relativweges during an actuation path of the friction clutch in the direction counterpressure plate moving pressure plate, the drive pawl positively in the outer profile the pinion engages and rotated in a return movement of the pressure plate, the pinion by a predetermined amount.
  • the spindle of the spindle drive is rotated after the following kinematic chain and rotatably mounted on the spindle and radially in the adjusting ring engaging spindle nut moves along the spindle, so that the adjusting ring is rotated by a predetermined amount and thereby the original distance between the lever system and platen is restored.
  • the drive pawl subsequently moves out of the outer profile again and slides on it until the next wear distance is reached.
  • the drive pawl is received axially between the lever system and the housing.
  • the drive pawl is axially elastically displaced in the direction of the housing, wherein the stiffness of the drive pawl is designed so that the force for axially elastic displacement of the drive pawl against the movement of the pressure plate for rotating the pinion larger as is the force to be expended in a conventional adjustment process from the drive pawl to the rotation of the pinion.
  • a suitable axial space must be provided in the housing.
  • a free space for the drive pawl is provided in the area between the plate spring and the housing, which increases the axial space requirement of the friction clutch.
  • the drive pawl is not visible during assembly of an assembly formed from lever system, housing and drive pawl with an assembly formed from the adjusting ring, the pressure plate and the spindle drive, so that it is possibly damaged when contacting with the pinion. Furthermore, from the unpublished German patent application no.
  • a modified friction clutch in which an axial distance for limiting the Axialweges of the drive pawl against the pinion takes place by a spacer pin is placed at a predetermined axial distance on the plate spring. This spacer pin is attached to a biasing spring disposed outside the housing, which also biases the drive pawl axially in the direction of the housing.
  • German patent application no. 10 2010 021 414.0 also discloses a friction clutch in which a limitation of the axial travel of the drive pawl is achieved by means of an axial stop which is arranged on the adjusting ring.
  • the contact pressure of the pressure plate relative to the counter-pressure plate for clamping the friction linings and forming the frictional engagement of the friction clutch is provided by the plate spring.
  • the plate spring force are the pad spring and the restoring force of the energy storage, which connect the pressure plate with the housing axially displaceable and rotationally fixed and axially spaced at an opening of the friction clutch, the pressure plate of the friction linings, for example, opposite leaf springs. While the lining suspension remains the same after initial setting losses substantially over the life of the friction clutch or the clutch disc, the biasing force of the leaf springs increases with increasing wear of the friction linings, thereby weakening the contact force.
  • the object of the invention is to improve a generic friction clutch with a path-controlled wear compensation whose contact force over life, in particular depending on the Reibbelagsverschl employ is constant.
  • the object is achieved by a friction clutch at least consisting of a arranged around a rotation axis housing with a rotatably and axially limited against the action of energy storage to this displaceably arranged pressure plate, which is supported by a plate spring supporting the housing against a fixed to the housing counter pressure plate under tension of friction linings Clutch disc is axially displaceable, solved, which falls below a distance formed in the clamped friction linings between pressure plate and counter-pressure plate between a spindle arranged on the pressure plate with a spindle drive for rotational drive of a pressure plate and disc spring arranged adjusting ring with respect to the pressure plate in the circumferential direction arranged ramps connected pinion gear and a housing on the housing elastically mounted under bias in the direction of pressure plate drive pawl is formed during an actuator movement of
  • a partial compensation of the occurring wear of the friction linings can be provided by a wear-dependent change of the axial path between the pinion and the drive pawl. If this Axialweg namely increased, the Nachstellweg is increased or adjusted more frequently, while at a reduction of the Axialwegs the adjustment paths are less or less frequently adjusted. According to the inventive idea, therefore, the axial travel is changed via the wear.
  • the compensation of the contact force depending on the wear occurring by adjusting the Axialwegs between a arranged on the adjusting Axialantsch and axially fixed to the drive pawl stop sensor is adjusting the Axialwegs between a arranged on the adjusting Axialantsch and axially fixed to the drive pawl stop sensor.
  • the Axialweg the drive pawl relative to the pinion by means of a relative to the drive pawl effective, arranged on the adjusting ring, and depending on the wear of the friction linings adjustable axial limit can be limited.
  • a change of the Axialwegs is provided depending on the contact pressure of the plate spring against the pressure plate and the increasing wear of the friction linings.
  • the relationship between the contact pressure of the plate spring and the position of the plate spring against a contact surface is evaluated by, for example, the angle of attack of the plate spring against the angle of the plate spring in the new state is allowed relative to the adjusting ring.
  • the change of the Axialwegs is achieved according to the inventive idea, for example, by a circumferential stop along the axis of at least one ramp of the adjustment is provided an A- stop stop forming axially relative to the axis of rotation of the friction clutch axially varying heights, so that during the compensation the wear causing rotation of the adjusting ring an axially varying axial path between the axial stop and the non-rotatably mounted on the housing stop sensor is formed.
  • the formation of the Axialwegs on the angle of rotation of the adjusting depends on the course of the contact force on the wear of the friction linings, ie the force curves of the plate spring and the leaf springs between pressure plate and housing and necessary for the compensation of wear-dependent changes of force compensation curve. Accordingly, the Axialweg set by means of the Axialanschlags can be provided on the wear decreasing, so that with increasing wear of the friction linings the adjustment can be linearly or progressively reduced by, for example, the axial stop forming, provided on the adjusting stop area opposite to a slope of the ramp opposite slope having. Alternatively, the axial travel set by means of the axial stop can be designed as a freeform over the wear, so that courses of the force compensation curve adapted to non-linear force courses can be provided.
  • stop areas of different axial height relative to the axis of rotation may be provided, so that the Axialweg can be adapted to component and manufacturing tolerances by the adjusting ring is rotated on its ramps that a stop area with a suitable axial height axially facing the stop probe to form the dimensional axial path.
  • FIG. 2 shows a detail of the friction clutch of FIG. 1 in a view
  • FIG. 3 shows a schematically illustrated section of the adjusting device of the friction clutch of FIG. 1 when new
  • Figure 4 shows a schematically illustrated section of the adjusting device of
  • FIG. 5 shows a diagrammatically represented side view of a stop region of the
  • Figure 6 shows the adjusting ring of Figure 1 in view
  • FIG. 7 shows a detail of the adjusting ring of FIG. 6.
  • FIG. 1 shows the friction clutch 1 arranged around the axis of rotation 4 in partial section with the housing 2 and the counter-pressure plate 3 held firmly against it, against which the pressure plate 6 axially displaceable by the plate spring 5 and non-rotatably connected to the housing 2 Forming a frictional engagement with the friction linings 7 - not shown - - Clutch disc is clamped.
  • the adjusting ring 8 is arranged between the plate spring 5 and the pressure plate 6, which is rotated when detected wear of the spindle drive 9.
  • the pinion 10 connected to a spindle of the spindle drive 9 and the drive pawl 11 received on the housing 2
  • a positive connection is produced if, as a result of the wear, an extended axial travel of the pressure plate 6 with respect to the housing 2 results.
  • the drive pawl 11 is mounted outside of the housing 2, wherein the fastening part 14 of the drive pawl 11 ra- dial aligned and radially inwardly by means of the blind rivet 15 is attached to the housing 2.
  • the drive member 16 is axially folded at the free end of the fastening part 14 and passes through the housing 2 through the window 17.
  • the drive pawl 11 In normal operation, the drive pawl 11 is radially biased against the outer profile 18 as serrations of the pinion 10 and slides on this during the actuation operations of the friction clutch first
  • the drive pawl 1 1 engages positively in the outer profile 18 when the friction clutch 1 is closed and takes on the pinion 10 when the friction clutch 1 is opened. Subsequently, the drive pawl 11 slides back out of the outer profile 18 and an adjustment cycle is completed.
  • the drive pawl 11 relative to the housing 2 is received axially elastic.
  • the biasing spring 19 is placed over the fastening part 14 of the drive pawl 1 and secured together with the fastening part 14 by means of the blind rivet 15 on one side of the housing 2.
  • the biasing spring 19 is then displaced by the stop sensor 20 against its bias against the drive pawl 1 1, when the Axialweg 21, which corresponds to at least one pitch of the outer profile 18, between the directly attached to the adjusting 8 axial stop 22 and the stop sensor 20, for example a Stop plate is used up.
  • the plate spring 5 In the illustrated closed state of the friction clutch 1, the plate spring 5 is clamped against the stop surface 24 of the adjusting ring and acts on the pressure plate 6 with the angle of attack of the disc spring 5 relative to the stop surface 24 dependent plate spring force. This counteracts the pad spring force of the pad spring 27 of the friction linings and the restoring force of the formed as a leaf springs 25 energy storage 26, which spaced the pressure plate 6 at decreasing disc spring force at opening friction clutch 1 of the friction linings 7.
  • the balance of forces between disc spring force of the plate spring 5, pad spring force of the pad spring 27 and restoring force of the leaf springs 25 forms at the contact pressure.
  • the contact pressure changes due to the wear of the friction linings, ie their axial decrease with increasing service life.
  • the stopper portion 23 is mounted on the adjusting ring 8 so that its axial stop 22 viewed in the circumferential direction axially so is varied that depending on the wear different Axialwege 21 are adjusted and thus due to the adjusted with appropriate intensity and frequency of readjustments a uniform contact force on the wear of the friction linings by the position of the plate spring 5 against the stop surface 24 and thus the cup spring force of Diaphragm spring 5 is controlled accordingly.
  • Figure 2 shows a partial view of the friction clutch 1 with the adjusting ring 8, recorded on the pressure plate not shown spindle drive 9 and the housing side received drive pawl 11 and the stop sensor 20.
  • the distributed over the circumference of ramps 13 are on counter ramps of the pressure plate and thus ensure by the spindle drive 9 driven adjusting ring 8 for raising the stop surface 24 relative to the pressure plate.
  • By raising the axial wear of the friction linings is compensated and held the plate spring at a constant position such as angle to the stop surface 24.
  • the wear adjustment as portionwise rotation of the adjusting ring is controlled by means of the drive pawl 1 1 and the axial travel 21 set by means of the stop sensor 20 and the axial stop 22 formed by the abutment portion 23.
  • the pressure plate and thus the adjusting ring 8 is axially displaced relative to the housing and thus with respect to the drive pawl 11.
  • the Axialweg 21 and the stop sensor 20 contacted finally in large disengagement movements the axial stop 22, so that the drive pawl 1 1 against the action of the biasing spring 19 (FIG 1) is taken and a further relative movement between the drive pawl 11 and pinion and thus an inadvertent sensing of wear is prevented.
  • FIGS. 3 and 4 illustrate this schematically for the new condition of a friction clutch shown in FIG. 3 and the wear condition shown in FIG. 4 with maximum wear. While in the new state, the friction linings 7 form their full axial lining thickness 29, they are - as shown in Figure 4 - reduced by the wear gap 28 in the wear state. Consequently, the adjusting ring 8 after a plurality of Nachstellvor- gears compared to the new state relative to the pressure plate 6 is rotated by the maximum angle of rotation.
  • the amount of adjustment by the Axialweg 21, which is formed by the life of the friction clutch is axially constant arranged on the housing stop sensor 20 and arranged on the twisting over the adjusting ring 8 stop region 23 is formed.
  • the axial stop 22 With the slope 30 is on the wear of the friction linings 7 in the embodiment shown above the angle of rotation of the adjusting ring 8 and thus with increasing wear a linear reduction of the axial travel 21, which reduces at maximum wear around the differential path 37 is.
  • Figure 5 shows a section through a schematically illustrated embodiment of an abutment portion 23 which, in comparison to the horizontal line 34, which does not cause a wear path changing axial path, shows a line 35 for forming an axial path continuously decreasing over wear.
  • setting operations of the pad spring suspension 27 can be taken into account, which lead to increasing contact forces, at least at the beginning of the operation of the friction clutch up to average wear conditions, so that the line 36 makes a partial compensation of the slope of the line 35 necessary and Overall slope of the line 36 to form the Axialwegs flat over the closure fails.
  • FIGS. 6 and 7 show the adjusting ring 8 in view or in detail view.
  • the adjusting ring 8 can be punched, for example, from a narrow sheet-metal strip, bent around and then closed or deep drawn ring.
  • the ramps 13 and the radially expanded abutment region 23 with the circumferentially changing axial stop 22 and the abutment surface 24 are produced by means of appropriate forming process, calibrated and preferably manufactured tool falling.
  • the adjusting ring 8 can be massively produced and machined.

Abstract

L'invention concerne un embrayage à friction constitué au moins d'un carter disposé autour d'un axe de rotation, comportant un plateau de pression monté de manière fixe en rotation et à déplacement axial limité contre l'action d'accumulateurs d'énergie, pouvant être déplacé axialement, par un ressort à disques s'appuyant contre le carter, par rapport à un plateau de contre-pression monté de manière solidaire au carter, en sollicitant les garnitures de friction d'un disque d'embrayage. En cas de passage sous une distance, formée lorsque les garnitures de friction sont sollicitées, entre le plateau de pression et le plateau de contre-pression, un engagement est formé entre un pignon ‑ relié à une broche d'un mécanisme à broche disposé sur le plateau de pression et destiné à l'entraînement en rotation d'une bague de réglage disposée entre le plateau de pression et le ressort à disque et pourvue de rampes disposées en direction circonférentielle par rapport au plateau de pression ‑ et un cliquet d'entraînement fixé élastiquement sur le carter avec précontrainte en direction du plateau de pression ; cet engagement est défait pendant un mouvement d'actionnement du plateau de pression par rapport au carter, à la suite d'une rotation relative du pignon au moyen du cliquet d'entraînement. L'invention vise à compenser une force de pression qui se modifie sur la plage d'usure du disque d'embrayage. A cet effet, on compense plus ou moins - en fonction de l'allure de la courbe caractéristique de force de pression - de hauteur de came que l'usure des garnitures effectivement apparue, afin que le point de fonctionnement de l'embrayage soit déplacé de la manière voulue. De même, par une « forme libre » de la rampe de butée, on peut obtenir qu'on compense plus que l'usure des garnitures effectivement apparue jusqu'à une certaine plage, puis moins que l'usure des garnitures effectivement apparue.
PCT/DE2011/000449 2010-05-25 2011-04-26 Embrayage à friction présentant une compensation d'usure à commande proportionnelle à la course WO2011147394A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112011101755.3T DE112011101755B4 (de) 2010-05-25 2011-04-26 Reibungskupplung mit weggesteuerter Verschleißkompensation
CN201180023139.2A CN102884333B (zh) 2010-05-25 2011-04-26 具有行程控制的磨损补偿的摩擦离合器

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE102010021414 2010-05-25
DE102010021414.0 2010-05-25
DE102010035447.3 2010-08-26
DE102010035446 2010-08-26
DE102010035447 2010-08-26
DE102010035446.5 2010-08-26

Publications (1)

Publication Number Publication Date
WO2011147394A1 true WO2011147394A1 (fr) 2011-12-01

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Family Applications (2)

Application Number Title Priority Date Filing Date
PCT/DE2011/000448 WO2011147393A1 (fr) 2010-05-25 2011-04-26 Embrayage à friction avec une compensation d'usure à déplacement commandé et procédé de montage dudit embrayage à friction
PCT/DE2011/000449 WO2011147394A1 (fr) 2010-05-25 2011-04-26 Embrayage à friction présentant une compensation d'usure à commande proportionnelle à la course

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Application Number Title Priority Date Filing Date
PCT/DE2011/000448 WO2011147393A1 (fr) 2010-05-25 2011-04-26 Embrayage à friction avec une compensation d'usure à déplacement commandé et procédé de montage dudit embrayage à friction

Country Status (3)

Country Link
CN (2) CN102884332B (fr)
DE (5) DE112011101755B4 (fr)
WO (2) WO2011147393A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112011101755B4 (de) 2010-05-25 2020-06-04 Schaeffler Technologies AG & Co. KG Reibungskupplung mit weggesteuerter Verschleißkompensation
EP2670994B1 (fr) * 2011-02-04 2015-01-07 Schaeffler Technologies GmbH & Co. KG Dispositif d'embrayage
DE102011018416B4 (de) * 2011-04-21 2020-06-10 Schaeffler Technologies AG & Co. KG Nachstelleinrichtung für eine Reibungskupplung
DE102012201402A1 (de) 2012-02-01 2013-08-01 Schaeffler Technologies AG & Co. KG Reibungskupplungseinrichtung
CN105408650B (zh) * 2013-07-29 2017-11-21 舍弗勒技术股份两合公司 补偿调节装置的斜坡系统用的斜坡环以及用于装配摩擦离合器的方法
DE102015205145A1 (de) 2014-04-17 2015-10-22 Schaeffler Technologies AG & Co. KG Reibungskupplung mit zweiteiliger Anpressplatte
FR3050492B1 (fr) * 2016-04-21 2018-04-27 Valeo Embrayages Dispositif d'embrayage a rattrapage d'usure, notamment pour vehicule automobile
KR101795406B1 (ko) * 2016-06-27 2017-11-08 현대자동차 주식회사 마모 보상장치, 이를 구비한 클러치 액추에이터 유닛, 및 이를 구비한 차량
FR3060685B1 (fr) * 2016-12-19 2019-06-14 Valeo Embrayages Procede de fabrication d'un organe de rattrapage d'usure pour un mecanisme d'embrayage
DE102018103480A1 (de) * 2018-01-17 2019-07-18 Schaeffler Technologies AG & Co. KG Schwenkelement zum schwenkbaren Aufnehmen einer Dämpfervorrichtung
WO2020053385A1 (fr) * 2018-09-13 2020-03-19 Eaton Intelligent Power Limited Système de réglage d'embrayage doté de caractéristiques résistantes à l'usure pour la prévention de la conduite en marche arrière
DE102018131667A1 (de) 2018-12-11 2020-06-18 Schaeffler Technologies AG & Co. KG Reibungskupplung mit einer weggesteuerten Verschleißkompensation

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DE102009005738B4 (de) * 2008-02-13 2015-10-15 Schaeffler Technologies AG & Co. KG Reibungskupplung
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EP1918599A1 (fr) * 2006-10-30 2008-05-07 Valeo Embrayages Embrayage pour véhicules automobiles à dispositif amélioré d'équilibrage de "cordon rampe "
DE102008051100A1 (de) 2007-10-31 2009-05-07 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Reibungskupplung
DE102009055895A1 (de) * 2008-12-18 2010-09-30 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Reibungskupplung

Also Published As

Publication number Publication date
DE102011018591A1 (de) 2012-01-05
WO2011147393A1 (fr) 2011-12-01
CN102884333A (zh) 2013-01-16
DE112011101755B4 (de) 2020-06-04
DE112011101764A5 (de) 2013-03-21
DE102011018592A1 (de) 2011-12-01
CN102884332A (zh) 2013-01-16
CN102884332B (zh) 2016-01-27
DE102011018593A1 (de) 2012-01-05
DE102011018593B4 (de) 2017-06-08
CN102884333B (zh) 2015-06-17
DE112011101755A5 (de) 2013-03-14
DE112011101764B4 (de) 2020-06-10

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