WO2011147393A1 - Embrayage à friction avec une compensation d'usure à déplacement commandé et procédé de montage dudit embrayage à friction - Google Patents

Embrayage à friction avec une compensation d'usure à déplacement commandé et procédé de montage dudit embrayage à friction Download PDF

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Publication number
WO2011147393A1
WO2011147393A1 PCT/DE2011/000448 DE2011000448W WO2011147393A1 WO 2011147393 A1 WO2011147393 A1 WO 2011147393A1 DE 2011000448 W DE2011000448 W DE 2011000448W WO 2011147393 A1 WO2011147393 A1 WO 2011147393A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure plate
housing
adjusting ring
friction clutch
stop
Prior art date
Application number
PCT/DE2011/000448
Other languages
German (de)
English (en)
Inventor
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 DE112011101764.2T priority Critical patent/DE112011101764B4/de
Priority to CN201180023134.XA priority patent/CN102884332B/zh
Publication of WO2011147393A1 publication Critical patent/WO2011147393A1/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 and a method for mounting them at least consisting of a housing with a rotatably and axially limited to this displaceably arranged pressure plate, which is axially displaceable by a bearing on the housing plate spring against a fixed housing back pressure plate under tension of friction linings of a clutch disc , Wherein falling below a distance formed in the case of strained friction linings between the pressure plate and counterpressure plate, a form fit between a arranged with a spindle of a pressure plate on the spindle drive for rotary drive arranged between pressure plate and plate spring adjusting ring connected to the pressure plate in the circumferential direction ramps connected pinion gear and one on the housing elastically formed under bias in the direction of pressure plate drive pawl is formed and during an actuating movement of the pressure plate relative to the Housing is solved after a rotation of the pinion 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 pressure plate 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 is not engaged between Counter-pressure plate and pressure plate are, 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 to limit the Axialweges the drive pawl against the pinion is done by a distance pin is placed at a predetermined ⁇ xialabstand on the plate spring. This spacer pin is attached to a biasing spring arranged outside the housing, which also axially biases the drive pawl in the direction of the housing.
  • Lifting the pressure plate with the adjusting ring creates a relative path between the drive pawl and the stroke of the pressure plate, so that the drive pawl is moved to another tooth of the pinion and thus can sense an uncontrolled adjustment, so that the adjusting ring can adjust without existing wear when closing the friction clutch.
  • 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. A simple calibration possibility of the axial stop is not disclosed.
  • the object of the invention is therefore to develop a friction clutch with wegenfiner wear compensation and a method for assembling this to the effect that during installation, an adjustment of the axial stop is made possible in a simple manner and cost-effective, if possible without further components.
  • a friction clutch at least consisting of a housing with a rotatably and axially limited to this displaceable pressure plate, which is axially displaceable by a plate spring supported on the housing against a housing fixedly arranged counter-pressure plate under tension of friction linings of a clutch disc, wherein at If the distance between the pressure plate and the counterpressure plate that is formed in the case of strained friction linings falls below a positive connection between a spindle drive arranged with a spindle of a spindle drive arranged on the pressure plate for the rotational drive of an adjusting ring arranged between the pressure plate and disc spring, with respect to the during an actuating movement of the pressure plate relative to the housing by a rotation of the pinion by means of the drive pawl is released and an axial travel of the drive pawl relative to the pinion by means of a relative to the drive pawl effective, arranged on the adjusting ring, adjustable during assembly of the friction clutch axial stop is limited.
  • the geometry provided on the housing for the drive pawl can remain unchanged and only by means of the adjusting ring the axial distance to the drive pawl or a component fixedly connected thereto axially, for example a stop feeler made of sheet metal and the like is adjusted.
  • an abutment region can be provided which is axially displaceable relative to the adjusting ring, for example by means of screws, or the abutment region can be plastically deformed.
  • the adjusting ring distributed over the circumference has a plurality of radially extended abutment regions, arranged axially at different heights relative to a rotational axis of the adjusting ring and forming the axial stops. In this way, additional components can be avoided. Different axial heights of a stop area for adjusting the axial travel of the adjusting ring to the drive pawl can be provided in one piece on the adjusting ring and are selected by simply rotating the adjusting ring to the appropriate number of stop areas without further processing steps and interference with the adjusting ring.
  • a number of ramps equal to or greater than the number of axial stops is sufficient to allow sufficient resolution of the Axialwegs.
  • six distributed over the circumference impact areas of different axial height are provided. If the axial travel is, for example, 2 to 3 mm, it can be resolved by six stop zones of different heights and the same gradation and a fault tolerance of one millimeter already in the range of 170 micrometers.
  • the adjusting ring has, in addition to the ramps and abutment areas for the axial stop a profile range with which the spindle nut of the spindle drive forms a positive connection to rotatably displace the adjusting ring upon rotation of the pinion and thereby on the spindle of the spindle drive spindle nut. It has proved to be advantageous in this case if the abutment regions each have a profile region which comes into positive engagement with a spindle nut of the spindle drive.
  • the profile region can be formed as a cutout in each stop region into which an axially extending at least the maximum tolerance band of all stop regions driving profile engages, so that regardless of the axial height of each selected for calibration stop area a secure fit between the adjusting and spindle nut is formed ,
  • the adjusting ring is preferably made in one piece from sheet metal and can be stamped from a narrow sheet-metal strip and bent to ring shape and closed, the stop areas are folded.
  • the adjusting ring can be punched in one piece and closed from sheet metal, wherein the ramps and abutment areas are formed by forming, for example by means of a deep-drawing process.
  • the object is further achieved by a method for mounting a friction clutch according to the features described in the application documents, the method being characterized by the following features:
  • both subassemblies - the housing and the pressure plate - each on a flat surface which may for example correspond to the position of the counter-pressure plate, be added.
  • the corresponding dimensions can be determined and transferred to the later assembly.
  • the plate spring can be biased in the housing so that both their operating force adjusted at the operating point and its position relative to the adjusting ring and the corresponding dimensions and forces can be removed.
  • FIG. 2 shows the adjusting ring used in the friction clutch of FIG. 1 in a view
  • FIG. 5 shows a subassembly of the housing of the friction clutch of FIG. 1
  • 6 shows a sub-assembly of the pressure plate of the friction clutch of Figure 1.
  • 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 fastened outside the housing 2, wherein the fastening part 14 of the drive pawl 11 is radially aligned and radially inwardly by means of the blind rivet 15 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 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 11 engages positively in the outer profile 18 with the friction clutch 1 closed and takes when opening the friction clutch 1, the pinion 10 with.
  • the biasing spring 19 is then displaced by the stop sensor 20 against its bias against the drive pawl 11 when the Axialweg 21, which corresponds to at least one pitch of the outer profile 18, between the attached directly to the adjusting 8 axial stop 22 and the spacer plate 20 is used up.
  • the drive pawl 11 with the pinion 10 when a Abhubterrorism the pressure plate 6 of the counter-pressure plate 3 after exhaustion of the Axialwegs 21, the drive pawl 11 with the pinion 10.
  • the axial travel 21 is subject to deviations that are set during assembly to a constant amount. For this purpose, if appropriate, the axial position of the arranged on the adjusting ring 8 axial stop 22 is corrected, so that the housed in the housing 2 components such as drive pawl 11 with biasing spring 19 and stop sensor require no additional calibration.
  • radially expanded abutment portions 23 are provided which form the stop sensor 20 facing axial stops 22 which have relative to the axis of rotation 4 axially different heights, so that upon rotation of the adjusting ring 8 by a pitch the abutment regions 23 a stop region 23 providing a suitable axial stop 22 can be selected.
  • the adjusting ring 8 is applied for rotation in the adjusting by an axially on rotation of the spindle of the spindle drive 9 ( Figure 1) on the spindle displaced spindle nut, which by means of a driving profile in each of the stop areas 23i, 23 2 , 23 3 , 23, 23 5 , 23 6 provided in the form of the cutout 25 and only apparent from Figure 2 profiling 26 positively engages.
  • Figure 5 shows the subassembly 27 with the housing 2, the drive pawl 11, the stopper sensor 20 and the plate spring 5.
  • the housing 2 is mounted on the mounting plate 29 having an axial calibration point 30, which is substantially the surface of the counterpressure plate 3 to be mounted later ( Figure 1) corresponds.
  • the calibration is completed and the two sub-assemblies 27, 28 are joined, for example by means of leaf springs for axially displaceable and rotationally fixed recording of the pressure plate 6 on the housing 2, for example riveted.
  • the adjusting ring 9 is rotated until the stop area 23 ! , 23 2 , 23 3 , 23 4 , 23 5 , 23 6 (FIGS. 2 to 4), which sets the best approximation to the ideal axial travel.
  • the operating point adjustment is performed again by rotating the adjusting ring 9 relative to the pressure plate 6 along the ramps 13 and counter ramps 12. Finally, the sub-assemblies 27, 28 are joined.

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 et un procédé de montage dudit embrayage à friction qui est au moins constitué d'un carter comportant une plaque de pression, qui est montée de manièreimmobile en rotation et de manière à pouvoir être déplacée de manière limitée dans le sens axial et qui, moyennant le serrage des garnitures de friction d'un disque d'embrayage, peut être déplacée axialement par rapport à une plaque de contre-pression solidaire du carter, par une rondelle ressort prenant appui sur le carter. Lorsque la distance, formée par les garnitures de friction en position serrée, entre la plaque de pression et la plaque de contre-pression devient inférieure à une valeur définie, il se forme un assemblage par conjugaison de forme entre un pignon, lequel est relié à une broche d'un entraînement à broche agencé sur la plaque de pression pour l'entraînement en rotation d'une bague de réglage, agencée entre la plaque de pression et la rondelle ressort et munie de plans inclinés agencés dans la direction circonférentielle par rapport à la plaque de pression, et un cliquet d'actionnement fixé de manière élastique au carter moyennant une précontrainte vers la plaque de pression ; ledit assemblage par conjugaison de forme se désolidarise pendant un mouvement de manœuvre de la plaque de pression par rapport au carter, à la suite d'une rotation du pignon au moyen du cliquet d'actionnement. Pour pouvoir régler aisément et sans sollicitation en vibrations le déplacement axial du cliquet d'actionnement, celui-ci est limité dans son déplacement par rapport au pignon au moyen d'une butée axiale disposée sur la bague de réglage, agissant à l'encontre du cliquet d'actionnement et réglable pendant le montage de l'embrayage à friction.
PCT/DE2011/000448 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 WO2011147393A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112011101764.2T DE112011101764B4 (de) 2010-05-25 2011-04-26 Reibungskupplung mit weggesteuerter Verschleißkompensation und Verfahren zu deren Montage
CN201180023134.XA CN102884332B (zh) 2010-05-25 2011-04-26 具有行程控制的磨损补偿的摩擦离合器及其装配方法

Applications Claiming Priority (6)

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

Publications (1)

Publication Number Publication Date
WO2011147393A1 true WO2011147393A1 (fr) 2011-12-01

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ID=44501838

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

Family Applications After (1)

Application Number Title Priority Date Filing Date
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

Country Status (3)

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CN (2) CN102884332B (fr)
DE (5) DE102011018592A1 (fr)
WO (2) WO2011147393A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011018591A1 (de) 2010-05-25 2012-01-05 Schaeffler Technologies Gmbh & Co. Kg Reibungskupplung mit weggesteuerter Verschleißkompensation
WO2012103866A1 (fr) * 2011-02-04 2012-08-09 Schaeffler Technologies AG & Co. KG Dispositif d'embrayage

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102014213498A1 (de) * 2013-07-29 2015-01-29 Schaeffler Technologies Gmbh & Co. Kg Rampenring für ein Rampensystem einer Nachstelleinrichtung sowie Verfahren zur Montage einer Reibungskupplung
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
US11441615B2 (en) * 2018-09-13 2022-09-13 Eaton Intelligent Power Limited Clutch adjustment system with wear resistant features for back driving prevention
DE102018131667A1 (de) 2018-12-11 2020-06-18 Schaeffler Technologies AG & Co. KG Reibungskupplung mit einer weggesteuerten Verschleißkompensation

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
WO2010020205A1 (fr) * 2008-08-21 2010-02-25 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Embrayage à friction
DE102010051254A1 (de) * 2009-11-26 2011-06-01 Schaeffler Technologies Gmbh & Co. Kg Reibungskupplung mit Verschleißkompensation

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2739158B1 (fr) * 1995-09-21 1997-11-28 Valeo Embrayage a friction a dispositif de rattrapage de jeu, notamment pour vehicule automobile
CN201050559Y (zh) * 2007-04-12 2008-04-23 广西工学院 自动补偿摩擦片磨损的汽车离合器
DE102008018860A1 (de) * 2007-05-14 2008-11-20 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Reibungskupplung mit integriertem Verschleißausgleich
DE102009005738B4 (de) * 2008-02-13 2015-10-15 Schaeffler Technologies AG & Co. KG Reibungskupplung
DE102009055895B4 (de) * 2008-12-18 2019-12-19 Schaeffler Technologies AG & Co. KG Reibungskupplung mit Nachstelleinrichtung
DE102010045791B4 (de) 2009-10-12 2017-06-22 Schaeffler Technologies AG & Co. KG Reibungskupplung mit weggesteuerter Verschleißkompensation
DE102010054247A1 (de) * 2009-12-21 2011-06-22 Schaeffler Technologies GmbH & Co. KG, 91074 Verfahren zur Einstellung einer selbstnachstellenden Reibungskupplung
DE102011018592A1 (de) 2010-05-25 2011-12-01 Schaeffler Technologies Gmbh & Co. Kg Reibungskupplung mit weggesteuerter Verschleißkompensation und Verfahren zu deren Montage

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
WO2010020205A1 (fr) * 2008-08-21 2010-02-25 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Embrayage à friction
DE102010051254A1 (de) * 2009-11-26 2011-06-01 Schaeffler Technologies Gmbh & Co. Kg Reibungskupplung mit Verschleißkompensation

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011018591A1 (de) 2010-05-25 2012-01-05 Schaeffler Technologies Gmbh & Co. Kg Reibungskupplung mit weggesteuerter Verschleißkompensation
WO2012103866A1 (fr) * 2011-02-04 2012-08-09 Schaeffler Technologies AG & Co. KG Dispositif d'embrayage
US8789675B2 (en) 2011-02-04 2014-07-29 Schaeffler Technologies AG & Co. KG Clutch device

Also Published As

Publication number Publication date
CN102884333A (zh) 2013-01-16
CN102884332B (zh) 2016-01-27
DE102011018593A1 (de) 2012-01-05
CN102884332A (zh) 2013-01-16
DE102011018593B4 (de) 2017-06-08
DE112011101764A5 (de) 2013-03-21
DE112011101764B4 (de) 2020-06-10
CN102884333B (zh) 2015-06-17
WO2011147394A1 (fr) 2011-12-01
DE112011101755A5 (de) 2013-03-14
DE112011101755B4 (de) 2020-06-04
DE102011018591A1 (de) 2012-01-05
DE102011018592A1 (de) 2011-12-01

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