WO2014127775A1 - Butée de débrayage - Google Patents

Butée de débrayage Download PDF

Info

Publication number
WO2014127775A1
WO2014127775A1 PCT/DE2014/200035 DE2014200035W WO2014127775A1 WO 2014127775 A1 WO2014127775 A1 WO 2014127775A1 DE 2014200035 W DE2014200035 W DE 2014200035W WO 2014127775 A1 WO2014127775 A1 WO 2014127775A1
Authority
WO
WIPO (PCT)
Prior art keywords
flange
shoulder
bearing ring
ring
clutch
Prior art date
Application number
PCT/DE2014/200035
Other languages
German (de)
English (en)
Inventor
Steffen BREUN
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
Publication of WO2014127775A1 publication Critical patent/WO2014127775A1/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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F16D25/083—Actuators therefor

Definitions

  • the invention is concerned with a clutch release bearing, as used for example for the actuation of shift disconnect couplings in motor vehicles.
  • a particular aspect of the invention is directed to the angle compensation between the transmission input shaft and the disconnect clutch or the output shaft of the drive unit.
  • a shift disconnect clutch which interrupts the power flow in the drive train.
  • this is realized in such a way that a frictional engagement between the friction partners of the shift disconnect clutch is canceled by an axial movement of an axial adjuster.
  • IE this is achieved by providing a clutch release bearing between the transmission and the shift clutch, which comprises an inner race, an outer race and rolling elements, the outer race arranged coaxially with the inner race and the rolling elements in the annular space between the two races Unroll raceways provided by the bearing rings.
  • the drive unit, the shift disconnect clutch and the transmission are integrally buildable components that have all their tolerances fluctuating dimensions, can not be ruled out that after assembly to a radial offset and an angular offset between the drive unit and the transmission, at which usually also the clutch release bearing is attached comes.
  • Radial misalignment is generally addressed by providing self-centering.
  • the stationary bearing ring is provided with a flange which engages radially movably in a groove of another, likewise stationary component.
  • this segment inevitably increases the axial extent of the release bearing.
  • the mobility for compensating the angular offset is limited by the clamping of the outer bearing ring with the segment.
  • special precautions must be taken to exclude a wear-increasing co-rotation of the segment at least when disengaging.
  • the invention is therefore based on the object to provide a Kupplungsaus Wegla- ger, which is very compact and allows compensation of a large angular offset.
  • each shoulder has a contact surface, with which the first shoulder is in physical contact with the second shoulder, and at least one of the contact surfaces has a convex contour, the angle compensation is completely displaced into the interior of the clutch release bearing, whereby space is saved.
  • a further component reduction or simplification is given when the ring element either forms the second shoulder itself or receives it.
  • the cohesion is improved when the ring member has at its edge facing away from the flange of the inner bearing ring spring tongues, which rest on the side of the first shoulder, which faces away from the flange of the inner bearing ring.
  • the free mobility of the two, the angle compensation ensuring shoulders is not limited if the free ends of the Federzun- gene with convex, projecting in the direction of the axis of rotation abutment surfaces are provided and if the spring tongues exclusively with the contact surfaces with the side of the first shoulder in physical contact occur, which faces away from the flange of the inner bearing ring.
  • FIG. 2 is a clutch release bearing in detail;
  • FIG. 3 shows a detail A according to FIG. 2;
  • FIG. 4 shows a variant of the detail A according to FIG. 3;
  • Fig. 5 shows a further variant
  • FIGS. 6 shows a side view of a ring element according to FIGS. 2 and 3
  • This periphery which corresponds to the installation situation in a motor vehicle, is essentially formed by a hydraulic actuating device 2 and a clutch 3. If the clutch pedal 2.1 is actuated, pressure is built up in the connecting line 2.2 and transmitted to a piston, which is arranged inside the clutch release bearing 1, of an axial adjuster located centrically to the rotational axis R (not shown in FIG. 1).
  • the shift disconnect clutch 3 is essentially formed by a pressure plate 3.1, a flywheel 3.2, a friction disc 3.3 and a diaphragm spring 3.4. If the outer bearing ring 4 of the clutch release bearing 1 is then moved by the action of the central axial adjuster in FIG. 1 to the right against the diaphragm spring 3.4 resting against the outer bearing ring 4, the pressure plate 3.1 lifts off from the friction disk 3.3 and the force flow transmitted to the shaft 3.5 via the flywheel 3.2 is interrupted (all not shown in FIG. 1).
  • the clutch release bearing 1 is formed by an outer bearing ring 4, an inner bearing ring 5 and rolling elements 6, wherein the rolling elements 6 between the races 4, 5 are provided by the races 4, 5 Roll raceways 7.1, 7.2.
  • the central axial adjuster 9 which is connected to the supply line 2.2, is annular and is arranged and fixed concentrically to the axis of rotation R. Integral part of the zen-trale
  • Axialverstellers 9 is a piston 10, which closes a pressure chamber 1 1, in which the supply line opens 2.2. If pressure is then built up by actuation of the clutch pedal 2.1 (FIG. 1), the piston 10 moves out of the pressure chamber 11 (indicated in FIG. 3 by the arrow P).
  • the inner bearing ring 4 facing the end 12 of the piston 10 is provided with a first shoulder 13.1.
  • the flange 8.2 of the inner bearing ring 5 engages in a groove 14 which is provided by a ring member 15 extending in the axial direction.
  • a plate spring 16 is provided, which is supported in the groove 14 and the flange 8.2 presses against one of the walls 17 of the groove 14.
  • This type of axial fixation causes a radial offset of the shaft 3.5 (Fig. 1) and the flywheel 3.2 (Fig. 1) offset this offset by a radial movement of the flange 8.2 in the groove 14.
  • the ring element 15 which is formed from sheet metal, is connected to a second shoulder 13.2, which extends from the flange 8.2 in the direction of the axial adjuster 9.
  • This shoulder 13.2 is provided with a contact surface 18.1, which has a convex or curved contour, wherein the zenith Z of the curvature points in the direction of the axis of rotation R and is in physical contact with the newly formed contact surface 18.2 of the first shoulder 13.1.
  • spring tongues 20 are provided at the edge 19 of the ring element 15, which points in the direction of the central axial adjuster 9, which engage around the first shoulder 8.1, as shown in FIG - are snapped. So that the spring tongues 20 do not hinder a relative movement between the two shoulders 8. 1, 8. 2 or their contact surfaces 18. 1, 18. 2 known as angular displacement, the spring tongues 20 are protruding at their free ends 21 in the direction of the axis of rotation R, spherical or rounded projections Provided 22 which rest on the side of the shoulder 13.1, which faces away from the inner bearing ring 5.
  • a side view of a ring element 15 corresponding to FIG. 3 is illustrated in more detail in FIG. 6. This illustration can be taken that the groove 14 is circumferential and the edge 19 is uniform with spring tongues 20 understand.
  • the variant according to FIG. 4 differs from the embodiment according to FIG. 3 in that there no ring element 15 is provided between the flange 8.2 and the second shoulder 13.2 and instead the shoulder 13.2 is formed directly on the flange 8.2. Only for the sake of completeness it should be stated that in order to reduce the number of components, the shoulder 13.2 and the flange 8.2 can also form an integral unit.
  • the connection between the flange 8.2 and the shoulder 13.1 is also formed by a simple-shaped ring member 15 which is pushed onto the shoulder 13.2 and secured in this position.
  • the spring tongues 20 are substantially straight, although the
  • the embodiment according to FIG. 5 differs from the embodiment according to FIG. 3 only in that in order to improve the mobility of the shoulders 13.1, 13.2, the contact surface 18.2 of the shoulder 13.1, with which it is in physical contact with the shoulder 13.2, is crowned or rounded profile.
  • both contact surfaces 18.1, 18.2 may be coated with a sliding coating, for example made of Teflon.

Landscapes

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

Abstract

La présente invention concerne une butée de débrayage, du type utilisé par exemple pour actionner des embrayages de changement de vitesse de véhicules à moteur. selon l'invention, pour assurer la compensation d'un décalage angulaire entre par exemple un embrayage de changement de vitesse (3) et une boîte de vitesses, pour des systèmes de débrayage comportant un dispositif de débrayage central ou un dispositif de déplacement axial (9), l'extrémité (12) du piston (10) du dispositif de déplacement axial (9) qui est dirigée vers l'embrayage de changement de vitesse (3) possède un premier épaulement (13.1) et la bride (8.2) de la bague de roulement intérieure fixe (8.2) possède un second épaulement (13.2). L'un au moins des deux épaulements (13) en contact physique présente un contour arrondi ou sphérique.
PCT/DE2014/200035 2013-02-25 2014-02-03 Butée de débrayage WO2014127775A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013203016.9A DE102013203016A1 (de) 2013-02-25 2013-02-25 Kupplungsausrücklager
DE102013203016.9 2013-02-25

Publications (1)

Publication Number Publication Date
WO2014127775A1 true WO2014127775A1 (fr) 2014-08-28

Family

ID=50184709

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2014/200035 WO2014127775A1 (fr) 2013-02-25 2014-02-03 Butée de débrayage

Country Status (2)

Country Link
DE (1) DE102013203016A1 (fr)
WO (1) WO2014127775A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016212284A1 (de) * 2016-07-06 2018-01-11 Schaeffler Technologies AG & Co. KG Kupplungsausrückanordnung
DE102018005150A1 (de) 2018-06-29 2020-01-02 Fte Automotive Gmbh Zentralausrücker für eine Kupplungsbetätigung
DE102019115178A1 (de) * 2019-06-05 2020-12-10 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Betätigungsmechanismus für einen Kupplungssteller mit mehrteiligem Betätigungselement

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4565272A (en) * 1983-02-12 1986-01-21 Nippon Seiko Kabushiki Kaisha Self-aligning type clutch release apparatus
DE19912432A1 (de) 1998-03-20 1999-09-23 Luk Lamellen & Kupplungsbau Ausrücklager
DE10114844A1 (de) * 2001-03-24 2002-09-26 Ina Schaeffler Kg Selbsteinstellendes Kupplungsausrücklager
DE602005002726T2 (de) * 2004-12-30 2008-08-07 Renault S.A.S. Hydraulische Kupplungsvorrichtung mit synchronisiertem Kolben

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4565272A (en) * 1983-02-12 1986-01-21 Nippon Seiko Kabushiki Kaisha Self-aligning type clutch release apparatus
DE19912432A1 (de) 1998-03-20 1999-09-23 Luk Lamellen & Kupplungsbau Ausrücklager
DE10114844A1 (de) * 2001-03-24 2002-09-26 Ina Schaeffler Kg Selbsteinstellendes Kupplungsausrücklager
DE602005002726T2 (de) * 2004-12-30 2008-08-07 Renault S.A.S. Hydraulische Kupplungsvorrichtung mit synchronisiertem Kolben

Also Published As

Publication number Publication date
DE102013203016A1 (de) 2014-08-28

Similar Documents

Publication Publication Date Title
EP2310702B1 (fr) Embrayage double
EP3069037B1 (fr) Ensemble embrayage
WO2015144157A1 (fr) Système à double embrayage et cylindre récepteur concentrique (csc) avec montage sur palier axial comportant un talon pour recevoir le csc et chaîne de transmission
DE102017104458A1 (de) An ihrem steuerungssystem gestützte nasse doppelkupplung
DE102015205832A1 (de) Axiale Lamellenkupplung
EP2880330A1 (fr) Unité à piston/cylindre d'un système hydraulique
DE102017104949A1 (de) Nasse doppelkupplung mit zur begrenzung des hubs der kolben des steuerungssystems geeigneten sicherheitsanschlägen
EP1808612B1 (fr) Butée de débrayage d'un véhicule automobile
WO2014127775A1 (fr) Butée de débrayage
EP2529127B1 (fr) Dispositif de désaccouplement pour des embrayages de véhicules
EP2554868B2 (fr) dispositif de débrayage
DE102015220266A1 (de) Ausrücklager
DE102007054290A1 (de) Ausrücklager für eine Schalttrennkupplung eines Kraftfahrzeugs
EP2280183B1 (fr) Embrayage de friction tiré doté d'un actioneur intégré
DE102017119722B3 (de) Kupplungsnehmerzylinder
DE102016202300A1 (de) Deckelanordnung für eine Reibungskupplung
DE102017110213A1 (de) Schirmring mit Federfunktion und Eigenzentrierung für Kupplungsnehmerzylinder
DE102014225788A1 (de) Selbstnachstellende Kupplung mit federzungenaufweisendem Rampenring zur Reduzierung des Drop-Offs
DE102014218964B3 (de) Reibkupplung
EP2899419B1 (fr) Embrayage à disques
DE102013221836A1 (de) Deckelanordnung für eine Reibungskupplung sowie Verfahren zum Betätigen einer Reibungskupplung
DE102013218723A1 (de) Deckelanordnung für eine Reibungskupplung
WO2011141013A1 (fr) Dispositif d'accouplement
WO2011137888A1 (fr) Débrayeur pour embrayage tiré
DE102016210670A1 (de) Kupplungsanordnung

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14706779

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 14706779

Country of ref document: EP

Kind code of ref document: A1