EP2861883A1 - Embrayage à friction - Google Patents

Embrayage à friction

Info

Publication number
EP2861883A1
EP2861883A1 EP13727094.8A EP13727094A EP2861883A1 EP 2861883 A1 EP2861883 A1 EP 2861883A1 EP 13727094 A EP13727094 A EP 13727094A EP 2861883 A1 EP2861883 A1 EP 2861883A1
Authority
EP
European Patent Office
Prior art keywords
spring
pressure plate
servo
force
friction clutch
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP13727094.8A
Other languages
German (de)
English (en)
Inventor
Christophe Reichert
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 EP2861883A1 publication Critical patent/EP2861883A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/583—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 a drive shaft of a motor vehicle engine can be coupled to a transmission input shaft of a motor vehicle transmission.
  • a friction clutch for coupling a drive shaft of a
  • Motor vehicle engine with a transmission input shaft of a motor vehicle transmission provided with a counter-plate for introducing a torque, a relative to the counter-plate displaceable pressure plate for frictionally pressing a clutch disc for discharging the torque, a connected to the counter-plate clutch cover for at least partially covering the pressure plate, a pivotally supported on the clutch cover lever spring, in particular plate spring, for displacing the pressure plate and a, in particular designed as a lever spring servo spring to reduce a force required for displacing the pressure plate by an actuating system applied operating force during wear, wherein the servo spring is supported on a first force edge on the clutch cover and on a second edge of force on the lever spring.
  • the servo spring can be supported on the clutch cover and the lever spring, it is particularly not necessary to provide a bolt bolted to the pressure plate, so that the friction clutch can be manufactured with a low design effort, with an increase in an operating force at wear by the servo spring at least partially compensated. In particular, it is possible to reduce the number of components and / or to save machining operations, in particular production of an internal thread in the pressure plate. Furthermore, the servo spring can act substantially directly on the lever spring, so that between the servo spring and the lever spring provided intermediate components can be saved in the power flow. This avoids that intermediate components due to their own elastic behavior under the influence of force can affect the spring effect applied by the servo spring on the lever spring.
  • the servo spring exerts a spring force on the pressure plate, so that the pressure plate can pass this spring force to reduce the operating force in the wear area to the lever spring.
  • the power flow between the servo spring and the lever spring can be guided past the pressure plate, so that there is a cost-effective and space-saving design for the friction clutch.
  • the maximum operating force to be provided for actuating the friction clutch can be reduced so that an actuating system for generating the actuating force can be dimensioned to be smaller and less bulky. It is possible that the smaller space requirement for the actuating system does not lead to an increased space requirement for the remaining friction clutch.
  • the servo spring is designed such that the servo spring builds up an increasingly strong spring force with an increasingly strong wear of friction linings in the unactuated state of the friction clutch, which points in the direction of the actuating force. If, during an actuation of the friction clutch, the lever spring sweeps over an increasingly larger pivoting path with ever increasing wear on the clutch disc, a part of the force required to displace the pressure plate over an ever increasing stroke can be provided by the servo spring be, so that in particular an increase in the actuation force, for example by setting up the lever spring designed as a plate spring, can be compensated.
  • the servo spring can be configured in particular as a plate spring.
  • the servo spring can be designed for this purpose, for example, as a circumferential conical ring.
  • the servo spring has radially outwardly and / or radially inwardly projecting lugs, which form the first force edge or the second force edge.
  • the servo spring can, for example, have a circumferential, conical annular disk spring area, which in particular provides a large part of the spring action of the servo spring.
  • the lever spring can in particular have radially inwardly projecting spring tongues, which preferably protrude from a circumferential ring, wherein the servo spring can be supported with the protruding lugs on the spring tongues of the lever spring.
  • the radial position of the respective force margin can be easily adjusted.
  • the spring properties of the servo spring can be adjusted by low design and manufacturing effort.
  • the counterplate of the friction clutch can be configured, in particular, by a flywheel, which can be non-rotatably connected to, for example, a crankshaft of an automobile engine.
  • a flywheel which can be non-rotatably connected to, for example, a crankshaft of an automobile engine.
  • the friction clutch for a double clutch, wherein the counter-plate can be formed in particular by a common central plate of the double clutch, so that this central plate can form a counter-plate on both axial sides for a respective friction clutch.
  • the clutch cover is preferably fixedly connected to the counter-plate, for example by screwing or riveting.
  • the coupling disc provided in the axial direction between the pressure plate and the counterplate can be non-rotatably connected to the transmission input shaft, for example via spline teeth.
  • the clutch disc may in particular have friction linings which wear over their service life and can thereby become thinner.
  • the clutch disc has a lining suspension for the friction linings, which allow a smooth closing of the friction clutch and in particular provide a spring force for opening the friction clutch in the closed state of the friction clutch.
  • a return spring connected to the pressure plate and the clutch cover or the counter plate for positioning the attachment. press plate in an open position, when no pressure is applied to the pressure plate of the lever spring provided.
  • the pressure spring may follow the lever spring by the return spring when the lever spring is in position by an actuating force applied to the lever spring by the actuating system
  • the return spring is particularly preferably fastened to the pressure plate by means of a spacer bolt fixedly connected to the pressure plate, for example by plastic deformation, for example by a corresponding opening in the clutch cover through the clutch cover be guided to the outside, so that a projecting from the bolt stop can strike on reaching the clutch of a predetermined maximum wear at the wear area end of the friction linings Tandbolzen a transport lock are formed, which can prevent unintentional relative movement of the pressure plate to the counter plate before mounting the friction clutch in a drive train of a motor vehicle.
  • the lever spring can in particular be pivoted about a ring-shaped pivot point, wherein the annular circumferential pivot point is preferably defined by at least one supported on the clutch cover wire ring.
  • the first force edge contacts the clutch cover and / or the second force edge the lever spring. Due to the direct contact of the servo spring with the clutch cover and / or with the lever spring intermediate components can be saved, so that a small number of components and a simple construction of the friction clutch is made possible.
  • the friction clutch can be designed as a drawn normally closed friction clutch. This makes it possible in particular to provide the pivot point for the lever spring radially outward to a contact point of the lever spring on the pressure plate.
  • the servo spring can thereby be particularly easily attacked without additional significant space requirements significantly spaced from the pivot point of the lever spring on the lever spring, so that there is a correspondingly large spring travel for the servo spring by the lever effect of the lever spring.
  • the first force edge of the servo spring is arranged radially outside the second force edge of the servo spring.
  • the servo spring can thereby be supported radially on the outside of the clutch cover and radially inward on the lever spring. This makes it easier to design the servo spring, in particular in a drawn normally closed friction clutch, as a compression spring, which can be designed in particular as a space-saving plate spring.
  • the first force edge of the servo spring is located on an inner side of the clutch cover and the second force edge of the servo spring is located on a pressure plate side of the lever spring facing the pressure plate.
  • the servo spring can thereby be positioned substantially completely within the friction clutch, so that no additional space for the friction clutch is required.
  • the servo spring can be supported on a provided between the lever spring and the pressure plate and / or counter plate part of the clutch cover.
  • the servo spring may be completely provided within a space bounded by the clutch cover and the counter plate. The inside of the clutch cover points to a limited by the clutch cover and the counter plate space in which the pressure plate is provided.
  • the lever spring can cover the approach of the holding hook.
  • the lever spring in particular recesses in order to pass the retaining hooks through the lever spring can.
  • the lever spring after passing the holding hook in the circumferential direction be twisted so that at the same time a captive for the lever spring in the clutch cover is formed by the retaining hook.
  • the retaining hook can be used as a stop for a maximum permissible pivot position of the lever spring.
  • the servo spring is preferably arranged completely in a radial region which can be covered by the pressure plate.
  • the radially inner and radially outer boundary of the radial region can be defined by the first force edge and the second force edge. Viewed in the axial direction, the pressure plate can completely cover the servo spring.
  • the radial space requirement of the friction clutch is thus not determined by the servo spring, so that no additional radial space is required for the servo spring.
  • the pressure plate has at least one cam for engagement with the lever spring on a contact radius, wherein the second force edge of the servo spring contacts the lever spring substantially on the contact radius.
  • both the force flow between the lever spring and the pressure plate and the power flow between the lever spring and the servo spring can take place on a substantially common radius.
  • a part of the servo spring, which forms the second force edge is arranged between two cams or a cam between two parts of the servo spring which form the second force edge, so that an anti-twist arrangement results which prevents a relative rotation of the servo spring to the pressure plate or at least limited.
  • the servo spring has a guided through openings in the clutch cover and the lever spring spring hook for supporting the servo spring on the lever spring, wherein in particular the spring hook via a support element, in particular a wire ring, is supported on the lever spring.
  • the servo spring can be designed as a ring closed in the circumferential direction, so that in particular only exactly one servo spring is sufficient.
  • the support member By the support member, the servo spring can be supported on the facing in the mounting direction to the pressure plate back of the lever spring.
  • the spring hook can be clipped for this purpose in particular with a closed wire ring.
  • the servo spring may, in particular, have a cup spring region which is conical in the manner of a cup spring.
  • the spring hooks can protrude substantially in the axial direction of the disc spring area.
  • the disc spring area can thereby be provided substantially completely on the outside of the clutch cover.
  • a kinematically inverted design is also possible, in which the cup spring region is provided with the second force edge substantially completely on the pressure plate side of the lever spring and the spring hook is supported with the first force edge, in particular by means of a support member on the clutch cover.
  • the invention further relates to a clutch assembly for coupling a drive shaft of an automotive engine having at least one transmission input shaft of a motor vehicle transmission with at least one friction clutch, which may be off and on as described above and an actuating system for actuating the at least one friction clutch.
  • the clutch unit is in particular as a double clutch with two friction clutches for coupling the drive shaft with a first transmission input shaft and / or a second transmission input shaft, wherein preferably the counter plates for both friction clutches are formed by a common central plate.
  • FIG. 1 is a schematic sectional view of a friction clutch in a first embodiment
  • FIG. 2 is a schematic exploded perspective view of the friction clutch of FIG. 1,
  • FIG. 3 shows a schematic sectional view of a friction clutch in a second
  • FIG. 4 is a schematic exploded perspective view of the friction clutch of Fig. 3 and
  • the friction clutch 10 shown in FIG. 1 has a counter-plate 12 and a pressure plate 14 which is displaceable relative to the counter-plate 12 in order to be able to press a friction plate 16 containing friction plate 16 frictionally to close the friction clutch 10.
  • a clutch cover 20 is screwed to which an annular ring pivot forming a ring 22 designed as a slotted plate spring lever spring 24 is pivotally supported for displacing the pressure plate 14.
  • the lever spring 24 abut a protruding cam 36 of the pressure plate 14.
  • a return spring 28 designed as a leaf spring, which moves the pressure plate 14 away from the counter plate 12 when substantially no axial force acts on the pressure plate 14.
  • the servo spring 32 With a radially inner second force edge 38, the servo spring 32 is radially spaced from the ring 22 supported on a pressure plate 14 facing the pressure plate side 40 of the lever spring 24.
  • the lever spring 24 In a wear of the friction linings 16, the lever spring 24 is pivoted with the friction clutch 10 in a position in which the servo spring 32 has set up stronger and applies a spring force in the direction of the actuating force 30 on the lever spring 24, so that a correspondingly lower actuation force 30 for Opening the friction clutch 10 is required.
  • the servo spring 32 is disposed entirely within a bounded by the counter-plate 12 and the clutch cover 20 space.
  • the servo spring 32 rests with its first force edge 36 on an inner side 42 of the clutch cover 20, wherein the servo spring 32 is supported by the retaining hook 34 in a region of the inner side 42 facing away from the counter-plate 12.
  • the servo spring 32 may have a plurality of radially projecting lugs 44, through which the first force edge 36 and the second force edge 38 can be formed.
  • the lugs 44 forming the second force edge 38 can be provided on a comparable radius as the cams 26 of the pressure plate 14, in order to form an anti-twist device.
  • the servo spring 32 is not on the inside 42 but on an outside 46 of the coupling in comparison to the embodiment of the friction clutch 10 shown in FIGS. 1 and 2.
  • Lungsdeckels 20 supported.
  • the servo spring 32 has a guided through the clutch cover 20 and the lever spring 24 spring arm 48 which is connected to a wire ring 50, for example by clipping, to be supported on the Anpressplattenseite 40 of the lever spring 24.
  • a formed by the clutch cover 20 holding hook 34 is not required in this case.

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 destiné à accoupler un arbre d'entraînement d'un moteur de véhicule automobile et un arbre d'entrée d'une boîte de vitesses de véhicule automobile, comprenant un contre-plateau (12) servant à induire un couple, un plateau de pression (14) déplaçable par rapport au contre-plateau pour presser par friction un disque d'embrayage afin d'évacuer le couple, un couvercle d'embrayage relié au contre-plateau et destiné à recouvrir au moins en partie le plateau de pression, un ressort de levier (24) appuyé pivotant sur le couvercle d'embrayage (20), en particulier un ressort à diaphragme, pour déplacer le plateau de pression et un servo-ressort (32), réalisé notamment sous forme de ressort de levier, destiné à réduire une force d'actionnement pouvant être appliquée par un système d'actionnement et nécessaire au déplacement du plateau de pression en cas d'usure, le servo-ressort s'appuyant par un premier bord de force (36) sur le couvercle d'embrayage et par un second bord de force (38) sur le ressort de levier. Etant donné que le servo-ressort peut s'appuyer sur le couvercle d'embrayage et le ressort de levier, il n'est pas nécessaire notamment de prévoir un boulon vissé au plateau de pression, de sorte que l'embrayage à friction peut être fabriqué avec une complexité de conception minimale.
EP13727094.8A 2012-06-14 2013-05-29 Embrayage à friction Withdrawn EP2861883A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012209992 2012-06-14
PCT/EP2013/061003 WO2013186046A1 (fr) 2012-06-14 2013-05-29 Embrayage à friction

Publications (1)

Publication Number Publication Date
EP2861883A1 true EP2861883A1 (fr) 2015-04-22

Family

ID=48576977

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13727094.8A Withdrawn EP2861883A1 (fr) 2012-06-14 2013-05-29 Embrayage à friction

Country Status (4)

Country Link
EP (1) EP2861883A1 (fr)
CN (1) CN104379955B (fr)
DE (2) DE112013002928A5 (fr)
WO (1) WO2013186046A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190114283A (ko) * 2018-03-29 2019-10-10 주식회사평화발레오 펄크럼 링 센터링 기능을 구비한 클러치 어셈블리

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105518328B (zh) 2013-09-06 2018-03-27 舍弗勒技术股份两合公司 摩擦离合器装置
DE102014216277A1 (de) 2013-09-30 2015-04-02 Schaeffler Technologies Gmbh & Co. Kg Reibungskupplungseinrichtung
DE112015002026A5 (de) * 2014-04-28 2017-02-23 Schaeffler Technologies AG & Co. KG Deckelanordnung für eine Reibungskupplung
CN105864310B (zh) * 2015-01-23 2020-07-28 舍弗勒技术股份两合公司 用于摩擦离合器的具有凸块结构的模块式压板
KR20180063257A (ko) * 2015-10-05 2018-06-11 섀플러 테크놀로지스 아게 운트 코. 카게 마찰 클러치
DE102015219734B3 (de) * 2015-10-12 2017-02-02 Schaeffler Technologies AG & Co. KG Deckelanordnung für eine Reibungskupplung und Kraftfahrzeug
DE102016125101A1 (de) 2016-12-21 2018-06-21 Schaeffler Technologies AG & Co. KG Reibungskupplung

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JP3489939B2 (ja) * 1996-06-13 2004-01-26 株式会社エクセディ クラッチカバー組立体
FR2866397A1 (fr) * 2004-02-18 2005-08-19 Valeo Embrayages Embrayage a mecanisme perfectionne et procede de montage de cet embrayage
JP4667222B2 (ja) 2005-12-09 2011-04-06 株式会社エクセディ クラッチカバー組立体
CN101512178B (zh) * 2006-08-31 2011-08-31 卢克资产管理有限责任公司 用于操作具有自补偿调节装置的摩擦离合器的装置
DE102007053724A1 (de) * 2006-12-16 2008-06-19 Zf Friedrichshafen Ag Kupplungsvorrichtung
WO2010000217A1 (fr) * 2008-07-03 2010-01-07 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Accouplement par friction
WO2011088857A1 (fr) * 2010-01-20 2011-07-28 Volkswagen Aktiengesellschaft Unité embrayage

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None *
See also references of WO2013186046A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190114283A (ko) * 2018-03-29 2019-10-10 주식회사평화발레오 펄크럼 링 센터링 기능을 구비한 클러치 어셈블리
KR102051211B1 (ko) 2018-03-29 2019-12-02 주식회사평화발레오 펄크럼 링 센터링 기능을 구비한 클러치 어셈블리

Also Published As

Publication number Publication date
CN104379955B (zh) 2017-12-08
WO2013186046A1 (fr) 2013-12-19
CN104379955A (zh) 2015-02-25
DE112013002928A5 (de) 2015-03-12
DE102013209993A1 (de) 2013-12-19

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