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WO2008138297A1 - Embrayage à friction à auto-ajustage - Google Patents

Embrayage à friction à auto-ajustage Download PDF

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Publication number
WO2008138297A1
WO2008138297A1 PCT/DE2008/000683 DE2008000683W WO2008138297A1 WO 2008138297 A1 WO2008138297 A1 WO 2008138297A1 DE 2008000683 W DE2008000683 W DE 2008000683W WO 2008138297 A1 WO2008138297 A1 WO 2008138297A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
lever
spring lever
friction clutch
pawl
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/DE2008/000683
Other languages
German (de)
English (en)
Inventor
Gerd Ahnert
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 Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
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 LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Priority to DE112008001041.2T priority Critical patent/DE112008001041B4/de
Publication of WO2008138297A1 publication Critical patent/WO2008138297A1/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
    • F16D13/58—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 self-adjusting friction clutch according to the preamble of claim 1.
  • Fig. 6 shows such a per se known arrangement in which the spring lever 10, which has an outer circumferentially continuous annular portion 12 projecting from the radially inwardly resilient tongues 14, via a rotatably connected to the spring lever 10 ramp ring 16 and a relative to the spring lever 10 rotatable ramp ring 18 is supported on the pressure plate 20 a known in its construction and therefore not shown coupling.
  • the rotation of the ramp ring 18 can take place in a manner known per se by means of a drive spring 22 (FIG. 7), which has a radially outer ring part 26 interrupted in the circumferential direction by a gap 24, from which spokes 28 project radially inwards, by means of which the drive spring 23 is fixed to the spring lever 10.
  • a gap 24 adjacent end portion 30 of the drive spring 22 is fixed in the circumferential direction relative to the spring lever 10.
  • the other end portion 32 is circumferentially movable relative to the spring lever 10 and terminates in a pawl 34 which is in one direction force-transmitting engagement with a toothing (not shown in Fig. 6).
  • the attachment of the drive spring 22 to the spring lever 10 is such that the diameter of the ring member 26 depends on the conical deformation of the spring lever 10, so that at a suprathreshold conical deformation of the spring lever 10, for example due to wear of the pads, the pawl 34 not shown toothing overflows, for example, is firmly connected to the rotatable ramp ring 18, and in a subsequent recovery of the spring lever 10 entrains the teeth, so that the ramp ring 18 is rotated in the direction of a wear adjustment. Also known is the possibility that the pawl of the drive spring does not engage directly in a circumferentially extending toothing, but that the adjustment of the ramp ring 18 via a transmission gear.
  • such a transmission gear may have a worm gear mounted on the spring lever or a clutch housing, whose axis of rotation is inclined to the axial direction of the clutch and which is formed with a peripheral toothing, in which engages the pawl in unilaterally force-transmitting manner.
  • An end face of the worm wheel is formed with a spiral toothing, which engages in a rigidly connected to the ramp ring 18 toothing.
  • a peculiarity of such known worm gear is that the worm gear must be exactly positioned relative to the teeth of the ramp ring 18, for example, in which it engages; For example, the worm gearing must engage only on one side of the axis of rotation of the worm wheel in the toothing, otherwise it comes to a deteriorated tooth engagement, wear or even a malfunction. Furthermore, the surface pressure on the tooth engagement is relatively large.
  • the invention has for its object to further develop a generic self-adjusting friction clutch such that the above-mentioned problems of worm gears in the translation between the drive spring and teeth do not occur.
  • a self-adjusting friction clutch comprises a housing, a non-rotatably, but axially limited movably connected pressure plate, by means of which provided with friction plates clutch disc is frictionally engageable with the pressure plate and a counter plate, provided between the housing and the pressure plate, a total annular disc-shaped spring lever with a circumferential radially outer peripheral edge projecting radially inwardly from a plurality of circumferentially spaced spring tongues whose radially inner peripheral edge is axially movable for actuation of the friction clutch, a drive spring approximately concentric with the spring lever having a radially outer annular portion radially inwardly thereof Spokes protrude, by means of which the drive spring is fixed to the spring lever, wherein the drive spring and the lever spring are matched to one another such that the diameter of the annular part of the drive spring changes with a conical deformation of the lever spring due to an axial displacement of the inner peripheral edge, and a wear adjustment with a connected to the ring member pawl
  • the radial movement of the pawl of the drive spring can be achieved in that the annular part of the drive spring is formed continuously in the circumferential direction and has a spoke-free intermediate region on which the pawl is formed.
  • the intermediate region is arranged between two circumferentially spaced, deformable regions.
  • the assembly of spring lever and drive spring is rotatably connected to the housing of the clutch and the spring lever is supported via a rotationally fixed and a rotatable ramp ring on the pressure plate.
  • the pawl engages in a drive pinion of a threaded spindle mounted on the rotationally fixed ramp ring, which is in engagement with a nut mounted on the rotatable ramp ring.
  • the spring lever may be secured by means of circumferentially spaced rivets to the clutch housing, to which rivets on the side facing away from the clutch housing side of the spring lever, a support ring is mounted, between which and the spring lever, the drive spring is arranged on the support ring and radially inwardly of the rivets supported on the spring tongues of the spring lever.
  • the drive spring is advantageously designed such that its spokes connect a circumferentially closed, radially inner ring part to the radially outer ring part.
  • FIG. 1 is a schematic view of a half section through relevant for the execution of the invention parts of a friction clutch
  • FIG. 2 is a perspective view of a drive spring with pawl and ramp rings
  • FIG. 3 is a plan view of the arrangement of FIG. 2 with rivets inserted
  • FIG. 5 is a perspective view similar to FIG. 2 with additionally existing spring lever and pressure plate,
  • Fig. 6 is a view similar to Fig. 5 but without the means for rotational adjustment of the ramp rings, a known friction clutch and
  • Fig. 7 is a plan view of a drive spring according to the prior art.
  • a friction clutch has an overall spring-type lever 10 which is in the form of a plate-spring and which, in a manner known per se, has an outer ring area or circumferential area. has edge 12, protrude from the radially inwardly resilient tongues 14.
  • the spring lever 10 is mounted in the region of the roots of the spring tongues 14 on rivets 36 which are rigidly connected to a cover or housing 38 of the coupling.
  • the radially outer region of the peripheral edge 12 is supported on a pressure plate 20 via a first ramp ring 16, connected rotatably to the spring lever 10 or the housing 38, and a second ramp ring 18 rotatable relative to the first ramp ring 16, with which in a manner known per se a not shown, provided with friction linings clutch disc can be pressed against a counter-plate.
  • the ramp ring 18 is preferably rotatable relative to the pressure plate 20 and the pressure plate 20 is axially displaceable relative to the housing 28, but fixed in the circumferential direction.
  • the rivets 36 are formed with stepped diameter and have a central, formed with a larger diameter portion on which is mounted on two axially spaced wire bearings of the spring lever 10.
  • the pressure plate 20 facing wire bearing is supported on an intermediate disc 40 which is supported at a stage between the central portion of the rivet 36 and a smaller diameter portion and between the and a head 42 of the rivet 36, a support ring 44 is clamped.
  • Supported on the support ring 44 is a drive spring 22, which is visible in plan view in FIG. 4 and which has an outer, circumferentially continuous ring member 46 which is connected via spokes 48 with a radially inner ring member 50 closed in the circumferential direction.
  • the outer ring member 46 and the inner ring member 50 each have a spoke-free intermediate region 52 and 54, wherein the intermediate region 52 of the radially outer ring member 46 is preferably formed deformable than the spoked region of the radially outer ring member 46 and advantageously via targeted deformable portion 56 and 58 is connected to the spoked portion of the outer ring member 46. From the intermediate portion 52 is radially outwardly a pawl 60 before.
  • the radially inner ring member 54 is supported, as shown in FIG. 1, via a ring bearing 62 on the spring tongues 14 of the spring lever 10 from.
  • the pawl In order to implement this radial movement of the pawl 60 connected to an actuation of the clutch into a relative rotation between the ramp rings 16 and 18 (the ramp ring 16 is in the region in which the pawl 60 or the intermediate region 52 extends radially outside the ramp ring 18) , recessed), the pawl cooperates with a drive pinion 64 of a threaded spindle 66 which is mounted on a projection of the rotatable fixed to the spring lever 10 ramp ring 16.
  • the threaded spindle 66 which is mounted substantially immovably in the projection 68 in the circumferential direction of the ramp ring 16, engages with its external thread a nut 70 which is immovably and immovably fixed in the circumferential direction on a projection 72 which is rigidly connected to the rotatable ramp ring 18 ,
  • the peripheral toothing of the drive pinion 64 is formed as a sawtooth, so that the pawl 60 can overflow the peripheral teeth in a movement of the pawl of FIG. 1 down and on their return upward the drive pinion 64 and thus the threaded spindle Turned 66 in FIG. 1 counterclockwise direction.
  • FIG. 3 shows a plan view of the assembly showing the intermediate discs 40 of the rivets 36 holding radially inwardly directed tongues 74 of the support ring 44 formed with through holes 76 penetrated by the rivets 36.
  • FIG. 5 shows the arrangement according to FIG. 2, but additionally with the pressure plate 20 and the spring lever 10.
  • the nut 70 can be rotatably mounted on the projection 68 and provided with external teeth, so that it takes over the function of the drive pinion.
  • the threaded spindle 66 is then rotatably mounted on the projection 72, but mounted immovably in the circumferential direction and meshes with an internal thread of the nut.
  • the spindle gear can be arranged between the cover of the clutch and an adjusting ring or between the pressure plate and an adjusting ring.
  • the ramp rings can also be arranged between the clutch housing and the spring lever. It may also be a rotation of the spring lever, with integrated Ram pen lake can be formed relative to the lid, which is formed with corresponding counter-ramps.

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 à auto-ajustage comprenant un ressort d'entraînement (22) servant à compenser l'usure, qui est connecté à un levier de ressort (10) réalisé sous forme de ressort Belleville, de telle sorte qu'un cliquet (60) disposé sur le ressort d'entraînement se déplace dans la direction radiale en cas de variation du diamètre du ressort d'entraînement.
PCT/DE2008/000683 2007-05-14 2008-04-21 Embrayage à friction à auto-ajustage Ceased WO2008138297A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112008001041.2T DE112008001041B4 (de) 2007-05-14 2008-04-21 Selbstnachstellende Reibungskupplung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007022539.5 2007-05-14
DE102007022539 2007-05-14

Publications (1)

Publication Number Publication Date
WO2008138297A1 true WO2008138297A1 (fr) 2008-11-20

Family

ID=39590229

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2008/000683 Ceased WO2008138297A1 (fr) 2007-05-14 2008-04-21 Embrayage à friction à auto-ajustage

Country Status (2)

Country Link
DE (2) DE112008001041B4 (fr)
WO (1) WO2008138297A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015201674A1 (de) 2014-02-07 2015-08-27 Borgwarner Inc. Selbstnachstellende kupplungsgegendruckplatte
CN108930725A (zh) * 2018-09-25 2018-12-04 上海萨克斯动力总成部件系统有限公司 膜片弹簧离合器的盖总成装置

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010051254B4 (de) * 2009-11-26 2019-09-05 Schaeffler Technologies AG & Co. KG Reibungskupplung mit Verschleißkompensation
DE102011015279A1 (de) 2010-04-14 2011-10-20 Schaeffler Technologies Gmbh & Co. Kg Nachstellbare Reibungskupplung
CN103154547B (zh) * 2010-07-22 2016-01-27 舍弗勒技术股份两合公司 调整装置
JP5911515B2 (ja) * 2011-02-04 2016-04-27 シェフラー テクノロジーズ アー・ゲー ウント コー． カー・ゲーＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ クラッチ装置
DE102011010340B4 (de) * 2011-02-04 2020-01-30 Schaeffler Technologies AG & Co. KG Kupplungsvorrichtung
DE102012221322A1 (de) 2012-11-22 2014-05-22 Schaeffler Technologies Gmbh & Co. Kg Verbindung einer Zwischenscheibe mit einem Bauteil
WO2015144154A2 (fr) * 2014-03-25 2015-10-01 Schaeffler Technologies AG & Co. KG Mécanisme à broche pour dispositif de rattrapage à commande proportionnelle à la course
EP2933515A3 (fr) * 2014-04-17 2016-05-25 Schaeffler Technologies GmbH & Co. KG Embrayage à friction doté d'un plateau de pression en deux parties
DE102014211035A1 (de) 2014-06-10 2015-12-17 Schaeffler Technologies AG & Co. KG Spindelbetrieb für eine weggesteuerte Nachstelleinrichtung und Reibkupplung mit einer derartigen Nachstelleinrichtung
DE102014213095A1 (de) 2014-07-07 2016-01-07 Schaeffler Technologies AG & Co. KG Reibungskupplung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2753503A1 (fr) * 1996-09-17 1998-03-20 Valeo Embrayage a friction a dispositif de rattrapage d'usure, notamment pour vehicule automobile
EP1568905A1 (fr) * 2004-02-24 2005-08-31 LuK Lamellen und Kupplungsbau Beteiligungs KG Embrayage à réglage automatique

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2753503A1 (fr) * 1996-09-17 1998-03-20 Valeo Embrayage a friction a dispositif de rattrapage d'usure, notamment pour vehicule automobile
EP1568905A1 (fr) * 2004-02-24 2005-08-31 LuK Lamellen und Kupplungsbau Beteiligungs KG Embrayage à réglage automatique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015201674A1 (de) 2014-02-07 2015-08-27 Borgwarner Inc. Selbstnachstellende kupplungsgegendruckplatte
CN108930725A (zh) * 2018-09-25 2018-12-04 上海萨克斯动力总成部件系统有限公司 膜片弹簧离合器的盖总成装置

Also Published As

Publication number Publication date
DE112008001041A5 (de) 2010-01-21
DE102008019947A1 (de) 2008-11-20
DE112008001041B4 (de) 2018-08-02

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