WO2019149308A1 - Agencement d'actionnement muni d'un carter de cylindre récepteur assemblé sans vis et centré, ainsi que système d'embrayage - Google Patents

Agencement d'actionnement muni d'un carter de cylindre récepteur assemblé sans vis et centré, ainsi que système d'embrayage Download PDF

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Publication number
WO2019149308A1
WO2019149308A1 PCT/DE2019/100012 DE2019100012W WO2019149308A1 WO 2019149308 A1 WO2019149308 A1 WO 2019149308A1 DE 2019100012 W DE2019100012 W DE 2019100012W WO 2019149308 A1 WO2019149308 A1 WO 2019149308A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
slave cylinder
region
receiving portion
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.)
Ceased
Application number
PCT/DE2019/100012
Other languages
German (de)
English (en)
Inventor
Gerrit Volz
Thomas Niesen
Manuel BAßLER
Sebastian LATZER
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
Priority to DE112019000663.0T priority Critical patent/DE112019000663A5/de
Publication of WO2019149308A1 publication Critical patent/WO2019149308A1/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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • 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
    • 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
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/12—Mounting or assembling

Definitions

  • the invention relates to an actuating arrangement for a clutch of a motor vehicle, such as a car, truck, bus or other commercial vehicle, with a slave cylinder, wherein the slave cylinder further comprises a housing and a piston slidably received in the housing along a longitudinal axis, and with a The housing (of the slave cylinder) and the receiving portion are axially supported relative to one another and radially aligned relative to each other via insertion areas axially projecting into one another / pushed into one another.
  • the invention relates to a coupling system for a drive train of a motor vehicle with a clutch and this acting on the clutch actuator assembly.
  • WO 2013/007 231 A1 a disengagement device for a friction clutch, with an actuator for the axial actuation of the friction clutch.
  • a carrier element serves with an integrated attachment point for supporting the actuator on a clutch bell.
  • the fastening element only needs to be placed on one of the two insertion regions so that, when the insertion regions are inserted into one another, they come together for axial fixation. There is no need Anschraubvor- direction on the tape, as before, necessary. This simplifies assembly.
  • the production effort is also significantly reduced, since a receptacle for the fastening element, if at all, is to be provided only at one of the two insertion areas. It can therefore be dispensed with separate screws, which brings a further cost savings.
  • the solution is self-centering via force equilibrium / fit, as a result of which it is also possible to eliminate screw-on lugs / spacer sleeves on the housing.
  • the fastening element is pressed in radially between the first insertion region and the second insertion region (radially).
  • a non-positive connection of the two insertion areas / the pressure housing and the Receiving section by generating a radial force realized particularly simple.
  • the fastener needs to be placed only one of the two insertion areas during assembly. When inserting the two insertion areas into each other, it thus automatically comes to generating sufficient force to implement the frictional connection.
  • the fastening element rests against one of the two insertion regions or at both insertion regions exclusively by means of friction / adhesion (that is to say with the generation of a frictional force / adhesive force). As a result, the manufacturing cost is further reduced.
  • the receiving portion is preferred (scherinteiliger or separate and fixed) component of a clutch bell.
  • the fastening element is of annular design, a connection which is as uniform as possible over the circumference is produced between the two insertion regions.
  • first insertion region and the second insertion region are radially supported relative to each other via a fit (designed as a sliding fit, for example).
  • the fastening element is then more preferably received with radial clearance or in turn radially compressed between the two insertion areas.
  • the fastening element is designed as a seal, which is pressed tightly in the radial direction both at the first insertion region and at the second insertion region, an additional sealing of a fluid supply of the slave cylinder is implemented in a simple manner.
  • the fastening element is designed as an O-ring / O-ring seal.
  • the fastening element is inserted in a radially (inwardly or outwardly) open recess (preferably designed as a groove / annular groove) of the first insertion region or of the second insertion region. As a result, a mounting position of the fastening element is simply determined.
  • the first insertion region is provided directly on a radial inner side or on a radial outer side of a chamber region of the housing of the slave cylinder which accommodates the piston or on a projection region (of the housing of the slave cylinder) projecting axially from the chamber region.
  • the housing of the slave cylinder is particularly simple and compact.
  • the projection region can be positioned relative to the receiving section individually and thus in turn be made compact in the axial direction.
  • the latter is located directly on a radial inner side or on a radial outer side of the (preferably tubular) receiving section or on a radial (preferably inwardly or outwardly pointing) shoulder of the receiving section.
  • ter is further preferably formed by a frontally open receiving space in the receiving section, is provided. This saves additional space.
  • the slave cylinder is defined in all directions of movement secured relative to the receiving portion.
  • an anti-twist device it is particularly expedient for an anti-twist device to be realized by a form-locking connection between the housing and the receiving section.
  • a corresponding nose on the receiving portion or the housing engages positively in a corresponding recess in the other component of the housing and of the receiving portion.
  • This nose can in turn also be replaced by a separate pin, which is then arranged in a form-fitting manner in respective recesses in the housing and in the receiving section.
  • a fluid supply to a pressure chamber formed between the housing and the piston has an axially open connection and / or a channel extending transversely to the longitudinal axis on the side of the housing of the slave cylinder.
  • the invention relates to a clutch system for a drive train of a motor vehicle, with a clutch, which is preferably designed as a friction clutch, and an actuator assembly according to the invention according to at least one of the previously described embodiments.
  • the slave cylinder acts in operation in a typical manner during its operation for engagement and disengagement of the clutch.
  • a slave cylinder attachment to the clutch bell is realized without screws.
  • the CSC housing (housing of the slave cylinder) is fastened to the clutch bell via a radially compressed O-ring (/ fastening element, preferably designed as a seal).
  • O-ring / fastening element, preferably designed as a seal.
  • FIG. 1 shows a longitudinal sectional illustration of an actuating arrangement according to the invention according to a first exemplary embodiment, wherein a housing of a slave cylinder forms a projection area which is fastened to a receiving section of a clutch bell via a fastening element,
  • FIG. 2 shows a detailed representation of the area marked "II" in FIG. 1 between the receiving section and the projection area, wherein the fastening element can also be seen in detail
  • FIG. 3 is a longitudinal sectional view of an actuator assembly according to the invention according to a second embodiment, which differs substantially by providing a conical inner surface at the projection portion of the first embodiment,
  • FIG. 4 shows a longitudinal sectional representation of an actuating arrangement according to the invention in accordance with a third exemplary embodiment, the projection area now being compared with the two first exemplary embodiments of FIGS. 1 to 3 is no longer supported radially from the inside, but radially from the outside at the receiving portion via the fastening element,
  • FIG. 5 is an enlarged view of a half-section of FIG. 4,
  • FIG. 6 shows a longitudinal section of an actuating arrangement according to the invention according to a fourth exemplary embodiment, wherein a chamber region of the housing of the slave cylinder is inserted directly into the receiving section and the fastening element is arranged directly on a radial outer side of this chamber region,
  • FIG. 7 is an enlarged view of a half-section of FIG. 6, 8 shows a longitudinal sectional illustration of an actuating arrangement according to the invention in accordance with a fifth exemplary embodiment, wherein, in contrast to the exemplary embodiment, FIGS. 6 and 7, the chamber area is pushed with its radially inner side directly onto a shoulder of the receiving section and the fastening element is arranged directly on this radial inner side of the chamber area,
  • FIG. 9 is an enlarged view of a half-section of Fig. 8,
  • FIG. 1 wherein the sectional plane is offset relative to FIG. 1 such that a fluid supply of the slave cylinder can be seen, and wherein this fluid supply is implemented by an axial connection to the housing, FIG.
  • FIG. 11 shows a detailed view of a longitudinally cut actuating arrangement according to the invention in a sixth embodiment in the region of the fluid supply of the slave cylinder, the fluid supply having a channel extending transversely to the longitudinal axis as compared to FIG.
  • FIG. 12 shows a perspective view of the actuating arrangement according to FIG. 6, where a rotation lock provided between the housing and the receiving section can be seen,
  • FIG. 13 shows an exploded perspective view of the housing and the receiving section, as they are used in FIG. 12, wherein the shape of a nose realizing the anti-rotation lock and a recess formed corresponding to the nose can be seen,
  • FIG. 14 shows a perspective illustration of an actuating arrangement according to the invention in accordance with a seventh exemplary embodiment, wherein the position of a pin which rotates the housing relative to the receiving section can be recognized, and 15 is a detail view of the longitudinally cut actuator assembly of FIG. 14, wherein the cutting plane is placed so that the pin and its receptacle on the part of the housing and the receiving portion are well recognizable bar.
  • the actuating arrangement 1 has a slave cylinder 2 as well as a receiving section 6 arranged fixed to the transmission housing or fixed to the clutch housing.
  • This receiving portion 6 is stoffeinteiliger part of a clutch bell 37 having a transmission housing.
  • the further gear housing is not shown in detail for the sake of clarity.
  • the actuating arrangement 1 thus represents a combination of a slave cylinder 2 with a gear housing section in the form of the receiving section 6.
  • a friction clutch is also provided in a receiving space enclosed by the clutch bell 37 used, wherein the slave cylinder 2 actuation acts on this friction clutch.
  • the slave cylinder 2 is designed as a concentric slave cylinder 2 (CSC / "Concentric Slave Cylinder").
  • the slave cylinder 2 is implemented here as a fluidic, namely hydraulic slave cylinder 2.
  • the slave cylinder 2 is holistic annular and extends continuously around its imaginary longitudinal axis 4 around.
  • a housing 3 (also referred to as a slave cylinder housing) of the slave cylinder 2 has a chamber portion 13 receiving a piston 5 of the slave cylinder 2 displaceable in the axial direction (i.e., along the longitudinal axis 4).
  • the piston 5 projects out of the housing 3 through an axial opening 25.
  • the pressure chamber 21 can be subjected to pressure during operation in order to displace the piston 5 from its retracted position shown in FIG. 1 into an extended position and thus along an actuating bearing 24 of the slave cylinder 2 which cooperates displaceably with the piston 5 to move the longitudinal axis 4.
  • the actuating bearing 24 is designed as a roller bearing and acts during operation in a typical manner adjusting the friction clutch.
  • the chamber region 13 has a disc-shaped bottom 26, which forms a planar contact surface 27.
  • the housing 3 is axially supported on an end face 28 of the tube-shaped in this embodiment receiving portion 6.
  • the receiving portion 6 forms a circumferential paragraph.
  • the housing 3 furthermore has a projection region 14 protruding axially from the chamber area 13.
  • the projection portion 14 is formed annularly.
  • the projection region 14 extends away from an axial side of the chamber region 13 facing away from the piston 5 / actuating bearing 24.
  • the projection region 14 adjoins a radial inner side 11 of the chamber region 13 at this.
  • the projection portion 14 extends from a radial inner side 11 of the chamber portion 13 in the axial direction of the chamber portion 13 away.
  • the projection region 14 forms a first insertion region 7, which is inserted into a second insertion region 8 formed by the receiving section 6. ben is.
  • the second insertion region 8 is formed by a radial inner side 15 of the receiving section 6.
  • the two plug-in areas 7 and 8 thus form a shaft-hub connector.
  • Characterized the housing 3 is aligned relative to the longitudinal axis 4 and thus relative to the receiving portion 6, which is coaxial with the longitudinal axis 4, centered.
  • a fastening element 9 is pressed radially between the two insertion areas 7 and 8 / supported on both insertion areas 7 and 8 under prestressing.
  • the two insertion regions 7 and 8 are prevented from moving relative to one another in the axial direction by means of a frictional connection.
  • a fastening element 9 is dispensed with a radial compression of the fastener 9 and instead the two slide-in areas 7 and 8 via a fit (push fit) inserted into each other.
  • both the radial compression of the fastening element 9 and the fit (push fit) between the insertion regions 7, 8 are realized.
  • the fastening element 9 is formed as a ring.
  • the fastening element 9 is round / elliptical in cross-section.
  • the fastening element 9 is therefore implemented as an O-ring.
  • the fastening element 9 consists of an elastomeric material.
  • the fastening element 9 is therefore elastically compressible.
  • the annular fastening element 9 10 is received in a recess 10 of the first insertion region 7.
  • the recess 10 is introduced from radially outside / opened outwards in the radial direction.
  • the recess 10 is realized as a groove, namely as an annular groove.
  • a fluid supply 20 is shown in a further section, so that a fluid supply 20 can be seen.
  • the fluid supply 20 has an axial connection 22.
  • This axial connection 22 is formed, in particular, by a channel of the fluid supply 20 which axially penetrates the bottom 26.
  • a seal to the environment then takes place through the trained as a seal / sealing ring fastener 9 with.
  • a chamber seal 30 is present.
  • the chamber seal 30 is likewise designed as a sealing ring and inserted into a bore 31 of the connection 22.
  • the fluid supply 20 is used to connect the pressure chamber 21 with a master cylinder, which is not shown here for the sake of clarity, in operation.
  • the fastening element 9 does not necessarily have to be arranged in a recess 10 on the part of the first insertion region 7 / of the projection region 14, but can also be arranged in principle according to further embodiments in a recess on the part of the second insertion region 8 / receiving section 6 , Also, in a further embodiment, a plurality of fastening elements 9 are provided, which are then preferably arranged axially next to one another.
  • FIG. 3 illustrates a second embodiment which is slightly modified compared to the first exemplary embodiment.
  • the projection portion 14 is made somewhat shorter in the axial direction as compared with the first embodiment.
  • the projection region 14 in this embodiment has a conical inner flank 29.
  • the projection region 14 and thus the first insertion region 7 on a radial outer side 12 of the chamber region 13.
  • the projection region 14 then extends away from the chamber region 13 in the axial direction from the radial outer side 12 of the chamber region 13.
  • the second insertion region 8 is implemented directly by a radial outer side 16 of the receiving section 6.
  • the projection region 14 / first insertion region 7 therefore lies firmly against the fastening element 9 on a radial outer side 16 of the receiving section 6.
  • the first insertion region 7 can in principle also be formed directly through the chamber region 13.
  • the housing 3 is even formed entirely without projection area 14.
  • the first insertion region 7 is formed directly by the radial outer side 12 of the chamber region 13.
  • the recess 10 in this embodiment is also formed directly on the radial outer side 16 of the chamber area 13.
  • the receiving portion 6 forms a radial shoulder 17, which surrounds the chamber portion 13 radially from the outside.
  • the second insertion region 8 is formed by a radial inner side 15 of the shoulder 17.
  • the fastening element 9 is in turn pressed against the inside 15.
  • the shoulder 17 is formed, in particular, by introducing a receiving space 18 which is open axially towards the slave cylinder 2.
  • the second insertion region 8 is formed by a shoulder 17 arranged radially on the receiving section 6, inside the housing 3.
  • the receiving portion 6 axially / frontally to the slave cylinder 2 towards channel-shaped, wherein the radially inner shoulder 17 forms the second insertion region 8 radially outward.
  • the first insertion area 7 is not as shown in FIGS. 6 and 7 formed directly by a radial outer side 16, but by a radial inner side 11 of the chamber portion 13.
  • the fluid supply 20 of the respective exemplary embodiment does not necessarily have to be designed according to FIG.
  • the fluid supply 20 has a transversely to the longitudinal axis 4 extending channel 23.
  • This channel 23 is formed by a nozzle portion 32, which is formed directly with the housing 3 (one-piece material).
  • the Fign. 12 and 13 exemplarily for the embodiment of FIG. 6 illustrates a rotation. This rotation is preferably provided in each embodiment.
  • a positive connection 19 is provided, which realizes this rotation.
  • the positive connection 19 is formed in the receiving section 6 by a projection 33 projecting radially outward from the housing 3 and a recess 34 formed complementary to the projection 33.
  • the nose 33 extends in a peripheral region in the radial direction from the outside 12 to the outside.
  • the recess 34 is designed as a frontally open recess and formed complementary to the nose 33 shaped.
  • the nose 33 is positively received in the mounted state in the rotational direction in the first recess 34 without play, so that the housing 3 is fixed against rotation relative to the receiving portion 6.
  • FIGS. 14 and 15 show an alternative to this form-locking connection 19.
  • the nose 33 of FIG. 12 and 15 is a separately molded from the housing 3 and the receiving portion 6 element in the form of a pin 35 used to prevent rotation.
  • the pin 35 protrudes in the axial direction into both a (first) recess 34 of the receiving portion 6 and into a (second) recess 36 of the housing 3.
  • the pin 35 is received in the recesses 34 and 36 each against rotation and thus serves to implement the rotation.
  • the CSC (slave cylinder 2) with one or more O-rings 9 is pressed into the clutch or transmission bell 37 (as is the case, inter alia, in FIGS. 1 and 2).
  • this assembly achieves that the CSC 2 is axially fixed by the pretensioning of the O-ring 9 and, on the other hand, the O-ring 9 is centered by the uniform compression of the CSC 2.
  • the function of the centering can also be done via a fit, in this case the O-ring 9 serves only for axial fixation in the installation space.
  • FIGS. 1 and 2 shown.
  • the O-rings 9 are hereby inserted in an O-ring seat (recess 10) (FIG.
  • This compression serves for the axial fixation of the releaser 2.
  • the CSC housing 3 is centered over the O-rings 9. This centering sets itself by a balance of power.
  • a fit between CSC housing 3 and the bell geometry above or below the O-ring seat is provided for centering.
  • the (compressed) O-ring 9 serves exclusively for the axial fixation of the CSC 2 during transport / assembly. It is possible to mount the O-ring 9 on the inside or outside diameter (inside 11 or outside 12) of the release housing 3 (Figs. If the O-ring 9 is attached to the outer edge, the counter-geometry in the bell 37 can be designed cup-shaped (FIG. 7) or as a step (FIG. 5).
  • the O-ring 9 can also be pressed on a shoulder of the bell 37 (FIG. 3) or one of a cup-shaped geometry (FIG. 9), depending on the installation space.
  • the O-ring 9 is located on the outer ring: the large centering O-ring 9 is provided on the outer part of the CSC housing (outer side 12).
  • An outwardly open O-ring groove (10, Fig. 6) requires a circumferential, pot-shaped geometry in the bell 37. If there is a shoulder in the bell 37, a groove 10 is provided on the CSC housing 3 which is open inwards (FIG. 4).
  • the O-ring grooves 10 may be provided in both arrangements, also in the clutch or bell housing 37, instead of in the CSC housing 3.
  • the large centering O-rings 9 are used in addition to the centering nor the radial fixation.
  • a fit between CSC housing 3 and bell 37 may additionally / alternatively be provided.
  • the O-ring 9 is located on the inner ring:
  • the large centering O-ring 9 can also be provided on the inner part of the CSC housing 3.
  • An outwardly open O-ring groove (10, Fig. 1) requires a circumferential shoulder in the bell 37. If a cup-shaped geometry is present in the bell 37, a groove 10 is provided on the CSC housing 3 which is opened inwards (FIG. 8).
  • the O-ring grooves 10 may, in both arrangements, also be provided in the clutch or transmission bell 37, instead of in the CSC housing 3.
  • the large centering O-rings 9 are also used in the second variant the centering nor the radial fixation.
  • a fit between the CSC housing 3 and the bell 37 can additionally / alternatively be provided.
  • Fluid supply 20 The fluid supply can be purely axial (FIG. 10), ie from the bell 37, or by transverse bores (channel 23) and a connector (FIG. 11).
  • the O-ring seat can be mounted in the CSC housing 3 or in the bell 37. With an axially-sealing O-ring 9, the preload of the coupling has to be sufficiently large to guarantee the tightness of the system.
  • this rotational movement is to be prevented.
  • a groove (recess 34) and a tab (nose 33, FIGS. 12 and 13) can be provided as antirotational means (either tab 33 on CSC 3 or in the bell 37) or a pin 35 in a slot (Recess 34, Figures 14 and 15) engages.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

L'invention concerne un agencement d'actionnement (1) destiné à un embrayage d'un véhicule automobile, comportant un cylindre récepteur (2), le cylindre récepteur (2) présentant par ailleurs un carter (3) et un piston (5) logé coulissant le long d'un axe longitudinal (4) dans le carter (3), ainsi qu'une partie logement (6) montée ou pouvant être montée solidaire du carter d'embrayage ou de transmission. Le carter (3) et la partie logement (6) sont en appui axialement l'un par rapport à l'autre, et orientés radialement l'un par rapport à l'autre par des zones d'insertion (7, 8) en saillie axialement l'une dans l'autre vers l'intérieur, et un élément de fixation (9) servant d'appui axial aux zones d'insertion (7, 8) l'une par rapport à l'autre est placé radialement entre une première zone d'insertion (7) du côté du carter (3) et une seconde zone d'insertion (8) du côté de la partie logement (6). L'invention concerne en outre un système d'embrayage muni dudit agencement d'actionnement (1).
PCT/DE2019/100012 2018-02-05 2019-01-08 Agencement d'actionnement muni d'un carter de cylindre récepteur assemblé sans vis et centré, ainsi que système d'embrayage Ceased WO2019149308A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112019000663.0T DE112019000663A5 (de) 2018-02-05 2019-01-08 Betätigungsanordnung mit durch schraubenloseverbindung gefügtem undzentriertem gehäuse eines nehmerzylinders;sowie kupplungssystem

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018102450.9 2018-02-05
DE102018102450.9A DE102018102450A1 (de) 2018-02-05 2018-02-05 Betätigungsanordnung mit durch schraubenlose Verbindung gefügtem und zentriertem Gehäuse eines Nehmerzylinders; sowie Kupplungssystem

Publications (1)

Publication Number Publication Date
WO2019149308A1 true WO2019149308A1 (fr) 2019-08-08

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PCT/DE2019/100012 Ceased WO2019149308A1 (fr) 2018-02-05 2019-01-08 Agencement d'actionnement muni d'un carter de cylindre récepteur assemblé sans vis et centré, ainsi que système d'embrayage

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WO (1) WO2019149308A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022199744A1 (fr) * 2021-03-24 2022-09-29 Schaeffler Technologies AG & Co. KG Piston pour dispositif de libération pourvu d'un moyen de fixation

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1255002A (en) * 1967-09-01 1971-11-24 Skefko Ball Bearing Company Lt Improvements in or relating to clutch operating mechanisms
DE2131393A1 (de) * 1970-07-22 1972-01-27 Clark Equipment Co Hilfskraftgesteuerte Kupplung
DE10039242A1 (de) * 1999-08-24 2001-03-08 Luk Lamellen & Kupplungsbau Ausrücksystem
DE602004001215T2 (de) * 2003-02-20 2007-03-29 Valeo Embrayages Drehmomentübertragungsvorrichtung mit einem dämpfenden zweimassenschwungrad, für ein kraftfahrzeug
DE102010051152A1 (de) * 2009-11-19 2011-06-01 Schaeffler Technologies Gmbh & Co. Kg Deckelfeste Ausrückvorrichtung für Fahrzeugkupplungen
WO2013007231A1 (fr) 2011-07-11 2013-01-17 Schaeffler Technologies AG & Co. KG Dispositif de débrayage
DE102014215301A1 (de) 2014-08-04 2016-02-04 Schaeffler Technologies AG & Co. KG Anbindung eines Nehmerzylinders an ein Gehäuse
DE102016220021A1 (de) 2015-10-26 2017-04-27 Schaeffler Technologies AG & Co. KG Einheitlicher Nehmerzylinder mit variabler Anschraubgeometrie

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1255002A (en) * 1967-09-01 1971-11-24 Skefko Ball Bearing Company Lt Improvements in or relating to clutch operating mechanisms
DE2131393A1 (de) * 1970-07-22 1972-01-27 Clark Equipment Co Hilfskraftgesteuerte Kupplung
DE10039242A1 (de) * 1999-08-24 2001-03-08 Luk Lamellen & Kupplungsbau Ausrücksystem
DE602004001215T2 (de) * 2003-02-20 2007-03-29 Valeo Embrayages Drehmomentübertragungsvorrichtung mit einem dämpfenden zweimassenschwungrad, für ein kraftfahrzeug
DE102010051152A1 (de) * 2009-11-19 2011-06-01 Schaeffler Technologies Gmbh & Co. Kg Deckelfeste Ausrückvorrichtung für Fahrzeugkupplungen
WO2013007231A1 (fr) 2011-07-11 2013-01-17 Schaeffler Technologies AG & Co. KG Dispositif de débrayage
DE102014215301A1 (de) 2014-08-04 2016-02-04 Schaeffler Technologies AG & Co. KG Anbindung eines Nehmerzylinders an ein Gehäuse
DE102016220021A1 (de) 2015-10-26 2017-04-27 Schaeffler Technologies AG & Co. KG Einheitlicher Nehmerzylinder mit variabler Anschraubgeometrie

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DE112019000663A5 (de) 2020-10-15
DE102018102450A1 (de) 2019-08-08

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