WO2011116740A1 - Double embrayage - Google Patents

Double embrayage Download PDF

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Publication number
WO2011116740A1
WO2011116740A1 PCT/DE2011/000216 DE2011000216W WO2011116740A1 WO 2011116740 A1 WO2011116740 A1 WO 2011116740A1 DE 2011000216 W DE2011000216 W DE 2011000216W WO 2011116740 A1 WO2011116740 A1 WO 2011116740A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
cover
bearing
clutch cover
locking element
Prior art date
Application number
PCT/DE2011/000216
Other languages
German (de)
English (en)
Inventor
Florian Krebs
René Daikeler
Heiko Madlinger
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 DE112011101026.5T priority Critical patent/DE112011101026B4/de
Priority to CN201180015773.1A priority patent/CN102939472B/zh
Publication of WO2011116740A1 publication Critical patent/WO2011116740A1/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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a housing
    • 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
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • 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
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/43—Clutches, e.g. disengaging bearing
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0669—Hydraulically actuated clutches with two clutch plates
    • 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
    • F16D2300/26—Cover or bell housings; Details or arrangements thereof
    • 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

Definitions

  • the invention relates to a double clutch, by means of which a motor-side input shaft with two different transmission-side coaxially arranged output shafts can be coupled substantially traction interruption free.
  • a double clutch is known with the aid of which a motor-side input shaft can be coupled to a first gear-side output shaft and / or a second gear-side output shaft.
  • the dual clutch has a first clutch and a second clutch, each having a relative to a first counter-plate axially movable pressure plate for coupling a clutch disc connected to the respective output shaft.
  • the pressure plates are actuated by means of an actuating device which pivots within the dual clutch connected to the respective pressure plate actuating pot to move the respective pressure plate on the associated counter-plate.
  • the counter-plates are bolted to a clutch cover, wherein the clutch cover is supported via a cover bearing on the actuator.
  • the clutch cover is deep-drawn in the region of the cover bearing in the direction of the transmission, wherein on the extending in the axial direction deep-drawn portion of the clutch cover, a radially inwardly projecting shoulder is provided to connect the cover bearing captive with the clutch cover.
  • dual clutches can be assembled and / or disassembled in an easy to assemble manner, for example to facilitate adjustments to be made within the dual clutch.
  • the double clutch according to the invention for coupling an engine-side input shaft with a first transmission-side output shaft and / or a second transmission-side output shaft has a first clutch which has a relative to a first counter-plate axially having movable first pressure plate for coupling a first clutch connected to the first output shaft first clutch plate. Furthermore, the dual clutch has a second clutch, which has a second pressure plate, which is axially movable relative to a second counterplate, for coupling a second clutch disk connected to the second output shaft. With the first counter-plate and the second counter-plate, a clutch cover is connected.
  • an actuating device for axially moving the first pressure plate and / or the second pressure plate
  • a cover bearing is arranged between the actuating device and the clutch cover.
  • the cover bearing and the clutch cover are designed such that the cover bearing in the direction of the drive shaft to be introduced into the clutch cover, and the cover bearing is connected to the clutch cover via a locking element for locking the cover bearing with the clutch cover such that actuation forces on the locking element the actuator can be derived on the clutch cover.
  • the cover bearing and thus the actuator introduced from outside the dual clutch in the double clutch in particular can be inserted later, it is possible to mount the actuator independently of the other components or to dismantle.
  • the actuator can be installed as late as possible and / or subsequently dismantled for maintenance and adjustment purposes, so that the assembly and / or disassembly is simplified.
  • the locking element ensures that the cover bearing and / or the actuator can be firmly positioned or fixed in their position relative to the clutch cover in the axial direction and / or in the circumferential direction.
  • the locking element is in this case designed so stable that the forces occurring during actuation of the Betuschistsstöpfe can be removed from the actuator via the locking element to the clutch cover.
  • the locking element is in particular designed such that the locking element can remove all operating forces of the actuator, so that it is not necessary to have to take into account a frictional engagement between the cover bearing and the clutch cover, for example due to a press fit.
  • the double clutch has maintenance and assembly-friendly onteability or disassembly capability without impairing the reliable removal of occurring forces. At the same time the space of the double clutch is not significantly increased.
  • the respective clutch disc can be rotatably connected via a toothing with the respective output shaft, but axially movably connected.
  • the first counterplate and / or the second counterplate may protrude radially inward as a separate component from a radially outer housing wall.
  • the first counterplate and the second counterplate may be releasably connected to the clutch cover.
  • the first counter-plate or the second counter-plate of the clutch cover and / or a clutch cover axially opposite component, in particular in one piece.
  • one of the counter-plates may be formed by a flywheel connected to the engine-side input shaft and / or an output flange of a dual-mass flywheel connected to the input shaft.
  • the clutch disc can have a friction lining, in particular on axially facing end faces pointing away from one another, in order to bring about frictional contact with both the counterplate and the pressure plate during coupling, wherein the respective counterplate and / or the respective pressure plate may or may not also have a friction lining.
  • the respective pressure plates and counter plates are configured in particular as separate, functionally separate components, so that a so-called "four-plate design" is possible for the double clutch without significantly increasing the installation space
  • the respective clutch disc may be damped, particularly preferably the dual clutch is designed as a dry directly actuated double clutch, that is, the actuating pots are not with the aid of this provided components pivoted to move the pressure plates axially.
  • the clutch cover from a plate with a defined nominal thickness can be produced, the clutch cover rests with the nominal thickness of the top bearing with a maximum.
  • the clutch cover can thereby rest flush against the cover bearing or even be arranged spaced over a gap to the cover bearing. Since the forces applied by the actuator forces can be removed via the locking element, a direct power flow between the cover bearing and the clutch cover is not required, so that the cover bearing with a clearance, in particular H7 / h6 or H8 / h9 in the Clutch cover can be used.
  • it is not necessary to bend the clutch cover in the region of the cover bearing by deep drawing and / or to extend in the axial direction the production of the clutch cover in the region of the cover bearing can be greatly simplified. At the same time the construction of the clutch cover can be reduced in the axial direction.
  • the clutch cover has a bearing opening for receiving the cover bearing, wherein the bearing opening is configured such that the bearing opening can be produced with a restriction exclusively from punching and / or turning operations.
  • the bearing opening can be produced, for example, by punching a central opening in the clutch cover, which is then optionally machined again, for example by turning.
  • the tilting stiffness between the cover bearing and the clutch cover is increased.
  • After the production of the bearing opening with the final nominal diameter by punching and / or turning a deep drawing is not required.
  • only slight non-cutting bending process which change less than 50% by volume of the structure of the bent out part of the clutch cover.
  • the locking element has a variable in the radial direction extent, wherein the locking element is configured in particular as a securing ring. Due to the variability of the locking element in the radial direction, it is possible to use the locking element on a smaller diameter in the clutch cover and then bring to a larger diameter, so that the locking element can be held captive in the clutch cover. At the same time, the locking element can extend radially inward to the extent that the locking element can also abut against the cover bearing. As a result, the actuating device and the cover bearing can be connected captively to the clutch cover.
  • both the cover bearing and the clutch cover can strike the locking element when the actuator generates an actuating force for axially moving a pressure plate, a sufficient force flow capacity is provided by the actuating device via the locking element to the clutch cover.
  • a tab for axial movement limitation of the locking element between the tab and the clutch cover is provided, wherein the tab is formed in particular by the clutch cover, preferably by punching and bending. Through the tab, for example, a pocket can be formed between the clutch cover and the tab into which the locking element can be inserted. The locking element is thereby limited in its movement in the axial direction or fixed substantially immovable even in the axial direction.
  • the part of the locking element which is not arranged in the pocket, can form a stop for the cover bearing, by which the cover bearing is connected captively to the clutch cover.
  • the tab may be releasably or permanently connected as an additional component with the clutch cover.
  • the additional tab can be connected, for example by welding, soldering, riveting, screwing and / or pinning with the clutch cover.
  • the tab can also be formed by the clutch cover itself by a corresponding portion of the clutch cover punched example and bent out of the plane of the clutch cover.
  • the locking element has in the circumferential direction in particular a greater extent than the single tab, so that the locking element can be securely positioned between the tab and the clutch cover.
  • the tab for clamping the locking element is axially movable.
  • the tab can, for example, change its distance from the clutch cover by means of a screw so that a locking element arranged between the clutch cover and the tab can be clamped substantially without axial play. This leads to an axial fixation of the locking element with the clutch cover and / or leads to an axially substantially play-free salaried storage of the cover bearing. Furthermore, by a sufficiently high clamping force and a rotation of the locking element can be avoided in the circumferential direction.
  • the locking element is located both on a transmission-side end face of the clutch cover and on a motor-side end face of the clutch cover, wherein the clutch cover in particular has in the axial direction extending shafts.
  • the waves can have alternating wave peaks and wave troughs, wherein the peaks of the wave crests and wave tails can be excavated out of the planes of the clutch cover in the axial direction.
  • a tangent applied to one of the wave crests and / or wave troughs may be substantially orthogonal to the radial direction.
  • the locking member can abut both the motor-side, and on the transmission-side end face of the clutch cover, the Clutch cover securely received and / or jammed by the locking element.
  • the locking member may be configured substantially annular.
  • the locking element may in this case have, in particular, radially projecting fastening lugs, which may rest against the clutch cover in the bent-out regions of the shafts.
  • the attachment lugs can be arranged in particular in a plane.
  • the cover bearing and / or the clutch cover on a projecting in the radial direction approach wherein the approach using the locking element with the clutch cover or with the cover bearing, preferably releasably connected.
  • the cover bearing may have at its gear-side end a radially outwardly protruding approach, which serves as a stop when the cover bearing is inserted into the clutch cover.
  • This approach can be connected, for example by knurling or flanging with the clutch cover.
  • the locking element may for example be designed as a screw or riveting.
  • the clutch cover having a motor side radially inwardly projecting approach to which the cover bearing and / or the actuator can strike when inserting the actuator in the clutch cover.
  • the locking element may be designed for example as a screw, riveting or other releasable or unsolvable fastener.
  • the clutch cover and / or the cover bearing on a recess for positive and / or frictional engagement of the locking element wherein the recess is designed in particular as a groove for receiving a locking ring.
  • the recess can be formed by the recess between the clutch cover and the cover bearing an axially outwardly opening bevel, in which a particular annular wedge can be introduced as a locking element to frictionally fix the cover bearing with the clutch cover.
  • the wedge may be self-locking or secured by means of a securing element, for example a securing pin.
  • the recess can also be designed as a groove, so that there are two stops in the axial direction for the locking element, by which the locking element is taken captive.
  • the locking element as interlocking in the
  • Cover bearing and provided in the clutch cover thread is configured.
  • the locking element in the form of a thread between the cover bearing and the clutch cover the cover bearing can be screwed and unscrewed in the clutch cover.
  • the thread can be designed in particular self-locking. The axial position of the cover bearing of the actuator relative to the clutch cover can be adjusted precisely.
  • the actuating device has a first piston for the axial movement of the first pressure plate by means of a first actuating pot and a second piston for the axial movement of the second pressure plate by means of a second actuating pot, wherein the actuating travel of the first piston substantially corresponds to the displacement of the first pressure plate and / or the actuating travel of the second piston essentially corresponds to the displacement path of the second pressure plate.
  • a directly actuated translation-free coupling is formed. A pivoting of the respective operating pot does not take place, so that the corresponding components for enabling pivoting of the respective operating pot can be saved.
  • the actuating travel of the respective piston corresponds exactly to the displacement of the associated pressure plate.
  • the displacement of the respective pressure plate thus differs from the actuating travel of the associated piston only to the distance in the axial direction by which the associated actuating pot is bent elastically upon actuation of the respective clutch.
  • the double clutch can be constructed much simpler.
  • the actuating means comprises a first annular pressure cylinder for moving the first pressure plate and a second annular pressure cylinder for moving the second pressure plate, wherein the first pressure cylinder and the second pressure cylinder are arranged coaxially with each other.
  • the coaxial arrangement of the ring-shaped pressure cylinder results in a particularly compact and space-saving design for the actuator.
  • the invention further relates to a transmission line for a motor vehicle with an engine-side input shaft, a first transmission-side output shaft, a second transmission-side output shaft and a dual clutch for coupling the input shaft to the first output shaft and / or the second output shaft, wherein the dual clutch, as vorste- described, can be trained and further educated. Due to the double clutch, the actuating device can be mounted as late as possible for maintenance and adjustment purposes and / or dismantled subsequently, so that the assembly and / or disassembly is simplified.
  • FIG. 1 is a schematic sectional view of a dual clutch in a first embodiment
  • FIG. 3 is a schematic detail view of the dual clutch of FIG. 2,
  • FIG. 5 shows a schematic sectional view of a double clutch in a fourth embodiment
  • FIG. 6 is a schematic sectional view of a double clutch in a fifth embodiment
  • FIG. 7 is a schematic sectional view of a double clutch in a sixth embodiment
  • Fig. 8 is a schematic sectional view of a double clutch of a seventh embodiment
  • Fig. 9 is a schematic sectional view of a double clutch in an eighth embodiment.
  • the dual clutch 10 shown in FIG. 1 has a first clutch 12 and a second clutch 14.
  • the first clutch 12 has a first pressure plate 16 which is axially movable to a first counter-plate 18 in order to couple a clutch disc 20 arranged between the first pressure plate 16 and the first counter-plate 18.
  • the first clutch disc 20 has friction linings 22, by way of which the frictional engagement between the first counterplate 18 and the clutch disc 20 and between the first pressure plate 16 and the clutch disc 20 can be produced.
  • the first clutch plate 20 may be rotatably connected via a toothing 24 with a first output shaft, not shown, but axially displaceable.
  • the second clutch 14 has a second pressure plate 26 which is axially displaceable to a second counter-plate 28 to frictionally couple a second clutch disc 30 arranged between the second pressure plate 26 and the second counter-plate 28 via the friction linings 22.
  • the second clutch plate 30 may be rotatably connected via a toothing 24 with a second output shaft, not shown, but axially displaceable.
  • an actuator 32 which has a first annular pressure cylinder 34 for disengaging a first piston 35, with the aid of a first operating pot 36 can be moved purely axially to the first pressure plate 16 on the first counter-plate 18 to move. Accordingly, the actuator 32 has a coaxially within the first pressure cylinder 34 arranged second pressure cylinder 38 for disengaging a second piston 39, with the aid of a second actuator pot 40 can be moved purely axially to move the second pressure plate 26 on the second counter-plate 28 to ,
  • a coupling pot 42 is connected, which abuts with its radially inwardly directed by punching contact surface 44 produced on a cover bearing 46.
  • a bearing opening is defined, which receives the cover bearing 46.
  • the cover bearing 46 and the coupling pot 42 have in their contact area on a flat surface, so that the cover bearing 46 can be inserted axially into the clutch cover 42 from the outside and pulled out again.
  • the axial fixation of the cover bearing 46 with the clutch cover 42 is carried out with the aid of a designed as a locking ring 48 locking element, which is inserted from radially inside a pocket 50.
  • the pocket 50 which is open in the circumferential direction and radially inward is formed by the clutch cover 42 and an additional lug 52 fixedly connected to the clutch cover 42.
  • the securing ring 48 is thereby connected in a fixed position in the axial direction with the clutch cover 42 and at the same time forms a impact in the axial direction of the cover bearing 46, so that the cover bearing 46 is inserted captive in the clutch cover 42 and in the axial direction preferably substantially free of movement is limited.
  • the locking ring 48 can be removed and the actuator 32 are pulled out together with the cover bearing 46 of the double clutch 10.
  • the clutch cover 42 further comprises a tab made by punching 54, which is bent out of the plane of the clutch cover 42 slightly to form an enlarged contact surface 44 for the clutch cover 42 in the axial direction. This increases the tilting stiffness.
  • the additional tab 52 may be connected to the clutch cover 42, for example via a rivet connection, screw connection, solder connection, welded connection and other detachable or non-detachable connection.
  • the additional tab 52 instead of the additional tab 52, only one tab 54 formed by the clutch cover 42 has been provided.
  • This tab 54 does not necessarily have to be produced by stamping, but can also be formed by a wavy configuration of the clutch cover in the circumferential direction, wherein the tab 54 is formed by the respectively formed shaft 56 (FIG. 3).
  • the locking element 48 need not necessarily extend over the entire or substantially the entire circumference, but may also extend over a significantly smaller angular range, which is just large enough so that the locking element 48 both on a motor-side end face 58 and on a disconnected end face 60 can rest.
  • the cover bearing 46 has a radially outwardly projecting lug 62, which bears against the motor-side end face 60 of the clutch cover 42.
  • the locking element is designed as a screw 64, via which the neck 62, the cover bearing 46 is releasably screwed to the clutch cover 42.
  • the locking ring 48 is inserted in a groove 66 of the clutch cover 42.
  • the securing ring 48 can thereby be fixed without straps 54, 52 in the axial direction with the clutch cover 42.
  • the groove 66 is configured such that it can absorb the actuation forces of the actuating device 32 occurring when the clutches 12, 14 are actuated and can be diverted via the clutch cover 42.
  • the clutch cover 42 has tabs 54 bent out both on the engine side and on the transmission side. By the tabs 54, both the contact surface 44 can be increased to increase the tilting stiffness, and the locking ring 48 between the clutch cover 42 and the transmission side projecting tab 54 are limited in its axial movement.
  • the clutch cover 42 has a radially inwardly projecting tab 54, which is issued in the form of a bead.
  • the tab / bead 54 can be made, for example, after the cover bearing 46 is inserted into the clutch cover 42.
  • the flap / bead 54 is configured ramp-shaped, so that the cover bearing 46 can be inserted along the ramp-shaped tab 54 in the clutch cover 42.
  • the ramp-shaped tab 54 can snap back radially inward and form a stop against axial falling out of the cover bearing 46.
  • the cover bearing 46 is captively retained in the clutch cover 42 after assembly of the actuator 32 and the cover bearing 46.
  • both the clutch cover 42 and the cover bearing 46 have an outwardly open recess 68, resulting in a substantially wedge-shaped recess between the clutch cover 42 and the cover bearing 46.
  • a particular self-locking wedge 70 is pressed as a locking element, so that the cover bearing 46 is fixed in the axial direction with the clutch cover 42.
  • the wedge 70 may in particular be configured continuously in the circumferential direction and preferably be annular.
  • the wedge 70 may optionally be secured with a securing element, such as a locking pin against axial slipping out.
  • the cover bearing 46 may also be connected via a locking element in the form of a bayonet lock with the clutch cover 42.
  • a protruding from the cover bearing 46 approach can be used in a corresponding recess of the clutch cover 42 and are rotated radially after insertion in the circumferential direction. After radial rotation, the actuator 32 and / or the cover bearing 46 can be secured against rotation with the clutch cover 42, for example by means of a safety pin.
  • the invention further relates to a double clutch 10, in which in comparison to the above-described embodiments of the double clutch 10, the cover bearing 46 is fixedly connected to the clutch cover 42 and the fastening possibilities described above by means of the locking means for the axial attachment of the actuator 32 between the cover bearing 46th and the actuator 32 act.
  • the above explanations thus also apply to the actuating device 32 instead of the clutch cover 42, wherein the mechanical configuration can be correspondingly kinematically reversed.
  • all the described embodiments can also be combined with one another, so that more than one fastening possibility, in particular with differently configured locking elements, can be provided.
  • the closing force for the clutches is introduced via actuators, preferably without leverage, directly into the clutches, the pressure pots as intermediate elements between pressure plates and actuators substantially rigid or can be formed with a defined elasticity.

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

Abstract

L'invention concerne un double embrayage pour accoupler un arbre d'entrée côté moteur à un premier arbre de sortie côté transmission et/ou un deuxième arbre de sortie côté transmission, comportant un premier embrayage (12) comprenant une première plaque de compression (16) axialement mobile par rapport à une première contre-plaque (18), destinée à accoupler un premier disque d'embrayage (20) relié au premier arbre de sortie, et un deuxième embrayage (14) comprenant une deuxième plaque de compression (26) axialement mobile par rapport à une deuxième contre-plaque (28), destinée à accoupler un deuxième disque d'embrayage (30) relié au deuxième arbre de sortie. Un couvercle d'embrayage (42) est relié à la première contre-plaque (18) et à la deuxième contre-plaque (28). Un dispositif d'actionnement (32) est également prévu pour déplacer la première plaque de compression (16) et/ou la deuxième plaque de compression (26), un palier de couvercle (46) étant prévu entre le dispositif d'actionnement (32) et le couvercle d'embrayage (42). Le palier de couvercle (46) et le couvercle d'embrayage (42) sont conçus de telle manière que le palier de couvercle (42) peut être introduit dans le couvercle d'embrayage (42) en direction de l'arbre d'entrée. Par ailleurs, le palier de couvercle (46) est relié au couvercle d'embrayage (42) au moyen d'un élément butée (48) pour arrêter le palier de couvercle (46) au moyen du couvercle d'embrayage (42), de telle manière que l'élément butée (48) permet de transmettre des forces d'actionnement du dispositif d'actionnement (32) au couvercle d'embrayage (42). A des fins d'entretien ou de réglage, il est alors possible de monter le dispositif d'actionnement (32) tardivement et/ou de le démonter ultérieurement de telle manière que le montage et/ou le démontage sont simplifiés.
PCT/DE2011/000216 2010-03-25 2011-03-03 Double embrayage WO2011116740A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112011101026.5T DE112011101026B4 (de) 2010-03-25 2011-03-03 Doppelkupplung
CN201180015773.1A CN102939472B (zh) 2010-03-25 2011-03-03 双离合器

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DE102016214710A1 (de) * 2016-08-09 2018-02-15 Schaeffler Technologies AG & Co. KG Mehrteilige materialunterschiedliche Zentralplatte für trockene Doppelkupplung und Doppelkupplung im Dreiplatten-Design

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KR101519262B1 (ko) * 2013-12-18 2015-05-11 현대자동차주식회사 Dct의 터치포인트 보정방법
JP6618922B2 (ja) * 2014-03-31 2019-12-11 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 軸受ユニット
DE102020108818B3 (de) * 2020-03-31 2021-03-18 Schaeffler Technologies AG & Co. KG Reibkupplungsdeckel aus Blech mit gefalteten Wälzlagersitzen, Getriebeanordnung und Herstellverfahren

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EP1380765A1 (fr) * 2002-07-12 2004-01-14 ZF Sachs AG Embrayage à friction
FR2851627A1 (fr) * 2003-02-20 2004-08-27 Valeo Embrayages Dispositif de transmission de couple pour vehicule automobile
FR2861147A1 (fr) * 2003-10-21 2005-04-22 Valeo Embrayages Embrayage, notamment pour vehicule automobile, et procede de montage de cet embrayage.
WO2006012972A1 (fr) * 2004-07-30 2006-02-09 Zf Friedrichshafen Ag Embrayage a friction du type no

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DE10236806A1 (de) 2002-07-12 2004-01-22 Zf Sachs Ag Reibungskupplung
DE102004040224B4 (de) 2004-08-19 2010-04-08 Ab Skf Wälzlager
FR2880932B1 (fr) 2005-01-18 2008-07-25 Valeo Embrayages Element de transmission a palier de centrage et de reprise d'effort
FR2881490B1 (fr) 2005-01-31 2007-03-02 Valeo Embrayages Dispositif de montage d'un palier sur un element de transmission.

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DE10155458A1 (de) 2000-11-22 2002-05-23 Luk Lamellen & Kupplungsbau Kupplungsaggregat
EP1380765A1 (fr) * 2002-07-12 2004-01-14 ZF Sachs AG Embrayage à friction
FR2851627A1 (fr) * 2003-02-20 2004-08-27 Valeo Embrayages Dispositif de transmission de couple pour vehicule automobile
FR2861147A1 (fr) * 2003-10-21 2005-04-22 Valeo Embrayages Embrayage, notamment pour vehicule automobile, et procede de montage de cet embrayage.
WO2006012972A1 (fr) * 2004-07-30 2006-02-09 Zf Friedrichshafen Ag Embrayage a friction du type no

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Publication number Priority date Publication date Assignee Title
DE102016214710A1 (de) * 2016-08-09 2018-02-15 Schaeffler Technologies AG & Co. KG Mehrteilige materialunterschiedliche Zentralplatte für trockene Doppelkupplung und Doppelkupplung im Dreiplatten-Design
DE102016214710B4 (de) * 2016-08-09 2020-08-13 Schaeffler Technologies AG & Co. KG Doppelkupplung mit mehrteiliger materialunterschiedlicher Zentralplatte

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DE112011101026A5 (de) 2013-01-17
DE102011012896A1 (de) 2011-12-15
CN102939472A (zh) 2013-02-20
DE112011101026B4 (de) 2022-09-08
CN102939472B (zh) 2019-05-31

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