EP3030800A1 - Moyen d'actionnement pour embrayage à friction - Google Patents

Moyen d'actionnement pour embrayage à friction

Info

Publication number
EP3030800A1
EP3030800A1 EP14761783.1A EP14761783A EP3030800A1 EP 3030800 A1 EP3030800 A1 EP 3030800A1 EP 14761783 A EP14761783 A EP 14761783A EP 3030800 A1 EP3030800 A1 EP 3030800A1
Authority
EP
European Patent Office
Prior art keywords
point
actuating
drive
lever
bearing
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Withdrawn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
EP14761783.1A
Other languages
German (de)
English (en)
Inventor
Dirk Reimnitz
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 EP3030800A1 publication Critical patent/EP3030800A1/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F16D23/143—Arrangements or details for the connection between the release bearing and the diaphragm
    • F16D23/144—With a disengaging thrust-ring distinct from the release bearing, and secured to the diaphragm
    • 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
    • F16D25/088—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members being distinctly separate from the axis of rotation

Definitions

  • the invention relates to an actuating device for an actuated depending on an actuation path friction clutch with one of a drive at a drive point actuated, fixed to a support housing fixed to a pivot point rotatably received and a lever spring of the friction clutch rotatably coupled to an output point axially acting actuating lever.
  • Friction clutches are known from powertrains, for example, as simple friction clutches, partial clutches accommodated in double clutches, and hybrid clutches interconnecting components of a hybrid powertrain.
  • an axially displaceable pressure plate is braced against an axially fixed counter-pressure plate, so that when bracing a frictional engagement with the friction linings is formed and dissolved without distortion of the frictional engagement.
  • the bias of the pressure plate by means of a lever member which is acted upon axially by an actuating device along an actuating path.
  • forced open friction clutch normally closed
  • forced closed friction clutch normally open
  • actuating force to the actuator, depending on the design of the friction clutch, a plate spring, a lever spring or spring-loaded levers.
  • an actuating device serve an actuating lever which is axially supported at a fulcrum to counteract the actuating force, axially displaced at a further fulcrum of a drive and applied to the last fulcrum, the lever member axially.
  • an actuator is known for example from DE 10 2006 050 956 A1.
  • a drive designed as a pressure cylinder is arranged on a drive end provided as a lever end and a thrust bearing of a lever element acting on the output point to the one lever end of the actuating lever.
  • the housing-fixed support point is provided at the fulcrum of the actuating lever.
  • the driving force of the drive is supported at the supporting point and converted into the actuating force for actuating the lever element. directs.
  • drive point, output point and support point are each acted upon only in one axial direction.
  • Such controls are only suitable for drives in which there is no change of sign of the driving force on the change of operation, that is, in which over the entire actuation a tensile or compressive force is applied.
  • the object of the invention is the development of an actuating device which can transmit a drive force of the drive with a sign change containing operating force on the actuation path of a friction clutch.
  • the proposed actuator for an actuated depending on a Betjansweg friction clutch includes one of a drive, such as an electric motor, a hydraulic or pneumatic pressure cylinder or the like actuated at a drive point, fixed to the housing at a support point rotatably received by a fulcrum and a lever member such as plate spring, lever spring, Actuating lever or the like of the friction clutch rotatably coupled at an output point axially acting actuating lever.
  • Drive point, support point and output point are formed axially transmitting force in both directions, so that tensile and compressive forces of the drive can be transmitted and the friction clutch as a single clutch, partial clutch of a dual clutch, hybrid clutch or the like operated as a so-called push / pull clutch.
  • the zero point of the drive can lie between a fully closed and a fully open position of the friction clutch.
  • the friction clutch can be actively opened in a force direction substantially independently of the force relationships existing in the friction clutch, and in the other direction to be actively closed, for example, to be able to make quick operations of these.
  • the actuator may be self-locking, so that at each waypoint of the actuation path a set position of the friction clutch can be kept substantially free of force. For example, with a compressed friction clutch (normally open), starting from an open position, the actuating lever may be pulled to a minimum actuating travel. In the same way, first a tensile and then a pressure movement of the drive close the friction clutch. Furthermore, by means of the actuating device according to an imprinted friction clutch can be actuated.
  • output point and support point may be provided on variable lever locations of the operating lever.
  • the support point between the drive point and output point is arranged on the actuating lever.
  • the output point between drive point and support point can be arranged on the actuating lever.
  • the drive point between output point and support point can be arranged on the actuating lever.
  • the drive of the actuating lever may be formed as an electric motor.
  • a rotational movement of the rotor is converted by means of a transmission in a linear movement to drive the actuating lever
  • the transmission can be designed as a spindle gear.
  • worm gears and the like may be provided.
  • a spindle nut may be provided with a cam, roller or the like, which is inserted into a slide which is introduced into the actuating lever and which extends obliquely to the actuating travel, on a threaded spindle driven by a rotor of the electric motor. These can roll over the backdrop preferably roller bearings.
  • a drive bidirectionally effective pressure cylinder such as a hydraulic or pneumatic pressure cylinder, with which the drive point is coupled.
  • a pressure cylinder has, for example, two pressure chambers which can be acted upon by pressure of a master cylinder, a pump or the like, which are separated from one another by a displaceable piston and to which the drive point of the actuating lever is coupled.
  • a pressure chamber takes over the loading tion of the piston in the pulling direction and the other in the pressure direction of the actuating lever.
  • two pressure cylinders can be switched in their effect against each other.
  • a connection between the piston and the drive point or actuating lever for example, a piston rod serving as a coupling rod can be connected by means of a hinge articulated to the drive point.
  • a movement direction of the drive may be formed perpendicular or parallel to the actuation path.
  • output point and support point can be pivot bearings and / or bidirectionally effective Abicalzitatien, for example, in annular grooves abrolling forks and the like.
  • ball joints displaced in joint connections for example in joint sockets, can be provided.
  • FIG. 2 a section through an actuating device with a support point arranged between the drive point and the output point;
  • FIG. 3 shows a section through an actuating device with a drive point arranged between the output point and the supporting point
  • FIG. 4 shows a section through an actuating device with a drive consisting of two pressure cylinders connected against each other
  • Figure 5 shows a section through an actuator with an electromotive
  • FIG. 8 shows a section through a structural design of an actuating device with a spherical support point
  • FIG. 9 shows the actuating device of FIG. 8 in an oblique view from the front
  • FIGS. 8 and 9 shows the actuating device of FIGS. 8 and 9 in an oblique view from behind
  • FIG. 11 shows the actuating device of FIGS. 8 to 10 during assembly
  • FIG. 12 shows the actuating device of FIGS. 8 to 11 in the fully assembled state from the front
  • FIG. 13 a with respect to the actuating device of FIGS. 8 to 12 with respect to FIG
  • FIG. 14 shows a further variant of the actuating devices of FIGS. 8 to 13 in FIG.
  • FIG. 15 shows an actuating device similar to the actuating devices of FIGS. 8 to 14 with an axially prestressed supporting point in section;
  • FIG. 16 shows a preload plate of the actuating device of FIG. 15 in a view
  • Figure 18 shows the uncut actuator of Figure 17 in enlarged
  • FIG. 19 shows an oblique view of the actuating device modified with respect to the receptacle of the ball head in relation to the actuating device of FIGS. 18 and 19;
  • FIG. 20 shows a view of the actuating device of FIG. 19 from radially outside with a plate spring of the friction clutch
  • FIG. 21 is a sectional oblique view of the actuator modified with respect to the receptacle of the ball head in relation to the actuators of FIGS. 18 to 20;
  • FIG. 22 shows an alternative embodiment of an actuating device with axially biased bidirectionally effective bearing points in rear view
  • FIG. 23 shows an actuating device with an actuating bearing, which can be rotated directly on the actuating lever, in section,
  • FIG. 24 shows the actuating device of FIG. 23 in an oblique view
  • FIG. 25 shows the actuating device of FIGS. 23 and 24 in front view
  • FIG. 26 an actuating device with a housing-fixed rotatable receptacle of the supporting point by means of a snap connection in an oblique view
  • FIG. 27 shows the actuating device of FIG. 26 before assembly
  • FIG. 28 shows the actuating device of FIGS. 26 and 27 of an alternative structural design during assembly in front view
  • FIG. 29 shows the actuating device of FIG. 28 during assembly in FIG
  • Figure 30 shows the actuating device of Figures 26 to 29 in the fully assembled state in front view
  • FIG. 31 shows the actuating device of FIGS. 26 to 29 in an assembled state in an oblique view
  • Figure 32 shows two nested actuators for actuating a
  • FIG. 33 shows a detail view of the actuating devices of FIG. 32.
  • the friction clutch 1 is a so-called push / pull clutch, in which by means of the plate spring 2 in the closed state of the friction clutch 1, the pressure plate 3 under tension of the friction linings 4 of the clutch disc 5 braced against the platen 6. In addition, the force exerted by the pressure plate 3 on the friction linings 4, further increased by the actuator 100 pulls on the plate spring tongues 7. By axially displacing the plate spring tongues 7 by means of the actuating device 100 in the direction counterpressure plate 6, the tension of the plate spring 2 is reduced and the friction clutch 1 is opened. In this case, the actuating device 100 exerts both a pressing and a pulling function on the plate spring tongues 7.
  • the plate spring tongues 7 are accommodated on both sides in the ball-shaped contact surfaces 101 of the actuating bearing 102.
  • the axial displacement of the concentric about the transmission input shaft 103 of a transmission not shown actuator bearing 102 is rotationally coupled by means of the actuating lever 104 which has the force application points drive point 105, output point 106 and support point 107 to the driving force of the drive 108, which here as bidirectionally effective Pressure cylinder 109 is formed on the actuating bearing 102 in compliance with predetermined lever to transmit the results.
  • all force application points are formed axially fixed.
  • the drive point 105 is axially fixed and rotatably connected to the piston rod 1 10 of the pressure cylinder 109 shown only schematically by means of the pivot bearing 1 1 1.
  • the actuating lever 104 is at the between drive point 105 and the output point 106 arranged, a two-armed lever forming supporting point 107 by means of the pivot bearing 1 12 against the only indicated gear housing 1 13 axially fixed and rotatably supported.
  • the output point 106 is formed by means of the slide bearing 1 14, which takes place as a sliding movement in the radial direction, the fork-shaped and spherical lever ends 1 16 as fork heads of the actuating lever 104 relative to the grooves 1 15 of the actuating bearing 102.
  • Figures 2 to 7 show different embodiments of actuators 100, 200, 300, 400, 500, 600, which are suitable for example for actuating the friction clutch 1 of Figure 1, each in a schematic representation.
  • the actuating device 100 of FIG. 2 has already been described in FIG. 1 and, with respect to the supporting point 107, has an output point 106 opposite the drive point 105.
  • the output point 206 and the support point 207 are arranged at the opposite end of the lever lever of the actuating lever 204 and the drive point 205 is between them.
  • the actuating lever 204 is designed as a one-armed lever and the drive path of the Ant- riebs 208 in the form of the pressure cylinder 209 is shorter than the actuation path of the friction clutch and extends in the same direction.
  • Actuating device 300 is provided with the drive 308, which is formed of two mutually effectively switched individual pressure cylinders 309, 309a.
  • the drive point 305 and the support point 307 at the lever ends of the actuating lever 304 to form a one-armed lever and between these the output point 306 are arranged. Such an arrangement results in a higher drive path of the drive 308 with reduced force stress compared with the actuating travel of the friction clutch.
  • FIG. 5 shows the actuating device 400 with the drive 408 driven by an electric motor.
  • the rotor 410 of the electric motor 409 drives the worm 417 of the worm gear 419.
  • the actuating lever 404 engages the worm 417 by means of the about the pivot bearing 412 of the support point 407 arc-shaped, applied to the actuating lever 404 or molded toothed segment 418, so that upon rotation of the rotor 410 depending on the direction of rotation a tensile or compressive movement by means of Operation lever 404 is performed on the actuating bearing 402.
  • Serving as the drive point 405 worm gear 419 and the output point 406 are arranged at the lever ends of the actuating lever 404. In between, the housing-fixed support point 407 is provided.
  • FIG. 6 shows the actuating device 500 with the drive 508 arranged between the support point 507 and the output point 506 of the actuating lever 504 with the drive point 505 slidably provided along the actuating lever 504.
  • the drive 508 is designed as an electric motor 509 with the spindle drive 519.
  • the threaded spindle 517 or a ball screw is provided on the rotatably and axially displaceable upon rotation of the rotor 510, the spindle nut 518 is added.
  • the spindle nut 518 has a cam or the roller 520 or on, which engages in the link 51 1 and is preferably rotatably received on the spindle nut 518.
  • FIG. 7 shows the actuating device 600, in which the electromotive drive 608 with the electric motor 609 and the spindle gear 619 is arranged on a lever end of the actuating lever 604.
  • the spindle nut 618 of the spindle gear 619 is displaced axially upon rotation of the rotor 610 on the threaded spindle 617 and is non-rotatably fixed to the housing, for example, received on the clutch bell 613.
  • the spindle nut 618 forms the driving point 605 and actuates the actuating bearing 602 depending on the direction of rotation of the rotor at the output point 606 pulling or pushing.
  • the actuating lever 604 is formed in one arm with the support point 607 arranged at the lever end of the actuating lever opposite the drive point 605.
  • Figures 8 to 14 show the actuator 700 in different representations and mounting conditions.
  • the actuating device 700 is driven in a pulling or pushing manner by a drive (not shown), for example an electric motor with a gear or one or more pressure cylinders, by means of the coupling rod 710, which is essentially free of play at a lever end of the actuating lever 704 ,
  • the coupling rod 710 forms by means of the yoke 720, the drive point 705 to the fork heads 721 of the actuating lever 704.
  • the operating lever 704 By the two movement points between vertically arranged coupling rod 710 and yoke 720 on the one hand and between yoke 720 and clevis 721 on the other hand, the operating lever 704, the intended pivoting movement for actuation perform the friction clutch by means of linear displacement of the actuating bearing 702 and at the same time has the ability to easily tilt about its longitudinal axis, if necessary to compensate for component inaccuracies.
  • the support point 707 between the drive point 705 and the output point 706 of the actuating lever 704 is formed by the ball head 712 connected to the actuating lever 704.
  • the ball head 712 is fixed to the housing by means of the pin 712a in the connected to the housing 713, serving as axial compensation relative to the housing 713 and possibly dispensable support member 713a, which may be integrally formed with the housing 713, connected such as screwed.
  • the ball head 712 is substantially firmly enclosed by the shaping 723 of the actuating lever 704 on the one hand and on the opposite side by the retaining plate 724 connected to the actuating lever 704 and thus supported fixed to the housing bidirectionally in the direction of the displacement of the actuating bearing 702. It may be provided that an embodiment of the ball head bearing is provided such that the ball center of the ball head 712 within the Kon- clock points of the formation 723 and the retaining plate 724 and gaps between the contact points are smaller than the ball diameter.
  • the actuating lever 704 is fork-shaped with spherically formed, for example, cylindrical bearing surfaces 701, by means of which it rolls between two contact surfaces 725 of the introduced into the bearing bracket 726 of the actuating bearing 702 grooves 715.
  • the contact points between the actuating lever 704 and the bearing support 726 thereby resemble the contact points between the yoke 720 and actuating lever 704, which can also transmit forces in both directions through the two opposite contact surfaces.
  • the guide sleeve 727 is fastened to the housing 713 and then the ball head 712 together with the supporting element 713a and the retaining plate 724 attached to the housing 713 as screwed.
  • the ball head 712 is provided by means of a non-visible tool connection contour on the outer diameter outside of the later contact points. For example, outer and hexagon or six-round contours can be used as the tool connection contour, or differently shaped elevations or depressions can be formed in the ball head 712.
  • the operating lever 704 When the ball head 712 is connected to the housing 713, the operating lever 704 is fitted onto the threaded studs 728 of the retaining plate 724 and screwed thereto.
  • the actuator bearing 702 and the bearing bracket 726 are connected in advance with the lever member, for example, operating tongues such as plate or lever spring tongues of the friction clutch.
  • the bearing carrier 726 is threaded onto the guide sleeve 727 when the friction clutch is pushed into the clutch bell.
  • Figures 1 1 and 12 show the actuator 700 with the suspension of the actuating lever 704 in the bearing bracket 726th Since the drive point 705 of the actuator 700 protrudes on the clevises 721 of the actuating lever 704 outside of the clutch housing to be connected there to the drive, This can be used during assembly to the actuating lever 704 - as shown in Figure 1 1 - laterally around the Ku To rotate gel head 712 so that the bearing support 726 can be axially guided past the inner fork heads 729 when threading the bearing support 726 on the guide sleeve 727 and brought to the axial position of the grooves 715. Subsequently, according to FIG.
  • the actuating lever 704 is pivoted back into its operating position and the fork heads 729 are pivoted into the grooves 715. Subsequently, the yoke 720 is connected to the piston rod at the drive point 705. As a result, the connection to the drive is produced and at the same time prevents the operating lever 704 laterally undesirably twisting during later operation and thus spilling out of the bearing carrier 726 again. As a result, an anti-rotation is formed, which may alternatively be provided by a separate guide member.
  • the actuating devices 800, 900 of FIGS. 13 and 14 show modified tool connection contours 830, 930 of the ball head 812, 912.
  • the tool connection contour 830 is provided as a hexagon on the pin 812 a of the ball head 812.
  • the recess 931 is provided on the Anformung 923 of the actuating lever 904.
  • the tool connection contour 930 is provided here as an inner hexagon aligned with the recess 931.
  • the respective ball head 812, 912 can also be screwed into the housing 813, 913 like gear back wall, if this is already connected to the actuating lever 804, 904 is connected.
  • the operating lever 804 In order to reach the tool connection contour 830 on the pin 812a of the ball head 812, the operating lever 804, for example, is gripped from radially outward with the tool. If the ball head 912 is provided with a tool connection contour 930 mounted on the front side, the tool can be used directly from the front through the recess 931 of the actuating lever 904 and the ball head 912 can be screwed in.
  • actuators forces are transmitted in both directions, so that play in the bearings and contact points is to minimize, as in contrast to unilaterally loaded actuators an existing game can not be eliminated by one-sided load but at each change of direction leads to unwanted free travel.
  • the game can be minimized by very precisely manufactured parts and precisely matched contact partners at all contact points. If wear-resistant or at least low-wear material combinations are provided at the same time, the play over the service life of an actuating device can be be kept ring.
  • a further advantageous embodiment, to bias all contact points in one direction shows the actuator 1000 of Figure 15.
  • the contact points a change of direction of force and an associated game passage between the two contact flanks of the two-sided connection points is allowed at the contact points.
  • the biasing force is given at which operating force level as Ein- or Ausgurkraftset the play passage takes place at the respective contact point.
  • the low-biased contact points is that game passages can be distributed to the individual contact points on the operating force characteristic and so not necessarily all game passages at the zero crossing of the actuating force occur simultaneously.
  • the actuating device 1000 of FIG. 15 shows the shaped spring 1034 with two functions of two separate biasing springs 1035, 1036, which bias the contact points between the coupling rod 1010 and the yoke 1020 on the one hand and the yoke 1020 and fork heads 1021.
  • the shaped spring 1034 is supported between an end face of the fork heads 1021 and the yoke 1020 and presses against the end face of the coupling rod 1010th
  • the contact points between the radially inner fork heads 1029 of the actuating lever 1004 and the bearing surfaces 1001 of the bearing support 1026 are of two leaf spring-like spring tabs 1037th biased, which are fixed to the actuating lever 1004 and press against the contact flanks of the bearing carrier 1026.
  • the operating lever 1004 always abuts the opposite flank of the bearing bracket 1026 when the actuator 1000 does not transmit an actuating force. Whether an edge change occurs during operation depends on the biasing force of the spring tabs 1037.
  • the spring tabs 1037 may be arranged between the contact point of the actuating lever 1004 and the contact flanks of the bearing carrier 1026 so that the actuating lever 1004 abuts the bearing carrier 1026 when overcoming its biasing force to bear on block. In a further variant, it may be provided for the spring tabs 1037 to be pressed onto the bearing carrier 1026 in addition to the contact points of the actuating lever 1004. As a result, only the shape of the actuating lever 1004 and the bearing carrier 1026 is relevant to the bearing clearance. As shown in Figure 15 can be provided that the two spring tabs 1037 are attached to a common spring plate associated with the already existing riveting of the holding plate 1024. The spring tabs 1037 may also be separate components which are fastened with their own fastening means on the actuating lever 1004. Furthermore, the spring tabs 1037 may be attached directly or indirectly to the bearing bracket 1026 and press the operating lever 1004.
  • the support point 1007 of the actuating lever 1004 is biased by the inherent elasticity of the here not visible, corresponding to the retaining plate 724 of Figure 10 formed holding plate 1024.
  • an insufficient bias spring characteristic of the ball head 1012 may be biased by separate springs such as spring plates, diaphragm springs, corrugated springs, conical springs and the like against the operating lever 1004 or the holding plate 1024.
  • a biasing spring can also be used to press the retaining plate 1024 against the actuating lever 1004 and bias in this way the ball head, for example by means of at least one plate spring, leaf spring, coil spring or the like.
  • FIG. 17 and 18 show the actuating device 1 100, which is slightly modified in comparison with the previously described actuating devices, in various views, wherein a part of the actuating lever 1 104 of FIG. 17 is cut out for better viewing on components lying behind it.
  • the actuating lever 1 104 is formed as a sheet metal part that offers sufficient rigidity by its laterally folded shape even with a small sheet thickness and thus a low material usage.
  • the actuating lever 1 104 is provided both at the drive point 1 105 and the output point 1 106 corresponding with clevis extensions 1 138, 1 139, 1 140.1 141, each on both sides of the contact pin 1 142, 1 143 of the coupling rod 1 1 10 engage around the actuating lever 1004 coupling yoke 1 120 and the bearing support 1 126.
  • the two extensions 1 138, 1 139 and 1 140, 1 141 which are respectively arranged on the opposite sides of a contact pin 1 142, 1 143 and ensure the transmission in both directions of actuation of a friction clutch are arranged slightly offset from each other. This facilitates the embossing and calibration of the later contact points in the production of the actuating lever.
  • support points can be created which are wider than the sheet thickness of the actuating lever 1 104 and are preferably work hardened. Furthermore, this allows a distance between the two diagonally opposite contact points are made exactly.
  • the actuating lever 1 104 is fixed to the housing and rotatably supported on the attached to a gear back wall, not shown axis 1 1 12.
  • the axis 1 1 12 has the ball head 712 of Figures 8 to 10 corresponding spherical thickening 1 1 12a, on which the actuating lever 1 104 is arranged pivotable and tiltable in different directions. If a movement of the actuating lever 1 104 can be limited to a predetermined pivoting movement, the axis 1 1 12 may be formed as a cylindrical body or provided at the bearing point of the actuating lever 1 104 a cylindrical thickening or taper. Alternatively, the axis 1 1 12 may be attached to the actuating lever 1 104 and the axis be accommodated by means of a arranged on a housing such as gear housing pivot bearing.
  • the actuating lever 1 104 rotates coaxially with the axis 1 1 12. This is fixed to the housing by means of the axially from the coupling side recesses of the actuating lever 1 104 by cross-bolts 1 145 with those attached to the transmission housing Bearing blocks 1 144 bolted on both sides.
  • the screws 1 145 are achieved by a tool which is axially guided by the friction clutch with mounted friction clutch. In this case, corresponding gaps are used or provided corresponding recesses in the friction clutch.
  • the friction clutch can be used with it attached actuation bearing 1 102 and bearing support 1 126 and plugged thereon operating lever 1 104 in the clutch bell.
  • Figures 19 and 20 show the actuator 1200 with respect to the
  • Actuating device of Figures 17 and 18 modified housing fixed recording of the actuator 1200.
  • the axis Verschrau- axle 1212 takes place radially by means of screws 1245 to the attached to the gear housing 1213 or on this integrally received bearing blocks 1244 and is radially aligned.
  • the attachment is simplified from radially outside axially between the actuating lever 1204 and the gear housing 1213.
  • the tool is introduced, for example, through an opening in the clutch bell, through which the actuating lever 1204 protrudes from the clutch bell.
  • FIG. 20 shows the actuating device 1200 from radially outward from the same perspective, which can be seen through a corresponding opening provided in the clutch bell. It can be seen that the bolts 1245 of the axle 1212 are recognizable and accessible from above.
  • FIG. 21 shows the actuating device 1300, in which the bearing blocks 1344 are provided with slots 1346. If the bearing blocks 1344 formed from the transmission housing or connected to the transmission housing and receiving the axle 1312 have slots 1346 instead of holes for the bolts 1345, assembly is facilitated. Through the slots 1346, a preferably secured against loss pre-assembly of the screws 1345 on the Axis 1312 carried out before mounting the actuator 1300 in the clutch bell. During assembly, therefore, only a positioning of the screws 1345 in the slots 1346 and subsequent tightening of the pre-mounted on the axis 1312 screws 1345 is necessary.
  • Figure 22 shows a possible bias of the contact points of the actuators 1 100, 1200, 1300 of Figures 17 to 21. Both at the drive point 1 105 and at the output point 1 106 corresponding, connected to the operating lever 1 104 and against the yoke 1 120 or against the bearing carrier 1 126 prestressed spring plates 1 134, 1 137, for example, leaf spring tabs, springs and the like may be provided.
  • Figures 23 to 25 show in different views the actuator 1400.
  • the actuator 1400 In contrast to the previous actuators of the bearing support 1426 by means of the pivot bearing 1443 is rotatable and otherwise fixedly attached to the actuating lever 1404.
  • a housing-fixed and the bearing carrier 1426 and the actuating bearing 1402 leading and radially supporting guide sleeve can therefore be omitted.
  • this construction principle is particularly suitable for the actuation of double clutches, since two coaxially arranged arranged in a double clutch friction clutches actuation devices are required, which are formed radially nested, at least one actuator must encompass the other at least partially.
  • the absence of a guide sleeve facilitates the formation of such actuators.
  • the actuating device 1400 also shows the forged actuating lever 1204. However, the operating principle of the actuating device 1400 here is not coupled to a specific manufacturing method of the actuating lever 1404.
  • the actuating lever 1404 is driven by means of a drive which drives the actuating lever 1404 at the drive point 1405 by means of the coupling rod 1410, which is articulatedly coupled to the condyle 1420 of the actuating lever 1404.
  • the support point 1407 is supported by the hinge bearing 1412 fixed to the housing. By the joint head 1420 and the joint bearing 1412, the actuating lever 1404 can pivot in addition to the actuating direction and about its longitudinal axis.
  • the actuating bearing 1402 is thus gimbaled and can be adapted to slight misalignment of the friction clutch or its connection geometry, for example cup spring tongues.
  • the support point 1407 may also be mounted on a rigid axle.
  • Figures 26 to 31 show in different views and mounting conditions, the actuator 1500.
  • the support point 1507 is provided in the form of both on both sides of the operating lever 1504 mounted bearing pin 1547.
  • the bearing journals 1547 form a common axis of rotation of the actuating lever 1504 relative to the housing 1513, for example the gear housing or associated bearing blocks.
  • the drive point 1505 of the actuating lever 1504 only has to be connected to the drive, not shown.
  • the coupling rod 1510 is provided for this purpose, which by means of the slot 1549 surrounds the crowned clevis 1521 of the actuating lever 1504.
  • bearing journals 1547 may for example be rigidly connected to the actuating lever 1504 and rotate in the abutments 1544.
  • the movement point and the mounting interface can be structurally separated.
  • the bearing journal 1547 can be rotatably connected to the actuating lever 1504. be bound and then be inserted with oversize in the counter bearing 1544.
  • the bearing between the operating lever 1504 and bearing pin 1547 can be individually optimized, for example, minimum clearance or backlash.
  • the inclusion in the abutments 1544 can be independently optimized, for example, a firm and play-free seat.
  • the actuating lever 1504 are radially displaceable prepositioned on the gear back wall before the friction clutch is pushed into the clutch bell.
  • the actuating bearing 1502 and the bearing carrier 1526 are positioned, the actuating lever 1504 is - as shown in Figures 30 and 31 - pushed radially inward so that its fork head 1529 engages in the bearing bracket 1526.
  • the abutments 1544 may be provided with guide elements 1550 (FIGS. 28 to 31) or supplemented with other parts to form a guide for the operating lever.
  • the correct journal position can be secured to the counter bearings 1544 with guide elements 1550, for example by means of an additional snap connection.
  • the guided actuating lever 1504 always hits the snap connection 1548 from a precisely defined direction, some of the embodiments previously shown in FIGS. 26 and 27 can eliminate threading bevels on the counter bearings 1544 in favor of the guide elements 1550.
  • the assembly concept with a pre-positioned displaceable operating lever 1504 may be combined with a support point which, in addition to pivoting, also permits tilting about the longitudinal axis of the lever.
  • a combination of the actuators 1400 of Figures 23 to 25 and the actuators 1500 of Figures 26 to 31 may be provided.
  • the actuator 1400 is provided with a radially pluggable connection between actuating lever 1404 and thrust bearings corresponding to the bearing pin 1547 and thrust bearings 1544 of the actuator 1500.
  • the support point 1407 of the actuating lever 1404 relative to the housing slidably executed.
  • the joint bearing 1412 may for example be slidably mounted in a transmission-side fixed carrier or the carrier may receive the pivot bearing and be provided slidably relative to the transmission housing.
  • the actuating lever can also be displaced relative to the lever axle mounted on the transmission bottom.
  • actuators described in the preceding figures can be used in a similar manner in double clutches with two integrated friction clutches.
  • two similar actuators may be arranged offset around the axis of rotation of the double clutch over the circumference or be coaxially nested.
  • Figures 32 and 33 show the actuating system 8 in partial section and in a detail thereof with the two actuating systems 1600, 1700.
  • the actuating system 8 has two coaxially arranged actuating bearings 1602, 1702, each of which is connected to a friction clutch such as part clutch of a double clutch. Both actuating bearing 1602, 1702 are connected by means of a separate bearing support 1626, 1726, the operating levers 1604, 1704 and the coupling rods 1610, 1710, each with a drive, not shown. Both bearing brackets 1626, 1726 are centered on the common guide sleeve 1627 without the bearing brackets 1626, 1726 hampering or influence each other in their axial movement.
  • the radially outer bearing carrier 1626 engages with radially inwardly projecting extensions 1651 through slots 1751 in the inner bearing carrier 1726 and thus supports itself radially on the guide sleeve 1627.
  • the bearing brackets 1626, 1726 extend beyond pressure and tensile forces.
  • the inner bearing support 1726 is designed divisible to push the extensions 1651 of the outer bearing support 1626 in the slots 1751 can.
  • the webs 1752 between the slots 1751 are integrally formed on the bearing-side part of the inner bearing carrier 1726 and are suspended in the lever-side part of the inner bearing carrier 1726.
  • the compounds are biased.
  • Another embodiment is to make the inner bearing support 1726 in one piece and to provide the outer bearing support 1626 with removable radial extensions 1651.
  • the outer bearing support 1626 can be slid over the inner bearing support 1726 without the extensions 1651 until it slides over the slots 1751 of the bearing support 1726 is located.
  • the projections 1651 are set from radially outside into the slots 1751, pushed under the annular body 1753 of the bearing carrier 1726 and fixed there. Untitled.
  • the extensions 1651 may be secured from radially inward to the outer bearing bracket 1626.
  • the mounting of the projections 1651 takes place through the inner bearing carrier 1726 through which is not yet mounted on the guide sleeve 1627 at this time. Regardless of how the bearing brackets 1626, 1726 are formed, they can be connected in advance via the actuating bearing 1602, 1702 with the corresponding friction clutch. As a result, the assembly of the double clutch and the actuating system 8 takes place in accordance with the previously described actuators.
  • the bearing carrier 1626, 1726 are pushed in the assembly of the double clutch on the guide sleeve 1627 and then the two actuating levers 1604, 1704 on the contact pins 1654, 1754 of the respective bearing support 1626, 1726 plugged.
  • an anti-rotation device is provided on these. This can be done on the guide sleeve 1627, for example by means of one or more guide webs, a shape deviating from the cylindrical shape of this and the like. Alternatively, the bearing brackets 1626, 1726 can be prevented from rotating by the associated operating lever 1604, 1704.
  • bearing supports 1626, 1726 have a rotationally symmetrical connection contour, for example, by a circumferential groove such as an annular groove - as indicated for example in Figures 2 to 7 - or by a circumferential survey, can be dispensed with a positive rotation. Since in this case by means of the rotationally symmetrical connection contour of the bearing carrier, the operating lever can not unhook, small rotational movements of the bearing carrier are unproblematic.
  • the drive-side end of the lever as drive point protrudes radially outward from the clutch bell and is connected there to the drive.
  • the actuators may alternatively be used in clutch bells in which no openings are provided for the actuating lever.
  • the connection of the actuating lever with the drive takes place within the clutch bell.
  • This can be provided, for example, for a drive arranged inside the clutch bell or for a drive arranged outside the clutch bell with the connection of the actuating lever and the drive, for example the coupling rod such as piston rod, threaded spindle and the like, to the outside be.
  • the coupling rod such as piston rod, threaded spindle and the like

Landscapes

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

Abstract

L'invention concerne un moyen d'actionnement (100) destiné à un embrayage à friction (1) actionné sur un chemin d'actionnement et équipé d'un levier d'actionnement qui est actionné par un moyen d'entraînement au niveau d'un point d'entraînement (105), qui est reçu à rotation autour d'un pivot en étant immobile par rapport au boîtier au niveau d'un point d'appui (107), et qui sollicite axialement au niveau d'un point de sortie (106) un ressort de levier de l'embrayage à friction en étant découplé en rotation. Pour pouvoir actionner l'embrayage à friction dans les deux sens, le point d'entraînement, le point d'appui et le point de sortie sont configurés de façon à transmettre les forces axialement dans les deux sens.
EP14761783.1A 2013-08-07 2014-07-16 Moyen d'actionnement pour embrayage à friction Withdrawn EP3030800A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013215579 2013-08-07
PCT/DE2014/200323 WO2015018409A1 (fr) 2013-08-07 2014-07-16 Moyen d'actionnement pour embrayage à friction

Publications (1)

Publication Number Publication Date
EP3030800A1 true EP3030800A1 (fr) 2016-06-15

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EP14761783.1A Withdrawn EP3030800A1 (fr) 2013-08-07 2014-07-16 Moyen d'actionnement pour embrayage à friction

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EP (1) EP3030800A1 (fr)
CN (1) CN105393014A (fr)
DE (2) DE102014213884A1 (fr)
WO (1) WO2015018409A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102017221419A1 (de) * 2017-11-29 2019-05-29 Zf Friedrichshafen Ag Betätigungseinrichtung einer Reibungskupplung
KR102360572B1 (ko) * 2019-10-16 2022-02-10 오토딘시스 주식회사 신규한 구조의 회전축 어셈블리
DE102021101141B4 (de) 2021-01-20 2022-08-18 Schaeffler Technologies AG & Co. KG Abkoppelvorrichtung und Abkoppelsystem
DE102021132822B3 (de) 2021-12-13 2022-11-03 Schaeffler Technologies AG & Co. KG Kupplung mit beidseitig betätigbarem Kolben und mechanischen Rastierelementen
DE102021132819B3 (de) 2021-12-13 2022-11-10 Schaeffler Technologies AG & Co. KG Kupplung mit beidseitig beaufschlagbarem Kolben und Anschlagscheibe
DE102021132821B3 (de) 2021-12-13 2023-01-05 Schaeffler Technologies AG & Co. KG Kupplung mit beidseitig beaufschlagbarem Kolben und axialelastischer Endanschlagscheibe für Schiebemuffe
DE102021132824B3 (de) 2021-12-13 2022-12-22 Schaeffler Technologies AG & Co. KG Kupplung mit beidseitig unter Druck setzbarem Kolben und Kragarm aufweisendem Schnappverschluss

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WO2001061205A1 (fr) * 2000-02-15 2001-08-23 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Dispositif de transmission de couple pourvu d'un dispositif de debrayage
DE102004019280A1 (de) * 2004-04-21 2005-11-17 Zf Friedrichshafen Ag Kupplung
KR100586774B1 (ko) * 2004-06-28 2006-06-08 재단법인 전주기계산업리서치센터 세미오토 클러치 구동장치 및 구동방법
DE102006050956A1 (de) 2005-11-19 2007-05-24 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Ausrückvorrichtung insbesondere zur Betätigung einer Fahrzeugkupplung
DE102007047912A1 (de) * 2007-12-03 2009-06-04 Zf Friedrichshafen Ag System zur automatisierten Betätigung einer Kupplung eines Antriebsstrangs eines Kraftfahrzeugs
CN201184377Y (zh) * 2008-04-09 2009-01-21 新疆八一钢铁股份有限公司 冷轧平整机组的齿式离合器
FR2976989B1 (fr) * 2011-06-23 2013-10-18 Valeo Embrayages Dispositif d'actionnement d'un embrayage, notamment pour vehicule automobile
CN202228561U (zh) * 2011-09-23 2012-05-23 孔凡鲁 一种干片摩擦离合器拨叉装置

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Also Published As

Publication number Publication date
DE112014003642A5 (de) 2016-04-21
DE102014213884A1 (de) 2015-02-12
WO2015018409A1 (fr) 2015-02-12
CN105393014A (zh) 2016-03-09

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