Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D13/00—Friction clutches
  • F16D13/58—Details
  • F16D13/583—Diaphragm-springs, e.g. Belleville
  • F16D13/585—Arrangements or details relating to the mounting or support of the diaphragm on the clutch on the clutch cover or the pressure plate

Definitions

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

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

Applications Claiming Priority (2)

Publications (1)

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Family Applications (1)

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Cited By (1)

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• 2013
  • 2013-05-29 CN CN201380030797.3A patent/CN104379955B/zh not_active Expired - Fee Related
  • 2013-05-29 EP EP13727094.8A patent/EP2861883A1/de not_active Withdrawn
  • 2013-05-29 DE DE102013209993A patent/DE102013209993A1/de not_active Withdrawn
  • 2013-05-29 WO PCT/EP2013/061003 patent/WO2013186046A1/de active Application Filing
  • 2013-05-29 DE DE112013002928.6T patent/DE112013002928A5/de not_active Withdrawn

Non-Patent Citations (2)

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