WO2014173406A1 - Corps de rampe pour système de rampes d'un dispositif d'ajustement - Google Patents

Corps de rampe pour système de rampes d'un dispositif d'ajustement Download PDF

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Publication number
WO2014173406A1
WO2014173406A1 PCT/DE2014/200147 DE2014200147W WO2014173406A1 WO 2014173406 A1 WO2014173406 A1 WO 2014173406A1 DE 2014200147 W DE2014200147 W DE 2014200147W WO 2014173406 A1 WO2014173406 A1 WO 2014173406A1
Authority
WO
WIPO (PCT)
Prior art keywords
ramp
counter
ring
adjusting
pressure plate
Prior art date
Application number
PCT/DE2014/200147
Other languages
German (de)
English (en)
Inventor
Gerd Ahnert
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 DE112014002152.0T priority Critical patent/DE112014002152B4/de
Publication of WO2014173406A1 publication Critical patent/WO2014173406A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/75—Features relating to adjustment, e.g. slack adjusters
    • F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate
    • 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
    • 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
    • F16D2021/0684—Mechanically 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
    • 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
    • F16D2021/0692—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 with two clutches arranged axially without radial overlap

Definitions

  • the invention relates to a ramp body for a ramp system of an adjusting device for adjusting a wear-related misalignment of a pressure plate to a counter plate of a friction clutch, wherein the ramp body can be rotated relative to a counter ramp to compensate for increased by wear of friction linings of the friction clutch stroke of the pressure plate at least partially ,
  • Friction clutches can compensate for the occurrence of wear
  • a friction clutch with a travel-controlled adjusting device in which a drive pawl of a sensing plate which axially displaces depending on the distance of an actuating system with a plate spring and a pressure plate acts on a pinion of a spindle , Wherein a spindle nut accommodated on the spindle, when the spindle is rotated, rotates a ramp ring of a ramp system arranged between the pressure plate and the cup spring relative to a counter ramp of the pressure plate, whereby the original distance of the actuating system to the pressure plate is restored.
  • the drive pawl slides on the teeth of the pinion and engages with a predetermined wear in a tooth gap between two teeth.
  • the drive pawl positively engages the pinion during the next opening operation of the friction clutch and thereby rotates the pinion and thus the spindle, whereby the spindle nut is moved along the spindle and rotates the ramp ring by a corresponding angular amount to thereby adjust the friction clutch.
  • Adjusting devices with such an actuation principle are hereinafter also referred to as "TAC spindle”.
  • TAC spindle Adjusting devices with such an actuation principle are hereinafter also referred to as "TAC spindle".
  • the plate spring can rest during a readjustment process with a remaining spring force, whereby the resulting clamping force on the ramp ring can be overcome by the adjusting force applied by the drive pawl to the spindle.
  • a double clutch with two friction clutches in which a wear-related incorrect distance of a pressure plate to a counter-plate can be compensated via a path-controlled adjusting device.
  • the adjusting device has a sensing ring which slides on a counter-ramp of a coupling housing part and is acted upon in the peripheral direction by a spring force of a tension spring relative to the coupling housing part.
  • the Sensierring is frictionally locked by means of a riveted to the coupling housing part clamping spring against a designed as a plate spring lever spring for axially moving the pressure plate relative to the counter plate. Between the pressure plate and the counter plate provided with friction linings clutch disc can be pressed frictionally to transmit a torque.
  • the ring-shaped clamping spring is coupled to the plate spring, so that the plate spring elastically deflects the clamping spring away from the Sensierring at a correspondingly large stroke of the plate spring, whereby the clamping force of the clamping spring is reduced to the Sensierring or even the clamping spring can lift off the Sensierring.
  • the stroke of the plate spring is so great that the sensing ring can overcome the frictionally applied clamping force of the clamping spring, whereby the sensing ring is rotated in the circumferential direction by an angular amount by the spring force applied by the tension spring.
  • the sensing ring configured ramp-shaped in the axial direction slides on the counter-ramp of the coupling housing part, whereby the axial distance increases again until the clamping force of the clamping spring bent away elastically from the disc spring is sufficient to frictionally block the sensing ring from further movement in the circumferential direction.
  • the plate spring can strike the sensing ring at a point displaced in the axial direction due to the twisted sensing ring, so that the plate spring lifts off from an adjusting ring for adjusting the wear-related incorrect spacing or at least reduces a clamping force on the adjusting ring.
  • the adjusting ring is also acted upon in the circumferential direction with a spring force, so that the ramp-shaped adjusting ring in the axial direction can slide on a corresponding counter-ramp of the pressure plate until the clamping force provided by the plate spring is again sufficient to prevent further rotation of the adjusting ring.
  • the adjusting ring can thereby bridging in the axial direction a greater distance between the plate spring and the pressure plate, whereby the wear-related fault clearance of the pressure plate is adjusted to the counter plate and the plate spring with a correspondingly lower stroke, the pressure plate can move to the counter plate.
  • Adjusting devices with such an actuation principle are also referred to below as "TAC-2VR".
  • the spring force acting in the circumferential direction on the sensing ring or on the adjusting ring can overcome the clamping force acting on this respective ramp ring.
  • the object is achieved by a ramp body for a
  • a ramp body for a ramp system of an adjustment device for adjusting a wear-related misalignment of a pressure plate to a counter plate of a friction clutch is provided with a substantially circumferentially extending base, a protruding from the base ramp, the ramp has a ramp surface for sliding on a counter ramp, wherein the ramp surface in the circumferential direction has a deviating from a linear course with a constant slope irregular course.
  • a transmission ratio of an amount of change in the extent of the ramp system in the axial direction can be changed as a function of an amount of a torsion angle change compared to a linear progression with a constant gradient.
  • the transmission ratio of the ramp system with such a ramp body is not constant over the entire wear range but variable. This makes it possible to react on the wear range changing force conditions with an achievable by the irregular contouring of the ramp surface of the ramp body variable translation of the ramp system.
  • a return spring designed in particular as a leaf spring can be provided for displacing a pressure plate of a friction clutch into an open starting position, in particular, if no actuating force is exerted on the pressure plate, which exerts a clamping force on the ramp ring of the adjusting device, without the need for too high an adjusting force. especially at a decreasing spring force of the return spring over the wear area, the displacement of the pressure plate is affected by the return spring or even thwarted. For these effects It is not necessary to increase the space requirement compared to ramp bodies with a constant pitch. Instead, even the space requirement can be reduced.
  • the gear ratio of the ramp system of the adjusting device with such a ramp body can be adapted to changing over the wear area force ratios, which makes it possible to maintain a readjustment function of an adjusting without a.
  • a large wear area of a friction clutch Endanger the functionality of the friction clutch.
  • the base of the ramp body can be, for example, a closed ring body, from which the at least one ramp protrudes in the axial direction.
  • the ring body can be made, for example, from a metal sheet, so that the ramp body can form a ramp ring used in particular as an adjusting ring and / or as a sensing ring.
  • the ramp body forms a Gegenrampe, so that for example the base can be formed by a clutch cover, a pressure plate or between the pressure plate and an actuating element, in particular lever spring, in the power flow path intermediate component.
  • a plurality of ramps are provided, which are arranged in particular on a common diameter and are preferably uniformly distributed in the circumferential direction.
  • the ramp body can be designed in a developed representation comparable to a sawtooth profile, wherein the ramps can connect directly behind one another and / or in the circumferential direction subsequent ramps can be positioned spaced apart from each other over a distance.
  • the ramp surface has an extent in the circumferential direction, which corresponds in particular at least to the maximum intended angle of rotation of the ramp system of the adjusting device. Compared to the extent of the ramp surface in the circumferential direction, the extent of the ramp surface in the radial direction can be made smaller.
  • the ramp body may for example be made of a metal sheet, so that the radial extent of the ramp surface may correspond to the sheet thickness.
  • the slope of the ramp surface in the radial direction is substantially constant.
  • An irregular course in the circumferential direction is essentially understood to mean a non-linear course whose pitch changes at least once in the circumferential direction.
  • the ramp surface has at least two partial regions with gradients which are different in the circumferential direction, the gradient of the ramp surface changing continuously in particular along the circumferential direction.
  • the partial regions can have a significant extent in the circumferential direction, so that the partial regions can be connected to one another via a corner at which the gradient changes abruptly.
  • the course of the ramp surface in the circumferential direction can thereby be partially linear, whereby a substantially angular course can result.
  • the partial regions preferably have an infinitesimal small extent in the circumferential direction, so that a sudden change in the gradient can be avoided.
  • the course of the ramp surface in the circumferential direction can be carried out smoothly and without corners.
  • a curved course can result which, for example, corresponds to the course of a curve based on a polynomial, in particular a quadratic polynomial.
  • the course can also be exponential or logarithmic.
  • the ramp surface is at least partially concave and / or convex in the circumferential direction.
  • a concave and / or convex configuration of the ramp surface can be easily taken into account in the production.
  • the ramp surface is punctiform and / or linearly applied to an opposite counter ramp. As a result, it is particularly easy to set a desired pitch and a corresponding gear ratio at a specific angular position.
  • the ramp body can be produced by punching or milling, in particular roll milling. This makes it possible to produce the ramp body easily, wherein it is possible, in particular, to provide the contouring of the ramp surface without additional machining processes.
  • the ramp body is as a pressure plate of a friction clutch, as
  • Clutch cover of a friction clutch designed as an adjusting ring of an adjusting a friction clutch and / or as a sensing ring of an adjusting a friction clutch.
  • the ramp body can already function as a fully functional component be provided without it being necessary to connect the ramp body with a component acting as a carrier separately.
  • the ramp body may in particular be part of a friction clutch, the rest of its structural design as described in DE 10 2009 035 225 A1, WO 2009/056092 A1, WO 2008/058508 A1, the contents of which are hereby incorporated by reference as part of the invention.
  • the invention further relates to an adjusting device for adjusting a wear-related incorrect spacing of a pressure plate to a counter-plate of a friction clutch with a rotatable relative to a counter-ramp ramp ring, wherein the ramp ring and / or the counter-ramp is designed as a ramp body, which may be as described above and further developed ,
  • the ramp ring and the counter ramp can in this case form a ramp system of the adjusting device.
  • the adjusting device has a clamping spring which presses the ramp ring against the counter ramp with a clamping force.
  • the transmission ratio of the ramp system of the adjustment device can be adapted to force conditions changing over the wear region, thereby making it possible to maintain an adjustment function of an adjustment device without the functionality of the friction clutch Risk of friction clutch.
  • a first ramp surface of the ramp ring pointing towards the counter ramp and a second ramp surface of the counter ramp facing the ramp ring are contoured differently in the circumferential direction, wherein in particular the ramp ring abuts the counter ramp essentially in a punctiform or linear manner.
  • the other ramp surface is designed, for example, convex.
  • the ramp ring is pressed with a, in particular over the angle of rotation of the ramp ring relative to the counter ramp variable, clamping force F K against the counter ramp, wherein on the ramp ring and / or on the counter ramp one, in particular over the angle of rotation of the ramp ring relative to the counter ramp variable, adjusting force F N acts for relative rotation of the ramp ring relative to the counter ramp in a readjustment situation, the course of the ramp surface of the ramp body being designed in such a way, that at a first angle of rotation of the ramp ring relative to the counter ramp, in which a lower clamping force F K and / or a higher adjusting force F N is present, a higher local slope and at a second angle of rotation of the ramp ring relative to the counter ramp, in which a higher clamping force F K and / or a lower adjustment force F N is present, a lower local slope is provided.
  • the clamping force F K is less than or equal to the second angle of rotation, wherein at the first angle of rotation, the adjusting force F N is greater than or equal to the second angle of rotation. If the clamping force F K changes with a change in the angle of rotation, the adjusting force F N can remain constant. If the adjusting force F N changes as the angle of rotation changes, the clamping force F K can remain constant. Preferably, both clamping force F K and the adjusting force F N changes when the angle of rotation changes. At the first angle of rotation, the clamping force F K of the adjusting force F N can be overcome more easily, so that it is possible to provide a higher slope for the ramp surface.
  • the increased moment of resistance due to the increased slope can easily be overcome by the adjusting force F N at the first twist angle.
  • a lower slope of the ramp surface is provided, so that the resistance moment can be reduced in order to rotate the ramp ring safely in a readjustment without risking jamming.
  • the adjusting force F N to a required Minimalnachstellkraft F N, min to overcome the clamping force F K for rotation of the ramp ring relative to the counter-ramp in a Nachstellsituation by an amount AF N is greater, with the profile of the ramp surface of the ramp body is configured such is that at least in a partial region of the angle of rotation of the ramp ring relative to the counter-ramp, the amount AF N is substantially constant, wherein in particular the amount AF N corresponds to an intended minimum safety amount AF N min .
  • An unnecessarily large distance between the currently provided adjustment force F N and the currently required minimum adjustment force F N min can thereby be avoided.
  • the adjustable wear area can instead be increased and / or the demands on the springs for providing the clamping force F K and / or the adjusting force F N can be reduced.
  • the invention further relates to a friction clutch for coupling a drive shaft of a motor vehicle engine having at least one transmission input shaft of a motor vehicle transmission, with a counter plate, a relative to the counter plate axially displaceable pressure plate for frictional pressing a clutch disc between the pressure plate and the counter plate and an adjusting device, as described above - and further- may be formed for adjusting a wear-related pitch of the pressure plate to the counter plate, in particular a lever feeder for displacing the pressure plate is provided relative to the counter plate and the lever spring for changing a force acting between the ramp ring and the counter ramp clamping force F K is configured.
  • the transmission ratio of the ramp system of the adjusting device can be adapted to changing over the wear range force ratios, which makes it possible to maintain a readjustment function of an adjustment without the operability of the friction clutch to a large wear area of the friction clutch compromise.
  • the lever spring for example, exert on the ramp ring and the counter ramp an actuating force for displacing the pressure plate, as can be done with TAC spindle friction clutches, and / or reduce a stop the clamping force of acting on the ramp ring and the counter ramp clamping spring, as with TAC 2VR friction clutches.
  • 1 is a schematic sectional view of a friction clutch according to the TAC-2VR principle
  • FIG. 2 shows a schematic perspective view of a friction clutch according to the TAC spindle principle
  • FIG. 3 is a schematic sectional view of the friction clutch of FIG. 2,
  • FIG. 4 shows a schematic sectional view along a development of a ramp system in a first embodiment for the friction clutch from FIG. 1 or FIG. 2, FIG.
  • FIG. 5 shows a schematic sectional view along a development of a ramp system in a second embodiment for the friction clutch from FIG. 1 or FIG. 2
  • FIG. 6 shows a schematic diagram of the force ratios achievable with the aid of the invention
  • FIG. 8 is a schematic diagram of the force and travel conditions of a ramp system in a first embodiment of the invention.
  • FIG. 9 shows a schematic diagram of the force and travel conditions of a ramp system in a second embodiment of the invention.
  • the illustrated in Fig. 1 double clutch 1 comprises two friction clutches 2, 3, which are shown in the disengaged, ie open state.
  • the dual clutch 1 comprises two clutch plates 4, 5, which can be connected to different transmission input shafts, wherein the motor vehicle transmission having these shafts can advantageously form a so-called power shift transmission, which can have two partial transmissions.
  • the clutch discs 4, 5 bear radially outside friction linings 6, 7, which can be pressed axially between a two friction clutches 2 and 3 common counter-plate 8 and a respective friction clutch 2 and 3 associated pressure plate 9, 10. Due to the common central plate, which forms the counter-plate 8 for both friction clutches 2, 3, a double clutch according to the so-called "three-plate design" results for the double clutch 1.
  • the counter-plate 8 forms part of a flywheel which is connected to a drive shaft of a flywheel
  • the counterplate 8 is connected via axially extending regions, which are not shown here in detail, to a drive plate or a drive cage 1 1.
  • the drive plate 11 is designed as a driver ring Counter plate 8 and the drive plate 1 1 manufacture, can either be formed on the counter plate 8 or on the drive plate 1 1 or at least partially provided on both parts 8, 1 1.
  • the drive plate 1 1 can either a kind of torque converter with a For example, strigocon, a provided on the crankshaft of the drive motor drive plate be ubbar or connectable to a motor side arranged drive element via an axial connector.
  • the counter-plate 8 is mounted on the transmission side via a bearing 38 and fixed at least in an axial direction in order to axially intercept the closing forces required for at least one of the friction clutches.
  • the counter plate 8 can therefore be mounted on a transmission input shaft or axially supported. However, it can also be accommodated and axially supported on a fixedly connected to the transmission housing support tube or support tube.
  • the clutch discs 4 and 5 have axially between their two annular
  • Friction linings 6 and 7 a so-called lining suspension, which ensure a progressive construction and degradation of the transferable from the friction clutches 2, 3 torque over at least a portion of the actuation path.
  • the pressure plate 9 is indirectly or directly preferably via leaf spring-like elements with the counter-plate 8 rotatably, but limited axially displaceable connected.
  • the pressure plate 10 of the friction clutch 3 is drivingly coupled to the counter plate 8 in a similar manner.
  • a clutch cover 12 is attached, which is designed here as a metal cover. Axial on both sides of this clutch cover 12 are provided in an annular arrangement provided lever springs 13, 14, by means of which the respectively associated friction clutch 2, 3 can be actuated.
  • the lever springs 13, 14, which are designed in particular as disc springs, can each form a ring-like component which has dish-spring-like properties, that is, is resiliently variable in its conicity.
  • These disc springs 15, 16 preferably each have a spring property which ensures that they tend to position themselves in a frusto-conical position which corresponds to an open state of the friction clutches 2 and 3.
  • the pressure plate 10 carries traction means 17 which extend axially and at their the
  • Anpressplatte 10 end facing away 18 carry a pivot bearing or Abubalzauflage 19, on which the lever spring 16 is supported tiltable or pivotable.
  • the Abubalzauflage 19 is integrally formed with the traction means 17 and formed by a radially inwardly directed annular area.
  • a tie rod 17 is formed.
  • the traction means 17 may be formed by individual distributed over the circumference hook-like components. In an advantageous manner, however, these traction means 17 can also be combined to form a component, preferably made of sheet metal, which has a preferably closed annular region, from which a plurality of axial legs can extend, which are firmly connected to the pressure plate 10.
  • the traction means 17 form a tie rod 17.
  • the lever spring 16 Radially within the rolling support 19, the lever spring 16 is supported on an annular support ring 20.
  • the annular support ring 20 is clamped axially between the clutch cover 12 and the lever spring 16 and forms part of an adjusting device 21, by means of which at least the wear occurring on the friction linings 7 can be compensated for at least partially automatically.
  • the radially inner spring tongues 22 of the lever spring 16 are acted upon in the left direction.
  • a closing force, at least substantially in the friction clutch 3 introductory actuating element, such as an actuating bearing is provided.
  • Such an actuator forms part of an actuating system, which may be formed as a pneumatic, hydraulic, electrical or mechanically actuated actuating system or has a combination of the aforementioned actuation options, that is, for example, designed as an electro-hydraulic actuation system.
  • actuating system which may be formed as a pneumatic, hydraulic, electrical or mechanically actuated actuating system or has a combination of the aforementioned actuation options, that is, for example, designed as an electro-hydraulic actuation system.
  • Suitable lever elements 13, 14 or lever springs 15, 16 are described for example in DE 103 40 665 A1, DE 199 05 373 A1, EP 0 992 700 B1 and EP 1 452 760 A1.
  • spring means in particular leaf springs, which connect the components 8 and 10 together, preferably have a defined axial bias, which ensures that the pressure plate 10 is acted upon in the opening direction of the friction clutch 3.
  • the support ring 20 forms a so-called adjusting ring 20 which is axially supported by a ramp system on the clutch cover 12.
  • the ramp system has ramps extending in the circumferential direction and rising in the axial direction.
  • Corresponding ramps can be formed directly on the adjusting ring 20 and cooperating with these counter ramps can be introduced in an advantageous manner directly in the region of the housing bottom of the clutch cover 12.
  • the adjusting device 21 further comprises a sensor device 23, which has a
  • Sensierring 24 which is supported in a similar manner, as described in connection with the adjusting ring 20, via a ramp system on the housing bottom of the clutch cover 12 and circumferentially acted upon in the adjustment direction by a spring.
  • the Sensierring 24 is here axially disposed between the clutch cover 12 and the outer regions of the lever spring 16, and here at the radial height of the Abisselzauflage 19th
  • the sensor device 23 furthermore has a sensor element 25, in particular designed as a clamping spring, which preferably has axially resilient regions.
  • the sensor element 25 clamps, if no wear has occurred, the sensing ring 24 axially, so that it is then held non-rotatably.
  • the sensor element 25 has stop regions 26 which can cooperate with counter-stop regions 27 carried by the traction means 17, in particular when wear occurs on the friction linings 7.
  • the axial arrangement of the stop regions 26 and counter stop regions 27 and the axial paths occurring between them when the friction clutch 3 is actuated are matched to one another such that when the friction clutch 3 is closed and there is no wear at most, only a contact between the stop regions 26 and the counterstop regions 27 can take place.
  • the sensor element 25 having the abutment regions 26 may be formed by an annular component which, viewed over the circumference, has individual, preferably uniformly distributed, fastenings to the clutch cover 12.
  • the existing between these fasteners areas of the annular sensor element 25 carry the stop areas 26.
  • the provided in the circumferential direction between the fasteners areas of the sensor element 25 are elastically or resiliently deformable in the axial direction. For some applications, it may be expedient if these areas are also exposed to a torsional stress causing at least a slight twisting of at least the laterally of the abutment portions 26 circumferentially extending regions of lesser radial width.
  • the lever spring 15 of the friction clutch 2 is provided opposite to the lever spring 16 axially on the other side of the radial portions of the clutch cover 12.
  • the lever spring 16 is supported with a radially outer region on a support ring or as Nachstellring 28 configured adjusting.
  • the adjusting ring 28 is in a similar manner as described in connection with the adjusting ring 20, rotatable relative to the clutch cover 12 and axially supported on this via a ramp system.
  • the adjusting ring 28 forms part of an adjusting device 29 which is effective between the radial regions of the clutch cover 12 and the lever spring 15.
  • torque transmitting means are provided, which are preferably formed by leaf springs, which are axially biased so that the pressure plate 9 is pressed axially against the lever spring 15.
  • the total axial force which acts on the lever spring 15 in the direction of the right, is dimensioned such that during operation of the clutch unit 1, an axial displacement or pivoting of the lever spring 16 due at least to resonance phenomena and / or axial vibrations or tumbling oscillations of at least one Components of the clutch unit is prevented.
  • additional energy storage devices or spring elements may be provided in addition to the leaf spring elements. hen, which act on the pressure plate 9 or directly on the lever spring 15.
  • the clutch cover 12, the lever spring 13 and arranged between the clutch cover 12 and the lever spring 13 adjusting device 29 together form a clutch cover assembly 40, which can be installed as a common unit. Additionally or alternatively, the lever spring 14 and arranged between the clutch cover 12 and the lever spring 14 adjusting 23 together form the clutch cover assembly 40, wherein in particular the clutch cover 12, the lever springs 12, 13 and the adjusting devices 23, 29 form the clutch cover assembly 40, the in this embodiment is designed specifically for the operation of dual clutches.
  • the adjusting device 29 further comprises a sensor device 30, which is arranged radially inside and spaced from the adjusting ring 28 here.
  • the sensor device 30 comprises a sensing ring 31 which, like the sensing ring 24, is rotatable relative to the clutch cover 12 and supported by a ramp system.
  • the sensor device 30 has a sensor element 32 configured in particular as a clamping spring, which is carried either indirectly or directly by the clutch cover 12.
  • the sensor element 32 has at least one, preferably a plurality of stop regions 33 distributed over the circumference, which interact with counterstop regions 34 at least when wear occurs on the friction linings 6 of the clutch disk 4.
  • the counter-abutment portions 34 may be formed by elements connected to the lever spring 15.
  • the sensor element 32 has regions 35 which cooperate with axial prestressing at regions 36 of the sensing ring 31. Due to the axial prestressing of at least the regions 35, the sensing ring 31 is clamped axially, so that a rotation of the same at least in the absence of wear on the friction linings 6 is avoided. As a result, an uncontrolled, not attributable to wear adjustment of the adjusting device 29 is avoided.
  • the sensor element 32 may also be formed by an annular member which is similarly formed connected to the clutch cover 12 and effective, as described in connection with the sensor element 25.
  • the axial distance between the abutment regions 33 and the counter abutment regions 34 is dimensioned such that when the friction clutch 2 is completely closed and there is no wear on the friction linings 6, only a touch or slight contact between these regions 33 and 34 takes place, which ensures that the sensing ring 31 against rota- on blocked.
  • the closing of the friction clutch 2 is carried out in a similar manner as has been described in connection with the friction clutch 3. It is introduced by means of an actuating device, a closing force in the region of the spring tongues 37 of the lever spring 15. This closing force is gradually built up, and that until the axial force exerted on the pressure plate 9 sufficient to forward the torque output by the engine via the clutch disc 4 to the motor vehicle transmission.
  • the maximum contact force can have at least a constant value. However, it may also be advantageous to adjust this closing force accordingly depending on the operating state of the motor vehicle engine and the torque delivered thereby. This means that when the engine delivers only 50% of its nominal torque, the contact pressure can be reduced accordingly. A similar operation is also possible for the friction clutch 3.
  • the alternative embodiment of the friction clutch 2, 3 partially shown in Fig. 2 shows a pressure plate 9, 10 with a ramp system 42 and a twisting device 44.
  • the pressure plate 9, 10 has known elements for receiving on the clutch housing, for example, molded and optionally reworked Receivers 46 with openings 48 for attachment of energy storage devices such as leaf springs, which allow a rotationally fixed and axially displaceable connection to the clutch cover 12, wherein a bias voltage of the energy storage takes place in such a way that the pressure plate 9, 10 against the action of the energy storage by the action of force of the lever system is closed and returns to reducing the contact pressure by the lever system by the relaxing effect of the energy storage in the open position.
  • energy storage devices such as leaf springs
  • the openings 48 can be used in many ways and can serve, for example, for attaching an additional mass acting as an absorber mass, which can be displaced axially relative to the pressure plate.
  • On the pressure plate 9, 10 are on a predetermined radius circumferentially distributed counter ramps 50 incorporated, which may already be formed and machined in a representation of the pressure plate 9, 10 in a forging in the blank. Alternatively, for example, a pressing or a plastic part on the pressure plate 9, 10 are placed and secured.
  • a ramp ring 52 of corresponding diameter with circumferentially corresponding ramps 54 is placed on the counter ramps 50, which has an annular surface 56 which forms a contact surface for the lever system.
  • the ramp ring 52 can be fixed secured against loss on the counter ramps 50 at least for assembly.
  • the lever system and the clutch cover 12 is mounted immediately after placing the ramp ring 52.
  • the illustrated in Fig. 3 partial section of an embodiment of the friction clutch 2, 3 extends longitudinally through its axis of rotation 58, wherein only one half is shown with the adjusting device 29.
  • the friction clutch 2, 3 is formed from a clutch cover 12, in which a pressure plate 9, 10 by means not visible in this section energy storage rotatably and axially displaceable added.
  • a lever system 60 is received in the clutch cover 12 as a plate spring 62 having radially inner plate spring tongues 22 which are axially displaced by a release system, not shown.
  • the embodiment shown is a depressed friction clutch 2, 3, which is disengaged by pressing the disc spring tongues 22.
  • the plate spring 62 by means of two wire rings 64, 66 on the clutch cover 12 pivotally supported by not shown, both rings 64, 66 against each other bracing rivets supported to form a two-armed lever, wherein the radially outer force edge 68, the pressure plate 9, 10 against a counter plate, not shown 8 clamped under tension of friction linings, also not shown.
  • the ramp ring 52 is braced between the pressure plate 9, 10 and the plate spring 62, which cooperates with the pressure plate 9, 10 and the twisting device 44 with a drive wheel 70.
  • the adjusting device 29 is formed by a spring element 72 which is attached to the radially extending cover part of the clutch cover 12 and an axially bent part which forms a drive pawl 74, which is radially braced against the drive wheel 70.
  • a stop 76 which limits the prestressed spring element 72 in the direction of the pressure plate 9, 10, is formed by a bolt 78 or rivet, which passes through the spring element 72 and forms an axial stop for the spring element 72 by means of a head 80.
  • the pin 78 is axially limited against a stop 82 displaceably received in the clutch cover 12, so that when a loading of the head 80 by a contact surface 84 of the plate spring 62 at a large Ausgurweg the friction clutch 2, 3 of the pin 78 axially against the Biasing force of the spring element 72 is displaced, whereby this is taken and an optionally occurring adjustment is completed.
  • the spindle 88 is rotatably mounted in a holder 96 and connected to the pressure plate 9, 10.
  • the ramp system illustrated in FIG. 4 has a ramp body designed as a ramp ring 52, which has a base 98, from which ramps 54 pointing toward the counter ramp 50 protrude.
  • the ramps 54 have a technological from the base 98 ramp surface 100 which is rounded in the circumferential direction and has a non-linear course with a changing pitch, so that upon relative rotation of the ramp ring 52 to the counter ramp 50, in particular by the Pressure plate 9, 10 or the clutch cover 12 may be formed along a direction of rotation 102, the translation of the ramp system 42 changes.
  • the counter ramp 50 ramp elements 104, the ramp ring 52 facing counter ramp surfaces 106 is also not linear but concave.
  • the ramp surface 100 of the ramp ring 52 may be made concave with a slight change in pitch, while the counter ramp surface 106 of the counter ramp 50 is made linearly for the most part and only for the first time End of the wear area is gradually exceeded in a region with a lower slope.
  • Fig. 6 is a slope of the ramps 54 of the ramp body and occurring forces 1 10 over a twist angle 1 12 of the ramp ring 52 to the counter ramp 50 between a wear area beginning 1 14 and a wear area end 1 16 shown.
  • a gradient 1 18 of the ramp body according to the invention is not constant, but changes continuously with a constant rate of change and has a constant curvature.
  • the resistance moment applied by the ramp system 42 is greater relative to the rotation of the ramp ring 52 relative to the counter ramp 50, so that in the vicinity of the wear area beginning 1 14 a required accordinglynachstellkraft F N min greater than in the vicinity of Wear area end 1 16.
  • the applied for example by a drive pawl 74 Vietnamese F N may remain substantially constant, but one of a return spring for displacing the pressure plate 9,10 in a particular open starting position when no operating force on the pressure plate 9, 10 exercised is, on the ramp system 42 attachable clamping force F K can increase.
  • FIG. 7 a path 120 of a trailing adjustment path 122 is shown in FIG.
  • the pitch curve 1 18 of the ramp body is adapted such that a minimum adjustment force F N min required over a significant range of the angle of rotation 1 12 lies only below the minimum amount of safety AF N, min below the applied adjusting force F N.
  • this can result in a maximum possible translation via the angle of rotation without falling below the required minimum safety amount AF N min .
  • This makes it possible to achieve the maximum Nachstellweg 122 at a much lower angle of rotation 1 12.
  • a residual torsion angular range 124 resulting therefrom can be used to separate other components between two subsequent the ramps 54 to position and / or maximum Nachstellweg 122 to increase, whereby the use of thicker friction linings is made possible, which lead to an increased life of the friction clutch 2, 3.

Abstract

La présente invention concerne un corps de rampe destiné à un système de rampes (42) d'un dispositif (29) d'ajustement d'un jeu anormal, dû à l'usure, entre une plaque de pression (9, 10) et une contre-plaque (8) d'un embrayage à friction (2, 3) comprenant une base (98) qui s'étend sensiblement dans la direction circonférentielle et une rampe (54) qui en saillie par rapport à la base. La rampe comporte une surface (100) destinée à glisser sur une contre-rampe (50). La surface de la rampe présente dans la direction circonférentielle une allure irrégulière qui s'écarte d'une allure linéaire avec une pente constante. En raison de l'allure irrégulière de la pente de la surface de la rampe dans la direction circonférentielle, le rapport de transmission entre le système de rampes du dispositif d'ajustement muni d'un tel corps de rampe peut être adapté à des rapports de forces qui varient sur la zone d'usure. Ainsi, lorsqu'un embrayage à friction présente une zone d'usure importante, le dispositif d'ajustement peut conserver une fonction d'ajustement sans compromettre la fonctionnalité de l'embrayage à friction.
PCT/DE2014/200147 2013-04-24 2014-03-31 Corps de rampe pour système de rampes d'un dispositif d'ajustement WO2014173406A1 (fr)

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DE112014002152.0T DE112014002152B4 (de) 2013-04-24 2014-03-31 Nachstelleinrichtung zum Nachstellen eines verschleißbedingten Fehlabstands einer Anpressplatte zu einer Gegenplatte einer Reibungskupplung

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DE102013207380 2013-04-24

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DE102020116326B4 (de) 2020-06-22 2023-03-30 Schaeffler Technologies AG & Co. KG Rampensystem für eine Reibungskupplung mit einer verschleißabhängigen Nachstelleinrichtung
DE102022106921A1 (de) 2022-03-24 2023-09-28 Schaeffler Technologies AG & Co. KG Doppelkupplungsgetriebe mit Verschleißnachstellung

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DE4239291A1 (fr) 1991-11-26 1993-05-27 Luk Lamellen & Kupplungsbau
DE4322677A1 (de) 1992-07-11 1994-01-13 Luk Lamellen & Kupplungsbau Kupplungsaggregat
DE4431641A1 (de) 1993-09-13 1995-03-16 Luk Lamellen & Kupplungsbau Ausrückvorrichtung
US5690203A (en) * 1993-11-04 1997-11-25 Fichtel & Sachs Ag Motor vehicle friction clutch with automatic wear adjustment
US5845750A (en) * 1995-09-21 1998-12-08 Valeo Ramp means for a device for taking up clearance designed to equip a friction clutch, notably for a motor vehicle
DE19905373A1 (de) 1999-02-10 2000-08-31 Sachs Race Eng Gmbh Reibungskupplung und Anpreßhebelanordnung für eine Reibungskupplung
DE10011418A1 (de) * 1999-03-12 2000-09-14 Luk Lamellen & Kupplungsbau Kupplungsaggregat
EP0992700B1 (fr) 1998-10-05 2004-08-25 Aisin Seiki Kabushiki Kaisha Embrayage à friction pour véhicules
EP1452760A1 (fr) 2003-02-25 2004-09-01 ZF Sachs AG Dispositif de transmission de force pour un embrayage à friction
DE10340665A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Kraftspeicher für eine Reibungskupplung
WO2008058508A1 (fr) 2006-11-17 2008-05-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Système d'embrayage
WO2009056092A1 (fr) 2007-10-31 2009-05-07 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Embrayage à friction
DE102009035225A1 (de) 2008-08-21 2010-02-25 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Reibungskupplung

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Publication number Priority date Publication date Assignee Title
DE4337613A1 (de) 1993-11-04 1995-05-11 Fichtel & Sachs Ag Reibungskupplung mit automatischem Verschleißausgleich und Spielgeber

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4239289A1 (fr) 1991-11-26 1993-05-27 Luk Lamellen & Kupplungsbau
DE4239291A1 (fr) 1991-11-26 1993-05-27 Luk Lamellen & Kupplungsbau
DE4322677A1 (de) 1992-07-11 1994-01-13 Luk Lamellen & Kupplungsbau Kupplungsaggregat
DE4431641A1 (de) 1993-09-13 1995-03-16 Luk Lamellen & Kupplungsbau Ausrückvorrichtung
US5690203A (en) * 1993-11-04 1997-11-25 Fichtel & Sachs Ag Motor vehicle friction clutch with automatic wear adjustment
US5845750A (en) * 1995-09-21 1998-12-08 Valeo Ramp means for a device for taking up clearance designed to equip a friction clutch, notably for a motor vehicle
EP0992700B1 (fr) 1998-10-05 2004-08-25 Aisin Seiki Kabushiki Kaisha Embrayage à friction pour véhicules
DE19905373A1 (de) 1999-02-10 2000-08-31 Sachs Race Eng Gmbh Reibungskupplung und Anpreßhebelanordnung für eine Reibungskupplung
DE10011418A1 (de) * 1999-03-12 2000-09-14 Luk Lamellen & Kupplungsbau Kupplungsaggregat
EP1452760A1 (fr) 2003-02-25 2004-09-01 ZF Sachs AG Dispositif de transmission de force pour un embrayage à friction
DE10340665A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Kraftspeicher für eine Reibungskupplung
WO2008058508A1 (fr) 2006-11-17 2008-05-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Système d'embrayage
WO2009056092A1 (fr) 2007-10-31 2009-05-07 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Embrayage à friction
DE102009035225A1 (de) 2008-08-21 2010-02-25 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Reibungskupplung

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DE112014002152A5 (de) 2016-01-07
DE102014205917A1 (de) 2014-10-30

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