DE102021115730B3 - Clutch disc with integrated actuation device for positive or frictional support; coupling device; and hybrid module - Google Patents

Abstract

The invention relates to a clutch disc (1) for a clutch device (2) of a motor vehicle, having a carrier plate (3), a friction component (5) rotationally coupled to the carrier plate (3) and equipped with axial friction surfaces (4a, 4b), and with an actuating device (6) which increases the torque transmission of the clutch device (2) in at least one activated state when a limit torque to be transmitted by the carrier plate (3) during operation is exceeded, the actuating device (6) being inactive at least one between an initial position State and a release position in the activated state displaceable in the radial direction, radially outward from the friction component (5) protruding blocking element (7). The invention also relates to a clutch device (2) and a hybrid module (20).

Description

The invention relates to a clutch disc for a clutch device of a motor vehicle according to the preamble of claim 1, with a carrier plate, a friction component which is rotationally coupled to the carrier plate and is equipped with axial friction surfaces, and with a torque transmission of the clutch device in at least one activated state, when it is exceeded an actuating device which increases the limit torque to be transmitted during operation by the carrier plate. Furthermore, the invention relates to a clutch device and a hybrid module.

Various actuating devices for clutches are already known from the prior art.

In the case of the designs known from the prior art, however, it has been found that the actuating devices used for additional torque support can be further optimized with regard to the support force that can be generated, in order to also enable higher torques to be supported over a longer period of operation. Furthermore, the actuating device should be easy to manufacture and should have as little or no adverse effect as possible on the structural space, in particular the axial space of the clutch disk. In particular, it is preferred that the clutch disk does not, or only slightly, exceed the dimensions of known clutch disks.

In particular, from the DE 10 2018 122 385 A1 a clutch disc in the form of a friction plate is known, which can be read from the preamble of claim 1.

It is the object of the present invention to provide a clutch disk with an actuating device which is of compact design and has a reliable and robust supporting effect.

This object is achieved according to the invention by a clutch disc according to claim 1, wherein the actuating device has at least one locking element which can be displaced in the radial direction between an initial position in its inactive state and a release position in its activated state and protrudes radially outwards from the friction component.

Such a conversion of the actuating device forms an axially compact clutch disk. Due to the fact that the locking element serving for the connection/support with other coupling components of the coupling device is offset outwards as far as possible in the radial direction, the actuating forces acting on the locking element are as small as possible. This also results in the longest possible service life of the actuating device.

Further advantageous embodiments are claimed with the dependent claims and explained in more detail below.

Accordingly, it is also advantageous if the at least one blocking element is guided in a ring body of the friction component so that it can be displaced in the radial direction and is prepared with an active region protruding radially outwards from the ring body for a positive connection or friction-locked connection with a clutch component of the clutch device. This further simplifies the structure of the friction component.

According to an advantageous embodiment, the at least one blocking element is designed directly for form-fitting engagement in counter-toothing of a (further) clutch component of a clutch device. This keeps the required number of components as low as possible. Alternatively, according to a further embodiment, it is also advantageous if the at least one blocking element is movably coupled to a friction body, which friction body is radially frictionally pressed against the second clutch component by the adjustment from the initial position to the release position. As a result, the part of the additional clutch component that interacts with the actuating device can be produced easily.

If the at least one blocking element is prestressed inwards into the starting position in the radial direction by means of a return spring, the blocking element is cleverly secured against loss.

In this regard, it is also expedient if the restoring spring is designed as a compression spring, more preferably as a leaf spring (i.e. arcuate) following a radial outside of the annular body. This leads to a radially compact design.

Furthermore, it is advantageous if the carrier plate interacts with the at least one locking element in such a way that if the limit torque to be transmitted by the carrier plate during operation is exceeded and the carrier plate rotates relative to the friction component as a result, the at least one locking element is locked by means of a the at least one blocking element used ramp device or link device the at least one Blocking element is moved radially outwards into the release position. As a result, the actuating device is designed with as few additional components as possible.

It is also expedient here if the carrier plate can be rotated by a limited rotational angle range relative to the friction component against the action of a spring accumulator clamped in the circumferential direction between the friction component and the carrier plate. As a result, the clutch disc is designed to be as robust as possible. The spring accumulator is formed by one compression spring(s), more preferably by a plurality of compression springs distributed in the circumferential direction.

A locking unit is present and inserted in such a way that it supports/fixes the carrier plate in a rotational position corresponding to the release position. Thus, among other things, those micro-movements occurring in the release position, which cause increased wear, are avoided.

The locking unit is constructed as robustly as possible, since it has a blocking body which is pressed against a radial outer peripheral side of the carrier plate.

The blocking body preferably snaps into a depression in the carrier plate in a rotational position of the carrier plate that corresponds to the release position relative to the friction component. More preferably, that blocking body is slidably received directly on the annular body. This further simplifies the structure.

Furthermore, the invention relates to a clutch device for a drive train of a motor vehicle, with a first clutch component having the clutch disk according to at least one of the embodiments described above and a second clutch component that can be selectively coupled to the first clutch component.

Furthermore, the invention relates to a hybrid module for a drive train of a motor vehicle, with this clutch device and an electric machine, the second clutch component of the clutch device being permanently non-rotatably connected to a rotor of the electric machine.

More preferably, several blocking elements are distributed in the circumferential direction. In other words, the at least one blocking element is consequently positioned/received axially between friction surfaces/friction linings of the clutch disk.

In other words, according to the invention, a rotor-integrated, two-stage KO clutch (clutch device) is proposed in a hybrid module, which preferably works frictionally and positively, with a positive-locking device being integrated into the clutch disk and being effective in particular in the radial direction. The positive-locking device can also be replaced by a friction-locking device.

The invention will now be explained in more detail below with reference to figures, in which context various exemplary embodiments are also shown.

• 1 eine perspektivische Darstellung einer erfindungsgemäßen teilweise dargestellten Kupplungsscheibe nach einem ersten Ausführungsbeispiel, wobei ein Aufbau einer Betätigungseinrichtung im Detail zu erkennen ist,
• 2 eine Längsschnittdarstellung der nach 1 ausgebildeten gesamten Kupplungsscheibe,
• 3 eine perspektivische Darstellung der gesamten Kupplungsscheibe,
• 4 eine Vorderansicht einer erfindungsgemäßen teilweise dargestellten Kupplungsscheibe nach einem zweiten Ausführungsbeispiel, wobei mehrere Sperrelemente nun mit zusätzlichen Reibkörpern verbunden sind, sowie
• 5 eine Längsschnittdarstellung eines die Kupplungsscheibe nach den 1 bis 3 aufweisenden Hybridmoduls, wobei die Kupplungsscheibe vereinfacht dargestellt ist.

Show it:

• 1 a perspective view of a clutch disc according to the invention, partially shown, according to a first exemplary embodiment, in which a structure of an actuating device can be seen in detail,
• 2 a longitudinal section view of the 1 trained entire clutch disc,
• 3 a perspective view of the entire clutch disc,
• 4 a front view of a clutch disc according to the invention, partially shown, according to a second exemplary embodiment, with several locking elements now being connected to additional friction bodies, and
• 5 a longitudinal sectional view of the clutch disc according to 1 until 3 having hybrid module, wherein the clutch disc is shown in simplified form.

The figures are only of a schematic nature and serve exclusively for understanding the invention. The same elements are provided with the same reference numbers.

With 5 a preferred area of application of a clutch disc 1 according to the invention is illustrated. The clutch disk 1 is therefore preferably integrated in a clutch device 2 designed as a friction clutch. The clutch device 2 is also used in a hybrid module 20 of a motor vehicle drive train. In particular, the clutch device 2 is designed as a separating clutch/K0 clutch.

In addition to the clutch device 2 , the hybrid module 20 has an electric machine 21 in the usual way. The coupling device 2 is under formation of the separating clutch between an internal combustion engine 24 and the electric Machine 21 used effective. The internal combustion engine 24 is in 5 for the sake of clarity, only the crankshaft 25 is shown. It can also be seen in principle that the clutch device 2 is implemented as a multi-plate clutch.

A first clutch component 10a of the clutch device 2 is rotationally connected to the crankshaft 25 , whereas a second clutch component 10b of the clutch device 2 is rotationally connected to a rotor 22 of the electric machine 21 . Typically, the second clutch component 10b has a rotor carrier 26, on the radial outside of which the rotor 22 is arranged. A stator 27 of the electrical machine 21 is again accommodated in a housing 28 of the hybrid module 20 radially outside the rotor 22 .

The first coupling component 10a has according to the invention 1 until 3 converted clutch disc 1. The clutch disc 1 is after 5 inserted between a pressure plate 29 and an intermediate plate 30. In other embodiments, this clutch disc 1 is also used in other ways, such as in a single disc clutch or between the intermediate plate 30 and a pressure plate 31. Pressure plate 29, intermediate plate 30 and pressure plate 31 belong to the second clutch component 10b.

For the sake of completeness, it should be noted that the directional information used in the present case is to be understood as axial, radial and circumferential in relation to a central axis of rotation 32 of clutch disk 1 , which corresponds to an axis of rotation 32 of rotor 22 . The axial/axial direction is thus a direction along the axis of rotation 32 , the radial/radial direction is a direction perpendicular to the axis of rotation 32 and the circumferential direction is a direction along a circle running concentrically to the axis of rotation 32 .

In the 1 until 3 It can be seen that the clutch disc 1 according to the invention basically has an essentially ring-shaped friction component 5 and a carrier plate 3 accommodating this friction component 5 . The support plate 3 is according to 5 further connected during operation to an intermediate shaft 33 leading to the crankshaft 25 .

The friction component 5 of the clutch disc 1 has an annular body 8 . A first friction lining 34a is arranged on a first receiving disk 35a on a first axial side of the annular body 8 . A second friction lining 34b is arranged on a second receiving disk 35b on a second axial side of the annular body 8 . The two friction linings 34a, 34b in turn directly form one of two axial friction surfaces 4a, 4b of the clutch disk 1. The receiving disks 35a, 35b protrude inward in the radial direction beyond the friction linings 34a, 34b and thereby cover the carrier plate 3 axially. Preferably, as is also implemented here, the receiving disks 35a, 35b directly form the annular body 8. In particular, the receiving disks 35a, 35b each have directly recesses 39 in the sense of radial through-holes, in each of which a blocking element 7 is displaceably guided.

The carrier plate 3 can be rotated relative to the friction component 5 over a limited range of angles of rotation. It can be seen that the carrier plate 3 is spring-loaded in the circumferential direction along the twisting angle range relative to the friction component 5 via three compression springs 36 distributed uniformly in the circumferential direction, which together form a spring accumulator 15 .

The clutch disk 1 also has an actuating device 6 implemented according to the invention. The actuating device 6 itself has a plurality of locking elements 7 distributed (equally) in the circumferential direction, which locking elements 7 serve to lock the clutch disc 1 when a specific limit torque to be transmitted by the clutch device 2 in its closed position is exceeded during operation, in addition to the second To support coupling component 10b. The actuating device 6 consequently serves to support/connect the clutch disk 1 to the second clutch component 10b with an additional holding force via the frictional connection of its friction surfaces 4a, 4b to the second clutch component 10b.

The locking elements 7 protrude in the radial direction from the ring body 8 and are between the in 1 shown starting position and a radially compared to this starting position further outwards offset trigger position displaceable. In this release position, there is an additional form-fitting support of the first clutch component 10a relative to the second clutch component 10b during operation using the clutch disk 1 of the first exemplary embodiment. According to the first embodiment of the 1 until 3 the blocking elements 7, with an active region 9 projecting radially outwards from the friction component 5, engage in a form-fitting manner in corresponding gaps, not shown in detail for the sake of clarity, of an internal toothing of the second clutch component 10b.

Each locking element 7 is designed as a pin and is located with its radially inner end on a ramp device 14 of the support plate 3 in plant. Each locking element 7 rests radially from the outside on its own ramp contour 37, which rises in the circumferential direction, of a radially protruding cam. In further embodiments, the ramp contour 37 is also implemented as a link, according to which the ramp device 14 is alternatively referred to as a link device.

The ramp contour 37 is designed such that when the carrier plate 3 rotates relative to the friction component 5 in a first direction of rotation, the respective ramp contour 37 displaces the associated blocking element 7 in the radial direction from the initial position to the release position. The limited range of rotation angles of the carrier plate 3 relative to the friction component 5 ensures that the blocking element 7 is always in contact with the ramp contour 37 .

For the radial return of the locking elements 7 to the starting position, d. H. radially inwards, each blocking element 7 is assigned at least one, here even two, return spring(s) 11 .

The respective return spring 11 is designed as a leaf spring 13 . The leaf spring 13 follows the radial outer side 12 of the annular body 8 in an arc. Spaced apart from the blocking element 7 in the circumferential direction, the leaf spring 13 is fixed to the annular body 8 at least radially and axially. In addition, the leaf spring 13 is connected to the blocking element 7 in a non-displaceable manner in a further area. In this way, two return springs 11/leaf springs 13 are preferably attached to mutually opposite peripheral sides of the blocking element 7.

Furthermore, there is a locking unit 16 which serves to fix the carrier plate 3 relative to the friction component 5 in a rotational position corresponding to the release position of the blocking element 7 . The detent unit 16 has a locking body 17 which is accommodated in the friction component 5, namely the annular body 8, so as to be displaceable in the radial direction and which is embodied, for example, as a ball. That locking body 17 is biased inward in the radial direction by a biasing spring 38 . The blocking body 17 is thereby permanently pressed against a radial outer peripheral side 18 of the carrier plate 3 . The carrier plate 3 has a radial indentation 19 at a circumferential point, which is designed to be essentially complementary to the blocking body 17 . The recess 19 is positioned in such a way that the locking body 17 automatically engages in the recess 19 in the rotational position of the carrier plate 3 relative to the friction component 5, which corresponds to the release position of the locking element 7, and thus prevents/blocks the carrier plate 3 from twisting relative to the friction component 5 . The locking unit 16 is also designed in such a way that when the torque to be transmitted by the coupling device 2 again falls below a specific threshold value, the blocking body 17 is released from the form-fitting contact with the recess 19 .

Combined with 4 Finally, a second exemplary embodiment of the clutch disk 1 according to the invention is illustrated, which, however, is constructed and implemented essentially in accordance with the first exemplary embodiment. For the sake of brevity, therefore, only the differences from the first exemplary embodiment are described.

The clutch disc 1 of 4 differs from the first exemplary embodiment in that the blocking elements 7 are each now connected to a friction body 23 radially outside of the friction component 5 . One end of the respective friction body 23 running in the circumferential direction/arcuate is coupled for movement to the blocking element 7/the radially outwardly projecting active region 9 of the blocking element 7 and the other end is fixed/supported, forming a pivot point, preferably on the friction component 5. When the blocking element 7 moves from the initial position to the release position, the end of the friction body 23 connected to the blocking element 7 pivots radially outwards about the pivot point, as a result of which the friction body 23 comes into frictional contact with an inner peripheral side of the second clutch component 10b.

In other words, according to the invention, an actuating mechanism (actuating device 6) for producing a positive connection is integrated in a friction disk (clutch disk 1).

The friction disk essentially consists of an input element (driver disk; carrier plate 3), two side plates (receiving disks 35a; 35b / annular body 8) with friction lining 34a, 34b, several radial pins guided in the side plates (output element; locking element 7) with return and compression springs . Optionally, a ratchet mechanism (locking unit 16) consisting of balls and compression springs as well as a lining spring between the carrier plate and the friction lining can be added.

The drive disk has a ramp profile (ramp contour 37) on the outer contour and has several compression spring windows. The ramp profile can optionally be designed as a link to allow radial outward movement and radial inward movement on the pins. In addition, the drive plate has radial recesses (indentations 19) on the outer diameter to accommodate the balls (locking body 17) of the detent mechanism.

The side plates have radial recesses 39 for receiving and guiding the pins. Leaf springs 13 are attached to the outside diameter, which ensure the return function of the pins and the compensation of the centrifugal effects. The inner contour has radial recesses for accommodating the latching mechanism. Pressure spring windows are integrated in the circumferential direction. The friction linings 34a, 34b are then in turn attached to the side plates. There is an optional pad spring in between.

This results in the following function in operation:

The drive plate is connected to the combustion engine via the hybrid shaft. If the frictional KO clutch is now closed, the torque can be transmitted via the drive plate (carrier plate 3) through the compression springs 36, the side plates (ring body 8) and the friction linings 34a, 34b to the pressure plate 31 and pressure plate 29 of the clutch, which is connected to the rotor carrier 26 are connected to the transmission input shaft. This state describes, for example, starting the combustion engine in overrun mode.

The same procedure applies on the train up to a switching moment. However, if a higher torque is required (the switching torque is exceeded), the drive plate rotates at a larger angle to the side plates. The pins are pushed radially outwards via a ramp system on the drive plate and engage in the counter-toothing of the rotor carrier 26 . In addition to the frictional KO torque, a form-fitting torque is connected in parallel. In addition, there are notches in the drive plate into which a ball is pressed in the end position by a preloaded compression spring (preloading spring 38). This latching mechanism causes the form closure to open belatedly while the torque is being reduced and prevents constant micro-movements in the ramp mechanism.

If the torque has fallen below a defined threshold value, the balls track out again and the radial pins are pressed radially inwards by the leaf springs 13 . These return springs also serve to compensate for centrifugal force and prevent it from wandering out at high speeds.

The adjustment mechanism serves primarily as a torque sensor and actuator, since it converts a relative rotation into a radial movement. If the pins are also spring-loaded radially, an overload function can be integrated, which ensures a free-wheeling function if the torque is too high.

In addition, instead of the return springs in the circumferential direction, a link mechanism can also be used, which actively pushes the pins outwards and also retracts them.

In one variant, an additional frictional connection is implemented instead of the positive connection: A component of this design is an actuating mechanism integrated into a friction disc for producing a frictional connection. In addition to the components described in the first exemplary embodiment, friction blocks (friction body 23) are added on the outer diameter of the friction disk. One end of the friction shoe is designed as a joint and is connected to the friction disc. The friction shoes can be compared to the brake shoes of a drum brake.

This results in the following function during operation: Here the actuating mechanism is used to actuate another friction contact. In this case, the radial pins press the friction jaws against the inner diameter of the rotor carrier 26. This creates a frictional connection between the outer diameter of the friction disc and the inner diameter of the rotor carrier.

In addition to the advantages mentioned above, this system also has the following advantages: Self-reinforcement in the train due to running jaws; Overload function is scalable through the contact pressure; Use of a friction pairing with high coefficients of friction (preferably steel-steel, carbon, etc.); and finding the counter toothing is no longer necessary.

Reference List

1

clutch disc

2

coupling device

3

backing plate

4a

first friction surface

4b

second friction surface

5

friction component

6

actuating device

7

blocking element

8th

ring body

9

effective range

10a

first clutch component

10b

second clutch component

11

return spring

12

outside of the body of the ring

13

leaf spring

14

ramp facility

15

spring accumulator

16

locking unit

17

locking body

18

outer peripheral side

19

deepening

20

hybrid module

21

electric machine

22

rotor

23

friction body

24

internal combustion engine

25

crankshaft

26

rotor carrier

27

stator

28

Housing

29

printing plate

30

intermediate plate

31

pressure plate

32

axis of rotation

33

intermediate shaft

34a

first friction lining

34b

second friction lining

35a

first recording disc

35b

second recording disc

36

compression spring

37

ramp contour

38

bias spring

39

recess

Claims (8)

Clutch disk (1) for a clutch device (2) of a motor vehicle, with a carrier plate (3), a friction component (5) coupled in rotation with the carrier plate (3) and equipped with axial friction surfaces (4a, 4b), and with a torque transmission of the Clutch device (2) in at least one activated state, when a limit torque to be transmitted by the carrier plate (3) during operation is exceeded, actuating device (6) increasing, wherein the actuating device (6) moves at least one between an initial position in its inactive state and a release position in the activated state, has a locking element (7) that can be displaced in the radial direction and protrudes radially outwards from the friction component (5), a locking unit (16) being present and inserted in such a way that it places the carrier plate (3) in a position corresponding to the release position Supports rotational position, characterized in that the locking unit (16) has a locking body (17) which is pressed against a radial outer peripheral side (18) of the carrier plate (3). Clutch disc (1) after claim 1 , characterized in that the at least one blocking element (7) is guided in a ring body (8) of the friction component (5) so as to be displaceable in the radial direction and has an active region (9) protruding radially outwards from the ring body (8) for positive connection or frictional connection with a coupling component (10b) of the coupling device (2) is prepared. Clutch disc (1) after claim 1 or 2 , characterized in that the at least one locking element (7) is biased by a return spring (11) in the radial direction inwards into the initial position. Clutch disc (1) after claim 3 , characterized in that the restoring spring (11) is designed as a compression spring. Clutch disc (1) according to one of Claims 1 until 4 , characterized in that the carrier plate (3) interacts with the at least one blocking element (7) in such a way that when the limit torque to be transmitted during operation by the carrier plate (3) is exceeded and the carrier plate (3) rotates relative to the friction component as a result (5) the at least one blocking element (7) is displaced radially outwards into the release position by means of a ramp device (14) or link device inserted between the carrier plate (3) and the at least one blocking element (7). Clutch disc (1) according to one of Claims 1 until 5 , characterized in that the carrier plate (3) can be rotated by a limited angle of rotation relative to the friction component (5) against the action of a spring-loaded accumulator (15) clamped in the circumferential direction between the friction component (5) and the carrier plate (3). Coupling device (2) for a drive train of a motor vehicle, with one, the Kupp Lung disc (1) according to one of Claims 1 until 6 comprising, first coupling component (10a) and, with the first coupling component (10a) optionally coupled, second coupling component (10b). Hybrid module (20) for a drive train of a motor vehicle, with a clutch device (2). claim 7 and an electrical machine (21), wherein the second clutch component (10b) of the clutch device (2) is permanently non-rotatably connected to a rotor (22) of the electrical machine (21).

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