EP3350465A1

EP3350465A1 - Pressure plate for a friction clutch, and friction clutch

Info

Publication number: EP3350465A1
Application number: EP16769854.7A
Authority: EP
Inventors: Andreas Kern; Jens LANGANKI; Florian Maas
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2015-09-18
Filing date: 2016-08-25
Publication date: 2018-07-25
Also published as: WO2017045678A1; DE112016004222A5; DE102016216934A1

Abstract

The invention relates to a pressure plate (4) for a friction clutch (1) of a motor vehicle. The pressure plate (4) has a substantially annular shape when seen in the axial direction (A) of the pressure plate (4) and is divided into a plurality of pressure plate segments (16, 17, 18) which are arranged so as to follow one another in the circumferential direction (U) of the pressure plate (4) and which can be at least partly moved relative to one another. The circumferential direction (U) runs on a normal plane (N) with respect to the axial direction (A), and at least two pressure plate segments (16, 17, 18) which are adjacent to each other in the circumferential direction (U) have two mutually facing end faces (19, 20) which are connected together by at least one connecting device (21) extending on the normal plane (N). At least one of the two pressure plate segments (16, 17, 18) has a recess (22) which substantially corresponds to a contour of the connecting device (21) and receives the connecting device (21), and the recess (22) has a constant width (B) which is measured on the normal plane (N) or the width (B) measured on the normal plane (N) decreases towards the interior of the pressure plate segment (16, 17, 18) starting from the end face (20) of the pressure plate segment (16, 17, 18).

Description

Pressure plate for a friction clutch and friction clutch

The present invention relates to a pressure plate for a friction clutch of a motor vehicle according to the preamble of patent claim 1. Furthermore, the present invention relates to a friction clutch for a motor vehicle.

From DE 100 31 598 A1 a pressure plate for a friction clutch of a motor vehicle is known, which is read on the preamble of claim 1. The pressure plate is viewed in the axial direction of the pressure plate substantially annular and divided into a plurality of circumferentially of the pressure plate arranged successively and with respect to each other at least partially displaceable Anpressplattensegmenten. With respect to the axial direction, the circumferential direction is in a normal plane, that is, in a plane pierced at right angles by a vector of the axial direction. Two contact pressure plate segments adjacent in the circumferential direction have two end faces facing one another, which are connected to one another by a connecting device extending in the normal plane, wherein one of the two contact plate segments has a hammerhead-shaped recess essentially corresponding to a contour of the connecting device and receiving the connecting device.

Such a construction of the pressure plate makes it possible to produce the pressure plate from individual sheet metal segments which can be punched out without excessive punching waste. At the same time, such a pressure plate makes it possible to compensate for unevenness during operation of the friction clutch and to reduce the cupping / shielding, that is to say the deformation of the pressure plate which, due to the introduced thermal energy, is caused by the expansion of the friction surface of the pressure plate facing the clutch disc The duration of time required for this introduced heat energy to spread over the entire volume of the pressure plate arises. It is an object of the present invention to provide a pressure plate for a friction clutch and a corresponding friction clutch, which are inexpensive and reliable to produce, and in which at the same time the Topfung can be reduced.

According to the invention this object is achieved by a pressure plate for a friction clutch of a motor vehicle according to claim 1, wherein the pressure plate viewed in the axial direction of the pressure plate is substantially annular and arranged in a plurality of circumferentially of the pressure plate successively and with respect to each other at least partially

is displaceable Anpressplattensegmenten divided, wherein the circumferential direction in a normal plane with respect to the axial direction, wherein at least two circumferentially adjacent Anpressplattensegmente two facing end faces, which are interconnected by at least one extending in the normal plane connecting means, wherein at least one of the two Anpressplattensegmente one of a contour of the connecting device substantially corresponding and the connecting device receiving recess. Since the recess has a uniform width measured in the normal plane, or the width measured in the normal plane decreases starting from the end face of the pressure plate segment into the interior of the pressure plate segment, it is possible to produce the individual pressure plate segments in a cost-effective and reliable manner Pressure plate is inexpensive and reliable to produce. In particular, hammerhead-shaped recesses and connecting devices can be dispensed with, which favors punching technology production.

Preferred embodiments of the present invention are set forth in the dependent claims.

According to a preferred embodiment, the mutually facing end faces are spaced apart from one another, at least in the circumferential direction, by a gap-shaped intermediate space. The gap-shaped interspace can be used to ensure that the individual pressure plate segments are relieved to a limited extent. tive to each other, which favors the compensation of unevenness and the reduction of the Topfung the pressure plate. The gap-shaped gap preferably includes the entire end faces, that is also the contour of the connecting device and the recess, but may also relate exclusively to the circumferentially facing each other, in particular straight, portions of the adjacent pressure plate segments.

Furthermore, it is advantageous if the recess has a central axis, and the central axis has a non-concentric with respect to a center of rotation of the pressure plate course. Thus, no additional fastening means are required to hold the individual Anpressplattensegmente relative to each other permanently in position or to allow a limited displaceability of the individual Anpressplattensegmente each other.

It is particularly advantageous if the central axis has at least one direction change. Particularly by means of a hook-shaped or meander-shaped contour of the recess and the corresponding connecting device, a reliable positioning of the pressure plate segments relative to one another or the limited displaceability of the pressure plate segments relative to each other is made possible.

In particular, it is advantageous if the change of direction includes an angle greater than 45 °.

According to a further preferred embodiment, all contact plate segments of the pressure plate each have a first end face with a projecting in the direction of each adjacent Anpressplattensegments connecting device and a second end face with a corresponding, extending into the interior of this respective pressure plate segment recess. Thus, the entire pressure plate can be made of Anpressplattensegmenten the same type, that is, the industrial production aimed at the use of common parts to reduce the process and storage costs is supported. According to an alternative preferred embodiment, the pressure plate on two groups of Anpressplattensegmenten, of which the Anpressplattensegmente the first group have two end faces each projecting in the direction of the adjacent Anpressplattensegmente the second group Verbindungsseinrichtun- gene, and of which the Anpressplattensegmente the second group with two end faces corresponding, extending into the interior of these respective Anpressplattensegmente the second group extending recesses, and wherein the Anpressplattensegmente the first group and the second group are arranged alternately in the circumferential direction. This makes it possible to produce the pressure plate from two different types of Anpressplattensegmenten, which may be advantageous, for example, if it is expected with different heat inputs in the circumferential direction.

According to a further preferred embodiment, the pressure plate segments cover the same angular ranges of the pressure plate, that is to say have the same length in the circumferential direction. Thus, the pressure plate may for example be composed of six Anpressplattensegmenten, each of which Anpressplattensegment covers an angular range of 60 °. According to an alternative embodiment, the Anpressplattensegmente cover different angular ranges of the pressure plate, that is, have different lengths in the circumferential direction. Thus, the pressure plate can for example be composed of six pressure plate segments, of which two Anpressplattensegmente cover an angular range of 30 °, two Anpressplattensegmente an angular range of 60 ° and two Anpressplattensegmente an angular range of 90 °.

The above object is further achieved according to the invention by a friction clutch for a motor vehicle according to claim 10 with at least one counter-pressure plate, with at least one clutch plate connected to the counter-pressure plate, and with at least one with respect to the platen in the axial direction of the friction clutch limited displaceable pressure plate for frictional clamping a clutch disc between the counter-pressure plate and the pressure plate, wherein the pressure plate according to one of the preceding Ausführungsbei- games is formed. The advantages explained above in connection with the pressure plate apply equally to the friction clutch.

The present invention will be explained in more detail below with reference to preferred exemplary embodiments in conjunction with the associated figures. 1 shows a sectional view of a friction clutch with a pressure plate, wherein the pressure plate has at least one cam ring and a friction plate, and wherein the friction plate has a plurality of pressure plate segments,

a perspective view of a first embodiment of the friction plate, which is composed of six Anpressplattensegmenten, wherein three Anpressplattensegmente a first group and three Anpressplattensegmente be assigned to a second group,

a pressure plate segment of the first group of Figure 2, a Anpressplattensegment the second group of Figure 2, a partial view of a second embodiment of the friction plate with

Pressure plate segments of the same group, and

a partial view of a third embodiment of the friction plate with

Pressure plate segments of the same group.

Figures 1 to 6 relate to preferred embodiments of a Reibungskupp- ment 1 and a pressure plate 4 for a friction clutch 1 of a motor vehicle. Features that are not marked in the present description as essential to the invention are to be understood as optional. Therefore, the following description also relates to further embodiments of the friction clutch 1 and the pressure plate 4, the sub-combinations of the features to be explained below.

The friction clutch 1 has at least one pressure plate 4, at least one counter-pressure plate 2 and at least one coupling arranged in the axial direction A of the friction clutch 1 between the pressure plate 4 and the counter-pressure plate 2. disc 3 on. The counter-pressure plate 2 is one or more

Housing components, in particular a clutch cover 5, firmly connected, in particular screwed. The pressure plate 4 is rotatably mounted with respect to the counter-pressure plate 2 and with respect to the clutch cover 5 and displaced in the axial direction A to engage the friction clutch 1, that is to clamp the clutch disc 3 frictionally between the pressure plate 4 and the counter-pressure plate 2, or to disengage the friction clutch 1, that is, the frictional connection between the pressure plate 4 and the clutch disc 3 and between the clutch disc 3 and the counter-pressure plate 2 cancel.

In addition, the friction clutch 1, a plate spring 6, the

on the housing side, in particular on the clutch cover 5 is tilted supported and supported by a pivot bearing 10, and by a not shown

Actuator is actuated. The plate spring 6 has in its outer region a circumferential, annular force edge 7. In the radial direction R of the friction clutch extend from the force edge 7 starting plate spring tongues 8 inwardly on the free ends of the actuator device, preferably by means of a release bearing, not shown, acts to disengage the friction clutch 1 and / or einzutücken.

The pivot bearing 10 has in the embodiment of the friction clutch 1, which is shown in Figure 1, a facing away from an inside of the clutch cover 5 and one of the pressure plate 4 side of the plate spring 6 arranged wire ring 1 1 and on the pressure plate 4 facing side of the plate spring. 6 arranged support spring 12. The support spring 12 is in the illustrated embodiment by coupling cover side hook portions 13 which are integrally formed with the clutch cover 5, supported and tilted, wherein the support spring 12 presses the plate spring 6 in the region of its force edge 7 in the axial direction A against the clutch cover side wire ring 1 1.

Deviating from the embodiment of the friction clutch 1 shown in Figure 1 but also friction clutches 1 with a different design pivot bearing 10 are possible. For example, the pivot bearing by two wire rings, that is, by a clutch cover side wire ring as in Figure 1 and a pressure-plate-side wire ring may be formed. The pressure-plate-side wire ring can be supported by cover-side hook portions, such a friction clutch is usually referred to as a pinless coupling, or supported by Tellerfederzentrierbolzen, wherein such a friction clutch is commonly referred to as a pin clutch. The Tellerfederzentrierbolzen are usually riveted to the clutch cover. In order to reduce the hysteresis of the friction clutch in the worn state, it is possible to rivet the Tellerfederzentrierbolzen with cover-side tab portions which are biased limited in their elastic range in the axial direction. Such a friction clutch is commonly referred to as a tab clutch.

In order to transmit the torque from the counter-pressure plate 2 or from the clutch cover 5 to the pressure plate 2, a plurality of leaf springs 9 arranged distributed in the circumferential direction U of the friction clutch 1 are provided in the embodiment shown, by which the pressure plate 4 with respect to its center of rotation D or respect the axis of rotation of the friction clutch 1 rotatably and in the axial direction A limited displaceable on the clutch cover 5 is connected.

In a normally-engaged, shown in Figure 1 friction clutch 1, the effective force of the plate spring 6 in the non-actuating state outweighs the opposing force of the leaf springs 9, that is, in the non-actuating state, the friction clutch 1 is engaged. Accordingly, an operation of the plate spring 6 of the normally-engaged friction clutch 1 by the actuator means for disengaging the friction clutch 1 by tilting or snapping the plate spring 6, that is for lifting the pressure plate 4 and for removing the pressure plate 4 of the counter-pressure plate 2, whereby the frictional engagement between the pressure plate 4 and the clutch disc 3 or between the clutch disc 3 and the counter-pressure plate 2 is canceled. In a non-illustrated, normally-disengaged friction clutch, the plate spring is usually replaced by a lever spring. In the non-actuated state of the normally-disengaged friction clutch, the opposing force of the leaf springs outweighs the effective force of the lever spring, that is, the friction clutch is disengaged in the non-actuated state. Accordingly, an operation of the lever spring the normally-disengaged friction clutch by the actuator means for engaging the friction clutch by tilting or snapping the lever spring, that is, for the frictional clamping of the clutch disc between the pressure plate and the counter-pressure plate.

When the friction clutch 1 is engaged, the torque is transmitted from the input side of the friction clutch, for example, by a dual-mass flywheel, via the counterpressure plate 2 and the clutch cover 5 to the pressure plate 4 arranged inside the clutch cover 5. From the counter-pressure plate 2 and the pressure plate 4, the torque is transmitted to the clutch disc 3, which is frictionally clamped between the pressure plate 4 and the counter-pressure plate 2, wherein the clutch disc 3, for example, rotatably mounted on an input shaft of a transmission.

The pressure plate 4 has in the embodiment of the friction clutch 1 shown in Figure 1 a multi-part friction plate 14, leaf spring tabs and a cam ring 15. All components of the pressure plate 4 are preferably made of sheet metal. The cam ring 15 serves to rest on the force edge 7 of the disk spring 6 in order to initiate the cup spring force acting in the axial direction A into the pressure plate 4. Like the cam ring 15, the leaf spring tabs on the side facing away from the clutch disc 3 of the friction plate 14 are fixed to the friction plate 14, wherein the leaf spring tabs are preferably distributed in the circumferential direction U and the connection of the pressure plate 4 serve to the leaf springs 9. Both the cam ring 15 and the leaf spring tabs represent optional features of the pressure plate 4, since the functions of the cam ring 15 and / or the leaf spring tabs can be equally integrated in the friction plate 14 and in Anpressplattensegmente 16, 17, 18 of the friction plate 14.

FIG. 2 shows an exemplary embodiment of the pressure plate 4 or the friction plate 14. The friction plate 14 is viewed in the axial direction A formed substantially annular and in a plurality of circumferentially U successively arranged and with respect to each other at least partially displaceable Anpressplattensegmenten 16, 17, 18 divided. In the illustrated embodiment, there are six Anpressplattensegmente 17, 18, the two different Assign to groups. The pressure plate 4 and the friction plate 14 has with respect to its center of rotation D a Drehsymmet e of 120 °.

The circumferential direction U of the pressure plate 4 extends in a normal plane N with respect to the axial direction A of the pressure plate 4. That is, a vector of the axial direction A pierces the normal plane N at right angles.

Two contact pressure plate segments 16, 17, 18 which are adjacent in the circumferential direction U have two end faces 19, 20 facing one another, which are connected to one another by a connecting device 21 extending in the normal plane N. One of the two contact pressure plate segments 16, 17, 18 has a recess 22 which essentially corresponds to a contour of the connecting device 21 and receives the connection device 21. The recess 22 has a uniform width B measured in the normal plane N. Alternatively, the measured in the normal plane N width B, starting from the end face 20 of the Anpressplattensegments 16, 17, 18 into the interior of the Anpressplattensegments 16, 17, 18 from.

The mutually facing end faces 19, 20 are spaced apart in the circumferential direction U by a gap-shaped intermediate space 23. In the illustrated embodiment, the gap-shaped intermediate space 23 comprises both the actual end faces 19, 20 and the adjacent regions of the connecting device 21 and the recess 22.

The recess 22 has a central axis 24, which has a non-concentric profile relative to the center of rotation D of the pressure plate 4. In the exemplary embodiments illustrated in FIGS. 2 to 4, the central axis 24 has a change of direction, which in the illustrated exemplary embodiment includes an angle of 90 °, wherein the end of the recess 22 located in the interior of the pressure plate segment 18 moves in the radial direction R outside points. Preferably, the change of direction of the central axis 24 contains an angle greater than 45 °.

The exemplary embodiments of the pressure plate 4 or of the friction plate 14 and of the pressure plate segments 16, 17, 18 illustrated in FIGS. 2 to 4 differ from the following exemplary embodiments, which are shown in FIGS. 5 and 6. 2, in particular by the fact that the pressure plate 4 or the friction plate 14 in FIG. 2 has two groups of pressure plate segments 17, 18, of which the pressure plate segments 17 of the first group project two end surfaces 19 each in the direction of the adjacent pressure plate segments 18 of the second group - Have lowing connection means 21, and of which the Anpressplattensegmente 18 of the second group have two end faces 20 with corresponding, extending into the interior of the Anpressplattensegmente 18 of the second group recesses 22. The contour of the connecting device 21 is formed according to the contour of the recess 22 described above. The pressure plate segments 17, 18 of the first group and the second group are arranged alternately in the circumferential direction U.

Furthermore, it is possible, for example, for the pressure plate segments 17 of the first group or the pressure plate segments 18 of the second group to have outwardly extending leaf spring tabs in the radial direction R, which are integral with the respective pressure plate segments 17 of the first group or the respective pressure plate segments 18 of the second group Group are formed, and where the pressure-plate-side ends of the leaf springs 9 are fixed. It is also possible that all pressure plate segments 16, 17, 18 are provided on their sides facing away from the clutch disc 3 with cam portions for bearing the force edge 7 of the plate spring 6.

Figures 5 and 6 relate to embodiments of the pressure plate 4 and the friction plate 14, in which each pressure plate segments 16 are assigned to a single group of Anpressplattensegmente 16. Each of the pressure plate segments 16 has a first cutting surface 19 with a connecting device 21 projecting in the direction of the respectively adjacent pressure plate segment 16 and a second end surface 20 with a corresponding recess 22 extending into the interior of the pressure plate segment 16. The two end faces 19, 20 of the respective pressure plate segment 16, 17, 18 are arranged opposite each other in the circumferential direction U of the pressure plate 4 and the friction plate 14.

In Figure 5, the central axis 24 of the recess 22 and thus also the same contour connecting means 21 more, in the specific case three, change of direction on, so that the recess 22 is formed meander-shaped. The inner end of the recess 22 has in the radial direction R inwards.

In FIG. 6, the central axis 24 of the recess 22 and thus also the connectionless connecting device 21 have a single change of direction, wherein the inner end of the recess 22 is directed outward in the radial direction R.

In the illustrated embodiments, the Anpressplattensegmente 16, 17, 18 cover equal angular ranges of the pressure plate 4 and the friction plate 14 from. In the specific case, each pressure plate segment 16, 17, 18 covers an angular range of 60 °, so that the pressure plate 4 or the friction plate 14 is composed of six pressure plate segments 16, 17, 18. However, it is also possible that the pressure plate segments 16, 17, 18 cover different angular ranges of the pressure plate 4 and the friction plate 14.

The preceding embodiments relate to a pressure plate 4 for a friction clutch 1 of a motor vehicle, the pressure plate 4 viewed in the axial direction A of the pressure plate 4 is substantially annular and arranged in a plurality of circumferentially U of the pressure plate 4 successively and with respect to each other at least partially displaced Pressure plate segments 16, 17, 18 is divided, wherein the circumferential direction U in a normal plane N with respect to the axial direction A, wherein at least two circumferentially U adjacent Anpressplattensegmente 16, 17, 18 two facing end faces 19, 20, which by at least a connecting device 21 extending in the normal plane N are connected to one another, wherein at least one of the two pressure plate segments 16, 17, 18 opens up a connecting device 21 substantially corresponding to a contour of the connecting device 21 hmende recess 22, wherein the recess 22 has a measured in the normal plane N, constant width B or measured in the normal plane N width B, starting from the end face 20 of the Anpressplattensegments 16, 17, 18 inside the Anpressplattensegments 16, 17, 18th decreases. In addition, the preceding embodiments relate to a friction clutch 1 for a motor vehicle with at least one counter-pressure plate 2, with at least one connected to the counter-pressure plate 2 clutch cover 5, and with at least one with respect to the platen 2 in the axial direction A of the friction clutch 1 limited displaceable pressure plate 4 to frictional clamping a clutch disc 3 between the platen 2 and the pressure plate 4, wherein the pressure plate 4 is formed according to one of the preceding embodiments.

LIST OF REFERENCE NUMBERS

friction clutch

Platen

clutch disc

pressure plate

clutch cover

Belleville spring

force boundary

8 plate spring tongue

9 leaf spring

10 pivot bearing

1 1 wire ring

12 support spring

13 hook section

14 friction plate

15 cam ring

16 pressure plate segment

17 pressure plate segment

18 pressure plate segment

19 face

20 face

21 connection device

22 recess

23 space

24 central axis

A axial direction

D turning center

R radial direction

U circumferential direction

N normal level

B width

Claims

claims

Pressure plate (4) for a friction clutch (1) of a motor vehicle, wherein the pressure plate (4) in the axial direction (A) of the pressure plate (4) viewed substantially annular and in a plurality of circumferentially (U) of the pressure plate (4 ) is successively arranged and with respect to each other at least partially displaceable Anpressplattensegmenten (16, 17, 18) is divided, wherein the circumferential direction (U) in a normal plane (N) relative to the axial direction (A), wherein at least two in the circumferential direction (U) adjacent contact pressure plate segments (16, 17, 18) have two mutually facing end faces (19, 20) which are connected to one another by at least one connecting device (21) extending in the normal plane (N), wherein at least one of the two contact pressure plate segments (16, 17 , 18) one of a contour of the connecting means (21) substantially corresponding and the connecting means (21) receiving recess (22), characterized in that the recess (22) has a uniform width (B) measured h of the normal plane (N) or the width (B) measured in the normal plane (N) starting from the end face (20) of the Pressure plate segment (16, 17, 18) into the interior of the pressure plate segment (16, 17, 18) decreases.

Pressure plate (4) according to claim 1, wherein the mutually facing end faces (19, 20) at least in the circumferential direction (U) by a gap-shaped intermediate space (23) are spaced from each other.

Pressure plate (4) according to claim 1 or 2, wherein the recess (22) has a central axis (24), and the central axis (24) with respect to a center of rotation (D) of the pressure plate (4) non-concentric course.

Pressure plate (4) according to claim 3, wherein the central axis (24) has at least one change of direction.

5. pressure plate (4) according to claim 4, wherein the change of direction includes an angle greater than 45 °. Pressure plate (4) according to one of claims 1 to 5, wherein all Anpressplattensegmente (16) of the pressure plate (4) each have a first end face (19) with a in the direction of each adjacent Anpressplattensegments (16) projecting connection means (21) and a second end face (20) with a corresponding, in the interior of the Anpressplattensegments (16) extending recess (22).

Pressure plate (4) according to one of claims 1 to 5, wherein the pressure plate (4) comprises two groups of Anpressplattensegmenten (17, 18), of which the Anpressplattensegmente (17) of the first group two end faces (19), each in the direction of the adjacent Pressure plate segments (18) of the second group projecting connection means (21), and of which the pressure plate segments (18) of the second group two end faces (20) with corresponding, extending into the interior of the Anpressplattensegmente (18) of the second group recesses (22) , and wherein the pressure plate segments (17, 18) of the first group and the second group are arranged alternately in the circumferential direction (U).

Pressure plate (4) according to one of claims 1 to 7, wherein the Anpressplattensegmente (16, 17, 18) cover the same angular ranges of the pressure plate (4).

Pressure plate (4) according to one of claims 1 to 7, wherein the Anpressplattensegmente (16, 17, 18) cover different angular ranges of the pressure plate (4).

Friction clutch (1) for a motor vehicle with at least one counterpressure plate (2), with at least one clutch cover (5) connected to the counterpressure plate (2), and with at least one relative to the counterpressure plate (2) in the axial direction (A) of the friction clutch (1 ) limited displaceable pressure plate (4) for frictional clamping of a clutch disc (3) between the counter-pressure plate (2) and the pressure plate (4), wherein the pressure plate (4) is designed according to one of claims 1 to 9.