Clutch device

Abstract

The clutch device comprises a first clutch with a friction plate group and a second clutch with a friction plate group. A first and a second spring element are arranged to generate a reset force. The first operating element can be moved against the first spring element to press the first friction plate group together, and the second operating element can be moved against the second spring element to press the second friction plate group together. The first and second spring elements are supported on a common supporting ring on the premise of forming a common spring group. The first and second spring elements are supported on the supporting ring at the same radius. The first spring element is also supported on a first pressure section of a first clamping ring that can be moved by the first operating element, and the second spring element is also supported on a second pressure section of a second clamping ring that can be moved by the second operating element. The first and second spring elements have the same length and a through hole is designed between the first pressure section, and the second pressure section passes through the through hole.

Description

Technical Field

[0001] The present invention relates to a clutch device, which comprises a first clutch having a friction plate group that can be pressed together against a first reset force, and a second clutch having a friction plate group that can be pressed together against a second reset force, wherein first and second spring elements are provided to generate the reset force, wherein a first operating element can be moved relative to the first spring element to press the first friction plate group together and a second operating element can be moved relative to the second spring element to press the second friction plate group together, wherein the first and second spring elements are supported on a common support ring on the premise of forming a common spring group, wherein the first and second spring elements are supported on the support ring on the same radius. Background Art

[0002] As is known, such clutch devices are used to temporarily establish a torque-transmitting force-fit connection between a drive shaft of an internal combustion engine or electric machine and an output shaft running to a transmission. When designed as a single clutch, the clutch device usually comprises an outer friction plate carrier with an outer friction plate that can be axially displaced thereon, an inner friction plate carrier with an inner friction plate that can be axially displaced thereon, and an operating element, usually in the form of a pressure tank, which can be axially displaced in order to axially press the friction plate pack together. The outer friction plate carrier is connected, for example, to a drive shaft for introducing torque, while the inner friction plate carrier is connected to an output shaft leading to the transmission. By pressing the friction plate pack together to form a force-fit or friction-fit connection, the torque introduced from the drive shaft via the outer friction plate carrier can be directed to the inner friction plate carrier via the friction plate pack and then to the output shaft leading to the transmission.

[0003] In addition to the single clutch with only one friction plate group, it is also known that the clutch device can be designed as a double clutch. In this case, the clutch device includes a first clutch and a second clutch, which each have a corresponding friction plate group including an outer friction plate and an inner friction plate, and an outer friction plate carrier and an inner friction plate carrier, wherein each friction plate group can be pressed together by a separate operating element, i.e., a separate pressure tank. The two outer friction plate carriers are, for example, jointly connected to a drive shaft for introducing torque, while the two inner friction plate carriers are connected to a separate output shaft leading to a separate gear stage, which can be individually connected by a single clutch.

[0004] The structure of the above-mentioned single or double clutch is well known.

[0005] As described above, a torque-transmitting friction fit connection is formed by pressing the individual friction plate groups together. If this connection is no longer required, the individual friction plate groups pressed together must be reopened to relieve the load. For this purpose, it is required to release the operating element from the friction plate group as quickly as possible in order to ventilate it. Therefore, the operating element, i.e. the pressure tank, can be moved against the spring element to press the friction plate group together, and the spring element will generate a restoring force, thereby pushing the operating element back to the starting position when it is relieved of the load by the upstream hydraulic operating device.

[0006] In the double clutch, corresponding first and second spring elements, for example helical springs, are provided, wherein the first operating element can be moved against the first spring element and the second operating element can be moved against the second spring element. Usually, the first spring element in the form of a first spring group and the second spring element in the form of a second spring group are pressed together and supported on a support ring respectively, so that each spring group can be coupled to the corresponding operating element separately. In the case of a radial arrangement of the first separator relative to the second clutch or a radial arrangement of the first friction plate group relative to the second friction plate group, the spring groups have different diameters accordingly. As an alternative, it is also conceivable, see for example DE 10 2016 222 739 A1, to arrange the first and second spring elements as compactly as possible, according to DE 10 2016 222 739 A1, for which the second spring element is placed concentrically in the first spring element, so that the corresponding spring pair is formed by the first and second spring elements. In this case, the second spring element is significantly longer than the first spring element, so that when viewed in the axial direction, the two operating elements are also coupled to the corresponding first and second spring elements in different axial planes. In addition to this integrated spring element arrangement, DE 10 2016 222 739 A1 also discloses a separate arrangement of first and second spring elements of different lengths on the same radius.

[0007] Due to the different lengths of the first and second springs, the known spring arrangement is not very compact when viewed in the axial direction. In particular, different centrifugal forces are generated during operation due to the different geometries of the spring elements and are also distributed unevenly. This is problematic in particular when such dual clutch devices are used in conjunction with purely electric drives, since the drive or the electric motor runs at very high speeds and the clutch device, together with its spring assembly, therefore also rotates at very high speeds.

[0008] The problem underlying the present invention is to provide an improved clutch device. Summary of the invention

[0009] In order to solve the problem, the present invention stipulates that for a clutch device of the type described at the beginning, the first spring element is also supported on a first pressure section of a first clamping ring that can be moved by a first operating element, and the second spring element is also supported on a second pressure section of a second clamping ring that can be moved by a second operating element, wherein the first and second spring elements have the same length and a through hole is designed between the first pressure section, and the second pressure section passes through the through hole.

[0010] In the clutch device described in the present invention, the first and second spring elements have the same length, that is, spring elements with the same geometry can be used, wherein only differences can be shown in the spring element characteristics, but this does not affect the spring geometry. They are supported on a common support ring by one end. The other end of the first and second spring elements is supported on the corresponding first and second pressure segments of the two operating elements, wherein, because the spring elements have the same length, these pressure segments are in the same axial plane in the non-operated state, that is, when no load is applied to the clamping ring. In order to realize the separate operation of the first and second spring elements, the following possibility must be provided, namely: the pressure segments can pass through each other. For this purpose, corresponding through holes are designed between the first pressure segments designed on the first clamping ring, and the second pressure segment of the second clamping ring slightly separated from the first clamping ring when viewed in the axial direction can pass through the through holes.

[0011] This results in a very compact spring assembly structure viewed in the axial direction, since identical spring elements can be used, the structure is also uniform, whereby the centrifugal forces acting on the spring elements are kept low in combination with the compact arrangement on the same radius, in particular, since the spring elements can be arranged very close around the drive shaft due to the compact arrangement on the same radius, i.e., this structure also keeps the diameter of the spring arrangement relatively small. The clutch device according to the invention is therefore particularly suitable for use at high speeds.

[0012] Preferably, a helical spring is provided as the spring element, wherein, viewed in the circumferential direction, the first and second spring elements are preferably arranged alternately, and the first and second pressure sections are therefore also designed alternately with one another. Of course, this also results in a symmetrical design of the pressure ring, which, on the one hand, ensures a symmetrical introduction of force from the pressure ring to the spring element assembly and vice versa, so that no tilting occurs, and, on the other hand, allows the pressure ring to achieve a certain degree of balance with respect to centrifugal forces.

[0013] The pressure section itself is preferably designed as a flat web, so that a sufficiently large supporting surface is available for the corresponding spring element or helical spring.

[0014] In order to be able to fix the helical spring to the support ring and the connecting piece in a simple manner, it is advantageous if an axial projection is provided on the support ring and the connecting piece, on which the inner circumference of the helical spring is fixed. This cylindrical, axially extending projection engages in the inner circumference of the helical spring, that is, the helical spring is pressed against the projection and is thereby fixed firmly.

[0015] As described, the first clamping ring is moved by the first operating element, i.e. the first pressure tank, and the second clamping ring is moved by the second operating element, i.e. the second pressure tank, wherein the pressure tank is axially moved in a known manner by a corresponding hydraulic piston device, such as a CSC operating device. Regardless of whether the first and second clutches are radially nested or axially arranged, the first pressure tank is axially offset relative to the second pressure tank, which results in that, when viewed in the axial direction, the first and second clamping rings are also offset from each other, at least the segments acted upon by the pressure tanks are offset from each other. In order to be able to couple the first operating element to the piston device or the intermediate clutch bearing in a simple manner, it is advantageous that a through hole is provided on the clamping ring, through which a corresponding axially extending locating pin of the first operating element passes. The locating pin extends axially to the clutch bearing of the piston device and abuts against it, thereby forming a mechanical coupling. Here, the through hole of the second clamping ring can be designed in the extension of the first pressure section of the first clamping ring, but they are also designed to be offset in the circumferential direction.

[0016] In particular, when two clutches are radially nested, but in principle it is also feasible when two clutches are axially arranged, it is advantageous that the second clamping ring has an outer diameter greater than that of the first clamping ring, wherein a contact section for the first or second operating element is designed on the outer circumference of the first and / or second clamping ring. In particular, when two clutches are radially nested, the second operating element must continue to be radially guided outward to the radially outer second friction plate group. However, since the hydraulic operating device, such as the CSC device, is also coaxially designed, and the corresponding pistons are arranged coaxially with each other and are therefore radially nested like the corresponding clutch bearings, the second clamping ring is designed with an inner diameter greater than that of the first clamping ring. Therefore, relative to the first pressure tank on the first clamping ring, the second pressure tank acts on the contact section of the second clamping ring at a position further outward when viewed in the radial direction. Regardless of whether this is the case, the corresponding clamping ring design allows for further compactness and thus better utilization of the existing structural space.

[0017] The support ring, but in particular also the two clamping rings, are manufactured as simple sheet metal components made of sheet metal. Taking into account the forces, the support ring and / or the first and / or second clamping ring can be reinforced by ribs and / or flanged edge sections to strengthen them, i.e. the rigidity can be increased by a corresponding geometric design.

[0018] Furthermore, in a clutch device which essentially corresponds to the definition at the outset and is also known and does not necessarily have the above-mentioned features of the invention, it can be provided that a hub is arranged on the shaft in a rotationally fixed manner, a synchronizing element is arranged on the hub and is coupled to the outer friction plate carriers of the two friction plate groups, wherein the hub is axially locked by a retaining ring axially fixed in a groove on the shaft, wherein at least one axially extending locking section is arranged on the support ring of the spring group and abuts against the retaining ring in a radially overlapping manner. As described at the outset, the torque is introduced via the drive shaft and is transmitted to the drive shaft via a synchronizing element in the form of an annular flange connected to the drive shaft, which is connected to the two outer friction plate carriers of the two clutch parts, which are preferably radially nested and arranged coaxially with each other. The synchronizing element is connected to the drive shaft in a rotationally fixed manner via a hub with internal teeth, which is inserted into the radial gear teeth on the outer circumference of the drive shaft in a snap-fit ​​manner. The hub is pushed into the axial gear teeth from one end of the drive shaft and is axially fixed to the axial gear teeth by the retaining ring. The retaining ring, a slotted metal ring, is engaged in a radial groove formed in the area of ​​the external toothing of the drive shaft, thus supporting the hub axially thereon.

[0019] In conventional use in conjunction with an internal combustion engine, the clutch is not exposed to excessively high rotational speeds, so that there is no risk of deformation of the retaining ring due to centrifugal forces, whereas when the clutch is used in conjunction with a purely electric drive, i.e. a corresponding electric motor, expansion may occur and may pop out of the groove due to the slot, which proves to be a risk at very high rotational speeds. In order to prevent the retaining ring from expanding due to centrifugal forces in a simple manner, the invention provides that this is ensured by a support ring of the spring assembly containing the first and second spring elements, which is possible when the spring elements or the spring element arrangement are very compact and extend around the drive shaft or the wheel hub with a small spacing. This allows the design of corresponding locking segments on the support ring, which extend axially, overlap the retaining ring radially and abut against the retaining ring. The support ring thus fulfills a dual function, namely: on the one hand, it supports the first and second spring elements and on the other hand, it locks the retaining ring. That is to say, the clutch can also be rotated at a speed that is significantly higher than the release speed of the slotted retaining ring (without additional locking by the support ring), without causing any problems for the arrangement of the retaining ring in the groove.

[0020] Here, the collar can be designed as a curling section surrounding the entire inner circumference of the support ring, that is, the curling section surrounds the collar around the entire circumference and abuts against the collar. As an alternative, it is also conceivable to design a plurality of curling connecting pieces on the inner circumference of the support ring, which are spaced from each other in the circumferential direction and each constitutes a locking section. In this case, contact does not occur over the entire circumference, but only at a local position, but this is also sufficient to ensure locking. For example, 4-10 such curling connecting pieces are designed.

[0021] As described, the two clutches are preferably arranged in a radially staggered manner, that is, the two friction plate groups are radially staggered and extend concentrically with each other, as are the corresponding annular friction plate carriers. In particular, viewed in the axial direction, this can result in a very compact structure, wherein, since the spring element device has to a certain extent the smallest possible inner diameter and extends directly adjacent to the drive shaft or the wheel hub, it can be further compacted, since the spring element device can be integrated in a still existing, hitherto unused structural space, or, as before, no structural space is required for a separate spring device. Viewed in the radial direction, since the corresponding components can be arranged at a small distance from each other, a sufficiently high degree of compactness is also provided. Of course, as an alternative, the friction plate groups or clutches can also be arranged in an axially series manner. This allows a relatively small structure, especially in the radial direction. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The present invention will be described below with reference to the drawings according to the embodiments. The drawings are schematic diagrams, wherein:

[0023] Figure 1 A perspective view of a spring element arrangement or a complete spring assembly including a support ring and two compression rings, and

[0024] Figure 2 The present invention comprises two clutches and Figure 1 The clutch device of the spring element device shown.

[0025] Description of Reference Numerals

[0026] 1 spring assembly 2 spring element 3 spring element 4 support ring 5 radial flange 6 projection 7 annular flange 8 locking section 9 pressure ring 10 pressure ring 11 pressure section 12 connecting plate 13 projection 14 through hole 15 through hole 16 connecting plate 17 flange 18 projection 19 radial flange 20 contact section 21 contact section 22 through hole 23 clutch device 24 clutch 25 friction plate assembly 26 outer friction plate bracket 27 outer friction plate bracket 28 inner friction plate bracket 29 inner friction plate 30 synchronization element 31 wheel hub 32 drive shaft 33 inner tooth 3 4 external teeth 35 snap ring 36 annular groove 37 synchronization pin 38 positioning pin 39 internal teeth 40 external teeth 41 output shaft 42 snap ring 43 clutch 44 friction plate group 45 external friction plate bracket 46 external friction plate 47 internal friction plate bracket 48 internal friction plate 49 positioning pin 50 snap ring 51 snap ring 52 hub 53 internal teeth 54 external teeth 55 output shaft 56 operating element 57 operating device 58 clutch bearing 59 piston 60 operating element 61 operating device 62 clutch bearing 63 annular piston 64 positioning pin 65 perforation. DETAILED DESCRIPTION

[0027] Figure 1 A perspective view of a spring assembly 1 provided for the clutch device according to the invention is shown, which comprises a first spring element 2 and a second spring element 3, which are supported alternately with one another on a support ring 4 on the same radius by means of one side. The spring elements 2, 3 are preferably identical in geometry and also preferably identical in number, but the number can also be different, just as different spring elements have, for example, different elastic forces. In any case, the first and second spring elements 2, 3 have the same length.

[0028] On the support ring 4 with corresponding radial flanges 5 there are corresponding axially aligned projections 6 which are cylindrical and engage in the first and second spring elements 2 , 3 , against which the spring elements 2 , 3 are pressed and thereby fixed to the support ring 4 .

[0029] In addition, the support ring 4 has an axially protruding annular flange 7 on its inner circumference, which is designed as a circumferentially flanged locking section 8 for locking a clamping ring, which will be described below.

[0030] The first spring element 2 is used to reset the first operating element of the first clutch in the form of a pressure tank that is movably coupled thereto, while the second spring element 3 is used to reset the second operating element of the second clutch in the form of a second pressure tank. In order to couple the first and second spring elements 2, 3 to the first and second operating elements, respectively, a first clamping ring 9 and a second clamping ring 10 are provided, which are arranged close to the support ring 4 in the axial direction. A first pressure section 11 in the form of a planar connecting piece 12 that protrudes radially inward is designed on the first clamping ring 9, and a corresponding protrusion 13 that engages in the first spring element 2 is also designed thereon, that is, the first spring element 2 on this side is pressed against the protrusion.

[0031] A through hole 14 is provided between the first pressure sections 11, in which a second pressure section 15 in the form of a large flat connecting piece 16, which is provided on the second pressure ring 10, is engaged. For this purpose, an axially extending flange 17 is provided on the second pressure ring 10, on the inner circumference of which the connecting piece 16 directed radially inward is molded. A corresponding protrusion 18 is also provided on the connecting piece 16, on which the second spring element 3 is pressed.

[0032] Since the spring elements 2 and 3 have the same length, the connecting pieces 12 and 16 are in the same plane when viewed in the axial direction without being loaded. When the first clamping ring 9 is axially moved by the first operating element, the first spring element 2 is squeezed together, the first clamping ring 9 moves away from the second clamping ring 10 which is not operated, and the second connecting piece 16 moves out of the through hole 14. On the contrary, if the first clamping ring 9 is not loaded and the second operating element axially moves the second clamping ring 10, the second spring element 3 is compressed, wherein the second connecting piece 16 is moved through the through hole 14 during the movement of the clamping ring. In other words, a corresponding penetration is formed, thereby allowing the two clamping rings 9 and 10 to move independently relative to each other.

[0033] A radial flange 19 is designed on the second clamping ring 10, and a molded contact section 20 is provided on its outer circumference, on which a second operating element in the form of a pressure tank is closely attached, which will be described below. The first clamping ring 9 also has a contact section 21 on its outer circumference, and the first operating element, i.e., the first pressure tank, is in close contact with this contact section. The geometry of the edge sides of the two pressure tanks 9 and 10 is formed by a corresponding forming process, and the surrounding bends are used to strengthen each clamping ring 9 and 10, wherein additional ribs or similar structures can also be molded in the corresponding annular segments, although not shown in detail. If the clamping rings 9, 10 and the supporting ring 4 are composed of metal sheets, the design can be implemented without any problems.

[0034] As long as the second clamping ring 10 (because it is axially externally arranged) can be mechanically coupled to the second operating element, i.e. the second pressure tank, without any problems in the area of ​​the contact section 20, corresponding precautions are provided for the coupling of the first clamping ring 9 to the first operating element or the first pressure tank so that the other end of the first operating element is connected to the hydraulic operating device or the relevant clutch bearing. A plurality of through-holes 22 distributed in the circumferential direction are provided on the radial flange 19, through which the axially extending positioning pins of the first clamping ring (not shown in detail here) which in the installed position abut against the clutch bearing of the relevant hydraulic operating device extend. In the example shown, the through-holes 22 are designed to be radially offset relative to the first connecting plate 12, but can also be positioned in the axial extension.

[0035] Figure 2 The schematic diagram of the clutch device 23 described in the present invention is shown, and the clutch device includes a first sub-clutch 24 with a first friction plate group 25, and the first friction plate group includes an axially movable outer friction plate 27 arranged on a first outer friction plate bracket 26 and an axially movable inner friction plate 29 arranged on a radially inner first inner friction plate bracket 28, which is clamped between the outer friction plates 27.

[0036] The outer friction plate carrier 26 is connected to a drive shaft 32 for introducing the torque to be transmitted via a synchronization element 30 with a corresponding hub 31, for which purpose the hub 31 with axial internal teeth 33 is pushed into the axial external teeth 34 of the drive shaft 32. Axial locking is achieved by a retaining ring 35 which is engaged in an annular groove 36 of the external teeth 34. The radial flange 30 passes through the outer friction plate carrier 26 via corresponding synchronization pins 37, and at the end of the outer friction plate carrier there are corresponding positioning pins 38 which are clamped between the synchronization pins 37.

[0037] The inner friction plate carrier 28 is pushed onto the axial outer teeth 40 of the first output shaft 41 by means of the axial inner teeth 39 and is axially locked here by a retaining ring 42 which engages in a groove. The retaining ring applies the torque introduced via the drive shaft 32 to the first output shaft 41 when the friction plate pack 25 is pressed together.

[0038] Furthermore, a second partial clutch 43 (43 = groove) is provided, which is located further outward in the radial direction and has a second friction plate set 44, which comprises an outer friction plate carrier 45 with an outer friction plate 46 which can be axially displaced thereon and an inner friction plate carrier 47 with an inner friction plate 48 which can be axially displaced thereon. The outer friction plate carrier 45 has corresponding axially aligned positioning pins 49 at its ends, between which the synchronization pins 37 are clamped. The synchronization pins 30 thus provide a rotationally fixed coupling between the drive shaft 32 and the two outer friction plate carriers 26 and 45, so that the outer friction plate carriers are also forced to rotate together with their outer friction plates 27, 46 when the drive shaft 32 rotates. In order to lock the mechanical connection, the synchronization element 30 is axially locked by corresponding retaining rings 50, 51 which engage in corresponding grooves in the positioning pins 38, 49.

[0039] The inner friction plate carrier 47 is received in a torsionally fixed manner on the axial outer teeth 54 of the second output shaft 55 via a hub 52 having axial inner teeth 53 and is locked by a retaining ring 42. Therefore, when the second friction plate group 44 is pressed together, the torque introduced via the drive shaft 32 is transmitted to the inner friction plate carrier 47 and, via it, to the second output shaft 55.

[0040] In order to press the first friction plate group 25 together, a first operating element 56 is provided. Figure 2 As shown, the first operating element acts on the first friction plate group 25 on the one hand and is coupled at its other end to the hydraulic first operating device 57 or its clutch bearing 58. When the hydraulically axially movable piston 59 is axially displaced, the clutch bearing 58 is also displaced, and then the first operating element 56, i.e. the pressure tank, is displaced against it in order to press the friction plate group together.

[0041] In the same way, the second friction plate group 44 can be pressed together axially by a second operating element 60, which is also in the form of a pressure tank. The second operating element 60 is coupled to the hydraulic operating device 61 or its clutch bearing 62 through its other end, so that when the other annular piston 63 is hydraulically moved, the clutch bearing 62 and thus the second operating element 60 are moved to press the second friction plate group 44 together.

[0042] The first and second actuating elements 56, 60 are moved against a spring assembly 1 which is arranged radially directly adjacent to the hub 31 or drive shaft 32 and which extends significantly below the inner friction plate carrier 28 of the first clutch 24. The sectional view shows by way of example a second spring element 3 which is fastened on the one hand to the support ring 4 and on the other hand to the second web 16 of the second pressure ring 10. In addition to the second pressure ring 10, the first pressure ring 9 is also shown, wherein it can also be seen from the figure that the webs 12 and 16 are in the same axial plane, i.e. are aligned with each other when viewed in the radial direction.

[0043] The first clamping ring 9 is used to support the first operating element 56, which is close to its upper edge area. When the first operating element 56 is moved axially to the left, the first spring element 2 is squeezed together, the second spring element 3 remains in an unoperated state, and the second clamping ring 10 does not move. The first spring element 2 forms a restoring force, which pushes the first operating element 56 back to the starting position when the load is removed.

[0044] The second operating element 60 acts on the second pressure ring 10 in the contact section 20. When the second connecting piece 16 is moved axially to the left, it pushes the second connecting piece 16 through the first pressure ring 9 or the through hole 14, thereby squeezing the second spring element 3 together and forming a restoring force, which pushes the second operating element 60 back again when the load is released.

[0045] Based on the axial series arrangement of the two clamping rings 9 and 10, the first operating element 56 passes through the through-hole 22 of the second clamping ring 10 with its corresponding axially extending locating pin 64, and the locating pin 64 also passes through the corresponding through-hole 65 in the synchronization element 30, so that the locating pin 64 is close to the clutch bearing 58.

[0046] As described, the hub 31 is axially locked on the drive shaft 32 by the snap ring 35. It can be seen that the axially extending and surrounding locking section 8 molded on the support ring 4 overlaps the snap ring 35 and also bears radially against it. Due to this completely surrounding design, it is impossible for the snap ring 35 to deform and expand and pop out of the groove 36, even at very high rotational speeds. Rather, it is forcibly fixed in the groove 36 by the locking section 8.

[0047] Due to the very small diameter of the spring assembly 1, its structure is also very small, so that the spring assembly can be arranged in a position with significantly lower centrifugal forces due to the small diameter compared to designs with a larger diameter and other positioning methods. By integrating the spring assembly 1 to a certain extent below the first inner friction plate carrier 28, the structural space can also be optimally utilized. In addition, the support ring 4 can also fulfill its dual function, namely, on the one hand, as a supporting ring for the spring elements 2, 3, and on the other hand, as a locking member of the clamping ring 35 on the support ring side locking section 8.

[0048] although Figure 1 and 2 A circumferential locking segment 8 is shown, but it is also conceivable to provide separate web-shaped locking segments offset in the circumferential direction, which do not overlap the snap ring 35 over the entire circumference but only partially, but are equally effective.

Claims

1. A clutch device, comprising a first clutch (24) having a first friction plate group (25) that can be pressed together against a first reset force, and a second clutch (43) having a second friction plate group (44) that can be pressed together against a second reset force, wherein: In order to generate the restoring force, a first and a second spring element (2, 3) are provided, wherein a first operating element (56) can be moved against the first spring element (2) in order to press the first friction plate group (25) together, and a second operating element (60) can be moved against the second spring element (3) in order to press the second friction plate group (44) together, wherein the first and the second spring elements (2, 3) are supported on a common support ring (4) under the premise of forming a common spring group (1), wherein the first and the second spring elements (2, 3) are supported on the support ring (4) at the same radius, characterized in that the first spring element (2) is also supported on a first pressure section (11) of a first pressure ring (9) which can be moved by the first operating element (56), and the second spring element (3) is also supported on a first pressure section (11) of a first pressure ring (9) which can be moved by the second operating element (56). The first and second spring elements (2, 3) have the same length and a through hole (14) is provided between the first pressure section (11), and the second pressure section (15) passes through the through hole. The first pressure ring (9) and the second pressure ring (10) are arranged at intervals in the axial direction, and a contact section is provided on the outer circumference of the first pressure ring (9), and the first operating element (60) is in close contact with the contact section. The second pressure ring (10) is provided with an axially extending flange (17) and a radial flange (19), and the second pressure section (15) is radially inwardly aligned on the inner circumference of the flange (17), and a contact section is provided on the outer circumference of the radial flange (19). The second pressure ring (10) is mechanically coupled with the second operating element (60) in the area of ​​the contact section.

2. The clutch device according to claim 1, characterized in that: The spring elements (2, 3) are helical springs.

3. The clutch device according to claim 1 or 2, characterized in that: The pressure sections (11, 15) are designed as planar connecting pieces (12, 16).

4. The clutch device according to claim 3, characterized in that: Axial protrusions (6, 13, 18) are designed on the supporting ring (4) and the connecting pieces (12, 16), and a spiral spring is fixed on the inner circumference of the protrusions.

5. The clutch device according to claim 1 or 2, characterized in that: A through hole (22) is formed on the second pressure ring (10), through which a positioning pin (64) of the first operating element (56) passes.

6. The clutch device according to claim 1 or 2, characterized in that: The second pressure ring (10) has a larger outer diameter than the first pressure ring (9), wherein contact sections (20, 21) for the first or second operating element (56, 60) are formed on the outer circumference of the first and / or second pressure ring (9, 10).

7. The clutch device according to claim 1 or 2, characterized in that: The support ring (4) and / or the first and / or second clamping ring (9, 10) are reinforced by ribs and / or flanged edge sections.

8. The clutch device according to claim 1 or 2, characterized in that: A hub (31) is provided which is arranged on a shaft (32) in a rotationally fixed manner, and a synchronizing element (30) is arranged on the hub which is coupled to the outer friction plate brackets (26, 45) of the first friction plate group (25) and the second friction plate group (44), wherein the hub (31) is axially locked by a retaining ring (35) axially fixed in a groove (36) on the shaft (32), and wherein at least one axially extending locking section (8) is provided on the supporting ring (4) of the spring group (1), which is closely attached to the retaining ring (35) in a manner of radially overlapping the retaining ring.

9. The clutch device according to claim 8, characterized in that: The locking section (35) is designed as a flange section surrounding the entire inner circumference of the support ring (4), or a plurality of flange connecting pieces spaced apart from each other in the circumferential direction and each constituting a locking section are designed on the inner circumference of the support ring (4).

10. The clutch device according to claim 1 or 2, characterized in that: The first friction plate group (25) and the second friction plate group (44) are arranged in a radially staggered manner, or in an axially series manner.

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