WO2014154217A1

WO2014154217A1 - Bearing and axial support for a dual clutch on a gearbox input shaft

Info

Publication number: WO2014154217A1
Application number: PCT/DE2014/200140
Authority: WO
Inventors: Marcus Hoppe; Michael Baumann; Ivo Agner
Original assignee: Schaeffler Technologies Gmbh & Co. Kg
Priority date: 2013-03-26
Filing date: 2014-03-25
Publication date: 2014-10-02
Also published as: DE102014205506A1; DE112014001701A5

Abstract

The invention relates to a dual clutch for a drive train of a motor vehicle, comprising two outer supports non-rotationally connected to one another and each receiving at least one friction disc, wherein a first outer support in an operative state of the clutch is driven by an output shaft of an internal combustion engine and wherein the first outer support can be non-rotationally connected by the at least one friction disc thereof to a first inner support driving a first gearbox input shaft, and furthermore a second outer support can be non-rotationally connected by the at least one friction disc thereof to a second inner support driving a second gearbox input shaft, and comprising a bearing element rotatably supporting the first and the second outer supports relative to the gearbox input shafts, wherein the bearing element is in the form of a central bearing axially and radially supporting the first and the second outer support.

Description

Bearing and axial support of a double clutch on a transmission input shaft

The invention relates to a dual clutch (friction clutch), such as designed as a dry multi-plate clutch double clutch for a drive train of a motor vehicle, such as a car, truck, bus or agricultural utility vehicle, with two rotatably connected to each other and at least one friction disc receiving outer carriers, wherein a first Outer support in an operating state of the clutch from an output shaft / crankshaft of an internal combustion engine, such as a gasoline engine or a diesel engine, driven and rotatably connected with its at least one friction disc with a, a first transmission input shaft driving, first inner support is connectable, and further a second outer support with at least a friction disc rotatably connected to a second transmission input shaft driving, second inner carrier is connectable, and with a first and the second outer carrier rotatably relative to the transmission input shafts rotatably supporting Lagerele ment. The first transmission input shaft is preferably designed as a solid shaft, the second transmission input shaft preferably as a hollow shaft.

Such friction clutches are already disclosed in principle by the prior art. EP 1 850 025 B1, for example, shows a torque transmission device with two clutches for use in the drive train of a motor vehicle for torque transmission between a drive unit with an output shaft and a transmission with at least two transmission input shafts. The transmission input shafts are each rotatably connected to a friction linings having clutch disc one of the clutches, between the friction linings of a clutch disc and between the friction linings of the other clutch disc an intermediate pressure plate is arranged, the rotatably connected to the output shaft of the drive unit and in the radial direction at least one of Transmission input shafts is mounted. The friction linings of the clutch plates are arranged between the intermediate pressure plate and pressure plates, which are movable by means of an actuator in relation to the transmission input shafts, axial direction relative to the intermediate pressure plate to actuate the clutches. The attached to one of the transmission input shafts and the drive side of the intermediate plate arranged clutch disc has a radial inner part and a radial outer part, which parts are coaxial with each other.

Also from DE 10 201 1 013 998 A1 a double clutch for coupling a motor-side input shaft is known. This dual clutch has a first gearbox side Output shaft and / or a second transmission-side output shaft, which in turn has a first clutch having a relative to a first counter-plate axially movable first pressure plate for coupling a first clutch connected to the first output shaft first clutch plate having. Also, the dual clutch on a second clutch, which has a relative to a second counter-plate axially movable second pressure plate for coupling a second clutch connected to the second output shaft second clutch plate. The double clutch also has a co-rotating clutch cover connected to the first counterplate and the second counterplate and an actuating device for moving the first pressure plate and / or the second pressure plate, wherein the actuating device is provided on the input side via the clutch cover and a driveplate connected directly or indirectly to the clutch cover or Flexplate is supported on the input shaft and the output side is radially mounted on one of the output shafts and / or on a transmission housing.

DE 10 2005 025 772 A1 also discloses a torque transmission device in the drive train of a motor vehicle for torque transmission between a drive unit, in particular an internal combustion engine, with an output shaft, in particular a crankshaft, and a transmission with at least one transmission input shaft. Between the transmission input shaft and the output shaft of the drive unit, a clutch device is connected to an input part, which has a clutch housing section, in particular a clutch cover. The clutch cover limits the volume receiving the clutch device and is supported on a transmission housing section. The input part of the coupling device is mounted or supported by means of a bearing device in the axial direction on the coupling housing section. This clutch is designed as a wet-running double clutch.

In particular, with regard to the storage of the individual coupling elements, such as clutch plates / friction plates and clutch plates, so far always a high effort to operate. The individual plates and discs must be mounted axially and radially in each case via at least one separate bearing, which in turn causes a high number of components. Such high complexity in turn has the disadvantage that in particular the manufacturing and assembly costs for such double clutches are relatively high.

It is therefore an object of the present invention to overcome the disadvantages known from the prior art and a cost-effectively producible double clutch with a to the Operating conditions adapted storage of individual coupling components to provide.

This object is achieved in that the bearing element is designed as a, the first and the second outer carrier axially and radially superimposed central warehouse.

This has the effect that the number of bearings is significantly reduced, since two components (first and second outer carrier) are held both axially and radially to the transmission input shaft by a common bearing. As a result, the number of components and the assembly costs are significantly reduced. The double clutch can therefore be produced more cheaply.

Further embodiments are claimed in the subclaims and explained in more detail below.

It is advantageous if the double clutch is a dry-running double clutch, that is, a dual clutch, the friction plates are surrounded by a gas, such as air in the operating state. In such a double clutch, the central warehouse is particularly easy running ausgestaltbar because the central warehouse is sealed to form an inner lubricating space in which the bearing elements slide off or roll off to the environment. As a result, the manufacturing effort of the double clutch can be further reduced. It is also possible to design the dual clutch as a wet double clutch, in which connection a more powerful multi-plate clutch would be feasible. It is also expedient if an actuating force to be expended for actuating the double clutch during engagement and / or disengagement can be introduced via the central bearing into the first or second transmission input shaft, in an operating state of the dual clutch. As a result, the outer support is sufficiently stable supported for forwarding the actuating force.

If a connecting web element rotatably connects the first outer carrier to the second outer carrier and / or the bearing element is designed as a rolling bearing, such as an angular contact ball bearing, and / or the bearing element is rotatably held with a bearing outer ring in the first outer carrier or the second outer carrier, then the Double clutch even cheaper to produce. It is also advantageous if the first outer carrier has a toothing, in which a counter-toothing of a rotatably connected to the output shaft of the internal combustion engine / connectable flywheel, such as a dual mass flywheel, meshingly engages. This gearing fulfills the basic function of torque transmission from

Flywheel for coupling, whereby a simple assembly engine (flywheel) to the transmission (clutch) is possible. It is e.g. no screwing of clutch and flywheel during assembly engine / gearbox necessary.

If a plurality of disc-shaped friction disks are attached to the first outer carrier and / or a plurality of disc-shaped friction disks are attached to the second outer carrier, then the dual clutch can be designed particularly simply as a multi-disc clutch, wherein the torque of the internal combustion engine in the engaged states of the clutch via as many friction discs and thus as many friction surfaces can be transmitted to the respective transmission input shafts. This makes a particularly powerful dual clutch executable.

In this context, it is also advantageous to a plurality of lamella-shaped Gegenreibscheiben are attached to the first inner support, which are reibkraftschlüssig connectable to the friction disks of the first outer support, and / or on the second inner support a plurality of lamellar formed Gegenreibscheiben are attached, the frictionally engaged with the friction plates of the second outer carrier are connectable. Thus, the connected to the transmission input shaft part of the coupling is particularly easy to produce.

Are / is the first inner support and / or the second inner support multi-part, approximately in two parts, configured, the mountability of the double clutch is efficiently enabled (mounting order: 1) pressing the clutch (central bearing) on the transmission shaft; 2) mounting the circlip on the shaft; 3) inserting the hub part of the inner carrier).

It is also expedient for the first inner support to have a first hub part which is non-rotatably connected to the first transmission input shaft in the operating state and a first carrier element which can be connected non-rotatably to the first outer carrier and / or the second inner carrier has a second hub part connected non-rotatably to the second transmission input shaft in the operating state a rotatably connectable to the first outer carrier second carrier element, wherein preferably the first hub part separable / detachable from the first support member and / or the second hub part are designed separable from the second support member / is. As a result, the assembly and disassembly of the coupling is particularly easy. As a result, the preferably sleeve-shaped hub part can be mounted as a connecting element between the transmission input shaft and friction disks of the inner support rotationally fixed on the respective transmission input shaft, then then, in a subsequent operation, the remaining part of the inner support, namely the first or second support member, which is separate from the respective first or second hub part is configured, applied to the hub part and fixed thereto / is connected to this. As a result, the mounting of the locking ring during storage of the coupling is made possible on the hollow shaft.

It is also expedient if the first inner support in the operating state in the axial direction, for example by means of two retaining rings, a locking ring and a shoulder in the first transmission input shaft, or a locking ring and a bearing ring (such as a bearing inner ring) of the central warehouse, secured to the first transmission input shaft and / or the second inner support is secured in the axial direction, for example by means of two retaining rings, a locking ring and a shoulder in the second transmission input shaft, or a locking ring and a bearing ring of the central bearing on the second transmission input shaft. Alternatively, it is also possible at least one or both inner support not axially hold / secure, but to store in the axial direction slidably on the respective transmission input shaft. As a result, a displacement of the inner support in the operation of the double clutch can be avoided so as to avoid a collision of the individual inner and outer support. As a result, the utilization of the installation space can be further optimized or the axial dimensions of the double clutch can even be reduced.

It is also advantageous if for connecting the first outer support to the first

Innenträger a first, cuppfig ausgestalteter pressure pot is present, which is supported by a first plate spring on the second outer support and / or for connecting the second outer support to the second inner support a second, cuppfig ausgestalteter pressure pot is present, which is by means of a second plate spring on the second outer support is supported. As a result, the actuation force is particularly cleverly introduced into the outer supports, whereby the power flow is further optimized. Also, in this case can be dispensed with a further locking ring, whereby the number of components continues to decrease.

It is also useful if an expended during engagement and / or disengagement of the dual clutch and transmitted to the central warehouse, axial component of an actuating force from the central warehouse in the operating state of the double clutch further by means of a axial circlip, directly a bearing inner ring of the central warehouse or a locking ring and the first or second hub part in the first or second transmission input shaft can be introduced. As a result, the actuation force upon actuation of the coupling can be transmitted structurally simply directly (via central bearing inner ring) or indirectly (retaining rings and / or shoulder) to the transmission input shafts in order to obtain a closed power circuit.

In other words, a double clutch is implemented which acts as a directly operated one

Multi-disc dual clutch is executed. The storage of this multi-plate clutch takes place on a transmission input shaft via a central bearing (the central warehouse). The applied during the operation force flow is closed. For this purpose, the interconnected via the connecting web element outer carrier (also executable as outer disc carrier) are mounted together on the central warehouse on one of the solid or hollow shaft configured transmission input shafts. For the actuating force flow, a support element, preferably a plate spring is provided, which is supported in the region of the connecting web element on the outer support / the coupling. By way of this, the force flow is transmitted to the second inner support when the first clutch of the double clutch is actuated, that is to say when the first outer carrier is connected to the first inner carrier. Circlips guide the actuating force from the central warehouse to the transmission input shaft. This is still a shaft paragraph, z. B. on a bearing on the bell housing, supported and can guide over the actuation force in a central clutch release. If the central warehouse is arranged on the first transmission input shaft configured as a solid shaft or as a second transmission input shaft configured as a hollow shaft, for example pressed by means of its bearing inner ring, another bearing is provided on the transmission side, which supports the hollow shaft and thus introduces the actuating force into the transmission bell. Due to space reasons, the axial space is limited. In order to avoid contact between the plate carriers, ie the two outer carriers and the two inner carriers and / or the pressure pots, the hubs / hub parts of the inner carriers are secured to the transmission input shafts. In this case, preferably at least one hub part on the motor side or on the transmission side is also blocked directly by the inner ring of the central bearing. Further disc springs are provided, via which the pressure pots are additionally supported on the second outer disk carrier / second outer carrier, so that the actuating force is always guided in part via these disc springs on the central warehouse. The disc springs are otherwise also the bias of the actuating bearing of the central clutch release. For the assembly of the clutch, the engine-side / connecting-engine-side inner support, that is, the first or second inner support may be divided into two, so that the retaining rings are used accordingly can be. Especially with dry multi-plate clutches, the dual clutch is particularly effectively ausgestaltbar.

The invention will now be explained in more detail with reference to drawings in several embodiments. Show it:

1 is a longitudinal sectional view of a dual clutch according to the invention according to a first embodiment, wherein the longitudinal section is along a plane in which also runs the axis of rotation of the clutch and the dual clutch is shown in an operating condition in which the dual clutch to the transmission input shafts and the flywheel the output shaft of the internal combustion engine is mounted / attached,

Fig. 2 is a longitudinal sectional view of Figure 1, wherein herein the flow of force at

Actuation of the first clutch / the first coupling part is shown,

Fig. 3 is also a longitudinal sectional view according to the figure 1, but in contrast to Figure 2 now the Betätigungskraftflussverlauf is located, which takes place upon actuation of the second clutch / the second coupling part, and

Fig. 4 is a longitudinal sectional view of a dual clutch according to the invention according to a further, second embodiment, this longitudinal section is also performed in a plane in which the axis of rotation of the coupling extends, and the central warehouse is mounted in this embodiment on the designed as a solid shaft transmission input shaft, whereas this Central warehouse was held in the embodiment of Figures 1 to 3 only on the designed as a hollow shaft transmission input shaft.

The figures are merely schematic in nature and are only for the understanding of

Invention. Identical elements are provided with the same reference numerals.

In Fig. 1, a dual clutch 1 according to the invention is particularly easy to recognize, the dual clutch 1 is designed as a dry-running friction clutch (dry clutch) and, as explained in more detail below, as multi-plate clutch / multi-plate clutch. The dual clutch 1 is suitable for a drive train of a motor vehicle, such as a car, truck, bus or agricultural utility vehicle. The double clutch 1 basically has two non-rotatably connected and at least one friction disc 2, 3 receiving external support 4, 5 on. A first outer carrier 4 is in an operating state of the clutch / the dual clutch 1 of an output shaft 6 of an internal combustion engine, such as a crankshaft, driven and with its at least one friction disc 2, hereinafter also referred to as the first friction disc 2, rotatably with a, a first transmission input shaft 7 driving, first inner support 9 connectable. Also, a second outer support 5 is still present, which with its at least one friction disc 3, hereinafter also referred to as second friction disc 3, rotatably connected to a second transmission input shaft 8 driving, second inner support 10 is connectable. Also, a bearing element 1 1 is present, which rotatably supports the first and the second outer support 4, 5 relative to the transmission input shafts 7 and 8, wherein the bearing element 1 1 according to the invention as one, the first and the second outer support 4, 5 axially and radially superimposed Central warehouse 1 1 is executed.

The dual clutch 1 has an axis of rotation / coupling rotational axis 12 about which the interconnected outer supports 4, 5 and inner supports 8, 9 rotate in the respective, engaged states during operation of the motor vehicle. The first outer support 4 is configured essentially cup-shaped and has a disk-shaped bottom region 13 extending essentially in the radial direction. At a radially outer end of the bottom region 13, a cylindrical side wall region 14 extends substantially in the axial direction away from the bottom region 13.

The disk-shaped bottom region 13 of the first outer support 4, hereinafter also referred to as the first bottom region 13, has an inner hole / an inner bore in a radially inner region, which is arranged concentrically with the axis of rotation 12 in the operating state. In addition, a toothed ring 15 is fastened to the first bottom region 13 in this radially inner region. This toothed ring 15 is preferably fastened by means of a screw or a rivet, in the axial direction on the end face of the bottom portion 13. The toothed ring 15 has at its radially outer end a toothing 16 which is preferably formed as an external toothing. With this toothing 16 meshes again, a counter toothing 19 having and with a dual mass flywheel 17 rotatably connected Gegenverzahnungsring 18 for transmitting the torque of the internal combustion engine to the first outer support 4. The counter teeth 19 of the Gegenverzahnungsrings 18 is designed as internal teeth, whereas the teeth 16 of the toothed ring 15 is designed as external teeth. As a result, the dual mass flywheel is coupled in sections with the first outer support 4 rotatably coupled / connected. The dual mass flywheel 17 is further in a known manner with the designed as a crankshaft output shaft 6 rotatably connected, namely screwed to the front side of the crankshaft. As a result, a damping element is provided between the internal combustion engine output side output shaft 6 and the first outer carrier 4, which dampens in particular jerky torsional vibrations during engagement, disengagement or operation of the internal combustion engine / vehicle. The dual-mass flywheel 17 continues to be essentially constructed and acting in principle essentially like the vibration damping device from DE 10 2005 025 772. This document is intended to be considered integrated herein for this purpose.

In the first side wall portion 14, which is integrally connected to the bottom portion 13 of FIG. 1, the first friction plates 2 are rotatably attached to the first outer support 4, wherein the first friction plates 2 are at least partially displaceably mounted in the axial direction. The first friction disks 2, as can also be clearly seen in FIG. 1, are configured essentially disk-shaped, have a central inner bore / a central inner hole and are arranged next to one another in the axial direction. The first friction disks 2 are held on a radial inner side / a radial inner peripheral surface of the first side wall area 14.

In the exemplary embodiment according to FIG. 1, three first friction disks 2 are present, with two counter-friction disks 20, also referred to as first counter-friction disks 20, being placed between each two adjacent friction disks 2. These first Gegenreibscheiben 20 are in turn rotatably connected to the first inner support 9. In the embodiment according to FIG. 1, two first counter-friction disks 20 are provided which protrude in the radial direction into the intermediate space between the adjacent first friction disks 2 such that their front-side friction surfaces extend parallel and opposite to the friction surfaces of the first friction disks 2. At a radially inner end of the first Gegenreibscheiben 20 then includes a side wall portion 21 (hereinafter referred to as second side wall portion 21) of the likewise substantially cup-shaped configured first inner support 9 at , This likewise extends substantially hollow cylinder-like in the axial direction and merges into a second bottom region 22 at an end facing the first bottom region 13. Also, the second bottom portion 22 is configured substantially disc-shaped and has a central inner hole. The second side wall region 21 and the second bottom region 22, like the first bottom region 13 and the first side wall region 14, are configured integrally with one another. The first and second friction disks 2, 3 are in this embodiment each designed as steel disks / steel disks, wherein their friction surface represents a reibwertoptimier- te / roughened surface of a made of cast steel or steel plate. Alternatively, the respective first and second friction disks 2, 3 may also be designed as friction lining disks / friction lining disks, their friction surfaces being designed as a friction-optimized / roughened surface of a friction lining. The first and second Gegenreibscheiben 20, 33 are each configured in this embodiment as Reibbelagscheiben / Reibbelaglamellen, with their friction surfaces are designed as a reibwertoptimier- te / roughened surface of a friction lining. Alternatively, the respective first and second counter-friction disks 20, 33 can also be designed as steel disks / steel disks, with their friction surface representing a friction-optimized / roughened surface of a plate made of cast steel.

In a radially inner region of the second bottom region 22, a first hub part 23 by means of a fastening device 24, comprising a rivet, but alternatively also a screw rotatably connected. The first hub part 23 has an outer toothing. The bottom part 22 a meshing with the external teeth internal teeth. About these teeth, the torque from the bottom part 22 of the first inner support 9 is transferred to the inner hub part 23. A retaining ring 25 which furthermore belongs to the fastening device 24 ensures the axial position of the two components relative to one another. In the operating state of the double clutch 1 shown in FIG. 1, two plates extending in the radial direction inwards toward the first hub part 23 are fastened to the bottom area 22 by the rivet. The first sheet is fastened on a side of the bottom area 22 facing the dual mass flywheel 17 in the operating state, the second sheet is on a side of the floor area facing away from the dual mass flywheel 17 in the operating state

22 attached. The securing ring 25 is positioned such that it is clamped with a radially outer side between the first sheet metal and the bottom region 22 and bears against the first hub part 23 with a radially inner side and thereby secures the first hub part 23 in the axial direction to the bottom region 22. The second plate in turn overlaps the first hub part

23 in the radial direction and thus secures the first hub part before an axial displacement to the side facing away from the dual mass flywheel 17 side. As a result, a releasable connection for easier assembly and disassembly between the first hub part 23 and the first support member 38 is implemented.

The first hub part 23 is furthermore embodied in a substantially sleeve-shaped manner and with a peripheral side facing the rotation axis 12 on an outer side of the first gear mechanism. output shaft 7, which is designed here as a solid shaft, pressed on / attached. In the axial direction, the first hub part 23 and thus also the first inner support 9 by means of two retaining rings 25 on the first transmission input shaft 7, namely held in a form-fitting manner. In this case, a first retaining ring 25 is positively held in the outer peripheral surface of the first transmission input shaft 7, in an axial region of the first transmission input shaft 7, which adjoins the internal combustion engine in the operating state side facing the first hub portion 23, held a second locking ring 25 is on one of the first hub portion 23, which is remote from the end of the internal combustion engine, held in the outer peripheral surface of the first transmission input shaft 7 positively. As a result, the axial movement of the first inner support 9 during operation of the double clutch 1 is avoided by abutment of the first hub part 23 on one of the retaining rings 25.

The first outer support 4 is furthermore connected in a rotationally fixed manner to the second outer support 5 by means of a connecting web element 26, which likewise has a substantially disc-shaped design. For this purpose, the connecting web element 26 has a plurality of holes at a radial outer area, protrude / protrude into the axial projections of the first side wall portion 14, so that these projections abut circumferentially on the inner sides of the holes and the first outer support 4 rotatably connected to the connecting web element 26. The connecting web element 26, which is configured in the form of a disk, has an inner hole in a radially inner region. In the area of the inner circumferential surface of this inner hole, the connecting web element 26 again has sections which engage in a form-fitting manner in the second outer carrier 5, so that the second outer carrier 5 is in turn connected in a rotationally fixed manner to the connecting web element 26.

The second outer carrier 5 is likewise designed cup-shaped and has a bottom region 27, referred to below as the third bottom region 28, and a third side wall region 27 connected integrally to this third bottom region 28. The third bottom region 27 is in turn substantially disk-shaped and has a central inner bore. This third floor area 28 adjoins a, the output shaft 6 in the operating state, facing the end of the third side wall portion 27 at. The third bottom region 28 has on its radially inner side / on its inner circumferential surface a, substantially in the axial direction extending retaining ring 29, which retaining ring 29 is in turn integrally connected to the third bottom portion 28. The retaining ring 29 extends substantially parallel to the axis of rotation 12 and is configured to receive a bearing outer ring 30 of the central warehouse 1 1. The central warehouse 1 1 is a roller bearing 32, which is designed as angular contact ball bearings. The bearing outer ring 30 is preferably pressed into the retaining ring 29 and thus held in a non-positive manner in this. Furthermore, it is also conceivable to attach the retaining ring 29 in a form-fitting manner to the outer bearing ring 30 additionally or alternatively. A bearing inner ring 31 of the central bearing 1 1 is again in the operating state of the double clutch 1 non-positively and / or positively held on the second transmission input shaft 8, which is configured as a hollow shaft. The bearing inner ring 31 is pressed onto the second transmission input shaft 8 and / or secured axially with a securing ring 25. Between the bearing outer ring 30 and the bearing inner ring 31 a plurality of rolling elements 32 are arranged distributed along the circumference. These rolling elements 32 are designed as balls.

Again axially within the second outer support 5, the second inner support 10 is arranged. For Reibkraftschlüssigen connecting the second outer support 5 with the second inner support 10, the second friction plates 3 and second Gegenreibscheiben 33 are provided. The second friction plates 3 are arranged on the second outer carrier 5, wherein they are held on a radial inner side of the third side wall portion 27 and extend radially inwardly from this third side wall portion 27. The second friction disks 3 are configured substantially like the first friction disks 2 and are arranged relative to the second counter friction disks 33, which second counter friction disks 33 are in turn non-rotatably connected to the second inner support 10. The second Gegenreibscheiben 33 extend in a lamellar manner, in axial spaces between two adjacent second friction plates. 3

Also, the second inner support 10 in turn has a side wall portion 34, hereinafter referred to as the fourth side edge portion 34, on. Also, it has a fourth bottom portion 35, which in turn is configured substantially disc-shaped. The fourth side edge portion 34 and the fourth bottom portion 35 also constitute a pot and are integrally connected with each other. On an inner side of the fourth bottom region 35, a separate hub part 36, referred to below as the second hub part 36, is connected, this second hub part 36 being connected in a rotationally fixed manner to the fourth bottom region 35.

In the first inner support 9, the composite of the second floor area 22 and the second side wall area 21 is referred to as the first support element 38 carrying the first friction disks 2. In the case of the second inner support 10, the composite of fourth floor area 35 and fourth side wall portion 34 as a second, the second friction plates 3 supporting support member 37 denotes.

Also, the second hub portion 36 is configured substantially sleeve-shaped and pushed onto an outer peripheral surface of the second transmission input shaft 8. The second hub part 36 is positively and / or non-positively fixed on the second transmission input shaft 8 for rotationally fixed connection. At a first axial end region, which region adjoins the second hub part 36 on a side facing away from the internal combustion engine, the second hub part 36 is secured directly via a first securing ring 25, which securing ring is secured against displacement on the second transmission input shaft. On one of the output shaft 6 facing side of the second hub portion 36, the second hub portion 36 is located on the bearing inner ring 31 of the central warehouse 1 1 at. The central warehouse 1 1, as already described above, is secured in position in the axial direction via a further securing ring 25, the surfaces of an outer peripheral surface of the second transmission input shaft 8 is positively held and rests against the bearing inner ring 31. As a result, the second hub part 36 and the second inner support 10 is axially secured.

Thus, in the dual clutch 1, a first clutch / a first coupling part 39 is provided, which is formed by the first outer support 4 and the first inner support 9, and a second clutch / a second coupling part 40, by the second outer support 5 and by the second Inner carrier 10 is formed, which coupling parts 31 and 40 are alternately rotatably connected to the respective first or second transmission input shaft 7, 8.

For rotationally fixed connection of the first inner support 9 with the first outer support 4, a first actuating device 41 is provided, which is configured substantially as a central clutch release. The first actuating device 41 has a first pressure pot 43, which is coupled via a first actuating bearing 44, namely a release bearing, with a first axially adjustable release piston 45. The first pressure pot 43 is moved axially for engagement or disengagement in order to press the first friction disks 2 against the first counter-friction disks 20 for frictional connection. For this purpose, the second actuator 42 for frictional connection of the second outer support 5 with the second inner support 10 has a second actuating piston 44 connected to a second actuating bearing 44. This actuating bearing 44 in turn acts axially displaceable on a second pressure pot 46 a. If now one of the two coupling parts 39, 40 be concluded, the respective first or second actuator 41, 42 is actuated and the friction plates 2, 3 with the respective Gegenreibscheiben 20, 33 frictionally engaged. In this case, an axial end face of the first pressure pot 43 presses on actuation of the first coupling part 39 on one of the first friction plates 2 and moves it axially in the direction of the other friction plates 2, so that the respective first Gegenreibscheiben 20 are clamped between the first friction plates 2 and thus rotatably get connected. Also, the second actuator 42 functions in this sense and connects upon actuation of the release piston 45 of the second actuator 42, the second coupling part 40, whereby the second Gegenreibscheiben 33 are clamped between the second friction plates 3. These actuators 41, 42 are also already known in principle from DE 10 2005 025 772 A1 and thus are considered integrated herein.

Furthermore, the first pressure pot 43 of the first actuating device 41 is supported on the second outer carrier 5 via a first plate spring 47. Also, the second pressure pot 46 is supported on the second outer support 5 via a plate spring 48, hereinafter referred to as the second plate spring 48. As a result, for connecting the first outer support 4 to the first inner support 9, the first pot-shaped pressure pot 43 is provided, which is supported on the second outer support 5 by means of the first disc spring 47. For connecting the second outer support 5 with the second inner support 10, a second pot-shaped pressure pot 46 is provided, which is supported by means of a second disc spring 48 on the second outer support 5.

As can also be clearly seen in FIG. 1, a shaft shoulder 49 is formed on the second transmission input shaft 8, that is to say a projection extending in the radial direction, the shaft shoulder 49 being supported on a further bearing 50 / rolling bearing and securing this bearing 50 axially , The bearing 50 preferably receives the bell housing in stock.

As can further be seen in FIG. 2, when the first actuating device 41 is actuated, the force flow of the actuating force extends in such a way that it extends from the first actuating piston 45 through the first actuating bearing 44 and the first pressure cup 43. From the first pressure pot 43, a part of the actuating force is transferred to the first plate spring 47, the other part of the actuating force moves via one of the first friction plates 2 directly into the other friction plates 2 and thus into the first outer carrier 4, in turn, by a locking ring 25, the actuating force on the connecting web element 26 to the second outer support 5 passes. This second outer carrier 5 is connected by the axial and radial support through the central warehouse 1 1 with the first transmission input shaft 7, so that the actuating force is passed through this central warehouse 1 1 to the first transmission input shaft 7 and forms a closed power flow circuit.

As can further be seen in FIG. 3, upon actuation of the second actuating device 42, the force flow of the actuating force is such that it extends from the second actuating piston 45 through the second actuating bearing 44 and the second pressure pot 46. From the second pressure pot 46, a part of the actuating force is transferred to the second plate spring 48, the other part of the actuating force moves through one of the second friction plates 3 directly into the other friction plates 3 and into the second outer support 5. This second outer support 5 is through the axial and radial support through the central warehouse 1 1 connected to the first transmission input shaft 7, so that the actuating force is passed through this central warehouse 1 1 to the first transmission input shaft 7 and forms a closed power flow circuit.

Furthermore, a further embodiment is shown in FIG. 4, which in principle is designed like the first embodiment. The second embodiment differs only in principle from the first that the second outer support 5, instead of the second transmission input shaft 8, on the first transmission input shaft 7, namely the solid shaft is held positively and / or non-positively. The other parts of the dual clutch 1 are preferably designed as the elements of the double clutch 1 shown in Figures 1 to 3.

It should also be noted that each of the two inner disk carrier (first inner carrier 9 and second inner carrier 10) are also integrally ausgestaltetbar, in which case the first support member 38 is integrally formed with the first hub portion 23 and / or the second support member 37 with the second hub portion 36th is integral. The respective circlip 25 for transmitting the axial actuating forces would then be used after pressing the coupling 1 on the respective transmission input shaft 7, 8. It is also possible at least not axially secure the second inner support 10, but to store axially displaceable by omitting the axial securing / locking rings on the second inner support 10. Also, it is also possible to store the first inner support 9 also axially displaceable. In other words, the axial and radial coupling forces via a central ball bearing (central warehouse 1 1) are supported. The ball bearing is arranged on one of the two transmission input shafts 7, 8. The ball bearing is seated in the outer disk carrier / the second outer carrier 5. The outer disk carrier is connected to the connecting web / connecting web element 26 and the connecting web to the outer disk carrier / the first outer carrier 4 via a tooth system. By means of a toothing 16, the torque is transmitted from the flywheel 17 to the outer disk carrier of the clutch 1. If the storage takes place on the hollow shaft, the inner disk carrier / first inner carrier 9 is made in two parts. After assembly of the clutch / second clutch part 40 into the transmission, the circlip 25 is mounted on the transmission input shaft 8. Subsequently, the inner part of the disk carrier is used. The position of the hubs 23, 36 of the inner disk carrier / the first inner carrier 9 is ensured by means of securing rings 25 on the transmission input shafts 7, 8 or paragraphs on the transmission input shafts 7, 8. This ensures that the inner disk carrier does not collide with the outer disk carriers 4, 5 (both rotate at differential speed to the inner disk carrier). The positioning of the hub / hub parts 23, 36 takes place with play or without play / pretensioned. The play-related design is less expensive in terms of costs and installation. The position of the hubs 23, 36 of the disk carrier is ensured by means of retaining rings on the transmission input shafts or shoulders on the transmission input shafts 7, 8. Respectively. This ensures that the inner disk carrier does not collide with the outer disk carrier or the pressure pot (both rotate at differential speed to the inner disk carrier K2). The positioning of the hub takes place with play or without play / preloaded. The play-related design is less expensive in terms of costs and installation.

The central warehouse 1 1 is also optimized in particular with regard to the axial bearing and designed as angular contact ball bearings. Needle bearings, such as those used for axial bearing in wet-running clutches can be avoided because they are not suitable for use in dry double clutches, in particular due to the centrifugal forces occurring during operation, which would distribute the bearing grease unevenly in the rolling bearing.

It is further noted that the lamellae, or friction disks 2, 3 respectively

Have teeth and are arranged with these axially movable in the outer supports 4.5 in the complementary gears. The torque is then transmitted from the outer supports 4, 5 to the friction disks 2, 3 and further to the respective counter-friction disks 33, 34 or lamellae via these toothings. The coupling therefore works here corresponding to how a wet multi-plate clutch without oil, the outer support 4.5 here the outer disk carriers and in turn the friction plates 2,3 are inserted.

Reference numerals double clutch

First friction disc

Second friction disc

First external carrier

Second outer carrier

output shaft

First transmission input shaft

Second transmission input shaft

First interior carrier

Second inner carrier

Bearing element / central warehouse

Axis of rotation / coupling axis of rotation

First floor area

First sidewall area

toothed ring

gearing

Dual Mass Flywheel

Counter teething ring

counter teeth

First antreibscheibe

Second sidewall area

Second floor area

First hub part

fastening device

Retaining rings

Connecting web element

Third sidewall area

Third floor area

retaining ring

Bearing outer ring

Bearing inner ring

rolling elements

Second counter friction discs

Fourth sidewall area Fourth floor area

Second hub part

Second carrier element

First carrier element

First coupling part

Second coupling part

First actuating device

Second actuating device

First pressure pot

operation seat

release piston

Second pressure pot

First disc spring

Second plate spring

shaft shoulder

camp

Claims

claims

1 . Double clutch (1) for a drive train of a motor vehicle, with two rotatably connected and at least one friction disc (2, 3) receiving outer supports (4, 5), wherein a first outer support (4) in an operating state of the clutch (1) of a Output shaft (6) of an internal combustion engine driven and with its at least one friction disc (2) rotatably connected to a, a first transmission input shaft (7) driving, first inner support (9) is connectable, and further a second outer support (5) with its at least one friction disc ( 3) rotatably connected to a second transmission input shaft (8) driving, second inner support (10) is connectable, and with a first and the second outer support (4, 5) relative to the transmission input shafts (7, 8) rotatably supporting bearing element (1 1 ), characterized in that the bearing element (1 1) as a, the first and the second outer support (4, 5) axially and radially overlapping Zentralla ger (1 1) is executed.

2. Double clutch (1) according to claim 1, characterized in that the double clutch (1) is a dry-running double clutch (1) and / or one for the actuation of the double clutch (1) during engagement and / or disengagement expended actuating force on the Central warehouse (1) in the first or second transmission input shaft (7, 8), in an operating state of the dual clutch (1), can be introduced.

3. Double clutch (1) according to one of claims 1 and 2, characterized in that a connecting web element (26) rotatably connects the first outer support (4) with the second outer support (5) and / or the bearing element (1 1) as a rolling bearing, about an angular contact ball bearing, is executed and / or the bearing element (1 1) with a bearing outer ring (30) rotatably in the first outer support (4) or the second outer support (5) is held.

4. dual clutch (1) at least according to the preamble of claim 1, characterized in that the first outer carrier (4) has a toothing (16) into which a counter toothing (19) of the output shaft (6) of the internal combustion engine rotatably connectable flywheel , about a dual-mass flywheel (17), meshing engages.

5. Double clutch (1) according to one of claims 1 to 4, characterized in that on the first outer support (4) a plurality of lamellar friction disks (2) are attached and / or on the second outer support (5) a plurality of lamellar friction disks (3) are mounted.

6. Double clutch (1) according to claim 5, characterized in that on the first inner support (9) a plurality of lamellar formed Gegenreibscheiben (20) are mounted, which frictionally engaged with the friction plates (2) of the first outer support (4) are connectable, and / or on the second inner support (10) a plurality of lamellar formed Gegenreibscheiben (33) are mounted, which are reibkraftschlüssig with the friction discs (3) of the second outer support (5) connectable.

7. Double clutch (1) according to one of claims 1 to 6, characterized in that the first inner support (9) and / or the second inner support (10) in several parts, approximately in two parts, are configured / is.

8. dual clutch (1) according to claim 7, characterized in that the first inner support (9) in the operating state non-rotatably connected to the first transmission input shaft (7), the first hub part (23) and with the first outer support (4) rotatably connectable first Carrier element (38) and / or the second inner support (10) in the operating state rotationally fixed to the second transmission input shaft (8) connected, second hub part (36) and with the first outer support (4) rotatably connectable second support member (37), wherein preferably, the first hub part (23) is divisible from the first carrier element (38) and / or the second hub part (23) is divisible from the second carrier element (38).

9. dual clutch (1) according to one of claims 1 to 8, characterized in that the first inner support (9) in the operating state in the axial direction, such as by means of two retaining rings (25), a retaining ring (25) and a shoulder in the first transmission input shaft (7), or a retaining ring and a bearing ring of the central bearing (1 1), on the first transmission input shaft (7) is secured and / or the second inner support (10) in the axial direction, such as by means of two retaining rings (25), a retaining ring ( 25) and a shoulder in the second transmission input shaft (8), or a locking ring (25) and a bearing ring (30, 31) of the central bearing (1 1) is secured to the second transmission input shaft (8).

10. Double clutch (1) according to one of claims 1 to 9, characterized in that a on input and / or disengagement of the double clutch (1) expended and on the central warehouse (1 1) transmitted, axial component of an actuating force from the central warehouse ( 1 1) from in the operating state of the double clutch (1) further by means of an a- xialen circlip (25), directly to a bearing inner ring (31) of the central bearing (1 1) or a locking ring (25) and the first or second hub part (23, 36) in the first or second transmission input shaft (7, 8) can be introduced.