DE102011014778A1 - Concentric dual clutch device for arrangement in drive train of motor vehicle between drive unit and gear box, comprises clutch arrangement, which is assigned primary transmission input shaft for torque transmission - Google Patents

Abstract

The concentric dual clutch device (2) comprises a clutch arrangement (28), particularly multiple disk clutch arrangement, which is assigned a primary transmission input shaft (10) for torque transmission between a drive unit (4) and the primary transmission input shaft. A pressure chamber housing (96,98) is provided, which is formed partially, particularly completely in a torque-proof manner.

Description

The present invention relates to a concentric dual clutch device for arrangement in a drive train of a motor vehicle between a drive unit and a transmission having a first transmission input shaft associated first clutch assembly for selectively transmitting torque between the drive unit and the first transmission input shaft and a second transmission input shaft associated second clutch assembly for selectively transmitting torque between the drive unit and the second transmission input shaft, wherein the first clutch assembly by means of at least one hydraulically driven first actuating piston, which is associated with a first pressure chamber, which is bounded by a first pressure chamber housing and the first actuating piston, and the second clutch assembly by means of at least one hydraulically driven second Actuating piston can be actuated, which is associated with a second pressure chamber through a second pressure chamber housing and the second actuating piston is limited.

The DE 100 34 730 A1 describes a concentric dual clutch device having a first clutch assembly and a second clutch assembly arranged radially nested, the first clutch assembly of the optional torque transmission between a drive unit and a first transmission input shaft, while the second clutch assembly of the optional torque transmission between the drive unit and a second transmission input shaft is used , The two clutch assemblies can each be actuated by means of a hydraulically driven actuating piston. For this purpose, a pressure chamber is assigned to each of the two actuating pistons, which is delimited by a pressure chamber housing and the respective actuating piston. The pressure chamber housing is formed in each case by a portion of an inner, rotating hub and a portion of the rotatably connected to this hub plate carrier of the concentric double clutch device. In addition, a compensation chamber for the Fliehölausgleich is provided on the side facing away from the pressure chamber of each actuating piston. The aforementioned hub of the concentric dual clutch device is substantially tubular, wherein the tubular hub is supported in the radial direction on a fixed support tube. To pressurize the pressure chambers with pressure oil and thus to drive the actuating piston, rotary feedthroughs are provided between the hub and the support tube, which are separated by means of appropriate rotary feedthrough seals.

The known concentric double clutch device has proven itself, but has some disadvantages. On the one hand, the amount of pressure of the hydraulic medium for driving the actuating piston is limited due to leakage, so that the use of a high pressure accumulator to increase the efficiency of the concentric dual clutch device is not or only partially possible. On the other hand, the known concentric double clutch device has a complex and space-consuming construction.

It is therefore an object of the present invention to provide a concentric double clutch device, on the one hand ensures a particularly high pressure of the hydraulic medium, possibly the use of a high-pressure accumulator, and a leak-free operation and on the other hand has a simple and space-saving construction, moreover, a simple Assembly of the concentric dual clutch device should be possible.

This object is achieved by the features specified in claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

The dual clutch device according to the invention for arrangement in a drive train of a motor vehicle between a drive unit and a transmission has a first clutch input shaft associated first clutch assembly and a second transmission input shaft associated second clutch assembly. The two clutch assemblies are arranged radially nested, so that it is a concentric dual clutch device in the double clutch device according to the invention. While the first clutch assembly is for selectively transmitting torque between the drive unit and the first transmission input shaft, the second clutch assembly is for selectively transmitting torque between the drive unit and the second transmission input shaft. It is preferred if a transmission input shaft is designed as a hollow shaft, within which the other transmission input shaft extends, so that it can also be spoken of a radial nesting of the transmission input shafts. In turn, the two clutch arrangements are preferably in each case a multi-disc clutch arrangement, particularly preferably a wet-running multi-disc clutch arrangement. The first clutch arrangement can be actuated by means of at least one hydraulically drivable first actuating piston, which is preferably an annular actuating piston or an annular piston. For this purpose, the first actuating piston is a assigned first pressure chamber, which is preferably limited exclusively by a first pressure chamber housing and the first actuating piston. It is preferred if the first pressure chamber is limited exclusively by the first pressure chamber housing and the first actuating piston. The second clutch arrangement, however, can be actuated by means of a hydraulically driven second actuating piston. The second actuating piston is associated with a second pressure chamber for this purpose, which is delimited by a second pressure chamber housing and the second actuating piston, wherein it is also preferred here, when the second pressure chamber is limited exclusively by the second pressure chamber housing and the second actuating piston. The actuating piston can therefore be driven independently by acting on the associated pressure chamber with pressure oil or other hydraulic medium to actuate the respective clutch assembly. The pressure chamber housing, that is, at least the first or second pressure chamber housing, preferably both the first and the second pressure chamber housing, is at least partially, preferably entirely, fixed or / and rotationally fixed. This can for example be achieved in that the pressure chamber housing is arranged on a fixed and / or rotationally fixed coupling housing.

An at least partially, preferably completely, fixedly and / or rotationally fixed trained pressure chamber housing has the advantage that no rotary feedthrough is required to pressurize the pressure chambers with hydraulic oil or other hydraulic medium and thus to drive the actuating piston. By dispensing with a rotary feedthrough with the associated rotary feedthrough seals, which - as in the DE 100 34 730 A1 - Guarantee an approximately leak-free operation only at a low pressure of the pressure oil or hydraulic medium, in the concentric dual clutch device according to the invention, a particularly high operating pressure of the pressure oil or hydraulic medium can be selected. Thus, in particular the use of a high-pressure accumulator in the pressure oil supply path is possible without a leakage-free operation of the concentric double clutch device is at risk. This ultimately achieves an increase in the efficiency of the overall system. By eliminating the necessary for a rotary feedthrough rotary joints seals the drag torque of the clutch assemblies is reduced beyond and improves their hysteresis. Furthermore, the structure of the concentric dual clutch device is substantially simplified, which can equally lead to a reduction of the required installation space. This simplification of the structure is due on the one hand to the elimination of the rotary unions with the associated rotary feedthrough seals. On the other hand, the simplified structure is achieved in that no equalization space for the Fliehölausgleich is required by the at least partially, preferably entirely, fixedly and / or rotationally fixed pressure chamber housing. In particular, this eliminates additional measures or components for the production of said compensation spaces for the Fliehölausgleich.

Based on the above-mentioned advantages of the concentric dual clutch device according to the invention, the concentric dual clutch device according to the invention in a preferred embodiment of the same on the actuating piston associated compensation chambers for the Fliehölausgleich.

In a further preferred embodiment of the concentric dual clutch device according to the invention, the concentric dual clutch device has no rotary feedthrough in the pressure oil supply path for the pressure chambers associated with the actuating piston to allow a particularly high pressure of the pressure oil or hydraulic medium and optionally the use of a high-pressure accumulator within the pressure oil supply path.

According to a further preferred embodiment of the concentric dual clutch device according to the invention, a high-pressure accumulator is provided within the pressure oil supply paths for the pressure chambers in order to increase the efficiency of the overall system.

In a particularly preferred embodiment of the concentric dual clutch device according to the invention, the actuating pistons, the associated pressure chambers and the associated pressure chamber housing are arranged on the slave side of the hydraulic system. Thus, in the pressure chamber housing delimiting the respective pressure chamber, it is also possible to speak of a slave cylinder.

In an advantageous embodiment of the concentric dual clutch device according to the invention, at least one opening for supplying pressurized oil or another hydraulic medium into the pressure chamber of the pressure chamber housing is provided. This opening for supplying the pressure oil is preferably provided in the fixed and / or rotationally fixed pressure chamber housing or fixed and / or rotationally fixed part of the pressure chamber housing to dispense with a rotary feedthrough, the rotary feedthrough seals would make a limitation of the operating pressure of the pressure oil necessary ,

In order not to have to arrange the respective actuating piston directly in the region of the associated coupling arrangement and rather to achieve a relatively free and space-saving arrangement of the respective actuating piston, in a further advantageous embodiment of the concentric double clutch device according to the invention each a force transmission element is provided, via which the respective clutch assembly the associated actuating piston can be actuated. In this way, the actuating piston may be arranged, for example, radially inside or outside of the associated coupling arrangement to effect by corresponding nesting a shortening of the axial length of the concentric double clutch device, wherein the respective force transmission element can cause a bridging of the distance between the actuating piston and the associated clutch assembly.

In a particularly advantageous embodiment of the concentric dual clutch device according to the invention, the actuating piston is decoupled from the previously mentioned force transmission element. In this way, any rotation or rotation of the power transmission element is not transmitted to the actuating piston, so that the actuating piston is not or only slightly rotated relative to the at least partially stationary and / or rotationally fixed pressure chamber housing. This ensures two things. On the one hand, due to the rotational drive decoupled actuating piston, a flow of fluid pressure within the pressure chamber is avoided, albeit a smaller one, so that even less expensive measures for centrifugal oil compensation are eliminated. On the other hand, only a simple sealing of the respective pressure chamber by using simple seals between the actuating piston on the one hand and the pressure chamber housing on the other hand necessary, which are also suitable to withstand a particularly high pressure of the pressure oil or hydraulic medium.

In order to achieve a particularly secure rotational drive decoupling between actuating piston and power transmission element in the embodiment described above, the rotational drive decoupling between the actuating piston and the force transmission element in a further advantageous embodiment of the concentric dual clutch device according to the invention by means of a engagement bearing between the actuating piston and the power transmission element, wherein the engagement bearing preferably as Rolling is formed. By the engagement bearing and its optionally internal rolling elements friction between the optionally rotating power transmission element and the rotational drive decoupled actuating piston is largely excluded, so that a transmission of the rotational movement of the power transmission element is prevented on the actuating piston. In this embodiment, it is further preferred if a replaceable spacer is provided in the direction of actuation of the respective actuating piston between the actuating piston and the engagement bearing, so that the distance between the actuating piston and engagement bearing in the actuating direction is flexibly adjustable and tolerance compensation is feasible.

In a further particularly preferred embodiment of the concentric dual clutch device according to the invention, the actuating piston is non-rotatably connected to the pressure chamber housing. In this way, all the walls of the respective pressure chamber can be formed rotationally fixed, so that not even the lowest Fliehöldruck can arise within the pressure chamber and countermeasures for Fliehölausgleich completely eliminated. In addition, a simple sealing of the pressure chamber by means of a seal between the actuating piston on the one hand and the pressure chamber housing on the other hand can be achieved by the non-rotatably connected to the pressure chamber housing actuating piston, which ensures a leak-free operation even at a particularly high pressure of the pressure oil or hydraulic medium. In this embodiment, it is also particularly preferred if the rotationally fixed connection of the actuating piston takes place in a form-fitting manner with the pressure chamber housing. Thus, for example, a protruding projection or a recess may be provided on the actuating piston, wherein the protruding projection may engage in a recess on the pressure chamber housing or a protruding approach to the pressure chamber housing in the recess on the actuating piston to effect the rotationally fixed connection.

In principle, the previously mentioned force transmission element could be lever-shaped in order to amplify the actuating force of the actuating piston by means of a lever transmission, so that the force ultimately acting on the clutch arrangement is increased. Alternatively or additionally, the force transmission element could also be elastic, so that it can exert a restoring force on the actuating piston. To realize these two features, the power transmission element could be formed for example by a plate spring. In a further particularly advantageous embodiment of the concentric dual clutch device according to the invention, however, the force transmission element is designed such that the actuating force of the actuating piston in the ratio 1: 1 can be transmitted to the clutch assembly. An increase in the the respective clutch assembly acting force by a corresponding leverage between the actuating piston and the clutch assembly is not required in this embodiment, especially since the concentric dual clutch device already allows a particularly high pressure of the pressure oil or hydraulic medium for the reasons mentioned above. Said transmission of the actuating force of the actuating piston in the ratio 1: 1 to the clutch assembly could in principle be achieved in this embodiment by means of a lever-type power transmission element, but it is preferred in this embodiment, when the actuating force is transmitted to the clutch assembly without leverage, ie Power transmission element is preferably not lever-shaped. This has the advantage that the force transmission element is less expensive and less prone to failure, while on the other hand, a smaller overall length in the direction of the actuating force, preferably in the axial direction, can be achieved. In this embodiment, it is also particularly preferred if the force transmission element is integrally formed and / or directly cooperates with the engagement bearing and / or the clutch assembly to achieve a particularly simple construction of the concentric dual clutch device. It is also preferred in this embodiment, when the one-piece power transmission element is substantially inelastic and thus has a lower elasticity than a plate spring or a similar spring means, while the restoring force is applied to return the actuating piston of a separate spring means.

In principle, the two actuating pistons could be arranged radially nested. However, this would have the consequence that the Betätigungsaktuatorik for the two clutch assemblies in the region of the actuating piston would have a large extent in the radial outward direction, which is due, inter alia, that the inner actuating piston would then have a particularly large extent in the radial direction, to have an effective area that is the same size as the effective area of the outer actuating piston. In order to reduce the expansion of the Betätigungsaktuatorik in the region of the actuating piston in the radial direction to the outside, the two actuating pistons are arranged axially staggered in a further particularly preferred embodiment of the concentric dual clutch device according to the invention. In this way, for example, additional space can be created radially outside of the actuating piston, within which preferably the pump drive member described in more detail later, the rotary driving member of a rotary driving device or another component of the concentric double clutch device described in more detail is arranged. In this embodiment, it is further preferred if the active surfaces of the actuating pistons facing the respective pressure chamber overlap in the axial direction, whereby it can also be said that the projections of the active surfaces of the actuating pistons overlap at least partially in the axial direction. As already explained at the outset, this results in a particularly compact arrangement of the two actuating pistons relative to the radial directions.

In principle, each of the two clutch assemblies of the concentric dual clutch device according to the invention may be assigned a plurality of isolated actuating pistons, which are arranged distributed in the circumferential direction. However, on the one hand to simplify the production of the concentric double clutch device and on the other hand to ensure a uniform transmission of the actuating force to the respective clutch assembly, the actuating piston are formed in a further advantageous embodiment of the concentric dual clutch device according to the invention as an annular piston, so that only an annular first actuating piston and an annular second actuating piston is required. In this embodiment, it is further preferred if the actuating piston having an open in the axial direction U-shaped cross-section, in which the aforementioned engagement bearing between the actuating piston on the one hand and the power transmission element is used on the other. Thanks to the U-shaped cross-section of the actuating piston, on the one hand, reliable guidance of the actuating piston along the wall of the pressure chamber formed by the associated pressure chamber housing is ensured and, on the other hand, a small axial length of the combination of actuating piston and engagement bearing is ensured. Furthermore, it is particularly preferred in this embodiment, when the engagement bearing is supported in only one of the two opposite radial directions on the actuating piston. Thus, the engagement bearing can be supported, for example, either on the inner leg of the U-shaped cross section in the radial direction inwardly or on the outer leg of the U-shaped cross-section in the radial direction to the outside. As a result, the insertion of the engagement bearing in the U-shaped cross-section of the actuating piston is simplified without jeopardizing a secure centering of the engagement bearing relative to the trained as an annular piston actuating piston.

In a further advantageous embodiment of the concentric invention Double clutch device is provided a fixed and / or rotationally fixed clutch housing, in which the dual clutch device is arranged. The clutch housing may be formed for example by a part of the transmission housing and / or a part of the drive or motor housing.

In order to create an at least partially, preferably completely, fixedly and / or rotationally trained pressure chamber housing for the respective actuating piston, at least one of the pressure chamber housing in a further preferred embodiment of the concentric dual clutch device according to the invention fixed or / and rotationally fixed to the clutch housing or integrally with the clutch housing educated. Although two alternatives to the arrangement of the pressure chamber housing are described on the clutch housing, so the first alternative, in which the pressure chamber housing is fixed or / and rotatably mounted on the clutch housing, still preferred, especially in the first alternative, the pressure chamber housing and the clutch housing initially separately can be manufactured and processed to fix the pressure chamber housing only then fixed or / and rotationally fixed to the coupling housing. As a result, a particularly accurate and equally simple production of the pressure chamber housing with the associated pressure chamber allows, which can not be achieved to an extent in a one-piece design of the pressure chamber housing to the coupling housing. Moreover, it is preferred in the former alternative, when the pressure chamber housing is removably or interchangeably attached to the clutch housing, especially since this on the one hand in the context of manufacturing a rapid adaptation of the pressure chamber housing to the respective concentric double clutch device and on the other hand, if necessary, a quick repair of the concentric dual clutch device possible is.

In a further advantageous embodiment of the concentric double clutch device according to the invention runs within the wall of the clutch housing at least one pressure oil passage for supplying pressure oil or hydraulic medium in at least one of the pressure chambers. In this case, said pressure oil channel preferably opens into the previously mentioned opening for supplying pressure oil into the pressure chamber of the pressure chamber housing.

According to a further advantageous embodiment of the concentric double clutch device according to the invention, the aforementioned clutch housing has a first housing section and a second housing section opposite in the axial direction. The first housing section is preferably a housing or gear housing bell with a housing opening, while the second housing section is preferably formed by a housing cover for closing the housing opening. In this case, the second housing section in the form of the housing cover is particularly preferably removably attached to the first housing section in the form of the housing or gearbox housing bell to allow quick access to the concentric dual clutch device in repair or maintenance case.

In a further preferred embodiment of the concentric dual clutch device according to the invention, both pressure chamber housings are provided either on the first or on the opposite second housing section. Thus, for example, the two pressure chamber housings could be provided together on the aforementioned first housing section in order to enable a gear-like arrangement and thus a short guidance of the pressure oil or hydraulic medium. On the other hand, however, the two pressure chamber housing could also be provided together on the opposite second housing portion, so that the Betätigungsaktuatorik is particularly easy to reach by removing the housing cover. Here, however, the former embodiment is preferred with a gear-near arrangement of the pressure chamber housing to the first housing portion.

In principle, both pressure chamber housings could each be mounted directly on the coupling housing. However, this would make the structure more expensive and difficult assembly, especially if an axial staggering of the actuating piston is to be achieved, which has been previously described with reference to an embodiment of the invention. For this reason, the first pressure chamber housing is mounted in a further preferred embodiment of the concentric dual clutch device according to the invention to the pressure chamber housing, while the second pressure chamber housing is attached to the first pressure chamber housing. It can therefore be said that the second pressure chamber housing is attached indirectly via the first pressure chamber housing to the coupling housing. Alternatively, the second pressure chamber housing could also be formed integrally with the first pressure chamber housing, but this alternative is only preferred if a radial nesting of the actuating piston is desired. Otherwise, the former alternative should be selected, in which the first separate second pressure chamber housing is mounted in the context of assembly to the first pressure chamber housing, especially as this is the production of Pressure chamber housing with axial staggering of the actuating piston is much easier.

Moreover, in the embodiment described above, it is preferable if both pressure chamber housings are each formed in one piece. This is to be understood that the essential for limiting the pressure chamber sections of the pressure chamber housing integrally formed and not just composed of several initially separate items. In this way, not only the assembly is simplified, but it is also created a very dense pressure chamber. In this case, it is preferred if the respective pressure chamber is delimited exclusively by the one-piece pressure chamber housing and the associated actuating piston, wherein this does not preclude a seal between the pressure chamber housing and the actuating piston. In this embodiment, it is further particularly preferred if the second pressure chamber housing, which is attached indirectly via the first pressure chamber housing to the coupling housing, has an open in the axial direction U-shaped cross section, within which the second pressure chamber and the second pressure chamber additionally limiting second Actuating piston is arranged. By the latter embodiment, a particularly easy to produce second pressure chamber housing is created, which may also have a particularly low weight. In order to achieve a relatively small axial length of the concentric double clutch device despite an optionally existing axial staggering of the actuating piston, the actuating piston and / or the associated engagement bearing are arranged radially inwardly of the clutch assemblies, preferably at least one actuating piston and / or the associated engagement bearing with respect Coupling arrangements arranged radially nested, particularly preferably independent of the axial position of the displaceable actuating piston.

In a further advantageous embodiment of the concentric dual clutch device according to the invention, at least one spring device for resetting the actuating piston is assigned to the actuating piston, of which at least one is arranged radially nested with respect to the clutch assemblies. In this embodiment, it is further particularly preferred if the spring device is formed separately from the aforementioned force transmission element and thus does not serve to transmit the actuating force of the actuating piston to the associated clutch assembly. Furthermore, it is preferred in this embodiment, when the spring means of a plurality of arranged between the inner or outer disk spring elements, preferably corrugated rings, is formed, which thus serve in addition to the provision of the piston and the spacing of the slats.

In principle, the double clutch device, preferably its input side, can be supported indirectly or directly on one of the transmission input shafts in the axial or / and radial direction. However, in order to achieve a particularly tilt-proof arrangement of the concentric double clutch device, the concentric dual clutch device, preferably the input side, in a further preferred embodiment of the invention alternatively or additionally in the axial and / or radial direction on the clutch housing, preferably on a fixed support tube to the clutch housing , supported or supportable. In this case, the support tube must not necessarily be connected directly to the coupling housing, but also an indirect attachment of the support tube to the coupling housing is possible, as will be explained later. The support tube is in this embodiment preferably fixedly connected to that housing portion of the clutch housing, which is arranged on the transmission side, wherein the transmission input shafts may be arranged radially nested to the fixed support tube, d. h., The transmission input shafts then ran through the fixed support tube.

In a further particularly preferred embodiment of the concentric dual clutch device according to the invention, which represents a development of the embodiment described above, the support of the dual clutch device, preferably the input side, takes place in the axial or / and radial direction on the clutch housing or the fixed support tube by means of a rolling bearing, in which it is preferably a ball bearing.

In a further advantageous embodiment of the concentric dual clutch device according to the invention, the actuating piston on the same direction of actuation. The direction of actuation here means the direction in which the actuating pistons are displaced and exert their actuating force in order to actuate the respective clutch arrangement, the actuating direction preferably being one of the axial directions of the concentric double clutch device. In this case, the actuating forces in the actuating direction, preferably via the rolling bearing, particularly preferably via the support tube, are supported on the coupling housing.

In principle, the abovementioned support tube, on which the concentric double clutch device, preferably its input side, could be supported in the axial or / and radial direction is to be provided directly on the clutch housing or one of said housing portions of the clutch housing. In a further advantageous embodiment of the concentric dual clutch device according to the invention, however, the support tube is attached to one of the pressure chamber housing or formed by a portion of the pressure chamber housing. By the support tube is thus arranged indirectly via the pressure chamber housing to the clutch housing, a particularly compact and lightweight construction of the concentric dual clutch device is achieved. In the former alternative, in which the support tube is attached to one of the pressure chamber housing, the support tube can first be manufactured separately from the pressure chamber housing to then attach the support tube to the pressure chamber housing. This first alternative is preferred over the second alternative, in which the support tube is formed by a portion of the pressure chamber housing and thus formed integrally therewith, preferably, as this is a modular design of the concentric dual clutch device is possible in which the pressure chamber housing is associated with a module while the support tube may be associated with other components of the dual clutch device another module. As a result, in any case, the assembly of the concentric dual clutch device is simplified.

In order to achieve a particularly useful modular design of the concentric dual clutch device, which simplifies the installation of the concentric dual clutch device, the support tube is alternatively or additionally to the embodiment described above in a further advantageous embodiment of the invention releasably attached to the clutch housing or the pressure chamber housing. In order to simplify the mounting of the support tube to the clutch housing or the pressure chamber housing thereby, it is further preferred if the support tube is screwed to the clutch housing or the pressure chamber housing. To be particularly advantageous has been found in this context, when the support tube has an external or internal thread, via which the support tube with the coupling housing or the pressure chamber housing is screwed, which has a corresponding internal or external thread.

In principle, the rolling bearing already described above could be fixed to the support tube in both axial directions with the aid of corresponding securing or fixing elements, such as securing rings. However, in order to further simplify the structure of the concentric double clutch device, the rolling bearing is supported in one axial direction, preferably directly, on one of the pressure chamber housing in a further preferred embodiment of the invention. In this way, no additional securing or fixing element is required in this axial direction, which would increase the assembly effort. Rather, one of the already existing pressure chamber housing is used for fixing the rolling bearing in this axial direction. Thus, for example, the previously described second pressure chamber housing having a U-shaped cross-section could have an extended inner leg on which the rolling bearing can be supported on the end side in the axial direction mentioned. In order to support the rolling bearing in the other axial direction meaningful and without much effort, the rolling bearing is also supported in this embodiment, preferably in the other axial direction of the support tube, wherein the support in the other axial direction preferably takes place on a flange portion of the support tube, which is particularly preferably formed integrally with the support tube. Thus, in this embodiment, the rolling bearing can be supported in both axial directions solely by attaching the support tube to the clutch housing or pressure chamber housing and thus fixed. As a result, the assembly of the concentric dual clutch device is further simplified. Also in this embodiment, it is preferred if the roller bearing is supported directly on the support tube or the flange portion of the support tube.

In order to further simplify the assembly of the concentric double clutch device and in particular to enable a modular assembly, in a further preferred embodiment of the concentric dual clutch device according to the invention on the support tube, preferably on the aforementioned flange portion of the support tube, a mounting portion for releasably securing an insertion tool, while in the input and / or output side of the dual clutch device mounting windows are formed, which are aligned with each other in the axial direction and with the mounting portion such that the insertion tool can be brought in the axial direction through the mounting window to the mounting portion. For example, the mounting windows may be provided, for example, in the drive disk of the input side and on the other hand in the disk carriers of the output side in order to allow easy insertion of an insertion tool through the mounting windows to the mounting portion of the support tube. The mounting portion is preferably formed in this embodiment such that the insertion tool attached thereto forms a rotary driving connection with the support tube, so that the support tube can be screwed by turning the insertion tool to the clutch housing or the pressure chamber housing.

In a further particularly preferred embodiment of the concentric dual clutch device according to the invention, a rotationally fixed, preferably immediately, provided on the input side of the dual clutch device rotational drive means is provided, which can be releasably brought into rotational drive connection with a pump drive member for an oil pump. In this case, the rotational drive means is preferably non-rotatably attached to a plate carrier of the input side of the dual clutch device. The input side of the dual clutch device according to the invention does not include the aforementioned force transmission elements, even if they rotate at the same speed as the input side of the dual clutch device. Thus, this embodiment excludes in particular a variant in which the rotational drive means is rotationally fixedly attached to one of the force transmission elements. While an undesirable axial displacement of the rotary driving device is connected together with the power transmission element in a rotationally fixed attachment of the rotary driving device on one of the power transmission elements, the rotationally fixed on the input side of the dual clutch device rotational drive means can be set together with the input side of the dual clutch device in the axial direction already described above be so that also an axial displacement of the rotary driving device is omitted during operation.

In order to achieve a particularly compact construction of the rotary driving device, the rotary driving device in a further preferred embodiment of the concentric dual clutch device according to the invention on axial fingers extending in the axial direction through windows in at least one of the power transmission elements to the clutch assemblies facing away from the side of the power transmission element. In this way, a particularly short connection of the input side of the dual clutch device via the rotary driving device is achieved with the pump drive member. In this connection, it should be noted that said windows may also be formed by the central recess in the power transmission element, but it is preferred that the windows are notches located radially further outwardly than the central recess in the power transmission element , Especially in the radially outer region more space can be provided for the arrangement of the pump drive member, as is the case with a radially inner region of the case.

In a further particularly advantageous embodiment of the concentric dual clutch device according to the invention, which represents a development of the embodiment described above, the rotary driving device on a rotary driving member on the axial fingers on the side facing away from the clutch assemblies of the power transmission element. The rotary driving member is preferably a toothed wheel or a traction mechanism gear which can be brought into rotary driving connection with the pump drive member in a known manner. The rotational driving member can be pressed example, subsequently caulked on the axial fingers of the rotary driving device or caulked with these. In this embodiment, it is further preferred if the rotary driving member is arranged radially nested with respect to at least one of the actuating piston.

In a further preferred embodiment of the concentric dual clutch device according to the invention, at least one of the force transmission elements has actuating fingers extending in the axial direction which extend through recesses in the input side of the dual clutch device in order to reach the respective clutch arrangement, preferably the associated disk set. The part forming the input side is preferably a plate carrier or the radial section of a plate carrier. The actuating fingers are latchingly inserted or inserted into the recesses, so that the force transmission element is arranged relatively securely after insertion on the input side and can be installed or installed particularly easily with this module. In this embodiment, it is further preferable that the actuating fingers are inserted or insertable into the recesses in an insertion direction, which is preferably one of the axial directions, in such a manner that the force transmission element is in the opposite direction to the insertion direction at the input side, optionally the plate carrier, supported or supportable. The aforementioned embodiments can be effected by any latching connection between the actuating fingers and the recesses. Particularly advantageous, an embodiment has been found in which in at least one of the recesses a, preferably designed as a plastic element, locking element is used, which cooperates latching with the respective actuating finger.

In a further particularly preferred embodiment of the concentric dual clutch device according to the invention, at least one of the actuating piston has a seal for sealing the pressure chamber, which is fastened under fixing in the axial direction on the end face of the actuating piston facing the pressure chamber. The attachment to the front has in Contrary to an attachment to the radially outwardly or inwardly facing sides of the actuating piston, inter alia the advantage that the actuating piston is easy to produce and can be easily connected to the seal. In this embodiment, preferably at least one recess is provided in the end face into which the seal engages positively in order to effect the axial fixing of the seal on the actuating piston. In this embodiment, it is further particularly preferred if the seal does not extend beyond the radially inwardly and outwardly facing side surfaces of the actuating piston. In this way, the production of the seal is simplified, which must be tuned primarily to the piston guide of the pressure chamber housing, but not in addition to the dimensions of the actuating piston.

In a further advantageous embodiment of the concentric dual clutch device according to the invention, at least one of the actuating pistons is latchingly connected to the engagement bearing. In this way, the engagement bearing can be quickly and safely connected to the actuating piston to install the actuating piston together with the associated engagement bearing and possibly other parts simply as a module or to install. In this embodiment, it is preferred if at least one elastic locking element is provided on the actuating piston, which may be formed for example by a latching tongue. It has been found to be particularly advantageous if the locking element is formed integrally with the, preferably made of plastic, actuating piston.

The invention is explained in more detail below by means of exemplary embodiments with reference to the accompanying drawings. Show it:

1 a side view of a first embodiment of the concentric dual clutch device according to the invention in a sectional view,

2 a side view of a second embodiment of the concentric dual clutch device according to the invention in a sectional view,

3 to 7 the double clutch device of 2 when mounting the same on a gearbox.

1 shows a first embodiment of the concentric dual clutch device according to the invention 2 within a drive train of a motor vehicle between a drive unit 4 and a gearbox 6 , From the drive unit 4 , which is, for example, an internal combustion engine, is only the output hub 8th shown, wherein it is at the output hub 8th Preferably, the output hub of a torsional vibration damper, which is between the drive unit 4 on the one hand and the concentric double clutch device 2 on the other hand is arranged. From the transmission 6 , which is preferably a dual-clutch transmission, in the figure, only a first transmission input shaft 10 and a second transmission input shaft 12 shown. The concentric double clutch device 2 is about a rotation axis 14 rotatable, extending in the opposite axial directions 16 . 18 extends, wherein in the figure also the opposite radial directions 20 . 22 and the opposite circumferential directions 24 . 26 indicated by corresponding arrows. The two transmission input shafts 10 . 12 extend along the axis of rotation 14 in the axial directions 16 . 18 wherein the second transmission input shaft 12 is formed as a hollow shaft through which coaxially the first transmission input shaft 10 extends. The two transmission input shafts 10 . 12 are thus in the radial direction 20 . 22 nested so that the first transmission input shaft 10 as an internal transmission input shaft and the second transmission input shaft 12 can be referred to as external transmission input shaft. The inner first transmission input shaft 10 can be designed as a solid shaft, but it is also possible and possibly desirable if the first transmission input shaft 10 is also designed as a hollow shaft, as indicated in the figure by a dashed line.

The concentric double clutch device 2 has one of the first transmission input shaft 10 associated first clutch assembly 28 and one of the second transmission input shaft 12 associated second clutch assembly 30 on. Since it is the dual clutch device 2 around a concentric double clutch device 2 are the two clutch arrangements 28 . 30 in the radial direction 20 . 22 arranged nested. Thus, the first clutch assembly 28 Also referred to as external clutch assembly, while the second clutch assembly 30 Also may be referred to as an internal clutch assembly. In both coupling arrangements 28 . 30 are wet-running multi-plate clutch assemblies, so that the clutch assemblies 28 . 30 are each essentially composed of a disk set of inner and outer disks. The first clutch arrangement 28 serves the optional torque transmission between the drive unit 4 and the first transmission input shaft 10 of the transmission 6 while the second clutch assembly 30 the optional torque transmission between the drive unit 4 and the second transmission input shaft 12 of the transmission 6 serves.

The concentric double clutch device 2 also has a radially inner clutch input hub 32 on that with the output hub 8th the drive unit 4 is in rotary driving connection, said rotational driving connection is preferably formed positively and releasably. The clutch input hub 32 is in the axial direction 16 formed closed, ie, this has none in the axial direction 16 through opening. At the clutch input hub 32 is a driver disk 34 rotatably attached, extending from the clutch input hub 32 essentially in the radial direction 20 extends to the outside. In the radial direction 20 to the outside is the drive plate 34 rotatably with an outer disk carrier 36 connected. This is a positive rotational drive connection, wherein the drive plate 34 via a circlip 38 in the axial direction 16 on the outer disk carrier 36 is supportable. In addition, the drive disc 34 arched in their radially outer region in such a way that they are equally one in the axial direction 18 protruding stop 40 forms, to which the first clutch assembly 28 in the axial direction 16 is supportable.

The outer disc carrier 36 essentially consists of a first disk support section 42 , which is tubular and with the drive plate 34 is in rotational driving connection, a support section 44 which extends from the one in the axial direction 18 facing end of the first slat support section 42 essentially in the radial direction 22 extends inwardly and integrally with the first slat support portion 42 is formed, and a second disk support portion 46 together, the latter rotatably with the support portion 44 connected, tubular and in the radial direction 22 within the first slat support section 42 and is arranged radially nested with this. The support section 44 is in a first radial section 48 extending from the first sipe supporting portion 42 in the radial direction 22 extends inwardly and at its in the axial direction 16 facing side of the second slat support section 46 is arranged, one on the first radial section 48 following tubular section 50 extending from the radial direction 22 inwardly facing end of the first radial section 48 in the axial direction 16 extends and thus based on the clutch assemblies 28 . 30 is arranged radially nested, and one in the axial direction 16 facing end of the tubular section 50 subsequent second radial section 52 divided, extending from the tubular portion 50 again in the radial direction 22 extends inwards, around there a support hub 54 to receive an indirect support of the concentric double clutch device 2 effected at the clutch housing described in more detail later, with the support will be discussed later in more detail. At the second sipe carrying section 46 of the outer disk carrier 36 is also another circlip 56 provided over which the second clutch assembly 30 in the axial direction 16 at the second sipe carrying portion 46 is supportable.

The first clutch assembly 28 is also an inner disk carrier 58 assigned, which consists essentially of a tubular lamella carrying section 60 and one in the axial direction 16 to the tubular lamella carrying section 60 subsequent support section 62 composed, wherein the support section 62 in the radial direction 22 extends inwards to there via a first Kupplungsausgangsnabe 64 in rotational engagement with the first transmission input shaft 10 to stand. The second clutch assembly 30 is again a second inner disc carrier 66 associated, which consists of a tubular lamella carrying section 68 and a to the slat support section 68 in the axial direction 16 subsequent support section 70 composed, wherein the support section 70 in the radial direction 22 extends inward to there via a second clutch output hub 72 with the second transmission input shaft 12 to be in rotary driving connection. The outer disks of the clutch assemblies 28 respectively. 30 are non-rotatably, but axially displaceable with the first and second disk support portion 42 . 46 of the outer disk carrier 36 connected while the inner disks of the clutch assemblies 28 respectively. 30 rotatably, but axially displaceable with the slat support portion 60 respectively. 68 the inner disc carrier 58 respectively. 66 are connected.

As can also be seen from the figure, is in the axial direction 16 . 18 between the drive plate 34 and the support section 62 , between the support section 62 and the support section 70 and between the support section 70 and the flange portion of a support tube, which will be described in detail later, each have a thrust bearing 74 provided in the form of a needle bearing to the said components in the axial direction 16 . 18 to support each other or to separate from each other. Here are the mentioned thrust bearing 74 in the axial direction 16 . 18 arranged in alignment with each other. In addition, the clutch input hub 32 in the radial direction 22 via a radial bearing 76 at the radial direction 20 outwardly facing side of the first clutch output hub 64 supported, wherein the first clutch output hub 64 for this purpose in the axial direction 16 in a recess in the cup-shaped clutch input hub 32 extends. About the radial bearing 76 and the first clutch output hub 64 Thus, initially an indirect support of the input hub takes place 32 in the radial direction 22 at the first transmission input shaft 10 ,

The concentric double clutch device 2 is in a wet room 78 arranged by a fixed and non-rotatable coupling housing 80 is surrounded. In this case, the coupling housing 80 a first housing portion 82 who has the wet room 78 in the axial direction 18 as well as in the radial direction 20 limited and in the present example as a transmission housing bell with one in the axial direction 16 facing housing opening is formed, and a second housing portion 84 on, which is designed as a housing cover, the housing opening of the first housing portion 82 closes and thus the wet room 78 in the axial direction 16 limited. In the area of the rotation axis 14 has the first housing section 82 a central shaft passage opening 86 on, through which the transmission input shafts 10 . 12 of the transmission 6 in the axial direction 16 to the concentric dual clutch device 2 in the wet room 78 extend. Also the second housing section 84 has a central shaft passage opening 88 on, through which the clutch input hub 32 in the axial direction 16 to the drive unit 4 to and from the wet room 78 extends, with a seal 90 between the inside of the shaft passage opening 88 in the second housing section 84 and the radially outwardly facing side of the clutch input hub 32 is arranged to the wet room 78 in the axial direction 16 seal.

The first clutch assembly 28 is a first Betätigungsaktuatorik 92 assigned during the second clutch assembly 30 a second Betätigungsaktuatorik 94 which will be explained in more detail below. So is a first pressure chamber housing 96 the first Betätigungsaktuatorik 92 fixed and rotationally fixed to the housing section 82 of the coupling housing 80 attached while a second pressure chamber housing 98 fixed and rotationally fixed to the first pressure chamber housing 96 is attached, so that the second pressure chamber housing 98 at least indirectly via the first pressure chamber housing 96 fixed and rotationally fixed to the first housing portion 82 is appropriate. Thus, both are pressure chamber housing 96 . 98 on the same housing section 82 of the coupling housing 80 attached or provided. The first pressure chamber housing 96 was initially separate from the first housing section 82 manufactured while the second pressure chamber housing 98 initially separate from the first pressure chamber housing 96 was manufactured to then the first pressure chamber housing 96 on the housing section 82 and the second pressure chamber housing 98 on the first pressure chamber housing 96 to install in the manner mentioned. The first pressure chamber housing 96 is detachable to the first housing section 82 fastened while the second pressure chamber housing 98 detachable on the first pressure chamber housing 96 is attached. Each of the two pressure chamber housings 96 . 98 is designed in one piece by itself. Alternatively, the first pressure chamber housing could 96 and the first housing section 82 and / or the second pressure chamber housing 98 and the first pressure chamber housing 96 also be integrally formed with each other, however, the illustrated embodiment is preferred in terms of manufacturing and any necessary repair or maintenance. In any case, by the attachment of the pressure chamber housing 96 . 98 on the housing section 82 of the coupling housing 80 the pressure chamber housing 96 . 98 as well as the clutch housing 80 fixed and rotatable trained.

Both pressure chamber housing 96 . 98 are annular, so that they are the axis of rotation 14 in the circumferential direction 24 . 26 completely enclose. The first pressure chamber housing 96 is mentally in a radially outer pressure chamber housing section 100 and a radially inner pressure chamber housing section 102 subdivided, said pressure chamber housing sections 100 . 102 are integrally formed with each other. The second pressure chamber housing 98 is at the in the axial direction 16 further protruding inner pressure chamber housing section 102 of the first pressure chamber housing 96 attached and has one in the axial direction 16 open U-shaped cross-section on. In this case, the U-shaped cross-section has a radially inner leg 104 and a radially outer leg 106 on that over a bottom leg 108 are integrally connected to each other. In the outer pressure chamber housing section 100 of the first pressure chamber housing 96 a circumferential recess is provided in the axial direction 16 is open and in a hydraulically driven first actuating piston 110 creating a first pressure space 112 is used. The first pressure room 112 is thus exclusively by the integrally formed first pressure chamber housing 96 and the first actuating piston 110 limited. The first pressure room 112 is also annular, further comprising circumferential seals 114 between the first actuating piston 110 and the wall of the first pressure chamber 112 are provided. In the also in the axial direction 16 open circumferential recess within the second pressure chamber housing 98 with the U-shaped cross section is a hydraulically driven second actuating piston 116 used such that a second pressure chamber 118 arises, the only by the integrally formed second pressure chamber housing 98 and the second actuating piston 116 is limited, in which case on the hydraulically driven second actuating piston 116 circumferential seals 114 are provided to the second pressure chamber 118 secure seal.

Both actuating pistons 110 . 116 are in the axial direction 16 . 18 within the associated pressure chamber housing 96 respectively. 98 slidably disposed, but are the actuating piston 110 . 116 each rotatably with the associated pressure chamber housing 96 respectively. 98 connected. Thus, even with the actuating piston 110 . 116 are spoken of non-rotatable actuating piston, not about the axis of rotation 14 in the circumferential direction 24 . 26 can be rotated. The rotationally fixed connection of the actuating piston 110 . 116 with the associated pressure chamber housing 96 respectively. 98 This is preferably achieved by positive locking, wherein the representation of the positive connection in the figure was omitted for reasons of clarity. In addition, both have trained as an annular piston actuating piston 110 . 116 one in the axial direction 16 open U-shaped cross-section on. Thus, the respective U-shaped cross-section each have a radially inner leg 120 , a radially outer leg 122 and one the two thighs 120 and 122 connecting radial leg 124 on, the latter being the respective pressure chamber 112 . 118 in the axial direction 18 facing active surface of the actuating piston 110 . 116 formed. This will be a particularly lightweight actuator piston 110 . 116 achieved, moreover, particularly safe within the respective pressure chamber housing 96 . 98 is guided. Furthermore, this can be the axial length of Betätigungsaktuatorik 92 respectively. 94 be reduced, as will be explained later.

As can be seen from the figure, the second pressure chamber housing 98 such on the inner pressure chamber housing section 102 of the first pressure chamber housing 96 attached that second pressure chamber housing 98 in the radial direction 20 to the outside over the inner pressure chamber housing section 102 of the first pressure chamber housing 96 protrudes. This has the consequence that the two actuating pistons 110 . 116 in the axial direction 16 . 18 are arranged staggered, especially since the inner pressure chamber housing section 102 of the first pressure chamber housing 96 to which the second pressure chamber housing 98 is fixed, further in the axial direction 16 protrudes than that in the outer pressure chamber housing section 100 of the first pressure chamber housing 96 the case is. The two actuating pistons 110 . 116 are therefore not arranged nested radially to each other, but axially staggered, which are the pressure chambers 112 respectively. 118 facing active surfaces of the actuating piston 110 . 116 in the axial direction 16 . 18 overlap. By this axial staggering in conjunction with the overlap of the active surfaces of the actuating piston 110 . 116 becomes an actuation actuator 92 . 94 created in the area of the pressure chamber housing 96 . 98 or the actuating piston 110 . 116 a particularly small extent in the radial direction 20 has to the outside, so that in this way additional space for other components can be created, as will be explained later.

To the first pressure room 112 be supplied with pressure oil or other hydraulic medium is within the wall of the first housing portion 82 of the coupling housing 80 at least one first pressure oil channel 126 intended. The first pressure chamber housing 96 is in this case on the first housing section 82 attached that the first pressure oil channel 126 in an opening 128 in the fixed and rotationally fixed first pressure chamber housing 96 opens and the first pressure chamber 112 over the first pressure oil channel 126 and the opening 128 can be supplied with pressure oil. In addition, within the wall of the first housing section 82 of the coupling housing 80 at least one second pressure oil channel 130 formed, that of the first pressure oil passage 126 is separated and into a channel 132 within the inner pressure chamber housing section 102 of the first pressure chamber housing 96 empties. The channel 132 opens in the axial direction 16 turn into an opening 134 in the second pressure chamber housing 98 so that the second pressure chamber 118 over the second pressure oil channel 130 , the channel 132 and the opening 134 can be acted upon with pressure oil.

The two clutch arrangements 28 . 30 are not directly through the associated actuating piston 110 respectively. 116 actuated. It is rather a first power transmission element 136 and a second power transmission element 138 intended. The two power transmission elements 136 and 138 are designed such that they are the distance between the actuating piston 110 . 116 and the associated clutch assembly 28 respectively. 30 in the radial direction 20 . 22 bridged. This is necessary insofar as that both the actuating piston 110 . 116 as well as the associated engagement bearing, which will be described later, based on the clutch assembly 28 . 30 are arranged radially further inside. In this way, the available space is used optimally and an increase in the axial length of the concentric dual clutch device 2 can be avoided. In this case, the second actuating piston 116 and the associated engagement bearing in the radial direction 20 . 22 with respect to the coupling arrangement 28 . 30 arranged radially nested, said radial nesting preferably independent of the respective axial position of the second actuating piston 116 or the associated engagement bearing is given.

The power transmission elements 136 . 138 extend from the actuating piston 110 . 116 essentially in the radial direction 20 to the outside, then over end, in the axial direction 16 extending actuating fingers 140 to the associated clutch assembly 28 respectively. 30 heranzureichen. In this case, the actuating fingers extend 140 in the axial direction 16 through corresponding recesses 142 in the first radial section 48 of the outer disk carrier 36 in that, in addition, a rotational drive connection between the power transmission elements 136 . 138 and the outer disc carrier 36 is effected. Both power transmission elements 136 . 138 have a central recess through which inter alia the transmission input shafts 10 . 12 can extend.

To prevent a torque - and even if only due to friction - of the power transmission element 136 . 138 on the associated actuating piston 110 respectively. 116 is transmitted, are the actuating piston 110 . 116 and the associated power transmission element 136 respectively. 138 with the help of a return bearing 144 respectively. 146 between the actuating piston 110 . 116 and the power transmission element 136 respectively. 138 rotate therewith decoupled. Thanks to this rotational drive decoupling could basically on the rotationally fixed arrangement of the actuating piston 110 . 116 at the associated pressure chamber housing 96 respectively. 98 be omitted, the rotationally fixed arrangement of the actuating piston 110 . 116 at the associated pressure chamber housing 96 respectively. 98 However, it is preferred, in particular as a result of a rotation of the actuating piston 110 . 116 in the circumferential direction 24 . 26 relative to the associated pressure chamber housing 96 respectively. 98 Especially, can be effectively prevented, so that in the area of circumferential seals 114 a particularly high density of the respective pressure chamber 112 . 118 can be achieved.

As can be seen from the figure, the engagement bearing 144 . 146 such on the associated actuating piston 110 respectively. 116 arranged at least partially in the U-shaped cross-section of the respective actuating piston 110 . 116 in the axial direction 18 are used or immerse. This is not only a particularly lightweight actuator piston 110 . 116 , but also a short axial length of the concentric double clutch device 2 achieved. Also are the engagement bearings 144 . 146 in only one of the two opposite radial directions 20 . 22 on the associated actuating piston 110 respectively. 116 supported, whereby on the one hand a secure centering of the engagement bearing 144 . 146 relative to the associated actuating piston 110 respectively. 116 is effected and on the other hand, a simple insertion of the engagement bearing 144 . 146 in the associated actuating piston 110 respectively. 116 is possible. In the present example, the support of the engagement bearing takes place 144 . 146 only in the radial direction 20 inwardly on the inner leg 120 of the respective actuating piston 110 respectively. 116 while no support in the radial direction 20 outwards on the outer leg 122 of the respective actuating piston 110 or 116, wherein the support could also be reversed.

From the figure it can also be seen that in the axial direction 16 . 18 between the actuating piston 110 . 116 and the associated engagement bearing 144 respectively. 146 an annular disk-shaped spacer 148 is provided, over which the engagement bearing 144 . 146 in the axial direction 18 on the radial leg 124 the associated actuating piston 110 respectively. 116 is supported. The spacers 148 are interchangeable in the U-shaped cross-section of the actuating piston 110 respectively. 116 introduced, so that a simple tolerance compensation by selecting corresponding thicker or thinner spacers 148 can be achieved.

Thanks to the fixed and non-rotating pressure chamber housing 96 . 98 and the non-rotating actuating piston 110 . 116 , moreover, from the associated power transmission element 136 respectively. 138 are decoupled, the pressure chambers 112 respectively. 118 Under particularly high pressure with pressurized oil are applied, especially the inventive concentric dual clutch device 2 dispensed with a rotary feedthrough, the rotary feedthrough seals are only partially suitable to withstand high pressure of the pressure oil. For this reason, in the illustrated concentric dual clutch device 2 Furthermore, at least one high-pressure accumulator integrated into the pressure oil supply paths, said high-pressure accumulators are not shown in the figure. In addition, the fixed and rotationally fixed pressure chamber housing 96 . 98 and the non-rotatable and rotationally decoupled actuating piston 110 . 116 that in the pressure chambers 112 respectively. 118 no Fliehöldruck arises, so that the concentric double clutch device 2 waived corresponding compensation spaces for Fliehölausgleich entirely, the more complex structure of the concentric dual clutch device 2 would require.

Among other things, due to the higher pressure within the pressure oil supply paths can also be a lever-like design of the power transmission elements 136 . 138 , which in principle would also be possible here, be waived. So are the power transmission elements 136 . 138 such that they act in the direction of actuation Forces of the actuating piston 110 . 116 without lever ratio in the ratio 1: 1 to the associated clutch assembly 28 respectively. 30 transfer. The actuation direction of both actuating pistons 110 . 116 corresponds to the axial direction 16 , By dispensing with lever-type force transmission elements, a reduction of the axial length of the concentric double clutch device 2 and a reduced design effort can be achieved. Also, the power transmission elements 136 . 138 designed to simplify the construction in one piece. To further simplify the structure, the power transmission elements act 136 . 138 directly with the associated engagement bearing 144 respectively. 146 and the associated clutch assembly 28 respectively. 30 together.

The return of the two actuating pistons 110 . 116 in their starting positions shown in the figure does not take place via an elastic force transmission element 136 . 138 Rather, the stiff and almost inelastic trained power transmission element 136 respectively. 138 in each case at least one spring device 150 respectively. 152 assigned, which causes the provision. So is the spring device 150 on the one hand in the axial direction 16 at the first radial section 48 of the outer disk carrier 36 and on the other hand in the axial direction 18 on the first power transmission element 136 supported, wherein the spring device 150 is formed in the present example as a plate spring, which allows a particularly short axial length. The spring device 152 is, on the other hand, in the axial direction 16 at the in the axial direction 16 recessed second radial section 52 of the outer disk carrier 36 indirectly or directly and on the other hand in the axial direction 18 on the second power transmission element 138 supported, wherein the spring device 152 is formed in the illustrated embodiment as a helical spring, which only a small extent in the radial direction 20 . 22 having. Also, the spring device 152 , the second pick-up warehouse 146 and the second actuating piston 116 with the clutch assemblies 28 . 30 arranged radially nested.

As previously indicated, the clutch input hub is 32 in the radial direction 22 over the radial bearing 76 on the first clutch output hub 64 and thus on the first transmission input shaft 10 supported. However, this is not enough, even in the axial direction 16 acting actuating forces of the actuating piston 110 . 116 meaningful support. For this reason, the input side of the concentric double clutch device 2 further in the axial direction 16 and in the radial direction 22 indirectly to the coupling housing 80 supported or supportable. The input side described herein includes the clutch input hub 32 , the driving disc 34 and the outer disc carrier 36 but not the power transmission elements 136 . 138 although in rotational engagement with the input side of the concentric dual clutch device 2 stand as explained earlier.

To such a support of the concentric double clutch device 2 and thus the actuating forces of the actuating piston 110 . 116 to effect, is also a fixed support tube 154 provided, which indirectly on the first housing portion 82 of the coupling housing 80 attached and supported. The support tube 154 is in one piece from a tubular section 156 which is in the axial direction 16 . 18 extends and through which the transmission input shafts 10 . 12 run, and one in the axial direction 16 to the tubular portion 156 subsequent flange section 158 together, which is essentially in the radial direction 20 extends to the outside. The flange section 158 further comprises a mounting portion 160 for releasably securing an insertion tool (not shown), wherein the mounting portion 160 at the radial direction 20 outwardly facing end of the flange portion 158 is trained. At the mounting section 160 it may be, for example, a section with fastening recesses and / or projections, which can be brought into rotational drive connection in a form-fitting manner with said setting tool. The mounting section 160 is in the axial direction 16 . 18 aligned with mounting windows 162 in the drive plate 34 , the support section 62 of the first inner disk carrier 58 and the support section 70 of the second inner disk carrier 66 arranged. In other words, the mounting windows 162 in the input and output side of the concentric double clutch device 2 educated. The mounting windows are aligned 162 with each other and with the mounting section 160 such that the insertion tool in the axial direction 18 through the mounting windows 162 to the mounting section 160 can be introduced. In the axial direction 16 . 18 is between the support section 70 of the second inner disk carrier 66 and the flange portion 158 of the support tube 154 the previously mentioned thrust bearing 74 arranged in the form of a needle bearing, which is the support section 70 in the axial direction 18 at the flange portion 158 supports or said components in the axial direction 16 . 18 separates each other.

On his the flange section 158 opposite side is the tubular portion 156 of the support tube 154 detachable on the inside Pressure chamber housing section 102 of the first pressure chamber housing 96 appropriate. For this purpose, the tubular portion 156 an external thread (no reference numeral), which is in an internal thread on the inner pressure chamber housing section 102 of the first pressure chamber housing 96 is screwed. Basically, the support tube could 154 also directly with the first housing section 82 of the coupling housing 80 However, it is preferred if the support tube 154 indirectly via the first pressure chamber housing 96 on the first housing section 82 of the coupling housing 80 is attached, especially as a result, inter alia, a much simpler structure and a lower weight of the concentric dual clutch device 2 can be achieved. Also, the support tube could 154 alternatively from a portion of the first pressure chamber housing 96 formed and thus integral with the first pressure chamber housing 96 be formed, due to the additional flange portion 158 However, the embodiment shown is preferred, especially since this not only the production of the individual parts, but also the installation of the concentric dual clutch device 2 is simplified.

In order now to the input side of the concentric dual clutch device described above 2 in the axial direction 16 and in the radial direction 22 on the clutch housing 80 support, is in the radial direction 20 . 22 between the support hub 54 of the outer disk carrier 36 and the radially outwardly facing side of the tubular portion 156 of the support tube 154 a rolling bearing 164 provided, which is formed in the present example as a ball bearing. The support hub 54 is designed such that these in the axial direction 16 on the outer ring of the rolling bearing 164 is supportable. The inner ring of the rolling bearing 164 is, however, in the axial direction 16 , preferably immediately, at the tubular portion 156 facing side of the flange portion 158 of the support tube 154 supported. Moreover, the inner ring of the rolling bearing 164 in the axial direction 18 on one of the two pressure chamber housings 96 or 98 supported. In the present example, the inner ring of the rolling bearing 164 in the axial direction 18 on the inner leg 104 the second pressure chamber housing 98 supported, wherein the inner leg 104 for this purpose in the axial direction 16 over the outer leg 106 the second pressure chamber housing 98 protrudes. By supporting the rolling bearing 164 in the axial direction 18 on one of the pressure chamber housing 96 or 98 eliminates the need for an additional locking ring on the tubular portion 156 of the support tube 154 , Rather, the already existing pressure chamber housing 96 or 98 for the determination of the rolling bearing 164 used, the support of the inner ring of the rolling bearing 164 in the axial direction 18 on the pressure chamber housing 96 or 98 automatically when the support tube 154 on the first pressure chamber housing 96 is screwed so that the assembly is much easier. Although this is not shown in the figure, it should also be noted that it is in the rolling bearing 164 could also be a rolling bearing with split inner and / or outer ring, to ensure increased resistance to tipping. So it could be at the rolling bearing 164 For example, a so-called four-point bearing, so a deep groove ball bearing with specially ground inner and outer rings act, whereby the stability would be improved. It should be noted, however, that the assembly cost would be increased in this case.

The in the operating direction or in the axial direction 16 acting actuating forces of the actuating piston 110 . 116 can be particularly useful over the clutch assembly 28 . 30 , the spring devices 150 . 152 , the rolling bearing 164 , the support tube 154 and the first pressure chamber housing 96 on the first housing section 82 of the coupling housing 80 indirectly supported. Although always above from pressure chamber housings 96 . 98 the speech was, so these pressure chamber housing 96 . 98 also as a cylinder of the respective Betätigungsaktuatorik 92 respectively. 94 be designated. It should be further clarified that the fixed and non-rotatable pressure chamber housing 96 . 98 on the slave side of the respective Betätigungsaktuatorik 92 respectively. 94 are arranged so that the pressure chamber housing 96 . 98 can also be referred to as slave cylinder.

As already mentioned above, the illustrated clutch arrangements are 28 . 30 to wet-running multi-plate clutch assemblies, which are thus traversed by a cooling oil or other cooling medium. For this purpose, a cooling oil supply path is provided, which initially passes through the shaft passage opening 86 extends and between the edge of the shaft passage opening 86 and the outside of the second transmission input shaft 12 runs. Subsequently, the cooling oil supply path runs in the axial direction 16 further in the annular space between the inner pressure chamber housing section 102 and the tubular portion 156 on the one hand and the second transmission input shaft 12 on the other hand. Both in the tubular section 156 as well as in the extension of the inner thigh 104 Cooling oil openings are provided (no reference numeral), through which the cooling oil supply path then in the radial direction 20 can extend to the outside. In the further course of the cooling oil supply path, this extends through a cooling oil opening in the tubular portion 50 of the outer disk carrier 36 , In this way, the cooling oil supply path first reaches the second clutch arrangement 30 and then to the first clutch assembly 28 , wherein in the Lamellentragabschnitten 68 . 46 . 60 and 42 corresponding further cooling oil openings are provided, although not all of these cooling oil openings are shown in the figure. In other words, the Coolant oil supply from the transmission 6 or the gear side, while the wet room 78 to the drive unit 4 or is sealed to the drive side.

Inside the wet room 78 is also a pump drive member 166 arranged for an oil pump, not shown, wherein the oil pump may serve, for example, the promotion of the cooling oil. In the illustrated embodiment, the pump drive member 166 formed as a gear, but it may also be a Zugmittelgetrieberad or another pump drive member. To the pump drive member 166 could drive on the first power transmission element 136 For example, be provided a corresponding rotational drive means, especially the first power transmission element 136 because of through the recesses 142 in the outer disk carrier 36 engaging actuating fingers 140 at the same speed as the input side of the concentric dual clutch device 2 rotates. However, this would mean that the rotary driving device together with the first power transmission element 136 in the axial direction 16 . 18 would be shifted if the first actuating piston 110 would be axially displaced in a corresponding manner, so that there are connection problems between the pump drive member 166 and the rotational drive means on the first power transmission element 136 would. To avoid this, has the concentric dual clutch device 2 a rotary driving device 168 on, not on any of the power transmission elements 136 . 138 but rotatably on the previously described input side of the concentric double clutch device 2 is attached. The illustrated rotary driving device 168 releasably connected to the pump drive member 166 is in rotary driving connection, is substantially tubular and formed in the tubular portion 50 of the outer disk carrier 36 introduced to non-rotatable and in the axial direction 16 . 18 immovable on the outer disk carrier 36 to be attached. The rotary driving device 168 is thus attached directly to the input side. The substantially tubular rotary drive device 168 also points in the axial direction 18 protruding axial fingers 170 on. The axial fingers 170 extend in the axial direction 18 through windows 172 in the two power transmission elements 138 . 136 up to the clutch assemblies 28 . 30 opposite side of the first power transmission element 136 , On this page is a rotary driver 174 to the axial finger 170 attached, with the pump drive member 166 releasably engaged in rotary driving connection. In the illustrated embodiment, the rotary driving member 174 designed as a gear, depending on the design of the pump drive member 166 However, also a Zugmittelgetrieberad or another form of a rotary driving member 174 to get voted.

By the rotary driving device 168 or their axial fingers 170 through the windows 172 in the power transmission elements 136 . 138 extend, a particularly direct connection of the input side of the concentric double clutch device 2 with the pump drive member 166 causes. Thus, in particular a rotary driving device can be avoided, which the force transmission elements 136 . 138 in the radial direction 22 engages behind from the outside, what the concentric double clutch device 2 required space would unnecessarily increase. It should be clarified in this context that it is also possible in principle that the rotary driving device 168 in the axial direction 18 through the central recess in the power transmission elements 136 . 138 extends, since in this area, however, relatively little space is available, the windows 172 but preferably in the radial direction 20 further outside than the central recess arranged. In addition, the rotary driving member 174 with the first actuating piston 110 and the pickup warehouse 144 arranged radially nested, wherein the rotary driving member 174 due to the advantageous axial staggering of the actuating piston 110 . 116 may have a particularly small diameter.

2 shows a second embodiment of the double clutch device according to the invention 2 , wherein below only the differences from the first embodiment will be discussed, the same reference numerals are used for the same or similar parts and the rest of the description applies otherwise.

In the second embodiment of the concentric double clutch device 2 to 2 are the actuating fingers 140 of the first power transmission element 136 latching in the recesses 142 in the radial section 48 of the outer disk carrier 36 introduced or insertable. So are the actuating fingers 140 in an insertion direction, here the axial direction 16 corresponds to latching in the recesses 142 inserted or insertable that the power transmission element 136 in the opposite direction of insertion, here in the axial direction 18 , at which the input side of the dual clutch device 2 forming plate carrier 36 supported or supportable. For this purpose is in at least one of the recesses 142 a, locking element 186 . 188 used, the latching with the respective actuating finger 140 interacts. The locking element 186 . 188 is preferably formed as a plastic element.

The two actuating pistons 110 . 116 each have a seal 202 . 204 for sealing the pressure chamber 112 . 118 on that under lay down in the axial direction 16 . 18 on the actuating piston 110 . 116 at the pressure room 112 . 118 facing end face of the actuating piston 110 . 116 is attached. In other words, the seal 202 . 204 in the illustrated embodiment, in the axial direction 18 pointing end face of the actuating piston 110 . 116 attached. For this purpose, said end faces each have one or more recesses into which the associated seal 202 . 204 positively engages to effect their axial fixing. One can also speak of a knotted seal, which in the axial direction 16 was pressed into said recess. The seals 202 . 204 the trained as an annular piston actuating piston 110 . 116 do not extend beyond those in the radial direction 20 outwards and in the radial direction 22 inwardly facing side surfaces of the actuating piston 110 . 116 ,

Both actuating pistons 110 . 116 are made of plastic and latching with the respective engagement bearing 144 . 146 connected. For this purpose, the actuating piston elastic locking elements 206 on, which is integral with the actuating piston 110 . 116 are formed. In the illustrated embodiment, the locking elements 206 designed as locking tongues, wherein the locking elements 206 the engagement bearing 144 . 146 after locking preferably from the inside in the axial direction 18 engage behind.

In contrast to the first embodiment according to 1 the reset of the actuating piston takes place 110 . 116 Although also via spring devices, however, the spring devices are here each of a plurality of between the outer disk of the clutch assemblies 28 . 30 arranged spring elements 190 causes, in the embodiment according to 2 are formed as corrugated rings. The spring elements 190 serve therefore also the spacing or separation of the outer disk and thus the achievement of the set clearance between the slats. How out 2 can be seen, includes the dual clutch device 2 Further, an input side torsional vibration damper 192 who is also in the wet room 78 is arranged. An output side of the torsional vibration damper 192 via a radial bearing 194 in the radial direction on the first clutch output hub 64 supported while the engine torque via a damper input hub 196 in the torsional vibration damper 192 can be introduced.

The pressure chamber housing 96 . 98 are as a one-piece piston housing 180 executed, with a rotation 182 between the actuating piston 110 and the piston housing 180 and a rotation lock 184 between the actuating piston 116 and the piston housing 180 is trained. Both anti-rotation devices 182 . 184 are caused by simple radial projections and / or radial depressions, as is the 2 can be removed. In addition, there are cooling and / or lubricating oil holes 198 in the piston housing 180 provided over which the engagement bearing 144 . 146 be supplied with cooling and / or lubricating oil. Furthermore, this is between the piston housing 180 and the support tube 154 provided thread 208 designed as a right-hand thread, so that the rotational movement of the dual clutch device 2 during operation, a release of the support tube 154 from the piston housing 180 counteracts. Also is a centering of the support tube 154 relative to the piston housing 180 this ensures that a centering section 210 on the piston housing 180 or / and support tube 154 is provided, by the way, even in the first embodiment 1 provided, but is not marked there.

Hereinafter, the procedure for mounting the dual clutch device after 2 with reference to the 3 to 7 described, wherein the method for mounting in a corresponding manner to the dual clutch device after 1 is applicable.

The body shell 180 forms with the actuating piston 110 . 116 , the seals 202 . 204 and the engagement camps 144 . 146 a coherent actuator module 200 out ( 3 ), that - like out 4 visible - on the first housing section 82 of the coupling housing 80 is fastened, wherein the first housing portion 82 is formed by a part of the transmission housing.

Subsequently, this will be essentially from the clutch assemblies 28 . 30 , the support tube 156 , the power transmission elements 136 . 138 and the torsional vibration damper 192 composite clutch damper module ( 3 ) in the wet room 78 used, with the with the recesses 142 latched actuating fingers 140 a secure hold of the power transmission elements 136 . 138 on the clutch damper module. The second power transmission element 138 can preferably be on the first power transmission element 136 in the axial direction 18 be supported, so that in this case, in principle, no locking or no locking element 188 between the actuating fingers 140 of the second power transmission element 138 and the recesses 142 is required.

After that the claws become 212 a socket wrench through the mounting holes 162 guided to the support tube 154 with the piston housing 180 to bolt ( 6 ), wherein the screwing is preferably carried out with a predetermined tightening torque to stop.

Is the support tube 154 with the piston housing 180 screwed, so is the wet room 78 then by means of the second housing section 84 closed in the form of a lid and sealed ( 7 ), wherein the damper input hub 196 extends outwardly from the wet room through a central recess within the lid.

LIST OF REFERENCE NUMBERS

2

concentric double clutch device

4

drive unit

6

transmission

8th

output hub

10

first transmission input shaft

12

second transmission input shaft

14

axis of rotation

16

axial direction

18

axial direction

20

radial direction

22

radial direction

24

circumferentially

26

circumferentially

28

first clutch arrangement

30

second clutch arrangement

32

Kupplungseingangsnabe

34

driver disc

36

External disk carrier

38

circlip

40

attack

42

first slat support section

44

support section

46

second slat support section

48

first radial section

50

tubular section

52

second radial section

54

support hub

56

circlip

58

first inner disk carrier

60

Panel support section

62

support section

64

first clutch output hub

66

second inner disk carrier

68

Panel support section

70

support section

72

second clutch output hub

74

thrust

76

radial bearings

78

wet room

80

clutch housing

82

first housing section

84

second housing section

86

Shaft passage opening

88

Shaft passage opening

90

poetry

92

first Betätigungsaktuatorik

94

second Betätigungsaktuatorik

96

first pressure chamber housing

98

second pressure chamber housing

100

External pressure chamber housing section

102

internal pressure chamber housing section

104

inside thigh

106

outboard leg

108

bottom leg

110

first actuating piston

112

first pressure chamber

114

circumferential seals

116

second actuating piston

118

second pressure chamber

120

inside thigh

122

outboard leg

124

radial leg

126

first pressure oil channel

128

opening

130

second pressure oil channel

132

channel

134

opening

136

first power transmission element

138

second power transmission element

140

actuating fingers

142

recesses

144

engagement bearing

146

engagement bearing

148

spacer

150

spring means

152

spring means

154

support tube

156

tubular section

158

flange

160

mounting portion

162

mounting window

164

roller bearing

166

Pump drive member

168

Rotary driving device

170

axial finger

172

window

174

Rotationally driving element

180

piston housing

182

twist

184

twist

186

locking element

188

locking element

190

spring element

192

torsional vibration damper

194

radial bearings

196

Dämpfereingangsnabe

198

Cooling and / or lubricating oil bores

200

actuator module

202

poetry

204

poetry

206

locking elements

208

thread

210

centering

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 10034730 A1 [0002, 0007]

Claims (17)

Concentric double clutch device ( 2 ) for arrangement in a drive train of a motor vehicle between a drive unit ( 4 ) and a transmission ( 6 ), one of a first transmission input shaft ( 10 ) associated first clutch assembly ( 28 ), preferably multi-disc clutch assembly, particularly preferably wet-running multi-disc clutch assembly, for optional torque transmission between the drive unit ( 4 ) and the first transmission input shaft ( 10 ) and a second transmission input shaft ( 12 ) associated second clutch assembly ( 30 ), preferably multi-disc clutch assembly, particularly preferably wet-running multi-disc clutch assembly, for optional torque transmission between the drive unit ( 4 ) and the second transmission input shaft ( 12 ), wherein the first clutch arrangement ( 28 ) by means of at least one hydraulically driven first actuating piston ( 110 ), to which a first pressure chamber ( 112 ) assigned by a first pressure chamber housing ( 96 ) and the first actuating piston ( 110 ), and the second clutch arrangement ( 30 ) by means of at least one hydraulically driven second actuating piston ( 116 ) is operable, which a second pressure chamber ( 118 ) assigned by a second pressure chamber housing ( 98 ) and the second actuating piston ( 116 ) is limited, characterized in that the pressure chamber housing ( 96 . 98 ) is at least partially, preferably entirely, fixed or / and rotationally fixed. Concentric double clutch device ( 2 ) according to claim 1, characterized in that the coupling arrangement ( 28 . 30 ) indirectly via a power transmission element ( 136 . 138 ) by the actuating piston ( 110 . 116 ) is actuated, wherein the actuating piston ( 110 . 116 ) and the power transmission element ( 136 . 138 ), optionally by means of a bearing ( 144 . 146 ) between the actuating piston ( 110 . 116 ) and the power transmission element ( 136 . 138 ), preferably rotationally decoupled, and the actuating piston ( 110 . 116 ) particularly preferably rotatably with the pressure chamber housing ( 96 . 98 ) connected is. Concentric double clutch device ( 2 ) according to claim 2, characterized in that the force transmission element ( 136 . 138 ) is designed such that the actuating force of the actuating piston ( 110 . 116 ), preferably without leverage, in the ratio 1: 1 to the clutch assembly ( 28 . 30 ) is transferable, wherein the force transmission element ( 136 . 138 ) is particularly preferably formed in one piece and / or directly with the engagement bearing ( 144 . 146 ) and / or the coupling arrangement ( 28 . 30 ) cooperates. Concentric double clutch device ( 2 ) according to one of the preceding claims, characterized in that the two actuating pistons ( 110 . 116 ) are arranged axially staggered, wherein the respective pressure space ( 112 . 118 ) facing active surfaces of the actuating piston ( 110 . 116 ) preferably in the axial direction ( 16 . 18 ) overlap. Concentric double clutch device ( 2 ) according to one of the preceding claims, characterized in that the actuating pistons ( 110 . 116 ) are formed as annular piston, wherein the actuating piston ( 110 . 116 ) preferably one in the axial direction ( 16 ) open U-shaped cross-section, in which the engagement bearing ( 144 . 146 ) is inserted, and the engagement bearing ( 144 . 146 ) particularly preferably in only one radial direction ( 22 ) on the actuating piston ( 110 . 116 ) is supported. Concentric double clutch device ( 2 ) according to one of the preceding claims, characterized in that a fixed or / and non-rotatable coupling housing ( 80 ) is provided, in which the double clutch device ( 2 ), wherein preferably at least one of the pressure chamber housing ( 96 . 98 ) fixed or / and rotationally fixed to the coupling housing ( 80 ) or integral with the coupling housing ( 80 ) is formed and within the wall of the coupling housing ( 80 ) particularly preferably at least one pressure oil channel ( 126 . 130 ) for supplying pressurized oil into one of the pressure chambers ( 112 . 118 ) runs. Concentric double clutch device ( 2 ) according to claim 6, characterized in that the coupling housing ( 80 ) a first housing section ( 82 ), preferably a housing or gear housing bell with a housing opening, and one in the axial direction ( 16 ) opposite the second housing section ( 84 ), preferably a housing cover for closing the housing opening, wherein particularly preferably both pressure chamber housing ( 96 . 98 ) on the first or second housing section ( 82 . 84 ) are provided. Concentric double clutch device ( 2 ) according to one of claims 6 or 7, characterized in that the first pressure chamber housing ( 96 ) on the coupling housing ( 80 ), while the second pressure chamber housing ( 98 ) on the first pressure chamber housing ( 96 ) or in one piece with the first pressure chamber housing ( 96 ) is formed, wherein both pressure chamber housing ( 96 . 98 ) are preferably each formed in one piece and the second pressure chamber housing ( 98 ) particularly preferably one in the axial direction ( 16 ) has opened U-shaped cross-section. Concentric double clutch device ( 2 ) according to one of the preceding claims, characterized in that the actuating pistons ( 110 . 116 ) and / or the associated engagement bearing ( 144 . 146 ) relative to the coupling arrangements ( 28 . 30 ) are arranged radially inward, wherein preferably at least one actuating piston ( 116 ) and / or the associated engagement bearing ( 146 ) with respect to the coupling arrangements ( 28 . 30 ) is arranged radially nested and the actuating piston ( 110 . 116 ) particularly preferably in each case at least one spring device ( 150 . 152 ) for returning the actuating piston ( 110 . 116 ) is assigned, of which at least one with respect to the coupling arrangements ( 28 . 30 ) is arranged radially nested. Concentric double clutch device ( 2 ) according to one of the preceding claims, characterized in that the double clutch device ( 2 ), preferably the input side, in the axial or / and radial direction ( 16 . 22 ) on the coupling housing ( 80 ), preferably on a fixed support tube ( 154 ) on the coupling housing ( 80 ), particularly preferably by means of a rolling bearing ( 164 ), is supported. Concentric double clutch device ( 2 ) according to one of the preceding claims, characterized in that the actuating pistons ( 110 . 116 ) have the same actuating direction, wherein the actuating forces in the actuating direction, preferably via the rolling bearing ( 164 ), particularly preferably via the support tube ( 154 ), on the clutch housing ( 80 ) are supportable. Concentric double clutch device ( 2 ) according to claim 9 or 10, characterized in that the support tube ( 154 ) on one of the pressure chamber housing ( 96 . 98 ) or from a portion of the pressure chamber housing ( 96 . 98 ) and / or releasably attached to the coupling housing ( 80 ) or the pressure chamber housing ( 96 . 98 ), preferably screwed on, more preferably via an external or internal thread of the support tube ( 154 ) is screwed on. Concentric double clutch device ( 2 ) according to one of claims 10 to 12, characterized in that the rolling bearing ( 164 ) in the one axial direction ( 18 ) on one of the pressure chamber housing ( 96 . 98 ) is supported while the rolling bearing ( 164 ) in the other axial direction ( 16 ) preferably on the support tube ( 154 ), particularly preferably a flange section ( 158 ) of the same, is supported. Concentric double clutch device ( 2 ) according to any one of claims 10 to 13, characterized in that on the support tube ( 154 ), preferably at its flange portion ( 158 ), a mounting section ( 160 ) is provided for releasably securing an insertion tool, while in the input and / or output side of the dual clutch device ( 2 ) Mounting window ( 162 ) are formed, which in the axial direction ( 16 . 18 ) with each other and with the mounting section ( 160 ) are aligned such that the insertion tool in the axial direction ( 18 ) through the mounting windows ( 162 ) to the mounting section ( 160 ) is approachable. Concentric double clutch device ( 2 ) according to one of the preceding claims, characterized in that a rotationally fixed to the input side, preferably a plate carrier ( 36 ) of the input side, the double clutch device ( 2 ) fixed rotary driving device ( 168 ) provided with a pump drive member ( 166 ) for an oil pump releasably in Drehmitnahmeverbindung can be brought, wherein the rotational drive means ( 168 ) preferably axial fingers ( 170 ), which in the axial direction ( 18 ) through windows ( 172 ) in at least one of the power transmission elements ( 136 . 138 ) to the clutch assemblies ( 28 . 30 ) facing away from the power transmission element ( 136 . 138 ), and more preferably a rotary driver ( 174 ), optionally a gear or Zugmittelgetrieberad, on the Axialfingern ( 170 ) on the clutch assemblies ( 28 . 30 ) facing away from the power transmission element ( 136 . 138 ) having. Concentric double clutch device ( 2 ) according to one of claims 2 to 15, characterized in that at least one force transmission element ( 136 ) in the axial direction ( 16 ) extending actuating fingers ( 140 ), which through recesses ( 142 ) in the input side, optionally a plate carrier ( 36 ) of the input side, the double clutch device ( 2 ), wherein the actuating fingers ( 140 ) latching in the recesses ( 142 ) are inserted or insertable, preferably in an insertion direction ( 16 ) latching in the recesses ( 142 ) are introduced or insertable, that the power transmission element ( 136 ) in the direction of insertion ( 16 ) opposite direction ( 18 ) on the input side, optionally the plate carrier ( 36 ), supported or supportable, and particularly preferably in at least one of the recesses ( 142 ), preferably designed as a plastic element, locking element ( 186 . 188 ) is inserted, the latching with the respective actuating finger ( 140 ) cooperates. Concentric double clutch device ( 2 ) according to one of the preceding claims, characterized in that at least one of the actuating pistons ( 110 . 116 ) a seal ( 202 . 204 ) for sealing the pressure chamber ( 112 . 118 ), which are fixed in the axial direction ( 16 . 18 ) at the pressure chamber ( 112 . 118 ) facing end face the actuating piston ( 110 . 116 ), wherein in the end face preferably at least one recess is provided into which the seal ( 202 . 204 ) engages positively, and the seal ( 202 . 204 ) particularly preferably not via the radially inwardly and outwardly facing side surfaces of the actuating piston ( 110 . 116 ), and / or at least one of the actuating pistons ( 110 . 116 ) latching with the engagement bearing ( 144 . 146 ), wherein preferably at least one elastic locking element ( 206 ) on the actuating piston ( 110 . 116 ) is provided, which particularly preferably in one piece with the, optionally made of plastic, actuating piston ( 110 . 116 ) is trained.

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