CN108916262B

CN108916262B - Concentric dual clutch device

Info

Publication number: CN108916262B
Application number: CN201810762516.8A
Authority: CN
Inventors: J.亨齐; H.J.豪克
Original assignee: BorgWarner Inc
Current assignee: BorgWarner Inc
Priority date: 2010-03-25
Filing date: 2011-03-11
Publication date: 2021-05-04
Anticipated expiration: 2031-03-11
Also published as: CN108916262A; DE102011014778B4; CN102200173A; DE102011014778A1

Abstract

The invention relates to a concentric dual clutch device (2) for arrangement between a transmission (4) and a transmission (6) in a drive train of a motor vehicle, having a first clutch arrangement (28) associated with a first transmission input shaft (10) for selective torque transmission between the transmission shaft (4) and the first transmission input shaft (10) and a second clutch arrangement (30) associated with a second transmission input shaft (12) for selective torque transmission between the transmission shaft (4) and the second transmission input shaft (12), wherein the first clutch arrangement (28) can be actuated by at least one hydraulically drivable first actuating piston (110) associated with a first pressure chamber (112) which is delimited by a first pressure chamber housing (96) and the first actuating piston (110), and the second clutch arrangement (30) can be actuated by at least one second hydraulically drivable actuating piston (116) which is assigned to a second pressure chamber (118) which is delimited by a second pressure chamber housing (98) and the second actuating piston (116), wherein the pressure chamber housing (96, 98) is at least partially fixed and/or rotationally fixed.

Description

Concentric dual clutch device

The application is a divisional application of the Chinese invention patent application with the application number of 201110059786.0, the application date of 2011, 03 and 11 and the invention name of 'concentric dual clutch device'.

Technical Field

The invention relates to a concentric dual clutch device for arrangement between a transmission and a transmission in a drive train of a motor vehicle, having: a first clutch arrangement assigned to a first transmission input shaft for selective torque transmission between the transmission and the first transmission input shaft, and a second clutch arrangement assigned to a second transmission input shaft for selective torque transmission between the transmission and the second transmission input shaft, wherein the first clutch arrangement can be actuated by means of at least one first actuating piston which is assigned to a first pressure chamber and can be hydraulically driven, the first pressure chamber is delimited by a first pressure chamber housing and the first actuating piston, and the second clutch arrangement can be actuated by means of at least one second actuating piston which is assigned to a second pressure chamber and which is hydraulically drivable, the second pressure chamber being delimited by a second pressure chamber housing and the second actuating piston.

Background

DE 10034730 a1 describes a concentric dual clutch device having: a first clutch arrangement and a second clutch arrangement of a radial nested arrangement, wherein said first clutch arrangement is for selective torque transfer between a transmission and a first transmission input shaft and said second clutch arrangement is for selective torque transfer between the transmission and a second transmission input shaft. Both clutch arrangements can be actuated correspondingly by means of a hydraulically drivable actuating piston. For this purpose, a pressurizing chamber is assigned to each of the two actuating pistons, which pressurizing chamber is delimited by a pressurizing chamber housing and the respective actuating piston. The pressurized chamber housing is formed in each case by a part of an internal rotary sleeve and a part of the disk carrier of the concentric dual clutch device, which is connected to the sleeve in a rotationally fixed manner. Furthermore, a balancing chamber for centrifugal oil balancing is provided on the side of each actuating piston facing away from the pressurizing chamber. The sleeve of the concentric dual clutch device is substantially tubular, wherein the tubular sleeve is supported radially on a fixed carrier tube. In order to be able to act on the pressure chamber by means of hydraulic oil and to be able to drive the actuating piston thereby, a rotary channel is provided between the sleeve and the support tube, which rotary channels are separated from one another by means of corresponding rotary channel seals.

The known concentric dual clutch device is effective but has disadvantages. One aspect is that the pressure strength of the hydraulic medium for driving the actuating piston is limited due to leakage, so that a method of using a high-pressure reservoir for increasing the efficiency of the concentric dual clutch device is not possible or is only possible under certain conditions. On the other hand, the known concentric dual clutch device construction is costly and takes up a large amount of construction space.

The object of the present invention is therefore to create a concentric dual clutch device which, on the one hand, has a particularly high hydraulic medium pressure and, if necessary, ensures the use of a high-pressure accumulator and leakage-free operation; on the other hand, it has a particularly simple and space-saving design, and it should furthermore be possible to assemble the concentric dual clutch device in a simple manner.

Disclosure of Invention

The proposed task is achieved by the features set forth in claim 1. Advantageous embodiments of the invention are comprised in the dependent claims.

The double clutch device according to the invention for arrangement between a transmission and a transmission in a drive train of a motor vehicle comprises: a first clutch arrangement associated with a first transmission input shaft and a second clutch arrangement associated with a second transmission input shaft. The two clutch arrangements are arranged radially one above the other, so that the dual clutch device according to the invention relates to a concentric dual clutch device. The first clutch is arranged for selective torque transfer between the transmission and a first transmission input shaft, and the second clutch is arranged for selective torque transfer between the transmission and a second transmission input shaft. In this case, it is preferred if one transmission input shaft is embodied as a hollow shaft, through the interior of which the other transmission input shaft passes, which can also be said to be a radial sleeve of the transmission input shaft. The two-clutch arrangement also preferably relates to a multiplate clutch arrangement, particularly preferably to a wet-running multiplate 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 annular piston. For this purpose, a first pressure chamber is assigned to the first actuating piston, which is preferably delimited only by a first pressure chamber housing and the first actuating piston. In this case, it is preferred that the first pressurizing chamber is delimited only by the first pressurizing chamber housing and the first actuating piston. In contrast, the second clutch arrangement can be actuated by means of a second hydraulically drivable actuating piston. For this purpose, a second pressurizing chamber is associated with the second actuating piston, which is delimited by a second pressurizing chamber housing and the second actuating piston, wherein here preferably also the second pressurizing chamber is delimited only by the second pressurizing chamber housing and the second actuating piston. Thus, the actuation pistons can be driven independently of each other by the action of hydraulic oil or other hydraulic medium on the slave pressurized chambers in order to actuate the respective clutch arrangements. The pressure chamber housing (i.e. at least the first pressure chamber housing or the second pressure chamber housing, preferably both the first and the second pressure chamber housing) is at least partially fixed and/or is rotationally fixed. This can be achieved, for example, by arranging the pressurized chamber housing on a stationary and/or rotationally fixed clutch housing.

An at least partially fixed and/or rotationally fixed, preferably completely fixed and/or rotationally fixed pressure chamber housing has the advantage that the pressure chamber can be acted upon by hydraulic oil or another hydraulic medium to drive the actuating piston without the need for the rotary channel at all. By eliminating the rotary channel with associated rotary channel seals (as described in DE 10034730 a 1), which only ensures a nearly leakage-free operation when the hydraulic oil pressure or the hydraulic medium pressure is low, a particularly high hydraulic oil operating pressure or hydraulic medium operating pressure can be selected in the concentric dual clutch device according to the invention. In particular, a high-pressure accumulator can thereby be used in the hydraulic oil supply line without this being detrimental to the leak-free operation of the concentric dual clutch device. Thereby, the efficiency of the whole system will be improved finally. In addition, by eliminating the rotary channel seals required for the rotary channels, the drag torque of the double clutch arrangement is likewise reduced and its hysteresis is improved. Furthermore, the construction of the concentric dual clutch device is substantially simplified, which at the same time allows the required construction space to be reduced. The structural simplification is due on the one hand to the elimination of the rotary channel with the secondary rotary channel seal. On the other hand, the simplification of the construction is achieved in that a balancing chamber for centrifugal oil balancing is no longer required because of the pressurized chamber housing which is at least partially, preferably completely fixed and/or is formed rotationally fixed. In this way, in particular, additional measures or components for producing balancing chambers for so-called centrifugal oil balancing are eliminated.

In view of the aforementioned advantages of the concentric dual clutch device according to the invention, in a preferred embodiment the concentric dual clutch device according to the invention does not comprise balancing chambers for centrifugal oil balancing, which are assigned to the actuating pistons.

In a further particularly preferred embodiment of the concentric dual clutch device according to the invention, the concentric dual clutch device is completely free of rotary channels in the hydraulic oil supply line for the pressure chambers to which the actuating pistons are assigned, so that particularly high hydraulic oil pressures or hydraulic medium pressures can be achieved and, in certain cases, high-pressure accumulators can be used in the hydraulic oil supply line.

According to another preferred embodiment of the concentric dual clutch device according to the invention, a high-pressure reservoir is provided in the hydraulic oil supply line for the pressure chambers in order to increase the efficiency of the entire system.

In a particularly preferred embodiment of the concentric dual clutch device according to the invention, the actuating pistons, the associated pressurizing chambers and the associated pressurizing chamber housing are arranged on the receiving side of the hydraulic system. Thus, the pressurizing chamber housing defined by each pressurizing chamber can also be said to be a receiving cylinder.

In an advantageous embodiment of the concentric dual clutch device according to the invention, at least one opening for feeding hydraulic oil or another hydraulic medium into the pressurized chamber of the pressurized chamber housing is provided. In order to be able to dispense with a rotary channel whose rotary channel seal can necessarily limit the operating pressure of the hydraulic oil, the opening for supplying the hydraulic oil is preferably arranged in the stationary and/or rotationally fixed pressure chamber housing or in a stationary and/or rotationally fixed part of the pressure chamber housing.

In order to avoid the necessity of arranging the actuating pistons directly in the region of the associated clutch arrangement, while at the same time achieving a relatively more free and space-saving arrangement of the actuating pistons, in a further advantageous embodiment of the concentric dual clutch device according to the invention a force transmission element is correspondingly provided, by means of which the respective clutch arrangement can be actuated by means of the associated actuating piston. In this way, for example, the actuating piston can be arranged radially inside or outside the associated clutch arrangement in order to achieve a reduction in the axial overall length of the concentric dual clutch device by means of a corresponding sleeve stack, wherein the force transmission elements can form a bridge of the spacing between the actuating piston and the associated clutch arrangement.

In a particularly advantageous embodiment of the concentric dual clutch device according to the invention, the actuating pistons are rotationally synchronously decoupled by the aforementioned force transmission elements. In this way, an unintentional rotation or rotation of the force transmission element is not transmitted to the actuating piston, so that the actuating piston cannot be twisted or only meaningfully twisted relative to the at least partially fixed and/or rotationally fixed compression chamber housing. Thereby a double guarantee can be achieved. On the one hand, due to the rotationally synchronously decoupled actuating piston, centrifugal pressures (even small) inside the pressure chamber are avoided, which makes the centrifugal oil balancing measures, which are less costly per se, cancelled. On the other hand, by using a simple seal between the actuator piston on the one hand and the pressurized chamber housing on the other hand, only a simple sealing of the individual pressurized chambers is required, which sealing is furthermore suitable for maintaining a particularly high hydraulic oil pressure or hydraulic medium pressure.

In order to achieve a reliable rotationally synchronous decoupling between the actuating piston and the force transmission element in the aforementioned embodiment, in a further advantageous embodiment of the concentric dual clutch device according to the invention, the rotationally synchronous decoupling can be carried out by means of a coupling bearing between the actuating piston and the force transmission element, wherein the coupling bearing is preferably designed as a roller bearing. Friction between the rotating force transmission element and the rotationally synchronously decoupled actuating piston can be largely avoided (in certain cases) by the roller bearing and its (in certain cases) built-in rolling bodies, so that the transmission of the rotational movement of the force transmission element to the actuating piston is prevented. In this embodiment, it is further preferred that a replaceable spacer is provided between the actuating piston and the coupling bearing in the actuating direction of the respective actuating piston, so that the spacing between the actuating piston and the coupling bearing can be flexibly adjusted in the actuating direction and tolerance compensation can be carried out.

In a further particularly preferred embodiment of the concentric dual clutch device according to the invention, the actuating piston is connected in a rotationally fixed manner to the pressurized chamber housing. In this way, all the outer walls of the individual pressure chambers can be formed in a rotationally secure manner, so that a minimum centrifugal oil pressure cannot occur inside the pressure chambers and measures for centrifugal oil balancing can be completely eliminated. In addition, by means of the actuating piston which is connected in a rotationally fixed manner to the pressure chamber housing, a simple sealing of the pressure chamber can be achieved by means of a seal between the actuating piston on the one hand and the pressure chamber housing on the other hand, which sealing ensures leak-free operation even in the case of particularly high hydraulic oil pressures or hydraulic medium pressures. In this embodiment, it is also particularly preferred that the rotationally secure connection between the actuating piston and the pressure chamber is formed in a form-fitting manner. This makes it possible to provide, for example, a projection or a recess on the actuator piston, wherein the projection can engage in a recess on the pressure chamber housing or a projection on the pressure chamber housing can engage in a recess on the actuator piston, in order to form a rotationally secure connection.

The aforementioned force transmission element can in principle be constructed in the form of a lever in order to intensify the actuating force of the actuating piston by means of a lever transmission ratio in order to increase the force ultimately acting on the clutch arrangement. Alternatively or additionally, the force transmission element may also be designed to be elastic, so that it exerts a restoring force on the actuating piston. To achieve both features, the force transmission element can be designed, for example, in the form of a leaf spring. In yet another particularly advantageous embodiment of the concentric dual clutch device according to the invention, the force transmission element can be constructed such that the actuating force of the actuating piston can be transmitted to the clutch arrangement in a ratio of 1: 1. In this embodiment, there is no need to increase the force acting on the respective clutch arrangement by means of a corresponding lever transmission ratio between the actuation piston and the clutch arrangement; in particular, for the reasons described above, the concentric dual clutch device already allows particularly high hydraulic oil pressures or hydraulic medium pressures. The transmission of the actuating piston actuating force to the clutch arrangement in a ratio of 1:1 can in principle be realized in this embodiment by means of a force transmission element in the form of a lever, but in this embodiment it is preferred to transmit the actuating force to the clutch arrangement without a lever transmission ratio, i.e. the force transmission element is preferably formed in a non-lever manner. This has the advantage that, on the one hand, the force transmission element is less expensive and less susceptible to interference, while, on the other hand, a smaller overall length in the actuation force direction, preferably in the axial direction, can be achieved. It is further particularly preferred in this embodiment that said force transmission element is constructed in one piece and/or directly co-acts with said engagement bearing and/or said clutch arrangement to achieve a particularly simple construction of the concentric dual clutch device. In this embodiment, it is also preferred that the one-piece force transmission element is essentially of inelastic design and thus has a lower elasticity than a leaf spring or similar spring device, while the restoring force required for restoring the actuating piston is exerted by a separate spring device.

The two actuating pistons can in principle be arranged radially one above the other. This may have the result, however, that the actuating gear for the two clutch devices may have a relatively large dimension in the radial outward direction in the region of the actuating pistons, since, among other things, the inner actuating piston may have to have a particularly large dimension in the radial outward direction in order to have a working surface which is as large as the working surface of the outer actuating piston. In order to reduce the dimension of the actuation gear unit in the region of the actuation pistons in the radial outward direction, in a further particularly preferred embodiment of the concentric dual clutch device according to the invention, the two actuation pistons are arranged axially in stages. In this way, for example, an additional installation space can be created radially outside the actuating piston, in which the pump drive member (explained in more detail below), the rotation synchronization member of a rotation synchronization device (explained in more detail below) or other components of the concentric dual clutch device are preferably arranged. In this embodiment, it is further preferred that the working surfaces of the actuating piston facing the respective pressurizing chamber overlap in the axial direction, wherein it can also be said that the projections of the working surfaces of the actuating piston at least partially overlap in the axial direction. As mentioned at the outset, a particularly compact arrangement of the two actuating pistons with respect to the radial direction is thereby achieved.

The two clutch arrangements of the concentric dual clutch device according to the invention can in principle each be associated with a plurality of spaced actuating pistons which are distributed in the circumferential direction. However, in order to simplify the manufacture of the concentric dual clutch device on the one hand and to ensure a uniform transmission of the actuating forces to the individual clutch arrangements on the other hand, in a further advantageous embodiment of the concentric dual clutch device according to the invention the actuating pistons are designed as annular pistons, so that only one annular first actuating piston and one annular second actuating piston are required. In this embodiment it is further preferred that the actuating pistons have an axially open U-shaped cross section, in which the aforementioned joint bearing between the actuating piston on the one hand and the force transmission element on the other hand is arranged. By means of the U-shaped cross section of the actuating piston, on the one hand, a reliable guidance of the actuating piston along the pressure chamber wall formed by the associated pressure chamber housing is ensured, and on the other hand, a small overall length combined by the actuating piston and the joint bearing is ensured. Furthermore, in this preferred embodiment it is particularly preferred that the engagement bearing is supported on the actuating piston in only one of two opposite radial directions. Thus, the joint bearing can be supported, for example, either on the inner side of the U-shaped cross-section in the radially inward direction or on the outer side of the U-shaped cross-section in the radially outward direction. The assembly of the joint bearing into the U-shaped cross section of the actuating piston is thereby simplified, and a reliable centering of the joint bearing relative to the actuating piston, which is designed as an annular piston, is not impaired.

In a further advantageous embodiment of the concentric dual clutch device according to the invention, a clutch housing is provided which is stationary and/or rotationally fixed, wherein the dual clutch device is arranged. The clutch housing can be formed, for example, by a part of the transmission housing and/or a part of the transmission housing or of the motor housing.

In order to create an at least partially, preferably completely fixed and/or rotationally fixed pressure chamber housing for each actuating piston, in a further preferred embodiment of the concentric dual clutch device according to the invention at least one of the pressure chamber housings is fixedly and/or rotationally fixed on the clutch housing or is formed integrally with the clutch housing. Although two alternatives for arranging the pressure chamber housing on the clutch housing are described, the first-described alternative in which the pressure chamber housing is fixed and/or is fixedly mounted in a rotational sense on the clutch housing is preferred, in particular in the first-described alternative in which the pressure chamber housing and the clutch housing can be separately manufactured and machined in order to then fix and/or fixedly secure the pressure chamber housing in a rotational sense on the clutch housing. This makes it possible to produce the pressure chamber housing with the associated pressure chamber particularly precisely and also simply, which cannot be realized on such a scale if the pressure chamber housing with the clutch housing is formed in one piece. In the first-mentioned alternative, it is furthermore preferred that the pressure chamber housing is detachably or replaceably arranged on the clutch housing, and that, in this way, it is possible, on the one hand, to quickly adapt the pressure chamber housing to the respective concentric dual clutch device within the scope of manufacture, and, on the other hand, it is possible to quickly repair the concentric dual clutch device if required.

In a further advantageous embodiment of the concentric dual clutch device according to the invention, at least one hydraulic oil duct extends within the clutch housing wall, which hydraulic oil duct serves to convey hydraulic oil or a hydraulic medium into at least one of the pressurizing chambers. In this case, the hydraulic oil line preferably opens into the aforementioned opening for feeding hydraulic oil into the pressure chamber of the pressure chamber housing.

According to a further advantageous embodiment of the concentric dual clutch device according to the invention, the clutch housing has a first housing part and an axially opposite second housing part. The first housing part is preferably a housing shell or transmission housing shell with a housing opening, while the second housing part is preferably formed by a housing cover for closing the housing opening. In this case, the second housing part in the form of the housing cover is particularly preferably detachably mounted on the first housing part in the form of a housing cover or transmission housing cover, in order to be able to quickly access the concentric dual clutch device during servicing or maintenance.

In a further preferred embodiment of the concentric dual clutch device according to the invention, the two pressurized chamber housings are arranged either on the first housing part or on the opposite second housing part. In this way, the two pressurized chamber housings can be arranged, for example, jointly on the aforementioned first housing part in order to achieve an arrangement close to the transmission and thus a short distance of the hydraulic oil or hydraulic medium feed. On the other hand, however, the two pressurized chamber housings can also be arranged together on the opposite second housing part, so that the actuating gear can be accessed particularly easily by removing the housing cover. However, the embodiment variant described above, in which the pressurized-chamber housing is arranged close to the transmission on the first housing part, is preferred here.

The two pressure chamber housings can in principle each be arranged directly on the clutch housing. However, this can make the production more complex and more difficult to assemble, in particular if the axial stepping of the actuating piston described above with reference to one embodiment of the invention is to be realized. For this reason, in another preferred embodiment of the concentric dual clutch device according to the present invention, the first pressurized chamber housing is disposed on the clutch housing, and the second pressurized chamber housing is disposed on the first pressurized chamber housing. Thus, it can be said that the second pressurizing chamber housing is indirectly disposed on the clutch housing through the first pressurizing chamber housing. Alternatively, the second pressurized chamber housing may also be formed integrally with the first pressurized chamber housing, but this alternative is preferred only if it is desired to radially telescope the actuating piston. In other cases, the first-named alternative should be selected, in which a second, now separate pressurizing chamber housing is attached to the first pressurizing chamber housing in the assembly phase, and in addition the manufacture of the pressurizing chamber housing is significantly simpler in the case of axial stepping of the actuating piston.

In the embodiment described above, it is preferable that the two pressurizing chamber housings are integrally manufactured. It will be understood here that the parts of the pressure chamber housing which are essential for defining the pressure chamber are constructed in one piece and are not assembled from a plurality of individual parts which are first separated. In this way, not only is assembly simplified, but more importantly a particularly sealed pressurized chamber is also established. In this case, it is preferred that each pressurizing chamber is delimited only by the one-piece pressurizing chamber housing and the associated actuating piston, wherein a seal between the pressure housing and the actuating piston is not excluded. It is further preferred in this embodiment that the second pressure chamber housing, which is indirectly arranged on the clutch housing by means of the first pressure chamber housing, has an axially open U-shaped cross section in which the second pressure chamber and additionally the second actuating piston delimiting the second pressure chamber are arranged. By means of the embodiment variant described at the end, a second pressurized-chamber housing can be created which can be produced particularly easily and which, moreover, can be particularly lightweight. In order to be able to achieve a relatively small axial structural length of the concentric dual clutch device even in the specific case of an axial nesting of the actuating pistons, the actuating pistons and/or the associated engagement bearings are arranged radially inwardly with respect to the clutch arrangement, wherein preferably at least one actuating piston and/or the associated engagement bearing is/are arranged radially nested with respect to the clutch arrangement, particularly preferably independently of the axial position of the movable actuating piston.

In a further advantageous embodiment of the concentric dual clutch device according to the invention, the actuating pistons are each assigned a spring device for resetting the actuating pistons, at least one of the spring devices being arranged radially one above the other with respect to the clutch arrangement. In this embodiment, it is further particularly preferred that the spring device is formed separately from the aforementioned force transmission element and thus does not have the function of transmitting the actuating force of the actuating piston to the associated clutch arrangement.

The dual clutch device (preferably its input side) can in principle be supported axially and/or radially indirectly or directly on one of the transmission input shafts. In order to achieve a particularly rotationally stable arrangement of the concentric dual clutch device, however, in a further preferred embodiment of the invention the concentric dual clutch device (preferably the input side thereof) is supported or supportable alternatively or additionally axially and/or radially on the clutch housing, preferably on a fixed carrier tube of the clutch housing. In this case, the carrier tube does not necessarily have to be directly connected to the clutch housing, but rather can also be indirectly fastened to the clutch housing, as explained in more detail below. In this embodiment, the carrier tube is preferably connected fixedly to a housing part of the clutch housing, which housing part is arranged on the transmission side, wherein the transmission input shaft can be placed radially on top of one another on the fixed carrier tube, i.e. the transmission input shaft passes through the fixed carrier tube.

In a further particularly preferred embodiment of the concentric dual clutch device according to the invention, which represents an improvement of the above-described embodiment, the support of the dual clutch device, preferably of its input side, takes place axially and/or radially on the transmission or on the fixed carrier tube by means of a roller bearing, preferably a ball bearing.

In another advantageous embodiment of the concentric dual clutch device according to the invention, the actuating piston has its own actuating direction. Here, the actuating direction is to be understood such that the actuating piston is moved in this direction and exerts its actuating force to actuate the respective clutch arrangement, wherein the actuating direction preferably relates to one of the axial directions of the concentric dual clutch device. In this case, the actuating force can be supported on the clutch housing in the actuating direction, preferably by the roller bearing (particularly preferably by the support tube).

The aforementioned carrier tube, on which the dual clutch device (preferably its input side) can be supported in the axial direction and/or in the radial direction, can in principle be arranged directly on the clutch housing or on one of the housing parts of the clutch housing. In a further advantageous embodiment of the concentric dual clutch device according to the invention, however, the support tube is arranged on one of the pressure chamber housings or is formed by a part of the pressure chamber housing. A particularly compact and particularly lightweight construction of the concentric dual clutch device is achieved when the carrier tube is thereby arranged indirectly on the clutch housing via the pressurized chamber housing. In the first-mentioned alternative of the mounting of the support tube on the pressure chamber housing, the support tube can first be produced separately from the pressure chamber housing in order to subsequently mount the support tube on the pressure chamber housing. Since the carrier tube in this first alternative is formed by a part of the pressure chamber housing and is thus produced in one piece therewith, the first alternative is preferred over the second alternative, in particular so that a modular construction of the concentric dual clutch device is possible in which the pressure chamber housing is assigned to one module and the carrier tube can be assigned to the other module together with the other component of the dual clutch device. The assembly of the concentric dual clutch device can thereby be simplified in each case.

In order to be able to realize a particularly rational modular construction of the concentric dual clutch device, which simplifies the assembly of the concentric dual clutch device, in a further advantageous embodiment of the invention the carrier tube is releasably attached to the clutch housing or to the pressure chamber housing as an alternative or as an extension to the previously described embodiment. In order to simplify the assembly of the support tube on the clutch housing or the pressure chamber housing, it is further preferred that the support tube is screwed to the clutch housing or the pressure chamber housing. In this respect, it is particularly advantageous if the support tube has an external or internal thread, by means of which the support tube can be connected to the clutch housing or the pressure chamber housing with a corresponding internal or external thread.

The roller bearing described above can in principle be fixed to the support tube in both axial directions by means of corresponding securing elements or fastening elements (for example by means of circlips). However, in order to further simplify the construction of the concentric dual clutch device, in another preferred embodiment of the invention, the roller bearing is preferably supported directly in one axial direction on one of the pressurized chamber housings. In this way, no additional securing elements or fastening elements are required in the axial direction, which would increase the assembly effort. More precisely, the roller bearing is fixed in this axial direction by means of the pressurized chamber housing which is present in itself. Thus, for example, the second pressure chamber housing with a U-shaped cross section described above can have an elongate inner side on which the roller bearings can be supported with the end faces facing the axial direction. In order to be able to support the roller bearing in the other axial direction in a rational and cost-effective manner, it is further preferred in this embodiment that the roller bearing is supported in the other axial direction on a flange portion of the carrier tube, which flange portion is particularly preferably formed integrally with the carrier tube. In this embodiment, the roller bearing can thus be supported and thus fixed in both axial directions on the clutch housing or on the pressure chamber housing by means of the reinforcement of the carrier tube only. Thereby, the assembly of the concentric dual clutch device is further simplified. In this embodiment, it is also preferred that the roller bearing is supported directly on the carrier tube or on a flange portion of the carrier tube.

In order to further simplify the assembly of the concentric dual clutch device, and in particular to enable modular assembly, in a further preferred embodiment of the concentric dual clutch device according to the invention, a mounting section for releasably fixing an insertion tool is provided on the carrier tube (preferably on the flange section of the carrier tube), while mounting windows are formed in the input side and/or the output side of the dual clutch device, which are axially aligned with one another and with the mounting section in such a way that the insertion tool can extend axially through the mounting window to the mounting section. In this way, for example, these mounting windows can be provided in the input-side transmission disk on the one hand and in the output-side disk carrier on the other hand, so that a simple extension of the insertion tool into the mounting section of the carrier tube is possible via the mounting windows. In this embodiment, the mounting portion is preferably designed in such a way that the insertion tool fastened thereto is connected to the support tube in a rotationally synchronous manner, so that the support tube can be screwed to the clutch housing or the pressure chamber housing by rotation of the insertion tool.

In a further particularly advantageous embodiment of the concentric dual clutch device according to the invention, a rotational synchronization device is provided which is rotationally fixed, preferably directly fixed, to the input side of the dual clutch device and which can be releasably connected in rotational synchronization with a pump transmission member for an oil pump. In this case, the rotational synchronization device is preferably rotationally fixedly connected to the disk carrier on the input side of the dual clutch device. In the sense of the invention, the input side of the double clutch device does not comprise the force transmission element described above, even if the force transmission element rotates at the same rotational speed as the input side of the double clutch device. This embodiment thus particularly excludes variants in which the rotary synchronization device is rigidly secured in rotation to a force transmission element. Although the rotationally fixed synchronization device is rotationally fixed to a force transmission element, i.e. the unintended axial displacement of the rotationally fixed synchronization device is linked to the force transmission element, it is possible to axially fix the rotationally fixed synchronization device, which is rotationally fixed to the input side of the dual clutch device, together with the input side of the dual clutch device in the manner already described above, in order to prevent axial displacement of the rotationally fixed synchronization device during operation.

In order to achieve a particularly compact construction of the rotary synchronizing device, in a particularly advantageous embodiment of the concentric dual clutch device according to the invention, the rotary synchronizing device comprises an axial finger which extends in the axial direction through at least one window in the force transmission element to the side of the force transmission element facing away from the clutch arrangement. In this way, the input side of the double clutch device achieves a particularly short connection to the pump transmission member via the rotational synchronization device. In this context, it is to be noted that the window can also be formed by a central bore in the force transmission element, but preferably the window relates to a bore which is arranged radially further outward than the central bore in the force transmission element, and furthermore more installation space can be provided for the arrangement of the pump transmission member in a region which is radially further outward than in a region which is radially further inward.

In a further particularly advantageous embodiment of the concentric dual clutch device according to the invention, which represents a development of the above-described embodiment, the rotational synchronization device has a rotational synchronization member on the side of the force transmission element facing away from the clutch arrangement. The rotary synchronizing member preferably relates to a gear or a traction drive gear, which can be in a known manner or can be brought into a rotary synchronizing connection with the pump drive member. For example, the rotary synchronizing member can be pressed against or crimped with an axial finger of the rotary synchronizing device afterwards. It is further preferred in this embodiment that the rotational synchronization member is arranged radially nested with respect to at least one of the actuation pistons.

Drawings

The invention is explained in detail below with reference to the drawing by means of an exemplary embodiment.

The sole figure of the present description shows in section a side view of one embodiment of a concentric dual clutch device according to the invention.

Detailed Description

The single figure shows an embodiment of a concentric dual clutch device 2 according to the invention between a transmission 4 and a transmission 6 within a drive train of a motor vehicle. In the transmission 4, which is, for example, an internal combustion engine, only the output sleeve 8 is shown, wherein the output sleeve 8 is preferably an output sleeve of a rotational speed damper, which is arranged between the transmission 4 on the one hand and the concentric dual clutch device 2 on the other hand. In the transmission 6, which preferably relates to a dual clutch transmission, only one first transmission input shaft 10 and one second transmission input shaft 12 are shown. The concentric dual clutch device 2 can rotate about a rotational axis 14 extending in opposite

axial directions

16, 18, and opposite

radial directions

20, 22 and opposite

circumferential directions

24, 26 are also indicated in the figure by corresponding arrows. The two

transmission input shafts

10, 12 extend in

axial direction

16, 18 along the axis of rotation 14, wherein the second transmission input shaft 12 is designed as a hollow shaft, through which the first transmission input shaft 10 extends coaxially. The two

transmission shafts

10, 12 are thereby arranged one above the other in the

radial direction

20, 22, so that the first transmission shaft 10 can be referred to as the internal transmission shaft and the second transmission shaft 12 as the external transmission shaft. The internal input shaft of the first transmission 10 can be designed as a solid shaft, but, as is shown in the drawing by means of dashed lines, it is also possible and, in certain cases, desirable to design the first transmission shaft 10 as a hollow shaft.

The concentric dual clutch device 2 has a first clutch arrangement 28 assigned to the first transmission shaft 10 and a second clutch arrangement 30 assigned to the second transmission shaft 12. Since the dual clutch device 2 relates to a concentric dual clutch device 2, the two clutch arrangements 28, 30 are arranged one above the other in the

radial direction

20, 22. Thus, the first clutch arrangement 28 may also be referred to as an external clutch arrangement, while the second clutch arrangement 30 may also be referred to as an internal clutch arrangement. Both clutch arrangements 28, 30 relate to wet-running multiplate clutch arrangements, so that the clutch arrangements 28, 30 essentially each consist of a disk stack made up of inner and outer disks. The first clutch arrangement 28 functions to selectively transfer torque between the transmission 4 and the first transmission input shaft 10 of the transmission 6, while the second clutch arrangement 30 functions to selectively transfer torque between the transmission 4 and the second transmission input shaft 12 of the transmission 6.

The concentric dual clutch device 2 furthermore has a radially inner clutch input sleeve 32, which is in rotationally synchronous connection with the output sleeve 8 of the transmission 4, wherein the rotationally synchronous connection is preferably formed in a positively locking and releasable manner. In this case, the clutch input sleeve 32 is of closed design in the axial direction 16, i.e. it has no openings at all through the axial direction 16. A drive disk 34 is fixedly connected to the clutch input sleeve 32 in terms of rotation, said drive disk extending substantially radially 20 from the clutch input sleeve 32. The drive disk 34 is connected in a rotationally fixed manner to an outer disk carrier 36 radially outward of the radial direction 20. Here, a positive-locking rotationally synchronous connection is concerned, in which the drive disk 34 can be supported in the axial direction 16 on the outer disk carrier 36 by means of a circlip 38. Furthermore, the transmission disk 34 is arched in its radially outer region in such a way that it likewise forms a stop 40 which projects in the axial direction 18, on which the first clutch arrangement 28 can be supported in the axial direction 16.

The outer disk carrier 36 is formed essentially from a first disk carrier part 42, which is tubular and is rotationally synchronously connected to the drive disk 34, a support part 44, which extends from the axially 18 offset end of the first disk carrier part 42 essentially radially 22 inward and is formed integrally with the first disk carrier part 42, and a second disk carrier part 46, which is rotationally fixedly connected to the support part 44, is tubular and is arranged radially 22 within the first disk carrier part 42 and radially overlapping it. The support part 44 is divided into a first radial section 48, which extends from the first disk carrier part 42 radially 22 inward and on which the second disk carrier part 46 is arranged on the side offset in the axial direction 16, a tubular section 50 which extends from the end of the first radial section 48 offset in the radial direction 22 in the axial direction 16 and is thereby arranged radially overlapping in relation to the clutch arrangements 28, 30, and a second radial section 52 which is connected to the end of the tubular section 50 offset in the axial direction 16, which extends from the tubular section 50 further radially inward in the radial direction 22 to receive a support sleeve 54 here, which serves to indirectly support the concentric dual clutch device 2 on a clutch housing which will be described in more detail below, this support will also be discussed in detail below. Furthermore, a further circlip 56 is provided on the second disk carrier section 46 of the outer disk carrier 36, by means of which circlip the second clutch arrangement 30 can be supported on the second disk section 46 in the axial direction 16.

Furthermore, the first clutch arrangement 28 is assigned an inner disk carrier 58, which essentially consists of a tubular disk carrier part 60 and a support part 62 connected to the tubular disk carrier part 60 in the axial direction 16, wherein the support part 62 extends radially inward 22 in order to be in rotationally synchronous connection with the first transmission shaft 10 via a first clutch output sleeve 64. The second clutch arrangement 30 is also assigned a second inner disk carrier 66, which is composed of a tubular disk carrier part 68 and a support part 70 connected to the tubular disk carrier part 68 in the axial direction 16, wherein the support part 70 extends radially inward 22 in order to be in rotationally synchronous connection with the second transmission shaft 12 via a second clutch output sleeve 72. The outer disks of the clutch arrangement 28 or 30 are connected in a rotationally fixed but axially displaceable manner to the first or second disk carrier part 42, 46 of the outer disk carrier 36, while the inner disks of the clutch arrangement 28 or 30 are connected in a rotationally fixed but axially displaceable manner to the

disk carrier part

60 or 68 of the inner disk carrier 58 or 66.

As can be further seen from the figures, axial bearings 74 in the form of needle bearings are provided in the

axial directions

16, 18 between the transmission disc 34 and the support part 62, between the support part 62 and the support part 70, and between the support part 70 and a flange part of a carrier tube, which will be described in detail below, in order to support the components relative to one another or to separate them from one another in the

axial directions

16, 18. The axial bearings 74 are arranged in alignment with one another in the

axial direction

16, 18. Furthermore, the clutch output sleeve 32 is supported in the radial direction 22 via a radial bearing 76 on the side of the first clutch output sleeve 64 that is offset outward in the radial direction 20, wherein for this purpose the first clutch output sleeve 64 extends in the axial direction 16 into a recess in the clutch input sleeve 32 embodied in the form of a pot. Thus, the input sleeve 32 is supported indirectly in the radial direction 22 on the first transmission input shaft 10, first via the radial bearing 76 and the first clutch output shaft 64.

The concentric dual clutch device 2 is arranged in a wet chamber 78 surrounded by a stationary and rotationally fixed clutch housing 80. The clutch housing 80 has a first housing part 82, which delimits the wet space 78 in the axial direction 18 and in the radial direction 20 and is in this case designed as a transmission housing cover with a housing opening offset in the axial direction, and a second housing part 84, which is designed as a housing cover closing the housing opening of the first housing part 82 and thus delimits the wet space 78 in the axial direction 16. In the region of the rotational axis 14, the first housing part 82 has a central shaft passage opening 86, through which the

transmission input shafts

10, 12 of the transmission 6 extend in the axial direction 16 into the wet space 78 toward the concentric dual clutch device 2. The second housing part 84 also has a central shaft passage opening 88, through which the clutch input sleeve 32 extends in the axial direction 16 to the transmission 4 and out of the wet chamber 78, wherein a seal 90 is arranged between the inner side of the shaft passage opening 88 of the second housing part 84 and the radially outwardly offset side of the clutch input sleeve 32 in order to seal the wet chamber 78 in the axial direction 16.

A first actuating gear 92 is associated with the first clutch arrangement 28, and a second actuating gear 94, which will be described below, is associated with the second clutch arrangement 30. A first pressurizing chamber housing 96 of the first actuator 92 is then fixed and rotationally fixed to the housing part 82 of the clutch housing 80, while a second pressurizing chamber housing 98 is fixed and rotationally fixed to the first pressurizing chamber housing 96, so that the second pressurizing chamber housing 98 can be indirectly fixed and rotationally fixed to the first housing part 82 at least via the first pressurizing chamber housing 96. Thus, the two

pressurization chamber housings

96, 98 are disposed or provided on the same housing portion 82 of the clutch housing 80. The first pressurizing chamber housing 96 is first manufactured separately from the first housing portion 82, while the second pressurizing chamber housing 98 is first manufactured separately from the first pressurizing chamber housing 96, so that the first pressurizing chamber housing 96 is then placed on the housing portion 82 and the second pressurizing chamber housing 98 is placed on the first pressurizing chamber housing 96 in the manner described. Here, the first pressurizer chamber housing 96 is releasably secured to the first housing portion 82, while the second pressurizer chamber housing 98 is releasably secured to the first pressurizer chamber housing 96. Each of the two

pressure chamber housings

96, 98 is formed in one piece. Alternatively, the first pressurizing chamber housing 96 and the housing portion 82 and/or the second pressurizing chamber housing 98 and the first pressurizing chamber housing 96 may also be constructed integrally with each other, but the illustrated embodiment is preferable in view of manufacturing and, where possible, required maintenance or service issues. In any case, by fixing the pressurizing

chamber housings

96, 98 to the housing portion 82 of the clutch housing 80, the pressurizing

chamber housings

96, 98 are configured to be fixed and rotationally fixed, as in the clutch housing 80.

Both

pressure chamber housings

96, 98 are formed in an annular manner so as to completely surround the axis of rotation 14 in the

circumferential directions

24, 26. The first pressure chamber housing 96 is subdivided into a radially outer pressure chamber housing part 100 and a radially inner pressure chamber housing part 102, the pressure chamber housing parts 100, 102 being formed integrally with one another. The second pressurizing chamber housing 98 is fixed to an inner pressurizing chamber housing portion 102 of the first pressurizing chamber housing 96, which further protrudes in the axial direction, and has a U-shaped cross section that is open in the axial direction 16. The U-shaped cross section has a radial inner edge 104 and a radial outer edge 106, which are connected to one another by a base 108. An annular recess is provided in the outer pressurizer chamber housing part 100 of the first pressurizer chamber housing 96, which is open in the axial direction 16 and in which a first hydraulically actuatable actuating piston 110 is inserted when the first pressurizer chamber 112 is formed. Thus, the first pressurizing chamber 112 is defined only by the first pressurizing chamber housing 96 and the first actuating piston 110, which are integrally configured. The first pressure chamber 112 is likewise formed in an annular shape, wherein a plurality of annular seals 114 are also provided between the first actuating piston 110 and the wall of the first pressure chamber 112. A second hydraulically drivable pressure chamber piston 116 is inserted into an annular recess (with a U-shaped cross section) which is likewise open in the axial direction 16 in the interior of the second pressure chamber housing 98, in such a way that a second pressure chamber 118 is formed which is delimited only by the second pressure chamber housing 98 and the second actuating piston 116 which are formed in one piece, wherein in this case also annular seals 114 are provided on the second hydraulically drivable pressure chamber piston 116 in order to reliably seal the second pressure chamber 118.

The two actuating

pistons

110, 116 are arranged in the

axial direction

16, 18 so as to be displaceable within the associated

pressurized chamber housing

96 or 98, whereas the actuating

pistons

110, 116 are each connected in a rotationally fixed manner to the associated

pressurized chamber housing

96 or 98. It can thus be said that the actuating

pistons

110, 116 are rotationally robust actuating pistons which cannot rotate about the axis of rotation 14 in the

circumferential direction

24, 26. The rotationally secure connection of the actuating

pistons

110, 116 to the associated pressurizing

chamber housing

96 or 98 is preferably achieved by a form fit, which is not shown in the figures for reasons of visibility of the figures. Furthermore, the two actuating

pistons

110, 116, which are designed as annular pistons, have a U-shaped cross section which is open in the axial direction 16. Each U-shaped section has a radial inner edge 120, a radial outer edge 122 and a radial edge 124 connecting the two edges 120 and 122, the latter constituting the working surface of the

actuating piston

110, 116 facing the respective pressurizing chamber 112, 118 in the axial direction 18. A particularly

lightweight actuating piston

110, 116 is thereby achieved, which, moreover, is guided particularly reliably in the respective

pressurized chamber housing

96, 98. In addition, as will also be explained in more detail below, the axial length of the

actuation gear mechanisms

92 and 94 is thereby shortened.

As can be seen from the drawing, the second pressurization chamber housing 98 is fixed to the built-in pressurization chamber housing portion 102 of the first pressurization chamber housing 96 in such a manner that the second pressurization chamber housing 98 protrudes outward in the radial direction 20 through the built-in pressurization chamber housing portion 102 of the first housing 96. As a result, the two actuating

pistons

110, 116 are arranged in stages in the

axial directions

16, 18, and the internal pressurizing chamber housing portion 102 of the first pressurizing chamber housing 96, to which the second pressurizing chamber housing 98 is fixed, protrudes further in the axial direction 16 than in the case of the external pressurizing chamber housing portion 100 of the first pressurizing chamber housing 96. Thus, the two actuating

pistons

110, 116 are not radially nested but are arranged axially in stages, with the working surfaces of the actuating

pistons

110, 116 facing the pressurizing chamber 112 or 118 overlapping in the

axial direction

16, 18. By connecting such an axial step with the running surface overlap of the actuating

pistons

110, 116, an

actuating gear

92, 94 is created which has a particularly small outward dimension in the radial direction 20 in the region of the

pressure chamber housings

96, 98 or the actuating

pistons

110, 116, in order to be able to create additional installation space for further components in this way, as will be explained in more detail below.

In order to be able to supply the first pressurizing chamber 112 with hydraulic oil or another hydraulic medium, at least one first hydraulic oil duct 126 is provided inside the wall of the first housing part 82 of the clutch housing 80. The first pressure chamber housing 96 is fixed to the first housing part 82 in such a way that the first hydraulic oil line 126 opens into an opening 128 in the fixed and rotationally fixed pressure chamber housing 96 and the pressure chamber 112 can be supplied via the first hydraulic oil line 126 and the opening 128. Furthermore, at least one second hydraulic line 130, which is separate from the first hydraulic line 126 and opens into a line 132 inside the pressurized chamber housing part 102 of the first pressure housing 96, is formed in the wall of the first housing part 82 of the clutch housing 80. The line 132 opens again in the axial direction 16 into an opening 134 in the second pressurizing chamber housing 98, so that the second pressurizing chamber 118 can be charged with hydraulic oil via the second hydraulic oil line 130, the line 132 and the opening 134.

The two clutch arrangements 28, 30 cannot be actuated directly by the associated

actuating piston

110 or 116. More precisely, a first force-transmitting element 136 and a second force-transmitting element 138 are provided therein. The two

force transmission elements

136 and 138 are designed in such a way that they bridge the distance between the

actuating piston

110, 116 and the associated clutch arrangement 28 or 30 in the

radial direction

20, 22. This is necessary since not only the actuating

pistons

110, 116 but also the associated engagement bearings, which will be described in detail later, are arranged radially more inwardly with respect to the clutch arrangements 28, 30. In this way, the available installation space can be utilized in a more optimized manner and an increase in the axial installation length of the concentric dual clutch device 2 can be avoided. The second actuator piston 116 and the associated engagement bearing are arranged radially nested in the

radial direction

20, 22 relative to the clutch arrangement 28, 30, wherein such radial nesting preferably takes place independently of the respective axial position of the second actuator piston 116 and the associated engagement bearing.

The

force transmission elements

136, 138 extend from the actuating

pistons

110, 116 substantially radially 20 outward, so that they then reach the associated clutch arrangement 28 or 30 via an end-side actuating finger 140 extending in the axial direction 16. Here, the actuating fingers 140 extend in the axial direction 16 through a corresponding plurality of holes 142 in the first radial portion 48 of the outer disc carrier 36, in order to additionally form a rotationally synchronous connection between the

force transmission elements

136, 138 and the outer disc carrier 36. Both force-transmitting

members

136, 138 have a central bore through which, among other things, the

transmission input shafts

10, 12 extend.

In order to prevent a torque (even if this is due solely to friction) from being transmitted from the

force transmission element

136, 138 to the associated

actuating piston

110 or 116, the

actuating piston

110, 116 and the associated

force transmission element

136 or 138 are rotationally synchronously decoupled by means of an

engagement bearing

144 or 146 between the

actuating piston

110, 116 and the associated

force transmission element

136 or 138. Owing to this rotationally synchronous decoupling, a rotationally secure arrangement of the actuating

pistons

110, 116 on the associated pressurizing

chamber housing

96 or 98 can in principle be dispensed with, whereas a rotationally secure arrangement of the actuating

pistons

110, 116 on the pressurizing

chamber housing

96 or 98 is preferred, and in addition, a rotation of the actuating

pistons

110, 116 in the

circumferential direction

24, 26 relative to the associated pressurizing

chamber housing

96 or 98 can thereby be prevented particularly effectively, so that a particularly high tightness of the respective pressurizing chamber 112, 118 can be achieved in the region of the annular seal 114.

As can be seen from the figures, the

engagement bearings

144, 146 are arranged on the associated

actuating piston

110 or 116 in such a way that they are at least partially inserted or embedded in the axial direction 18 in the U-shaped cross section of the

respective actuating piston

110, 116. As a result, not only can particularly

lightweight actuating pistons

110, 116 be realized, but also a short axial structural length of the concentric dual clutch arrangement 2 can be realized. The

coupling bearings

144, 146 are also supported on the associated

actuating piston

110 or 116 only in one of the two opposite

radial directions

20, 22, as a result of which, on the one hand, the center of the

coupling bearings

144, 146 can be reliably aligned relative to the associated

actuating piston

110 or 116, and, on the other hand, the

coupling bearings

144, 146 can be simply inserted into the associated

actuating piston

110 or 116. In the above example, the support of the

engagement bearings

144, 146 takes place exclusively radially 20 inwardly on the inner side 120 of the

respective actuating piston

110 or 116, while absolutely no support takes place radially 20 outwardly on the outer side 122 of the

respective actuating piston

110 or 116, wherein this support can also take place in the opposite way.

It can also be seen in the figures that a spacer 148 in the form of an annular plate is arranged in the

axial direction

16, 18 between the

actuating piston

110, 116 and the associated engagement bearing 144 or 146, via which spacer the

engagement bearing

144, 146 is supported on the radial edge 124 of the associated

actuating piston

110 or 116 in the axial direction 18. In this case, the spacer 148 is exchangeably arranged in the U-shaped cross section of the

actuating piston

110 or 116, so that a simple tolerance compensation can be achieved by selecting a correspondingly thick spacer 148.

By means of the fixed and rotationally fixed

pressure chamber housings

96, 98 and the rotationally fixed

actuating pistons

110, 116, which are rotationally synchronously decoupled from the slave

force transmission elements

136 or 138, the pressure chambers 112 or 118 can be charged with hydraulic oil at particularly high pressures, and the concentric dual clutch device 2 according to the invention eliminates a rotary channel whose rotary channel seals are only conditionally suitable for maintaining a high pressure of the hydraulic oil. For this reason, in the case of the illustrated concentric dual clutch device 2, at least one high-pressure accumulator is also integrated in the hydraulic oil supply line, wherein the high-pressure accumulator is not shown in the drawing. Furthermore, the stationary rotationally fixed

pressure chamber housings

96, 98 and the rotationally fixed rotationally synchronously decoupled

actuating pistons

110, 116 determine that no centrifugal oil pressure is present in the pressure chambers 112 or 118, so that the concentric dual clutch device 2 completely dispenses with a corresponding balancing chamber for centrifugal oil balancing, which balancing chamber may be the only thing that determines the high outlay for producing the concentric dual clutch device 2.

Due to the high pressure in the hydraulic oil supply lines, it may in principle also be possible to dispense with the lever-type design of the

force transmission elements

136, 138. The

force transmission elements

136, 138 are designed in such a way that the force acting in the actuating direction by the actuating

pistons

110, 116 is transmitted to the associated clutch arrangement 28 or 30 in a ratio of 1:1 without a lever ratio. The actuating directions of both actuating

pistons

110, 116 correspond to the axial direction 16. By dispensing with lever-type force transmission elements, the axial structural length of the concentric dual clutch device 2 can be shortened and the structural complexity can be reduced. The

force transmission elements

136, 138 are also constructed in one piece for the sake of simplicity of construction. To further simplify the construction, the

force transmission elements

136, 138 directly cooperate with the associated engagement bearing 144 or 146 and the associated clutch arrangement 28 or 30.

The return of the two actuating

pistons

110, 116 to their starting position shown in the figures is not effected by an elastic

force transmission element

136, 138, but instead at least one

return spring device

150 or 152 is respectively associated with the

force transmission element

136 or 138, which is formed rigidly and virtually inelastically. In this way, the spring arrangement 150 is supported on the one hand in the axial direction 16 on the first radial section 48 of the outer disk carrier 36 and on the other hand in the axial direction 18 on the force transmission element 136, wherein the spring arrangement 150 is in this example designed as a leaf spring, which makes particularly short axial construction lengths possible. In contrast, the spring arrangement 152 is supported, on the one hand, in the axial direction 16, indirectly or directly on the second radial section 52 of the outer disk carrier 36 returning in the axial direction 16, and, on the other hand, in the axial direction 18, on the second force transmission element 138, wherein in the embodiment shown in the drawing the spring arrangement 152 is designed as a helical spring which has only small dimensions in the

radial directions

20, 22. The spring means 152, the second engagement bearing 146 and the second actuation piston 116 may also be arranged radially nested with the clutch arrangement 28, 30.

As already explained above, the clutch input sleeve 32 is supported in the radial direction 22 on the first clutch output sleeve 64 and thus on the first transmission shaft 10 via the radial bearing 76. However, this is not sufficient to support the actuating forces of the actuating

pistons

110, 116 acting in the axial direction 16 in a reasonable manner. For this reason, the concentric dual clutch device 2 is also indirectly supported or can be supported on the clutch housing 80 in the axial direction 16 and in the radial direction 22. The input side is illustrated here as including the clutch input sleeve 32, the driving discs 34 and the outer disc carrier 36, but not including the

force transmission elements

136, 138, although in a rotationally synchronous connection with the input side of the concentric dual clutch device 2 as explained hereinbefore.

In order to provide such a support of the concentric dual clutch device 2 and thus to realize the actuation force of the

actuation pistons

110, 116, a stationary carrier tube 154 is further provided, which is indirectly fixed and supported on the first housing part 82 of the clutch housing 80. Here, the carrier tube 154 is integrally composed of a tubular portion 156 extending in the

axial directions

16, 18 with the

transmission shafts

10, 12 passing therebetween, and a flange portion 158 connected to the tubular portion 156 in the axial direction 16, the flange portion extending substantially outward in the radial direction 20. The flange portion 158 further comprises a mounting portion 160 for releasably securing an insertion tool (not shown), wherein the mounting portion 160 is formed at an end of the flange portion 158 that is offset outward in the radial direction 20. For example, the mounting portion 160 can be a portion with a plurality of fastening holes and/or fastening projections, which can be brought into a rotationally synchronous connection with the insertion tool in a form-fitting manner. The mounting portion 160 is arranged in the

axial direction

16, 18 in alignment with the mounting window 162 in the transmission disc 34, the support portion 62 of the first inner disc carrier 58 and the support portion 70 of the second inner disc carrier 66. In other words, the fitting windows 162 are formed in the input side and the output side of the concentric dual clutch device 2. The mounting windows 162 are aligned with one another and with the mounting portion 160 in such a way that the insertion tool can extend in the axial direction 18 through the mounting windows 162 to the mounting portion 160. The axial bearings 74 in the form of needle rollers, which have already been mentioned above, are arranged in the

axial direction

16, 18 between the support part 70 of the second inner disc carrier 66 and the flange part 158 of the carrier tube 154, which radial bearings support the support part 70 in the axial direction 18 on the flange part 158 or separate said components from one another in the

axial direction

16, 18.

On its side facing away from the flange portion 158, the tubular portion 156 of the bracket tube 154 is releasably seated on the built-in plenum housing portion 102 of the first plenum housing 96. For this purpose, the tubular portion 156 has an external thread (no reference numeral) that is screwed into an internal thread on the built-in pressurization chamber housing portion 102 of the first pressurization chamber housing 96. The support tube 154 can in principle also be connected directly to the first housing part 82 of the clutch housing 80, but preferably the support tube 154 is indirectly fixed to the first housing part 82 of the clutch housing 80 via the first pressurized chamber housing 96, as a result of which, inter alia, a significantly simpler construction and a lighter weight of the concentric dual clutch device 2 can be achieved. Alternatively, the carrier tube 154 may also be formed by a part of the first plenum housing 96 and thus be formed integrally with the first plenum housing 96, however, due to the additional flange portion 158, the illustrated embodiment is preferred, in particular, thereby simplifying not only the manufacture of the individual components but also the assembly of the concentric dual clutch device 2.

Now, in order to support the input side of the concentric dual clutch device 2 in the axial direction 16 and in the radial direction 22 on the clutch housing 80, a roller bearing 164, which in the present example is designed as a ball bearing, is arranged in the

radial direction

20, 22 between the support sleeve 54 of the outer disk carrier 36 and the radially outwardly offset side of the tubular portion 156 of the carrier tube 154. The support sleeve 54 is designed in such a way that it can be supported in the axial direction 16 on the outer ring of the roller bearing 164. In contrast, the inner ring of the roller bearing 164 is preferably supported directly in the axial direction 16 on the side of the flange portion 158 of the carrier tube 154 facing the tubular portion 156. In addition, the inner ring of the roller bearing 164 is supported in the axial direction 18 on either of the

pressurization chamber housings

96 or 98. The inner ring of the roller bearing 164 in this example is supported in the axial direction 18 on an inner side 104 of the second plenum housing 98, wherein the inner side 104 projects for this purpose in the axial direction 16 on an outer side 106 of the second plenum housing 98. With the support of the roller bearing 164 in the axial direction 18 on one of the

pressurizer chamber housings

96 or 98, an additional circlip at the tubular portion 156 of the holder tube 154 is no longer required. Specifically, the roller bearing 164 is fixed by the always present

pressure chamber housing

96 or 98, wherein the inner ring of the roller bearing 164 is automatically supported in the axial direction 18 on the

pressure chamber housing

96 or 98 during the screwing of the support tube 154 on the first pressure chamber housing 96, so that the assembly is substantially simplified. Although not shown in the drawings, it should be further noted that the roller bearing 164 may equally well relate to a roller bearing with a separate inner and/or outer ring to ensure improved roll stability. Thus, the roller bearing 164 can be, for example, a so-called four-point roller bearing, i.e., a grooved ball bearing with specially ground inner and outer rings, whereby the roll stability is improved. However, it should be noted that in this case the assembly effort may increase.

The actuating force of the actuating

pistons

110, 116 acting in the actuating direction or in the axial direction 16 can be supported particularly expediently indirectly via the clutch arrangements 28, 30, the

spring devices

150, 152, the roller bearings 164, the support tube 154 and the first pressurized chamber housing 96 on the first housing part 82 of the clutch housing 80. Although the pressurizing

chamber housings

96, 98 have been discussed previously, such

pressurizing chamber housings

96, 98 may also be referred to as cylinders of the respective

actuation transmission mechanisms

92 or 94. It should also be mentioned that stationary and rotationally fixed

pressure chamber housings

96, 98 are arranged on the receiving side of the

respective actuator gear

92 or 94, whereby the

pressure chamber housings

96, 98 are also referred to as receiving cylinders.

As previously mentioned, the illustrated clutch arrangements 28, 30 relate to wet-running multiplate clutch arrangements through which cooling oil or other cooling medium flows. For this purpose, a cooling oil supply line is provided which first extends through the shaft passage opening 86 and runs between the edge of the shaft passage opening 86 and the second transmission input shaft 12. The cooling oil supply line then continues to move in the axial direction 16 in the annular space between the internally pressurized chamber housing part 102 and the tubular part 156 on the one hand and the second transmission input shaft 12 on the other hand. Whether in the tubular portion 156 or in the extension of the inner side 104, cooling oil openings (no reference numeral) are provided through which cooling oil lines can then extend outwardly in the radial direction 20. As the cooling oil supply line continues to extend, it extends through a cooling oil opening into the tubular section 50 of the outer disc holder 36. In this way, the cooling oil supply line reaches first the second clutch arrangement 30 and then the first clutch arrangement 28, wherein a corresponding plurality of further cooling oil openings are provided in the

disk carrier sections

68, 46, 60 and 42, although not all cooling oil openings are shown in the figures. In other words, the cooling oil supply takes place from the transmission 6 or transmission side, while the wet space 78 is sealed off towards the transmission 4 or drive side.

A pump drive member 166 for an oil pump (not shown in detail in the drawings) is further provided in the wet chamber 78, wherein the oil pump can be used, for example, for conveying cooling oil. In the embodiment shown in the figures, the pump drive member 166 is designed as a gear, but it can equally well involve a traction drive gear or other pump drive members. For driving the pump drive member 166, a corresponding rotational synchronization device can be provided, for example, on the first force transmission element 136, in particular, because the actuating finger 140 is clamped through the opening 142 in the outer disk carrier 36, the force transmission element 136 rotating at the same rotational speed as the input side of the concentric dual clutch device 2. However, it may be that when the actuating piston 110 is moved axially in a corresponding manner, this rotational synchronization device may be moved together with the first force transmission element 136 in the

axial direction

16, 18, so that a connection problem between the pump drive member 166 and the rotational synchronization device on the first force transmission element 136 may arise. This avoids this problem, the concentric dual clutch device 2 having a rotation synchronization device 168 which is not fixed to the

force transmission elements

136, 138, but is rather fixedly secured in a rotational sense to the aforementioned input side of the concentric dual clutch device 2. The illustrated rotation synchronization device 168, which is releasably connected in rotational synchronization with the pump drive member 166, is of tubular design in nature and is inserted into the tubular section 50 of the outer disk carrier 36 in order to be fixed in a rotationally fixed manner and immovably in the

axial direction

16, 18 on the outer disk carrier 36. Thereby, the rotation synchronization device 168 is directly fixed on the input side. The substantially tubular rotary synchronization device 168 further has an axial finger 170 projecting in the axial direction 18. The fingers 170 extend in the axial direction 18 through windows 172 in the two

force transmission elements

138, 136 to the side of the first force transmission element 136 facing away from the clutch arrangements 28, 30. On this side, the rotary synchronizing member 174 is fixed to the axial finger 170 and is releasably in rotary synchronizing connection with the pump drive member 166. In the illustrated embodiment, the rotary synchronizing member 174 is configured as a gear, however, another form of traction drive gear or rotary synchronizing member 174 may be selected depending on the configuration of the pump drive member 166.

The input side of the concentric dual clutch device 2 is particularly directly connected to the pump drive member 166, since the rotary synchronizing device 168 or its axial fingers 170 extend through the windows 172 into the

force transmission elements

136, 138. In particular, this makes it possible to avoid a rotation synchronization device, which clamps the

transmission elements

136, 138 back from the outside in the axial direction 22 and which may unnecessarily increase the installation space required for the concentric dual clutch device 2. In this respect, it should be clear that the rotation synchronization means 168 can in principle also extend in the axial direction 18 through a central bore in the

force transmission elements

136, 138, since in this region there is only a relatively small amount of available installation space, the window 172 is preferably arranged more outwardly in the radial direction 20 than the central bore. Furthermore, the rotational synchronization member 174 is arranged radially one above the other with the first actuating piston 110 and the joint bearing 144, wherein the rotational synchronization member 174 can have a particularly small diameter due to the advantageous axial stepping of the actuating

pistons

110, 116.

List of reference marks

2 Concentric double clutch device

4 driving device

6 speed variator

8 output sleeve

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 circumferential direction

26 circumferential direction of the base

28 first clutch arrangement

30 second clutch arrangement

32 clutch input sleeve

34 drive plate

36 outer disc support

38 circlip

40 stop

42 first disc holder portion

44 support part

46 second disk carrier section

48 first radial portion

50 tubular portion

52 second radial segment

54 support sleeve

56 circlip

58 first inner disc holder

60 disk holder section

62 support part

64 first clutch output sleeve

66 second inner disc holder

68 disc holder part

70 support part

72 second clutch output sleeve

74 axial bearing

76 radial bearing

78 Wet room

80 Clutch housing

82 first housing part

84 second housing part

86 shaft passage opening

88 shaft passage opening

90 sealing element

92 first actuating drive

94 second actuation transmission mechanism

96 first pressurizing chamber housing

98 second pressurization chamber housing

100 external pressurization chamber housing part

102 built-in pressurization chamber housing part

104 inner side edge

106 outer side edge

108 bottom edge

110 first actuating piston

112 first pressurized chamber

114 annular seal

116 second actuating piston

118 second pressurized chamber

120 inner side edge

122 outer side edge

124 radial edge

126 first hydraulic oil pipeline

128 opening

130 second hydraulic oil pipeline

132 conduit

134 opening

136 first force transmitting element

138 second force transmitting element

140 actuating finger

142 hole

144 jointed bearing

146 joint bearing

148 spacer

150 spring device

152 spring arrangement

154 support tube

156 tubular portion

158 flange portion

160 mounting part

162 mounting window

164 roller bearing

166 pump drive member

168 rotation synchronizing device

170 axial finger

172 window

174 rotating synchronizing member

Claims

1. Concentric dual clutch device (2) for arrangement in a motor vehicle drive train between a transmission (4) and a transmission (6), having a first clutch arrangement (28) assigned to a first transmission input shaft (10) for selective torque transmission between the transmission (4) and the first transmission input shaft (10) and a second clutch arrangement (30) assigned to a second transmission input shaft (12) for selective torque transmission between the transmission (4) and the second transmission input shaft (12), wherein the first clutch arrangement (28) can be actuated by at least one hydraulically drivable first actuating piston (110) assigned to a first pressure chamber (112) which is delimited by a first pressure chamber housing (96) and the first actuating piston (110), the second clutch arrangement (30) can be actuated by means of at least one second actuating piston (116) which is assigned to a second pressure chamber (118) and which is hydraulically drivable, which second pressure chamber is delimited by a second pressure chamber housing (98) and the second actuating piston (116), the pressure chamber housing (96, 98) being at least partially fixedly or/and rotationally fixedly formed, wherein a clutch housing (80) which is fixedly or/and rotationally fixedly formed is provided, in which the dual clutch device (2) is arranged, the clutch arrangement (28, 30) can be actuated indirectly by means of the actuating piston (110, 116) via a force transmission element (136, 138), wherein the actuating piston (110, 116) and the force transmission element (136, 138) are connected to one another by means of a connecting rod which is located in the actuating piston (110, 116) rotationally synchronously decoupled from an engagement bearing (144, 146) between the force transmission element (136, 138), characterized in that the engagement bearings (144, 146) are arranged radially inwardly with respect to the clutch arrangements (28, 30), the first pressurized chamber housing (96) is releasably mounted on the clutch housing (80), and the second pressurized chamber housing (98) is mounted on the first pressurized chamber housing (96) or is formed integrally with the first pressurized chamber housing (96); wherein the holder tube (154) is releasably mounted on the clutch housing (80) or the pressure chamber housing (96, 98); the flange part (158) is arranged on the support tube (154), wherein a mounting part (160) for releasably fixing an insertion tool is arranged at the end of the flange part (158) that is offset outward in the radial direction (20), and mounting windows (162) are formed on the input side and the output side of the dual clutch device (2), which are aligned with one another and with the mounting part (160) in the axial direction (16, 18) in such a way that the insertion tool can extend in the axial direction (18) through the mounting windows (162) onto the mounting part (160), wherein,

the input side of the double clutch device (2) is supported on the clutch housing (80) by means of a roller bearing (164) in the axial and/or radial direction (16, 22),

the holder tube (154) is screwed to one of the pressure chamber housings (96, 98) via an external thread or an internal thread of the holder tube (154),

the roller bearing (164) is supported in one axial direction (18) on one of the plenum housings (96, 98), while the roller bearing (164) is supported in the other axial direction (16) on the carrier tube (154) or on a flange portion (158) of the carrier tube,

an annular sheet-shaped spacer (148) is arranged in the axial direction (16, 18) between the actuating piston (110, 116) and the coupling bearing (144, 146) in an exchangeable manner, so that simple tolerance compensation can be achieved by selecting a correspondingly thicker or thinner spacer (148);

the two actuating pistons (110, 116) are arranged axially in stages, wherein the working faces of the actuating pistons (110, 116) facing the respective pressurization chamber (112, 118) overlap at least partially in the axial direction (16, 18); and is

The actuating pistons (110, 116) are designed as ring pistons, wherein the actuating pistons (110, 116) have a U-shaped cross section which is open in the radial direction (16) and in which the coupling bearing (144, 146) is inserted, and the coupling bearing (144, 146) is supported on the actuating piston (110, 116) only in the radial direction (22).

2. The concentric dual clutch device (2) as claimed in claim 1, characterized in that the first clutch arrangement (28) is a multiplate clutch arrangement.

3. The concentric dual clutch device (2) as claimed in claim 1, characterized in that the first clutch arrangement (28) is a wet running multiplate clutch arrangement.

4. The concentric dual clutch device (2) as claimed in claim 1, characterized in that the second clutch arrangement (30) is a multiplate clutch arrangement.

5. The concentric dual clutch device (2) as claimed in claim 1, characterized in that the second clutch arrangement (30) is a wet-running multiplate clutch arrangement.

6. The concentric dual clutch device (2) as claimed in claim 1, characterized in that the pressurized chamber housing (96, 98) is formed completely fixed or/and rotationally fixed.

7. The concentric dual clutch device (2) as claimed in claim 1, characterized in that the actuating piston (110, 116) is connected rotationally fast with the pressurized chamber housing (96, 98).

8. The concentric dual clutch device (2) as claimed in claim 7, characterized in that the force transmission element (136, 138) is constructed in such a way that the actuating force of the actuating piston (110, 116) can be transmitted to the clutch arrangement (28, 30) in a ratio of 1:1 without a lever transmission ratio.

9. The concentric dual clutch device (2) as claimed in claim 8, characterized in that the force transmission element (136, 138) is integrally formed or/and directly cooperates with the engagement bearing (144, 146) or/and the clutch arrangement (28, 30).

10. The concentric dual clutch device (2) as claimed in claim 1, characterized in that at least one hydraulic oil duct (126, 130) for supplying hydraulic oil to one of the pressurizing chambers (112, 118) extends in the wall of the clutch housing (80).

11. The concentric dual clutch device (2) as claimed in claim 10, characterized in that the clutch housing (80) has: a first housing portion (82) being a housing cover or transmission housing cover with a housing opening; and a second housing part (84) opposite in the axial direction (16), being a housing cover for closing the housing opening; wherein both pressurization chamber housings (96, 98) are disposed on the first housing portion or the second housing portion (82, 84).

12. The concentric dual clutch device (2) as claimed in claim 1, characterized in that the two pressurized chamber housings (96, 98) are each formed in one piece and the second pressurized chamber housing (98) has a U-shaped cross section which is open in the axial direction (16).

13. The concentric dual clutch device (2) as claimed in claim 1, characterized in that the actuating pistons (110, 116) are arranged radially inwardly with respect to the clutch arrangements (28, 30), wherein at least one actuating piston (116) or/and the engagement bearing (146) is arranged radially nested with respect to the clutch arrangements (28, 30), and the operating pistons (110, 116) are each assigned at least one spring device (150, 152) for resetting the operating piston (110, 116), at least one of the spring devices being arranged radially nested with respect to the clutch arrangements (28, 30).

14. The concentric dual clutch device (2) as claimed in claim 8, characterized in that the actuating pistons (110, 116) have the same actuating direction, wherein the actuating force can be supported on the clutch housing (80) in the actuating direction by means of the roller bearing (164).

15. The concentric dual clutch device (2) as claimed in claim 14, characterized in that the actuating force is supported on the clutch housing (80) in the actuating direction also via the carrier tube (154).

16. The concentric dual clutch device (2) as claimed in claim 1, characterized in that: a rotational synchronization device (168) which is fixedly secured in a rotational sense on the input side of the dual clutch device (2) and which can be releasably brought into a rotationally synchronized connection together with a pump drive member (166) for an oil pump is provided, wherein the rotational synchronization device (168) has axial fingers (170) which extend in the axial direction (18) through windows (172) in at least one of the force transmission elements (136, 138) to the side of the force transmission element (136, 138) facing away from the clutch arrangements (28, 30); and has a rotary synchronizing member (174), which is in each case a gear or a traction drive gear, on the axial fingers (170) on the side of the force transmission element (136, 138) facing away from the clutch arrangements (28, 30).

17. The concentric dual clutch device (2) as claimed in claim 16, characterized in that the rotational synchronization device (168) is fastened to an outer disc carrier (36) of the input side.