Clutch device

Abstract

The invention relates to a clutch device (2) for arrangement in a motor vehicle drive train between a drive unit (4) and a transmission (6), comprising a parallel double clutch (34) with a first multiplate clutch (36) for selectively transmitting torque between a clutch input side (38) and a first clutch output side (40) and a second multiplate clutch (42) for selectively transmitting torque between the clutch input side (38) and a second clutch output side (44), wherein the first multiplate clutch (36) has a first friction plate pack (46) which can be actuated by a first force transmission element (76), the second multiplate clutch (42) has a second friction plate pack (48) which can be actuated by a second force transmission element (78), and the first force transmission element (76) extends through an opening (96) in a friction plate of the second friction plate pack (48) to the first friction plate pack (46). The second force transmission element (78) extends through an opening (92) in the first force transmission element (76) to the second friction plate pack (48).

Description

Technical Field

[0001] The present invention relates to a clutch device for use in a motor vehicle transmission system arranged between a drive unit and a transmission, comprising a parallel dual clutch having a first multi-plate clutch for selectively transmitting torque between a clutch input side and a first clutch output side, and a second multi-plate clutch for selectively transmitting torque between a clutch input side and a second clutch output side, wherein the first multi-plate clutch has a first friction plate group actuated by a first force transmission member, the second multi-plate clutch has a second friction plate group actuated by a second force transmission member, and the first force transmission member extends through an opening in the friction plates of the second friction plate group to the first friction plate group. Background Technology

[0002] Patent document DE 10 2012 017 955 A1 discloses a motor vehicle clutch device with a parallel dual clutch. The dual clutch includes a first multi-plate clutch and a second multi-plate clutch. The first multi-plate clutch selectively transmits torque between the clutch input side and the first clutch output side, while the second multi-plate clutch selectively transmits torque between the clutch input side and the second clutch output side. Thus, the first multi-plate clutch has a first set of friction plates that can be actuated by a first force transmission member, and the second multi-plate clutch has a second set of friction plates that can be actuated by a second force transmission member. Since it is a parallel dual clutch, the two sets of friction plates are arranged axially staggered or aligned with each other in the axial direction. Both sets of friction plates can be actuated by the associated force transmission member in the same axial direction. The first force transmission member has an actuating finger projecting in the axial direction, which extends through a cavity in the outer friction plate of the second set of friction plates to reach and actuate the first set of friction plates.

[0003] While known clutch mechanisms are effective, improvements are still needed in terms of space requirements and torque uniformity in the transmission of torque from a second multi-plate clutch. Summary of the Invention

[0004] In view of this, the object of the present invention is to further improve the universal clutch device so that it has a more compact structure and ensures a high degree of torque uniformity when transmitting torque.

[0005] This invention utilizes a clutch device to achieve the above-mentioned objective. Preferred embodiments of this invention are described in detail below.

[0006] The clutch device according to the invention is designed to be arranged in a motor vehicle transmission system between a drive unit (preferably an internal combustion engine) and a transmission (preferably a dual-clutch transmission). The clutch device has a parallel dual clutch, preferably constructed as a wet dual clutch. Thus, the dual clutch has a first multi-plate clutch for selectively transmitting torque between the clutch input side (preferably an input-side friction plate support) and the first clutch output side (preferably a first output-side friction plate support). Additionally, the dual clutch includes a second multi-plate clutch for selectively transmitting torque between the clutch input side and the second clutch output side (preferably a second output-side friction plate support). The first multi-plate clutch has a first friction plate group actuated by a first force transmission member, while the second multi-plate clutch has a second friction plate group actuated by a second force transmission member. The force transmission member is preferably constructed as a sheet metal part. Since the dual clutch is a parallel dual clutch, the first and second friction plate groups are staggered in the axial direction, wherein the two friction plate groups are preferably arranged to be aligned with each other in the axial direction. The first force transmission member extends through an opening in the friction plates (preferably the outer friction plates) of the second friction plate group to the first friction plate group so as to apply actuation force to it. This achieves a very compact clutch device structure. To further reduce space requirements and achieve a high level of torque uniformity when transmitting torque through the second multi-plate clutch of the dual-clutch system, the second force transmission member extends through an opening in the first force transmission member to the second friction plate group so as to apply actuation force to it. It has been proven that the first force transmission member can thus be arranged relatively close to the second friction plate group without considering the intermediate arrangement of the second force transmission member through the first force transmission member, thereby reducing the space requirements in the axial direction. This also reduces the space requirements in the radial direction, mainly because the second force transmission member through the first force transmission member does not need to extend too far outward in the radial direction to surround the first force transmission member and interact with the second friction plate group. The second force transmission member passes through the first force transmission member through an opening, so preferably a rotational drive connection is further established between the first and second force transmission members. This means that the second force transmission member largely maintains its rotational position relative to the input side friction plate of the second friction plate group, thereby ensuring a high degree of torque uniformity when transmitting torque through the second multi-plate clutch.

[0007] In a preferred embodiment of the clutch device according to the invention, the second force transmission member has an actuating finger that extends through a cavity in the first force transmission member. For this purpose, it is preferable to provide a plurality of actuating fingers spaced apart in the circumferential direction, extending through correspondingly arranged cavities in the first force transmission member. In principle, the cavity can be a side cut in the first force transmission member, but for improving the stability of the first force transmission member, it has proven advantageous that the cavity in the first force transmission member is constructed in a window shape, wherein a window-shaped cavity should be understood as a cavity with closed edges on all four sides. Furthermore, it has proven advantageous in this embodiment that the cavity is formed in the radial segment of the first force transmission member, thus ensuring that the cut is minimal, thereby improving stability, and also ensuring a shorter travel distance of the first force transmission member, thereby reducing space requirements. It is also preferable that the radial segment and the actuating finger are integrally formed; therefore, it has proven advantageous that the second force transmission member, optionally the first force transmission member, is constructed as a sheet metal part.

[0008] In an advantageous embodiment of the clutch device according to the invention, the first force transmission member has an actuating finger that extends through a cavity in the friction plates (preferably the outer friction plates) of the second friction plate group. For this purpose, the first force transmission member preferably has a plurality of actuating fingers spaced apart in the circumferential direction, extending through correspondingly arranged cavities in the friction plates of the second friction plate group. The cavities in the friction plates of the second friction plate group are preferably constructed as window-shaped cavities or side cutouts in the friction plates. It has proven particularly advantageous that the side cutouts are constructed as radial extensions of the inter-tooth space of the friction plate tooth ring at the friction plate, thereby maintaining lower manufacturing costs.

[0009] In order to apply actuating force to the first friction plate assembly in a particularly preferred embodiment of the clutch device according to the invention in a particularly preferred embodiment, the actuating finger of the first force transmission member is provided with a circumferentially surrounding pressing portion that presses against the first friction plate assembly to apply actuating force to the first friction plate assembly through the first force transmission member and the surrounding pressing portion. To ensure that the actuating finger is reliably arranged on the pressing portion, preferably, the pressing portion has a tongue protruding in the axial direction, and the actuating finger is supported radially, preferably radially inward, on the tongue. The axially protruding tongue is preferably integrally formed with the pressing portion.

[0010] In another advantageous embodiment of the clutch device according to the invention, an opening is provided in the pressing portion into which the actuating finger of the first force transmission member extends to achieve a rotational drive connection between the actuating finger and the pressing portion when necessary. The pressing portion can preferably be in rotational drive engagement with the clutch input side. To achieve particularly simple manufacturing of the pressing portion, the opening in the pressing portion is preferably created by pressing a protrusion out of the base of the pressing portion, wherein the base of the pressing portion is preferably a substantially annular disc-shaped base.

[0011] In a particularly advantageous embodiment of the clutch device according to the invention, the tongue of the pressing portion is provided with a radially protruding, preferably radially outward protruding portion, which extends into the receiving portion of the actuating finger, thereby fixing the pressing portion to the actuating finger in the axial direction. Preferably, the protrusion is formed by embossing.

[0012] In another preferred embodiment of the clutch device according to the invention, the clutch input side of the dual clutch is radially supported on a fixed housing via a support hub. Preferably, the support hub on the clutch input side is supported on the fixed housing via two radial bearings, preferably on a support tube of the fixed housing, wherein it has proven advantageous that the two radial bearings are constructed as rolling bearings. By using two radial or rolling bearings to support the support hub on the housing, the oscillation on the clutch input side is reduced, thereby reducing uneven torque transmission. This effect is further enhanced by the fact that, as is further preferred in this embodiment, the two radial bearings are radially offset from each other on the housing and / or the support hub. Because the two radial bearings are offset from each other, and preferably also spaced apart in the axial direction, a more compact arrangement of the clutch device is achieved in the area of ​​the support hub and the adjacent housing is formed. To further ensure simple assembly and disassembly, it is also preferred in this embodiment that the two radial bearings do not have any overlapping area when viewed from the axial direction.

[0013] In another particularly preferred embodiment of the clutch device according to the invention, the clutch input side includes a supply hub with fluid lines through which hydraulic fluid and / or cooling fluid and / or lubricating fluid can be supplied to the dual clutch. The fluid is preferably fuel. For this purpose, the supply hub preferably extends into an opening in the fixed housing, wherein a rotary feedthrough is particularly preferably provided between the radially outward side of the supply hub and the radially inward wall of the opening to establish a flow connection in the radial direction between the fluid lines in the supply hub and the fluid lines in the housing. Due to this rotary feedthrough arrangement, the supply hub can be arranged relatively more inward in the radial direction, so as to provide more structural space for other components of the dual clutch on the radially outward side of the supply hub or to reduce the overall radial structural dimensions. This is particularly advantageous when the dual clutch is used in combination with an electric motor to form a hybrid powertrain module for a motor vehicle.

[0014] In another preferred embodiment of the clutch device according to the invention, the clutch input side is substantially formed by an outer friction plate support having an outer friction plate support section for the outer friction plates of the first and second friction plate groups. Preferably, the outer friction plate support section has a rotational drive profile associated with the outer friction plates of the first friction plate group and a rotational drive profile associated with the outer friction plates of the second friction plate group, having the same shape and / or dimensions. Alternatively or additionally, the rotational drive profiles associated with each outer friction plate are configured such that they transition directly to each other, i.e., also referred to as the common or continuous rotational drive profiles for the outer friction plates of the first and second friction plate groups.

[0015] In another particularly preferred embodiment of the clutch device according to the invention, the rotor of the motor is arranged anti-rotationally on the radially outward side of the outer friction plate support section to create the aforementioned advantageous hybrid powertrain module for motor vehicles. The motor preferably also has a stator, but this stator is fixed to the housing and / or cannot rotate. The rotor of the motor is preferably arranged or fastened to the outer friction plate support section on the clutch input side such that the rotor is radially staggered with the two friction plate groups, and thus has at least one axial overlap area with the first and second friction plate groups, to achieve a particularly compact structure in the axial direction.

[0016] In another advantageous embodiment of the clutch device according to the invention, the clutch device further comprises a third multi-plate clutch for selectively transmitting torque between the clutch input hub and the clutch input side. Therefore, a separable clutch is preferably integrated into the clutch device, which, for example, can be operated solely by an electric motor. The third multi-plate clutch has a third set of friction plates, which can be actuated by a third force transmission element and / or arranged axially aligned with the first and second sets of friction plates to reduce structural dimensions with respect to the radial direction.

[0017] According to another preferred embodiment of the clutch device of the present invention, the outer friction plate support segment on the clutch input side of the dual clutch has a rotational drive profile associated with the outer friction plate of the third friction plate group of the third multi-plate clutch, thereby the outer friction plate support segment on the clutch input side also represents the output side of the third multi-plate clutch. Preferably, the rotational drive profile on the outer friction plate support segment on the clutch input side associated with the outer friction plate of the third friction plate group and the rotational drive profile associated with the outer friction plates of the first and second friction plate groups have the same shape and / or size. Alternatively or additionally, the rotational drive profile associated with the outer friction plate of the third friction plate group transitions directly into the rotational drive profile associated with the outer friction plates of the first and second friction plate groups, i.e., it is also referred to as the continuous or common rotational drive profile of the outer friction plates of the first and second friction plate groups and the outer friction plates of the third friction plate group.

[0018] In another advantageous embodiment of the clutch device according to the invention, the first friction plate group and the second friction plate group can be powered by the first force transmission member and the second force transmission member in the first axial direction, while the third friction plate group can be powered by the third force transmission member in the second axial direction opposite to the first axial direction.

[0019] In another preferred embodiment of the clutch device according to the invention, the third multi-plate clutch is supplied with hydraulic fluid and / or cooling fluid and / or lubricating fluid via fluid lines in the support hub on the clutch input side of the dual clutch to ensure fluid supply to the third multi-plate clutch. Preferably, in this embodiment, a rotary feedthrough is provided to establish a flow connection between the fluid lines in the support hub and the fluid lines in the fixed housing. It has also proven advantageous that the rotary feedthrough is arranged axially between the two radial bearings or rolling bearings so that the support hub is rotatably supported on the fixed housing.

[0020] In another advantageous embodiment of the clutch device according to the invention, the first and second force transmission elements, and optionally the third force transmission element, are hydraulically actuated. Preferably, the respective force transmission elements have a piston section for this purpose, which can be applied with a corresponding hydraulic pressure. Thus, it is preferred that the first force transmission element or its piston section is associated with a first pressure chamber and a first pressure balance chamber, wherein the first pressure balance chamber preferably produces so-called centrifugal oil balance. Correspondingly, the second force transmission element or its piston section is preferably associated with the second pressure chamber and the second pressure balance chamber. If the third force transmission element is also hydraulically actuated, it is preferred that the third force transmission element or its piston section is associated with a third pressure chamber and a third pressure balance chamber so that at least partial centrifugal oil balance is also achieved in this case.

[0021] In another advantageous embodiment of the clutch device according to the invention, the first pressure chamber and the second pressure balance chamber are directly defined by a common partition wall. In other words, the fluid in the first pressure chamber and the fluid in the second pressure balance chamber are directly adjacent to the opposing sides of the partition wall. Furthermore, in this embodiment, it is preferable, from the perspective of a simple and lightweight clutch device structure, that the common partition wall is fastened to the supply hub and not integrally formed with it.

[0022] In another advantageous embodiment of the clutch device according to the invention, the first force transmission member is arranged axially after the second force transmission member, and the first friction plate group is arranged axially after the second friction plate group, and / or the first pressure balance chamber is arranged axially after the second pressure balance chamber, and / or the first pressure chamber is arranged axially after the second pressure chamber. The axial arrangement of the first force transmission member after the second force transmission member does not affect those sections in the second force transmission member that extend through the opening in the first force transmission member to the second friction plate group or protrude from the opening in the first force transmission member. Furthermore, in this embodiment, it is also preferred that the second pressure balance chamber, optionally the first pressure balance chamber, is staggered radially from the second friction plate group, such that there is an axial overlap region between the second pressure balance chamber, optionally the first pressure balance chamber, and the second friction plate group, in which a relatively short structural axial length can be achieved.

[0023] In another advantageous embodiment of the clutch device according to the invention, a sensor for detecting the rotational position on the clutch input side is also provided. This sensor is preferably configured as a so-called resolver, which is generally required to control the motor. In this embodiment, it is also preferred that the sensor be fixed, for example, fastened to the housing, and detect structures rotatably disposed on the clutch input side. It has proven advantageous in terms of measurement accuracy and compact structure that the sensor is arranged axially aligned with the motor. To prevent interference from the motor, it is also preferred that an intermediate wall be arranged axially between the sensor and the motor; advantageously, this intermediate wall is arranged on the clutch input side. Thus, the partition wall can be configured, for example, as a substantially annular disc and / or arranged or fastened to the radially outward side of the outer friction plate support section. Attached Figure Description

[0024] The present invention will now be described in detail with reference to the accompanying drawings and exemplary embodiments.

[0025] Figure 1 A partial side sectional view of the clutch device in a motor vehicle transmission system is shown. Detailed Implementation

[0026] Figure 1An embodiment of a clutch device 2 according to the invention is shown, which is arranged in a motor vehicle transmission system between a drive unit 4 (shown schematically only) and a transmission 6, wherein a transmission housing 8, a first transmission input shaft 10, and a second transmission input shaft 12 are also shown in the transmission 6. Opposite axial directions 14 and 16, opposite radial directions 18 and 20, and opposite circumferential directions 22 and 24 are indicated by corresponding arrows, wherein the clutch device 2 has a rotation axis 24 extending along the axial directions 14 and 16.

[0027] The clutch assembly 2 is arranged within a wet chamber 28, which is defined in the axial direction 14 by a first clutch housing segment 30, in the radial direction 18 by a second clutch housing segment 32, and in the axial direction 16 by a transmission housing 8. Both clutch housing segments 30 and 32 and the transmission housing 8 are constructed as fixed housings or housing segments such that they do not rotate about the rotation axis 26 in the circumferential directions 22 and 24.

[0028] The clutch assembly 2 has a parallel dual clutch 34. The parallel dual clutch 34 essentially consists of a first multi-plate clutch 36 for selectively transmitting torque between the clutch input side 38 and the first clutch output side 40, and a second multi-plate clutch 42 for selectively transmitting torque between the clutch input side 38 and the second clutch output side 44. The first multi-plate clutch 36 has a first friction plate group 46 consisting of outer friction plates and inner friction plates, while the second multi-plate clutch 42 has a second friction plate group 48 consisting of outer friction plates and inner friction plates. These two friction plate groups 46, 48 are arranged to be staggered or aligned with each other in the axial directions 14, 16 to form the parallel dual clutch 34.

[0029] The clutch input side 38 is essentially composed of an outer friction plate support, a radial section 52, and a radial section 56. The outer friction plate support has a tubular outer friction plate support section 50. The radial section 52 continues the outer friction plate support section 50 in the axial direction 14 and extends inwardly in the radial direction 20 to a support hub 54 of the clutch input side 38. The radial section 56 continues the outer friction plate support section 50 in the axial direction 16 and extends inwardly in the radial direction 20 to a supply hub 58 of the clutch input side 38. The first clutch output side 40 is formed by an inner friction plate support, which is associated with the inner friction plate of the first friction plate assembly 46 and extends inwardly in the radial direction 20 to be in a rotationally driven connection with the first transmission input shaft 10. The second clutch output side 44 is formed by another inner friction plate support, which is associated with the inner friction plates of the second friction plate assembly 48 and extends inward in the radial direction 20 to be in rotational drive connection with the second transmission input shaft 12. The two transmission input shafts 10, 12 extend axially 16 through the supply hub 58 into the transmission housing 8 of the transmission 6, and the second transmission input shaft 12 is constructed as a hollow shaft through which the first transmission input shaft 10 extends. The supply hub 58 is also rotatably supported on the second transmission input shaft 12 in the radial directions 18, 20 via two radial bearings 60 (here in the form of rolling bearings).

[0030] Additionally, the clutch assembly 2 includes a third multi-plate clutch 62 configured as a disengageable clutch. The third multi-plate clutch 62 selectively transmits torque between a clutch input hub 64 and a clutch input side 38 (more precisely, the outer friction plate support section 50 of the clutch input side 38), the clutch input hub 64 being directly or indirectly connected to the output side of a drive unit 4 (preferably configured as an internal combustion engine). The third multi-plate clutch 62 includes a third friction plate group 66, the inner friction plates of which are associated with an inner friction plate support 68 anti-rotationally connected to the clutch input hub 64, while the outer friction plates of the third friction plate group 66 are associated with the outer friction plate support section 50 of the clutch input side 38. The third friction plate group 66 is arranged to be staggered or aligned with the first friction plate group 46 and the second friction plate group 48 in the axial directions 14, 16.

[0031] The outer friction plate support section 50 on the clutch input side 38 has a first rotary drive profile 70 associated with the outer friction plate of the second friction plate group 48, a second rotary drive profile 72 associated with the outer friction plate of the first friction plate group 46, and a third rotary drive profile 74 associated with the outer friction plate of the third friction plate group 66, wherein the rotary drive profiles 70, 72, and 74 have the same shape and / or dimensions. Furthermore, the first rotary drive profile 70 transitions directly into the second rotary drive profile 72 in the axial direction 14, and the second rotary drive profile 72 transitions directly into the third rotary drive profile 74 in the axial direction 14. Therefore, for the outer friction plates of all three friction plate groups 46, 48, and 66, a common, continuous rotary drive profile is created that is particularly simple to manufacture, wherein the dimensions enclosed by the three rotary drive profiles 70, 72, and 74 are the same, especially the inner and outer diameters of these rotary drive profiles are the same, and optionally the gear rings are the same.

[0032] All three multi-plate clutches 36, 42, and 62 are hydraulically actuated. Thus, the first friction plate group 46 can be actuated in the axial direction 14 by the first force transmission member 76, while the second friction plate group 48 can be actuated in the same axial direction 14 by the second force transmission member. Conversely, the third friction plate group 66 is associated with the third force transmission member 80, which can be actuated in the opposite axial direction 16. The first, second, and third force transmission members are each constructed as sheet metal parts and are movable in the axial directions 14 and 16.

[0033] The first force transmission element 76 has a piston section 82, which is associated with a first pressure chamber 84 in the axial direction 16 and with a pressure balance chamber 86 in the axial direction 14 to achieve centrifugal oil balance. An axial section 88 extends outwardly from the piston section 82 in the radial direction 18, transitioning into a radial section 90 that extends outwardly from the axial section 88 in the radial direction 18. The radial section 90 has window-like openings 92 spaced apart in the circumferential directions 22, 24; only one opening is shown in the figure. The radial section 90 transitions outwardly in the radial direction 18 to a plurality of actuating fingers 94 spaced apart in the circumferential directions 22, 24, which extend outwardly from the radial section 90 in the axial direction 14. The actuating fingers 94 extend through openings 96 in the outer friction plates of the second friction plate group 48 to reach the first friction plate group 46. Actuating fingers 94 are arranged radially in directions 18 and 20 between the outer friction plate support section 50 and the inner friction plate of the second friction plate group 48. In the illustrated embodiment, the opening 96 is window-shaped, but alternatively, the opening 96 can also be constructed as a side cut in the outer friction plate of the second friction plate group 48. In this case, it is preferred that the side cut is constructed as a radial extension of the inter-tooth space of the friction plate tooth ring of the outer friction plate. It can also be seen from the figure that the first pressure chamber 84 and the first pressure balance chamber 86 are staggered with the second friction plate group 48 in the radial directions 18 and 20.

[0034] The first force transmission element 76 is arranged in the axial direction 14 after the second force transmission element, while the first friction plate group 46 is arranged in the same axial direction 14 after the second friction plate group 48. The second force transmission element also has a piston section 98, which is associated in the axial direction 16 with the second pressure chamber 100 and in the axial direction 14 with the second pressure balance chamber 102, so as to achieve centrifugal oil balance for the second force transmission element as well. The second pressure balance chamber 102 is directly defined in the axial direction 14 by a partition wall 104 fastened to the supply hub 58, wherein the first pressure chamber 84 is also directly defined in the axial direction 16 by the partition wall 104. Therefore, the partition wall 104 can also be referred to as the common partition wall 104, to which the fluid in the pressure balance chamber 102 and the pressure chamber 84 is directly adjacent. Axial segment 106 extends outwardly to piston segment 98 in the radial direction 18. This axial segment 106 extends from piston segment 98 in the axial direction 16 to the radial segment 108 of the second force transmission member, which is preferably parallel to the radial segment 90 of the first force transmission member 76. Adjacent to radial segment 108 in the radial direction 18 are actuating fingers 110, which extend from radial segment 108 in the axial direction 14 and are spaced apart from each other in the circumferential directions 22, 24.

[0035] Actuating finger 110 is arranged on radius R1, and actuating finger 94 is arranged on radius R2, where radius R1 is much smaller than radius R2. This saves structural space outside the actuating finger 110 in the radial direction 18 and near the radial segment 90 of the first force transmission member 76 in the axial direction 16, which would otherwise be occupied by the general-purpose first force transmission member 76 in a clutch device. Nevertheless, in order for the second force transmission member to apply actuating force to the second friction plate group 48, the actuating finger 110 extends along the axial direction 14 through a window-shaped opening 92 in the radial segment 90 of the first force transmission member 76 to reach the second friction plate group 48. The free end of the actuating finger 110 towards the axial direction 14 bends in the radial direction 18, wherein the bent free end of the actuating finger 110 interacts with the end friction plate of the second friction plate group 48, which is constructed as an outer friction plate.

[0036] In the arrangement, the first pressure balance chamber 86 is arranged after the second pressure balance chamber 102 in the axial direction 14, and the first pressure chamber 84 is arranged after the second pressure chamber 100 in the same axial direction 14. The second pressure balance chamber 102 is also staggered with the second friction plate group 48 in the radial directions 18 and 20.

[0037] The actuating finger 94 of the first force transmission member 76 is provided with a pressing portion 112 arranged around the circumferential direction 22, 24. The first force transmission member 76 can cause the pressing portion 112 to press against the first friction plate assembly 46 in the axial direction 14. The pressing portion 112 has a substantially annular disc-shaped base 114, which is radially outwardly engaged into the rotational drive profile 72 of the outer friction plate support section 50 and thus in rotational drive connection with the clutch input side 38. A plurality of protrusions 116 are pressed out from the base 114, thereby creating an opening 118, such that the protrusions 116 of the pressing portion 112 protrude in the axial direction 16. The protrusions 116 and the opening 118 are arranged at intervals in the circumferential direction 22, 24 on the pressing portion 112, such that the actuating finger 94 extends into the opening 118 in the axial direction, wherein the actuating finger 94 is also supported on the protrusions 116 in the radial direction 20. Additionally, the tongue 116 is provided with a protrusion 120 that protrudes radially 18. When the pressing part 112 is fixed to the actuating finger 94 in the axial directions 14 and 16, the protrusion 120 extends into the corresponding receiving part 122 at the actuating finger 94. This creates a pressing part 112 that is particularly easy to manufacture and can be stably fixed or fixed to the first force transmission member 76 in the axial directions 14 and 16.

[0038] When the first force transmission member 76 is in a rotational driving connection with the clutch input side 38 via the pressing part 112 and / or via the outer friction plate of the second friction plate group 48, the second force transmission member can be in a rotational driving connection with the first force transmission member 76 and indirectly with the clutch input side 38 via the actuation finger 110 extending into the opening 92 in the first force transmission member 76. This allows the rotational position of the second force transmission member relative to the outer friction plate of the second friction plate group 48 to change slightly at most, so as to achieve high torque uniformity when transmitting torque through the second multi-plate clutch 42.

[0039] To achieve better torque uniformity by preventing the clutch assembly 2 from wobbling, the clutch input side 38 is rotatably supported in the radial directions 18, 20 on the fixed second clutch housing section 30 via the aforementioned support hub 54, and more specifically, is rotatably supported on the bearing section 124 of the second clutch housing section 30 via two radial bearings 126, 128 spaced apart in the axial directions 14, 16. To reliably prevent the clutch input side 38 from wobbling while simultaneously saving structural space and simplifying assembly, the two radial bearings 126, 128 are offset from each other in the radial directions 18, 20 and supported on the bearing section 124 and / or support hub 54. The radial offset between the radial bearings 126, 128 is chosen such that they do not overlap when viewed from the axial directions 14, 16. Furthermore, the radial bearings 128 are staggered from the radial sections 52 in the radial directions 18, 20 and are preferably equipped with a load capacity exceeding that of the radial bearings 126.

[0040] The third multi-plate clutch 62 or its friction plate assembly 66 is associated with the third force transmission member 80, through which the third force transmission member 80 can apply force to the third friction plate assembly 66 in the axial direction 16. For this purpose, the third force transmission member 80 is associated with the third pressure chamber 132 in the axial direction 14 and with its opposite third pressure balance chamber 134 in the axial direction 16. Fluid is supplied to the pressure chamber 132 and the pressure balance chamber 134 via fluid lines in the support hub 54 on the clutch input side 38. These fluid lines are in flow connection with the fluid lines in the bearing section 124 via a rotary feedthrough 136, wherein the rotary feedthrough 136 is arranged between two radial bearings 126, 128 in the axial directions 14, 16.

[0041] Additionally, the clutch assembly 2 is connected to the motor 138 and grounded in the wet chamber 28 to form a hybrid clutch. The motor 138 consists of a stator 140 disposed in the clutch housing section 32 and a rotor 142 disposed radially 20 inside the stator 140, wherein the rotor 142 is anti-rotationally disposed on the outer friction plate support section 50 on the radially outward side 18. The rotor 142 is disposed on the outer friction plate support section 50 about axial directions 14, 16, such that it is staggered with the first friction plate group 46 and the second friction plate group 48 in radial directions 18, 20, thereby having an axial overlap area. Preferably, as shown, the rotor 142 is also arranged to be staggered with the third friction plate group 66 in radial directions 18, 20, even if there is only a small axial overlap area between them.

[0042] To further enable proper control of the motor 138, a sensor 144 is provided to detect the rotational position of the clutch input side 38, and consequently, the rotational position of the rotor 142. This sensor 144 is fixed to the housing and detects the anti-rotational fastening of the mating fitting 146 to the clutch input side 38 or the outer friction plate support section 50. The sensor 144 is arranged axially in directions 14, 16 aligned with the motor 138 (here, the stator 140 of the motor 138). A partition wall 148, surrounding the motor 138 in the circumferential directions 22, 24, is positioned between the sensor 144 and the motor 138, which is anti-rotationally mounted on the clutch input side 38 or the outer friction plate support section 50. When the sensor 144 includes the mating fitting 146, it is also referred to as a so-called decomposer.

[0043] The aforementioned supply hub 58 on the clutch input side 38 not only supports the clutch input side on the second transmission input shaft 12 via the radial bearing 60, but also houses a fluid line 150 through which hydraulic fluid and / or cooling fluid and / or lubricating fluid can be supplied to the dual clutch 34. The fluid line 150, for example, supplies hydraulic fluid to pressure chambers 84, 100 and pressure balance chambers 86, 102, and supplies cooling fluid and / or lubricating fluid to the wet chamber 28 of the wet multi-plate clutches 36, 42. For this purpose, the supply hub 58 extends axially 16 into the opening 152 in the fixed transmission housing 8, through which the transmission input shafts 10 and 12 also extend. A rotary feed passage 154 is provided between the radially outward side of the supply hub 58 and the radially inward wall 158 of the opening 152 to establish a flow connection between the fluid lines 150 in the supply hub 58 and the fluid lines 156 in the transmission housing 8 in the radial directions 18 and 20. In this way, compared to the case where the supply hub 58 is supported on the outside of a support pipe arranged in the housing and used to supply fluid, the clutch device 2 has a more compact structure in the radial directions 18 and 20.

[0044] List of reference numerals

[0045] 2. Clutch assembly

[0046] 4 drive units

[0047] 6. Transmission

[0048] 8. Transmission housing

[0049] 10 First gearbox input shaft

[0050] 12 Second gearbox input shaft

[0051] 14 Axial direction

[0052] 16 Axial direction

[0053] 18 Radial direction

[0054] 20 Radial direction

[0055] 22 Circumferential direction

[0056] 24 Circumferential Direction

[0057] 26. Axis of rotation

[0058] 28 wet room

[0059] 30 First clutch housing section

[0060] 32 Second clutch housing section

[0061] 34 Parallel Dual Clutch

[0062] 36 First Multi-plate Clutch

[0063] 38 Clutch input side

[0064] 40 First clutch output side

[0065] 42 Second Multi-plate Clutch

[0066] 44 Second clutch output side

[0067] 46 First Friction Plate Group

[0068] 48 Second Friction Plate Group

[0069] 50 External friction plate support section

[0070] 52 Radial segment

[0071] 54 Support Hub

[0072] 56 Radial segment

[0073] 58 Supply Hubs

[0074] 60 radial bearing

[0075] 62 Third Multi-plate Clutch

[0076] 64 Clutch input hub

[0077] 66 Third Friction Plate Group

[0078] 68 Internal friction plate support

[0079] 70 The first rotation drives the contour

[0080] 72 The second rotation drives the contour

[0081] 74 The third rotation drives the contour

[0082] 76 First force transmission component

[0083] 80 Third force transmission component

[0084] 82 Piston Section

[0085] 84 First Pressure Chamber

[0086] 86 First Pressure Balance Chamber

[0087] 88 Axial Section

[0088] 90 radial segment

[0089] 92. Open air

[0090] 94 Actuating finger

[0091] 96. Open air

[0092] 98 Piston Section

[0093] 100 Second pressure chamber

[0094] 102 Second Pressure Balance Chamber

[0095] 104 partition wall

[0096] 106 Axial Section

[0097] 108 radial segments

[0098] 110 Actuation finger

[0099] 112 Pressure Section

[0100] 114 Matrix

[0101] 116 tab

[0102] 118 Air Interface

[0103] 120 protrusion

[0104] 122 Reception Department

[0105] 124 Contract Section

[0106] 126 Radial bearing

[0107] 128 radial bearing

[0108] 132 Third Pressure Chamber

[0109] 134 Third Pressure Balance Chamber

[0110] 136 Rotary Feeder Section

[0111] 138 motor

[0112] 140 stator

[0113] 142 rotor

[0114] 144 sensors

[0115] 146 pairs of accessories

[0116] 148 Intermediate wall

[0117] 150 fluid pipeline

[0118] 152 Opening

[0119] 154 Rotating Feeder Section

[0120] 156 Fluid Piping

[0121] 158 Wall

[0122] R1 radius

[0123] R2 is the radius.

Claims

1. A clutch device (2) for use in a motor vehicle transmission system arranged between a drive unit (4) and a transmission (6), comprising a parallel dual clutch (34) having a first multi-plate clutch (36) for selectively transmitting torque between a clutch input side (38) and a first clutch output side (40) and a second multi-plate clutch (42) for selectively transmitting torque between a clutch input side (38) and a second clutch output side (44), wherein, The first multi-plate clutch (36) has a first friction plate group (46) that can be actuated by a first force transmission member (76), the second multi-plate clutch (42) has a second friction plate group (48) that can be actuated by a second force transmission member, and the first force transmission member (76) extends through an opening (96) in the friction plates of the second friction plate group (48) to the first friction plate group (46). Its features are, The second force transmission element extends through the opening (92) in the first force transmission element (76) to the second friction plate group (48).

2. The clutch device (2) according to claim 1, characterized in that, The second force transmission member has an actuation finger (110) that extends through a hole (92) in the first force transmission member (76), and / or the first force transmission member (76) has an actuation finger (94) that extends through a hole (96) in the friction plate of the second friction plate group (48).

3. The clutch device (2) according to claim 2, characterized in that, The opening (92) in the first force transmission component (76) is window-shaped.

4. The clutch device (2) according to claim 3, characterized in that, The opening (92) in the first force transmission member (76) is constructed in the radial segment (90) of the first force transmission member (76).

5. The clutch device (2) according to claim 2, characterized in that, The actuating finger (94) of the first force transmission member (76) extends through the opening (96) in the outer friction plate of the second friction plate group (48).

6. The clutch device (2) according to claim 2, characterized in that, The opening (96) in the friction pad of the second friction pad group (48) is constructed as a window-shaped opening (96) or as a side cut.

7. The clutch device (2) according to claim 6, characterized in that, The opening (96) in the friction plate of the second friction plate group (48) is constructed as the radial extension portion of the inter-tooth space of the friction plate tooth ring.

8. The clutch device (2) according to any one of claims 2 to 7, characterized in that, The first force transmission member (76) has an actuating finger (94) with a pressing part (112) arranged around it in the circumferential direction (22, 24). The pressing part (112) can press against the first friction plate group (46). The pressing part (112) has a tongue (116) protruding in the axial direction (16). The actuating finger (94) is supported on the tongue (116) in the radial direction (20).

9. The clutch device (2) according to claim 8, characterized in that, The actuating finger (94) of the first force transmission member (76) extends into the opening (118) in the pressing part (112).

10. The clutch device (2) according to claim 9, characterized in that, The opening (118) in the pressing part (112) is created by pressing the tongue (116) out from the base (114) of the pressing part (112).

11. The clutch device (2) according to claim 8, characterized in that, A radially protruding protrusion (120) is provided on the tongue (116). When the pressing part (112) is fixed to the actuating finger (94) in the axial direction (14, 16), the protrusion (120) extends into the receiving part (122) at the actuating finger (94).

12. The clutch device (2) according to any one of claims 1 to 7, characterized in that, The clutch input side (38) is supported in the radial direction (18, 20) on a fixed housing (30) via a support hub (54), and / or the clutch input side (38) includes a supply hub (58) with a fluid line (150) through which hydraulic fluid and / or cooling fluid and / or lubricating fluid can be supplied to the dual clutch (34).

13. The clutch device (2) according to claim 12, characterized in that, The support hub (54) is supported by two radial bearings (126, 128).

14. The clutch device (2) according to claim 13, characterized in that, The radial bearings (126, 128) are supported on the housing (30) and / or the support hub (54) in a radial direction (18, 20) offset from each other.

15. The clutch device (2) according to claim 13, characterized in that, The radial bearings (126, 128) do not overlap when viewed in the axial direction (14, 16).

16. The clutch device (2) according to claim 12, characterized in that, The supply hub (58) extends into the opening (152) of the fixed housing (8).

17. The clutch device (2) according to claim 16, characterized in that, A rotating feed passage (154) is provided between the radially outward side of the supply hub (58) and the radially inward wall (158) of the opening (152) to establish a flow connection in the radial direction (18, 20) between the fluid line (150) in the supply hub (58) and the fluid line (156) in the housing (8).

18. The clutch device (2) according to claim 12, characterized in that, The clutch input side (38) has an outer friction plate support section (50) for the outer friction plates of the first friction plate group and the second friction plate group (46, 48).

19. The clutch device (2) according to claim 18, characterized in that, The rotational drive profile (72) associated with the outer friction plate of the first friction plate group (46) and the rotational drive profile (74) associated with the outer friction plate of the second friction plate group (48) have the same shape and / or size and / or directly transition to each other.

20. The clutch device (2) according to claim 18, characterized in that, The rotor (142) of the motor (138) is arranged anti-rotationally on the outward side in the radial direction (18) of the outer friction plate support section (50).

21. The clutch device (2) according to claim 20, characterized in that, The rotor (142) and the two friction plate groups (46, 48) are arranged radially staggered.

22. The clutch device (2) according to claim 18, characterized in that, The clutch device (2) also has a third multi-plate clutch (62) for selectively transmitting torque between the clutch input hub (64) and the clutch input side (38), the third multi-plate clutch (62) having a third friction plate group (66) capable of being actuated by a third force transmission member (80) and / or arranged in the axial direction (14, 16) aligned with the first friction plate group and the second friction plate group (46, 48).

23. The clutch device (2) according to claim 22, characterized in that, The outer friction plate support segment (50) has a rotational drive profile (74) associated with the outer friction plate of the third friction plate group (66), and the rotational drive profile (74) associated with the outer friction plate of the third friction plate group (66) and the rotational drive profiles (72, 70) associated with the outer friction plates of the first friction plate group and the second friction plate group (46, 48) have the same shape and / or size and / or directly transition to each other.

24. The clutch device (2) according to claim 22, characterized in that, The first friction plate group and the second friction plate group (46, 48) can be powered by the first force transmission member and the second force transmission member in the first axial direction (14), while the third friction plate group (66) can be powered by the third force transmission member (80) in the second axial direction (16) opposite to the first axial direction (14).

25. The clutch device (2) according to claim 22, characterized in that, The third multi-plate clutch (62) is capable of supplying hydraulic fluid and / or cooling fluid and / or lubricating fluid via fluid lines in the support hub (54) of the clutch input side (38).

26. The clutch device (2) according to claim 25, characterized in that, A rotating feed passage (136) is provided to establish a flow connection between the fluid lines in the support hub (54) and the fluid lines in the fixed housing (30).

27. The clutch device (2) according to claim 26, characterized in that, The rotating feed section (136) is arranged in the axial direction (14, 16) between two radial bearings (126, 128).

28. The clutch device (2) according to claim 22, characterized in that, The first and second force transmission components are hydraulically driven.

29. The clutch device (2) according to claim 28, characterized in that, The first force transmission component, the second force transmission component, and the third force transmission component (80) are hydraulically driven.

30. The clutch device (2) according to claim 28, characterized in that, The first force transmission element (76) is associated with the first pressure chamber (84) and the first pressure balance chamber (86), while the second force transmission element is associated with the second pressure chamber (100) and the second pressure balance chamber (102).

31. The clutch device (2) according to claim 30, characterized in that, The first pressure chamber (84) and the second pressure balance chamber (102) are directly defined by a common partition wall (104).

32. The clutch device (2) according to claim 31, characterized in that, The common partition wall (104) is fastened to the supply hub (58).

33. The clutch device (2) according to claim 30, characterized in that, The first force transmission member (76) is arranged in the axial direction (14) after the second force transmission member, and the first friction plate group (46) is arranged in the same axial direction (14) after the second friction plate group (48), and / or the first pressure balance chamber (86) is arranged in the same axial direction (14) after the second pressure balance chamber (102), and / or the first pressure chamber (84) is arranged in the same axial direction (14) after the second pressure chamber (100).

34. The clutch device (2) according to claim 33, characterized in that, The second pressure balance chamber (102) is arranged in a staggered manner with the second friction plate group (48) in the radial direction (18, 20).

35. The clutch device (2) according to claim 34, characterized in that, The second pressure balance chamber (102) and the first pressure balance chamber (86) are arranged in a staggered manner with the second friction plate group (48) in the radial direction (18, 20).

36. The clutch device (2) according to claim 20, characterized in that, A sensor (144) is provided to detect the rotational position of the clutch input side (38).

37. The clutch device (2) according to claim 36, characterized in that, The sensor (144) is arranged to be aligned with the motor (138) in the axial direction (14, 16).

38. The clutch device (2) according to claim 36, characterized in that, An intermediate wall (148) is disposed in the axial direction (14, 16) between the sensor (144) and the motor (138).

39. The clutch device (2) according to claim 38, characterized in that, The intermediate wall (148) is arranged on the clutch input side (38).

Images