Coupling device

Abstract

Coupling device (20) - comprising a first friction pack (125), a second friction pack (140) and a coupling housing (51) rotatably mounted about an axis of rotation (50), - wherein the coupling housing (51) comprises a first coupling housing part (86), at least one second coupling housing part (87) and a flange (110), - wherein the first friction pack (125) comprises at least one first friction partner (126) and at least one second friction partner (127), - wherein the second friction pack (140) comprises at least one third friction partner (145) and at least one fourth friction partner (150), - wherein the flange (110) is arranged axially between the first coupling housing part (86) and the second coupling housing part (87), - wherein the first coupling housing part (86), the flange (110) and the second coupling housing part (87) are torque-locked together,- wherein the first clutch housing part (86) comprises an axially extending first toothed section (90) and the second clutch housing part (87) comprises an axially extending second toothed section (100), - wherein the flange (110) and the first toothed section (90) at least partially define a first clutch housing interior (111) and the flange (110) and the second toothed section (100) define a second clutch housing interior (112), - wherein the first friction pack (125) is arranged in the first clutch housing interior (111) and the second friction pack (140) is arranged in the second clutch housing interior (112), - wherein the first toothed section (90) carries the first friction partner (126) and the second toothed section (100) carries the third friction partner (145), - wherein the second friction partner (127) has a first output side (65) and the fourth friction partner (150) are coupled with a second output side (70),- wherein the first clutch housing part (86) has a third toothed section (400) on its end face on a side facing the second clutch housing part (87),- wherein the second clutch housing part (87) has a fourth toothed section (425) on its end face on a side facing the first clutch housing part (86),- wherein the third toothed section (400) and the fourth toothed section (425) engage at least partially with each other and connect the first clutch housing part (86) to the second clutch housing part (87) in a torque-locking manner.

Description

The invention relates to a coupling device according to claim 1. In particular, the invention relates to a coupling device for a hybrid drive. A motor vehicle has a first drive motor, which is an electric machine, and a second drive motor, which is an internal combustion engine. The motor vehicle can be driven in a hybrid manner, i.e., by any combination of the first and / or second drive motors. For this purpose, a coupling device is provided between the drive motors and the vehicle's transmission. DE 10 2009 059 944 A1 relates to a coupling device for a hybrid-powered motor vehicle. Further prior art references are made to GB 551002 A, GB 2 108 219 A, DE 10 2013 205 045 A1, DE 10 2010 015 431 A1 and WO 99 / 00199 A1. The invention is based on the objective of providing further variants for the design of a coupling device that can also be used in a hybrid drive. The invention achieves this objective by means of the subject matter of the independent claim. Dependent claims describe preferred embodiments. According to the invention, an improved coupling device can be provided by comprising a first friction pack, a second friction pack, and a coupling housing rotatably mounted about the axis of rotation. The coupling housing comprises a first coupling housing part, at least one second coupling housing part, and a flange. The first friction pack comprises at least one first friction partner and at least one second friction partner. The second friction pack comprises at least one third friction partner and at least one fourth friction partner. The flange is arranged axially between the first coupling housing part and the second coupling housing part. The first coupling housing part, the flange, and the second coupling housing part are torque-locked to one another.The first coupling housing part comprises a first toothed section extending in the axial direction, and the second coupling housing part comprises a second toothed section extending in the axial direction. The flange and the first toothed section define a first housing interior, and the flange and the second toothed section define at least a portion of a second housing interior. The first friction pack is located in the first coupling housing interior, and the second friction pack is located in the second coupling housing interior. The first toothed section carries the first friction partner, and the second toothed section carries the third friction partner. The second friction partner is coupled to a first output side, and the fourth friction partner to a second output side. This design has the advantage of providing a particularly stable coupling device, in which the coupling housing, in particular, is exceptionally torsionally rigid. In one embodiment according to the invention, the first clutch housing part has a third toothed section on its end face, on a side facing the second clutch housing part. The second clutch housing part has a fourth toothed section on its end face, on a side facing the first clutch housing part. The third toothed section and the fourth toothed section engage with each other, at least partially, and connect the first clutch housing part to the second clutch housing part in a torque-locking manner. In a further embodiment, the third toothed section has at least one axially extending claw, and the fourth toothed section has at least one axially extending recess. In the circumferential direction, the recess is at least congruent with the claw. The claw engages in the recess. In this way, a positive-locking connection is provided between the first coupling housing part and the second coupling housing part. In a further embodiment, the claw has a claw end face on an end face facing the second coupling housing part. The claw end face preferably extends in a first plane of rotation. The recess has a recess base. Preferably, the recess base extends in a second plane of rotation. The recess base and the claw end face are arranged axially offset from each other. In a further embodiment, the flange has an external toothing with at least one tooth on its radial outer side. The tooth engages in the recess and is arranged axially between the base of the recess and the claw end face. In a further embodiment, the coupling housing has a clamping device. The clamping device is designed to provide a clamping force acting in the axial direction. The clamping force connects the first coupling housing part to the flange and the second coupling housing part by means of a frictional connection. In a further embodiment, the third toothed section has a further claw. The fourth toothed section has a further recess. This further recess corresponds, at least in the circumferential direction, to the further claw. The further claw engages in this further recess. The further claw has a further claw end face on an end face facing the second coupling housing part. The further recess has a further recess base. Preferably, the further claw end face is arranged in a third plane of rotation, and the further recess base is arranged in a fourth plane of rotation. The further recess base and the further claw end face are arranged axially spaced from each other or are axially abutting each other. In another embodiment, the second claw has a different axial extension compared to the first claw. In a further embodiment, the coupling device comprises an element. This element has a further external toothing with at least one additional tooth. The additional tooth engages in the further recess and is arranged axially between the base of the further recess and the further claw end face. In a further embodiment, the coupling device comprises a third friction pack, a first input side, and a second input side. The third friction pack has at least a fifth friction partner and at least a sixth friction partner. The fifth friction partner is coupled to the first input side, and the sixth friction partner to the second input side. The first input side can be connected to the first drive motor, and the second input side to the second drive motor. The coupling housing is coupled to the second input side. The invention is explained in more detail below with reference to the figures. Figure 1 shows a semi-longitudinal section through a drive unit; Figure 2 shows a perspective longitudinal section through a clutch housing of the drive unit shown in Figure 1 according to a first embodiment; Figure 3 shows a perspective longitudinal section through a clutch housing according to a second embodiment; Figure 4 shows a perspective longitudinal section through a clutch housing according to a third embodiment; and Figure 5 shows a perspective longitudinal section through a clutch housing according to a fourth embodiment. Fig. 1 shows a semi-longitudinal section through a drive device 10. The drive unit 10 comprises a housing 15, a coupling unit 20, and a first drive motor 25. The housing 15 defines an interior space 30. The interior space 30 can be filled with a coolant 35. The first drive motor 25 and the coupling device 20 are arranged in the interior of the housing 30. The first drive motor 25 is designed as an electric machine. The first drive motor 25 comprises a stator 40 and a rotor 45 and is rotatably mounted about an axis of rotation 50. The stator 40 is fixedly connected to the housing 15. Preferably, the first drive motor 25 is of the internal rotor type, such that the stator 40 is arranged radially outside the rotor 45. It is further preferred that the stator 40 has at least one magnet coil and the rotor 45 has at least one permanent magnet. The first drive motor 25 is arranged radially outside the coupling device 20. The coupling device 20 comprises a coupling housing 51, a first input side 55, a second input side 60, a first output side 65, and a second output side 70. The first input side 55, the second input side 60, as well as the first output side 65 and the second output side 70 are rotatably arranged about the axis of rotation 50. Furthermore, the coupling device 20 comprises a first coupling 75, a second coupling 80, and a third coupling 85. The first coupling 75 is located between the first input side 55 and the first output side 65. The second coupling 80 is located between the second input side 60 and the second output side 70. The third coupling 85 is arranged between the first input side 55 and the second input side 60. In this embodiment, the couplings 75, 80, and 85 are arranged radially at the same level. The first coupling 75 is arranged axially between the third coupling 85 and the second coupling 80. The rotor 45 is arranged axially overlapping the couplings 75, 80, 85. An axial overlap is defined as the rotor 45 and the couplings 75, 80, 85 being projected into a plane in which the axis of rotation 50 is located, and thus overlapping. This means that the couplings 75, 80, 85 and the rotor 45 share a common installation space. The clutch housing 51 is essentially cylindrical in shape and rotatably mounted about the axis of rotation 50. The clutch housing 51 comprises a first clutch housing part 86 and a second clutch housing part 87. The first clutch housing part 86 is assigned to the first clutch 75 and comprises a first toothed section 90 extending in an axial direction with a first internal toothing 95. The second clutch housing part 87 is associated with the second clutch 80. The second clutch housing part 87 comprises a second toothed section 100 extending in the axial direction with a second internal toothing 105. A flange 110 of the clutch housing 51 is arranged axially between the first clutch housing part 86 and the second clutch housing part 87. The flange 110 is torque-locked to the first clutch housing part 86 and the second clutch housing part 87. Furthermore, the first clutch housing part 86 and the second clutch housing part 87 are torque-locked to each other. The flange 110 together with the first toothed section 90 defines a first clutch housing interior 111 and with the second toothed section 100 a second clutch housing interior 112. The first clutch 75 comprises a first lamellar carrier 115. The first lamellar carrier 115 has a first external toothing 120. The first lamellar carrier 115 radially delimits the first clutch housing interior 111 on its inner side. The clutch housing interior 111 is designed with an annular gap. A first friction pack 125 is arranged in the first clutch housing interior 111. The first friction assembly 125 comprises a first friction partner 126 and a second friction partner 127. The friction partners 126, 127 are preferably arranged alternately in a stack. In this exemplary embodiment, the first friction partner 126 is designed as a friction plate without a lining, and the second friction partner 127 is designed as a lining plate. Other configurations of the first and / or second friction partner 126, 127 are also conceivable. The first friction partner 126 is torque-locked to the first clutch housing part 86 via the first internal toothing 95. The second friction partner 127 is torque-locked to the first plate carrier 115 via the first external toothing 120. The second clutch 80 comprises a second lamellar carrier 130 with a second external toothing 135. The second lamellar carrier 130 radially delimits the inner space of the second clutch housing 112 and is designed with an annular gap. A second friction pack 140 of the second clutch 80 is arranged in the inner space of the second clutch housing 112. The second friction assembly 140 has a third friction partner 145 and a fourth friction partner 150. The third friction partner 145 is designed as a lamella without a coating, while, by way of example, the fourth friction partner 150 is designed as a coating lamella. Of course, other configurations of the third and fourth friction partners 145, 150 are also conceivable. The third clutch 85 has a third friction pack 160 with a fifth friction partner 165 and a sixth friction partner 170. The fifth friction partner 165 is designed as a friction plate without a lining, while the sixth friction partner 170 is preferably designed as a lining plate. The fifth and sixth friction partners 165, 170 can also be designed differently. A support element 175 is provided axially between the first friction pack 125 and the third friction pack 160. This support element is fixed in its axial position and is connected to the first clutch housing part 86. The third friction pack 160 is arranged radially overlapping the first and second friction packs 125 and 140. Radial overlap is defined as the fact that when the friction packs 125, 140, and 160 are projected into a plane perpendicular to the axis of rotation 50, they at least partially overlap in that plane. The fifth friction partner 165 is torque-locked to the first clutch housing part 86 via the first internal toothing 95. The second input side 60 includes a coupling rotor 180. The coupling rotor 180 is torque-locked to the sixth friction partner 170 of the third friction pack 160. The coupling device 20 further comprises a first connecting element 185 and a second connecting element 190. The connecting element 185, 190 is preferably disc-shaped. The connecting element 185, 190 extends radially from approximately the first coupling housing part 86 and the second coupling housing part 87 to the level of the rotor 45 of the electric machine 25. The first connecting element 185 is preferably connected to the first coupling housing part 86 and the rotor 45 by means of a positive-locking connection, in particular by means of a rivet connection, so that the first input side 55 is connected to the rotor 45 of the electric machine 25. Similarly, the second connecting element 190 connects the second coupling housing part 87 to the rotor 45. The second connecting element 190 is mirror-symmetrical with respect to the flange 110 and connects the second coupling housing part 87 to the rotor 45 in a torque-locking manner.One of the two connecting elements 185, 190 can also be dispensed with, since the first coupling housing part 86 is also torque-locked to the second coupling housing part 87 via the flange 110. The first clutch plate carrier 115 is radially connected on its inner side to the first output side 65. The first output side 65 is connected to a first transmission input shaft 191 of a dual transmission. The second clutch plate carrier 130 is connected to the second output side 70. The second output side 70 is connected to a second transmission input shaft 192 of the dual transmission. The dual transmission typically couples each of the transmission input shafts 191, 192 to a common output shaft, which ultimately drives a drive wheel of the motor vehicle, by means of a separate pair of gears. To select a gear in the dual transmission, the first clutch 75 and / or the second clutch 80 is engaged, while the other clutch 75, 80 may remain disengaged. Preferably, the dual transmission comprises several pairs of gears, of which only one is engaged at any given time. To open and close the first clutch 75, the first clutch 75 comprises a first actuating device 193. Furthermore, the second clutch 80 comprises a second actuating device 195, and the third clutch 85 comprises a third actuating device 200. Preferably, all actuating devices 193, 195, 200 operate hydraulically and are each configured to exert an axial actuating force on the respective friction pack 120, 140, 160 associated with the actuating device 193, 195, 200, such that the friction partners 126, 127, 145, 150, 165, 170 are pressed axially against each other to generate a frictional connection and a torque between the friction partners 126, 127, 145, 150, 165, 170. to transfer. Preferably, the friction partners 126, 127, 145, 150, 165, 170 are pressed together between the associated actuating device 193, 195, 200 and an axial abutment.The axial support for the first friction pack 125 can be formed by the support element 175. Furthermore, for the second friction pack 140, the axial support can be formed by a radially extending section of the second lamellar carrier 100, and for the third friction pack 160 by a radially extending section of the first lamellar carrier 90. It is also preferred that the hydraulic actuating devices 193, 195, 200 can be actively controlled individually and / or together by selectively introducing or releasing pressurized pressure medium into or out of a hydraulic pressure chamber of the actuating device 191, 195, 200 by means of a valve or a pump. Alternatively, for example, a centrifugal oil-controlled actuating device 193, 195, 200 can also be provided.The axial actuating forces of the actuating device 193, 195, 200 are preferably supported within the coupling device 20, so that no resultant forces need to be supported outwards. The second input side 60 can be torque-locked to a second drive motor 205, which is, for example, an internal combustion engine. This makes the drive unit 10 particularly suitable for use in a motor vehicle's powertrain. The motor vehicle can preferably be operated in hybrid mode, i.e., alternatively by the first drive motor 25, the second drive motor 205, or both drive motors 25, 205 together. If the second drive motor 205, preferably the internal combustion engine, is to be used, the third clutch 85 is closed by the third actuating device 200. This torque-locks the second input side 60 to the first input side 55. If the first drive motor 25, i.e., the electric motor, is to be used, it is typically electrically controlled to generate torque.Both drive motors 25 and 205 can supply both positive and negative torque to the drive unit 10. The first drive motor 25 can also absorb kinetic energy from the drivetrain and convert it into electrical energy, which can be temporarily stored, for example, in an energy storage device. Due to its compact design, the drive unit 10 is particularly suitable for installation at the front of the vehicle, transversely. The couplings 75, 80, 85 and the first drive motor 25 are arranged by way of example in the common housing interior 30, so that coolant 35 can flow to the couplings 75, 80, 85 as well as to the first drive motor 25. The coolant 35 can also be used as the working medium for the actuating device 191, 195, 200. The clutches 75, 80, 85 are exemplary wet-running types and can each be designed as single-disc or multi-disc clutches. Preferably, the first clutch 75 and the second clutch 80 are of the multi-disc type to allow sensitive opening and closing of the torque flow between the first input side 55 and the first output side 65 and / or the second output side 70. The third clutch 85 can be of the single-disc type, as shown in Fig. 1. Alternatively, the third clutch 85 can be of the multi-disc type. The third clutch 85 can also be designed as a switching clutch that is operated with minimal slippage. Fig. 2 shows a perspective longitudinal section through the clutch housing 51 of the drive device 10 shown in Fig. 1 according to a first embodiment. The flange 110 is arranged axially between the first coupling housing part 86 and the second coupling housing part 87. The coupling housing 51 has a clamping device 300. The clamping device 300 comprises at least one screw element 305, a first through-hole 310 arranged in the first coupling housing part 86, a second through-hole 315 arranged in the flange 110, and a threaded bore 320 arranged in the second coupling housing part 87. The screw element 305 is guided through the through-holes 310 and 315. The screw element 305 engages in the threaded bore 320. The screw element 305 and the threaded bore 320 are designed as a pre-tensioned screw connection, so that the clamping device 300 provides a clamping force FS acting in an axial direction, so that the first coupling housing part 86, the flange 110 and the second coupling housing part 87 are positively connected to each other. Fig. 3 shows a perspective longitudinal section through a coupling housing 51 according to a second embodiment. The coupling housing 51 is designed similarly to that described in Figures 1 and 2. In contrast, the first coupling housing part 86 has a third toothed section 400 on its end face facing the second coupling housing part 87. The third toothed section 400 has several first claws 405 spaced apart from one another in the circumferential direction and extending axially. The first claws 405 are arranged on a circular path around the axis of rotation 50. Each of the first claws 405 preferably has a first claw end face 410 on an end face facing the second coupling housing part 87. The first claw end face 410 is preferably arranged in a first plane of rotation with respect to the axis of rotation 50. Furthermore, each first claw 405 has a first claw side surface 415 and a second claw side surface 420.The claw side surfaces 415, 420 are preferably arranged parallel to each other and preferably parallel to the axis of rotation 50. Two first claws 405 arranged adjacent to each other in the circumferential direction form a first recess 421 with a first tooth base 422. Furthermore, the second coupling housing part 87 has a fourth toothed section 425 on its end face, on a side facing the first coupling housing part 86. The fourth toothed section 425 has at least one second recess 430. Preferably, in this embodiment, several second recesses 430 are provided, the number of which corresponds to the number of first claws 405. Two adjacent second recesses 430 arranged circumferentially form a second claw 431. The second recess 430 is formed circumferentially corresponding to the associated first claw 405 and extends axially, having a second recess base 435 which is arranged in a second plane of rotation relative to the axis of rotation 50. The second recess base 435 and the first claw end face 410 are axially offset from each other. Furthermore, the second recess 430 has a first recess side surface 440 and a second recess side surface 445. The first claw 405 engages in its corresponding second recess 430. The first recess side surface 440 rests against the first claw side surface 415, and the second recess side surface 445 rests against the second claw side surface 410. A torque exchange takes place between the recess side surfaces 440, 445 and the claw side surfaces 405, 410 between the first and second coupling housing parts 86, 87, so that they are positively connected in addition to the frictional connection. This allows a particularly high torque to be exchanged between the first and second coupling housing parts 86, 87. The flange 110 has a third external toothing 450 on its radial outer side. This third external toothing 450 preferably has several first teeth 455 spaced apart circumferentially. The number of first teeth 455 preferably corresponds to the number of jaws 405. Each first tooth 455 is formed corresponding to its associated second recess 430, at least circumferentially. The first tooth 455 engages in its associated second recess 430. The first tooth 455 is axially positioned between the base of the second recess 435 and the first jaw end face 410. Preferably, the first tooth 455 has a width corresponding to the axial distance between the first jaw end face 410 and the base of the second recess 435. This allows the flange 110 to be arranged without play between the two coupling housing parts 86, 87. The second claw 431 engages in the first recess 421, which is arranged axially opposite it. The second claw 431, with a second claw end face 460 facing the first coupling housing part 86, rests against the base 422 of the first recess 421. Fig. 4 shows a perspective longitudinal section through a coupling housing 51 according to a third embodiment. The clutch housing 51 is designed similarly to the clutch housing 51 shown in Fig. 3. In contrast, the support element 175 additionally has a fourth external toothing 500 on its radial outer side, with several second teeth 505 arranged circumferentially spaced apart from one another. The second tooth 505 engages in the first recess 421. The second tooth 505 is arranged correspondingly to its respective first recess 421. In this embodiment, the second claw 431 is axially shorter than in the embodiment shown in Fig. 3, for the arrangement of the support element 175 axially between the two clutch housing parts 86, 87. This design has the advantage that actuating forces from the first friction pack 125 can be reliably supported via the clutch housing parts 86, 87 by the support element 175. Furthermore, compared to Fig. 2, the clamping device 300 is arranged circumferentially offset, so that the through-hole 310, 315 in the flange 110 shown in Fig. 2 can be omitted. Instead, the second through-hole 315 is arranged in the support element 175, so that this is additionally force-fitted to the coupling housing part 86, 87 between the second claw end face 460 and the second recess base 422. Of course, the clamping device 300 can also be configured as shown in Fig. 2. Fig. 5 shows a semi-longitudinal section through a clutch housing 51 according to a fourth embodiment. The clutch housing 51 is similar to the clutch housing 51 shown in Fig. 4. In contrast, the third toothed section 400 has a third claw 600 in addition to the first claw 405. The third claw 600 is arranged circumferentially spaced from the first claw 405. The first recess 421 is arranged between the first claw 405 and the third claw 600. In this embodiment, the first claw 405 and the third claw 600 are identical in the circumferential direction. However, the third claw 600 is axially longer than the first claw 405. In this embodiment, the first claw 405 and the third claw 600 are arranged alternately in the circumferential direction. Other arrangements, for example two third claws 600, can also be arranged side by side in the circumferential direction.It is also conceivable that the third claw 600 and the first claw 405 are arranged to lie adjacent to each other in the circumferential direction, so that the arrangement of the first recess 421 between the first claw 405 and the third claw 600 is omitted. This results in a stepped claw. The third claw 600 has a third claw end face 605. The third claw end face 605 is arranged in a third plane of rotation relative to the axis of rotation 50. The third claw end face 605 is axially offset from the first claw end face 410. The second claws 431 of the fourth gear section 425 are identical to each other, with, for example, all second claw end faces 460 terminating in a common second plane of rotation. The fourth gear section 425 has a third recess 610 corresponding to the third claw 600. The third claw 600 engages in the third recess 610, so that the first clutch housing part 86 is also torque-locked to the second clutch housing part 87 via the third claw 600 and the third recess 610. The third recess 610 has a third recess base 615. The third recess base 615 is arranged in a fourth plane of rotation relative to the axis of rotation 50. The third recess base 615 and the third claw end face 605 are axially offset from each other. The clutch housing 51 has, in addition to the clutch housing 51 shown in Fig. 5, a further support element 620. This further support element 620 is designed similarly to the support element 175. In contrast, the further support element 620 has a fifth external toothing 625 on its radial outer side. The fifth external toothing 625 preferably has several circumferentially spaced third teeth 630. The third teeth 630 are formed corresponding to the third recess 610 and engage in the third recess 610, so that the further support element 620 is torque-locked to the clutch housing parts 86, 87. The axial width of the third tooth 630 corresponds to a distance between the base of the third recess 615 and the third claw end face 605. The further support element 620 is designed to support the actuating force for the first friction package 125 on the second clutch housing part 87 radially on the outside via the third tooth 630. By providing the additional support element 620, additional installation space can be created to the right of the additional support element 620, for example to accommodate another coupling (not shown) with an additional friction pack. This additional coupling could, for example, serve as a drive for a power take-off shaft. It would also be conceivable to use the additional friction pack of the additional coupling to switch a third drive motor. The design of the coupling devices 20 of the drive unit 10 described above has the advantage of enabling reliable bearing of the rotor 45 of the first drive motor 25. Furthermore, the third and fourth gear sections 400, 425 provide a means for fixing the flange 110 and / or the support elements 175, 620. Additionally, the coolant 35 can be guided radially outwards from the friction pack 125, 140, 160 via the third and fourth gear sections 400, 425. Moreover, the actuating forces for switching the friction packs 125, 140, 160 are supported internally within the coupling housing 51, so that no further support of the actuating forces is necessary. Furthermore, the arrangement of the third coupling 85 in the housing interior 30 ensures reliable cooling of the third coupling 85. Furthermore, it is pointed out that the third clutch 85 and the support element 175 can be dispensed with, so that the clutch housing 51 can also be used to accommodate a double clutch consisting of the first and second clutch 75, 80. It is also noted that the features of the drive devices 10 shown in Fig. 1, Fig. 2, Fig. 3, Fig. 4 to Fig. 5 can be combined with each other. Reference symbol list 10 Drive unit 15 Housing 20 Coupling unit 25 First drive motor 30 Housing interior 35 Coolant 40 Stator 45 Rotor 50 Shaft of rotation 51 Coupling housing 55 First input side 60 Second input side 65 First output side 70 Second output side 75 First coupling 80 Second coupling 85 Third coupling 86 First coupling housing part 87 Second coupling housing part 90 First gear section 95 First internal gear 100 Second gear section 105 Second internal gear 110 Flange 111 First coupling housing interior 112 Second coupling housing interior 115 Third friction plate carrier 120 First external gear 125 First friction pack 126 First friction partner 127 Second friction partner 130 Fourth friction plate carrier 135 Second external gear 140 Second friction pack 145 Third friction partner 150 fourth friction partner 160 third friction package 165 fifth friction partner 170 sixth friction partner 175 support element 180 rotor 185 first connecting element 190 second connecting element 191first transmission input shaft 192 second transmission input shaft 193 first actuating device 195 second actuating device 200 third actuating device 205 second drive motor 300 clamping device 305 screw element 310 first through hole 315 second through hole 400 third tooth section 405 first claw 410 first claw end face 415 first claw side face 420 second claw side face 421 first recess 422 first recess base 425 fourth tooth section 430 second recess 431 second claw 435 second recess base 440 first recess side face 445 second recess side face 450 third external tooth 455 first tooth 460 second claw end face 500 fourth external tooth 505 second tooth 600 third claw 605 third claw face 610 third recess 615 third recess base 620 further support element 625 fifth external toothing 630 third tooth

Claims

Coupling device (20) - comprising a first friction pack (125), a second friction pack (140) and a coupling housing (51) rotatably mounted about an axis of rotation (50), - wherein the coupling housing (51) comprises a first coupling housing part (86), at least one second coupling housing part (87) and a flange (110), - wherein the first friction pack (125) comprises at least one first friction partner (126) and at least one second friction partner (127), - wherein the second friction pack (140) comprises at least one third friction partner (145) and at least one fourth friction partner (150), - wherein the flange (110) is arranged axially between the first coupling housing part (86) and the second coupling housing part (87), - wherein the first coupling housing part (86), the flange (110) and the second coupling housing part (87) are torque-locked together,- wherein the first clutch housing part (86) comprises an axially extending first toothed section (90) and the second clutch housing part (87) comprises an axially extending second toothed section (100), - wherein the flange (110) and the first toothed section (90) at least partially define a first clutch housing interior (111) and the flange (110) and the second toothed section (100) define a second clutch housing interior (112), - wherein the first friction pack (125) is arranged in the first clutch housing interior (111) and the second friction pack (140) is arranged in the second clutch housing interior (112), - wherein the first toothed section (90) carries the first friction partner (126) and the second toothed section (100) carries the third friction partner (145), - wherein the second friction partner (127) has a first output side (65) and the fourth friction partner (150) are coupled with a second output side (70),- wherein the first clutch housing part (86) has a third toothed section (400) on its end face on a side facing the second clutch housing part (87),- wherein the second clutch housing part (87) has a fourth toothed section (425) on its end face on a side facing the first clutch housing part (86),- wherein the third toothed section (400) and the fourth toothed section (425) engage at least partially with each other and connect the first clutch housing part (86) to the second clutch housing part (87) in a torque-locking manner. Coupling device (20) according to claim 1, - wherein the third toothed section (400) has at least one claw (405) extending in the axial direction and the fourth toothed section (425) has at least one recess (430) extending in the axial direction, - wherein the recess (430) is formed corresponding to the claw (405) at least in the circumferential direction, - wherein the claw (405) engages in the recess (430). Coupling device (20) according to claim 2, - wherein the claw (405) has a claw end face (410) on an end face facing the second coupling housing part (87), - wherein the claw end face (410) preferably extends in a first plane of rotation, - wherein the recess (430) has a recess base (435), - wherein the recess base (435) preferably extends in a second plane of rotation, - wherein the recess base (435) and the claw end face (410) are arranged axially offset from each other. Coupling device (20) according to claim 3, wherein the flange (110) has an external toothing (450) with at least one tooth (455) on its radial outer side, wherein the tooth (455) engages in the recess (430) and is arranged axially between the recess base (435) of the claw end face (410). Coupling device (20) according to one of claims 1 to 4, - wherein the coupling housing (51) comprises a clamping device (300), - wherein the clamping device (300) is configured to provide a clamping force (FS) acting in an axial direction, - wherein the clamping force (FS) frictionally connects the first coupling housing part (86) to the flange (110) and the second coupling housing part (87). Coupling device (20) according to one of claims 2 to 5, wherein the third toothed section (400) has a further claw (600), wherein the fourth toothed section (425) has a further recess (610), wherein the further recess (610) is formed corresponding at least in the circumferential direction to the further claw (600), wherein the further claw (600) engages in the further recess (610), wherein the further claw (600) has a further claw end face (605) on an end face facing the second coupling housing part (87) and the further recess (610) has a further recess base (615), wherein preferably the further claw end face (605) is arranged in a third plane of rotation and the further recess base (615) is arranged in a fourth plane of rotation, wherein the further recess base (615) and the further claw end face (605) are arranged axially spaced apart from each other or are in contact with each other. Coupling device (20) according to claim 6, wherein the further claw (600) has a different extension in the axial direction to the claw (405). Coupling device (20) according to claim 6 or 7, comprising an element (175, 620), wherein the element (175, 620) has a further external toothing (625) with at least one further tooth (630), wherein the further tooth (630) engages in the further recess (610) and is arranged axially between the further recess base (615) and the further claw end face (605). Coupling device (20) according to one of claims 1 to 8, comprising a third friction pack (160), a first input side (55) and a second input side (60), wherein the third friction pack (160) comprises at least a fifth friction partner (165) and at least a sixth friction partner (170), wherein the fifth friction partner (165) is coupled to the first input side (55) and the sixth friction partner (170) is coupled to the second input side (60), wherein the first input side (55) is connectable to a first drive motor (25) and the second input side (60) is connectable to a second drive motor (205), wherein the coupling housing (51) is coupled to the second input side (60).

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