Coupling device for an electric or hybrid vehicle

Abstract

The invention relates to a coupling device (1) for an electric or hybrid vehicle comprising: - an input (2) for connection to a motor and for obtaining an input torque, - an output (3) for connection to at least one vehicle wheel and for delivering a torque, - a first coupling device (4) for separating and establishing a first power transmission path from the input (2) to the output (3), - a second coupling device (5) for separating and establishing a second power transmission path from the input (2) to the output (3), - a switching device (6) for selecting the power transmission path, - wherein the first coupling device (4) is arranged and designed to convert an incoming tangential force resulting from an input torque introduced at the input (2) into an outgoing tangential force and an axial force in order to pre-position the second coupling device (5) for establishing the second force transmission path.

Description

[0001] The present invention relates to a coupling device for an electric or hybrid vehicle.

[0002] In electric and hybrid vehicles, it is necessary in certain driving situations to decouple one or more wheels from the drive. Various state-of-the-art solutions exist for this. However, these are slow to operate and lack the necessary switching speed for engaging or disengaging.

[0003] As prior art, reference is made to EP 3 543 554 B1 and DE 697 29 313 T2, each of which discloses a coupling device.

[0004] Therefore, it is an object of the present invention to provide a coupling device for an electric or hybrid vehicle which overcomes the aforementioned disadvantages.

[0005] This problem is solved by the features of the independent patent claim. Further advantageous developments are the subject of the dependent claims.

[0006] The present invention comprises a coupling device for an electric or hybrid vehicle.

[0007] The coupling device has an input for connection to a motor and / or for receiving an input torque.

[0008] Furthermore, the coupling device comprises an output for connection to at least one vehicle wheel or to a vehicle axle and for outputting a torque.

[0009] The output or a part thereof, e.g., a hub, can be designed to be movable in the axial direction, so that an axial force leads to an axial displacement of the output or a part of the output. The output or a part of the output can be displaced in or against an axial direction. The output or a part of the output can also be subjected to a spring force for resetting, either against or in an axial direction. The spring force can be generated by a spring, e.g., a disc spring.

[0010] The axial direction may be oriented in the direction of the axis of rotation of the coupling device.

[0011] Furthermore, the coupling device comprises a first coupling device for disconnecting and establishing a first power transmission path from the input to the output. Thus, the first coupling device can be configured and designed to establish and disconnect a power transmission via the first power transmission path.

[0012] The coupling device further comprises a second coupling device for disconnecting and establishing a second power transmission path from the input to the output. In other words, the second coupling device can be configured and designed to establish or disconnect power transmission via the second power transmission path. The second coupling device can also be configured and designed to transmit an incoming tangential force resulting from an input torque introduced at the input, e.g., "only," as an outgoing tangential force or torque to the output.

[0013] Thus, the first and second clutch devices can be arranged and designed to transmit the tangential force or the input torque received at the input to the output.

[0014] In addition, the clutch device has a switching device for selecting the power transmission path and / or for activating and deactivating the first and second clutch devices or their power transmission paths. The switching device can be designed to be displaceable in and / or counter to the axial direction. The switching device can be hollow-cylindrical or have a ring gear. Furthermore, the switching device can be designed in the form of a sliding sleeve, which can be displaced back and forth in the axial direction from the radial outside using an actuator.

[0015] The first clutch device is also configured and designed to convert or transform an incoming tangential force, resulting from an input torque introduced at the input, into an outgoing tangential and an axial force in order to pre-position the second clutch device to establish the second power transmission path. This conversion / transformation therefore serves to pre-position the second clutch device so that it can be available for power transmission. This is because the pre-positioning allows, for example, the switching device to be easily displaced with little effort in such a way that it prepares the second power transmission path. As a result of this preparation, the second power transmission path is ready to transmit torque.

[0016] It can also be noted that pre-positioning or pre-positioning can serve to align the teeth of a gearwheel of the second clutch device and the teeth, e.g. on an inner side or on an inner circumferential surface, of the switching device. During alignment, the teeth of the second clutch device and the switching device can be positioned relative to one another in such a way that the switching device can be axially displaced with little effort. This can produce engagement between the teeth of the switching device and the teeth of the second clutch device. In this case, it is possible that the tooth flanks of the teeth of the switching device and the second clutch device do not yet touch or make contact.

[0017] Furthermore, the first clutch device can be configured and designed such that the axial force causes a relative rotation between the input and output or between the second clutch device and the switching device, thereby eliminating any play between the second clutch device and the switching device. In other words, the first clutch device can be configured and designed such that the axial force causes a relative rotation between the input and output or between the second clutch device and the switching device, thereby eliminating any play between a toothing of a gearwheel of the second clutch device and a toothing, e.g., on an inner side or on an inner circumferential surface, of the switching device.By eliminating the backlash, a portion of the incoming tangential force can be redistributed from the first clutch device to the second clutch device, thus protecting the first clutch device from overload. Furthermore, by eliminating the backlash, a large portion of the incoming tangential force or a large portion of the input torque can be redistributed to the second clutch device, thus also protecting the first clutch device from overload or largely relieving the load. A large portion can be greater than 50% of the total incoming torque or input torque.

[0018] Furthermore, the second clutch device and the switching device can each comprise a toothing configured such that they have a certain amount of play relative to one another in the circumferential direction. This allows the toothing of the switching device to engage the toothing of the second clutch device with minimal effort for axial displacement of the switching device. In this case, it is possible for the tooth flanks of the toothing of the switching device and the second clutch device to not yet touch or make contact.

[0019] By means of the first and second coupling devices, the coupling device can realize a first, second and third state.

[0020] In the first state, an input torque can be transmitted from the input to the output, wherein the first power transmission path can be realized by means of the first clutch device.

[0021] Furthermore, in the first state, the switching device can be switched or moved in the axial direction such that the first clutch device transmits a force or a torque from the input to the output and / or that clamping bodies of the first clutch device are aligned such that the clamping bodies can transmit a force or a torque / input torque from the input to the output.

[0022] More specifically, with the help of the first clutch device or its clamping elements, the input torque or the tangential force resulting from the input torque introduced at the input can be divided into a tangential and an axial force component, or into an outgoing tangential force and an axial force. This is because the clamping elements of the first clutch device can be arranged at an angle or slope between the input and output. As a result, a large portion of the input torque can be transmitted from the input to the output via the first clutch device.

[0023] In the present description, “oblique” can be understood as inclined to the axial direction and / or as inclined to the tangential direction of the coupling device, so that, for example, the angle between a clamping body of the first coupling device or its web and the tangential and / or the axial direction is less than or smaller than 90 degrees.

[0024] Furthermore, in the first state, the second clutch device is prepared or pre-positioned with the aid of the first clutch device, so that the shifting device can be moved in the axial direction with little effort.

[0025] Because of a play or a clearance fit between the input and output or between the second clutch device and the switching device, the switching device can be displaced in the axial direction with very little switching force so that the switching device connects the input to the output via the second power transmission path.

[0026] Consequently, the first coupling device and the switching device can be prepared or pre-positioned in the circumferential direction for a connection via the switching device.

[0027] In the second state, the input torque may be increased, equal, or similar to the first state. Similar to the first state, the entire input torque can be transmitted from the input to the output by the first clutch device or its sprags. Consequently, the first power transmission path can be realized in the second state just as in the first state.

[0028] However, in the second state, the switching device can be moved in the axial direction with little effort, so that the second power transmission path is prepared for the power and / or torque transmission.

[0029] In other words, in the second state, the switching device can be switched or moved in the axial direction such that the first clutch device transmits a force from the input to the output and / or the clamping bodies of the first clutch device are aligned such that they can transmit a force from the input to the output. Furthermore, in the second state, the switching device can be switched or moved in the axial direction such that the second clutch device can also transmit a force from the input to the output.

[0030] In order to enable the switching device to be moved or displaced with minimal effort, a clearance or a loose fit between the second clutch device and the switching device can be utilized in the second state. Because the first clutch device can be configured and designed such that the axial force causes relative rotation between the input and output or between the second clutch device and the switching device, the clearance or a loose fit between a toothing of a gearwheel of the second clutch device and a toothing, e.g. on an inner side or an inner circumferential surface, of the switching device can be utilized to displace the switching device in the axial direction with minimal effort. Thus, by utilizing the clearance between the input and output, the switching device can be moved with minimal force from an actuator.It is possible that the tooth flanks of the gears of the switching device and the second clutch device do not yet touch or contact each other.

[0031] Thus, in addition to the first power transmission path, the second power transmission path can now also be activated in order to transmit a tangential force or torque in the event of a further increase in the input torque.

[0032] In the third state, the input torque may have increased or increased further compared to the second state. The first and second power transmission paths may be implemented in the third state.

[0033] In short, the further increased input torque can now be transmitted from the input to the output partly via the first clutch device or its clamping body and partly via the second clutch device.

[0034] As already described, the clamping elements of the first clutch device can split the input torque or the resulting incoming tangential force in the tangential direction into an axial and a tangential force component, or into an outgoing tangential force and an axial force. This is because the clamping elements of the first clutch device can be aligned at an angle or incline between the input and output.

[0035] Due to the increased input torque (or the increased incoming tangential force) compared to the second state, the axial and tangential force components (or the outgoing tangential force and the axial force) can also increase, which are transmitted via obliquely or inclined clamping bodies of the first coupling device.

[0036] If the output or a part thereof, such as a hub, is axially displaceable, an increase in the input torque can cause an increase in the axial force on the sprags of the first clutch device, thereby causing an axial displacement of the output. The axial displacement of the output can cause a rotation or twisting of the sprags of the first clutch device.

[0037] In this case, the distance between the ends of the clamping bodies of the first coupling device decreases in the circumferential or tangential direction. In other words, when viewed in the circumferential direction, the ends of a clamping body move closer together as it rotates. In other words, the angle between the clamping body of the first coupling device or a web of the clamping body of the first coupling device and the tangential or circumferential direction increases.

[0038] This circumferential shortening allows the input and output to rotate relative to each other. This eliminates any play or loose fit, for example, between the input and output or between the second clutch device and the shifting device. Consequently, the input torque can be transmitted largely or at least partially via the second clutch device in the circumferential or tangential direction. In this case, it is possible for the tooth flanks of the gears of the shifting device and the second clutch device to touch or make contact.

[0039] Furthermore, in the third state, a change in the direction of rotation of the input torque can be transmitted from the input to the output via the second power transmission path. This also allows, for example, reverse travel. The input torque can then be transmitted completely, not just partially. This also applies when torque is transferred from the output to the input, for example, to enable recuperation.

[0040] Furthermore, the first clutch device can be designed as a combination of a freewheel and a dog clutch. The freewheel can be designed as a switchable freewheel. The freewheel can be switched, for example, using the switching device.

[0041] The second clutch device, for example, together with the shifting device, can be designed as a shift sleeve transmission. This is a reliable, yet easy-to-manufacture, and thus cost-effective implementation of the second clutch device.

[0042] Furthermore, the first coupling device can have a hollow cylindrical body with a plurality of ramps as axial extensions or as extensions or as axial ends or as extensions in the axial direction, which can be distributed or evenly distributed in the circumferential direction.

[0043] Furthermore, the first coupling device can be designed similarly to a crown gear, but instead of teeth, it can have ramps which can be arranged distributed in the circumferential direction.

[0044] In addition, the ramps can jump back and forth in the axial direction.

[0045] The ramps can also be designed and oriented in such a way that they cause a movement of clamping bodies of the first coupling device in the axial direction.

[0046] Furthermore, the first coupling device and / or the ramps can be formed at an axial end of the input.

[0047] Additionally, each circumferential ramp may have a stop at its first end. Furthermore, each circumferential ramp may smoothly transition into an axial end of the first coupling device or the input at its second end.

[0048] It is also conceivable that each ramp may have an arcuate course between its first and second ends, which is convexly aligned to an axial end of the first coupling device or the input.

[0049] The first coupling device can also comprise multiple clamping bodies. Each clamping body can be flat and / or plate-shaped. The clamping bodies serve to transmit force in the tangential and axial directions, namely from the input or from the ramps to the output or to a web of the first coupling device.

[0050] Additionally, each clamping body can have a shape similar to a double-T beam. Each clamping body can also comprise a web and two flanges, each of which can form one end of a clamping body. The web can be designed as a plate with a rectangular cross-section. Each flange can be designed as a projection that protrudes laterally at the ends of the web.

[0051] Furthermore, the first coupling device can comprise a spring element for each clamping body, wherein a spring element can be arranged on each clamping body. The spring element can be fastened to a first end of the clamping body and spaced from a second end of the clamping body in order to generate a spring force around the first end. Each spring element can have a spring tongue, which can be arranged on a second end of a clamping body of the first coupling device and can be designed to project freely towards the first end of the clamping body of the first coupling device. Furthermore, the spring tongue can be supported on a web of a clamping body of the first coupling device in order to generate a spring force. The spring element can be fastened to a clamping body of the first coupling device by clamps.

[0052] In addition, each clamping body can be geometrically designed to be inserted into pockets of a web of the first coupling device, in such a way that the spring element presses the clamping body out of the pocket, e.g. in the axial direction.

[0053] Furthermore, the first coupling device can have a web with pockets, which are introduced, for example, in the axial direction, for receiving clamping bodies of the first coupling device. The web can be circular or disk-shaped. Furthermore, the pockets can be geometrically designed to each accommodate a clamping body of the first coupling device, for example, such that a spring element of the clamping body presses it out of the pocket, for example, in the axial direction.

[0054] Furthermore, the web can connect a ring gear of the second clutch device to a hub of the output. The web, the ring gear, and the hub can be formed as a single piece.

[0055] Furthermore, it can be provided that the first coupling device comprises a spring and a retaining ring for tensioning the spring. The spring can be designed as a disc spring. Furthermore, the spring can bear against a hub of the output on the one hand and against the retaining ring on the other hand, and can tension the hub in a direction away from the retaining ring. The spring can limit the maximum torque that can be transmitted via the first coupling device.

[0056] Overcoming the spring force of the spring can be caused by tilting or twisting the clamping bodies of the first clutch device, whereby the tilting / twisting is caused by the input torque of a certain magnitude. This tilting / twisting leads to a shortening of the distance between the ends of the clamping bodies - viewed in the circumferential or tangential direction. In other words, when viewed in the circumferential direction, when a clamping body rotates, its ends move closer together. This, in turn, can cause the input and output to rotate relative to one another. This allows the second clutch device to be activated. When the input torque decreases, the spring or the disc spring rotates the clamping bodies of the first clutch device in such a way that - viewed in the circumferential or tangential direction - the distance between the ends of the clamping bodies increases.This allows the second clutch device to be deactivated. Furthermore, the retaining ring can be arranged in a groove of an output shaft. The retaining ring serves to support axially acting forces, such as those from the spring or the clamping elements of the first clutch device.

[0057] Furthermore, the switching device can be designed to be displaceable in the axial direction.

[0058] It can also be provided that the switching device comprises a control unit. The control unit can be designed to be displaceable in the axial direction.

[0059] Furthermore, the control unit can comprise two concentric or concentrically arranged ring elements which are designed and / or spaced apart from one another such that clamping bodies of the first coupling device can bear against or on ramps of the first coupling device and / or can bear against stops of the first coupling device.

[0060] In addition, the ring elements can be spaced apart such that a web of a clamping body of the first coupling device can be contacted by a ramp of the first coupling device. The two ring elements can serve to press or compress the clamping bodies or the spring elements arranged thereon into the pockets. This interrupts / separates the force transmission from the input to the output or from the ramps of the first coupling device to the pockets of a web of the first coupling device. Furthermore, the ring elements can be connected to one another.

[0061] One of the ring elements can also have at least one lug which projects outwards in the radial direction, so that the control unit can be displaced by means of the switching device by means of the at least one lug which engages in the switching device.

[0062] The control unit can be constructed as a single piece, facilitating manufacturing.

[0063] Furthermore, the switching device can be hollow-cylindrical or have a ring gear. Toothing and / or at least one stop for at least one lug of a ring element of a control unit of the switching device can be formed on the inside or on the inner circumferential surface of the ring gear. With the aid of the at least one stop, a ring element of a control unit of the switching device can be displaced in the axial direction together with the ring gear. On the outside, the switching device can have a groove for an actuator.

[0064] Furthermore, the second clutch device can comprise a gear and / or be designed as a gear. The gear can be arranged at the input in a rotationally fixed manner. Furthermore, the gear can be arranged between the axial ends of the input.

[0065] The second clutch device can also comprise a ring gear. The ring gear can have teeth on the outside, e.g., for the shifting device designed as a sliding sleeve.

[0066] In addition, a web of the first clutch device can connect the ring gear to a hub of the output. The web, the ring gear, and the hub can be formed as a single piece.

[0067] Furthermore, the output can comprise a shaft for transmitting torque to at least one vehicle wheel. The shaft can be arranged inside the hollow-cylindrical input, thereby saving installation space.

[0068] Furthermore, the shaft can be designed such that a hub of the output can be arranged on the shaft in a rotationally fixed and axially displaceable manner. This allows the second clutch device to be activated or a force and / or torque to be transmitted via the second clutch device.

[0069] In addition, the shaft can be designed to form a positive shaft-hub connection.

[0070] The shaft may have a splined shaft profile, a polygonal profile, a toothed shaft profile or serration or additional driving elements, such as a key.

[0071] In addition, the shaft may include a groove for a retaining ring to tension a spring.

[0072] It is also possible that the output includes a hub.

[0073] The output can be designed such that the hub is arranged on a shaft of the output in a rotationally fixed and axially displaceable manner on the shaft.

[0074] Furthermore, the hub can be designed to form a positive shaft-hub connection, wherein the hub can have a splined shaft profile, a polygonal profile, a toothed shaft profile or a serration or additional driver elements, such as a feather key.

[0075] In addition, the output may include a spacer ring or spacer sleeve for correct positioning of the hub on or around the shaft.

[0076] Furthermore, it is possible for the input to be hollow cylindrical or in the form of a hollow shaft or to have a hollow cylinder.

[0077] The input can also be formed and / or connected to a gear of the second clutch device and / or formed in one piece.

[0078] Furthermore, the input can be formed and / or connected and / or formed in one piece with ramps of the first coupling device.

[0079] A detailed description of the functioning of the coupling device, including the features described above, can be found in the description of the figures.

[0080] Finally, it should be noted that the present invention, in simplified form, can be a clutch device (DCU - Disk Connect Unit) for an electric or hybrid vehicle, which combines a freewheel with a shift sleeve transmission.

[0081] With this combination, both the advantages of the freewheel, ie very fast engagement, and the advantages of a shift sleeve transmission, ie very high torque capacity, can be used.

[0082] It should also be mentioned that the direction of the circumferential direction or the tangential direction can be determined by an input torque applied at the input.

[0083] The invention is explained in more detail below using an exemplary embodiment in conjunction with the accompanying drawings. The drawings schematically show: Fig. 1 a side view of a coupling device; Fig. 2 a first and a second spatial view of the coupling device from Fig. 1 ; Fig. 3 an exploded view of the coupling device Fig. 1 ; Fig. 4 a sectional view of the coupling device Fig. 1 ; Fig. 5 a further sectional view of the coupling device Fig. 1 including an enlarged section; Fig. 6a) to 6c) show various views of the coupling device in a first state; Fig. 7a) to 7c) different views of the coupling device in a second state; Fig. 8a) to 8c) show various views of the coupling device in a third state; and Fig. 9 a spatial view of a clamping body.

[0084] In the following description, the same reference symbols are used for the same items.

[0085] Fig. 1 shows a side view of a coupling device 1, Fig. 2 a first and a second spatial view of the coupling device from Fig. 1 and Fig. 3 an exploded view of the coupling device Fig. 1.

[0086] For the sake of simplicity and brevity, the following Fig. 1 to 3 described together.

[0087] The figures show a coupling device 1 for an electric or hybrid vehicle.

[0088] The coupling device 1 has an input 2 for connection to an engine and for receiving an input torque and an output 3 for connection to a vehicle wheel and for outputting a torque.

[0089] Furthermore, the coupling device 1 comprises a first coupling device 4 for separating and establishing a first power transmission path from the input 2 to the output 3.

[0090] The coupling device 1 also has a second coupling device 5 for separating and establishing a second power transmission path from the input 2 to the output 3.

[0091] Thus, the first and second clutch devices 4, 5 are arranged and designed to transmit the tangential force or the input torque received at the input 2 to the output 3.

[0092] In addition, for example, Fig. 3, that the clutch device 1 has a switching device 6 for selecting the power transmission path. The switching device 6 is designed to be displaceable in the axial direction. Furthermore, the Fig. 1 to 3, the switching device 6 is hollow-cylindrical or has a ring gear 6A. The switching device 6 is designed in the form of a sliding sleeve, which can be displaced back and forth in the axial direction A from the radial outside by means of an actuator (not shown).

[0093] The first clutch device 4 is configured and designed to convert an incoming tangential force, resulting from an input torque introduced at the input 2, into an outgoing tangential force and an axial force in order to pre-position the second clutch device 5 to establish the second power transmission path. This conversion / transformation therefore serves to pre-position the second clutch device 5 so that it can be available for power transmission. This is because the pre-positioning allows the switching device 6 to be easily displaced with little effort in such a way that it prepares the second power transmission path. As a result of this preparation, the second power transmission path is ready to transmit torque.

[0094] It can also be noted that pre-positioning or pre-positioning can serve to align a toothing of a gearwheel 5A of the second clutch device 5 and a toothing, e.g. on an inner side or on an inner circumferential surface, of the switching device 6. During alignment, the toothings of the second clutch device 5 and the switching device 6 can be positioned relative to one another in such a way that an axial displacement of the switching device 6 is possible with little effort. This can produce an engagement of the toothing of the switching device 6 with a toothing 5A of the second clutch device 5. In this case, it is possible that the tooth flanks of the toothings of the switching device 6 and the second clutch device 5 do not yet touch or make contact.

[0095] Furthermore, the first clutch device 4 is arranged and designed such that the axial force causes a relative rotation between the input 2 and the output 3 or between the second clutch device 5 and the switching device 6, whereby a play between the second clutch device 5 and the switching device 6 can be eliminated.

[0096] In other words, the first clutch device 4 is set up and designed such that the axial force causes a relative rotation between input 2 and output 3 or between the second clutch device 5 and the switching device 6, whereby play between a toothing of a gear 5A of the second clutch device 5 and a toothing, e.g. on an inner side or on an inner circumferential surface, of the switching device 6 can be eliminated. By eliminating the play, a portion of the incoming tangential force can be redistributed from the first clutch device 4 to the second clutch device 5 and thus the first clutch device 4 can be protected from overload. Furthermore, it is also possible for the elimination of the play to eliminate a large part of the tangential force ora large part of the input torque can be redistributed to the second clutch device 5, whereby the first clutch device 4 can also be protected from overload or completely relieved.

[0097] As already mentioned, the second clutch device 5 and the switching device 6 each have a toothing which is designed in such a way that they have a play with respect to one another in the circumferential direction U. As a result, with little effort for an axial displacement of the switching device 6, an engagement of the toothing of the switching device 6 with the toothing 5A of the second clutch device 5 can be achieved.

[0098] With the help of the first and second coupling devices 4, 5, the coupling device 1 can realize a first, second, and third state. More on this below.

[0099] In brief, the first clutch device 4 is designed as a combination of a freewheel and a dog clutch, and the second clutch device 5, together with the shifting device 6, is designed as a shift sleeve transmission. Both clutch devices 4, 5, as well as the exact functioning of the clutch device 1, will be explained in more detail below.

[0100] For further description, the Fig. 4 and Fig. 5 was added. Fig. 4 a sectional view of the coupling device 1 from Fig. 1 and Fig. 5 shows a further sectional view of the coupling device 1 from Fig. 1 including an enlarged section.

[0101] From the Fig. 3 and Fig. 4 shows that the first coupling device 4 has a hollow cylindrical body 10 with a plurality of ramps 16 as axial extensions, which are arranged distributed in the circumferential direction U.

[0102] In other words, the first clutch device 4 is designed similarly to a crown gear, but instead of teeth, the first clutch device 4 has ramps 16 which are distributed in the circumferential direction U. The ramps 16 project back and forth in the axial direction A and are formed at one axial end of the input 2.

[0103] The ramps 16 are designed and oriented in such a way that they cause a movement of clamping bodies 18 of the first coupling device 4 in the axial direction A.

[0104] Each ramp 16 has a stop 17 at its first end in the circumferential direction U - see. Fig. 5 - and merges smoothly in the circumferential direction U at its second end into an axial end of the first coupling device 4 or the input 2.

[0105] In addition, each ramp 16 has an arcuate profile between its first and second ends, which is convexly aligned with an axial end of the first coupling device 4 or the input 2.

[0106] In addition, the Fig. 3 and Fig. 5, that the first coupling device 3 - as already indicated - comprises a plurality of clamping bodies 18, each clamping body 18 being plate-shaped. The clamping bodies 18 serve to transmit force in the tangential direction T and in the axial direction A, specifically from the input 2 or from the ramps 16 to the output 3 or to a web 19 of the first coupling device 4.

[0107] According to Fig. 9, which shows a three-dimensional view of a clamping body 18, each clamping body 18 has a shape similar to a double-T beam and comprises a web 19 and two flanges 20, each forming one end of a clamping body 18. The web 19 is designed as a plate with a rectangular cross-section, wherein each flange 20 is designed as a projection which protrudes laterally at the ends of the web 19.

[0108] According to Fig. 3 and Fig. 9, the first coupling device 4 has a spring element 21 per clamping body 18, wherein the spring element 21 is arranged on each clamping body 18.

[0109] More specifically, the spring element 21 is attached to a first end 29 of the clamping body 18 and spaced from a second end 30 of the clamping body 18 in order to generate a spring force around the first end 29. Each spring element 21 has a spring tongue which is arranged at the second end 30 of the clamping body 18 and is designed to project freely towards the first end 29 of the clamping body 18 - see. Fig. 9. Furthermore, the spring tongue rests on the web 19 of a clamping body 18 to generate a spring force. The spring element 21 is also attached to the clamping body 18 by clamps.

[0110] In addition, each clamping body 18 is geometrically designed to be inserted into pockets 28 of a web 19 of the first coupling device 4, in such a way that the spring element 21 presses the clamping body in the axial direction A out of the pocket 28, as in Fig. 5 can be recognized.

[0111] Furthermore, the first coupling device 4 has a web 13 with pockets 28, introduced in the axial direction A, for receiving clamping bodies 18, wherein the web 13 is circularly formed - see Fig. 3, Fig. 4 and Fig. 5. The pockets 28 are geometrically designed to each accommodate a clamping body 18, in such a way that the spring element 21 of a clamping body 18 presses it out of the pocket 28, e.g. in the axial direction A.

[0112] The web 13 connects a ring gear 14 of the second clutch device 5 with a hub 11 of the output 3, wherein the web 13, the ring gear 14 and the hub 11 are formed in one piece (see also Fig. 4 and Fig. 5).

[0113] In addition, the Fig. 1 to 5, the first clutch device 4 comprises a spring 26 and a retaining ring 27 for tensioning the spring 26. The spring 26 is designed as a disc spring and rests on one side against a hub 11 of the output 3 and on the other side against the retaining ring 27. Thus, the spring 26 or disc spring 26 tensions the hub 11 in a direction away from the retaining ring 27. The retaining ring 27 is arranged in a groove 9 of the shaft 7 of the output 3.

[0114] Furthermore, Fig. 3 to 5 that the switching device 6 comprises a control unit 22 which is designed to be displaceable in the axial direction A.

[0115] The control unit 22 comprises two concentric ring elements 23, 24 which are designed and spaced apart from one another such that the clamping bodies 18 of the first coupling device 4 bear against or on the ramps 16 and also against the stops 17.

[0116] In other words, the ring elements 23, 24 are spaced apart from one another such that a web 19 of a clamping body 18 of the first coupling device 4 can be contacted by a ramp 16 of the first coupling device 4. The two ring elements 23, 24 serve to press or compress the clamping bodies 18 or the spring elements 21 arranged thereon into the pockets 28. This interrupts / separates the force transmission from the input 2 to the output 3 or from the ramps 16 to the pockets 28 of the web 13 of the first coupling device 4.

[0117] This shows Fig. 3 shows that the ring elements 23, 24 are connected to each other. Fig. 3, that one of the ring elements 23, 24 has three lugs 25 that project outward in the radial direction R, so that the control unit 22 can be displaced by means of the lugs 25, which engage in the switching device 6, with the aid of the switching device 6. The control unit 22 is formed in one piece in the present case.

[0118] According to Fig. 3, the switching device 6 has a ring gear 6A and is designed in the form of a sliding sleeve which can be moved back and forth in the axial direction A from the radial outside by means of an actuator (not shown).

[0119] On the inside or inner surface of the ring gear 6A, a toothing and three stops (not shown) for the three lugs 25 of the ring element 24 of the control unit 22 of the switching device 6 are formed. With the aid of the three stops, the ring elements 23, 24 of the control unit 22 can be displaced in the axial direction A together with the ring gear 6A. On the outside, the switching device 6 has a groove for an actuator (not shown).

[0120] Furthermore, the Fig. 1 to 5 that the second clutch device 5 comprises a gear 5A which is arranged in a rotationally fixed manner on the input 2 and between the axial ends of the input 2.

[0121] In addition, the second clutch device 5 has a ring gear 14 which has a toothing on the outside, e.g. for the switching device 6 designed as a sliding sleeve.

[0122] As already explained, the web 13 connects the ring gear 14 with a hub 11 of the output 3, whereby the web 13, the ring gear 14 and the hub 11 are formed in one piece (see also Fig. 4 and Fig. 5).

[0123] With a view to the Fig. 1 to 3 it can be seen that the input 2 is hollow cylindrical or in the form of a hollow shaft.

[0124] The input 2 is formed with the gear 5A of the second clutch device 5 and with ramps 16 of the first clutch device 4.

[0125] The output 3, on the other hand, has a shaft 7 for transmitting torque to a vehicle wheel. The shaft 7 is located inside the hollow-cylindrical input 2, thus saving installation space.

[0126] The shaft 7 is designed such that a hub 11 of the output 3 is arranged on the shaft 7 in a rotationally fixed and axially displaceable manner.

[0127] Furthermore, the shaft 7 is designed to form a positive shaft-hub connection, wherein the shaft 7 has a splined shaft profile 8.

[0128] In addition, Wave 7 has Fig. 3 a groove 9 for a retaining ring 27 for tensioning a spring 26.

[0129] As also Fig. 3, the output 3 has a hub 11. The output 3 is designed such that the hub 11 is arranged on the shaft 7 in a rotationally fixed and axially displaceable manner. For this purpose, the hub 11 is designed to form a positive shaft-hub connection, wherein the hub 11 has a splined shaft profile 12.

[0130] In addition, Fig. 3, that the output 3 comprises a spacer ring 15 or a spacer sleeve 15 for the correct positioning of the hub device 10 on the shaft 7.

[0131] Fig. 6a) to 6c) show different views of the described coupling device 1 in a first state.

[0132] In the first state, an input torque is transmitted from input 2 to output 3. The first power transmission path is realized in the first state.

[0133] According to the Fig. 6a) and Fig. 6b), the switching device 6 or its ring gear 6A is arranged entirely on or above the ring gear 14 of the second clutch device 5. Furthermore, the clamping bodies 18 are positioned by the spring force of their spring elements 21 in such a way that the clamping bodies 18 can transmit a force from the input 2 to the output 3.

[0134] Described in more detail, the spring elements 21 help ensure that the clamping bodies 18 rest with their second ends 30 in the stops 17 of the ramps 16 and with their first ends 29 in the pockets 28, so that a force or the input torque can be transmitted from the hollow cylindrical body 10 to the ramps 16 via the clamping bodies 18 further to the hub 11 and finally to the shaft 7.

[0135] The hub 11 then transmits a force or the input torque via the spline profile 12 to the spline profile 8 of the shaft 7 and thus to the output 3.

[0136] More specifically, the clamping bodies 18 split the input torque or the tangential force in the tangential direction T, resulting from the input torque introduced at input 2, into a tangential and an axial force component or into an outgoing tangential force and an axial force. This is because the clamping bodies 18 are designed according to Fig. 6b) are arranged obliquely or inclined between input 2 or ramps 16 and output 3 or hub 11.

[0137] In the present description, “oblique” can be understood as inclined to the tangential direction T of the coupling device 1, so that, for example, the angle α between a clamping body 18 or its web 19 and the tangential direction T is less than 90 degrees - see also Fig. 5.

[0138] In Fig. 6c) it can be seen that the toothing 5A of the first clutch device 4 and the toothing on the inside or on the inner surface of the switching device 6 are spaced apart from one another in the circumferential direction U. Thus, the tooth flanks of the toothings of the switching device 6 and the second clutch device 5 do not contact one another. There is therefore a play in the circumferential direction U between the toothing 5A of the first clutch device 4 and the toothing of the switching device 6. The play is distributed in such a way that the toothing 5A of the first clutch device 4 and the toothing of the switching device 6 are spaced apart from one another on both sides or to both tooth flanks. This may look different in reality, but is shown here for better understanding. Fig. 6c) is shown as follows. Consequently, no forces or moments are transmitted in the circumferential direction U or in the tangential direction T between the toothing 5A and the toothing of the switching device 6.

[0139] As a result, the entire torque is transmitted via the clamping bodies 18 from input 2 to output 3.

[0140] However, in the first state, the second clutch device 5 is prepared or pre-positioned with the aid of the first clutch device 4, so that the shifting of the switching device 6 in the axial direction A is possible with little effort.

[0141] Because of the play between input 2 and output 3 or between the second clutch device 5 and the switching device 6, the switching device 6 can be moved in the axial direction A with very little switching force so that the switching device 6 connects the input 2 to the output 3 via the second power transmission path.

[0142] Consequently, the toothing 5A of the first clutch device 4 and the toothing on the inside / inner surface of the switching device 6 can be prepared or pre-positioned in the circumferential direction U for a connection via the switching device 6.

[0143] Fig. 7a) to 7c) show different views of the described coupling device 1 in a second state.

[0144] Here, in the second state, the input torque is the same or increased compared to the first state. Similar to the first state, the entire input torque is transmitted by the first clutch device 4 or its clamping bodies 18 from input 2 to output 3. Thus, the first power transmission path is realized in the second state, just as in the first state.

[0145] However, it is now in the second state, as in the Fig. 7a) and Fig. 7b), it is possible to move the switching device 6 in the axial direction A or in the direction of the gear wheel 5A or in the direction of the toothing 5A, so that the second power transmission path is prepared for the power and / or torque transmission.

[0146] In this case, the switching device 6 is no longer arranged entirely on the ring gear 14 of the second clutch device 5. Consequently, it is now possible for a torque to be transmitted from the gear 5A or from the toothing 5A via the switching device 6 to the ring gear 14 of the second clutch device 5.

[0147] In order to enable the switching device 6 to be moved or displaced with minimal effort, the play between the second clutch device 5 and the switching device 6 or their toothings is utilized in the second state. Because the first clutch device 4 is configured and designed such that the axial force causes a relative rotation between input 2 and output 3 or between the second clutch device 5 and the switching device 6, the play between a toothing 5A of the gearwheel 5A of the second clutch device 5 and the toothing of the switching device 6 can be utilized to displace the switching device 6 in the axial direction A with minimal effort.

[0148] Thus, by utilizing the play between the teeth of the second clutch device 5 and the switching device 6, the switching device 6 can be moved with little force from an actuator.

[0149] Thus, in addition to the first power transmission path, the second power transmission path can now also transmit a tangential force or torque if the input torque increases further.

[0150] Nevertheless, in the second state, the clamping bodies 18 continue to transmit a tangential and axial force from the ramps 16 to the web 13 and thus to the hub 11 and the shaft 7.

[0151] In Fig. 7c) it can be seen that the gear wheel 5A of the second clutch device 5 and the internal toothing or the toothing of the switching device 6 are still spaced apart from one another in the circumferential direction U. Thus, there is still a play in the circumferential direction U between the toothing 5A of the first clutch device 4 and the toothing of the switching device 6. Thus, the tooth flanks of the toothings of the switching device 6 and the second clutch device 5 do not yet contact one another. The play is distributed in such a way that the toothing 5A of the first clutch device 4 and the toothing of the switching device 6 are spaced apart from one another on both sides or to both tooth flanks. This may look different in reality, but is shown here for better understanding. Fig. 7c) is shown as follows. As a consequence, as already explained, no forces or moments are transmitted in the circumferential direction U or in the tangential direction T between the gearwheel 5A and the toothing of the switching device 6.

[0152] As a result, the entire torque is transmitted via the clamping bodies 18 from input 2 to output 3.

[0153] Fig. 8a) to 8c) show different views of the described coupling device 1 in a third state.

[0154] Here, in the third state, the input torque has increased or continued to increase compared to the second state. In the third state, the first and second power transmission paths, or largely the second power transmission path, are realized. Briefly summarized, the input torque is now transmitted from input 2 to output 3 partly via the clamping bodies 18 and partly via the gear 5, the switching device 6, and the ring gear 14.

[0155] According to the Fig. 8a) and Fig. 8b) the switching device 6 is positioned identically as in the Fig. 7a) and Fig. 7b); i.e., the switching device 6 is displaced in the direction of the gear 5A of the second clutch device 5. In this way, a force or the input torque can be transmitted from the input 2 to the gear 5A of the second clutch device 5, to the switching device 6, and further to the ring gear 14. The ring gear 14, in turn, can transmit the force or the input torque to the hub 11 and thus to the shaft 7.

[0156] As already described, the clamping bodies 18 divide the input torque or the resulting incoming tangential force in the tangential direction T into an axial and a tangential force component or into an outgoing tangential force and an axial force. This is because the clamping bodies 18 are Fig. 8b) are arranged diagonally between entrance 2 or ramps 16 and exit 3 or bridge 13.

[0157] Due to the increased input torque (or the increased tangential force) compared to the second state, the axial and tangential force components (or the outgoing tangential force and the axial force) that are transmitted via the clamping bodies 18 also increase.

[0158] The axial force component or the axial force of all clamping bodies 18 reaches a level that is above the spring force of the disc spring 26, so that the disc spring 26, as in Fig. 8a) and Fig. 8b). The compression of the disc spring 26 is caused by the displacement of the hub 11, which is made possible by the spline profiles 8, 12 of the shaft 7 and the hub 11.

[0159] The displacement of the hub 11 in the axial direction A results, as already indicated, from the increasing input torque, which generates a force in the axial direction A on the hub 11 due to the oblique arrangement of the clamping bodies 18.

[0160] When the hub 11 is displaced in the axial direction A, the clamping bodies 18 rotate about the axial and tangential directions A, T. In the process, the distance between the ends 29, 30 of the clamping bodies 18 shortens in the circumferential direction U. In other words, when viewed in the circumferential direction U, the second end 30 of a clamping body 18, which rests against the stop 17, and the first end 29 of the clamping body 18, which rests in the pocket 28, approach each other. This shortening leads to the input 2 and the output 3, or the toothing 5A and the toothing of the ring gear 14, together with the toothing of the switching device 6, rotating relative to each other. In other words, the angle α between the clamping body 18 or its web 19 and the tangential direction T increases - see also Fig. 5.

[0161] In Fig.8c) it can be seen that the gear 5A of the first clutch device 4 and the toothing of the switching device 6 abut one another in the circumferential direction U. The tooth flanks of the toothings of the switching device 6 and the second clutch device 5 are therefore in contact. There is therefore no longer any play in the circumferential direction U between the gear 5A of the first clutch device 4 and the toothing of the switching device 6. Consequently, the input torque can be transmitted completely or partially in the circumferential direction U or in the tangential direction T between the gear 5 and the internal toothing of the switching device 6.

[0162] As a result, the majority of the input torque is transmitted via the gear 5A of the first clutch device 4 and the toothing of the switching device 6, as well as via the clamping bodies 18 from the input 2 to the output 3. This protects the clamping bodies 18 and thus the first clutch device 4 from overload.

[0163] If the input torque now decreases, the procedure described above can be carried out in reverse order.

[0164] Furthermore, it should be noted that in the third state, a change in the direction of the circumferential direction U or the tangential direction T or the input torque can be transmitted via the second power transmission path from input 2 to output 3. The input torque will then be transmitted entirely to the ring gear 14 via the gear 5A of the first clutch device 4 and the toothing of the switching device 6. This also makes reverse travel possible, for example. This also applies when torque is transmitted from output 3 to input 2, for example, to enable recuperation. List of reference symbols 1 coupling device 2 entrance 3 Exit 4 first coupling device 5 second coupling device 5A Gear / Toothing 6 Switching device 6A ring gear 7 Wave 8 spline profile 9 grooves 10 hollow cylindrical body 11 Hub 12 spline profile 13 jetty 14 ring gear 15 Spacer ring / spacer sleeve 16 ramps 17 stop 18 clamping bodies 19 jetty 20 flange 21 Spring element 22 Control unit 23 Ring element 24 ring element 25 Nose 26 spring 27 Retaining ring 28 bag 29 first end 30 second end A axial direction T tangential direction U circumferential direction

Claims

[1] Coupling device (1) for an electric or hybrid vehicle comprising: - an input (2) for connection to a motor and for obtaining an input torque, - an output (3) for connection to at least one vehicle wheel and for delivering a torque, - a first coupling device (4) for separating and establishing a first power transmission path from the input (2) to the output (3), - a second coupling device (5) for separating and establishing a second power transmission path from the input (2) to the output (3), - a switching device (6) for selecting the power transmission path, - wherein the first coupling device (4) is arranged and designed to convert an incoming tangential force resulting from an input torque introduced at the input (2) into an outgoing tangential force and an axial force in order to pre-position the second coupling device (5) for establishing the second force transmission path. [2] Coupling device according to claim 1, - wherein the first clutch device (4) is further configured and designed such that the axial force causes a relative rotation between the input (2) and output (3) or between the second clutch device (5) and the switching device (6), whereby a play between the second clutch device (5) and the switching device (6) can be eliminated, and / or - wherein the second clutch device (5) and the switching device (6) each comprise a toothing which is designed in such a way that it has a play in the circumferential direction (U) relative to one another, whereby an engagement of the toothing of the switching device (6) in the toothing of the second clutch device (5) can be produced with little effort for an axial displacement of the switching device (6). [3] Coupling device according to claim 1 or 2, - wherein the first coupling device (4) has a hollow cylindrical body (10) with a plurality of ramps (16) as axial extensions, which are arranged distributed in the circumferential direction (U), and / or - wherein the first coupling device (4) is designed similarly to a crown gear, but instead of teeth has ramps (16) which are arranged distributed in the circumferential direction (U). [4] Coupling device according to one of the preceding claims, - wherein the first coupling device (4) comprises a plurality of clamping bodies (18) which serve to transmit force in the tangential direction (T) and in the axial direction (A), namely from the input (2) to the output (3), - wherein the first coupling device (4) comprises a spring element (21) per clamping body (18), and - wherein a spring element (21) is arranged on each clamping body (18), [5] Coupling device according to one of the preceding claims, - wherein the first coupling device (4) has a web (13) with pockets (28) for receiving clamping bodies (18) of the first coupling device (4), and - wherein the web (13) connects a ring gear (14) of the second coupling device (5) to a hub (11) of the output (3). [6] Coupling device according to one of the preceding claims, - wherein the switching device (6) is designed to be displaceable in the axial direction (A), - wherein the switching device (6) is hollow-cylindrical or has a ring gear (6A), and / or - wherein the switching device (6) is designed in the form of a sliding sleeve which can be displaced back and forth in the axial direction (A) from the radial outside by means of an actuator. [7] Coupling device according to one of the preceding claims, - wherein the switching device (6) comprises a control unit (22), - wherein the control unit (22) is designed to be displaceable in the axial direction (A), and - wherein the control unit (22) comprises two concentric ring elements (23, 24) which are designed and / or spaced apart from one another such that clamping bodies (18) of the first coupling device (4) can bear against or on ramps (16) of the first coupling device (4). [8] Coupling device according to one of the preceding claims, - wherein the second coupling device (5) comprises a gear (5A), - wherein the gear (5A) is arranged at the input (2) in a rotationally fixed manner, - wherein the second clutch device (5) comprises a ring gear (14), and - wherein a web (13) of the first coupling device (4) connects the ring gear (14) to a hub (11) of the output (3). [9] Coupling device according to one of the preceding claims, - wherein the output (3) comprises a shaft (7) for transmitting a torque to at least one vehicle wheel, - wherein the output (3) has a hub (11), and - wherein the output (3) is designed such that the hub (11) is arranged on the shaft (7) in a rotationally fixed and axially displaceable manner. [10] Coupling device according to one of the preceding claims, - wherein the inlet (2) is hollow cylindrical or in the form of a hollow shaft or has a hollow cylinder, - wherein the input (2) is formed with a gear (5A) of the second clutch device (5), and - wherein the input (2) is formed with ramps (16) of the first coupling device (4).

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