Clutch apparatus for an electric or hybrid vehicle

Abstract

The invention relates to a clutch apparatus (1) for an electric or hybrid vehicle, having: an input (2) for connection to a motor and for receiving an input torque, an output (3) for connection to at least one vehicle wheel and for outputting a torque, a first clutch device (4) for separation and for production of a first force transmission path from the input (2) to the output (3), a second clutch device (5) for separation and for production of a second force transmission path from the input (2) to the output (3), a shift device (6) for selecting the force transmission path, wherein 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 into an axial force, in order to pre-position the second clutch device (5) for the production of the second force transmission path.

Description

[0001] Coupling device for an electric or hybrid vehicle

[0002] The present invention relates to a coupling device for an electric or hybrid vehicle.

[0003] 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 the drive.

[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 can be oriented in the direction of the rotational axis of the coupling device. Furthermore, the coupling device has 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.

[0011] The clutch device further comprises a second clutch device for disconnecting and establishing a second power transmission path from the input to the output. In other words, the second clutch device can be configured and designed to establish or disconnect power transmission via the second power transmission path. The second clutch 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, to the output as an outgoing tangential force or torque.

[0012] 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.

[0013] The clutch device also 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 by means of an actuator.

[0014] 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 force 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. This preparation means that the second power transmission path is ready to transmit torque.

[0015] Furthermore, it can 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 of the teeth of the switching device with 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.

[0016] 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, it is also possible to redistribute a large portion of the incoming tangential force from the input or a large portion of the input torque to the second clutch device, whereby the first clutch device can also be protected from overload or largely relieved. A large portion can be a portion greater than 50% of the total incoming torque or input torque. Furthermore, the second clutch device and the switching device can each comprise a toothing which is designed such that they have a play relative to one another in the circumferential direction.This allows the teeth of the switching device to engage with the teeth of the second clutch device with minimal effort required for axial displacement of the switching device. It is possible that the tooth flanks of the teeth of the switching device and the second clutch device may not yet touch or make contact.

[0017] By means of the first and second coupling devices, the coupling device can realize a first, second and third state.

[0018] 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.

[0019] 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.

[0020] 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.

[0021] In the present description, "oblique" can be understood as inclined to the axial direction and / or inclined to the tangential direction of the clutch device, so that, for example, the angle between a clamping body of the first clutch device or its web and the tangential and / or axial direction is less than or equal to 90 degrees. 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.

[0022] Because of a play or a loose fit between the input and output or between the second clutch device and the switching device, the switching device can be moved 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.

[0023] 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.

[0024] In the second state, the input torque may be increased, equal to, 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.

[0025] 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.

[0026] 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.

[0027] 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 in such a way 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 effort 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.

[0028] 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.

[0029] 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.

[0030] 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.

[0031] As already described, the sprags of the first clutch device can split the input torque or the resulting 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 sprags of the first clutch device can be aligned at an angle or incline between the input and output.

[0032] 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 clutch device.

[0033] 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 rotation or twisting of the sprags of the first clutch device.

[0034] 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.

[0035] 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.

[0036] 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 makes reverse driving possible, for example. 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.

[0037] 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.

[0038] The second clutch device, for example, together with the shifting device, can be designed as a shift sleeve transmission. This is a reliable but also easy-to-manufacture and thus cost-effective implementation of the second clutch device. Furthermore, the first clutch device can have a hollow cylindrical body with several ramps as axial extensions or as extensions or as an axial end or as extensions in the axial direction, which can be distributed or evenly distributed in the circumferential direction.

[0039] 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.

[0040] In addition, the ramps can move forward and backward in the axial direction.

[0041] 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.

[0042] Furthermore, the first coupling device and / or the ramps can be formed at an axial end of the input.

[0043] In addition, each ramp can have a stop at its first end in the circumferential direction. Furthermore, each ramp can smoothly transition into an axial end of the first coupling device or the input at its second end in the circumferential direction.

[0044] 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.

[0045] 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.

[0046] In addition, each clamping body can have a shape similar to a double-T beam. Each clamping body can also comprise a web and two flanges, which can each 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 which projects laterally at the ends of the web. 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 attached 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 at a second end of a clamping body of the first coupling device and can be designed to project freely toward 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 to generate a spring force. The spring element can be attached to a clamping body of the first coupling device by clamping.

[0047] 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.

[0048] Furthermore, the first coupling device can have a web with pockets, which are provided, 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.

[0049] 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.

[0050] Furthermore, it can be provided that the first clutch 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 on the one hand against a hub of the output and on the other hand against the retaining ring and 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 clutch device. This is because overcoming the spring force of the spring can be caused by tilting or twisting of the clamping bodies of the first clutch device, wherein the tilting / twisting is caused by the input torque of a certain magnitude. This tilting / twisting leads to the distance between the ends of the clamping bodies shortening 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 allows the input and output to rotate relative to one another. This means that the second clutch device can 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 direction or in the tangential direction, the distance between the ends of the clamping bodies increases. This means that the second clutch device can be deactivated. Furthermore, the retaining ring can be arranged in a groove in a shaft of the output. The retaining ring serves to support axially acting forces, such as those from the spring or from the clamping bodies of the first clutch device.

[0051] Furthermore, the switching device can be designed to be displaceable in the axial direction.

[0052] 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.

[0053] 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.

[0054] In addition, the ring elements can be spaced apart from one another 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 makes it possible to interrupt / separate force transmission from the input to the output or from the ramps of the first coupling device to pockets of a web of the first coupling device. In addition, the ring elements can be connected to one another. One of the ring elements can also have at least one lug that projects outwards in the radial direction, such that the control unit can be displaced with the aid of the switching device by means of the at least one lug that engages in the switching device.

[0055] The control unit can be constructed as a single piece, simplifying manufacturing.

[0056] Furthermore, the switching device can be hollow-cylindrical or have a ring gear. A 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.

[0057] 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.

[0058] 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.

[0059] 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.

[0060] 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.

[0061] In addition, 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 can be transmitted via the second clutch device. Furthermore, the shaft can be designed to form a positive shaft-hub connection.

[0062] 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.

[0063] In addition, the shaft may include a groove for a retaining ring to tension a spring.

[0064] It is also possible that the output includes a hub.

[0065] 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.

[0066] 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.

[0067] In addition, the output may include a spacer ring or spacer sleeve for correct positioning of the hub on or around the shaft.

[0068] 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.

[0069] The input can also be formed and / or connected to a gear of the second clutch device and / or formed in one piece.

[0070] Furthermore, the input can be formed and / or connected and / or formed in one piece with ramps of the first coupling device.

[0071] A detailed description of the functioning of the coupling device, including the features described above, can be found in the description of the figures.

[0072] Finally, it should be noted that, in simplified form, the present invention can be a clutch device (DCU Disk Connect Unit) for an electric or hybrid vehicle that combines a freewheel with a shift sleeve transmission. This combination thus makes it possible to utilize both the advantages of a freewheel, i.e., very fast engagement, and the advantages of a shift sleeve transmission, i.e., very high torque capacity.

[0073] 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.

[0074] The invention is explained in more detail below using an exemplary embodiment in conjunction with the accompanying drawings. The drawings schematically show:

[0075] Fig. 1 is a side view of a coupling device;

[0076] Fig. 2 shows a first and a second spatial view of the coupling device from Fig. 1;

[0077] Fig. 3 is an exploded view of the coupling device from

[0078] Figure 1 ;

[0079] Fig. 4 is a sectional view of the coupling device from Figure

[0080] 1 ;

[0081] Fig. 5 is a further sectional view of the coupling device from Fig. 1 including an enlarged section;

[0082] Fig. 6a) to 6c) different views of the coupling device in a first state;

[0083] Fig. 7a) to 7c) different views of the coupling device in a second state;

[0084] Fig. 8a) to 8c) show various views of the coupling device in a third state; and

[0085] Fig. 9 a spatial view of a clamping body.

[0086] In the following description, the same reference numerals are used for the same objects. Figure 1 shows a side view of a coupling device 1, Figure 2 shows a first and a second spatial view of the coupling device from Figure 1, and Figure 3 shows an exploded view of the coupling device from Figure 1.

[0087] For the sake of simplicity and brevity, Figures 1 to 3 are described together below.

[0088] The figures show a coupling device 1 for an electric or hybrid vehicle.

[0089] 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.

[0090] Furthermore, the coupling device 1 comprises a first coupling device 4 for separating and for establishing a first power transmission path from the input 2 to the output 3.

[0091] 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.

[0092] 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.

[0093] Furthermore, Figure 3, for example, shows 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, Figures 1 to 3 show that the switching device 6 is hollow-cylindrical and 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).

[0094] The first clutch device 4 is configured and designed to convert an incoming tangential force resulting from an input torque introduced at 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 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. This preparation makes the second power transmission path ready to transmit torque.

[0095] Furthermore, it can 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.

[0096] 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.

[0097] In other words, the first clutch device 4 is set up 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, as a result of which 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 the first clutch device 4 can thus 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 of load. As already mentioned, the second clutch device 5 and the switching device 6 each have a toothing which is designed such that they have a play relative to one another in the circumferential direction U. As a result, with little effort required 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] Briefly summarized, 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] Figures 4 and 5 are used for further description. Figure 4 shows a sectional view of the coupling device 1 from Figure 1, and Figure 5 shows a further sectional view of the coupling device 1 from Figure 1, including an enlarged section.

[0101] From Figures 3 and 4 it can be seen 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 that 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 such that they cause a movement of clamping bodies 18 of the first coupling device 4 in the axial direction A. Each ramp 16 has a stop 17 at its first end in the circumferential direction U (see Figure 5) and merges smoothly into an axial end of the first coupling device 4 or the input 2 at its second end in the circumferential direction U.

[0104] In addition, each ramp 16 has an arcuate profile between its first and second ends, which is convexly aligned to an axial end of the first coupling device 4 or the input 2.

[0105] Furthermore, Figures 3 and 5 show 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.

[0106] According to Figure 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 of which forms one end of a clamping body 18. The web 19 is designed as a plate with a rectangular cross-section, with each flange 20 being designed as a projection that protrudes laterally at the ends of the web 19.

[0107] According to Figures 3 and 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.

[0108] Described 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 to generate a spring force around the first end 29. Each spring element 21 has a spring tongue arranged at the second end 20 of the clamping body 18 and projecting freely toward the first end 29 of the clamping body 18 (see Figure 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 further attached to the clamping body 18 by clamps.

[0109] 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 out of the pocket 28 in the axial direction A, as can be seen, for example, in Figure 5.

[0110] 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 circular in shape, see Figures 3, 4 and 5. The pockets 28 are geometrically designed to each receive a clamping body 18, in such a way that the spring element 21 of a clamping body 18 presses this, e.g. in the axial direction A, out of the pocket 28.

[0111] The web 13 connects a ring gear 14 of the second clutch device 5 to 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 Figures 4 and 5).

[0112] Furthermore, Figures 1 to 5 show that 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.

[0113] Furthermore, it can be seen from Figures 3 to 5 that the switching device 6 comprises a control unit 22 which is designed to be displaceable in the axial direction A.

[0114] 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.

[0115] 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 a 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. Figure 3 shows that the ring elements 23, 24 are connected to one another. Furthermore, Figure 3 shows 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 with the switching device 6, with the aid of the switching device 6. In the present case, the control unit 22 is formed in one piece.

[0116] According to Figure 3, the switching device 6 has a ring gear 6A and 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).

[0117] 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).

[0118] Furthermore, it can be seen from Figures 1 to 5 that the second clutch device 5 comprises a gear 5A which is arranged on the input 2 in a rotationally fixed manner and between the axial ends of the input 2.

[0119] 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.

[0120] As already explained, the web 13 connects the ring gear 14 to 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 Figures 4 and 5).

[0121] Looking at Figures 1 to 3, it can be seen that the input 2 is hollow cylindrical or in the form of a hollow shaft.

[0122] 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.

[0123] The output 3, on the other hand, has a shaft 7 for transmitting torque to a vehicle wheel. The shaft 7 is arranged inside the hollow-cylindrical input 2, thus saving installation space. The shaft 7 is designed such that a hub 11 of the output 3 is arranged so as to rotate on the shaft 7 and is axially displaceable on the shaft 7.

[0124] Furthermore, the shaft 7 is designed to form a positive shaft-hub connection, wherein the shaft 7 has a splined shaft profile 8.

[0125] In addition, the shaft 7 according to Figure 3 has a groove 9 for a retaining ring 27 for tensioning a spring 26.

[0126] As can also be seen from Figure 3, the output 3 has a hub 11. The output 3 is designed such that the hub 11 is arranged on the shaft 7 so that it can rotate and be axially displaced. 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.

[0127] Furthermore, Figure 3 shows 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.

[0128] Figures 6a) to 6c) show different views of the described coupling device 1 in a first state.

[0129] In the first state, an input torque is transferred from input 2 to output 3. The first power transmission path is realized in the first state.

[0130] According to Figures 6a) and 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.

[0131] 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.

[0132] 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. More specifically, the clamping bodies 18 split the input torque or the tangential force arriving in the tangential direction T, resulting from the input torque introduced at the 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, as shown in Figure 6b), are arranged obliquely or inclined between the input 2 or ramps 16 and the output 3 or hub 11.

[0133] 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 between a clamping body 18 or its web 19 and the tangential direction T is less than 90 degrees (see also Figure 5).

[0134] In Figure 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. This means that 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 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 in Figure 6c) for better understanding. Consequently, in the circumferential direction U andNo forces or moments are transmitted in the tangential direction T between the toothing 5A and the toothing of the switching device 6.

[0135] As a result, the entire torque is transmitted via the clamping bodies 18 from input 2 to output 3.

[0136] 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.

[0137] 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 with the output 3 via the second power transmission path.

[0138] 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.

[0139] Figures 7a) to 7c) show different views of the described coupling device 1 in a second state.

[0140] 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.

[0141] However, in the second state, as shown in Figures 7a) and 7b), it is now 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.

[0142] 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.

[0143] In order to enable the switching device 6 to be moved or displaced with little effort, the play between the second clutch device 5 and the switching device 6 or its toothings is used in the second state.

[0144] Because the first clutch device 4 is designed and constructed in such a way 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 gear wheel 5A of the second clutch device 5 and the toothing of the switching device 6 can be used to move the switching device 6 in the axial direction A with little force. Thus, by using the play between the toothings of the second clutch device 5 and the switching device 6, the switching device 6 can be moved with little force from an actuator.

[0145] 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.

[0146] 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.

[0147] In Figure 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. There is therefore still 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 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 in Figure 7c) for better understanding. As a consequence, as already explained, in the circumferential direction U andNo forces or moments are transmitted in the tangential direction T between the gearwheel 5A and the teeth of the switching device 6.

[0148] As a result, the entire torque is transmitted via the clamping bodies 18 from input 2 to output 3.

[0149] Figures 8a) to 8c) show different views of the described coupling device 1 in a third state.

[0150] 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. In brief, the input torque is now transmitted partly via the clamping bodies 18 and partly via the gear 5, the switching device 6, and the ring gear 14 from the input 2 to the output 3. According to Figures 8a) and 8b), the switching device 6 is positioned identically to that in Figures 7a) and 7b); i.e., the switching device 6 is displaced toward 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 input torque to the hub 11 and thus to the shaft 7.

[0151] As already described, the clamping bodies 18 divide the input torque or the incoming tangential force generated thereby 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 due to the fact that the clamping bodies 18 are arranged diagonally between input 2 or ramps 16 and output 3 or web 13, as shown in Figure 8b.

[0152] 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.

[0153] The axial force component or the axial force of all clamping bodies 18 reaches a level that exceeds the spring force of the disc spring 26, so that the disc spring 26 is compressed, as shown in Figures 8a) and 8b). The reason for the compression of the disc spring 26 is the displacement of the hub 11, which is made possible by the spline profiles 8, 12 of the shaft 7 and the hub 11.

[0154] 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.

[0155] When the hub 11 is displaced in the axial direction A, the clamping bodies 18 rotate about the axial and tangential directions A, T. 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 causes 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, to rotate relative to each other. In other words, the angle between the clamping body 18, or its web 19, and the tangential direction T, increases (see also Figure 5).

[0156] In Figure 8c), it can be seen that the gearwheel 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 gearwheel 5A of the first clutch device 4 and the toothing of the switching device 6. Consequently, the input torque can be fully or partially transmitted in the circumferential direction U or in the tangential direction T between the gearwheel 5 and the internal toothing of the switching device 6.

[0157] As a result, the majority of the input torque is transmitted via the gear 5A of the first clutch device 4 and the gearing 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.

[0158] If the input torque now decreases, the procedure described above can be carried out in reverse order.

[0159] 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 is then transmitted entirely via the gear 5A of the first clutch device 4 and the toothing of the switching device 6 to the ring gear 14. Thus, for example, reversing is also possible. This also applies when a torque is transmitted from output 3 to input 2, for example, to enable recuperation.

[0160] Coupling device 19 web

[0161] Inlet 20 flange

[0162] Output 21 Spring element first clutch device 22 Control unit second clutch device 23 Ring elementA Gear / toothing 24 Ring element

[0163] Switching device 25 Nose A Ring gear 26 Spring

[0164] Shaft 27 retaining ring

[0165] Spline profile 28 pocket

[0166] Groove 29 first end 0 hollow cylindrical body 30 second end1 Hub 2 spline 3 web A axial direction4 ring gear T tangential direction5 spacer ring / spacer sleeve U circumferential direction6 ramps 7 stop 8 clamping body

Claims

Patent claims 1. A clutch device (1) for an electric or hybrid vehicle, comprising: an input (2) for connection to a motor and for receiving an input torque, an output (3) for connection to at least one vehicle wheel and for outputting a torque, a first clutch device (4) for disconnecting and for establishing a first power transmission path from the input (2) to the output (3), a second clutch device (5) for disconnecting and for 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 clutch device (4) is set up 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) for establishing the second power transmission path.

2. Clutch device according to claim 1, wherein the first clutch device (4) is further designed and constructed 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), as a result of which 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 relative to one another in the circumferential direction (U), as a result of which engagement of the toothing of the switching device (6) with the toothing of the second clutch device (5) can be produced with little expenditure of force 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) for each 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 designed as a hollow cylinder 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 on the input (2) in a rotationally fixed manner, wherein the second coupling device (5) has 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 on the shaft (7).

10. Coupling device according to one of the preceding claims, wherein the input (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 clutch device (4).

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