Switchable one-way clutch with friction clutch

Abstract

A switchable one-way clutch (1) has an electromagnetic actuation system (8) and a clutch mechanism (22), which is a friction clutch (15). The clutch mechanism comprises a clutch disc (6) which is connected to a cage (5) of the clamping body (4) in a form-fitting manner.

Description

Background Technology

[0001] Patent document DE 10 2010 031 508 B4 discloses a transmission device in which the shaft of a shaft module is supported in a housing by a sliding bearing. The wheel-shaped transmission element is constructed as a gear. A one-way clutch is arranged radially between the gear and the shaft. For this purpose, the gear has a gear hub, which is radially supported on the hub by means of a sliding bearing, and a clamping body runs radially outside the gear hub. The one-way clutch ring includes a clamping body ring located radially outside and rigidly connected to the shaft. The clamping body is arranged radially outside in the outer one-way clutch ring and radially between the outer one-way clutch ring and the gear hub. In this arrangement, the one-way clutch functionally connects the transmission element and the shaft.

[0002] US Patent 7,604,105 discloses an electromagnetically operated one-way clutch with a resilient clutch disc as its engagement mechanism. The clutch disc is coaxially arranged with a shaft, on which a clamping structure for the one-way clutch is also constructed. The resilient disc is form-fitted with a bridging member, which in turn is form-fitted with the cage of the one-way clutch, thereby forming a permanent form-fit connection between the clutch disc and the cage. The bridging member is axially fitted within the resilient clutch disc with a movable stroke, and when the electromagnetic actuator is energized, the disc, which has a ferromagnetic or magnetizable region, moves toward the magnetic coil by that amount. By energizing the electromagnetic actuator, the clutch disc is axially pulled toward the magnetic coil and supported there against rotation by a rotating bearing. With the aid of this bridging member, the cage of the one-way clutch is also briefly prevented from rotating, and the one-way clutch is switched.

[0003] In addition, other one-way clutches are disclosed in patent documents DE 11 2019 001 588 T5 and WO 2016 / 165 711 A1. Summary of the Invention

[0004] The purpose of this invention is to provide a switchable one-way clutch that has a simple structure, can transmit large torque, and can be manufactured at low cost.

[0005] The objective of this invention is achieved by the subject matter described in claim 1.

[0006] This invention specifies that the clutch mechanism is a friction clutch, which allows for repeated engagement and disengagement of the anti-rotational frictional connection between the cage and the second rail around the axis of rotation. The advantages of this type of clutch mechanism are particularly evident in that the relative movement / rotation between the cage and clamping structure of the one-way clutch achieves smooth braking without sudden stop shocks. In this way, controlled synchronous operation can be performed to compensate for relative movement deviations. The components of the one-way clutch (especially the cage) are protected from overload. Furthermore, this controlled braking prevents undesirable slippage between the actuator and the cage.

[0007] The clutch disc is arranged concentrically with the axis of rotation and is at least able to pivot relative to each track, that is, to selectively pivot and / or rotate about the axis of rotation in two circumferential directions.

[0008] The clutch disc and cage are circumferentially form-fitted around the axis of rotation such that the clutch disc can move axially relative to the cage within an axially defined travel, but remains permanently and anti-rotatably form-fittedly connected to the cage around the axis of rotation at any axial position within that travel. An exemplary configuration of this form-fitted connection is a plug-in connection, in which the clutch disc and cage can maintain relative axial movement without losing the form-fitted connection for torque transmission. In this case, the torque to be transmitted should be understood as a control torque necessary to stop or pivot the rotating cage, and consequently the mass forces and drag torques acting on the clamping bodies of the cage. The plug-in connection need not be directly constructed between the clutch disc and cage, but can be formed by a bridge designed as a separate component, through which the cage and clutch disc are connected to each other.

[0009] Another feature of this invention is that even when the magnetic field of the actuating device is activated, the ferromagnetic region of the clutch disc remains in a non-contact relative arrangement with the actuating device; that is, no direct contact occurs between the actuating device and the clutch disc in any operating state. The so-called ferromagnetic or magnetizable region refers to a region on the clutch disc that is axially attracted and / or repelled by the actuating device along the travel direction under the influence of the magnetic field generated by the actuating device. This invention intentionally avoids the direct contact between the clutch disc and the actuating device known in the prior art. This provides a beneficial effect, for example, eliminating the need for a rotary bearing between the actuating device and the clutch disc. The region can be designed as an annular surface or a hollow cylinder. Multiple regions can be described as circumferentially distributed around the axis of rotation and adjacent to each other.

[0010] A one-way clutch has a plurality of inner rails corresponding to the number of rows of clamping bodies. Additionally, a plurality of outer rails corresponding to the number of rows of clamping bodies are provided. The inner or outer rails of the one-way clutch are provided with clamping structures, which preferably have clamping ramps. The rails radially opposite the rails with clamping structures at radial clearances are raceways, which are preferably cylindrical in shape. The clamping bodies are arranged in a row circumferentially along the rotation axis of the one-way clutch, and radially positioned between the inner and outer rails. In a one-way clutch, each clamping body radially corresponds to a clamping ramp, and depending on different operating conditions, the clamping body may also alternately radially correspond to any section of the raceway. The raceway is constructed on the inner or outer rails, and is preferably an inner cylindrical rail or, more preferably, an outer cylindrical rail. The inner or outer rails of the one-way clutch (on which the clamping structures are constructed) are radially opposite the outer or inner raceways.

[0011] The one-way clutch may optionally have one or more rows of clamping bodies. A row consists of a predetermined number of clamping bodies arranged sequentially along the circumferential direction of the one-way clutch's rotation axis, and thus adjacent to each other in the circumferential direction. When there are multiple rows, each row is arranged adjacent to the others. In this case, either two rows of clamping bodies are opposite a common raceway, or each row is equipped with a separate raceway. In this case, the common raceway has a certain width along the axial direction, and the effective range of this width covers both rows of clamping bodies. If each raceway is a separate design, it is arranged adjacent to each other along the axial direction. Furthermore, the clamping ramps may be an integrated design that effectively covers both rows of clamping bodies axially, and each independent clamping ramp is arranged sequentially along the circumferential direction to collectively form a clamping structure. Alternatively, each of the multiple rows may be equipped with a corresponding clamping structure; each clamping structure consists of multiple clamping ramps arranged sequentially along the circumferential direction and is arranged adjacent to at least one other clamping structure along the axial direction. In any case, “arranged in sequence” means that these clamping ramps are directly continuous with each other in the circumferential direction, or in individual cases or always may form other elements such as retainers, grooves, etc. between two adjacent clamping ramps.

[0012] The inner rail, outer rail, clutch disc, and cage are arranged concentrically with the axis of rotation as their common central axis. The axis of rotation of the one-way clutch is also the axis of rotation of all rotating components of the clutch, and is defined as axially aligned regardless of their actual spatial orientation. Correspondingly, the radial direction is defined as the direction perpendicular to the axis of rotation.

[0013] The clamping body is positioned and guided by the cage and can pivot within the cage.

[0014] The fact that the clutch disc is arranged coaxially with the axis of rotation and is at least pivotally oriented relative to the rails means that the clutch disc is supported about the axis of rotation at least relative to two rails or, alternatively, relative to one of the rails.

[0015] One embodiment of the invention specifies that the friction clutch has at least one friction ring, which is rotatably connected to a second track about a rotation axis. The second track is a raceway for a clamping body, preferably constructed as an inner cylindrical or outer cylindrical shape. Furthermore, the friction ring has at least one first friction surface. The clutch disc has at least one second friction surface. The friction ring and clutch disc are optionally plate-type discs with annular planar friction surfaces, these friction surfaces corresponding to each other in a frictionally connected manner. Alternatively, the friction surfaces may also be constructed as inner conical and / or outer conical. The first and second friction surfaces are axially movable within an axial travel range to engage in a frictionally fitted functional connection. "Engagement" refers to establishing a frictional connection with or without slip between the clutch disc and the friction ring. "Disengagement" refers to separating the aforementioned frictional fit. The advantage of this design is that the manufacturing process of such friction rings and friction surfaces is simple and inexpensive. Whether it is suitable for wet working conditions (i.e., working in the environment of lubricant action, preferably using metal friction surfaces) or dry working conditions (e.g. using friction linings), it can be conveniently and cost-effectively manufactured in both mass production and small-batch production scenarios.

[0016] One design of the present invention specifies that the area and the actuating device are spaced apart from each other by a distance greater than the axial travel, without contact. This ensures that, even when using the maximum travel, the actuating device and the clutch disc remain spaced apart and do not contact each other.

[0017] Another design embodiment of the invention specifies that the form-fitting connection comprises at least two form-fitting elements. Optionally, a first form-fitting element is constructed on the cage and / or clutch disc, and the first form-fitting element constitutes at least one axially extending first protrusion having a polygonal or rounded cross-section. The protrusion is embedded in a first gap of a second form-fitting element allocated anti-rotationally to the clutch disc and / or cage. Exemplary structures of such form-fitting connections include fork-joint type connections or interlocking claw-like connections and plug-in connections. For example, these gaps are constructed in profiles such as fork structures or U-shaped / open / closed box types. Such connections are easy to manufacture and inexpensive, and can be manufactured using sheet metal structures or processed into plastic injection molded parts, compression molded parts, or castings.

[0018] One design aspect of the invention specifies that an axially arranged or clamped resilient stop is positioned between the friction ring and the clutch disc, wherein the clutch disc is axially resiliently preloaded against the resilient stop, at least during the engagement of the friction-fitted connection. According to one embodiment, the stop is initially axially arranged between the friction ring and the clutch disc without preload, and then clamped between the friction ring and the clutch disc by a clutch disc moved by a magnetic field. Another alternative embodiment specifies that the resilient stop remains clamped between the clutch disc and the friction ring, and its preload increases with the travel of the clutch disc toward the actuation mechanism. This arrangement ensures that the friction-fitted connection reliably disengages again when the clutch mechanism is disengaged.

[0019] One design of the present invention specifies that the clutch disc is radially supported on a first shaft about a rotational axis and is axially movable, wherein a second track (i.e., a track designed as a cylindrical raceway) is anti-rotatably connected to the first shaft about the rotational axis. The term "shaft" encompasses all rotatably supported or supported components, and / or all components suitable for torque transmission. The first shaft is anti-rotatably connected to a clamping structure. Anti-rotation connection refers to an optional integral construction, or, for example, a construction via a ring pressed onto or into the shaft. One embodiment specifies that the first shaft is a gear, with a thin-plate sleeve press-fitted into the inner cylindrical receiving portion of the gear, and a clamping ramp constructed on the thin-plate sleeve. Another improved embodiment specifies that the second shaft is integrally constructed with the outer cylindrical raceway of the one-way clutch. This arrangement integrates all components of the one-way clutch into a self-holding assembly. This reduces assembly workload and saves assembly costs. The latter is particularly suitable for situations where, as specified in one embodiment of the invention, the first shaft and the third shaft are torsionally connected, for example, by spline engagement, wedge-tooth connection, or key connection, and the second shaft is rotatably supported on the third shaft. Here, the second shaft is preferably constructed as a journal with a one-way clutch raceway. The first shaft is exemplarily a gear that houses the one-way clutch on its inner side and is supported on the third shaft, which is configured as a gearbox shaft. This gearbox shaft may optionally be supported on or at another gearbox shaft, or within a gearbox housing.

[0020] According to an improved embodiment of the foregoing, the clutch disc is preferably supported on the first shaft radially and axially by a radial needle roller bearing. This means that the radial needle roller bearing, which was originally only applicable to radial support, is given a new application according to the present invention, namely, as an axial sliding bearing, enabling low-friction movement of the clutch disc within its axial travel range. The radial load component of this needle roller bearing is small, as it only needs to provide radial rotational support for the clutch disc under no significant load. The friction between the needle rollers and the first shaft occurs in the line contact area between the needle rollers of the needle roller bearing and the cylindrical raceways on the first shaft (integrally constructed or provided on the sleeve). Due to the small radial load, this friction can also be kept at a low level. The advantage of this design is that this needle roller bearing structure for the clutch disc can be directly implemented using standard needle roller bearings already available in the product catalog, suitable for various application scenarios and mass-producible, at a low cost. Attached Figure Description

[0021] The present invention will be further described in detail below through embodiments.

[0022] Figure 1 A shaft module 50 is shown, which is equipped with a switchable one-way clutch 1. The figure is a longitudinal sectional view along its axis of rotation 12.

[0023] Figure 2 It shows Figure 1 The enlarged view A shows the clutch mechanism 22 of the one-way clutch 1 in an axially engaged state.

[0024] Figure 3 It shows Figure 1 The enlarged view A shows the clutch mechanism of the one-way clutch 1 in an axially disengaged state.

[0025] Figure 4 A partial cross-sectional view of the one-way clutch 1 is shown, in which the one-way clutch is switched to a locked state in another direction of rotation.

[0026] Figure 5 It shows Figure 4 The corresponding partial view shows that, in this figure, the one-way clutch 1 is switched to the reverse one-way locking working mode.

[0027] Figure 6 for Figure 4 In the corresponding partial view, the one-way clutch 1 in the figure is in a free-running state.

[0028] Figure 7 A three-dimensional structural view of the one-way clutch 1 is shown, with the clutch disc 6 arranged axially spaced from the one-way clutch, and shown in an exploded view.

[0029] Figure 8 A longitudinal sectional view of another embodiment of the shaft module 60 is shown, the sectional view being cut along its axis of rotation 12.

[0030] Figure 9 A partial cross-sectional view of the one-way clutch 61 of the shaft module 60 is shown, in which the one-way clutch is in a free-running state.

[0031] Figure 10 A partial cross-sectional view of the one-way clutch 61 of the shaft module 60 is shown, in which the one-way clutch is switched to a one-way locking operating mode. Detailed Implementation

[0032] Figure 1 The one-way clutch 1 is constructed in a double-row configuration, having two axially adjacent first tracks 2 with identical profiles, and two axially adjacent second tracks 3 with identical profiles. Each first track 2 is arranged opposite to one second track 3 at a radial gap 9 extending around the rotation axis 12. Two rows of cylindrical clamping bodies 4 32, 33 are radially arranged in the radial gap 9, located between the first tracks 2 and the second tracks 3 respectively, and housed within a retainer 5. Each first track 2 is provided with a clamping structure 10, which is integrally constructed and axially spans both first tracks 2. Each second track 3 is provided with an outer cylindrical raceway 37 for the clamping body 4, which is integrally constructed and axially spans both second tracks 3.

[0033] The switchable one-way clutch 1 is further provided with an electromagnetic actuator 8 and a clutch mechanism 22. The clutch mechanism 22 has a clutch disc 6, which is coaxially arranged with the rotation axis 12 and has at least one annular, disc-shaped ferromagnetic or magnetizable region 55. The region 55 is constructed in the material of the clutch disc 6 and is symbolically marked by a bold vertical line in the figures. The material of the clutch disc 6 may be either a ferromagnetic metal or plastic. In the latter case, the plastic is doped with a magnetizable or magnetic material in this region. Alternatively, the region 55 is embedded in and fixed to the clutch disc 6. The electromagnetic actuator 8 is provided with an energized magnetic coil 34 and a housing 35. The magnetic coil 34 and the region 55 are arranged opposite each other such that when the magnetic coil 34 is energized, the region 55 is in its magnetic field.

[0034] The shaft module 50 consists of a one-way clutch 1, a gear 51, a third shaft 31, and tapered roller bearings 41 and 42. The first shaft 28 of the one-way clutch 1 is a one-way clutch hub, integrally constructed with the second track 3, i.e., rotatably and anti-rotatably connected to the outer cylindrical raceway 37 around the rotation axis 12. The second shaft 30 of the one-way clutch is rotatably supported on the third shaft 31 via a sliding bearing 43. The second shaft 30 is also constructed as the housing of the gear 51 of the shaft module 50 and the one-way clutch ring 44. The first shaft 28 is anti-rotatably connected to the third shaft 31 via a wedge-shaped tooth 38. The third shaft 31 is provided with the wedge-shaped tooth 38, a bearing seat 39 for the sliding bearing 43, and the teeth 40 of the gear 52 integrally constructed with the third shaft 31, and is equipped with tapered roller bearings 41 and 42.

[0035] The first shaft 28 is connected to the third shaft 31 and the gear 52 constructed on the third shaft 31, and can therefore rotate together about the rotation axis 12. The second shaft 30, which has a clamping structure 10, and the gear 51 are constructed together and supported on the third shaft 32 by a sliding bearing 43, which allows rotation about the rotation axis 12 relative to the first shaft 28 when the clutch mechanism 22 is disengaged. The anti-rotational frictional connection between the cage 5 and the second track 3 about the rotation axis 12 can be repeatedly engaged and disengaged via the clutch mechanism 22 by the axial movement of the clutch disc 6 within a limited axial travel.

[0036] Figure 2 – The clutch mechanism 22 is a friction clutch 15. The friction clutch 15 has a friction ring 20. The friction ring 20 is rotatably connected to the second track 3 about the rotation axis 12 in an anti-rotational manner, and is provided with at least one first friction surface 19 configured as an inner cone. The clutch disc 6 has a second friction surface 21 configured as an outer cone. The second friction surface 21 is coupled to the cage 5 via the clutch disc 6. The clutch disc 6 is rotatably radially supported on the first shaft 28 about the rotation axis 12 by a radial needle roller bearing 29 and is axially movable. The movable interface of the clutch disc 6 relative to the first shaft 28 is formed by the line contact between the needles 48 of the radial needle roller bearing 29 and the bearing raceway 49 on the first shaft 28.

[0037] like Figure 2 As shown, the clutch disc 6 is in its final position, which is the position occupied by the clutch disc 6 after moving to the right as shown in the figure, thereby disengaging the clutch mechanism 22. The first shaft 28, the third shaft 32, and the gear 52 constructed on the third shaft 32 (only partially visible in this figure; see appendix for details) are also shown. Figure 1The first shaft 30 is connected to the clamping structure 10 and the gear 51, and can be rotatably supported around the rotation axis 12. The second shaft 30 is constructed together with or connected to the clamping structure 10 and the gear 51. When the clutch mechanism 22 is in the disengaged state, the second shaft 30 can rotate around the rotation axis 12 relative to the first shaft 28.

[0038] In the disengaged state, the clutch disc 6 is positioned such that the distance between the clutch disc 6 or its end face 36 and each profile of the actuator 8 that protrudes axially from the end face 54 of the actuator 8 at its furthest point is composed of the travel H and the safety distance A. The second friction surface 21 of the clutch disc 6 separates from the first friction surface 19 of the friction ring 20 upon disengagement. The clutch disc 6 is connected to the cage 5 by a form-fit connector 18 such that, even in this operating state, a torsional connection is formed between the cage 5 and the clutch disc 6 in the circumferential direction about the axis of rotation 12. This means that the clutch disc 6, which can move axially relative to the cage 5 within the axially limited travel H, is anti-rotatably connected to the cage 5 about the axis of rotation 12, and even when the clutch disc 6 moves away from the cage 5 away from the friction ring 20 by the entire travel H relative to the cage 5, the clutch disc 6 always maintains a form-fit connection with the cage 5.

[0039] Figure 3 – The second friction surface 21 of the clutch disc 6 is frictionally connected to the first friction surface 19 of the friction ring 20, meaning the clutch mechanism 22 is engaged. The stroke H is zero. The distance between the clutch disc 6 and each axially projecting profile on the actuating device 8 towards the end face 36 is equal to the safety distance A. The end face 36 on the clutch disc 6 opposite to the actuating device 8 is spaced apart from the farthest axially projecting profile on the actuating device 8 by the safety distance A, the minimum of which is always greater than zero. Therefore, even when the magnetic field of the magnetic coil 34 is engaged, the clutch disc 6 (particularly region 55) and the actuating device 8 are arranged opposite each other without contact in all operating states.

[0040] In the engaged state, each clamping body 4 forms an active connection through the retainer 5. The signal is transmitted from the retainer 5 to the clutch disc 6 via the form-fitting connector 18, then through the two friction surfaces 19 and 21 in a friction-fitting state to the friction ring 20 of the first shaft 28, and from the friction ring 20 to the second track 3 integrated within the first shaft 28, i.e., to the raceway 37. The one-way clutch 1 is in the locked state, thus forming a clamping connection between the first shaft 28 and the second shaft 30 in the one-way clutch 1 via the clamping bodies 4. The three shafts 28, 30, and 31 rotate together.

[0041] The one-way clutch ring 44 has a first track 2, i.e., a track with a clamping structure 10. The one-way clutch ring 44 is a sheet metal part manufactured by cold forming process, having a cylindrical sleeve 45 and a flange 46 extending radially inward from the sleeve 45 towards the rotation axis 12. The cylindrical sleeve 45 is firmly pressed into the inner cylindrical hole 47 of the second shaft 30.

[0042] Figure 4 The clamping structure 10, constructed on the first track 2, consists of a single clamping ramp 11 extending circumferentially tangentially. These clamping ramps are arranged in a row along the rotation axis 12 (not visible in this part) of the one-way clutch 1 and are sequentially constructed on the inner side of the sleeve 45. The outer cylindrical second track 3 for clamping body 4 is radially opposite to the first track 2 at the radial clearance 9. The clamping body 4 is held between tracks 2 and 3 because the clamping body 4 rolls onto the clamping ramp 11 arranged counterclockwise in the figure by the pivoting action of the retainer 5 at the form-fit connector 18. The operating state shown in the figure is similar to... Figure 3 The operating state shown is consistent, that is, the clutch mechanism 22 is in the engaged state.

[0043] Figure 5 As shown, clamping body 4 is held between rails 2 and 3 because clamping body 4 rolls onto clamping ramp 11 as the cage 5 pivots. The operating state shown in the figure is similar to... Figure 3 The operating state shown is consistent with that of clutch mechanism 22 being engaged. However, in this state, it is consistent with... Figure 4 Compared to the position shown, the clamping body 4 has rolled onto the clamping ramp 11 in the clockwise rotation direction.

[0044] Figure 6 –The working status and attachments shown in this view Figure 2 The working state shown corresponds to the clutch mechanism 22 being in the disengaged state. The clamping bodies 4 are respectively positioned within the gaps 53 constructed between the two adjacent clamping ramps 11, and are therefore no longer in the clamped state. Rails 2 and 3 can rotate freely and independently.

[0045] Figure 7 – The form-fitting connector 18 is composed of at least two form-fitting elements 13, 14. A corresponding first form-fitting element 13 is constructed on the cage 5 and is designed as an axial extension 23. As shown in the accompanying drawing, each protrusion 23 is respectively opposite to a gap 25 on the clutch disc 6, the gap being defined or formed by the second form-fitting element 14. Alternatively, viewed from another direction, an axial protrusion 24 may be constructed on the clutch disc 6, each axial protrusion being opposite to a gap 26 between two protrusions 23 on the cage 5. In the assembled state, each protrusion 23 or 24 is inserted into the gap 25 or 26.

[0046] Figure 8 , Figure 9 and Figure 10 – The structure of shaft module 60 is basically similar to that of the aforementioned shaft module 50. However, it differs in some specific features described below. The operating principles of the one-way clutches 1 and 61 are basically the same; therefore, the relevant descriptions above, taking into account the design differences described below, also apply to shaft module 60.

[0047] Figure 8 – Unlike the one-way clutch 1, the one-way clutch 61 has a single-row structure, that is, it is constructed with a row of clamping bodies 64. The clamping bodies 64 are housed within the retainer 65. The first track 2 has a clamping structure 10 on the sleeve 45. The second track 3 is provided with an outer cylindrical raceway 37 for the clamping bodies 64.

[0048] The switchable one-way clutch 61 is also equipped with the electromagnetic actuation device 8 and the clutch mechanism 22 described above. The structure and working principle of the clutch mechanism 22 and the actuation device 8 are exactly the same for both the one-way clutch 1 and the one-way clutch 61.

[0049] Shaft module 60 comprises a one-way clutch 61, a gear 51, and a third shaft 31. The first shaft 28 of the one-way clutch 61 is a one-way clutch hub, integrally constructed with the second track 3, i.e., rotatably and anti-rotatably connected to the outer cylindrical raceway 37 around the rotation axis 12. Unlike the structure of shaft module 50, the second shaft 30 of the one-way clutch 61 is rotatably supported on the needle roller assembly of the third shaft 31 via a needle roller assembly 57, consisting of needle rollers 59 guided within and in the retainer 65 of the needle roller assembly 57. The second shaft 30 is also constructed as the housing for the gear 51 and the one-way clutch ring 44 of shaft module 60. The first shaft 28 is torsionally connected to the third shaft 31 via wedge-shaped teeth 38. The third shaft 31 has partial wedge-shaped teeth 38, a bearing raceway 66 for the needle roller assembly 57, and teeth 40 of the gear 52 integrally formed on the third shaft 31.

[0050] The first shaft 28 is connected to the third shaft 31 and the gear 52 constructed on the third shaft 31, and can therefore rotate together about the rotation axis 12. The second shaft 30, having a clamping structure 10, is integrally constructed with the gear 51, and when the clutch mechanism 22 is in the disengaged state, it can be rotatably supported on the third shaft 32 about the rotation axis 12 relative to the first shaft 28 by means of the needle roller assembly 57. By means of the clutch mechanism 22, the anti-rotational frictional engagement between the cage 65 and the second track 3 about the rotation axis 12 can be repeatedly engaged and disengaged by means of the axial movement of the clutch disc 6 within the axially defined stroke. The friction ring 67 differs from the friction ring 20 of the one-way clutch 1 in that the friction ring is a split structure assembled from parts, wherein the friction surface 19 is constructed on a conical ring 68 made of plates fixed to the one-way clutch hub. An elastic stop 27 is constructed between the friction ring 67 and the end face of the clutch disc 6. In this case, the elastic stop is constructed as a wave spring or a disc spring. The elastic stop 27 is clamped at least when the clutch mechanism 22 is engaged to the maximum extent, so that the friction surfaces 19 and 21 are completely separated from each other.

[0051] Figure 9 – The form-fitting connector 62 shown is used to form-fit the cage 65 and the clutch disc 67, which is illustrated in this drawing only by form-fitting elements 13 or protrusions 23; this form-fitting connector 62 is distinct from the form-fitting connector 18 in the previously described one-way clutch 1. Each first form-fitting element 13 is optionally constructed on the cage 65 or the clutch disc 6 and designed as an axial protrusion 23. Each protrusion 23 is inserted into a hollow profile 63 designed with an open box-shaped cross-section, which constitutes a second form-fitting element 14. The form-fitting element 14 is constructed on the cage 65 or the clutch disc 6, or arranged as a bridging element between the cage 65 and the clutch disc 6. The diagram illustrates the working state and… Figure 2 The state shown is similar—that is, it should be understood that the clutch mechanism 22 is in the disengaged state. Each clamping body 64 is positioned in the gap 53 constructed between two adjacent clamping ramps 11, and is therefore no longer in the clamped state. Tracks 2 and 3 can operate freely and independently.

[0052] Figure 10 – As shown, the clamping body 64 is clamped between the tracks 2 and 3 because the retainer 65 pivots at the form-fit connector 62, causing the clamping body 64 to roll onto the clamping ramp 11, which is arranged in the counterclockwise rotation direction as shown in this figure. Figure 10 The working status shown is the same as Figure 3 The state shown is similar and should be understood as the clutch mechanism 22 being in the engaged state.

[0053] List of reference numerals 1. Switchable one-way clutch 2 First Track 3 Second track 4 clamping bodies 5 cages 6-clutch disc 7 Friction Device 8 Actuators 9 Radial clearance 10 clamping structures 11 Clamping the inclined plane 12 Rotation Axis 13 Shape-Matching Components 14 Shape-Matching Components 15 Friction Clutch 16-shell 17 regions 18 Shape-fitting connectors 19 First friction surface 20 friction ring 21 Second friction surface 22 clutch mechanism 23 First protrusion 24 Second protrusion 25 First gap 26 Second gap 27 Flexible Stop 28 First Axis 29 Radial Needle Roller Bearing 30 Second Axis 31 Third Axis 32 First row of clamping bodies 33 Second row clamping body 34 Electromagnetic coils of the actuation device 35 Actuator Housing 36 Clutch disc end face 37-rollway 38 wedge-shaped teeth 39 bearing housing 40 teeth 41 tapered roller bearing 42 tapered roller bearing 43 sliding bearing 44 One-way Clutch Ring 45 sleeve 46 flange 47 Inner Cylindrical Hole 48 radial needle roller bearing needle rollers 49 radial needle roller bearing raceway 50-axis module 51-axis module gear 52 Gear on the third shaft 53 gaps 54 Actuator end face Area 55 56 Wave springs or disc springs 57 needle roller assembly 58 needle roller assembly cage 59 Needle roller assembly needles 60-axis module 61 One-way Clutch 62 Shape-fit connector 63 Hollow Profile 64 clamping body 65 cage 66 bearing raceway 67 Friction Ring 68 conical ring A safe distance H-axis travel.

Claims

1. A switchable one-way clutch (1, 61) comprising: at least one first rail (2) and at least one second rail (3), a plurality of clamping bodies (4, 64), at least one retainer (5, 65), an electromagnetic actuator (8), and a clutch mechanism (22), wherein - The first track (2) and the second track (3) are radially opposed to each other at a radial gap (9) extending about the axis of rotation (12). - The first track (2) is provided with at least one clamping structure (10), wherein in the clamping structure (10), a plurality of individual clamping ramps (11) are arranged in a row around the rotation axis (12) of the one-way clutch (1, 61). - The second track (3) is provided with raceways (37) for the clamping bodies (4, 64), and the second track is rotatable relative to the first track (2) about the axis of rotation (12). - The clamping bodies (4, 64) are radially arranged between the rails (2, 3) in the radial gap (9) and housed in the retainer (5, 65). - The clutch mechanism (22) has at least one clutch disc (6), which is arranged concentrically with the rotation axis (12) and has at least one ferromagnetic or magnetizable region (55). -The region (55) is opposite to the on / off magnetic field of the actuation device (8). Its features are, The clutch mechanism (22) is a friction clutch (15), wherein -The anti-rotational frictional engagement between the cage (5, 65) and the second track (3) around the axis of rotation (12) via the friction clutch (15) can be repeatedly engaged and disengaged. - The clutch disc (6) is arranged to be axially movable relative to the tracks (2, 3). The clutch disc (6) and the cage (5, 65) are connected in a form-fitting manner (18, 62) in the circumferential direction about the axis of rotation (12) such that the clutch disc (6, 67), which is axially movable relative to the cage (5, 65) within an axially limited axial travel (H), is anti-rotatably and permanently connected to the cage (5, 65) about the axis of rotation (12) in a form-fitting manner. - When the magnetic field of the actuating device (8) is turned on, the region (55) is opposite to the actuating device without contact.

2. The switchable one-way clutch according to claim 1, characterized in that, The friction clutch (15) has at least one friction ring (20, 67), wherein the friction ring (20, 67) is rotatably connected to the second track (3) about the rotation axis (12) and has at least one first friction surface (19), and the clutch disc (6) has at least one second friction surface (21), wherein the second friction surface (21) is axially movable within the axial travel (H) and engages with the first friction surface (19) of the friction ring (20, 67) to form a frictional engagement, wherein the second friction surface (21) is coupled to the cage (5) through the clutch disc (6).

3. The switchable one-way clutch according to claim 1, characterized in that, The region (17) and the actuation device (8) are separated from each other by a distance (A) that is not in contact, the distance being greater than the axial travel (H).

4. The switchable one-way clutch according to claim 2, characterized in that, The friction surfaces (19, 21) are constructed in a conical shape.

5. The switchable one-way clutch according to any one of the preceding claims, characterized in that, The shape-fitting connector (18) is composed of at least two shape-fitting elements (13, 14), wherein a first shape-fitting element (13) of the shape-fitting elements (13, 14) is constructed on the cage (5, 65), the first shape-fitting element forming at least one axially extending first protrusion (23), wherein the first protrusion (23) is embedded in a second shape-fitting element (14) anti-rotationally assigned to the clutch disc (6), and / or, a second shape-fitting element (14) of the shape-fitting elements (13, 14) is constructed on the clutch disc (6) or the cage (5, 65), and at least one second protrusion (24) of the second shape-fitting element is embedded in the gap (25, 26) of the first shape-fitting element (13) or the second shape-fitting element (14).

6. The switchable one-way clutch according to any one of the preceding claims, characterized in that, An elastic stop (27) is axially arranged or clamped between the friction ring (67) and the clutch disc (6), wherein, in the engaged frictional engagement connection, the clutch disc (6) is axially elastically preloaded against the elastic stop (27).

7. The switchable one-way clutch according to any one of the preceding claims, characterized in that, The clutch disc (6) is rotatably supported radially on the first shaft (28) about the rotation axis (12) and is axially movable, wherein the second track (3) is anti-rotatably connected to the first shaft (28) about the rotation axis (12).

8. The switchable one-way clutch according to claim 7, characterized in that, The second track (3) is directly constructed on the first shaft (28), and / or the clutch disc (6) is radially supported on the first shaft (28) by at least one radial needle roller bearing (29) and is axially movable.

9. The switchable one-way clutch according to any one of the preceding claims, characterized in that, The first track (2) is constructed or fixed on the second shaft (30), which is rotatable relative to the first shaft (28) about the axis of rotation (12).

10. The switchable one-way clutch according to claim 9, characterized in that, The first shaft (28) is torsionally connected to the third shaft (31), and the second shaft (30) is rotatably supported on the third shaft.

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