Overload clutch device

Abstract

The invention provides an overload clutch device. The invention relates to an overload clutch device, through which a longitudinal axis passes, comprising:-a guide device,-at least one latch element, which is movably received in a bore of the guide device,-a structural component, which has a latch receptacle, in which the latch element can be selectively engaged, and-a displacement element which can be moved along the longitudinal axis and which can displace the at least one latch element into the latch receptacle,-wherein the at least one latch element can be adjusted between a latch position, in which the at least one latch element can be moved away from the latch receptacle, and an idle position, in which the at least one latch element can be moved away from the latch receptacle. The at least one latch element engages in its latch receptacle and rotationally fixedly couples the guide device to the structural member, and an idle position in which the at least one latch element is arranged outside its latch receptacle and allows the structural member to idle relative to the guide device.

Description

TECHNICAL FIELD

[0001] The present invention relates to an overload clutch device. BACKGROUND

[0002] Overload clutches arranged between a drive side and an output side are known in practice. In the event of an overload, they interrupt the mechanical force transmission path in order to protect components from damage. However, the previously known overload clutches require a large installation space and / or do not have a satisfactory functional range and / or cannot achieve a long service life. SUMMARY

[0003] It is therefore an object of the present invention to overcome the above-mentioned problems.

[0004] The features according to the invention are specified in the following overload clutch device.

[0005] According to the invention, an overload clutch device is proposed, a longitudinal axis passing through the overload clutch device, the overload clutch device comprising a guide device, at least one latching element which is movably received in a bore of the guide device, a structural component having a latching accommodation in which the latching element can be optionally engaged, and a displacement element which is movable along the longitudinal axis and which can displace the at least one latching element into the latching accommodation, wherein the at least one latching element is adjustable between a latching position, in which the at least one latching element is engaged in its latching accommodation and couples the guide device to the structural component for co-rotation, and an idling position, in which the at least one latching element is arranged outside of its latching accommodation and allows the structural component to idle relative to the guide device.

[0006] The overload clutch device comprises a displacement element to displace at least one latching element into a latching accommodation to achieve a latching position. This makes it possible to implement a mechanical force flow path in a simple manner. Rotational fixing means that the elements involved are fastened directly or indirectly to one another and that they can rotate together about a common rotational relationship. In the rotational fixed state, the elements involved can remain relatively stationary relative to one another. In the event of an overload, at least one latching element can be pushed out of its latching accommodation to achieve an idling position. A torque that can be present on the drive side or on the output side can trigger the overload. In the event of an overload, the latching element can be pushed out of its latching accommodation, for example by a structural component. This can interrupt the mechanical force flow path. In the event of an overload, at least one latching element can be pushed against the displacement element by the structural component, whereby the guide device is separated from the structural component (idling position). When the overload is alleviated or falls below the overload triggering torque, the latching element can again be returned into its latching accommodation to again produce a mechanical force flow path. In particular, components can be protected from damage by the latching element and the displacement element, wherein the overload clutch device according to the application requires little installation space, thus providing a desired functional range and being associated with a long service life. The components to be protected can be, for example, a drive and transmission components.

[0007] The overload clutch device can be arranged between a drive side and an output side. The guide device can be arranged on the drive side and the structural component can be arranged on the output side. The latching element can be a boundary element between the drive side and the output side. The latching element can produce a form fit and / or a force fit with its latching accommodation in the latching position. The latching element can be adjusted in its position in the radial direction relative to the longitudinal axis. The bore can extend in the radial direction relative to the longitudinal axis. This allows the latching element to be guided in the radial direction. The guide device, the latching element, the displacement element and / or the components can be formed separately from one another. This allows freedom of design. The displacement element has an outer circumferential surface on which the at least one latching element, preferably in both positions thereof, is located. The structural component can be arranged on the outer circumferential side of the guide device, the at least one latching element and / or the displacement element relative to the longitudinal axis. This allows a compact construction without a large installation space along the longitudinal axis. The term structural component refers to the structural component mentioned above. The structural component can be a structural component that can be rotated about the longitudinal axis. The structural component can be designed to be fixedly connected to an output shaft. The structural component can be a connecting element to the output shaft. The structural component can be the output shaft or a part of the output shaft. For this purpose, the structural component can have an internal and / or external toothing.

[0008] According to an conceivable refinement, the overload clutch device can comprise a plurality of latching elements and a corresponding number of latching receptacles. The latching elements and the latching receptacles can each be distributed equidistantly about the longitudinal axis. This serves for uniform engagement of the latching elements in the latching receptacles. The latching elements can be movably received in a respective hole of the guide device. The latching receptacles can be formed in the structural component.

[0009] According to an conceivable refinement, the displacement element can contactingly abut the structural component in the latching position. This makes it possible to precisely position the displacement element and to define the end position. Furthermore, this contact serves for the adjustability of the precisely defined pretensioning force of the spring device. For reasons of optimized installation space, it is conceivable that an end face of the displacement element contacts the structural component in the latching position.

[0010] According to an improvement, the guide device can be a cage sleeve ) and / or can be arranged in the force flow path or can be arranged in the force flow path. The guide device is advantageously a sleeve, and further components can therefore be arranged inside it in order to save installation space. The force flow path can extend through the cage sleeve. The cage sleeve can have fastening surfaces on the outer circumferential side and / or on the inner circumferential side. The cage sleeve can be fixedly connected to the gearwheel via the fastening surfaces. For example, it is conceivable that the guide device forms a form-fit and / or force-fit connection with the gearwheel. For example, it is conceivable that the guide device forms a hexagonal stub, to which the gearwheel is fastened with a corresponding hexagonal socket. This saves installation space inside the cage sleeve. The cage sleeve can be a separate component of the gearwheel. This reduces production costs and increases the design freedom. For example, the cage sleeve can be the same component, and the gearwheel can be adapted to the respective overload clutch device. Furthermore, this serves for the use of respectively independent materials in order to exploit the respective specific material properties.

[0011] According to an improvement, the latching elements can be balls. This makes self-alignment of the latching elements unimportant, since the balls can be brought into position in each self-alignment. Furthermore, balls are particularly suitable for withstanding the impact of the structure component driven by the overload in the idling position over a long service life, which can be moved relative to the ball. Furthermore, the balls can easily be moved between their positions. For example, the balls can interact with the displacement element in a simple manner and can be pushed out of the latching receptacles by this in the event of an overload.

[0012] According to an improvement, the displacement element can comprise an outer diameter which tapers along the longitudinal axis, preferably in the direction of the structural component. A displacement element configured in this way can exert a radially outward force on the at least one latching element depending on its own position along the longitudinal axis. The displacement element can be a cone with a straight or curved outer surface. The conical outer circumferential surface can displace the latching element radially outward into the latching accommodation. The latching element can also adjust the displacement element along the longitudinal axis via the conical outer circumferential surface.

[0013] According to one conceivable embodiment, the conical outer circumferential surface can be at an angle to the longitudinal axis when viewed in a longitudinal section, which angle can be in the range from 10° to 45°, preferably 10°. This angle can be used to influence the radial displacement of the latching element and its release force.

[0014] According to one conceivable improvement, the overload clutch device can comprise a guide rod along which the displacement element is movably guided along the longitudinal axis. The guide rod can protrude through a guide hole in the displacement element, so that the displacement element is guided internally. The guide rod is a component separate from the displacement element. This reduces production costs and increases design freedom. The guide rod can pass through the guide device along the longitudinal axis or at least engage there. This allows the installation space to be used best.

[0015] According to an improvement, the overload clutch device can comprise a spring device, preferably a Tellerfederpaket, which pre-tensions the displacement element in the direction of the latching element, whereby the latching element is pre-tensioned into its latching position. The pre-tensioning can take place along the longitudinal axis. The combination of the spring force acting along the longitudinal axis, the displacement element, which is preferably a cone, and the latching element, which is preferably a ball and can be moved in the radial direction, results in an orthogonal effect chain. The spring device generates a spring force acting on the displacement element. The displacement element in turn transmits this spring force parallel to the longitudinal axis in the radial direction to the latching element via the conical outer circumferential surface. This enables a very compact design. In the event of an overload, the at least one latching element can be removed from its latching accommodation against the spring force in order to achieve the freewheel position.

[0016] According to an improvement, the overload clutch device can comprise an adjustment sleeve, which preloads the spring device in the direction of the latching element. The preload can comprise a pretensioning. Advantageously, the preload force can be adjusted by the installation position of the adjustment sleeve, for example when installing the overload clutch device. The adjustment sleeve can be arranged within the guide device or inside the cage sleeve. The adjustment sleeve is arranged there in order to save installation space. The adjustment sleeve can be connected to the guide device and / or to the guide rod by means of a force-fit and / or form-fit connection. Preferably by means of an interference fit. This allows the adjustment sleeve to be pressed and / or pressed into the desired degree.

[0017] According to an improvement, the overload clutch device can comprise a damping device. The damping device can be a damping ring and / or can be made of an elastomer material. The damping ring can be arranged within the guide device or inside the cage sleeve in order to save installation space and the guide rod can pass through it at the same time. The elastomer material is particularly suitable for damping vibrations. The damping device reduces the noise from the overload clutch device and leads to a smooth operation of the structural component.

[0018] According to an envisageable embodiment, the spring device, the damping device and the adjustment sleeve can be arranged adjacent to one another in this order along the longitudinal axis. This even further improves the effect of the damping device. It is envisageable that the spring device is supported at one end, preferably directly, against the displacement element and at the other end, preferably directly, against one of the adjustment sleeve or the damping device. This also serves to optimize the installation space.

[0019] According to an improvement, the structural component can have a recess on the end face, in which the latching receptacle and / or the latching element running surface is formed. This improvement saves installation space and leads to a compact design. The latching element / elements can be arranged within the recess, preferably in the latching position and in the idling position. The recess can face the displacement element. The latching element / elements can run on the latching element running surface, preferably in the idling position. This serves to ensure reliable guidance of the idling position.

[0020] According to an envisageable improvement, the latching element running surface can be formed on the inner circumference of the structural component and / or extend in the circumferential direction around the longitudinal axis. Thus, the latching element / elements can be guided radially from the outside.

[0021] According to an envisageable improvement, the latching element running surface can extend into the latching receptacle. Thus, the latching element can change directly from the latching receptacle (latching position) to the latching element running surface (idling position) and vice versa. This allows a design with little complexity. The latching element running surface can be interrupted by the latching receptacle / latching receptacles. The latching element running surface can be segmented in the circumferential direction.

[0022] According to one conceivable refinement, the latching element running surface can have a profile in the longitudinal section which corresponds to the outer profile of the latching element. This serves to firmly guide the latching element in the idling position. It is conceivable that the latching element is a ball, which is the reason why the latching element running surface can thus have a profile in the longitudinal section which corresponds to the circular arc profile of the ball. The latching element running surface can be a channel.

[0023] According to one refinement, the latching accommodation can

[0024] - have a width in the circumferential direction, which width is in the range from 0.5 to 1.5 times the diameter of the latching element, and / or

[0025] - have opposite side walls which extend parallel to one another or at an angle to one another in the range from 10° to 90°, and / or

[0026] - form, together with the latching element in the latching position, an engagement depth which is in the range from 0.1 to 0.45 times the diameter of the latching element, preferably 0.33 times the diameter, and / or

[0027] - have an entry edge which has a rounded corner with a radius, and / or

[0028] - have an exit edge which has a rounded corner with a radius.

[0029] With these refinements, the latching and unlatching of the latching element can be influenced, in particular facilitated or impeded, depending on the refinement. Depending on the refinement, this can interact with the structural refinement or refinement of the force aspect of the spring device and / or the structural refinement of the displacement element. The interaction of these three components can then be used to optimize the installation space. The entry edge and / or the exit edge can be an impact edge between the latching element running surface and the latching accommodation. This serves for a direct transition. The latching element can enter the latching accommodation via the entry edge, and the latching element can exit the latching accommodation via the exit edge.

[0030] According to an improvement, the guide rod can be fixedly connected to the structural member. The guide rod can be the guide rod described above. The guide rod can extend along a longitudinal axis. The guide rod can be rotatable about the longitudinal axis. Since the guide rod can be fixedly connected to the structural member, a rotation of the structural member can directly enter the guide rod. The guide rod can be a separate component from the structural member. This reduces production costs and increases design freedom. The guide rod serves to firmly guide the component along the longitudinal axis and / or to fasten the component to the guide rod for a firm positioning. It is conceivable that the guide rod passes through the displacement element, the spring device, the adjustment sleeve and / or the damping device. This serves to optimize the use of the installation space. It is conceivable that the guide rod is rotatable relative to the displacement element, the spring device, the adjustment sleeve and / or the damping device. This allows the guide rod to transmit the movement, and the mass to be moved remains at a minimum. It is conceivable that the guide rod comprises a friction-reducing device, such as a coating, on the outer circumferential side. Thus, the sliding friction between the guide rod and the adjacent components can be reduced, in particular with respect to components that protrude relatively movably through the guide rod. The guide rod also serves to mechanically couple components that are located further away locally. Thus, for example, a rotational movement introduced into the guide rod at one end can be transmitted to a sensor or sensor target arranged at the other end of the guide rod. This ensures an optimal use of the installation space, and the sensor / sensor target receives the exact position of the structural member or output shaft.

[0031] According to an improvement, the overload clutch device can comprise a sensor device, which sensor device comprises:

[0032] - a first sensor target, which first sensor target is rotationally fixed to the structural member,

[0033] - a second sensor target, which second sensor target is designed to be rotationally fixed to the drive shaft,

[0034] - a first sensor for sensing the first sensor target, and

[0035] - a second sensor for sensing the second sensor target.

[0036] The sensor can be a Hall sensor. The sensor can be designed to detect the rotational speed and / or the rotational position. The drive shaft can be surrounded by an overload clutch device. The overload clutch device can surround the driver. The driver can drive the drive shaft. The sensor device has many advantages. A first pair of sensors (first sensor, first sensor target) can be arranged on the output side to detect the output side rotational speed and / or rotational position. A second pair of sensors (second sensor, second sensor target) can be arranged on the drive side to detect the drive side rotational speed and / or rotational position. The respective status can thus be determined. Furthermore, a comparison of the output side rotational speed with the drive side rotational speed can provide information about overload events and load states. On the basis of a comparison of the output side rotational position and the drive side rotational position, it is also possible to readjust the drive shaft position after an overload event. Furthermore, in the event of an overload, the first sensor still detects the "actual" position of the output shaft and can still provide this information for the entire system.

[0037] According to one conceivable refinement, the first sensor target can be fastened to the guide rod. This ensures that the rotation of the guide rod and the sensor target is instantaneous. The first sensor target can be fastened to the end of the guide rod opposite the structural component. The installation space in the region of the structural component is thus free of sensor components.

[0038] According to one conceivable refinement, a plain bearing (Gleitlagerung) can be formed between the structural component on the one hand and the guide device and / or the gearwheel of the guide device on the other hand. This serves a compact design. In the event of an overload, the plain bearing can serve an idling position.

[0039] In summary, the spring device can generate a defined force on the displacement element, which force can be adjusted by the adjustment sleeve and acts along the longitudinal axis. The displacement element pushes with this force onto the at least one latching element, which is subjected to a force acting in the radial direction by means of the cone. This force pushes the at least one latching element radially outwards into the latching receptacle of the structural component or the output shaft. There is thus a form fit, and torque can be transmitted from the driver or transmission to the output shaft (latched position). In the event of an overload on the structural component or the output shaft, which can be defined as too great a torque, said overload generates a release force on the at least one latching element by means of the latching receptacle. If said release force is greater than the opposing force / force component of the spring force, the at least one latching element releases from the corresponding latching receptacle against said force / force component, and there is no longer a form fit (released position). Torque can thus no longer be transmitted; the clutch is thus unloaded and the transmission components are protected. As soon as the torque has been overcome, the at least one latching element latches into the latching receptacle again, and the torque of the driver can be transmitted again.

[0040] If features are disclosed which appear to be separate items, features can also be implemented in a single item. Similarly, if items are described or claimed in the singular, they can also be implemented in the plural, and vice versa, unless context clearly indicates otherwise. BRIEF DESCRIPTION OF DRAWINGS

[0041] Other features, details and advantages of the present application will become clear from the wording of the claims and the description of exemplary embodiments, given below, with reference to the drawings, in which:

[0042] Figure 1 a perspective view of the overload device is shown,

[0043] Figure 2 a cross-sectional view along the line II-II of Figure 1

[0044] Figure 3a a longitudinal cross-sectional view in the latched position is shown,

[0045] Figure 3b a cross-sectional view along the line IIIb-IIIb of Figure 3a

[0046] Figure 4a a longitudinal cross-sectional view in the idling position is shown,

[0047] Figure 4b a cross-sectional view along the line IVb-IVb of Figure 4a

[0048] Figure 5 a detailed view of Figure 1

[0049] Figure 6 a first view of the guide device is shown,

[0050] Figure 7 a perspective view of the guide device of Figure 6

[0051] Figure 8 a first view of the structural member is shown, and

[0052] Figure 9 a perspective view of the structural member of Figure 8

[0053] LIST OF REFERENCE SIGNS

[0054] 2 guide device

[0055] 2a cage sleeve

[0056] 2b inner part

[0057] 2c fastening surface

[0058] 4 bore​​​​​​

[0059] 6. Latch element

[0060] 6a ball

[0061] 8 Shifting elements

[0062] 8a Outer circumferential surface

[0063] 10 Structural Components

[0064] 12. Latch Receiving Section

[0065] 14. Spring device

[0066] 14a Disc Spring Assembly

[0067] 16 Adjusting sleeve

[0068] 18 Damping devices

[0069] 18a Damping Ring

[0070] 20 concavity

[0071] 22. Operating surface of latching element

[0072] 24 Inner circumference

[0073] 26. Entrance Edge

[0074] 28 Export Edge

[0075] 30 guide rod

[0076] 32 First Sensor Target

[0077] 34 Second Sensor Target

[0078] 36 drive shafts

[0079] 38 First Sensor

[0080] 40 Second sensor

[0081] 42. Shell

[0082] 44 drives

[0083] 46 Transmission components

[0084] 48 gears

[0085] 50 pilot hole

[0086] 52 Internal teeth

[0087] 54. Circular arc profile

[0088] 56 Sidewalls

[0089] A longitudinal axis

[0090] B width

[0091] G sliding bearing

[0092] K force flow path

[0093] S1 latched position

[0094] S2 idling position

[0095] U circumferential direction

[0096] W1 angle

[0097] W2 angle DETAILED DESCRIPTION

[0098] In the drawings, identical or mutually corresponding elements are each denoted by the same reference signs, so that they will not be described again unless it is expedient. In order to avoid repetitions, features already described will not be described again and are applicable to all elements having the same or mutually corresponding reference signs, unless this is explicitly ruled out. The disclosure in the specification can be transferred analogously as a whole to identical parts having the same reference signs or the same structural component names. The same applies to the position indications used in the specification, such as above / top, below / bottom, lateral, etc., which are related to the currently described and illustrated drawing and will be transferred analogously to the new position in the case of a change in position. Furthermore, individual features or combinations of features from different exemplary embodiments shown and described can also constitute an independent or inventive solution or a solution according to the application.

[0099] Figures 1 to 9 An embodiment of an overload clutch device is shown. In the housing 42, a drive 44, which drives the drive shaft 36, is arranged on the drive side. A transmission component 46, which transmits the drive force along a mechanical force flow path K to a gear wheel 48, is connected to the drive shaft 36. The gear wheel 48 is connected in a rotationally fixed manner to the guide device 2, which is in the form of a cage sleeve 2a.

[0100] The overload clutch device is traversed by a longitudinal axis A and comprises, in the embodiment shown, two latch elements 6 in the form of balls 6a and movably received in respective holes 4 of the guide device 2. An output-side structural member 10 is provided, which has two latch receptacles 12 for the latch elements 6. The latch elements 6 and the latch receptacles 12 are each distributed equidistantly around the longitudinal axis A. Furthermore, the overload clutch device comprises a displacement element 8, which is configured as a cone and is movable along the longitudinal axis A. Depending on its own positioning along the longitudinal axis A, the displacement element 8 can displace the latch elements 6 into the respective latch receptacle 12. A plain bearing G is formed between the structural member 10 on the one hand and the guide device 2 and / or the gearwheel 48 on the other hand. The plain bearing G is used in the event of an overload, if the structural member 10 rotates faster than the guide device 2 and the gearwheel 48 due to an overload. The structural member 10 has an inner toothing 52, to which an output shaft, not illustrated, can be fixedly connected.

[0101] The latch elements 6 are adjustable into a latching position S1 Figure 3a , in which they engage in the latch receptacles 12. In the latching position S1, the guide device 2 is rotationally fixedly coupled to the structural member 10. Along the mechanical force flow path K, the drive force of the driver 44 can then be transmitted to the structural member 10 or the output side. Due to an overload, the latch elements 6 are also adjustable into an idling position S2 Figure 3b , in which they are arranged outside the latch receptacles 12. In the idling position S2, the structural member 10 is allowed to idle relative to the guide device 2. In the event of an overload, the structural member 10 pushes the latch elements 6 out of the latch receptacles 12.

[0102] The latch elements are boundary elements between the drive side and the output side. The guide device 2 is arranged on the drive side and the structural member is arranged on the output side.

[0103] The guide device 2 as a cage sleeve 2a has an interior 2b and on the outer circumferential side has a fastening surface 2c designed on a hexagon, via which the gearwheel 48 is fixedly connected. The holes 4 extend in the radial direction R relative to the longitudinal axis A. The latch elements 6 are thus adjustable relative to the longitudinal axis A in the radial direction R between the positions S1, S2.

[0104] The displacement element 8, which is in the form of a cone, comprises an outer diameter which tapers in the direction of the structural component 10 along the longitudinal axis A. A conical outer circumferential surface 8a displaces the latch element 6 radially outward into the latch accommodation 12. Conversely, in the event of an overload, the latch element 6 can move the displacement element 8 along the longitudinal axis A via the conical outer circumferential surface 8a in order to displace itself out of the latch accommodation 12. The conical outer circumferential surface 8a is at an angle W2 to the longitudinal axis A when viewed in a longitudinal section.

[0105] The overload clutch device further comprises a spring device 14 in the form of a disc spring assembly 14a. The spring device 14 pre-tensions the displacement element 8 along the longitudinal axis A onto the latch element 6. This results in the latch element being pre-tensioned into the latching position S1. In the event of an overload, the latch element 6 is taken out of the latch accommodation 12 against the spring force of the spring device 14 in order to achieve the freewheeling position S2.

[0106] The overload clutch device further comprises an adjustment sleeve 16 which preloads the spring device 14 in the direction of the latch element 6. The adjustment sleeve 16 is arranged in the interior 2b and is connected to the guide device 2 by a force-fit and / or form-fit connection.

[0107] The overload clutch device further comprises a damping device 18 in the form of an elastomer damping ring 18a. The damping device 18 is arranged in the interior 2b and can be connected to the guide device 2 by a force-fit and / or form-fit connection.

[0108] The overload clutch device further comprises a guide rod 30 on which the displacement element 8 is movably guided along the longitudinal axis A. The guide rod 30 passes through a guide hole 50 in the displacement element 8, so that the displacement element 8 is guided internally. The guide rod 30 also passes through the guide device 2, the spring device 14, the adjustment sleeve 16 and the damping device 18 along the longitudinal axis A. The guide rod 30 is fixedly connected to the structural component 10 and is rotatable relative to the guide device 2, the spring device 14, the adjustment sleeve 16 and the damping device 18. The guide rod 30 extends along the longitudinal axis A, which it is rotatable about.

[0109] The structural component 10 has a recess 20 on an end face, in which the latch accommodation 12 and the latch element running surface 22 are formed. The guide device 2 engages in the recess 20 and the latch element 6 is arranged within the recess 20 in the latching position S1 and the freewheeling position S2. The recess 20 faces the displacement element 8. In the latching position S1, the latch element 6 is located in the latch accommodation 12, while in the freewheeling position S2, the latch element 6 runs on the latch element running surface 22.

[0110] The latching element running surface 22 is formed on an inner circumference 24 of the structural component 10 and extends in the circumferential direction U about the longitudinal axis A. As a result, the latching element 6 is externally guided radially. The latching element running surface 22 extends into the latching accommodation 12. Thus, the latching element can be changed directly from the latching accommodation 12 (latching position S1) to the latching element running surface 22 (idling position S2) and vice versa. The latching element running surface 22 is interrupted by the latching accommodation 12, it is therefore segmented in the circumferential direction U. In a longitudinal section, the latching element running surface 22 has a contour which corresponds to the outer contour of the latching element 6, which in the present case is a circular-arc contour 54 which corresponds to a ball. The latching element running surface SS is a channel.

[0111] The individual latching accommodations 12 can have a width in the circumferential direction U, the individual latching accommodations 12 can have opposite side walls 56, wherein the latter can extend parallel to one another or can be angled W1 to one another. The parallel configuration is shown in Figure 3b The angled configuration is depicted in Figure 4b In the latching position S1, the latching element 6 is located in the latching accommodation 12, the individual latching elements 6 protrude into the latching accommodation 12 by a distance which is designated as engagement depth E, each latching accommodation 12 has an entry edge 26 as well as an exit edge 28. The entry edge 26 as well as the exit edge 28 are impact edges between the latching element running surface 22 and the latching accommodation 12. The latching element 6 can enter the latching accommodation 12 via the entry edge 26 and the latching element 6 can exit the latching accommodation 12 via the exit edge 28.

[0112] The overload clutch device further comprises a sensor device comprising a first sensor target 32 which is rotationally fixed to the structural component 10, a second sensor target 34 which is rotationally fixed to the drive shaft 36, a first sensor 38 for sensing the first sensor target 32 and a second sensor 40 for sensing the second sensor target 34. The first sensor target 32 is fixedly arranged on the guide rod 30 at an end opposite the structural component 10. A first pair of sensors formed by the first sensor 38 and the first sensor target 32 is arranged on the output side. A second pair of sensors formed by the second sensor 40 and the second sensor target 34 is arranged on the drive side.

[0113] The invention is not limited to any one of the embodiments described above, but can be modified in various very broad ways. All features and advantages which are apparent from the claims, the description and the drawings, including structural details, spatial arrangements and method steps, are important for the invention, both individually and in various very broad combinations.

[0114] The present invention includes all combinations of at least two of the features disclosed in the specification, claims, and / or drawings.

[0115] For the avoidance of repetition, features disclosed in relation to the apparatus are also considered to be disclosed in relation to the method and can be claimed. The same applies to features disclosed in relation to the method being considered to be disclosed in relation to the apparatus and can be claimed.

Claims

1. An overload clutch device, a longitudinal axis (A) running through the overload clutch device, the overload clutch device comprising: - a guide device (2), - at least one latch element (6) which is movably received in a bore (4) of the guide device (2), - a structural component (10) having a latch receptacle (12) in which the latch element (6) can be selectively engaged, and - a displacement element (8) which is movable along the longitudinal axis (A) and which can displace the at least one latch element (6) into the latch receptacle (12), - wherein the at least one latch element (6) is adjustable between a latching position (SI) in which it is engaged in its latch receptacle (12) and rotationally fixedly coupled to the structural component (10), and an idling position (S2) in which it is arranged outside of its latch receptacle (12) and allows the structural component (10) to idle relative to the guide device (2).

2. An overload clutch device according to claim 1, characterised in that The guide device (2) is a cage sleeve (2a) and / or can be arranged or arranged in a force flow path (K).

3. An overload clutch device according to any one of the preceding claims, characterised in that, The latch element (6) is a ball (6a).

4. An overload clutch device according to any one of the preceding claims, characterised in that, The displacement element (8) comprises an outer diameter which tapers along the longitudinal axis (A), preferably in the direction of the structural component (10).

5. An overload clutch device according to any one of the preceding claims, characterised in that A spring device (14), preferably a disc spring assembly (14a), pre-tensions the displacement element (8) in the direction of the latch element (6), whereby the latch element (6) is pre-tensioned into its latching position (SI).

6. An overload clutch device according to claim 5, characterised in that An adjustment sleeve (16) pre-loads the spring device (14) in the direction of the latch element (6).

7. An overload clutch device according to claim 5 or 6, characterised in that A damping device (18).

8. An overload clutch device according to any one of the preceding claims, characterised in that, The structural component (10) has a recess (20) on an end face, the latch receptacle (12) and / or a latch element running surface (22) being formed in the recess (20).

9. An overload clutch device according to any one of the preceding claims, characterised in that, The latch receptacle (12) - has a width (B) in a circumferential direction (U) which is in the range of 0.5 to 1.5 times a diameter of the latch element (6), and / or - has opposite side walls (56) which extend parallel to one another or at an angle (W) to one another in the range of 10° to 90°, and / or - forms an engagement depth (E) with the latch element (6) in the latching position (SI) which is in the range of 0.1 to 0.45 times a diameter of the latch element (6), preferably 0.33 times the diameter, and / or - has an entry edge (26) which has a rounded corner with a radius, and / or - has an entry edge (26) which has a rounded corner with a radius, and / or - has an outlet edge (28) with a rounded corner with a radius.

10. An overload clutch device according to any one of the preceding claims, characterised in that, A guide rod (30) is fixedly connected to the structural member (10).

11. An overload clutch device according to any one of the preceding claims, characterised in that A sensor arrangement, comprising: - a first sensor target (32) that is rotationally fixed to the structural member (10), - a second sensor target (34) that is rotationally fixed to a drive shaft (36), - a first sensor (38) for sensing the first sensor target (32), and - a second sensor (40) for sensing the second sensor target (34).

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