Pawl freewheel

Abstract

To provide a low-cost freewheel which is easy to handle, compact, and excellent in tolerance and functionality.SOLUTION: A pawl freewheel 2 comprises first and second races 16, 18 and pawls 22, 24 between the races, which include at least one first pawl 22 pivotable between a closed position, in which the first race can transmit power to the second race via the first pawl in a first direction of rotation 26 relative to the second race, and an open position, in which the first race is rotatable in the first direction of rotation relative to the second race. An actuating device 42 is provided with an actuating pin 46 which interacts with the first pawl and can be displaced from a first actuating position, in which the first pawl is pivoted into the closed position, in an axial direction 4 relative to the first pawl into a second actuating position, in which the first pawl is pivoted into the open position. The actuating pin has a face 48 with an impinging surface which is inclined relative to a radial plane and which can be supported or is supported directly on the first pawl when the first pawl pivots.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a pawl freewheel comprising a first bearing ring, a second bearing ring, and pawls arranged between the first bearing ring and the second bearing ring, the pawl including at least one first pawl pivotable between a closed position in which the first bearing ring is powerably coupled to the second bearing ring via the first pawl in a first rotational direction relative to the second bearing ring, and an open position in which the first bearing ring is rotatable in the first rotational direction relative to the second bearing ring, the actuator (42) comprising an actuation pin interacting with the first pawl and displaceable axially relative to the first pawl from a first operating position in which the first pawl is pivoted to the closed position to a second operating position in which the first pawl is pivoted to the open position.

[0002] Pawl freewheels having a first bearing ring (e.g., an outer or inner ring) and a second bearing ring (e.g., an inner or outer ring) are known from the prior art. A pivotable pawl is disposed between the first bearing ring and the second bearing ring and is powerably connected to one of the first bearing ring and the second bearing ring. For example, when the pawl is powerably connected to the first bearing ring, the pawl is pivotable from an open position in which the first bearing ring is rotatable in a first rotational direction relative to the second bearing ring to a closed position in which the first bearing ring is powerably coupled to the second bearing ring via the pawl in the first rotational direction.

[0003] Also known are generic pawl freewheels with actuators for pivoting the pawls. For example, actuators are commonly known that have an adjusting ring disposed on one of a plurality of bearing rings, the adjusting ring being rotatable relative to the respective bearing ring in the circumferential direction to pivot at least one pawl between a closed position and an open position.

[0004] Although known pawl freewheels with rotatable actuators such as those described above have proven their worth, they can be cumbersome and have relatively complex, space-consuming designs, which typically result in relatively high manufacturing costs.

[0005] The object of the present invention is therefore to produce a pawl freewheel having an actuating device for pivoting at least one pawl, which is easy to handle, has a simple and compact design, and which causes very little wear on the actuating device and the pawls, thereby increasing their service life and ensuring permanent functionality.

[0006] This object is achieved by the features specified in claim 1. Advantageous embodiments of the invention are the subject matter of the dependent claims.

[0007] The pawl freewheel according to the present invention has a first bearing ring and a second bearing ring. The first bearing ring may be, for example, an outer or inner ring, and the second bearing ring may be, for example, an inner or outer ring. The pawls are arranged between the first bearing ring and the second bearing ring, preferably arranged radially between the first bearing ring and the second bearing ring. The pawls are preferably powerably connected to the first bearing ring, and the first bearing ring is particularly preferably the outer ring. The pawls include at least one first pawl, and preferably a plurality of first pawls of the type described in more detail below are arranged. However, for example, all of the pawls may be formed by these first pawls, or only one pawl may be formed by a first pawl. The at least one first pawl is pivotable between a closed position in which the first bearing ring is powerably coupled to the second bearing ring via the first pawl in a first rotational direction relative to the second bearing ring, and an open position in which the first bearing ring is pivotable in the first rotational direction relative to the second bearing ring. The pivot axis preferably extends in the axial direction of the pawl freewheel. In this way, when the at least one first pawl is in the closed position, rotation of the first bearing ring in the first rotational direction also rotates the second bearing ring in the first rotational direction. The pawl freewheel also has an actuating device for actuating or pivoting the at least one first pawl. The actuating device has an actuating pin that interacts with the first pawl and preferably extends axially. The actuating pin is displaceable axially relative to the first pawl from a first actuating position in which the first pawl is pivoted to the closed position to a second actuating position in which the first pawl is pivoted to the open position. In this case, the first pawl is preferably pre-tensioned in its closed position. In order to pivot the associated first pawl by axially displacing the actuating pin of the actuating device, the actuating pin preferably has an axially facing surface designed as an end face, which is inclined with respect to the radial plane and has a collision surface that can be supported on or directly supported by the first pawl by pivoting the first pawl. The pawl freewheel is characterized by being particularly easy to handle when adjusting the first pawl, especially since only the actuating pin needs to be axially displaced.Furthermore, the actuating pin has a particularly simple structure, since its face has a collision surface that is inclined relative to the radial plane, which results in a pawl freewheel that is particularly easy to manufacture and has a simple and particularly compact structure.

[0008] In order to use particularly small and space-saving actuating pins, in a preferred embodiment of the pawl freewheel according to the invention, the face of the actuating pin further comprises a radial plane extending in the radial plane against which the collision surface can directly abut. The radial plane shortens the inclined collision surface, but the actuating pin does not protrude unnecessarily in the direction of the first pawl in its retracted position, thereby ensuring a short displacement path for the actuating pin.

[0009] In order to achieve a stronger pivoting movement with a small movement of the actuating pin despite the existence of radial planes in the face of the actuating pin, in a particularly preferred embodiment of the pawl freewheel according to the invention, when viewing the face along the axial direction, the impact face has a larger surface area and / or a larger extent in the circumferential and radial directions than the radial surface of this face.

[0010] According to another advantageous embodiment of the pawl freewheel according to the invention, the central axis of the actuating pin, which widens or extends in the axial direction, passes through the impact surface, preferably the central axis of the second shank of the actuating pin, which will be described in more detail below.

[0011] According to a further preferred embodiment of the pawl freewheel according to the invention, it has been found to be advantageous in terms of fast actuation and fast pivoting of the first pawl if the collision surface is inclined to the radial plane (optionally the radial surface of the face) at an angle of 25° to 55°, preferably 30° to 50°, particularly preferably 35° to 45°. Best results are obtained if the inclination angle of the collision surface to the radial plane is about 40°.

[0012] To use a particularly space-saving actuating pin, in another particularly advantageous embodiment of the pawl freewheel according to the invention, the actuating pin has a front shank (optionally an end) on which the impact surface extends and a rear shank that continues from the front shank. In this case, in order to produce a particularly thin and space-saving pin, the impact surface (optionally the entire surface of the actuating pin) is preferably arranged so that it is completely flush with the rear shank in the axial direction. The front and rear shanks preferably continue directly from each other, and it is also preferred that the rear shank transitions into the front shank without a step; the transition to the inclined impact surface is the only optional exception and may of course have a discontinuous course. In this embodiment, the rear shank is also preferably cylindrical, since its cross-sectional shape is preferably circular. The rear shank is also preferably dimensioned such that when the actuating pin is in the second actuating position, the first pawl can be supported or is supported on the rear shank of the actuating pin in the open position. This ensures that the pawl can be pivoted to the open position. The support referred to here is preferably a support in the radial direction of the pawl freewheel.

[0013] In another particularly preferred embodiment of the pawl freewheel according to the invention, the inclined impact surface has an out-of-plane shape to minimize wear and damage to the first pawl and actuation pin. Here, a curved impact surface in the direction of the first pawl has proven particularly advantageous. The level of wear and damage of the pawl freewheel is particularly minimized, thereby improving functionality and extending its service life. This results in a preferred variant in which the impact surface has a constant radius of curvature and / or is formed by a portion of a cylinder. In this context, a particularly large radius of curvature has proven advantageous, being at least twice the cross-sectional radius of the aforementioned rear shank. In particular, an absolute radius of curvature of 10 mm or more ensures increased durability and reliable functionality.

[0014] In another advantageous embodiment of the pawl freewheel according to the invention, the actuating device has a plurality of actuating pins, each assigned to a first pawl. Preferably, the movement of the actuating pins from the first actuating position to the second actuating position and vice versa is coupled to one another in order to pivot two or more first pawls approximately simultaneously. The coupling of the actuating pin movements is preferably achieved by a common support on which the actuating pins are arranged (optionally evenly distributed in the circumferential direction). In this context, an axially displaceable annular support has proven particularly advantageous for axially displacing the actuating pins.

[0015] In a further advantageous embodiment of the pawl freewheel according to the invention, the collision surface, preferably the surface of the front shank, particularly preferably the surface of the rear shank, is harder than the surface of at least one other part (optionally all other parts) of the actuating pin. In order to enable a wear-free interaction with the pawl while simplifying the handling of the actuating pin, in particular its attachment to the actuating device, the collision surface (the surface of the front shank and / or the surface of the rear shank) is preferably designed to be harder than the surface of the fastening part of the fastening pin following the rear shank, which fastening part is intended to fasten the fastening pin to the aforementioned support and is particularly preferably deformed to receive a fastening rivet and / or a fastening flange for fastening to the support. When viewed axially, the fastening part may have larger dimensions than the rear shank, in particular since it is only used for fastening to the actuating device or its support and does not interact directly with the pawl.

[0016] According to a further advantageous embodiment of the pawl freewheel according to the invention, the pawl further comprises at least one second pawl pivotable between a closed position in which the first bearing ring is powerably coupled to the second bearing ring via the second pawl in a second rotational direction opposite to the first rotational direction relative to the second bearing ring, and an open position in which the first bearing ring is rotatable in the second rotational direction relative to the second bearing ring. A second actuating device is arranged with a second actuating pin interacting with the second pawl and displaceable axially relative to the second pawl from a first actuating position in which the second pawl is pivoted to the closed position to a second actuating position in which the second pawl is pivoted to the open position. Again, the second actuating pin has an axially facing surface inclined with respect to the radial plane and with an impact surface that can rest on or be directly supported by the second pawl by pivoting the second pawl. For alternative configurations of the second pawl and the second actuating pin assigned to the second pawl, please refer to the above description of the actuating device with the associated first pawl and its variants. This also applies to the second actuating device and the second pawl. The second actuating device preferably allows for the manufacture of a pawl freewheel with at least three shift positions. One of these positions has the effect that the first bearing ring cannot rotate relative to the second bearing ring in either the first or second direction of rotation. This is particularly true because both the first and second pawls are in the closed position. It may also be advantageous for the two actuating devices to have a common support on which both the actuating pin and the second actuating pin are located. In this way, the actuating pin and the support can be displaced simultaneously. To allow the first and second pawls to pivot continuously, the actuating pin and the second actuating pin may be designed to have different lengths.

[0017] In another advantageous embodiment of the pawl freewheel according to the invention, the first pawl and / or the second pawl are pre-tensioned in their closed position.

[0018] According to another advantageous embodiment of the pawl freewheel according to the invention, the first pawl and the second pawl are pivotable to an open position in opposite pivot directions and are also pivotable to a closed position in opposite pivot directions.

[0019] According to another particularly preferred embodiment of the pawl freewheel according to the invention, the first pawl and / or the second pawl is rocker-shaped, with an engagement part in front of the pivot axis for achieving the rotational driving engagement in the closed position, and a rear part behind the pivot axis which interacts with the associated actuation pin.

[0020] In another advantageous embodiment of the pawl freewheel according to the invention, the collision surface can be or is supported on an edge of the first pawl and / or the second pawl, preferably a side edge defining a side surface of the pawl facing axially.

[0021] According to another advantageous embodiment of the pawl freewheel according to the invention, the collision surface in the closed position is arranged in the axial direction flush with the edge of the first and / or second pawl in order to most quickly impact the edge via the collision surface when the actuating pin is displaced. [Brief explanation of the drawings]

[0022] The invention will now be explained in more detail by means of exemplary embodiments with reference to the accompanying drawings, in which: [Figure 1] FIG. 1 is a partial perspective view of a pawl freewheel with the first pawl in a closed position. [Figure 2] FIG. 2 is a side view of the first claw in FIG. 1. [Figure 3] 2 shows the pawl freewheel of FIG. 1 with the first pawl in the open position. [Figure 4] FIG. 2 is a side view of the first claw in FIG. 1. [Figure 5] FIG. 5 is a side view of the operating pin shown in FIGS. 1 to 4. [Figure 6] FIG. 6 is a front view of the actuation pin in FIG. 5. [Figure 7] FIG. 7 is a perspective view of the actuation pin in FIGS. 5 and 6. [Figure 8] 5 to 7 taken along the section AA in FIG. [Figure 9] 5 to 8 taken along section BB in FIG. 5. FIG.

[0023] 1 to 4 each show a detail of the pawl freewheel 2. In these figures, the opposite axial directions 4 and 6, the opposite radial directions 8 and 10, and the opposite circumferential directions 12 and 14 of the pawl freewheel 2 are indicated by corresponding arrows.

[0024] The pawl freewheel 2 has a first bearing ring 16, here designed as the outer bearing ring 16 in the radial direction 8, only its rear part being shown in the axial direction 6, and a second bearing ring 18, here formed as the inner bearing ring 18 in the radial direction 10, surrounded on the outside in the radial direction 8 by the first bearing ring 16. A rotary drive contour 20 is formed on the side of the second bearing ring 18 facing the first bearing ring 16 in the radial direction 8, and a receptacle 22, which will be described in more detail below, is arranged on the side of the first bearing ring 16 facing the second bearing ring 18 radially inward in the radial direction 10.

[0025] The pawls are disposed in receptacles 22 in radial directions 8, 10 between the first and second races 16, 18, and the first and second pawls 22, 24 are disposed between successively alternating races 16, 18 in circumferential directions 12, 14. The first pawls 22 are pivotable between a closed position shown in FIGS. 1 and 2 in which the first race 16 is powerably coupled to the second race 18 via the first pawls 22 about a pivot axis 28 in a first rotational direction 26 relative to the second race 18, and an open position shown in FIGS. 3 and 4 in which the first race 16 is rotatable in the first rotational direction 26 relative to the second race 18, and vice versa.

[0026] 1 and 3, only the second pawl 24 is shown in the open position, but the description of the first pawl 22 also applies thereto. That is, the second pawl 24 is pivotable between a closed position (not shown) in which the first race 16 is powerably coupled to the second race 18 via the second pawl 24 about a pivot axis 32 in a second rotational direction 30 opposite the first rotational direction 26 relative to the second race 18, and an open position (shown in FIGS. 1 and 3) in which the first race 16 is rotatable in the second rotational direction 30 relative to the second race 18.

[0027] In either case, both the first pawl 22 and the second pawl 24 are pretensioned by the spring element 34 to their corresponding closed positions. Furthermore, the first pawl 22 and the second pawl 24 are pivotable to an open position about a pivot axis 28 or 32 in opposite pivot directions, and are also pivotable to a closed position about the pivot axis 28 or 32 in opposite pivot directions. The first pawl 22 and the second pawl 24 are also rocker-shaped. Thus, each rocker-shaped pawl 22, 24 has an engagement portion 36 in front of the pivot axis 38, where the pivot axis 28, 32 is formed, and a rear portion 40 behind the pivot axis 38. The engagement portion 36 is used to achieve rotational driving engagement with the rotational driving profile 20 of the second race 18 when the pawl 22 or 24 is in the closed position, and the rear portion 40 of the rocker-shaped pawl 22 or 24 interacts with an actuation pin of an actuation device, which will be described later.

[0028] The first pawl 22 is arranged rearward of the first bearing ring 16 in the axial direction 6 and is assigned an actuating device 42 having a plurality of actuating pins 46 arranged on an annular support 44, as shown in particular in FIGS. 5 to 7, which extend in the axial direction 4 to the rear portion 40 of the first pawl 22. Thus, each of the first pawls 22 is assigned an actuating pin 46, and the movement of the actuating pins 46 in the axial directions 4, 6 is coupled to one another via the common annular support 44, and the actuating pins 46 are uniformly distributed in the circumferential directions 12, 14 on the annular support 44 which extends circumferentially along the circumferential directions 12, 14. Before explaining the function of the actuating pins 46 in more detail, their structure will first be described in more detail with reference to FIGS. 5 to 9.

[0029] Actuation pin 46 has a surface 48 facing axial direction 4, having a radial plane 50 extending within the radial plane and an impact surface 52 preferably directly adjacent radial plane 50. Impact surface 52 is inclined relative to the radial plane (here, radial plane 50). As shown in FIG. 6 in particular, when viewing surface 48 along axial direction 6, impact surface 52 has a larger surface area and a larger extent than radial plane 50 in both circumferential directions 12, 14 and radial directions 8, 10. Furthermore, as shown in FIGS. 5-6 , a central axis 54 of actuation pin 46 extending in axial directions 4, 6 passes through impact surface 52 of surface 48. Central axis 54 is preferably the central axis of a cylindrical rear shaft portion of actuation pin 46, as described below.

[0030] The impact surface 52 is inclined relative to the radial plane (here again the radial plane 50) at an angle α of 25° to 55°, preferably 30° to 50°, particularly preferably 35° to 45°, with a particularly advantageous angle α of 40° being shown in the illustrated embodiment.

[0031] As mentioned above, the actuation pin 46 has a front shank 56 from which the impact surface 52 and the radial surface 50 extend, and therefore the front shank 56 may also be referred to as the end of the actuation pin 46 facing the axial direction 4. In the axial direction 6, the front shank 56 is located immediately behind the rear shank 58 of the actuation pin 46, which is formed integrally with the front shank 56. The rear shank 58 has a circular cross section and is therefore formed as a column or cylinder. The impact surface 52, or more precisely the entire surface 48, is located completely flush with the rear shank 58 in the axial directions 4 and 6. There is no discontinuity or step between the rear shank 58 and the front shank 56, except for the edge-shaped transition at the start of the impact surface 52.

[0032] A fastening portion 60 of the actuating pin 46 is arranged behind the rear shank 58 in the axial direction 6 for fastening the actuating pin 46 to the support 44 of the actuating device 42. At least the impact surface 52 is designed to be harder than the surfaces of the remaining parts of the actuating pin 46, in particular the surfaces of the fastening portion 60. It is also advantageous if the surfaces of the front shank 56 and / or the rear shank 58 are designed to be harder than the surfaces of the remaining parts of the actuating pin 46, in particular the surfaces of the fastening portion 60. The fastening portion 60 is used for fastening to the support 44 of the actuating device 42, for example by being deformed to receive a flange 62 and a fastening rivet 64.

[0033] In the illustrated embodiment, the impact surface 52 has a particularly advantageous out-of-plane shape. Specifically, the impact surface 52 is curved in the axial direction 4, and thus curved toward the first pawl 22. In this case, the impact surface 52 has a constant radius of curvature r that is at least twice the radius of the cross section of the rear shank 58. This constant radius r of the impact surface 52 can be seen particularly in FIGS. 8 and 9. FIG. 8 shows a cross section along section AA, and FIG. 9 shows a cross section along section BB parallel to section AA. In the illustrated embodiment, the impact surface 52 formed by a portion of the casing 66 of the cylinder 68, shown in dashed lines in FIG. 5, is more clearly shown, with the opposing upper surface of the casing 66 having the radius of curvature r. The cylinder 68 has a longitudinal axis 70 that intersects the central axis 54 of the actuation pin 46 and extends at an angle β=90°-α in the radial direction 8.

[0034] In the following, the operating mode of the actuator 42 connected to the first pawl 22 will first be described. In Figures 1 and 2, the actuating pin 46 is in a first actuating position, returned in the axial direction 6, in which the first pawl 22 is pivoted by the spring element 34 into the closed position. As shown in particular in Figure 2, the impact surface 52 of the face 48 is arranged in the axial direction 4, 6 so as to be flush with an edge 72 of the first pawl 22, more precisely with the rear part 40 of the first pawl 22, said edge 72 defining the side surface of the first pawl 22.

[0035] When the actuation pin 46 is displaced axially 4 relative to the first pawl 22 to the second actuation position shown in FIGS. 3 and 4 , the impact surface 52 is supported at the edge 72 within its range of movement, pivoting the first pawl 22 from the position shown in FIGS. 1 and 2 to the open position shown in FIGS. 3 and 4 . The impact surface 52 may be or is slidably supported on or along the edge 72 of the first pawl 22. As a result, the rear portion 40 of the first pawl 22 is depressed in the radial direction 10, causing the first pawl 22 to pivot about the associated pivot axis 28 to the open position shown. In the open position, the first pawl 22 is preferably supported in the radial direction 8 only on the rear shaft portion 58 against the pretensioning force of the spring element 34, thereby securely holding it in the open position.

[0036] As noted above, the structure of the second actuator for the second pawl 24 corresponds to the structure of the actuator for the first pawl 22, and therefore the foregoing description of the actuator pin 46 similarly applies to the second actuator pin 74. Accordingly, the second actuator pin 74 interacts with the second pawl 24. As shown in FIGS. 1 and 3 , the second actuator pin 74 is displaced in the axial direction 4 relative to the second pawl 24 from a first actuation position, in which the second pawl 24 is pivoted to a closed position, to a second actuation position, in which the second pawl 24 is pivoted to an open position. The second actuator pin 74 further has a surface 48 facing the axial direction 4 that is inclined with respect to the radial plane and that includes an impact surface 52 that is supportable or directly supported on the second pawl 24 when the second pawl 24 is pivoted. [Explanation of symbols]

[0037] 2: Pawl freewheel 4: Axial direction 6: Axial direction 8:Radial direction 10: Radial direction 12: Circumferential direction 14: Circumferential direction 16: First bearing ring 18: Second bearing ring 20: Rotational drive contour 22: First Claw 24: Second Claw 26: First rotation direction 28: Pivot axis 30: Second rotation direction 32: Pivot axis 34: Spring element 36: Engagement part 38: Pivot shaft 40: Rear 42: Actuator 44: Support part 46: Operating pin 48: Face 50: Radial surface 52: Collision surface 54: Central axis 56: Front shaft 58: Rear shaft 60: Fastening part 62: Flange 64: Fastening rivet 66: Casing 68: Cylinder 70: Longitudinal axis 72: Edge 74: Second operating pin α: Angle β: Angle r: radius of curvature

Claims

1. A wheeled freewheel (2) comprising a first raceway (16), a second raceway (18), and claws (22, 24) positioned between the first raceway (16) and the second raceway (18), wherein the first raceway (16) includes at least one first claw (22) pivotable between a closed position in which the first raceway (16) is power-transmittingly connected to the second raceway (18) via the first claw (22) in a first rotational direction (26) and an open position in which the first raceway (16) is rotatable relative to the second raceway (18) in the first rotational direction (26), and acts The device (42) is a freewheel (2) characterized by having an operating pin (46) that interacts with the first claw (22) and is displaceable in the axial direction (4) relative to the first claw (22) from a first operating position in which the first claw (22) is pivoted to the closed position to a second operating position in which the first claw (22) is pivoted to the open position, wherein the operating pin (46) has an axially oriented surface (48) that is inclined with respect to the radial plane and has an abutment surface (52) that can be supported on or directly supported on the first claw (22) when the first claw (22) is pivoted.

2. The surface (48) has a radial surface (50) extending in a radial plane into which the impact surface (52) arbitrarily directly contacts, and when the surface (48) is viewed along the axial direction (6), the impact surface (52) preferably has a larger surface area and / or range in the circumferential direction (12, 14) and radial direction (8, 10) than the radial surface (50), and it is particularly preferable that the central axis (54) of the operating pin (46) extending in the axial direction (4, 6) penetrates the impact surface (52), as described in claim 1, for the stabilizing freewheel (2).

3. The chock freewheel (2) according to claim 1 or 2, characterized in that the collision surface (52) is inclined with respect to the radial plane at an angle (α) of 25° to 55°, preferably 30° to 50°, and particularly preferably 35° to 45°.

4. The actuation pin (46) has a front shaft portion (56) on which the impact surface (52) extends, and a rear shaft portion (58) that is adjacent to the front shaft portion (56), wherein the impact surface (52), optionally the entire surface (48), is arranged to be completely coplanar with the rear shaft portion (58) in the axial direction (4, 6), and the rear shaft portion (58) particularly preferably has a circular cross-section, and the first claw (22) is optionally able to be supported or supported on the rear shaft portion (58) in the open position, characterized in that the chock freewheel (2) according to claim 1 or 2.

5. The collision surface (52) has a shape that is not a plane, preferably the first claw (22 The chock freewheel (2) according to claim 1 or 2, characterized in that it is curved in the direction of the ) and particularly preferably has a constant radius of curvature (r), and / or is formed by a portion of the casing (66) of the cylinder (68), wherein the radius of curvature (r) is optionally at least twice the radius of the rear shaft portion (58).

6. The actuation device (42) has a plurality of actuation pins (46) each assigned to the first claw (22), and the movement of the actuation pins (46) is preferably coupled to one another, optionally arranged, and optionally uniformly distributed in the circumferential direction (12, 14) via a common support portion (44), wherein the support portion (44) is particularly preferably annular. This is the case of the stud freewheel (2) according to claim 1 or 2.

7. The collision surface (52), preferably the surface of the front shaft portion (56), and particularly preferably the surface of the rear shaft portion (58), is formed to be harder than the surface of the other portion of the actuation pin (46), preferably the surface of the fastening portion (60) of the actuation pin (46) that extends to the rear shaft portion (58), and the fastening portion (60) is used to fasten the actuation pin (46) to the support portion (44), and is particularly preferably deformed to receive a fastening rivet (64) for fastening to the support portion (44), as described in claim 1 or 2, the stabilizing freewheel (2).

8. The claws (22, 24) further include at least one second claw (24) pivotable between a closed position in which the first raceway (16) is power-transmittingly connected to the second raceway (18) via the second claw (24) in a second rotational direction (30) opposite to the first rotational direction (26) relative to the second raceway (18), and an open position in which the first raceway (16) is rotatable relative to the second raceway (18) in the second rotational direction (30), the second actuator interacts with the second claw (24) and in the axial direction (4) The stabilizing freewheel (2) according to claim 1 or 2 is characterized in that it comprises a second operating pin (74) that is displaceable with respect to the second claw (24) from a first operating position in which the second claw (24) is pivoted to the closed position to a second operating position in which the second claw (24) is pivoted to the open position, and the second operating pin (74) has a surface (48) facing the axial direction (4) that is inclined with respect to the radial plane and has an impact surface (52) that can be supported on or directly supported on the second claw (24) when the second claw (24) is pivoted.

9. The first claw (22) and / or the second claw (24) are pre-tensioned in the closed position and / or pivotable to the open position and the closed position in opposite pivot directions and / or have a rocker shape with an engaging portion (36) in front of the pivot shafts (28, 32) for achieving rotational drive engagement in the closed position, and a rear portion (40) is formed behind the pivot shafts (28, 32) that interacts with the operating pins (46, 74), characterized in that the chock freewheel (2) according to claim 1 or 2.

10. The collision surface (52) may be supported on or on the edge (72) of the first claw (22) and / or the second claw (24), and / or is arranged to be coplanar with the edge (72) in the axial direction (4, 6) when in the closed position, as described in claim 1 or 2 of the stud freewheel (2).

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