Actuator for operating at least two gear elements

Abstract

The present invention relates to an actuator 1 with a pin gear 2, the pin gear 2 comprising a drive element 3 having at least one pin 4. The pin gear 2 further comprises an output element 5 having a star wheel 6 on a shaft, preferably an output shaft 8. The star wheel 6 is formed with at least one slot 7. The star wheel 6 can be pivoted by the pin 4, which for this purpose engages in the at least one slot 7. By a first pivoting of the star wheel 6 by means of the pin 4 by a first angle α', a first gear element 9 is actuated by means of the output element 5), preferably the output shaft 8, and by the pivoting of the star wheel 6 by a second angle β', which is different from the first angle α', wherein both angles α', β' are measured from the same origin, a second gear element 10 is actuated.

Description

[0001] The present invention relates to an actuator with a pin gear. The pin gear has a drive element, which in turn has a pin. Furthermore, the pin gear has an output element comprising a star wheel with at least one slot. The star wheel is arranged on a shaft, preferably on an output shaft, wherein the star wheel is pivoted by the pin, which engages in the at least one slot for this purpose.

[0002] Such actuators are known, for example, from DE 10 2018 123 139 A1 for shifting an automated transmission. This type of pinion gear is also commonly referred to as a Geneva Drive. As a coupling gear, it has a rest phase between incremental actuation sections of an output shaft, during which the star gear is locked in position by a cylinder locking mechanism.

[0003] This gear is also known for switching slide projectors or generally for step-by-step transport.

[0004] Another relevant pin gear is known from WO 2009 / 122 814 A1.

[0005] Furthermore, different types of actuators for actuating transmission elements within a drivetrain are known. For example, DE 10 2018 131 263 A1 discloses an actuator for actuating a parking lock, and DE 10 2021 126 151 A1 discloses an actuator for wheel decoupling.

[0006] The object of the present invention is to present an actuator that helps to reduce the necessary parts, in particular drive parts, for example within a drive train, or helps to simplify the drive train.

[0007] This object of the invention is achieved by a generic actuator having the characterizing features of claim 1.

[0008] Furthermore, the object of the invention is also achieved by a drive train according to claim 3.

[0009] Further embodiments of this invention are described in the subclaims.

[0010] According to the invention, the actuator is designed such that a first gear element is actuated by means of the output shaft by a first pivoting of the star wheel by a first angle, and a second gear element is actuated by pivoting the star wheel by a second angle, which is different from the first angle. The pivoting takes place by means of the pin of the drive element. The two angles are determined from the same reference point, e.g., a predetermined zero or neutral position. As a result, a drive element for actuating a second gear element can be eliminated by means of the actuator. The output shaft can be connected to the two gear elements, e.g., via spring elements, switched freewheels, or similar gear means.be provided to actuate a first gear element when pivoted in a first slot and a second gear element when pivoted in a second slot.

[0011] According to the invention, the second angle points in a neutral position of the pin in an opposite direction to the first angle. This means that the two angles can, in particular, be equal, but have different signs with respect to a neutral position. Starting from the neutral position, the first gear element is actuated upon pivoting in a first direction, and a different gear element is actuated upon pivoting in the opposite direction.

[0012] It is further provided that the neutral position of the pin is determined in that in this neutral position a straight line runs through an axis of rotation of the drive element, through the pin and also through an axis of rotation of the output shaft. The pin is therefore preferably located in the at least one slot in such a way that, on the one hand, maximum torque can be transmitted from the drive element to the output shaft and, on the other hand, the two possible directions of rotation of the drive element lead to identical, merely mirror-image pivoting of the star wheel. The angle through which the star wheel is pivoted is identical, as is the transmitted torque, i.e. the two resulting torque transmission characteristics are oppositely identical.

[0013] This neutral position is a non-self-locking position of the pin gear. In particular, it can be provided that a non-self-locking drive or drive motor is used to drive the pin gear. It can then further be provided that the two gear elements are preloaded towards this neutral position against a stop. A stop can here in particular be provided in the respective torque path of the corresponding gear element. Due to the preload and the stops, when the actuator is in a force-free position, it can be held stably in this non-self-locking position for a pin gear, since the respective preload of a gear element must first be overcome. The preload is ideally selected so that it is significantly higher than the disruptive forces that can be expected due to disturbances.In other words, it is possible to operate the actuator with a non-self-locking drive and to set the neutral position simultaneously in a non-self-locking state of the star wheel of the pin gear, or in a non-self-locking state of the pin gear itself, and at the same time, by connecting the output element of the pin gear, or the star wheel, to at least two gear elements, to keep this neutral position stable against unwanted adjustments, by the gear elements being automatically pressed against stops via preloads or restoring forces, e.g. via spring elements, so that when the actuator is in a drive-free state, the pin gear, or the star wheel, is automatically moved back into the neutral position and this neutral position is maintained.

[0014] According to the invention, the straight line in the neutral position of the pin represents an axis of symmetry, preferably the only axis of symmetry of the star wheel, wherein in the neutral position the first slot of the star wheel is divided longitudinally by the axis of symmetry and the first gear element is actuated by pivoting the pin in the first slot in a first direction and the second gear element is actuated by pivoting the pin in a second slot in a second direction, which is opposite to the first direction. This means that on the one hand identical, albeit mirror-inverted, characteristic curves for the transmission of the torque and / or angular pivoting of the star wheel can be ensured across all areas of the star wheel, in particular across multiple slots.Across specific, different ranges in one or the other direction of the star wheel's pivoting, different gear elements can then be actuated in a defined manner according to identical but opposite characteristic curve sections or also according to different, but preferably also opposite characteristic curve sections. This could, for example, allow actuators of the same design to actuate different, preferably pairs of gear elements, using actuators arranged as a mirror image of the other identical actuator. If necessary, correspondingly different resulting characteristic curves can be set using (non-linear) restoring forces or preload forces assigned to the gear elements. In general, however, identical characteristic curves can be expected, at least in some areas, even through pin actuation in different pins.

[0015] To simplify actuation of the various gear elements, it can be provided that pivoting the pin in the first slot pivots the spur gear from the neutral position into the second direction without any actuation. This makes it easier to separate the two torque paths for actuating the first and second gear elements, particularly in the area between the output shaft and the gear elements, and in particular to design them with larger tolerances. In particular, it can be provided that the characteristic curves for the respective actuation of the various gear elements are identical in terms of magnitude, but are caused by pin engagements in different slots. When a gear element is actuated from a second slot, the star gear travels through an angular range that is three times larger than that of the first gear element.This occurs through the first angular range in the first slot, which is traversed without actuation and is identical in size to the angular range for actuating the first gear element. This first angular range can preferably be 15°. The first angular range in the second direction is opposite to the first angular range in the first direction, i.e. for actuating the first gear element. After traversing the first angular range in the second direction, the drive element is rotated further so that the pin penetrates the second pin of the star wheel. In this case, the star wheel is not pivoted any further. After a further pivoting of the star wheel through an angular range, which in turn corresponds in size to the first angular range, the pin gear reaches a position in which the pin is again in the same position as in the neutral position. This then corresponds to a pivoting of the star wheel through twice the angular range, i.e.preferably 30°. Actuation of the second gear element can already be provided at this double angular range. However, in order to utilize the higher dynamics in this range and also to clearly separate the actuations of the two gear elements, it is preferably provided that the pin is pivoted again through a further angular range, which again corresponds in size to the first angular range. In total, the star wheel is therefore pivoted by three times the angular range, preferably 45°, opposite to the pivoting of the gear element. A further advantage is that the pin gear is in a self-locking position both when pivoting through the first angular range and when pivoting through the third angular range.Thus, both in the neutral position and when the star wheel is pivoted through a first angular range and through a triple angular range, preferred, stable positions of the actuator are present, in which the gear elements are held in the actuated state in the two latter pivots, even when the actuator is not driven.

[0016] Furthermore, the object of the invention is achieved by a drive train with an actuator which is designed such that a first gear element is actuated by means of the output shaft by a first pivoting of the star wheel by a first angle, and a second gear element is actuated by pivoting the star wheel by a second angle, which is different from the first angle. The pivoting takes place by means of the pin of the drive element. The two angles are determined from the same reference point, e.g., a predetermined zero or neutral position. As a result, a drive element for actuating a second gear element can be saved by means of the actuator. For this purpose, the output shaft can be connected to the two gear elements, e.g., via spring elements, switched freewheels or similar gear means.It may be provided to actuate a first gear element upon pivoting in a first slot and a second gear element upon pivoting of the pin in a second slot. Alternatively, the drive train has an actuator as described above. The drive train comprises at least a first and a second gear element, each of which is actuated by the same described actuator.

[0017] According to the invention, at least two actuators are provided on different sides in a transverse direction, wherein the at least two actuators are identically constructed and are each arranged pointing away from a center of the vehicle. The transverse direction here means a direction transverse to the direction of travel of the motor vehicle. This means that the drive train is constructed such that a first actuator for controlling a first pair (two) of transmission elements is arranged on one side, i.e. laterally to a direction from front to rear with respect to a direction of travel of the vehicle, and thus of the drive train. The drive train further comprises a further pair of transmission elements which are actuated by a second identical actuator. Due to the positioning of the second pair of transmission elements on a different side transverse to the drive train or motor vehicle, it is necessary to adapt the position of the actuator accordingly.Due to the actuator design described above, the use of a second identical actuator is sufficient for this purpose. This actuator is simply reversed so that the actuation is a mirror image of the first actuator. Advantageously, the second gear element can be actuated precisely when the star wheel of the respective actuator is pivoted from the neutral position by three times the angular amount required for the actuation of the first gear element.

[0018] For drivetrains, it is advantageous if the two transmission elements are a parking lock and a separating clutch, particularly a dog clutch. Actuation then occurs in a rotational manner from the output shaft, and two distinct end states are specified, each corresponding to an actuated and a deactuated state of the transmission element. Actuation using the described actuator is particularly advantageous for this purpose, since these two states can be maintained in a controlled, self-locking manner by appropriately positioning the pin within the corresponding slots or just outside the corresponding slots.On the one hand, these states are given by positions of the pin in respective slots in which a straight line through the axis of rotation of the drive element and the pin is exactly perpendicular to a straight line centrally through the slot and the output shaft, so that here no adjustment occurs through unintentional movement of the output shaft, i.e. the pin gear is self-locking here, and on the other hand the pin can also be moved outside the slot, so that an outer contour of the star wheel engages with a corresponding outer contour of the drive element in such a way that they roll against each other without torque transmission. In these preferred positions, self-locking of the actuator can therefore be achieved.Since the intermediate states between these two states have no effect on the function of these gear elements, a special course of torque transmission from the input element to the output shaft between the two self-locking positions is not important. Larger tolerances can be accepted here; in particular, self-locking is not necessary here, since these intermediate positions are only crossed during actuation and should not create static states. If a power failure occurs during actuation, the actuator returns to its neutral position or to the neutral position of the star wheel. If one of the gear elements is actuated, the actuator can be switched off, since the pin gear is in a self-locking state, as described above.

[0019] Furthermore, it can be provided for the drive train that in one or the first actuator, when the star wheel is pivoted in a first direction, preferably by a first angle, a first gear element, such as a parking lock, is actuated and in the case of pivoting in a second direction, preferably by a second angle, a second gear element, such as a dog clutch, is actuated, while in the case of a / the second, identical actuator, when pivoting in the first direction, preferably by the second angle, a second gear element is actuated and in the case of pivoting in the second direction, preferably by the first angle, a first gear element is actuated, wherein the first direction points opposite to the second direction and is measured in each case with respect to a neutral position of the star wheel.

[0020] To achieve the lowest possible energy consumption, the actuator(s) can be driven by a drive with as little or no self-locking as possible. The neutral position can be held securely and without drive by preloading the gear elements against stops.

[0021] Overall, it is thus possible to use the same actuator in different, mirror-image positions of the drive train, preferably to actuate pairs of first and second transmission elements, such as the parking lock and dog clutch, positioned mirror-image to each other. This can be provided in particular for an e-axle, where a pair of parking lock and disconnect clutch, e.g., as a dog clutch, is provided on both ends / sides of the e-axle. The pin gear used can then additionally ensure self-locking in preferred positions of the transmission elements in a simple manner.

[0022] Embodiments of the invention, from which further inventive features may arise and to which the invention is not limited, are shown in the following figures. They show: Fig. 1: an actuator in neutral position, Fig. 2: the actuator Fig. 1 in a second position Fig. 3: a symbolic representation of one side of a drive train with an actuator according to the invention

[0023] In Fig. 1 shows an actuator 1, or at least a section of an actuator 1. This section shows, in particular, a pin gear 2. The pin gear 2 has a drive element 3 and an output shaft 8. The output shaft 8 is accommodated in a star gear 6 of an output element 5. The pin gear 2 is essentially structurally similar to known Geneva gears, although here there is no complete cross for the star gear 6, or does not need to be.

[0024] Torque is transmitted to the star gear 6 via the drive element 3. This torque can, for example, be transmitted directly to further actuating elements via edges of the output shaft 5. In the case shown here, however, the torque is transmitted directly from the star gear 6 to the output shaft 8. The output shaft 8 is connected, e.g., via camshafts or similar, to actuating elements for actuating gear elements 9, 10. The output shaft 8 can also directly have cams (not shown here) and, via these, further actuate gear elements 9, 10 directly or indirectly.

[0025] The drive element 3 can be driven, i.e. set in rotation, indirectly or directly by an electric motor not shown here.

[0026] The drive element 3 here has an axially lower circular disc 30. A pin 4 protrudes eccentrically from this circular disc 30 in the axial direction away from the circular disc 30. Axial here is to be understood with respect to a rotational axis 20 of the drive element 3.

[0027] The pin 4 can engage in slots 7 in a manner known per se for Geneva gears and, via pivoting within these slots 7, torque can be transmitted from the drive element 3 to the star wheel 6, which has the slots 7 in the edge area.

[0028] The pin gear 2 and thus the star wheel 6 are located in Fig. 1 in a neutral position, in which the pin 4 engages in a central first slot 23. From this position, when the star wheel 6 is pivoted by a first angle α' in a first direction, a first gear element 9 is actuated. This first gear element 9 is in Fig. 3 as a short spring 31 in the form of an equivalent image. The pivoting of the star wheel 6 by the first angle α' is associated with a pivoting of the pin 4 from its neutral position, i.e. the position of the pin 4 which it also assumes in the neutral position of the star wheel 6, by an angle α. In the case shown here, α'=15°, while α lies approximately between -80° and -89°. This means that the pin 4 rotates in the opposite direction to the star wheel 6 and the actuation of the first gear element 9 occurs shortly before the pin 4 rotates out of the first slot 23.

[0029] From the neutral position, the torque is transmitted according to a characteristic curve that results from the angular position of the distance between the axis of rotation 20 of the drive element 3 and the pin 4 to the distance between the axis of rotation 22 of the output shaft 8 and the pin 4. At an angle of 0°, a maximum torque is transmitted. This is the case in the neutral position of the star wheel. Fig. 2, an angle of 90° is included, meaning that the torque is minimal. This is Fig. 2 shown position of the star wheel 6 is a self-locking state of the pin gear 2.

[0030] From the neutral position in Fig. 1, the pin can adjust in the direction of angle α by an angle of slightly less (here meant as an amount) than -90°. The angle α is related to the axis of rotation 20 of the drive element 3. This adjustment of the pin 4 corresponds to a pivoting of the star wheel 6 by an angle α'=15°. After this 15° rotation of the star wheel 6, the pin 4 is in a radially outer extreme position of the first slot 23. The transmitted torque is minimal; the pin gear 2 is self-locking in this state. As described, when the star wheel 6 pivots by 15°, a first gear element 9 is actuated. This actuation occurs due to the clockwise rotation of the output shaft 8 in direction 34. The pin 4 is accordingly moved counterclockwise to a position in which the two paths defined by the pin 4 and the axes of rotation 20 and 22 of the drive element 3 and star wheel 6, respectively.Output shaft 8 are perpendicular to each other. If the pin 4 is moved further in the direction of the angle α out of the first slot 23, a contour 32 of the drive element and a counter-contour 33 of the star wheel 6 roll against each other in a self-locking manner. This means that the position of the pin 4 in the first slot 23 does not have to be precisely controlled.

[0031] If the pin 4 is first rotated by the same angle α in the opposite direction, the actuation of the first gear element 9 is cancelled. Upon further rotation in the opposite direction by the angle β, no further actuation of a gear element 9, 10 takes place. The second angle β', by which the star wheel 6 is pivoted in the first slot 23 during this movement of the pin 4, is then also -15°, i.e. is directed opposite to the pivoting during the actuation of the first gear element 9. With other arrangements of slots 7 and sizes of the drive element 3, other angle sizes for α' and β' than 15° can also be set accordingly.

[0032] If the drive element 3 is rotated further in the direction of angle β, the pin 4 disengages from the first slot 23. Upon further rotation of the drive element 3, it then rotates via a contour 32 against a counter-contour 33 of the star wheel 6, as is known in a Geneva gear, without any torque being transmitted. Throughout this entire range of rotation 3, the pin gear is then held in a self-locking state.

[0033] After a corresponding further rotation, here at just over 270°, the pin 4 finally engages in the second slot 24. If the pin 4 is pivoted again by an angle β of just under 90° about the axis of rotation 20, the star wheel 6 is pivoted again by a second angle β'=-15°. The pin 4 is here again in its neutral position, i.e. a maximum torque can be transmitted here, while the pin gear 2 is not self-locking. The pin 4 can then be adjusted again by an angle of just under 90°. This corresponds to a further rotation of the star wheel by β'=-15°. This means that a total pivoting or twisting of the star wheel of γ=3*β=-45° takes place. After this pivoting of the star wheel 6 is complete, the pin gear 2 is once again in a self-locking position.The actuation of the second gear element 10 is completed in this position and can be held drive-free or without drive by the actuator 1. The output shaft 8 is rotated counterclockwise in direction 35 by three times the angular range in the opposite direction to that in the actuation of the first gear element 9. The characteristic curve of the torque transmission follows, while the pin 4 engages in the second slot 24 again from a minimum, a self-locking position, as shown in . Fig. 2, to a maximum in which the angle between the lines from the axes of rotation 20, 22 to the pin 4 is 0°, to a renewed self-locking position after a total angle of rotation of the star wheel 6 of -30°. If a further counter-contour 33 is provided behind the second slot 24 in the circumferential direction of the star wheel 6, the pin 4 can also be moved out of the second slot 24 by further rotation of the drive element 3 in the direction of the angle β. This second self-locking position then does not have to be approached exactly here either. Since the contour 32 and counter-contour 33 lie on top of one another here, a stable self-locking state of the pin gear 2 would also be achieved here.

[0034] A return movement of the pin gear 2 to the neutral position, as in Fig. 1, the actuation of the second gear element 10 is canceled again.

[0035] If the pin 4 is pivoted further in the direction of the angle α starting from an actuated first gear element 9, the pin 4 indeed reaches a further third slot 26, which here, however, is not assigned to any gear element 9, 10.

[0036] If this actuator 1 is integrated into a drive train 40 as shown in Fig. 3 is symbolically shown, two such actuators 1 can actuate two transmission elements 9, 10 on both sides of a drive train 40 in a mirror-inverted manner, as described above.

[0037] In Fig. 3 shows one side of such a drive train symbolically.

[0038] The two different gear elements 9 and 10 are shown here in a substitute image as springs 31 and 36 of different lengths. The springs 31 and 36 symbolize the restoring forces of the gear elements 9 and 10, with which they act on the pin gear 2 and which, upon actuation, must first be overcome by drive means not shown. When the pin is rotated by the angle α from the neutral position, the first gear element 9, shown as the short spring 31, is actuated first. When the pin 4 is rotated in the direction of the angle β, the star wheel 6 is first rotated by the second angle β'=- 15°, so that upon further rotation of the pin 4, it engages in the second slot 24. After a total rotation of the star wheel 6 of finally -45°, the second gear element 10 is actuated against the restoring force represented by the long spring 36.

[0039] The actuation of the gear elements 9 and 10 is symbolically achieved here by stops 41 on the star wheel 6, which act on struts 42, which are pivoted coaxially about a rotational axis 43 against the action of the springs 31, 36. The neutral position is then determined by stops 44 fixed to the housing. The restoring forces of the gear elements 9, 10 are represented here via the springs 31, 36. In the neutral position of the pin gear 2, it is held stable in both directions by the opposing restoring forces of the two gear elements 9 and 10, even without drive force. In the self-locking positions described above, these restoring forces are canceled. The states of the gear elements 9, 10 defined thereby can then be maintained energy-free.

[0040] Therefore, the use of the actuator 1 in drive trains 40 is recommended, in which transmission elements 9, 10 with one or two preferred actuation positions, such as parking locks or claw clutches as used in disconnect clutches, are arranged mirror-inverted with respect to a longitudinal or transverse direction of the drive train. List of reference symbols 1 actuator 2 pin gears 3 Drive element 4 pin 5 Output element 6 Star wheel 7 slot 8 Output shaft 9 first gear element 10 second gear element 20 axis of rotation 21 straight 22 axis of rotation 23 first slot 24 second slot 25 axis of symmetry 26 third slot 30 circular discs 31 short spring 32 Contour 33 Counter contour 34 direction 35 direction 36 long spring 40 Drivetrain 41 characters 42 struts 43 axis of rotation 44 characters α angle β angle α' first angle β' second angle

Claims

[1] Actuator (1) with a pin gear (2), the pin gear (2) comprising a drive element (3) which has at least one pin (4), further comprising an output element (5) comprising a star wheel (6) on a shaft, preferably an output shaft (8) with at least one slot (7), wherein the star wheel (6) is pivoted by the pin (4), which for this purpose engages in the at least one slot (7), wherein a first pivoting of the star wheel (6) by means of the pin (4) through a first angle (α') actuates a first gear element (9) by means of the output element (5), preferably the output shaft (8), and a second gear element (10) is actuated by pivoting the star wheel (6) through a second angle (β') which is different from the first angle (α'), wherein both angles (α', β') are measured from the same origin, characterized bythat the second angle (β') points to a neutral position of the star wheel (6) in an opposite direction to the first angle (α'), the neutral position of the star wheel (6) is determined in that in this neutral position a straight line (21) runs through an axis of rotation (20) of the drive element (3), the pin (4), and through an axis of rotation (22) of the star wheel (6), wherein the axis of rotation (22) of the star wheel (6) is preferably the axis of rotation (22) of an output shaft (8) and the straight line (21) in the neutral position of the star wheel (6) represents an axis of symmetry (25) of the star wheel (6), wherein in the neutral position a first slot (23) of the star wheel (6) is divided by the axis of symmetry (25) in the longitudinal direction and by pivoting the pin (4) in the first slot (23) in a first direction the first gear element (9) is actuated and by the Pivoting the pin (4) in a second slot (24) in a second direction,which is opposite to the first direction, the second gear element (10) is actuated., [2] Actuator (1) according to claim 1, characterized by that pivoting of the pin (4) in the first slot (23) from the neutral position of the star wheel (6) into the second direction takes place without actuation. [3] Drive train of a motor vehicle with an actuator (1) according to one of claims 1 or 2 and comprising at least a first transmission element (9) and a second transmission element (10). [4] Drive train of a motor vehicle with an actuator (1) according to the preamble of claim 1 and comprising at least a first transmission element (9) and a second transmission element (10) or according to claim 3, characterized bythat in a transverse direction, transverse to the direction of travel of the motor vehicle, at least two actuators (1) are present on different sides, wherein the at least two actuators (1) are of identical construction and arranged in mirror image to one another. [5] Drive train with an actuator (1) according to the preamble of claim 1 and comprising at least a first transmission element (9) and a second transmission element (10) or according to one of claims 3 or 4, characterized by that the first transmission element (9) is a parking lock and the second transmission element (10) is a separating clutch, preferably a claw clutch. [6] Drive train according to claim 4 or according to claims 4 and 5, characterized bythat in a first actuator (1) a first gear element (9) is actuated when the pin (4) is pivoted in a first direction and a second gear element (10) is actuated when the pin (4) is pivoted in a second direction, or a first gear element (9) is actuated when the star wheel (6) is pivoted in a first direction and a second gear element (10) is actuated when the star wheel (6) is pivoted in a second direction, while in a second, identical actuator (1) a second gear element (10) is actuated when pivoting in the first direction and a first gear element (9) is actuated when pivoting in the second direction, wherein the first direction points opposite to the second direction and is in each case related to a neutral position of the star wheel (6).

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