Actuator for actuating at least two transmission elements

Abstract

The invention relates to an actuator (1) comprising a pin-type gear mechanism (2) having a drive element (3) with at least one pin (4). The pin-type gear mechanism (2) also has an output element (5) with a star gear (6) on the shaft, preferably an output shaft (8). The star wheel (6) is designed to have at least one groove (7). The star wheel (6) can be pivoted by a pin (4) which engages in at least one groove (7) for this purpose. The first transmission element (9) is actuated by means of the output element (5), preferably the output shaft (8), as a result of a first pivoting movement of the star wheel (6) by means of the pin (4) over a first angle alpha ', and the second transmission element (10) is actuated by pivoting the star wheel (6) over a second angle beta' different from the first angle alpha ', both angles alpha' and beta 'being measured from the same reference point.

Description

Technical Field

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

[0002] For example, such an actuator for switching automatic transmissions is known from DE 10 2018 123 139 A1. This type of pin-gear mechanism is also commonly referred to as a Maltese cross drive or a Geneva drive. As a connecting gear mechanism, it has a stationary phase between the intermittently actuated sections of the output shaft, in which the star wheel is locked in its position by a cylindrical lock.

[0003] Such transmission devices are also known, for example, for switching in slide projectors or generally for step-by-step transmission.

[0004] Furthermore, different types of actuators for operating transmission elements within a drivetrain are also known. Thus, an actuator for operating a parking lock is known from DE102018131263 A1, and an actuator for disengaging a wheel is known from DE102021126151 A1. Summary of the Invention

[0005] The object of the present invention is to provide an actuator that helps to reduce, for example, necessary components in a transmission system, particularly drive components, or to simplify the transmission system.

[0006] This objective of the invention is achieved by a general-purpose actuator of the type discussed, having the features of claim 1.

[0007] Furthermore, the objective of the present invention is also achieved by the transmission system according to claim 7.

[0008] Other improvements to the invention are described in the dependent claims.

[0009] According to the invention, the actuator is designed such that a first transmission element is actuated by a first pivot at a first angle via an output shaft and a star wheel, and a second transmission element is actuated by pivoting the star wheel at a second angle different from the first angle. The pivoting is achieved by means of a pin on the drive element. The two angles are determined from the same reference point, such as a given zero position or neutral position. This allows the actuator to eliminate the need for a separate drive element to operate the second transmission element. The output shaft can be connected to the two transmission elements, for example, via a spring element, a switching freewheel, or a similar transmission element. For example, it can be contemplated that the first transmission element is actuated when the pin pivots in the first slot, and the second transmission element is actuated when the pin pivots in the second slot.

[0010] Specifically, it can be specified that when the pin is in the neutral position, the second angle points in the opposite direction to the first angle. This means that the two angles can have the same magnitude but different signs relative to the neutral position. Starting from the neutral position, when pivoting in the first direction, the first transmission element is actuated, and when pivoting in the opposite direction, a different transmission element is actuated.

[0011] In other improvements, the neutral position of the pin can be defined by a straight line passing through the axis of rotation of the drive element, through the pin, and through the axis of rotation of the output shaft in that neutral position. Preferably, the pin is positioned in at least one slot such that, on the one hand, maximum torque transmission from the drive element to the output shaft can be achieved, and on the other hand, the two possible directions of rotation of the drive element result in the same but mirror-image pivoting of the star wheel. This also applies here to both the magnitude of the pivoting angle of the star wheel and the transmitted torque; that is, the two resulting torque transmission characteristic curves are the same in opposite directions.

[0012] This neutral position is the non-locking position of the pin gear mechanism. Specifically, it can be specified that a non-locking actuator or a non-locking drive motor is used to drive the pin gear mechanism. It can then be further specified that the two transmission elements are pre-tensioned against a stop along the direction of this neutral position. Here, the stop can be provided, particularly in the corresponding torque path of the corresponding transmission element. Due to the pre-tension and the stop, the actuator can be stably held in this position when it is in a weak position, which is not self-locking for the pin gear mechanism because the corresponding pre-tension of the transmission element must first be overcome. The pre-tension is ideally chosen to be significantly higher than the expected disturbance force due to interference. In other words, the actuator can be operated with a non-self-locking drive, and a neutral position can be set in the non-self-locking state of the star gear of the pin gear mechanism or the non-self-locking state of the pin gear mechanism itself. At the same time, by connecting the output element of the pin gear mechanism or the star gear to at least two transmission elements, the neutral position is stabilized by means of pre-tension or restoring force, such as via a spring element, to prevent unnecessary adjustments. The spring element automatically presses the transmission element against the stop, so that in the non-driven state of the actuator, the pin gear mechanism or star gear automatically moves back to the neutral position and maintains the neutral position.

[0013] Furthermore, it can be specifically specified that the straight line at the neutral position of the pin represents the axis of symmetry, preferably the unique axis of symmetry of the star wheel, wherein, in the neutral position, the first groove of the star wheel is longitudinally separated by the axis of symmetry, and the first transmission element is actuated by pivoting in the first groove via the pin in a first direction, and the second transmission element is actuated by pivoting in the second groove via the pin in a second direction opposite to the first direction. This means that, on the one hand, the same but mirrored characteristic curves of torque transmission and / or angular pivoting of the star wheel can be ensured in all areas of the star wheel, particularly in several grooves. The defined different transmission elements can then be actuated in one pivoting direction and another pivoting direction of the star wheel via certain different areas according to the same but opposite characteristic curve segments or also according to different but preferably opposite characteristic curve segments. This will allow, for example, the same actuators arranged as mirror images of each other to operate different, preferably paired, transmission elements. The (non-linear) restoring force or pretension force allocated to the transmission elements can also be set as needed to correspond to different resulting characteristic curves. However, even when using different pins, it is generally expected that the characteristic curves will be the same in at least some areas.

[0014] To facilitate the operation of different transmission elements, it can be specified that the pin pivots in the first slot to pivot the spur gear from the neutral position to the second direction without any actuation. This makes it easier to separate the two torque paths for actuating the first and second transmission elements, especially in the region between the output shaft and the transmission element, and allows for greater tolerances. Specifically, it can be specified that the characteristic curves for the corresponding actuation of the various transmission elements are of the same magnitude, but caused by the pin engagement in different slots. When the transmission element is actuated from the second slot, the angular range traversed by the star gear is three times larger than the angular range of the first transmission element. This is achieved by a first angular range in the first slot, which requires no actuation traversal and is the same in magnitude as the angular range used to actuate the first transmission 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., opposite to the actuation of the first transmission element.

[0015] After traversing the first angular range in the second direction, the drive element rotates further such that the pin penetrates the second pin of the star wheel. The star wheel no longer pivots further. After the star wheel pivots further within a certain angular range, which again corresponds to the first angular range, the pin gear mechanism enters a position where the pin is again in the same position as the neutral position. This corresponds to a pivot of the star wheel by twice the angular range, preferably 30°. Actuation of the second transmission element can already be provided within this double angular range. However, to utilize the higher dynamics in this region and also to clearly separate the actuation of the two transmission elements, it is preferably specified that the pin pivots again by a further angular range, which again corresponds to the first angular range. Thus, the star wheel pivots a total of three angular ranges, preferably 45°, opposite to the pivoting of the transmission element. Another advantage is that the pin gear mechanism is in a self-locking position when pivoting about the first angular range and about the third angular range. Therefore, there are preferred stable positions for the actuator in the neutral position and when the star wheel pivots within the first angular range and three times the angular range, wherein the transmission element remains in the actuated state even when the actuator is not driven in the latter two pivot positions.

[0016] Furthermore, the object of the present invention is achieved by a transmission system having an actuator as described above. The transmission system includes at least a first transmission element and a second transmission element, each of which is actuated by the same actuator described above.

[0017] In a further improvement, it is specified that at least two actuators are present on different sides in the lateral direction, wherein the at least two actuators are identical in design and each is arranged to point away from the center of the vehicle. In this document, "lateral direction" refers to the direction perpendicular to the direction of travel of the motor vehicle. That is, the drivetrain is designed such that the first actuator for controlling the first pair (two) of transmission elements is arranged on one side, i.e., laterally relative to the vehicle and therefore relative to the direction of travel of the drivetrain in a front-to-rear direction. Furthermore, the drivetrain also includes another pair of transmission elements actuated by a second identical actuator. Since the second pair of transmission elements is positioned laterally to different sides of the drivetrain or vehicle, the positions of the actuators need to be adjusted accordingly. Due to the design of the aforementioned actuators, it is sufficient to use a second identical actuator, which can be simply reversed so that it is a mirror image of the first actuator. It can be advantageously specified that the second transmission element is precisely actuated when the star wheel of the corresponding actuator pivots from the neutral position by an amount equal to three times the angle actuating the first transmission element.

[0018] For the drivetrain, it is advantageous if the two drive elements are a parking lock and a disengaged clutch, particularly a pawl clutch. Actuation then occurs from the output shaft, specifying two distinct final states corresponding to the actuated and unactuated states of the drive elements. For this purpose, actuation by means of the described actuator is particularly advantageous because these two states can be controlled and maintained in a self-locking manner by the corresponding position of the pin within or just outside the corresponding slot. First, these conditions are determined by the position of the pin in the corresponding slot, where the axis of rotation passing through the drive element and the straight line of the pin are perfectly perpendicular to the straight line passing through the center of the slot and the output shaft, preventing adjustment due to unintentional movement of the output shaft; i.e., the pin-type gear mechanism is self-locking here. Second, the pin can also be moved outside the slot, such that the outer contour of the star wheel engages with the corresponding outer contour of the drive element, causing them to roll against each other without torque transmission. Therefore, in these preferred positions, self-restraint of the actuator can be achieved. Since the intermediate states between these two states have no effect on the function of these drive elements, the specific process of torque transmission from the drive element to the output shaft between the two self-locking positions is not important. Larger tolerances are acceptable here; in particular, self-locking is not necessary, as these intermediate components are only covered during actuation and should not be in a static state. If a power failure occurs during operation, the actuator will return to its own neutral position, or to the neutral position of the star wheel. As mentioned above, if one of the transmission elements is actuated, the actuator can switch to a non-drive state because the pin gear mechanism is in a self-locking state.

[0019] Furthermore, the drivetrain can be configured such that, in the case of a first actuator, a first drive element, such as a parking lock, is actuated when the star wheel pivots in a first direction, preferably at a first angle, and a second drive element, such as a claw clutch, is actuated when the star wheel pivots in a second direction, preferably at a second angle; and in the case of a second identical actuator, the second drive element is actuated when the star wheel pivots in the first direction, preferably at a second angle, and the first drive element is actuated when the star wheel pivots in the second direction, preferably at a first angle, wherein the first direction points in the opposite direction to the second direction, and is measured relative to the neutral position of the star wheel in each case.

[0020] To achieve the lowest possible energy consumption, it can be specified that each actuator has as little self-locking as possible or is driven by a driver without self-locking. The neutral position can be safely and undrivenly maintained by means of the pre-tensioning of the stop by the transmission element.

[0021] In summary, this allows the same actuator to be used in different mirror positions of the drivetrain to preferentially actuate pairs of first and second drive elements positioned mirror-relative to each other, such as parking locks and pawl clutches. This is particularly applicable to electric axles where a pair of parking locks and disconnectable couplings, for example, pawl clutches, are located at both ends / sides of the axle. The pin-gear mechanism used also allows for easy self-locking in the preferred positions of the drive elements. Attached Figure Description

[0022] The following figures illustrate exemplary embodiments of the present invention, from which further features of the invention can be derived, and the invention is not limited to these exemplary embodiments. In the figures: Figure 1 The actuator is shown in the neutral position. Figure 2 : Shows according to Figure 1 The actuator in the second position, Figure 3 : A symbolic representation of one side of a transmission system having an actuator according to the invention. Detailed Implementation

[0023] Figure 1 Actuator 1, or at least a portion thereof, is shown. This excerpt specifically shows a pin gear mechanism 2. The pin gear mechanism 2 has a drive element 3 and an output shaft 8. The output shaft 8 is received in the star wheel 6 of the output element 5. The pin gear mechanism 2 is substantially identical in construction to a known Maltese cross gear, except that a complete cross for the star wheel 6 is absent or unnecessary.

[0024] Torque is transmitted to the star wheel 6 via the drive element 3. For example, this torque could be transmitted directly to other actuating elements via the edge of the output shaft 5. However, in the case shown here, the torque is transmitted directly from the star wheel 6 to the output shaft 8. The output shaft 8 is connected, for example, via a camshaft or the like, to the actuating elements for actuating the drive elements 9, 10. The output shaft 8 may also have a cam, not shown here, and thereby directly or indirectly actuate the drive elements 9, 10.

[0025] The drive element 3 can be driven indirectly or directly by an electric motor (not shown), i.e., set to rotate.

[0026] The drive element 3 has a disk 30 at its lower axial position. A pin 4 protrudes eccentrically from the disk 30 in an axial direction away from the disk 30. Here, axial refers to the axis of rotation 20 of the drive element 3.

[0027] Pin 4 can engage in slot 7 in a manner known for Maltese cross gears, and transmit torque from drive element 3 to star wheel 6, which has slot 7 in its edge region, by pivoting within these slots 7.

[0028] Pin-type gear mechanism 2 and therefore star gear 6 in Figure 1 The star wheel 6 is in a neutral position, in which pin 4 engages in the central first groove 23. When the star wheel 6 pivots from this position along a first direction by a first angle α', the first transmission element 9 is actuated. This first transmission element 9... Figure 3 The short spring 31 is shown as a proxy image. The pivot of the star wheel 6 at a first angle α' is associated with the pivot of the pin 4 from its neutral position, that is, the position of the pin 4 assumed to be in the neutral position of the star wheel 6. In the case shown here, α' = 15°, while α is approximately between -80° and -89°. That is, the pin 4 rotates in the opposite direction to the star wheel 6, and the actuation of the first transmission element 9 occurs shortly before the pin 4 rotates out of the first slot 23.

[0029] Torque transmission proceeds from the neutral position according to a characteristic curve derived from the angular position of the distance between the rotation axis 20 of the drive element 3 and the pin 4, and the distance between the rotation axis 22 of the output shaft 8 and the pin 4. Maximum torque is transmitted at a 0° angle. This is the case when the star wheel is in its neutral position. Figure 2 In this context, the angle includes 90°, where the torque is at its minimum. Figure 2 The position of the star wheel 6 shown is the self-locking state of the pin gear mechanism 2.

[0030] Sales can be made from Figure 1The neutral position of pin 4 moves slightly less than -90° (meaning a quantity) along the direction of angle α. Angle α refers to the rotation axis 20 of drive element 3. This adjustment of pin 4 corresponds to the pivoting of star wheel 6 at angle α' = 15°. After the star wheel 6 rotates 15°, pin 4 is in the radially outer extreme position of the first groove 23. The transmitted torque is minimal; the pin-gear mechanism 2 is self-locking in this state. As described, when the star wheel 6 pivots 15°, the first transmission element 9 is actuated. This actuation occurs due to the rotation of output shaft 8 in the clockwise direction of rotation in direction 34. Pin 4 accordingly moves counterclockwise to two positions perpendicular to each other, formed by pin 4 and the rotation axis 20 of drive element 3 and the rotation axis 22 of star wheel 6 or output shaft 8. If pin 4 moves further out of the first groove 23 along the direction of angle α, the profile 32 of drive element and the reverse profile 33 of star wheel 6 will roll against each other in a self-locking manner. This means that the position of pin 4 in the first groove 23 does not need to be precisely controlled.

[0031] If pin 4 first rotates by the same angle α in the opposite direction, the actuation of the first transmission element 9 is reversed. When it rotates further by an angle β in the opposite direction, no further actuation of transmission elements 9 and 10 occurs. During this movement of pin 4, the second angle β' of the pivoting of the star wheel 6 in the first groove 23 is also -15°, that is, its direction is opposite to the pivoting during the actuation of the first transmission element 9. For other arrangements of groove 7 and dimensions of drive element 3, angles α' and β' can also be set to be correspondingly different from 15°.

[0032] If the drive element 3 rotates further in the direction of angle β, the pin 4 will disengage from the first groove 23. With further rotation of the drive element 3, the pin then rotates via profile 32 on the reverse profile 33 of the star wheel 6, as is known in Maltese cross gears, without any torque transmission. Throughout this entire region of rotation 3, the pin-type gear mechanism then remains in a self-locking state.

[0033] After a further corresponding rotation, slightly greater than 270°, pin 4 finally engages in the second slot 24. If pin 4 pivots again about the axis of rotation 20 by an angle β of almost 90°, the star wheel 6 pivots again by a second angle β' = -15°. Pin 4 is again in its neutral position, meaning that maximum torque can be transmitted here, and the pin gear mechanism 2 is not self-locking. Pin 4 can then be adjusted again by an angle of almost 90°. This corresponds to a further rotation of the star wheel by β' = -15°. That is, there is a total pivot or rotation of the star wheel γ = 3 * β = -45°. After the star wheel 6 completes this pivot, the pin gear mechanism 2 is again in the self-locking position. Actuation of the second transmission element 10 is completed in this position and can be kept undriven or without drive by actuator 1. The output shaft 8 rotates counterclockwise along direction 35 by three times the angle range opposite to the direction when the first transmission element 9 is actuated. When pin 4 engages in the second slot 24, the characteristic curve of torque transmission follows: from the minimum value, such as Figure 2 The self-locking position shown is at its maximum value, where the angle between the distances from the rotation axes 20 and 22 to the pin 4 is 0°, and it returns to the self-locking position after the total rotation angle of the star wheel 6 is -30°. If another reverse profile 33 is provided behind the second groove 24 in the circumferential direction of the star wheel 6, the pin 4 can also be moved out of the second groove 24 by further rotation of the drive element 3 in the direction of angle β. Precise proximity to this second self-locking position is not required here. Since profile 32 and reverse profile 33 are again on top of each other, a stable self-locking state of the pin gear mechanism 2 will also exist here.

[0034] Pin-type gear mechanism 2 to such Figure 1 The return motion from the neutral position shown in the figure will disengage the actuation of the second drive element 10.

[0035] If pin 4 pivots further in the direction of angle α from the actuated first transmission element 9, pin 4 will indeed enter another third slot 26, however, this third slot is not assigned to any transmission element 9, 10.

[0036] If the actuator 1 is integrated into the transmission system 40, such as Figure 3 Symbolically speaking, the two such actuators 1 can actuate the two transmission elements 9 and 10 on both sides of the transmission system 40 in a mirror manner as described above.

[0037] Figure 3 One side of this transmission system is symbolically shown.

[0038] Two distinct transmission elements 9 and 10 are represented here in the proxy diagram as springs 31 and 36 of different lengths. Springs 31 and 36 symbolize the restoring forces of transmission elements 9 and 10, which act on the pin-gear mechanism 2 via the transmission elements and must first be overcome by the drive mechanism (not shown) upon actuation. When the pin rotates by an angle α from its neutral position, the first transmission element 9, represented by the short spring 31, is actuated first. When the pin 4 rotates in the direction of angle β, the star wheel 6 first rotates by a second angle β' = -15°, causing the pin 4 to engage in the second groove 24 with further rotation of the pin. After the star wheel 6 has rotated a total of -45°, the second transmission element 10 is actuated by overcoming the restoring force represented by the long spring 36.

[0039] The actuation of transmission elements 9 and 10 is symbolically achieved here by a stop 41 on the star wheel 6, which acts on a support 42 that pivots coaxially about a pivot axis 43 against springs 31 and 36. The neutral position is then determined by a housing-fixed stop 44. The restoring forces of transmission elements 9 and 10 are represented here by springs 31 and 36. In the neutral position of the pin gear mechanism 2, even without a driving force, it is stably maintained in both directions by the opposing restoring forces of the two driving elements 9 and 10. In the aforementioned self-locking position, these restoring forces are eliminated. The state of transmission elements 9 and 10 defined in this way can then be maintained as energy-free.

[0040] Therefore, it is appropriate to use actuator 1 in drivetrain 40, in which drive elements 9, 10 having one or two preferred actuation positions, such as parking locks or claw clutches used in disengagement clutches, are arranged in a mirror manner relative to the longitudinal or lateral direction of the drivetrain.

[0041] List of reference numerals 1 Actuator 2. Pin-type gear mechanism 3. Driving components 4. Selling 5 Output Components 6 star wheels 7 slots 8 Output shafts 9 First transmission element 10 Second transmission element 20 Rotation axis 21. Straight Line 22. Rotation axis 23 First slot 24 Second slot 25. Axis of symmetry 26 Third slot 30 discs 31 Short Spring 32 Outline 33 Reverse Contour 34 directions 35 directions 36 Long Spring 40 Transmission System 41 Stop component 42 pillars 43. Axis of rotation 44 Stop components α angle β angle α' First angle β' Second Angle

Claims

1. An actuator (1) having a pin-gear mechanism (2). The pin-gear mechanism (2) includes a drive element (3) having at least one pin (4). The pin gear mechanism further includes an output element (5), which includes a star wheel (6) on a shaft, preferably an output shaft (8), the star wheel having at least one groove (7). The star wheel (6) is pivoted by the pin (4), which engages for this purpose in the at least one groove (7), characterized in that, A first transmission element (9) is actuated by means of the output element (5), preferably the output shaft (8), by means of the first pivot of the star wheel (6) at a first angle (α') via the pin (4), and a second transmission element (10) is actuated by means of the first pivot of the star wheel (6) at a second angle (β'), the second angle being different from the first angle (α'), wherein both angles (α', β') are measured from the same origin.

2. The actuator (1) according to claim 1, characterized in that, The second angle (β') points to the neutral position of the star wheel (6) in a direction opposite to the first angle (α').

3. The actuator (1) according to claim 2, characterized in that, The neutral position of the star wheel (6) is defined by the fact that in the neutral position, the straight line (21) passes through the rotation axis (20) of the drive element (3), the pin (4) and the rotation axis (22) of the star wheel (6), wherein the rotation axis (22) of the star wheel (6) is preferably the rotation axis (22) of the output shaft (8).

4. The actuator (1) according to any one of claims 1 to 3, characterized in that, The straight line (21) in the neutral position of the star wheel (6) represents the axis of symmetry (25) of the star wheel (6), wherein, in the neutral position, the first groove (23) of the star wheel (6) is longitudinally divided by the axis of symmetry (25), and the first transmission element (9) is actuated by pivoting in the first groove (23) in a first direction via the pin (4), and the second transmission element (10) is actuated by pivoting in the second groove (24) in a second direction opposite to the first direction via the pin (4).

5. The actuator (1) according to claim 4, characterized in that, The pivoting of the pin (4) in the first groove (23) from the neutral position of the star wheel (6) to the second direction is performed without actuation.

6. A transmission system for a motor vehicle, having an actuator (1) according to any one of claims 1 to 5, and comprising at least one first transmission element (9) and a second transmission element (10).

7. The transmission system of a motor vehicle according to claim 6, characterized in that, At least two actuators (1) are present on different sides in a lateral direction perpendicular to the direction of travel of the motor vehicle, wherein the at least two actuators (1) are identical in construction and arranged in a mirror manner with respect to each other.

8. The transmission system according to any one of claims 6 or 7, characterized in that, The first transmission element (9) is a parking lock, and the second transmission element (10) is a disengageable clutch, preferably a claw clutch.

9. The transmission system according to claim 7 or claims 7 and 8, characterized in that, In the first actuator (1), the first transmission element (9) is actuated when the pin (4) or the star wheel (6) pivots in a first direction, and the second transmission element (10) is actuated when the pin (4) or the star wheel (6) pivots in a second direction. In the same second actuator (1), the second transmission element (10) is actuated when pivoting in the first direction, and the first transmission element (9) is actuated when pivoting in the second direction, wherein the first direction is opposite to the second direction, and in each case refers to the neutral position of the star wheel (6).

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