Integration of a gear actuator

Abstract

Gear selector (1) for setting at least one shift position in a gearbox which has at least one gearbox shaft (2), wherein the gear selector (1) is designed to perform an actuating movement (1a) in an actuating direction (1b) to set the switching position, wherein a characteristic orientation direction of the gear actuator (1) relative to the gear shaft axis (2a) of at least one gear shaft (2) is not oriented parallel, wherein the characteristic orientation direction is the positioning direction (1b), and wherein the positioning direction (1b) is arranged substantially parallel to a tangent to the outer contour of two transmission stages arranged on the same transmission shaft (2) and formed by gear stages with different outer diameters, wherein the respective outer contour corresponds to the outer diameter of the respective gear.

Description

[0001] The present invention relates to a gear actuator, a transmission mechanism for the gear actuator, a system of gear actuator and transmission mechanism, a transmission with such a system, a drive train and a vehicle.

[0002] In vehicle development, the optimal use of installation space plays a crucial role. For example, if a component can be designed to be more space-saving, the space saved can either be used to install other components, or a housing can be made tighter around certain components.

[0003] In gearbox construction, it is common to use a gear selector to set a shift position, embodied by a gear stage ("gear"), or to set a neutral position within the gearbox. The gear selector performs an actuating movement that is applied directly or via intermediate elements to a shift element, particularly a shift sleeve, thereby moving it to achieve the desired shift position. The actuating movement of the gear selector is oriented parallel to the gearbox shaft axis, which means that the gear selector itself also extends essentially parallel to the gearbox shaft axis. The problem here is that there is free space between the outer contour of the gear stages, for example, between the outer diameter of the gears on the gearbox shaft, and the gear selector.

[0004] In this context, US 2,616,535 A relates to a three-speed positive-drive transmission system for motor vehicles, controlled by a single control element that can be manually moved from a common rest position of the transmission to two different driving positions, wherein one of the driving positions controls the engagement of a first driving gear and the other driving position controls the alternating engagement of a second and third driving gear by automatically actuated means controlled according to the accelerator pedal position and vehicle speed.

[0005] DE 197 05 557 A1 relates to a gearbox comprising two gears supported by two shafts, meshing in pairs, at least one of which is rotatably mounted on the associated shaft, an axially displaceable coupling sleeve cooperating with each rotatably mounted gear, which has an engagement position in which it locks the gear on the shaft and a disengagement position in which it allows free rotation of the gear on the shaft, a shift fork cooperating with each coupling sleeve for axial displacement of the coupling sleeve between the aforementioned positions, and a shift guide mechanism for controlling the respective shift fork.

[0006] JP 2012-207684A relates to a vehicle gearshift unit for switching a shift rod of the gearshift unit using a motor. The gearshift unit comprises a rotary / linear motion conversion mechanism that converts a rotary motion into a reciprocating linear motion and switches the shift rod, a driven gear that transmits the rotation to the rotary / linear motion conversion mechanism, and a pair of drive gears, each meshing with the driven gear and having a different reduction ratio to the driven gear.

[0007] A parallel arrangement of the actuating movement and the gearbox shaft axis can have disadvantages, particularly in short gearboxes or gearboxes with an increasing or decreasing housing geometry, with regard to installation space and in terms of mechanical support with regard to vibrations.

[0008] The purpose of the present invention is therefore to demonstrate ways to save this installation space.

[0009] This task is solved by the subject matter of the independent claims. Advantageous further developments are the subject matter of the dependent claims.

[0010] According to the invention, a gear actuator is provided for setting at least one switching position in a transmission which has at least one transmission shaft, wherein the gear actuator is designed to perform an adjusting movement in an adjusting direction for setting the switching position, wherein a characteristic orientation direction of the gear actuator is not oriented parallel to the transmission shaft axis of the at least one transmission shaft.

[0011] Preferably, the characteristic orientation direction is a principal extension direction of the gear actuator, in which the maximum extension of the gear actuator lies relative to its extensions in the other two spatial directions. For example, if the gear actuator has a width of 100 mm, a depth of 70 mm, and a length of 200 mm, then the extension direction along which the length of the gear actuator extends is the principal extension direction or characteristic orientation direction. Regardless of this, the characteristic orientation direction is the positioning direction of the gear actuator.

[0012] The gear actuator therefore preferably has a design that allows it to be mounted in or on the gearbox, such that its main direction of extension and / or its positioning direction are not oriented parallel to the gearbox shaft axis. In particular, the gear actuator can be designed for mounting by means of fasteners, such as screws.

[0013] Preferably, the main extension direction and the positioning direction of the gear actuator are parallel to each other or identical.

[0014] Preferably, the characteristic orientation direction of the gear actuator and the axis of the transmission shaft of at least one transmission shaft are oriented relative to each other such that they intersect at an angle. Alternatively, a skew orientation of the characteristic orientation direction of the gear actuator and the axis of the transmission shaft can also be provided.

[0015] Preferably, the gear actuator can be actuated hydraulically, pneumatically, electrically, magnetically, and / or mechanically. The actuating movement is preferably translational. In the case of hydraulic or pneumatic actuation, a piston is preferably provided which is moved by hydraulic or pneumatic pressure to perform the actuating movement. Mechanical actuation can be implemented, in particular, by a rack and pinion combination, a worm gear, or a ball screw. In the case of electrical or magnetic actuation, the required force is generated by electric or magnetic fields. Finally, different principles can also be combined. For example, an electric motor can drive a ball screw, thereby mechanically producing an actuating movement.

[0016] The characteristic orientation direction is essentially parallel to a tangent to the outer contour of two transmission stages, with the two transmission stages being arranged on the same transmission shaft. This allows the gear selector to be oriented according to the outer contour of the transmission stages, thereby achieving the desired space savings. The transmission stages are formed by gear stages. The outer contour is the outermost dimension of the transmission stages. In the case of a gear stage, this corresponds to the outer or pitch circle diameter of the gear.

[0017] According to the invention, a transmission mechanism for transmitting an actuating movement, in particular of a gear actuator as described above, is provided. This mechanism has a first coupling point configured to make contact with the gear actuator and receive its actuating movement, and a second coupling point configured to make contact with a switching element of a transmission, in particular a shift sleeve. The transmission mechanism is configured to convert the actuating movement into a shifting movement that sets a shift position in the transmission. This advantageously ensures that the linear actuating movement of the gear actuator does not have to be converted in parallel with the shifting movement of the shifting element. Instead, it now provides a way to position the gear actuator in a different orientation within the transmission.However, the transmission mechanism can also be designed to convert an positioning movement oriented parallel to the transmission shaft axis into a switching movement.

[0018] In this application, the term "coupling point" refers specifically to a location or element of the transmission mechanism through which the actuating movement can be applied to the transmission mechanism, or through which the switching movement can be transmitted. The coupling points therefore represent interfaces through which the transmission mechanism can come into contact with the gear actuator or the switching element. These interfaces can be configured in various ways, as illustrated by example below.

[0019] Preferably, the transmission mechanism includes a transmission element designed to convert the positioning movement into the switching movement. The transmission element can, for example, be designed as a rod or have a rod-like structure.

[0020] Preferably, the transmission element is designed to translate the positioning movement into the switching movement. This can involve either a reduction or a step-down transmission. A 1:1 ratio is also conceivable, so that the positioning movement corresponds to a movement that covers the same distance as the resulting switching movement. With a step-down transmission, i.e., when the positioning movement covers a greater distance than the resulting switching movement, it is advantageous that the gear actuator performing the positioning movement can be designed to be smaller or less powerful compared to an embodiment with a gear reduction, since the force applied to the switching element via the transmission mechanism from the gear actuator is simultaneously increased. With a gear reduction, it is again advantageous that the distance covered by the positioning movement is shorter than the distance covered by the switching movement.This means that less installation space needs to be provided for the gear actuator or for its actuating movement.

[0021] Preferably, the transmission element is rotatably mounted and designed to generate a switching movement through rotation. The transmission element is preferably rotatably mounted at a pivot point located between the coupling points. The transmission ratio can thus be determined by the respective distances between the pivot point and the respective coupling points, whereby further influences, such as contact surface pairing or length compensation, as described below, can further affect the transmission ratio.

[0022] The pivot point is preferably provided on the gear actuator or integrated in the gear actuator, so that the gear actuator and the transmission element form an integral unit which can be easily mounted directly onto the gearbox, wherein the transmission element particularly preferably establishes a direct mechanical connection to the switching element during assembly (e.g. by engaging a switching sleeve).

[0023] The transmission element can be specifically designed as a switching fork, or it can include a switching fork alongside other elements. The switching fork is preferably designed to be connected to the switching element at the second coupling point in order to impose the switching movement on it.

[0024] Preferably, the transmission element is designed to be translationally displaceable, in particular parallel to the axis of the transmission shaft, in order to convert the positioning movement into the switching movement. Translational displaceability can be provided as an alternative or in addition to the rotatable mounting of the transmission element. With additional displaceability, a more complex movement of the transmission element is also possible in combination with the rotatable mounting, in order to translate the positioning movement into a switching movement.

[0025] Preferably, the transmission mechanism includes a length compensation mechanism designed to compensate for length differences between the coupling points when the actuating movement is applied. Since the actuating movement is not parallel to the transmission shaft axis, length compensation must be performed between the coupling points. This length compensation mechanism can be designed in various ways. If the connection between the gear actuator or the switching element at the respective coupling point is implemented using a bearing that allows rotational movement between the gear actuator or switching element and the transmission mechanism, then length compensation must be performed between the two coupling points. The same applies if the connection at the coupling points does not allow rotational movement. The length compensation mechanism is preferably integrated as part of the transmission element. For example, a rolling or sliding bearing can be used as the bearing.

[0026] Preferably, the length compensation mechanism has an elastic preload acting between the coupling points. This elastic preload can preferably be generated by a spring. The elastic preload preferably ensures that the length compensation mechanism is always subjected to a force, so that the transmission element always tends to expand between the coupling points.

[0027] According to the invention, a system is provided which has a gear actuator as described above and a transmission mechanism as described above, wherein the gear actuator is connected to the transmission mechanism via the first coupling point for imprinting the actuating movement onto the transmission mechanism.

[0028] If the transmission mechanism has a transmission element that can be rotated about a pivot point, this pivot point is preferably provided on or integrated into the gear actuator, as already explained above.

[0029] Preferably, the connection between the gear actuator and the transmission mechanism at the first coupling point is designed to be rotationally fixed. Alternatively or additionally, this connection can also be formed in one piece. That is, at the first coupling point, an element of the transmission mechanism, preferably the element that transmits the switching movement to the switching element, and the element of the gear actuator that performs the positioning movement are formed as a single component.

[0030] Alternatively, the connection between the gear actuator and the transmission mechanism at the first coupling point can also be rotatable or comprise a contact surface pairing. A rotatable design can be achieved, in particular, by means of a sliding or rolling bearing, via which the transmission mechanism, preferably its transmission element, and the element of the gear actuator that performs the positioning movement are connected. In the case of a contact surface pairing, the connection between the transmission mechanism, preferably the transmission element, and the element of the gear actuator that performs the positioning movement is established by contact between the two elements. These are designed so that they merely abut each other, allowing the positioning movement to be imposed on the transmission mechanism. For this purpose, contact surfaces are formed on both elements.Particularly in the case of a rotatable transmission element or for the realization of length compensation, the contact surface pairing can be designed in such a way that both contact surfaces roll and / or slide against each other in their contact and / or perform a relative movement to each other in order to represent the rotational movement or the length compensation.

[0031] According to the invention, a transmission is provided which includes a system as described above and a switching element, in particular a switching sleeve. The switching element is configured to perform a switching movement in order to set a switching position in the transmission. The switching element is connected to the transmission mechanism for imprinting the switching movement onto the switching element via the second coupling point.

[0032] Preferably, the gear selector is arranged in the transmission such that a characteristic orientation direction of the gear selector, as described above, is not parallel to a transmission shaft axis. Particularly preferably, the characteristic orientation direction, especially the positioning direction and / or the main extension direction, is arranged essentially parallel to a tangent to the outer contour of two transmission stages, wherein the two transmission stages are preferably arranged on the same transmission shaft.

[0033] Preferably, the connection between the switching element and the transmission mechanism at the second coupling point is designed to be rotationally fixed. Alternatively or additionally, this connection can also be formed in one piece. That is, at the second coupling point, an element of the transmission mechanism, preferably the element to which the actuating movement of the gear actuator is applied, and the switching element are formed as a single component.

[0034] Alternatively, the connection between the switching element and the transmission mechanism at the second coupling point can be rotatable or comprise a contact surface pairing. A rotatable design can be achieved, in particular, by means of a sliding or rolling bearing, via which the transmission mechanism, preferably its transmission element, and the switching element are connected. In the case of a contact surface pairing, the connection between the transmission mechanism, preferably the transmission element, and the switching element consists of contact between the two elements. These are designed so that they merely abut each other, allowing the switching movement to be imprinted on the switching element. For this purpose, contact surfaces are formed on both elements.Particularly in the case of a rotatable transmission element or for the realization of length compensation, the contact surface pairing can be designed in such a way that both contact surfaces roll and / or slide against each other in their contact and / or perform a relative movement to each other in order to represent the rotational movement or the length compensation.

[0035] According to the invention, a drive train for a vehicle is provided which has a transmission as described above.

[0036] The articles according to the invention shown here are preferably designed to be installed in an electrically or hybrid-powered vehicle. Alternatively or additionally, the articles according to the invention shown here are designed to be installed in a commercial vehicle.

[0037] According to the invention, a vehicle is provided which has a transmission or drivetrain as described above. Preferably, the vehicle is electrically or hybrid powered and / or designed as a commercial vehicle.

[0038] The invention is not limited to the embodiments described above. Rather, further embodiments can be obtained by combining individual features, replacing them with others, or omitting them.

[0039] The invention will therefore be described in more detail below with reference to preferred embodiments and the accompanying drawings.

[0040] They show: Fig. 1 a first embodiment of the invention, and Fig. 2 a second embodiment of the invention.

[0041] Fig. Figure 1 shows a first embodiment of the invention. It shows a basic arrangement of a gear actuator 1, a transmission mechanism 8 and a gear shaft 2 in a sectional view.

[0042] The gear actuator 1 is designed to perform an positioning movement 1a, which is represented in the drawing by the double arrow as a translational movement. The positioning movement 1a can thus be executed parallel to a positioning direction 1b, which is indicated in the drawing by a dashed line. The positioning direction 1b is inclined relative to the gear shaft axis 2a by an angle 7, so that the positioning direction 1b and the gear shaft axis 2a are not oriented parallel to each other. In the embodiment shown, the positioning direction 1b corresponds to the characteristic orientation direction of the gear actuator 1, as described above.

[0043] The transmission shaft 2, whose axis 2a is oriented horizontally from left to right, has a first gear 3 and a second gear 4, which are rotatably mounted on the transmission shaft 2. Both gears 3 and 4 have different radii and thus form different gear ratios. Furthermore, a shifting element 5 in the form of a shift sleeve is provided on the transmission shaft 2 between the gears 3 and 4. This shifting element 5 is designed to be displaceable in a shifting movement 5a, which here is a translational movement parallel to the axis 2a of the transmission shaft. The shifting element 5 is fixed to the transmission shaft 2 about the axis 2a.

[0044] The arrangement shown here of transmission shaft 2, gears 3 and 4, and switching element 5 corresponds to an arrangement known from gearbox construction. To set a switching position, for example, via the gear ratio represented by the first gear 3, the switching element 5 is moved to the right by a switching movement 5a. Here, the switching element 5 comes into contact with the first gear 3 and forms a rotationally fixed connection around the transmission shaft axis 2a, so that the first gear 3 is now rotationally fixed to the transmission shaft 2 via the switching element 5. Setting the switching position via the gear ratio represented by the second gear 4 is accomplished analogously by a switching movement 5a of the switching element 5 to the left.

[0045] In the arrangement shown, the positioning direction 1b is oriented according to the outer contour of the transmission stages of the transmission shaft 2. Specifically, this means that the positioning direction 1b is oriented parallel to a tangent to the gears 3, 4. More generally, such an orientation can also be parallel to a three-dimensional envelope of the transmission stages.

[0046] Furthermore, a transmission mechanism 8 is provided for transmitting the actuating movement 1a to the switching element 5, so that the switching element 5 can execute the switching movement 5a. The transmission mechanism 8 has a first coupling point 8a, via which the gear actuator 1 is coupled to the transmission mechanism 8. The transmission mechanism 8 has a further second coupling point 8b, via which the switching element 5 is coupled to the transmission mechanism 8.

[0047] The transmission mechanism 8 further comprises a transmission element 8c which is rotatable about a pivot point 8d and which is designed to translate the actuating movement 1a, which is applied to the first coupling point 8a, into the switching movement 5a.

[0048] The connection between gear actuator 1 and switching element 5 can be implemented differently at coupling points 8a, 8b.

[0049] In one embodiment, at least one connection at one of the two coupling points 8a, 8b can be pivotally designed, so that the transmission element 8c can rotate about the first coupling point 8a relative to the gear actuator 1 and / or about the second coupling point 8b relative to the switching element 5. For example, a bearing, in particular a plain or roller bearing, can be provided in the corresponding coupling point 8a, 8b. With such a connection, the part of the transmission element 8c that is connected to the corresponding coupling point 8a, 8b must always be able to follow the bearing.Therefore, due to the non-parallel orientation of the transmission shaft axis 2a to the direction of rotation 1b at angle 7, length compensation must be performed during a rotational movement of the transmission mechanism 8 about the pivot point 8d in order to align the first coupling point 8a parallel to the direction of rotation 1b and the second coupling point 8b parallel to the transmission shaft axis 2a. For this purpose, the transmission mechanism 8 has a length compensation mechanism (not shown) designed to perform the length compensation between the two coupling points 8a and 8b.

[0050] The length compensation mechanism can, for example, be implemented by a transmission element 8c whose length between the coupling points 8a and 8b is variable. During a rotational movement of the transmission element 8c, it is ensured that the transmission element 8c can follow the changing distance between the coupling points 8a and 8b.

[0051] The length compensation mechanism can also incorporate an elastic preload force, which can be applied, for example, by a spring. The elastic preload force is oriented such that it acts between the coupling points 8a and 8b and is always oriented in the direction of extension of the transmission element 8c. In this way, any change in the length of the rod can be supported by the elastic preload force, ensuring reliable length compensation.

[0052] In a specific embodiment, a length compensation mechanism can have a transmission element 8c in the form of a rod, the ends of which are rotatably connected to the gear actuator 1 or the switching element 5 at the coupling points 8a, 8b by means of sliding or rolling bearings. The rod thus extends between the coupling points 8a, 8b. In addition, a spring is provided whose elastic preload force acts between the coupling points 8a, 8b and causes the rod to always maximize its length between the coupling points 8a, 8b.

[0053] The connection of the transmission element 8c in at least one of the coupling points 8a, 8b can also be designed as a rolling and / or sliding coupling. For this purpose, a contact surface pair (not shown) is formed in at least one of the coupling points 8a, 8b, via which the transmission element 8c is in contact with the gear actuator 1 and / or with the switching element 5. The positioning movement of the gear actuator 1 can now be transmitted to the transmission element 8c via the contact surface pair in the first coupling point 8a, with one contact surface being formed on the gear actuator 1 and the other contact surface on the transmission element 8c. Similarly, a rotary movement of the transmission element 8c can also be transmitted to the switching element 5. Here, too, a contact surface pair can be provided in the second coupling point 8b, with one contact surface being formed on the switching element 5 and the other contact surface on the transmission element 8c.The respective contact surfaces in the contact surface pairings are designed to roll and / or slide against each other. At least one contact surface can be curved for this purpose. If the transmission element 8c rotates about the pivot point 8d, the contact surfaces in the corresponding contact surface pairings roll and / or slide. Due to this rolling and / or sliding process, the contact point between the contact surfaces within the contact surface pairing moves. Therefore, length compensation is not strictly necessary here, as this is achieved by the moving contact point.

[0054] The connection of the transmission element 8c at at least one of the coupling points 8a, 8b with the gear actuator 1 and / or with the switching element 5 can also be formed integrally. That is, an element of the gear actuator 1 that performs the actuating movement 1a is integrally formed with the transmission element 8c at the first coupling point 8a. Alternatively or additionally, the switching element 5 can also be integrally formed with the transmission element 8c at the second coupling point 8b.

[0055] Depending on the embodiment, the gear actuator 1 can be actuated in particular hydraulically, pneumatically, electrically, magnetically and / or mechanically.

[0056] The functionality of the arrangement shown is as follows: Initially, the arrangement shown is configured as depicted. The switching element 5 is located between gears 3 and 4. Thus, the arrangement is in the neutral position. To set a switching position, represented by the first gear 3, the gear selector 1 performs an actuating movement 1a in the direction 1b to the upper left in the drawing. This moves the first coupling point 8a along the direction 1b to the upper left, rotating the transmission element 8c counterclockwise around pivot point 8d. This, in turn, moves the second coupling point 8b, and therefore the switching element 5, in an actuating movement 5a to the right, parallel to the gear shaft axis 2a. This continues until the switching element 5 engages the first gear 3, thereby setting the desired switching position, as described above.Setting a different switching position, namely the one embodied by the second gear 4 or the neutral position, is done analogously by a corresponding actuating movement 1a of the gear selector 1 to the right downwards or back into the position shown. Fig. Position 1 shown.

[0057] Fig. Figure 2 shows a second embodiment of the invention. Here, too, a sectional view shows an arrangement of a gear actuator 1, a transmission mechanism 8, and a gear shaft 2. The embodiment shown here differs from the one shown in Figure 2. Fig. 1 by a different design of the transmission mechanism' 8. The gear actuator 1 and the gear shaft 2 are equipped with those from Fig. 1 identical. Therefore, for their explanation, reference is made to the explanations regarding Fig. 1 referred.

[0058] Here too, the positioning direction 1b of the gear actuator 1 corresponds to the characteristic orientation direction of the gear actuator 1.

[0059] The transmission mechanism 8 here has a transmission element 8c which is connected at a first coupling point 8a to the gear actuator 1 and at a second coupling point 8b to the switching element 5. In contrast to the embodiment described in Fig. As shown in Figure 1, the transmission element 8c is not rotatably mounted. Instead, it is designed to be displaceable parallel to the transmission shaft axis 2a. This can be achieved, for example, by a guide (not shown) that guides the transmission element 8c parallel to the transmission shaft axis 2a. The guide can further be designed to guide the transmission element 8c in such a way that it is prevented from rotating with its axis of rotation perpendicular to the plane of the drawing.

[0060] The connection at coupling points 8a, 8b between the transmission element 8c and the gear actuator 1 or the switching element 5 can be designed in the same way as in the embodiment shown. Fig. 1. Thus, rotatable, rotationally fixed, one-piece designs and / or contact surface pairings can be provided, as described above. Fig. 1 were described.

[0061] When the gear actuator 1 performs an adjustment movement, a length compensation mechanism (not shown) must also be provided between coupling points 8a and 8b to compensate for length differences. This can also be configured as described above. Fig. 1 described as being trained.

[0062] The functionality of the arrangement shown is as follows: Initially, the arrangement shown is configured as depicted. The switching element 5 is located between gears 3 and 4. Thus, the arrangement is in the neutral position. To set a switching position, represented by the first gear 3, the gear selector 1 performs an actuating movement 1a in the direction 1b downwards and to the right in the drawing. This moves the first coupling point 8a downwards and to the right along the direction 1b, thereby shifting the transmission element 8c to the right. This, in turn, moves the second coupling point 8b, and thus the switching element 5, in an actuating movement 5a to the right, parallel to the transmission shaft axis 2a. Both coupling points 8a and 8b move towards each other because the length compensation mechanism allows for a shortening of the transmission element 8c.The shifting movement 5a to the right continues until the shifting element 5 contacts the first gear 3, thereby setting the desired shift position as described above. Setting a different shift position, namely the one represented by the second gear 4 or the neutral position, is accomplished analogously by a corresponding shifting movement 1a of the gear selector 1 to the upper left or back to the position shown.

[0063] In addition to the embodiments shown here, further embodiments are conceivable in which the positioning direction 1b of the gear actuator 1 is not oriented parallel to a tangent to the gears 3, 4. Rather, the positioning direction 1b can be oriented arbitrarily. Instead, a principal extension direction of the gear actuator 1 can be oriented parallel to the tangent to the gears 3, 4 as a characteristic orientation direction. This ensures that the gear actuator 1 adapts to the outer contour of the transmission stages embodied by the gears 3, 4 with its greatest extension direction. REFERENCE MARK LIST 1 Gearbox adjuster 1a Positioning movement 1b Direction of rotation 2 Gear shaft 2a Gearbox shaft 3 first gear 4 second gear 5 switching element 5a Switching movement 7 tilt angles 8 Transmission mechanism 8a first coupling point 8b second coupling point 8c transmission element 8d pivot point

Claims

[1] Gear selector (1) for setting at least one gear position in a gearbox having at least one gear shaft (2), wherein the gear selector (1) is designed to perform an actuating movement (1a) in an actuating direction (1b) to set the switching position, wherein a characteristic orientation direction of the gear actuator (1) relative to the gear shaft axis (2a) of at least one gear shaft (2) is not oriented parallel, wherein the characteristic orientation direction is the positioning direction (1b), and wherein the positioning direction (1b) is arranged essentially parallel to a tangent to the outer contour of two transmission stages which are arranged on the same transmission shaft (2) and are formed by gear stages with different outer diameters, wherein the respective outer contour corresponds to the outer diameter of the respective gear. [2] Gear actuator (1) according to claim 1, wherein the gear actuator (1) is hydraulically, pneumatically, electrically, magnetically and / or mechanically actuated. [3] Transmission mechanism (8) for transmitting an actuating movement (1a) of a gear actuator (1) according to one of claims 1 or 2, comprising: - a first coupling point (8a) designed to come into contact with the gear actuator (1) and to receive its actuating movement (1a), and - a second coupling point (8b) which is configured to come into contact with a switching element (5) of a transmission, in particular with a shift sleeve, wherein the transmission mechanism (8) is configured to convert the positioning movement (1a) into a switching movement (5a) which effects an adjustment of a switching position in the transmission. [4] Transmission mechanism (8) according to claim 3, comprising a transmission element (8c) configured to convert the positioning movement (1a) into the switching movement (5a). [5] Transmission mechanism (8) according to claim 4, wherein the transmission element (8c) is configured to effect a translation of the actuating movement (1a) into the switching movement (5a). [6] Transmission mechanism (8) according to claim 4 or 5, wherein the transmission element (8c) is rotatably mounted and is designed to generate a switching movement (5a) when the actuating movement (1a) is applied by means of rotation about a pivot point (8d). [7] Transmission mechanism (8) according to one of claims 4 to 6, wherein the transmission element (8c) is designed to be translationally displaceable in order to effect the conversion of the positioning movement (1a) into the switching movement (5a). [8] Transmission mechanism (8) according to one of claims 3 to 7, comprising a length compensation mechanism designed to perform length compensation between the coupling points (8a, 8b) when applying the actuating movement (1a). [9] Transmission mechanism (8) according to claim 8, wherein the length compensation mechanism has an elastic preload acting between the coupling points (8a, 8b). [10] System, comprising: - a gear actuator (1) according to one of claims 1 or 2 and - a transmission mechanism (8) according to one of claims 3 to 9, wherein the gear actuator (1) is connected to the transmission mechanism (8) via the first coupling point (8a) for imprinting the actuating movement (1a) onto the transmission mechanism (8). [11] System according to claim 10, wherein the connection between the gear actuator (1) and the transmission mechanism (8) at the first coupling point (8a) is rotationally fixed and / or formed in one piece. [12] System according to claim 10, wherein the connection between the gear actuator (1) and the transmission mechanism (8) in the first coupling point (8a) is rotatably designed or has a contact surface pairing. [13] Having a gearbox: - a system according to any one of claims 10 to 12, and - a switching element (5), in particular a switching sleeve, which is designed to perform a switching movement (5a) in order to set a switching position in the transmission, wherein the switching element (5) is connected via the second coupling point (8b) to the transmission mechanism (8) for imprinting the switching movement (5a) onto the switching element (5), wherein the transmission is preferably designed for an electrically or hybrid-powered vehicle and / or for a commercial vehicle. [14] Transmission according to claim 13, wherein the connection between the switching element (5) and the transmission mechanism (8) in the second coupling point (8b) is rotationally fixed and / or integrally formed. [15] Transmission according to claim 13, wherein the connection between the switching element (5) and the transmission mechanism (8) in the second coupling point (8b) is rotatably designed or has a contact surface pairing. [16] Drive train for a vehicle comprising a transmission according to any one of claims 13 to 15. [17] Vehicle comprising a transmission according to any one of claims 13 to 15 or a drive train according to claim 16.

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