Gearbox with non-linear characteristic curve

Abstract

The present invention relates to a transmission 1 comprising at least two transmission elements 12, 13, 14, 15, 16, wherein a first transmission element 12, 16 is arranged to be axially movable relative to a second transmission element 13, 14, 15. further comprising at least one switching shaft 2 and at least one axially displaceable switching element 3, 4 for axially moving the first transmission element 12, 16), a drive element 5 driving the at least one switching element 3,4 and at least two coupling elements provided between drive element 5 and switching element 3,4, wherein a first coupling element is designed as a pin 6 and a second coupling element as a slot 7 and the at least one switching element 3,4 is set into an axial movement by a movement of the pin 6 in the slot 7, wherein which at least one shift shaft 2 is arranged axially fixed to the second transmission element 13, 14, 15, the at least one switching element 3, 4 is axially displaced on or at the switching shaft 2 by the drive element 5 such that the axial movement of the at least one switching element 3, 4 follows a non-linear characteristic curve, and that the first transmission element 12, 16 is moved by the at least one switching element 3, 4 in such a way that a coupling of the first transmission element 12, 16 with the second transmission element 13, 14, 15 is selectively removed or established.

Description

[0001] The present invention relates to a transmission according to the preamble of claim 1 or 2, comprising at least two transmission elements, wherein a first transmission element is arranged to be axially movable relative to a second transmission element. The transmission further comprises at least one shift shaft, at least one axially displaceable shift element for axially moving the first transmission element, a drive element for driving the at least one shift element, and at least two coupling elements provided between the drive element and the shift element. A first coupling element is designed as a pin and a second coupling element as a slot. By moving the pin in the slot, the at least one shift element is set into an axial movement.

[0002] German patent DE 10 2014 221 904 A1 discloses a transmission in which exactly one single-motor transmission actuator is used for both selecting and shifting a multitude of gear sets. Complex mechanisms are required to engage a desired gear.

[0003] Furthermore, for example, switching drums for converting rotational movements into linear switching movements are known from GB 1,110,871 A.

[0004] Other relevant switching devices are known from DE 10 2005 038 681 A1, DE 10 2014 003 329 A1 and DE 100 11 271 A1.

[0005] Recently, the increasing electrification of powertrains has led to a greater demand for transmissions with simpler designs. The trend is moving towards transmissions with only one gear or with two selectable gears. In the commercial vehicle sector, there is a greater need for selectable transmissions, including those with more than two gears, than in the passenger car sector.

[0006] Therefore, in both conventional and electrified powertrains, there is still a fundamental need to switch or actuate individual switching elements. These can be, as already mentioned, two-speed gear sets, or also parking locks, differentials, or so-called disconnect units, which are needed, for example, to disconnect individual axles within the drivetrain. Actuating these switching elements places different demands on the switching dynamics than in familiar transmissions with multiple gear sets. In particular, higher forces are required for shifting, and higher speeds are desired for movement without shifting. Overall, simpler transmissions and switching actuators are preferred.

[0007] The present invention therefore aims to provide a gearbox that can meet the requirements for dynamics on the one hand and allows for a simple design on the other.

[0008] This problem of the invention is solved by a generic transmission with the characterizing features of claim 1 or claim 2.

[0009] Further advantageous embodiments of the transmission according to the invention are described in the dependent claims.

[0010] It is designed that at least one shift shaft is axially fixed to the second transmission element. This means that within the transmission, only the first transmission element moves relative to the second transmission element, while the second transmission element and the shift shaft are axially fixed to each other. If the transmission is located within a transmission housing, this means that the shift shaft and the second transmission element are fixedly mounted within this housing. No additional space needs to be provided for a moving shift shaft.

[0011] Furthermore, it is provided that the at least one switching element is axially displaced on or along the switching shaft by the drive element in such a way that the axial movement of the at least one switching element follows a non-linear characteristic curve. This allows, on the one hand, a higher speed of the switching element in a first movement phase to be combined with increased force / torque transmission in a second movement phase.

[0012] In this process, the second transmission element, through which at least one switching element is moved, is moved in such a way that a coupling of the first transmission element with the second transmission element is either removed or established.

[0013] Furthermore, according to the invention, the drive element is designed as a rotary disc.

[0014] In the second embodiment of the invention, the at least one pin is arranged on or attached to the rotary disk, and by rotating the rotary disk about an axis of rotation, the pin engages and disengages from the slot and is moved within the slot in such a way that the switching element is axially displaced. The movement of the pin within the slot essentially corresponds to the movement of a pin within a simple Maltese gear, with the torque being transmitted from the rotary disk to the switching element. The mechanics of the rotary disk allow for a particularly simple non-linear characteristic curve for the movement of the switching element and thus of the second gear element.

[0015] According to the invention, or preferably in an alternative solution, the at least one switching element has a driver fixedly arranged on the switching element, and the slot is formed in or on the driver. In this case, the torque is transmitted via the pin to the driver and thus to the switching element through the slot of the driver.

[0016] In the first alternative, and particularly preferably in the second alternative, the transmission may include two switching elements. These two switching elements are then preferably located either adjacent in a linear direction or on opposite sides of the rotary disk. Both switching elements have corresponding drivers arranged such that their slots are formed in a plane parallel or perpendicular to the axis of rotation of the rotary disk for the engagement of the at least one pin.

[0017] This design allows for a simple setup, enabling two different applications within the transmission using a single actuator or motor to drive the rotary disc. Two different switching elements can be actuated, each interacting with identical or different transmission elements, such as a parking lock, gear stages, switchable differential, interrupt switch, disconnect unit, or coupling. It is particularly advantageous if a first switching element engages exactly two gears, and in precisely one of these two positions, the second switching element is actuated to additionally bypass the differential, preferably in the lowest gear. The switching elements can be essentially identical and actuated by the same pin on or attached to the rotary disc.

[0018] Regardless of whether the switching elements are arranged adjacent in a linear direction or on opposite sides of the rotary disk, the drivers, slots, and pins can always be configured such that, in a first position, the drivers are positioned at an angle of 180° on a circle around the rotary disk, and in a second position, they are arranged on the same side of the rotary disk. In this second position, an angle of 0° between the drivers can be assumed. Accordingly, in a preferred embodiment, the slots are arranged such that their openings are opposite each other in both the first and second positions.

[0019] Depending on whether the pin is arranged perpendicularly on the plane of the turntable parallel to the axis of rotation or within the plane of the turntable, i.e., projecting from the turntable perpendicular to the axis of rotation, the drivers and slots are located in the plane of the turntable or perpendicular to it. Preferably, the slots are arranged parallel to the plane, radially spaced from the axis of rotation, and in two extreme positions of the turntable, particularly in a first and a second position, are essentially tangential to the turntable, i.e., in these extreme positions, they form a right angle with the radius vector of the turntable. Between the two extreme positions, the angle decreases, in particular from 90°, until it reaches 0° and then increases again until it reaches 90° once more.

[0020] In particular, it can be provided that a radius vector is defined in the plane of the turntable, extending from the axis of rotation to the pin, and that in a first position of the turntable the pin is received in the slot of the driver of the first switching element such that the slot forms a 90° angle with the radius vector, and in a second position of the turntable it is received in the slot of the first switching element such that the slot again forms a 90° angle with the radius vector, the second position corresponding to a 180° rotation of the turntable from the first position. The slot is guided by the pin in such a way that it initially engages the pin from one side and, after a 180° rotation of the turntable, from the other, opposite side.

[0021] In a further development, it is then provided that the pin in the first position and / or in the second position of the rotary disc is received in the slot of the driver of the second switching element in such a way that the slot of the driver of the second switching element also encloses a 90° angle with the radius vector.

[0022] It is preferably provided that in the first position and / or the second position, the pin is transferred from the driver of the first switching element to the driver of the second switching element. The first or second switching element is thereby moved from a first to a second switching position, for example, to open and close one or two gear elements. For this purpose, the first or second switching element assumes an engaged or locked state in the first or second position through the interaction of the slot and pin or rotary disc. In a particularly preferred embodiment, it is provided that in this engaged or actuated state, the switching element is held essentially force-free by the interaction of the slot and pin or rotary disc. This can be achieved, in particular, by the right angle or 90° angle between the radius vector and the slot.For movements occurring in the thrust direction, i.e., those transmitted from the slot to the pin, the respective driver would move in the direction of the radius vector, i.e., parallel to the radius vector. However, this prevents any rotational movement of the turntable. Since the turntable is secured against lateral movement, the pin is also secured against movement along the radius vector. Therefore, the pin cannot be displaced. Due to the interaction of the pin and driver via the slot, the switching element itself cannot be displaced and is also secured against unintentional adjustments, holding it force-free in this actuated position. The same applies to the actuated gear element.

[0023] Alternatively or additionally, the turntable can be provided with a locking cam. This locking cam is preferably arranged in the region of the turntable's axis of rotation. For example, a contour can be arranged axially on the turntable such that it rotates together with the turntable around its axis of rotation. This contour can have a cam section that forms the locking cam. In a further development, this cam section can be semicircular. The entire contour can then also be semicircular, with the axis of rotation preferably lying in the middle of the semicircle.

[0024] To interact with the locking cam, the first switching element and / or the second switching element have a locking recess, preferably on an end face of their driver. This locking recess is adapted to the locking cam in such a way that the locking cam engages positively in the locking recess of the respective switching element to prevent the switching element from moving, at least within certain angular ranges of the rotary disk.

[0025] For this purpose, it is provided that at least the locking cam engages positively in the locking recess of the second switching element when the pin of the rotary disc is received in the slot of the driver of the first switching element, and secures the second switching element against displacement when the slot of the second switching element is free of pins. In other words, the second switching element is secured against displacement, i.e., against movement, by the interaction of the locking cam with its locking recess when the pin engages in the slot of the first switching element for actuation.

[0026] Alternatively or additionally, it can be provided that at least the locking cam engages positively in the locking recess of the first switching element when the pin of the rotary disk is received in the slot of the driver of the second switching element, and secures the first switching element against displacement when the slot of the first switching element is free of pins. In other words, the first switching element is secured against displacement, i.e., against movement, by the interaction of the locking cam with its locking recess when the pin engages in the slot of the second switching element to actuate it. Preferably, these two positive locking mechanisms of the first and second switching elements are combined in such a way that whenever one switching element is actuated by the pin, the other switching element is protected against unintentional movement by the interaction of the locking cam and locking recess.

[0027] Although the terms cam and recess are used in this context, their geometric inverses are also explicitly included, meaning that alternatively, a cam-shaped element on the drive and a point of engagement in the area of ​​the turntable's axis of rotation are also present. Here, cam and recess should be understood primarily in a functional sense.

[0028] To enable simultaneous actuation of the first and second switching elements, a further development may provide the rotary disc with a second pin for engaging in a slot of at least one of the switching elements. This can be advantageous whenever simultaneous actuation of two gear elements is desired. In this case, locking elements such as recesses and cams can be omitted, since either the switching elements are locked without force in the first or second position, or both switching elements are actuated simultaneously.

[0029] Examples of the invention are shown in the following figures. They show: Fig. 1: A top view of a gearbox with two switching elements in first end positions, Fig. 2: the gearbox Fig. 1 with the first switching element in its second end position, Fig. 3: the gearbox Fig. 2 with the second switching element in its second end position, Fig. 4: an alternative transmission with a single shift shaft for two shift elements, and Fig. 5: an alternative gearbox with a shift shaft and a rotating disc turned by 90°.

[0030] Fig. Figure 1 shows a top view of a transmission 1 according to the invention, comprising a first switching element 3 and a second switching element 4, arranged to the left and right of a rotary disk 5. This is the opposite configuration of a transmission 1, in which the switching elements 3 and 4 are arranged antagonistically with respect to the rotary disk 5. The two switching elements 3 and 4 are each axially movable on a left switching shaft 2 and a right switching shaft 2', respectively. The switching shafts 2 and 2' are positioned parallel to each other and extend in a longitudinal direction X. The axial direction corresponds to this longitudinal direction X.

[0031] The turntable 5 is axially fixed and rotatable about an axis of rotation 9. A pin 6 is located on a radial outer surface of the turntable 5. A radius vector r points from the axis of rotation 9 to the pin 6, which is located at a distance of magnitude r from the axis of rotation 9. The pin 6 moves with the rotation of the turntable 5 and can be received and released by a slot 7. For this purpose, the pin 6 has a diameter that is matched to the width of the slot 7 such that play between the slot 7 and the pin 6 is reduced or eliminated. The pin 6 can only be displaced in the Y direction within the slot 7. The Y direction is perpendicular to the longitudinal direction X.

[0032] Drivers 8 are arranged on the switching elements 3, 4 to form the slots 7. The drivers 8 extend from the switching shafts 2, 2' in direction Y away from the switching elements 3, 4 towards the rotary disk 5 and lie in a plane parallel to the rotary disk 5. The slots 7 are open towards the rotary disk 5 to receive the pin.

[0033] In Fig. In position 1, the rotary disk 5, or rather the pin 6, is in a first position P1. The radius vector r forms an angle of 90° with the slot 7 of the first switching element 3. The first switching element 3 is located on the switching shaft 2 exclusively in the longitudinal direction X, i.e., in the first position P1, only in a direction parallel to the radius vector r. If the rotary disk 5 is not driven by rotation, a force acting on the rotary disk 5 from the direction of the first switching element 3 cannot cause any change in the position of the pin 6 from the first position P1, since at least one force component in a direction perpendicular to the radius vector r is necessary for this. However, this is not possible due to the system design, originating from the first switching element 3. Therefore, in this first position P1, the rotary disk 5, or rather the first switching element 3, is locked against unwanted adjustments caused by thrust movements into the gearbox 1.

[0034] If the rotary disk 5 is driven counterclockwise from the first position P1 by a drive device (not shown), which may, for example, include an electric motor and a rotor shaft, the pin 6 is initially moved primarily in the Y direction. This movement also includes a small component in the longitudinal X direction, so that the interaction of pin 6 and slot 7 moves the first switching element 3 longitudinally along the switching shaft 2 in the X direction. Due to the pivoting of pin 6 about the axis of rotation 9, the adjustment speed of the first switching element 3 initially increases with increasing adjustment angle of the rotary disk 5 from the first position P1, until it reaches a maximum at an adjustment angle of 90°. Simultaneously, the force acting on the first switching element 3 in the longitudinal X direction decreases from a maximum value and reaches a minimum at the adjustment angle of 90°.After passing through the 90° adjustment angle, the adjustment speed decreases again and the force in the longitudinal direction X increases again.

[0035] During this counterclockwise movement of the rotary disk 5, starting from the first position P1, only the first switching element 3 is moved. Fig. In position 1, the first switching element 3 is in its first end position. This first switching element 3 has a fork 20. With this fork 20, the first switching element 3 engages in a receptacle 21 of an axially movable first gear element 12. This first gear element 12 is loosely mounted on a gear shaft 22. When the rotary disk 5 is in the first position P1 and simultaneously the first switching element 3 is in its first end position, the first gear element 12 is engaged with a second gear element 13 that is axially fixed on the gear shaft 22. The first gear element 12 can, for example, be a synchronizing device, and the second gear element 13 can be a loose gear, which, in this first position P1 at the first end position of the first switching element 3, is rotationally fixed to the gear shaft 22 by the first gear element 12.The rotation of the rotary disk 5 axially displaces the first shifting element 3 and, via the fork 20, also the first transmission element 12, i.e., in the longitudinal direction X. The first shifting element 3 is moved out of its initial end position. The first transmission element 12 is disengaged from the second transmission element 13, thus engaging, for example, a first gear implemented via this mechanism. Advantageously, in the transmission 1 shown here, the first shifting element 3 follows a non-linear characteristic curve, so that engagement occurs at a lower speed with a greater force, and the first transmission element 12 is subsequently moved at a higher speed with a lower force towards the adjustment angle of 90° of the rotary disk 5.

[0036] While the first gear element 12 is moved by the first switching element 3, the second switching element 4 remains in its first end position as shown in Fig. Figure 1 shows the second switching element 4, which also has a driver 8 with a slot 7. In its Fig. In the first end position shown in Figure 1, the slot 7 of the second switching element 4 lies in the longitudinal direction X, i.e., in the axial direction of the switching shafts 2, 2', viewed on the opposite side of the axis of rotation 9 from the driver 8 of the first switching element 3. During the rotation of the rotary disk 5 from the first position P1, the pin 6 is engaged with the slot 7 of the first switching element 3 and disengaged from the slot 7 of the second switching element 4. The second switching element 4 also has a fork 30 with which it engages in a receptacle 31 of another axially movable first gear element 16 on a second gear shaft 32. The first gear element 16 is disengaged here from an axially fixed second gear element 15 on the second gear shaft 32.

[0037] Since there is no pin 6 in the slot 7 of the second switching element 4 in this end position, the second switching element cannot be locked without force via the pin 6. To prevent unintended adjustments of the second switching element 4, especially those that would change the position of the slot 7 in such a way that the pin 6 could no longer engage in the slot 7, the second switching element 4 is locked by the interaction of two locking elements. The driver 8 of the second switching element 4 has a locking recess 11 that is positively coupled to a locking cam 10 of the rotary disk 5. The locking cam 10 is a semicircular feature in the region of the axis of rotation 9. Its radial outer surface slides into the locking recess 11 of the driver 8.The locking recess 11 is formed by a quarter-circle recess on one side of the driver 8 and is provided at the same end as the opening of the slot 7. In the in . Fig. In the first end position of the second switching element 4 shown in Figure 1, the locking recess 11 is located on the side of the driver 8 facing the axis of rotation 9. The shape and size of the locking cam 10 and the locking recess 11 are coordinated so that the locking cam 10 only disengages from the locking recess 11 after a 180° rotation of the rotary disk 5 from the first position P1.

[0038] After a 180° counterclockwise rotation of the rotary disk 5 from position P1, the pin 6 engages with the slot 7 of the second switching element 4. The rotary disk 5, or rather the pin 6, then assumes a second position P2, in which the pin 6 is received in both the slot 7 of the first switching element 3 and the slot 7 of the second switching element 4, and both switching elements 3 and 4 are locked against adjustment by shear forces due to the perpendicular orientation of the slots 7 to the now rotated radius vector r. This second position P2 is in Fig. 2 shown.

[0039] In the second position P2, the locking cam 10 is now disengaged from the locking recess 11 of both the first and second switching elements 3 and 4. As the first switching element 3 moves into the second position P2, it engages the first transmission element 12, causing it to engage with a second, axially fixed transmission element 14. This allows the second transmission element 14 to be synchronized with the transmission shaft 22, enabling, for example, the engagement of a second gear. Since engaging the second gear may require a greater force, it is advantageous that in the region of the second position P2, maximum force combined with minimal actuation travel in the longitudinal direction X is transmitted by the rotary disk 5 or the pin 6.

[0040] If the rotary disk 5 is now rotated clockwise, the first switching element 3 moves from its position in accordance with the described non-linear characteristic curve. Fig. 2 shown second end position back into the in Fig. In the end position shown in Figure 1, the first and second gear elements 12 and 14 disengage, and the first and second gear elements 12 and 13 re-engage, while the first gear element 16, which is coupled to the second switching element 4, remains disengaged from the second gear element 15. The second switching element 4 is then locked against axial displacement in the longitudinal direction X by locking cam 10 and locking recess 11.

[0041] Starting from second position P2 as in Fig. As shown in Figure 2, during a further counterclockwise rotation of the rotary disk 5, the second switching element 4 is axially displaced in the longitudinal direction X on the switching shaft 2'. Due to the coupling of the second switching element 4 with the first gear element 16 on the second gear shaft 32, the first gear element 16 is correspondingly displaced axially in the longitudinal direction X according to the described nonlinear characteristic curve and engages with the second gear element 15. This state is shown in Fig. Figure 3 shows that the second switching element 4 is now in its second end position, while the rotary disc 5, or the pin 6, is again in the first position P1.

[0042] By coupling the first gear element 16 with the second gear element 15, another gear can be engaged, but preferably a differential can be bypassed. When the first gear element 16 engages the second gear element 15, the pin 6 returns to its first position P1. In this case, the second shift element 4 is locked without force. Further shifting operations are now only possible by reversing the rotation of the rotary disk 5. By means of locking elements (not shown), for example on the back of the rotary disk 5, rotations of the rotary disk 5 beyond 360° can be prevented. The first shift element 3 remains in its second end position, as already described in [reference missing]. Fig. 2 shown. If the rotary disc 5 is rotated 360° beyond this point, it would not be possible for the pin 6 to engage again in the slot 7 of the first switching element 3; a clockwise rotation is always necessary for this.

[0043] As previously described for the second switching element 4, during the movement of the second switching element 4 from the first end position to the second end position, the first switching element 3 is locked in the second end position by the interaction of a locking recess 11 on the driver 8 of the first switching element 3 with the locking cam 10 on the axis of rotation.

[0044] For the two movement sequences of the first switching element 3 from its first end position into Fig. 1 into its second final position in Fig. 2 and the second switching element 4 from its first end position in Fig. 2 into its second final position in Fig. 3. A locking mechanism for the actuated switching element 3 or 4 in intermediate positions is not provided. This is only possible for switching elements 4 and 3 held in their respective end positions by the locking cam 10 and the locking recess 11. However, if, for example, decoupling between the two end positions of the first switching element 3 is to be maintained as a stable state, a corresponding locking mechanism must be provided. This can be achieved by detents (not shown) between the two end positions of the switching element 3. These detents can be provided between the switching element 3 and a housing (not shown). Alternatively or additionally, detents between the first gear element 12 and a housing are also possible. The same applies to the second switching element 4 and the first gear element 16 associated with it. Such detents can also be provided additionally in the two end positions of the switching elements 3 and 4.Fixed stops for the switching elements 3, 4 on the switching shafts 2, 2' are also possible here. This is particularly useful for the second switching element 4, since no engagement of the first gear element 16 with a second gear element is provided here.

[0045] In the embodiments of the Fig. In figures 1 to 3, the two switching elements 3 and 4 are arranged on opposing switching shafts 2, 2'. Alternatively, the switching shafts can also be arranged longitudinally one behind the other. In this case, separation of the switching shafts is not necessary, so that a single switching shaft 42 can be used for two switching elements 43 and 44 as in Fig. 4 can be used as shown. The same applies accordingly to the first gear elements 52 and 56 and the second gear elements 53, 54 and 55, which are all arranged on a single gear shaft 63.

[0046] In the Fig. In positions 1 to 4, the axis of rotation 9 or 49 of the turntable 5 or 45 is located perpendicular to the longitudinal direction X and the direction Y. The electric motor required for driving the turntable can then be located below the turntable 5 or 45 and is connected to the Fig. 1 to 4 not shown. Alternatively, a construction is also possible in which the axis of rotation 79 lies in the X / Y plane. This example is based on the embodiment of Fig. 4 in Fig. 5 shown.

[0047] In Fig.Figure 5 also shows that the rotary disk 75 need not be a point-symmetric circular disk. In particular, it can also be a lever-shaped construction with the axis of rotation 79 at one end and a pin 76 at the other, since the only relevant factor is the circular movement of the pin 76 around the axis of rotation 79 with the corresponding engagement of the pin 76 in slots 77 of the drivers 78 of the switching elements 73, 74. In the embodiment shown here, the pin 76 extends in the Y direction, which necessitates an extension of the slots 77 in the longitudinal X direction. The pin 76 itself lies in the plane of the paper only in the respective first and second positions, which correspond to the first and second end positions of the first and second switching elements 73, 74. As shown here, the rotary disk 75 can be driven directly by the rotor shaft 81 of an electric motor 80.Even with this setup, a non-linear characteristic curve can be realized for both switching elements 73, 74 with a simple gearbox design of the gearbox 71.

[0048] In all described transmissions 1, 41, 71, nonlinear characteristics are achieved for shifting the first transmission elements 12, 16, 52, 56, 82, 86, thus meeting the requirements for higher forces for engaging gears while simultaneously achieving greater shift dynamics. For engaging the second transmission elements 15, 55, 85, which are preferably used to bridge a differential, the overall longer shift travels of the second shifting element 4, 44, 74 can be tolerated. Reference symbol list 1 gearbox 2 shift shaft 3 first switching element 4 second switching element 5 turntable 6 pens 7 slots 8 drivers 9 axis of rotation 10 locking cams 11 Locking recess 12, 16 first gear element 13, 14, 15 second gear element 20 Fork 21 recording 22 first transmission shaft 30 Fork 31 recording 32 second transmission shaft 41 gearboxes 42 Shift shaft 43 first switching element 44 second switching element 52, 56 first gear element 53, 54, 55 second gear element 63 Gear shaft 71 gearboxes 73 first switching element 74 second switching element 75 turntable 76 pens 77 slots 78 drivers 80 electric motor 81 Rotor shaft 82, 86 first gear element 83, 84, 85 second gear element P1 first position P2 second position r radius vector

Claims

[1] Gearbox (1) comprising at least two gear elements (12, 13, 14, 15, 16), wherein a first gear element (12, 16) is arranged to be axially movable relative to a second gear element (13, 14, 15), further comprising at least one switching shaft (2) and at least one axially displaceable switching element (3, 4) for axially moving the first transmission element (12, 16), a drive element driving the at least one switching element (3,4) and at least two coupling elements provided between the drive element and the switching element (3,4), wherein a first coupling element is designed as a pin (6) and a second coupling element as a slot (7) and the at least one switching element (3,4) is set into an axial movement by a movement of the pin (6) in the slot (7), wherein the at least one shift shaft (2) is arranged axially fixed to the second transmission element (13, 14, 15), the at least one switching element (3, 4) is axially displaced on or along the switching shaft (2) by the drive element in such a way that the axial movement of the at least one switching element (3, 4) follows a non-linear characteristic curve, and that the first transmission element (12, 16) is moved by the at least one switching element (3, 4) in such a way that a coupling of the first transmission element (12, 16) with the second transmission element (13, 14, 15) is selectively removed or established, the at least one switching element (3, 4) has a driver (8) fixedly arranged on the switching element (3, 4) and the slot (7) is formed in or on the driver (8), characterized by , that the drive element is designed as a rotary disk (5), two switching elements (3, 4) are provided adjacent in a linear direction or on opposite sides of the rotary disk (5) and the drivers (8) of both switching elements (3, 4) are arranged such that the slots (7) are formed in a plane parallel or perpendicular to the axis of rotation (9) of the rotary disk (5) for the engagement of the at least one pin (6). [2] Gearbox (1) comprising at least two gear elements (12, 13, 14, 15, 16), wherein a first gear element (12, 16) is arranged to be axially movable relative to a second gear element (13, 14, 15), further comprising at least one switching shaft (2) and at least one axially displaceable switching element (3, 4) for axially moving the first transmission element (12, 16), a drive element driving the at least one switching element (3,4) and at least two coupling elements provided between the drive element and the switching element (3,4), wherein a first coupling element is designed as a pin (6) and a second coupling element as a slot (7) and the at least one switching element (3,4) is set into an axial movement by a movement of the pin (6) in the slot (7), wherein the at least one shift shaft (2) is arranged axially fixed to the second transmission element (13, 14, 15), the at least one switching element (3, 4) is axially displaced on or along the switching shaft (2) by the drive element in such a way that the axial movement of the at least one switching element (3, 4) follows a non-linear characteristic curve, and that the first transmission element (12, 16) is moved by the at least one switching element (3, 4) in such a way that a coupling of the first transmission element (12, 16) with the second transmission element (13, 14, 15) is selectively removed or established, characterized by , that the drive element is designed as a rotary disk (5), the at least one pin (6) is arranged on or at the turntable (5), and by rotating the turntable (5) about an axis of rotation (9) the pin (6) comes into and out of engagement with the slot (7) on the one hand and on the other hand, it is moved within the slot (7) in such a way that an axial displacement of the switching element (3, 4) occurs. [3] Gearbox (1) according to claim 2, characterized by , that the at least one switching element (3, 4) has a driver (8) fixedly arranged on the switching element (3, 4) and the slot (7) is formed in or on the driver (8). [4] Gearbox (1) according to claim 3, characterized by , that two switching elements (3, 4) are provided adjacent in a linear direction or on opposite sides of the rotary disk (5) and the drivers (8) of both switching elements (3, 4) are arranged such that the slots (7) are formed in a plane parallel or perpendicular to the axis of rotation (9) of the rotary disk (5) for the engagement of the at least one pin (6). [5] Gearbox (1) according to one of claims 1 or 4, characterized by , that the slots (7) are arranged perpendicular to the axis of rotation (9) and parallel to the plane of the turntable (5), the slots (7) are radially spaced from the axis of rotation (9) and in two extreme positions of the turntable (5) are essentially tangential to the turntable (5). [6] Gearbox (1) according to claim 5, characterized by , that a radius vector (r) is defined in the plane of the turntable (5), this radius vector (r) runs from the axis of rotation (9) to the pin (6), and the pin (6) - in a first position (P1) of the rotary disk (5) is received in the slot (7) of the driver (8) of the first switching element (3) such that the slot (7) encloses a 90° angle with the radius vector (r), and - in a second position (P2) of the rotary disk (5) is received in the slot (7) of the first switching element (3) such that the slot (7) encloses a 90° angle with the radius vector (r), wherein - the second position (P2) corresponds to a 180° rotation of the turntable (5) starting from the first position (P1). [7] Gearbox (1) according to claim 6, characterized by , that the pin (6) in the first position (P1) and / or in the second position (P2) of the rotary disk (5) is received in the slot (7) of the driver (8) of the second switching element (4) such that the slot (7) of the driver (8) of the second switching element (4) also encloses a 90° angle with the radius vector (r). [8] Gearbox (1) according to one of claims 6 or 7, characterized by , that the first switching element (3) and / or the second switching element (4) assume an inserted or actuated state in the first position (P1) and / or the second position (P2) and in this inserted or actuated state the switching element (3, 4) is held essentially without force by the interaction of slot (7) and pin (6) or rotary disc (5). [9] Gearbox (1) according to any one of claims 4 to 8, characterized by , that the rotary disk (5) has a locking cam (10), preferably in the area of ​​the axis of rotation (9), the first switching element (3) and / or the second switching element (4) has a locking recess (11) preferably on an end face of a driver (8), so that the locking cam (10) engages positively in the locking recess (11) of the second switching element (4) when the pin (6) is received in the slot (7) of the driver (8) of the first switching element (3) and secures the second switching element (4) against displacement when the slot (7) of the second switching element (4) is pin-free and / or the locking cam (10) engages positively in the locking recess (11) of the first switching element (3) when the pin (6) is received in the slot (7) of the driver (8) of the second switching element (4) and secures the first switching element (3) against displacement when the slot (7) of the first switching element (3) is free of pins. [10] Gearbox (1) according to any one of claims 4 to 9, characterized by , that the rotary disk (5) has a second pin for engaging in a slot (7) of at least one of the switching elements (3, 4).

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