DE102015214534A1 - Claw transmission, in particular for a motor vehicle - Google Patents

Abstract

The invention relates to a jaw gear (1), in particular for a motor vehicle, with a drive shaft (2), with an output shaft (3), with at least one on a shaft (2, 3, 9) of the jaw gear (1) relative to the one Shaft (2, 3, 9) arranged displaceably, with the one shaft (2, 3, 9) rotatable and at least one shift gate (13a) having switching element (12a), by means of which by shifting the switching element (12a) along one shaft ( 2, 3, 9) a coupling of the output shaft (3) with the drive shaft (2) via at least one gear stage (Z1) of the jaw gear (1) is effected, with at least one actuator (14a) and at least one pin element (15a), which by means of the actuator (14a) in translation with the shift gate (13a) is translationally movable, whereby a displacement of the switching element (12a) relative to the one shaft (2, 3, 9) is effected.

Description

The invention relates to a jaw gear, in particular for a motor vehicle.

Gears for motor vehicles are already well known from the general state of the art and in particular from the production of standard vehicles. A gear is a machine element by means of which movement quantities can be changed. For example, torques which are provided by a drive element, in particular in the form of an internal combustion engine, are converted in terms of amount by means of such a transmission. Furthermore, alternatively or additionally, a speed conversion can take place, so that a particularly advantageous operation of the drive element can be realized.

In conventional stage transmissions for vehicles, the gears of all stages, which are also referred to as gears, constantly engaged. However, only at the torque transmitting and thus active stage both gears are rotatably connected to the Anbeziehungsweise output shaft. At the other, inactive stages at least one wheel rotates freely on the shaft. Such a gear, which is also referred to as a wheel, is arranged on a shaft and is rotatable relative to the shaft, also referred to as idler gear or impeller. The connection of the loose wheels with the shaft is usually carried out by a rotatably connected to the shaft sleeve with claws, wherein the sleeve is axially displaceable on the shaft and engages in recesses or jaws in the idler gear. For comfort reasons, a synchronization is usually used in vehicle transmissions, which causes the synchronization of sleeve and idler gear, wherein the positive connection of the sleeve and gear is done by the jaws. The sleeve is also referred to as a sliding sleeve or sliding sleeve.

For motorcycles gearboxes are usually unsynchronized for reasons of space and because of higher possible switching speed, the comfort disadvantage is accepted. Instead of sliding sleeves, the gears can be performed with claws and axially displaceable in spur gears, so that a sliding gear is formed.

To change the stages or gears the shift sleeves or the sliding wheels are shifted axially by shift forks, which engage in circumferential grooves in the sleeves, and so solved the non-rotatable connection of a gear and another operates. The axial movement of the shift forks is effected in a passenger car by a corresponding linkage. In motorcycle gearboxes, the shift forks are moved by a shift drum for reasons of space or because of foot control. The shift drum has corresponding guide grooves for pins on the shift forks. Upon rotation of the shift drum, the shift forks and shift sleeves move. The stepwise rotation of the shift drum is achieved by a complex switching mechanism, which is actuated by a foot pedal.

Usually, gearboxes for passenger cars and trucks are automated by the shift linkage is moved by electric or hydraulic actuators. In automated motorcycle transmissions, the shift drum is rotated by the actuators. Hydraulic actuators are supplied with the required operating pressure with engine oil pressure or a separate hydraulic unit. Electric actuators are usually designed as electric motors with countershaft transmission. Both types of actuation are relatively expensive, take up a lot of space and can be difficult to integrate into the drive, especially in a motorcycle. Automatic transmissions with planetary gear sets and hydraulic torque converters lead to higher fuel consumption due to the constantly required oil pump and the associated power loss.

Object of the present invention is therefore to provide a particularly cost-effective and space-saving jaw gear, which also can be automated in a particularly simple manner.

This object is achieved by a jaw gear with the features of claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

The jaw gear according to the invention, in particular for a motor vehicle such as a motorcycle or a passenger car, comprises a drive shaft, an output shaft and at least one switching element. The switching element is arranged on a shaft of the doggear and thereby displaceable relative to the one shaft, that is translationally movable. Furthermore, the switching element with the one shaft is rotatable. This means, for example, that the switching element is rotatably connected to the shaft, so that the switching element is driven by the shaft and rotates with the shaft about a common axis of rotation. In addition, the switching element has at least one shift gate. By means of the switching element, a coupling of the output shaft with the drive shaft via at least one gear stage of the doggearing can be effected by the switching element is displaced along the one shaft. In other words, the switching element serves to cause a coupling of the drive shaft to the output shaft. In This coupled state, the output shaft of the drive shaft via the gear stage is driven. For example, torques which are provided by a drive unit, such as an internal combustion engine, are introduced into the claw transmission and directed to the gear stage via the drive shaft. The torques are transmitted via the gear stage to the output shaft. The claw transmission can provide, for example, torques via the output shaft, by means of which, for example, at least one wheel of the motor vehicle can be driven.

The jaw gear further comprises at least one actuator and at least one pin element, which is translationally movable by means of the actuator into engagement with the shift gate, whereby a displacement of the switching element relative to the one shaft can be effected. The pin element is also referred to as a pin or bolt and is movable by means of the actuator into engagement with the shift gate. The shift gate is designed, for example, such that when the shift element is rotated about the axis of rotation and the pin element is moved by means of the actuator into engagement with the shift gate, by the engagement of the pin element in the shift gate and by the rotation of the switching element and thus the shift gate order the axis of rotation of the switching element is displaced, along the shaft or relative to the one shaft in the axial direction thereof, whereby the coupling of the drive shaft with the output shaft or vice versa is effected.

The jaw gear can be kept particularly simple in terms of its structure, so that very low cost and a particularly low weight of the doggear can be realized. Furthermore, the space requirement of the jaw gear can be kept particularly low. In addition, the output shaft can be coupled to the drive shaft as needed and in a simple manner, so that a particularly cost-effective torque and / or speed conversion can be realized by means of the claw mechanism according to the invention. By means of the actuator, moreover, a particularly simple automation of the claw transmission can be realized, so that the claw transmission can be designed as an automated claw transmission, in particular stepped claw transmission.

In order to keep the space requirements, in particular the axial space requirement, of the jaw gear particularly low, it is provided in an advantageous embodiment of the invention that the shift gate is formed in an outer peripheral side surface of the switching element, wherein the pin member by means of the actuator in the radial direction of a shaft translationally is movable in the shift gate, whereby the switching element along the one shaft due to rotation of the one shaft and the switching element is displaceable. The pin member is thus moved by means of the actuator not in the axial direction of a shaft, but in the radial direction of a shaft to move the pin member into engagement with the shift gate. As a result, the space requirement can be kept very low.

In a further embodiment of the invention, the shift gate in the circumferential direction of a shaft and the switching element on a different course from a circular course. In this way, a particularly simple, inexpensive and space-saving displacement of the switching element along the one shaft can be effected by the pin member is moved by means of the actuator in the shift gate and the switching element is rotated about the shaft. As a result, for example, the switching gate limiting wall portions of the switching element in support system with the engaging in the shift gate pin element, which due to the corresponding course or the corresponding geometry of the shift gate, the rotation of the switching element and thus the shift gate in a shift, ie translational movement of the switching element along the a wave is converted. This allows a particularly space-saving operation of the switching element can be realized.

It has proven particularly advantageous if the shift gate has a helical course, at least in a partial area. Under a helix, which is also referred to as a screw, helix, cylindrical spiral or helix, is a curve to understand, which winds, for example, at least substantially constant pitch around an at least substantially cylindrical, outer peripheral side surface of the switching element. In this case, at least a portion of the shift gate is at least formed as part of such a helix, so that at least the portion of the shift gate is helical. In this way, a particularly advantageous and in particular smooth and rapid displacement of the switching element can be effected by the switching element is rotated about the shaft and engages the pin member in the shift gate.

It is also advantageous if the shift gate runs obliquely to the axial direction of the one shaft at least in a partial area. As a result, rotational movements of the switching element and thus the shift gate can be particularly well converted into a translational movement, that is displacement of the switching element along the one shaft when the pin element engages in the shift gate.

In order to avoid unwanted and in particular uncontrolled movements of the switching element in a cost and space-saving manner, at least one in at least one position of the switching element form-fitting with the switching element and a shaft cooperating detent element is provided by means of which the switching element as a result of the respective positive cooperation against a relative displacement to secure a wave or is secured.

In a further embodiment of the invention, at least one on the one shaft or on another shaft of the doggear relative to the one or other shaft slidably disposed mitdrehwellen with one or the other second switching element is provided by means of which by moving the second switching element along the one or the other shaft, the coupling of the output shaft with the drive shaft via the gear stage is effected, wherein the second switching element is displaceable by moving the first switching element. In other words, it is provided in this embodiment, to move the first switching element for moving the second switching element. In this way, a particularly advantageous operability of the doggear can be realized.

In a further embodiment of the invention, it has been found to be advantageous if a locking device is provided, by means of which the second switching element is positively connected to one or the other shaft and thereby secured against relative displacement to one or the other shaft. The locking device makes it possible to ensure a particularly advantageous operation and in particular a particularly advantageous switchability of the doggear. If the output shaft is coupled to the drive shaft, then, for example, a gear of the doggear gear is engaged. By means of the locking device, it is possible to avoid undesired or unintentional engagement of the gear, that is to say unintentional or undesired coupling of the output shaft to the drive shaft via the gear stage belonging to the shifting elements. This is particularly advantageous when the jaw gear has at least one other gear, which is inserted. By means of the locking device, it is then possible to avoid inserting the other, first gear, since the second switching element can not be moved relative to one or the other shaft. This means that in the jaw gear can be avoided in a particularly simple and cost-effective manner that several courses of the jaw gear are inserted simultaneously or are. As a result, damage to transmission components can be avoided.

For example, the locking device comprises at least one blocking element, which is displaceable in a direction obliquely or perpendicular to the axial direction of one or the other shaft between at least one locking position and at least one release position relative to one or the other shaft. In the blocking position, the second switching element is under positive engagement of the locking element with one or the other shaft and the second switching element against a relative displacement to one or the other shaft to secure or secured, wherein the blocking element, the relative displacement between the second switching element and one or the other Shaft releases in the release position. As a result, a particularly simple, cost-effective and simultaneous effective securing of the second switching element can be realized. In addition, the space requirement of the doggear can be kept in a very small frame.

It is also advantageous if the blocking element is supported on one or the other shaft via at least one tensioned in the release position spring element by means of which the locking element is acted upon at least in the release position with a spring force, by means of which the locking element from the release position to the blocking position is movable. In this way, a particularly simple and cost-effective provision of the locking element from the release position can be realized in the locked position. Preferably, it is provided that the spring element acts on the blocking element in the blocking position with a spring force, for example, to keep the blocking element securely in the blocking position.

Further, it has been found to be advantageous if in one or the other shaft on which the second switching element is arranged, a slider is received, which between at least one securing the locking element against displacement from the locked position to the release position securing position and at least one Displacement of the locking element from the blocking position in the release position releasing release position relative to one or the other shaft is displaceable. In this way can be realized in a particularly simple and cost-effective manner needs-based securing and releasing the locking element and thus the second switching element. At the same time, the fact that the slider is at least partially accommodated in one or the other shaft, the space requirement of the doggear are kept particularly low. Under one wave or another, the wave is to be understood on which the second switching element is slidably received.

The slider has, for example, at least a first length range and a second length range adjoining the first length range. By means of the first length region, the blocking element is secured or secured by supporting it on the first length region, for example against displacement from the blocking position into the release position. The second longitudinal region has a recess which can be arranged in overlap with the blocking element, in which the blocking element can be received or received in the release position. In other words, is the first length range and not about the second length range with the recess in registration with the locking element, the locking element can not be moved from the locked position to the release position, since the blocking element at the first length range or one in the first Length range arranged, outer peripheral side surface of the slider is supported, in particular in the radial direction of one or the other shaft.

If the slider is displaced relative to one or the other shaft, in particular in the axial direction of the one or the other shaft, so that the recess comes into coincidence with the blocking element, the blocking element can at least partially pushed into the recess of the slider and thereby from the Lock position to be moved to the release position. It is provided, for example, that the first length region is in the securing position in registration with the blocking element, wherein the recess is arranged in the release position in register with the blocking element.

Furthermore, at least one further, third switching element can be provided, by means of which a coupling of the output shaft with the drive shaft via a further gear stage of the doggearing is effected by moving the further switching element, wherein the slider is coupled to the further switching element and slidable via the further switching element. In other words, the slider is mitverschiebbar example with the other switching element, so that no additional actuators or actuators for moving the slider are required and provided.

In a further advantageous embodiment, at least one spring device is provided, via which the second switching element of the first switching element is displaceable, wherein the spring means is elastically deformable by shifting the first switching element, when the second switching element by means of the locking device against a relative displacement to one or the other shaft is secured. In other words, the spring device allows a displacement of the first switching element, while the second switching element is secured by means of the locking device and thus can not be moved. As a result, damage to the shift gate and thus the first switching element and to the actuator can be avoided, at the same time an undesirable displacement of the second switching element and thus a simultaneous insertion of multiple gears can be avoided.

In order to keep the space requirement particularly low, it is preferably provided that the first switching element and the second switching element are arranged displaceably on the same shaft. The shaft on which the first switching element is arranged, for example, the drive shaft, the output shaft or in addition to the drive shaft and the output shaft provided switching shaft of the doggear. Further, preferably, the shaft on which the second switching element is arranged, the drive shaft, the output shaft or in addition to the output shaft and the drive shaft provided switching shaft of the doggear. In order to keep the structure of the doggear particularly simple, the switching shaft is preferably driven by the drive shaft or the output shaft.

In order to keep the space requirement of the jaw gear particularly low and to realize a particularly fast and efficient movement of the pin member, it is provided in a further embodiment that the actuator is designed as an electrical actuator.

The invention also includes a vehicle, in particular a motor vehicle, with a claw transmission according to the invention, in particular stepped claw transmission. Advantages and advantageous embodiments of the jaw gear according to the invention are to be regarded as advantages and advantageous embodiments of the vehicle according to the invention and vice versa.

Further details of the invention will become apparent from the following description of preferred embodiments with the accompanying drawings. Showing:

1 a schematic side view of a doggear according to a first embodiment of a motor vehicle, with a plurality of insertable gears, wherein shift gates and in the shift gates by means of respective actuators movable pin elements are provided for engaging and disengaging the gears;

2 a sectional view of a schematic sectional view of the doggear according to the first embodiment;

3 a detail of another schematic sectional view of the doggear according to the first embodiment;

4 a detail of another schematic sectional view of the doggear according to the first embodiment; and

5 a fragmentary sectional view of the doggear according to a second embodiment.

In the figures, identical or functionally identical elements are provided with the same reference numerals.

In 1 is in a schematic and partially sectioned side view as a whole with 1 designated claw gear, in particular stepped claw transmission, according to a first embodiment of a vehicle, in particular a motor vehicle shown. The claw transmission 1 has a drive shaft 2 and an output shaft 3 on. In the finished state of the vehicle is the claw transmission 1 For example, part of a drive train for driving the vehicle. The drive train further comprises at least one in 1 unrecognizable drive element or drive unit, which is designed for example as an internal combustion engine or electric motor. The drive element can provide torques which are applied to the drive shaft 2 transferable and thus via the drive shaft 2 in the claw transmission 1 can be introduced. By means of the claw gear 1 For example, the torques and / or rotational speeds of the drive element provided by the drive element, in particular an output shaft of the drive element, can be converted into different torques or speeds. This includes the jaw gear 1 a plurality of gears G1-6, each of which can be inserted or switched. The respective gear G1-6 each includes a gear stage Z1-6.

The respective gear stage Z1-6 in turn comprises one each on the drive shaft 2 arranged, first gear 4a -F, as well as a respective, on the output shaft 3 arranged, second gear 5a f. The respective gear 4a -F is presently designed as a loose wheel while on the drive shaft 2 relative to the drive shaft 2 around a rotation axis 6 rotatably arranged The respective idler gear is also referred to as an impeller and is in the axial direction of the drive shaft 2 secured or fixed relative to this, so that the respective idler gear is not relative to the drive shaft 2 can be moved in the axial direction. Here is the drive shaft 2 also around the axis of rotation 6 rotatable. In the present case is the respective first gear 4a -F about a bearing element 7 on the drive shaft 2 stored. The bearing element 7 is presently designed as a rolling bearing, in particular as a ball bearing.

The respective second gear 5a -F is non-rotatable with the output shaft 3 coupled and, for example, in one piece with the output shaft 3 educated. Thus, the output shaft 3 and the second gears 5a -F around a parallel to the axis of rotation 6 extending axis of rotation 8th rotatable. Here is the axis of rotation 8th from the axis of rotation 6 spaced.

Out 1 It can be seen that the first gears 4a -F and thus the second gears 5a -F differ in their diameters and numbers of teeth from each other, with the gears 4a -F in engagement with the gears 5a -F stand. Thus, it can in principle at different speeds between the drive shaft 2 and the first gears 4a -F come. Because the first gears 4a -F, however, are designed as loose wheels, the gears can 4a -F relative to the drive shaft 2 rotate.

The claw transmission 1 further comprises a switching shaft 9 , which a while of the claw gear 1 is. Also the drive shaft 2 and the output shaft 3 are waves of the claw gear 1 , The shift shaft 9 is present in addition to the drive shaft 2 and in addition to the output shaft 3 provided shaft of the doggear 1 , wherein the shift shaft 9 around a rotation axis 10 is rotatable. The shift shaft 9 is in 1 also shown in a cross-sectional view, which can be seen from the cross-sectional view that the shift shaft 9 is designed as a splined shaft.

The claw transmission 1 comprises a plurality of second switching elements in the form of second shift sleeves 11a -C, which is on the selector shaft 9 arranged and relative to the switching shaft 9 are displaceable in the axial direction. For example, the shift sleeves 11a -C non-rotatable with the selector shaft 9 connected and thus with the switching shaft 9 around the axis of rotation 10 so it also rotates. This means that the shift sleeves 11a -C from the selector shaft 9 are drivable. As will be explained in more detail below, the output shaft 3 with the drive shaft 2 via the respective gear stages Z1-6 by shifting the shift sleeves 11a -C can be coupled.

The claw transmission 1 further comprises about the axis of rotation 10 rotatable, first switching elements 12a -F, which are along the axis of rotation 10 displaceable, that is translationally movable. Here are the first switching elements 12a -F on the selector shaft 9 arranged and with the switching shaft 9 rotatably connected, so that the switching elements 12a -F with the shift shaft 9 rotatable as well as from the selector shaft 9 around the axis of rotation 10 are drivable. In other words, the switching element rotate 12a -F together with the stem 9 around the axis of rotation 10 , However, the switching elements 12a -F in the axial direction of the switching shaft 9 movable relative to this. Here are the switching elements 12a -F also sliding sleeves or sliding sleeves.

Out 1 It can also be seen that the switching elements 12a -F two shift gates each 13a and 13b exhibit. By means of the switching elements 12a -F are by moving the switching elements 12a -F displacements of the sliding sleeves 11a -C (second switching elements) effected. As will be explained in more detail below, by means of the shift sleeves 11a C respective couplings of the drive shaft 2 with the output shaft 3 via the respective gear stages Z1-6 effected. Furthermore, by means of the switching elements 12a -F by moving the switching elements 12a -F along the switching shaft 9 respective couplings of the output shaft 3 with the drive shaft 2 via the respective gear stages Z1-6 effected. The claw transmission 1 also includes actuators 14a -L and respective, corresponding pin elements 15a -L, which are also referred to as pins, pins or pins.

The pin elements 15a -L are by means of the actuators 14a -L in engagement with the respective shift gates 13a , b translationally movable, whereby respective displacements of the respective switching elements 12a -F are effected or be effected. In other words, for example, the pin element becomes 15a by means of the actuator 14a in engagement with the shift gate 13a of the switching element 12a moves translationally, and thereby becomes the switching element 12a over the selector shaft 9 around the axis of rotation 10 rotated, so the rotational movement of the switching element 12a around the axis of rotation 10 by means of the pin element 14a and the shift gate 13a of the switching element 12a in a shift of the switching element 12a along the axis of rotation 10 or along the shift shaft 9 converted relative to this, wherein in this case the switching element 12a related to the image plane of 1 for example, pushed to the right.

This is because the shift gate 13a respectively 13b does not have a straight course or an at least substantially circular course or is arranged in exactly one plane, but the respective shift gate 13a , B points in the circumferential direction of the switching shaft 9 and the respective switching element 12a -F one of a circular course different and present curved course. Further, for example, by means of the pin member 15a and the corresponding shift gate 13a and / or by means of the pin element 15b and the corresponding shift gate 13b a movement of the switching element 12a to move to the left. In this way, the respective switching elements 12a -F by means of the associated pin elements 15a -L and the associated actors 14a -L relative to the switching shaft 9 or along the axis of rotation 10 As will be explained in more detail below, the first switching elements 12a -F with the second switching elements in the form of sliding sleeves 11a C coupled or coupled, so that by moving the switching elements 12a -F displacements of the sliding sleeves 11a -C are effected or be effected.

Out 1 is particularly well recognizable that the respective shift gate 13a , am an outer peripheral side surface 36 of the respective switching element 12a F is formed, wherein the respective pin element 15a -L by means of the respective actuator 14a -L in the radial direction of the switching shaft 9 translational in the respective shift gate 13a , b is movable, whereby the respective switching element 12a -F along the switching shaft 9 due to a rotation of the switching shaft 9 and the switching element 12a -F is displaceable. For example, the shift gate runs 13a , B at least in a portion obliquely to the axial direction of the switching shaft 9 , so that the rotational movement of the respective switching element 12a -F in a translational movement along the shift shaft 9 can be converted. Furthermore, it can be provided that the respective shift gate 13a , B has a helical course at least in a partial region. In other words, the respective shift gate 13a , B, for example, helically or formed in the manner of a helix.

The respective shift gate 13a For example, b is a groove. Furthermore, the respective shift gate 13a , b in the axial direction of the switching shaft 9 and thus the respective switching element 12a F a slope, which, for example, a required axial displacement of the respective switching element 12a -F corresponds. Preferably, the respective shift gate 13a , b at the end of an ejector on. In the respective shift gate 13a , b can be the translationally movable pin (pin element 15a -L), wherein the respective pin element 15a -1 in the actuation case by the rotational movement of the respective switching element 12a F a corresponding axial movement of the switching element 12a -F causes. For example, after one revolution of the respective switching element 12a -F becomes the respective pin element 15a -L by means of the ejector ramp from the respective shift gate 13a , b pressed while present in the radial direction moves outward.

For example, the switching element 12a pushed to the left, so this is the shift sleeve 11a pushed to the left. For example, the switching switching element 12b pushed to the right, so this is the shift sleeve 11a pushed to the right. For example, the switching element 12c pushed to the left, so this is the shift sleeve 11b pushed to the left. Will the switching element 12d pushed to the right, so for example, the shift sleeve 11b pushed to the right. If, however, the switching element 12e pushed to the left, so for example, the shift sleeve 11c pushed to the left. If, however, the switching element 12f pushed to the right, so for example, the shift sleeve 11c pushed to the right.

The shift sleeves 11a -C are present form-fitting with respective shift forks 16a -C coupled. For this purpose, the shift sleeves 11a -C outer peripheral side recordings in the form of grooves 17a -C, into which the shift forks 16a -C intervene. The shift forks 16a C are along a guide element in the form of a guide rod 18 displaceable and with the sliding sleeves 11a -C with displaceable. In other words, the shift forks 16a -C on the guide bar 18 arranged and relative to the guide rod 18 movable relative to this. This means that the shift fork 16a is shifted to the right when the shift sleeve 11a is moved to the right. Will the shift sleeve 11a shifted to the left, so will the shift fork 16a moved to the left. Will the shift sleeve 11b shifted to the right, so will the shift fork 16b moved to the right. If, however, the shift sleeve 11b shifted to the left, so this is the shift fork 16b moved to the left. Will the shift sleeve 11c shifted to the right, so this is the shift fork 16c moved to the right. Will the shift sleeve 11c shifted to the left, so this is the shift fork 16c moved to the left.

Respective length ranges of the guide rod 18 are in corresponding shots of the shift forks 16a -C added, leaving the shift forks 16a -C by means of the guide rod 18 be guided. Because the grooves 17a -C in the circumferential direction of the sliding sleeves 11a -C completely circulate, the shift sleeves can 11a -C with the selector shaft 9 turn around while the shift forks 16a -C in the grooves 17a -C intervene. The claw transmission 1 In addition, further comprises switching elements in the form of further shift sleeves 19a c. The shift sleeves 19a -C are on the drive shaft 2 arranged and with the drive shaft 2 , in particular form-fitting, rotatably connected, so that the shift sleeves 19a -C with the drive shaft 2 are rotatable or so that the shift sleeves 19a -C with the drive shaft 2 around the axis of rotation 6 rotate. Also the shift sleeves 19a -C have outside circumference recordings in the form of grooves 20a -C, into which the shift forks 16a -C intervene. The grooves 20a -C are in the circumferential direction of the shift sleeves 19a -C fully encircling trained, so that the shift sleeves 19a -C relative to the shift forks 16a -C can rotate while the shift forks 16a -C in the corresponding grooves 20a -C intervene. Because the shift sleeves 19a -C against rotation with the drive shaft 2 are connected, provided by the drive element torques of the drive shaft 2 on the shift sleeves 19a -C transferred.

The shift sleeves 19a -C are also referred to as sliding sleeves and are in the axial direction of the drive shaft 2 relative to the drive shaft 2 displaceable. Here are the shift sleeves 19a C respectively displaceable between at least two coupling positions and at least one decoupling position. In a first of the coupling positions is the shift sleeve 19a , in particular form-fitting, with the gear 4a connected so that the torques from the drive shaft 2 on the shift sleeve 19a , the gear 4a , the gear 5a and finally the output shaft 3 be transmitted. As a result, the gear G1 is engaged. Here is the shift sleeve 19a in its first coupling position of the gear 4b decoupled. In the second coupling position is the shift sleeve 19a , in particular form-fitting, with the gear 4b coupled and from the gear 4a decoupled, leaving the output shaft 3 from the drive shaft 2 is driven via the gear stage Z2. Thus, the gear G2 is engaged. In its Entkoppelstellung is the shift sleeve 19a both from the gear 4a as well as from the gear 4b decoupled, so no torques from the gear 4a or 4b on the shift sleeve 19a can be transmitted. The same applies to the shift sleeves 19b and 19c to. in their first coupling position is the shift sleeve 19b with the gear 4c positively coupled and from the gear 4d decoupled, so that the gear G3 is engaged. in its second coupling position is the shift sleeve 19b with the gear 4d positively coupled and from the gear 4c decoupled so that the gear G4 is inserted. In its Entkoppelstellung is the shift sleeve 19b both from the gear 4c as well as from the gear 4d decoupled. In its first coupling position is the shift sleeve 19c with the gear 4e coupled and from the gear 4f coupled, so that the gear G5 is inserted. in its second coupling position is the shift sleeve 19c , in particular form-fitting, with the gear 4f coupled and from the gear 4e decoupled, so that the gear G6 is inserted. In its Entkoppelstellung is the shift sleeve 19c both from the gear 4e as well as from the gear 4f decoupled. So are the shift sleeves 19a -C in their decoupling positions, so is not a gear of the claw gear 1 inserted. The claw transmission 1 is then idle.

Out 1 is also seen that the shift shaft 9 via a coupling device 21 with the drive shaft 2 is coupled, so that the switching shaft 9 via the coupling device 21 from the drive shaft 2 is drivable. This will be the switching elements 12a -F via the coupling device 21 from the drive shaft 2 around the axis of rotation 10 driven.

Because the shift sleeves 19a -C form-fitting with the shift forks 16a -C are coupled, the shift sleeves 19a -C along the drive shaft 2 or shifted relative to this by the shift forks 16a -C are moved. Thus, the shift sleeves 19a -C by means of the shift forks 16a C between the respective coupling positions and the respective Entkoppelstellung relative to the drive shaft 2 displaceable. To move the shift forks 16a -C turn the shift sleeves 11a -C by means of the switching elements 12a -F moved.

Overall is in 1 recognizable that the output shaft 3 with the drive shaft 2 can be coupled via the respective gear stages Z1-6 by the shift sleeves 19a C are moved or pushed in their respective coupling positions. This is done in turn by the fact that the shift sleeves 11a -C using the switching elements 12a -F are moved, with the switching elements 12a -F are moved by the pen elements 15a -L in the radial direction of the switching shaft 19 in the respective shift gates 13a , b are moved.

To damage the doggear 1 To avoid it is desirable that all gears are designed, that is, that all shift sleeves 19a C are in their Entkoppelstellung, or - to drive the at least one wheel or the vehicle - only one of the gears G1-6 is inserted while the other courses are designed. In other words, each should only one of the shift sleeves 19a -C are in one of their coupling positions while the other shift sleeves are in their decoupling positions. By means of the actuators 14a -L is an automated switching of the doggear 1 realizable. For this purpose, the actors 14a For example, from an in 1 unrecognizable control unit driven so that, if necessary, the pin elements 15a -L in engagement with the corresponding shift gate 13a , b to thereby effect the on-demand engagement and disengagement of the gears G1-6.

This is the jaw gear 1 as a non-synchronized claw transmission 1 , in particular claw gear, trained, which is usually used in motorcycles, but also in general engineering. For switching the gears G1-6, the axially displaceable pin elements 15a -L in the groove-like or groove-shaped switching scenes 13a , b moves, thereby causing the switching elements 12a -F axially on the stem 9 be moved. The switching elements 12a -F are over the shift sleeves 11a -C and the shift forks 16a -C with the shift sleeves 19a -C coupled. Under the axial displaceability of the pin elements 15a -L is to understand that the pin elements 15a -L along its axial direction by means of the actuators 14a -L can be moved, with the respective axial direction of the pin elements 15a -L with the radial direction of the switching shaft 9 coincides.

Alternatively, it is conceivable that the respective switching elements 12a -F directly with the sliding sleeves 19a -C are coupled. Then, for example, the shift sleeves 11a -C and the shift forks 16a -C also omitted as the shift shaft 9 , Here are the switching elements 12a For example, on the drive shaft 2 slidably disposed relative to this. Furthermore, it can be provided that the switching elements 12a -F in one piece with the sliding sleeves 19a -C are formed. Furthermore, it is conceivable that instead of the gears 4a -F so-called sliding wheels are provided, which are both the function of the gears 4a -F and the function of the shift sleeves 19a -C take over. By moving the switching elements 12a -F then the sprockets on the drive shaft 2 shifted relative to this, so that they engage, for example, with the corresponding gears 5a -F and out of engagement with the gears 5a -F can be moved. In other words, it is conceivable that the aforementioned first switching switching elements, the shift sleeves 19a -C or on the drive shaft 2 arranged sliding wheels are.

In contrast to manual transmissions with shift drum, in which only one gear can be engaged by the course of grooves in the shift drum, it is in the case of the claw transmission 1 provided and by the individual actuators 14a -L effecting switching basically possible to insert several of the gears G1-6 at the same time. This can be done, for example, by not just one of the actuators 14a -L, but also at least one more of the actors 14a Is controlled so that, for example, not only exactly one of the gears G1-6, but also a second of the gears G1-6 is inserted. Since the gears G1-6 differ in their translations from each other, it can, if two gears are engaged or switched simultaneously, to massive damage to the dog transmission 1 come. This simultaneous switching or insertion of two gears is also referred to as a double engagement.

Now to such a double intervention in a simple, inexpensive way and effectively too avoid, includes the jaw gear 1 - like out 2 and 3 is recognizable - a whole with 22 designated locking device by means of which the respective shift sleeves 11a -C positive fit with the stem 9 connectable and thereby against relative displacements to the switching shaft 9 to be secured. The function of the locking device 22 will be described below using the sliding sleeve as an example 11a described, but can easily on the other shift sleeves 11b and 11c or the first switching elements 12a -F transferred. The locking device 22 comprises a respective locking element in the form of a spring-loaded locking element 23 , Which in the present case perpendicular to the axial direction of the switching shaft 9 between an in 2 shown blocking position and at least one relative displacement of the shift sleeve 11a to the switching shaft 9 releasing release position relative to the shift shaft 9 is displaceable. Here is the locking element 23 at least partially in the switching shaft 9 taken and at the switching shaft 9 slidably mounted. Furthermore, it is conceivable, for example, that the residual element 23 obliquely to the axial direction of the switching shaft 9 is displaceable relative to this.

In the blocking position is the shift sleeve 11a under positive engagement of the locking element 23 with the switching shaft 9 and with the sliding sleeve 11a against relative displacements to the switching shaft 9 secured. For this purpose, the shift sleeve 11a a recess 24 on, in which the locking element 23 engages in the locked position. The locking element 23 is formed at least in a partial area spherical or spherical segment-shaped, wherein the recess 24 adapted in terms of their shape to the shape of said portion and thus also spherical or spherical segment-shaped. The locking element 23 is at the selector shaft 9 over a in the switching shaft 9 arranged spring element 25 supported, wherein the spring element 25 in the release position is stretched. In other words, the locking element 23 moved from the locked position to the release position, so this is the spring element 25 cocked and compressed here. This will be the locking element 23 by means of it tensioned spring element 25 acted upon by a spring force, by means of which the latching element 23 can be moved from the release position to the locked position.

The locking device 22 also includes a respective, in the switching shaft 9 recorded slide 26 , which between at least one of the locking element 23 against a displacement from the locking position to the release position securing position and at least one of the displacement of the locking element 23 from the blocking position in the release position releasing release position relative to the switching shaft 9 is displaceable. The slider 26 is in accordance with 2 in the release position. According to 3 is the slider 26 in the secured position.

The slider 26 has two first length ranges 27 and a second, in the longitudinal direction of the slider 26 between the length ranges 27 arranged length range 28 with a recess 29 on. Is the recess 29 in overlap with the locking element 23 arranged, as is the case in the release position, so can the locking element 23 at least partially into the recess 29 pushed and thereby moved from the locked position to the release position. This movement from the blocking position to the release position is in the securing position of the slider 26 prevents, as if from 3 is recognizable - the locking element 23 at one of the length ranges 27 is supported. Out 2 and 3 are more slides 30 and 31 recognizable, the slider 30 for example, the shift sleeve 11b and the slider 31 the shift sleeve 11c assigned.

About the recess 24 can the shift sleeve 11a For example, in one with the Entkoppelstellung the shift sleeve 19a be secured or held corresponding first position.

Out 2 and 3 it can be seen that the shift sleeve 11a further recesses 37 and 38 has, which in the axial direction of the switching shaft 9 or the shift sleeve 11a on both sides of the recess 24 is arranged. For example, the locking element 23 in one with the first coupling position of the shift sleeve 19a corresponding second position of the shift sleeve 11a into the recess 37 engage, so that thereby the shift sleeve 11a by means of the recess 37 and the locking element 23 positively in the with the first coupling position of the shift sleeve 19a corresponding second position relative to the switching shaft 9 is secured. Furthermore, it is possible, for example, that the locking element 23 in one with the second coupling position of the shift sleeve 19a corresponding third position of the shift sleeve 11a into the recess 38 engages, so that thereby the shift sleeve 11a in her with the second coupling position of the shift sleeve 19a corresponding third position form fit against relative displacement to the shift shaft 9 is secured. By means of the actuators 14a -D and the corresponding pin elements 15a -D can the shift sleeve 11a be moved between these positions, the shift sleeve 11a in their respective positions by a through the respective recess 24 respectively 37 respectively 28 and the corresponding locking element 23 caused detent can be secured. This fuse the shift sleeve 11a in their respective positions respectively Positions can readily on the respective switching elements 12a -F transferred.

Out 2 and 3 is also seen that spring means are provided, which by spring elements 32 and 33 are formed. The spring element 32 is in the axial direction between the shift sleeve 11a and the switching element 12b arranged and supported on this, wherein the spring element 33 in the axial direction of the switching shaft 9 between the switching element 12a and the shift sleeve 11 is arranged on and supported on this. About the respective spring element 32 and 33 is the shift sleeve 11a from the switching elements 12a and 12b displaceable, wherein the spring elements 32 and 33 by moving the switching elements 12a and 12b in the direction of the sliding sleeve 11a are elastically deformable or deformed when the shift sleeve 11a by means of the locking device 22 against a relative displacement to the shift shaft 9 is secured.

This means that the switching elements 12a and 12b although relative to the switching shaft 9 can be moved, but the shift sleeve 11a by means of the locking device 22 against a relative displacement to the switching shaft 9 is secured. This allows relative displacements of the switching elements 12a and 12b to the switching shaft 9 and to the shift sleeve 11a be admitted, while a simultaneous insertion of multiple gears can be safely avoided. Thus cause malfunction in the control of the actuators 14a -L not for double engagement of gear wheels and the associated heavy damage to transmission components. Consequential damage, for example, by blocking the drive train and fall of the driver of the vehicle can be avoided. At the same time damage to the shift gates 13a , b and at the actors 14a -L be avoided because the spring elements 32 and 33 a relative displacement of the switching elements 12a and 12b to the switching shaft 9 and to the shift sleeve 11a allow. As a result, an overload protection is created.

Is the slide located 26 in its release position and becomes one of the switching elements 12a and 12b relative to the switching shaft 9 moved by, for example, one of the pen elements 15a -D in engagement with the shift gate 13a , b is moved, then the shift sleeve 11a over the spring element 32 respectively 33 from the respective switching element 12a respectively 12b with a in the axial direction of the switching shaft 9 acting force applied. The catch element engages 23 initially in the corresponding recess 24 one. Because the recess 24 and the corresponding portion of the locking element 23 formed at least substantially spherical segment, resulting from the force acting in the axial direction force acting in the radial direction force component, which of the shift sleeve 11a on the locking element 23 acts. By means of this force component is the locking element 23 in the radial direction of the switching shaft 9 from the recess 24 and in the recess 29 pushed, causing the spring element 25 is compressed.

This allows the shift sleeve 11a be moved so that by this shifting the shift sleeve 11a the shift fork 16a and in turn the shift sleeve 19a can be moved, so that finally the desired gear G1 or G2 can be inserted or interpreted. Will then the shift sleeve 11a again so moved that the recess 24 in overlap with the locking element 23 comes, so can the locking element 23 by means of the spring force of the tensioned spring element 25 on the locking element 23 acts, back into the recess 24 to be moved.

However, is the slider 26 in its securing position, so even if the corresponding switching element 12a respectively 12b is moved and, accordingly, said force in the axial direction of the shift sleeve 11a acts, the locking element 23 not be moved from the locking position to the release position, since the locking element 23 at one of the length ranges 27 is supported. Thus, the locking element remains 23 in engagement with the corresponding recess 24 so that the locking element 23 both with the switching shaft 9 as well as with the sliding sleeve 11a cooperates, in particular positively cooperates, whereby the shift sleeve 11a against a relative displacement of the switching shaft 9 is secured. In other words, the shift sleeve 11a not be moved, so that the shift fork 16a and the associated shift sleeve 19a can not be moved. As a result, a double intervention can be avoided.

Out 4 it can be seen that the slider 26 for example with the sliding sleeve 11b coupled and thus on the shift sleeve 11b between the securing position and the release position is displaceable. Thus, the gear G3 or the gear G4 by means of the shift sleeve 11b inserted, so is the slide 26 in a safety position so that gears G1 and G2 can not be engaged.

To the slider 26 with the sliding sleeve 11b to couple is another pin element 34 provided, which partially in the shift sleeve 11b and partly in the slide 26 intervenes. This is the slider 26 over the pin element 34 with the sliding sleeve 11b coupled and thus with the sliding sleeve 11b mitverschiebbar. Furthermore, in the shift shaft 9 a provided for example as a slot opening 35 provided in which the pin element 34 with the sliding sleeve 11b is mitverschiebbar. This means that of the shift sleeve 11a associated slide over another of the shift sleeves 11a -C, that is over the shift sleeve 11b and / or the shift sleeve 11c is displaceable.

Overall is off 1 to 4 recognizable that the construction of the doggear 1 can be kept very simple, so that the number of parts, the cost, the weight and space requirements of the jaw gear 1 can be kept very low. Furthermore, the jaw gear 1 operated particularly advantageous, in particular switched, since, by means of the locking device 22 a double intervention can be safely avoided. In addition, an automation of the doggear 1 realized in a particularly simple manner, since the switching elements 12a -F by means of the actuators 14a -L about the pin elements 15a -L can be moved automatically.

The spring elements 32 and 33 thus represent a resilient connection, by means of which damage to the doggear 1 , in particular by forced operation, can be prevented. Can a safe movement of the respective shift sleeve 19a -C can be achieved, for example by actively detecting the gap, so can on the respective spring element 32 and 33 be waived.

5 shows the jaw gear 1 fragmentary according to a second embodiment. In the second embodiment are - as mentioned above - the shift sleeves 11a -C and thus the shift forks 16a -C as well as the guide rod 18 not provided. As with the example of the switching element 12a can be seen, are the switching elements 12a For example, on the drive shaft 2 arranged and relative to the drive shaft 2 slidable in the axial direction. The following and previous versions of the sliding sleeves 11a -C and the stem 9 can easily on the switching elements 12a -F and the drive shaft 2 be transferred, in particular with regard to securing the shift sleeves 11a -C against axial relative displacements to the switching shaft 9 , Further, it is provided in the second embodiment that the shift sleeves 19a -C in the switching elements 12a -F are integrated. This means that the shift sleeve 19a in the switching element 12a is integrated, so that the shift sleeve 19a and the switching element 12a between the previously described coupling positions and the previously described decoupling position relative to the drive shaft 2 are displaceable.

If the in 5 shown embodiment of the doggear 1 for reasons of space is not possible, for example, the first embodiment can be realized. How out 5 can be seen, the switching element has 12a four shift gates 13a In which the respective pin elements 15a -D by means of the respective actuators 14a -D in the radial direction of the drive shaft 2 can be moved into it. The pin elements 15a -L the actors 14a -L can be operated in different ways. For a particularly space-saving and quick operation of the pin elements 15a -L, it is preferably provided that the actuators 14a -L are designed as electrical actuators or electric drives.

LIST OF REFERENCE NUMBERS

1

mesh transmission

2

drive shaft

3

output shaft

4a-f

gear

5a-f

gear

6

axis of rotation

7

bearing element

8th

axis of rotation

9

shift shaft

10

axis of rotation

11a-c

shift sleeve

12a-f

switching element

13a-d

shift gate

14a-l

actuator

15a-l

pin element

16a-c

shift fork

17a-c

groove

18

guide rod

19a-c

shift sleeve

20a-c

groove

21

coupling device

22

locking device

23

locking element

24

recess

25

spring element

26

pusher

27

first length range

28

second length range

29

recess

30

pusher

31

pusher

32

spring element

33

spring element

34

pin element

35

opening

36

outer peripheral side surface

37

recess

38

recess

G1-6

corridor

Z1-6

gear stage

Claims (11)

Claw transmission ( 1 ), in particular for a motor vehicle, with a drive shaft ( 2 ), with an output shaft ( 3 ), with at least one on a shaft ( 2 . 3 . 9 ) of the claw gear ( 1 ) relative to the a wave ( 2 . 3 . 9 ) arranged displaceably, with one shaft ( 2 . 3 . 9 ) rotatable and at least one shift gate ( 13a ) having switching element ( 12a ), by means of which by shifting the switching element ( 12a ) along the one wave ( 2 . 3 . 9 ) a coupling of the output shaft ( 3 ) with the drive shaft ( 2 ) via at least one gear stage (Z1) of the doggear ( 1 ) is feasible with at least one actuator ( 14a ) and with at least one pin element ( 15a ), which by means of the actuator ( 14a ) in engagement with the shift gate ( 13a ) is translationally movable, whereby a displacement of the switching element ( 12a ) relative to the one shaft ( 2 . 3 . 9 ) is feasible. Claw transmission ( 1 ) according to claim 1, characterized in that the shift gate ( 13a ) in an outer peripheral side surface ( 36 ) of the switching element ( 12a ), wherein the pin element ( 15a ) by means of the actuator ( 14a ) in the radial direction of the one shaft ( 2 . 3 . 9 ) translationally in the shift gate ( 13a , b) is movable, whereby the switching element ( 12a ) along the one wave ( 2 . 3 . 9 ) due to a rotation of the one shaft ( 2 . 3 . 9 ) and the switching element ( 12a ) is displaceable. Claw transmission ( 1 ) according to claim 2, characterized in that the shift gate ( 13a ) in the circumferential direction of the one shaft ( 2 . 3 . 9 ) and the switching element ( 12a ) has a different course from a circular course. Claw transmission ( 1 ) according to claim 3, characterized in that the shift gate ( 13a ) has a helical course at least in a partial region. Claw transmission ( 1 ) according to claim 3 or 4, characterized in that the shift gate ( 13a ) at least in a partial region obliquely to the axial direction of the one shaft ( 2 . 3 . 9 ) runs. Claw transmission ( 1 ) according to one of the preceding claims, characterized in that at least one in at least one position of the switching element ( 12a ) positively with this and the one wave ( 2 . 3 . 9 ) interacting detent element ( 23 ) is provided, by means of which the switching element ( 12a ) due to the respective form-fitting interaction against a relative displacement to the one shaft ( 2 . 3 . 9 ). Claw transmission ( 1 ) according to one of the preceding claims, characterized in that at least one on the one shaft ( 2 . 3 . 9 ) or on another wave ( 2 . 3 . 9 ) of the claw gear ( 1 ) relative to one or the other wave ( 2 . 3 . 9 ) arranged displaceably, with one or the other shaft ( 2 . 3 . 9 ) rotatable second switching element ( 11a ) is provided, by means of which by moving the second switching element ( 11a ) along one or the other wave ( 2 . 3 . 9 ) the coupling of the output shaft ( 3 ) with the drive shaft ( 2 ) via the gear stage (Z1) is effected, wherein the second switching element ( 11a ) by moving the first switching element ( 12a ) is displaceable. Claw transmission ( 1 ) according to claim 7, characterized in that a locking device ( 22 ) is provided, by means of which the second switching element ( 11a ) positively with one or the other wave ( 2 . 3 . 9 ) and thereby against a relative displacement to one or the other wave ( 2 . 3 . 9 ). Claw transmission ( 1 ) according to claims 7 and 8, characterized in that at least one spring device ( 32 . 33 ) is provided, via which the second switching element ( 11a ) of the first switching element ( 12a ) is displaceable, wherein the spring device ( 32 . 33 ) by moving the first switching element ( 12a ) is elastically deformable when the second switching element ( 11a ) by means of the locking device ( 22 ) against a relative displacement to one or the other wave ( 2 . 3 . 9 ) is secured. Claw transmission ( 1 ) according to one of the preceding claims, characterized in that the actuator ( 14a ) is designed as an electrical actuator. Vehicle, in particular motor vehicle, with a claw transmission ( 1 ) according to any one of the preceding claims.

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