DE102018108331A1 - Sliding sleeve device for a synchronization device for shifting transmission gears in a motor vehicle transmission - Google Patents

Abstract

A sliding sleeve device (14) is provided for a synchronizing device (10) for shifting gear trains in a motor vehicle transmission with a ramp ring (18) having a circumferential ramp (42) and a counter ramp (86) which can be slid off in the circumferential direction on the ramps (42). having a sliding sleeve (22) displaceable axially relative to the ramp ring (18) between a retracted position and an extended position for producing positive locking with a synchronizing body (16) associated with a gear, wherein the ramp (42) and / or the counter ramp (44 ) has an effective in the extended position plateau portion (46), and a locking device (26) for releasably locking the sliding sleeve (22), in particular with the ramp ring (18), in the extended position. By means of the plateau section (46), an axial support which is secured against movement by means of the arresting device (26) can be achieved over a larger angular range, so that a robust synchronizing device (10) for shifting transmission gears in a motor vehicle transmission is made possible.

Description

The invention relates to a sliding sleeve device, with the aid of which in a synchronizing gearshifts in a motor vehicle transmission can be switched.

From the German patent DE 199 82 494 C1 is a synchronizer for a transmission with a rotationally fixed on a transmission shaft in the circumferential direction of the transmission shaft synchronizer body known with a slidably mounted on the synchronizer body along the longitudinal center axis of the transmission shaft sliding sleeve, with at least one rotatably mounted on the transmission shaft and the synchronizer body subsequent gear, the is connected to a coupling body or provided with a coupling toothing and can be coupled via the coupling body or the coupling toothing by means of the sliding sleeve with the synchronizer body.

From the German patent application DE 10 2009 027 438 A1 a synchronizer for a transmission with a synchronizer body and at least one synchronizer ring is known, which are mutually fixable by means of indexing in the circumferential direction, wherein the indexing of at least one arranged on the synchronizer ring and is formed substantially in the axial direction extending projection, which in at least engages a recess of the synchronizer body, wherein the recess has at least one inclined surface portion, on which the projection rests on a rotation of the synchronizer ring relative to the synchronizer body slidably.

From the German patent application DE 10 2010 002 932 A1 a synchronization for a vehicle transmission is known which comprises a sliding sleeve, a synchronizer ring, a coupling body and a synchronizer body, wherein on the synchronizer body and on the synchronizer ring in each case at least one inclined surface is provided at which the synchronizer body and the synchronizer ring surface contact, and at least one acting between the synchronizer body and the synchronizer ring elastic element is provided which generates a force acting in the circumferential direction, which press the inclined surfaces of synchronizer body and synchronizer ring to each other so that on the synchronizer ring acting in the direction of the synchronizer body force component arises.

It is the object of the invention to show measures that allow a robust synchronizer for switching gears in a motor vehicle transmission.

The object is achieved according to the invention by a sliding sleeve device having the features of claim 1. Preferred embodiments of the invention are specified in the subclaims and the following description, which individually or in combination may represent an aspect of the invention.

According to the invention, a sliding sleeve device is provided for a synchronizing device for shifting transmission gears in a motor vehicle transmission with a ramp ring having circumferential ramps, counter ramps slidable on the ramps in the circumferential direction and axially displaceable relative to the ramp ring between a retracted position and an extended position Producing a positive connection with a transmission gear associated with a synchronizer body, wherein the ramp and / or the counter ramp has an effective in the extended position plateau section, and a locking device for releasably locking the sliding sleeve, in particular with the ramp ring, in the extended position.

In a motor vehicle transmission, the ratio between two transmission shafts can be predetermined by Stirnradverzahnungen, wherein the ratio of the number of teeth of the meshing gears of the respective spur gear teeth define the translation of the gear formed by this spur gear. For switching the respective transmission gear designed as a loose gear of the spur gears is rotatably coupled with its associated transmission shaft, so that a torque can be transmitted via the rotatably connected idler gear. To couple the idler gear to the transmission shaft, the rotational speed of the idler gear is synchronized with the rotational speed of the gear shaft by means of a synchronizer. For this purpose, for example, a synchronizing ring cause a frictional engagement between the idler gear and the gear shaft, so that adjust the rotational speeds in the slip mode. After the adjustment of the rotational speeds, a form fit between the idler gear and the gear shaft can be brought about, for example via a toothing and / or intermeshing claws. To produce the positive coupling, the sliding sleeve can be displaced axially by means of the sliding sleeve device, whereby, for example, a dog clutch, an axial toothing or a spline can be closed due to the axial displacement of a coupled with the sliding sleeve coupling element. For axial displacement of the shift sleeve, the shift sleeve by a relative rotation to a ramp ring via a between the ramps of the ramp ring and the counter ramps of the Shift sleeve trained ramp system can be moved axially in response to the relative rotation. The ramps which extend in the circumferential direction can change the axial extent of the ramp system. In the retracted position of the shift sleeve, the extension of the ramp system is minimal, so that the distance between the direction away from the ramp ring axial end face of the shift sleeve to the ramp ring is minimal. In the extended position of the shift sleeve, the extension of the ramp system is maximum, so that the distance between the direction away from the ramp ring axial end face of the shift sleeve to the ramp ring is maximum.

In the extended position of the shift sleeve, the ramp of the ramp ring and the counter ramp of the shift sleeve abut each other in the plateau section formed by the ramp and / or by the counter ramp. In particular, both the ramp and the counter ramp to the plateau section, wherein the respective plateau sections of the ramp and the counter ramp in the extended position can overlap each other at least partially. As a result, in the extended position, no punctiform contact between the ramp and the counter ramp, but at least a linear contact is provided which extends in the circumferential direction over a certain angular range. Preferably, the angular range in which the ramp and the associated counter ramp abut one another linearly in the plateau section, extends over an angular range Δα of 0.1 ° ≤ Δα ≤ 30.0 °, in particular 0.5 ° ≤ Δα ≤ 15.0 ° and preferably 1.0 ° ≤ Δα ≤ 5.0 °.

The plateau section thereby forms a stable support surface, can be distributed over the axial forces over a larger angular range and a lower surface pressure can be achieved. In particular, in one, for example, designed as a Hirth toothing, axial toothing of the positive coupling sufficient axial contact force, which prevents an independent opening of the axial toothing can be supported over the plateau section without a plastic deformation under load must be feared. If the positive coupling is formed as a spline, it is possible to save an undercut in the spline. This allows a cost-effective and robust axial support of the sliding sleeve. With the help of the locking device, an additional support of occurring forces can be achieved, so that in particular a relative rotation under load, by which the contact area between the ramp and the counter ramp could be reduced, can be blocked. Preferably, the locking device, at least until a defined limit torque at which the locking device is automatically released, remove torque and lock a relative rotation. Preferably, the locking device is designed to remove axial forces, so that the loads on the ramp and the counter ramp, for example in the case of sudden impacts, can be reduced. For switching a different transmission gear, the switched gear can be solved by the sliding sleeve is rotated together with the form-fitting coupled gear shaft relative to the coupled with the idler gear ramp ring. As a result, a sufficiently high torque can be impressed to release the locking device and, in particular only subsequently, to let the counter ramp of the sliding sleeve on the ramp ramp ramp slide back into the retracted position. Due to the axial displacement of the shift sleeve occurring in this case, the positive engagement with the transmission shaft can be canceled and a torque flow can be interrupted. By means of the plateau section, an axial support which is secured against movement by means of the arresting device can be achieved over a larger angular range, so that a robust synchronizing device for shifting transmission gears in a motor vehicle transmission is made possible.

The plateau portion is a circumferential angular range of the ramp and / or the counter-ramp, which extends substantially only in the circumferential direction and extends substantially with no proportion in the axial direction. In contrast to the ramp-shaped course of the ramp and the counter ramp to the circumferential direction, the plateau section has a slope of zero. The plateau section closes in particular directly to the tapered course of the ramp or the counter ramp. The locking means may comprise a locking element connected to the sliding sleeve, which can cooperate with another locking element in the extended position of the sliding sleeve to hold the sliding sleeve in the extended position. The other locking element may be connected, for example, with the ramp ring, with the idler gear and / or with a return plate. The locking device may in particular comprise a spring-loaded latching element which can cooperate with a spring force with the other latching element, wherein a force applied by the spring force latching force can be overcome at a sufficiently large actuation force to release the locking device. For example, the locking device on a ball pressure piece, wherein a spring-loaded ball engages in a recess to lock the locking device, wherein the spring-loaded ball can only get out of the recess from a defined minimum torque to release the locking device.

In particular, a maximum relative torsion angle between the sliding sleeve and the ramp ring by a, in particular with the Ramp ring firmly connected, return plate limited between the retracted position and an extended position, the return plate allows sweeping at least a majority of the plateau section. For example, the return plate on the sliding sleeve radially outwardly cross paragraphs, which form a retracted position of the sliding sleeve corresponding first tangential stop and the extended position of the sliding sleeve corresponding second tangential stop. The sliding sleeve, for example, have a protruding in the radial direction of the bolt, which can strike at a relative rotation of the shift sleeve to the ramp ring on the axial stops of the return plate. Particularly preferably, each of the first tangential stop and the second tangential stop forming approaches are connected to each other via a web extending in the circumferential direction, wherein the web forms a return ramp, which in a relative rotation from the extended position to the retracted position on the sliding sleeve, in particular on the radial protruding bolt, axially abuts and the sliding sleeve in the axial direction entrains. A significant lifting of the counter ramp from the ramp can be avoided. The return plate does not limit the relative rotation of the sliding sleeve to the ramp ring already when the maximum axial extent of the ramp system is reached, but only when a desired further relative rotation over the plateau section is achieved without further axial displacement of the sliding sleeve. For this purpose, in particular, the second tangential stop can be positioned further offset in the circumferential direction to the first tangential stop by a desired angle to the linear abutment in the plateau section, as it would be required to reach the maximum extent of the ramp system. In particular, it is possible in this case to offset the second tangential stop in the circumferential direction so far that the locking device can safely reach the locked position even in the case of small tolerance requirements with respect to the relative position in the circumferential direction. The resulting lower tolerance requirements, the manufacturing cost can be reduced.

Preferably, the locking device is configured such that a locking and releasing the locking device is carried out by taking place only in the circumferential direction relative rotation of, in particular designed as a recess and locking lug, locking elements. The locking device is provided in particular at a circumferential position, in which the sliding sleeve is further rotated in the extended position without further axial displacement relative to the ramp ring, when a locking of the locking device takes place. If the arreteirete locking device to be solved, must first be a relative rotation of the shift sleeve to the ramp ring, which initially takes place only a relative rotation without an axial offset due to the plateau section to be traversed. Due to the defined forces occurring only in the circumferential direction when locking and when releasing the locking device, the locking device can be made simpler. A support of axial forces when Aretieren and release the locking device is not required. The locking device has, for example, a ball pressure piece, in which a spring-loaded ball engages in a recess to lock the locking device, wherein the spring-loaded ball can only come out of the recess from a defined minimum torque to release the locking device.

Particularly preferably, in a common radius region with the plateau section, a detent element of the locking device, in particular designed as a recess or latching lug, is formed. The relative position of the particular provided in the ramp ring or in the shift sleeve locking element can be easily checked during manufacture. For example, the locking element is provided in a return plate, which is to be firmly connected to the ramp ring. The correct relative position of the return plate to the ramp ring in the circumferential direction can be easily checked by the positioning of the locking element in the immediate vicinity of the plateau section. Errors during assembly or during production can be better avoided.

The invention further relates to a synchronizing device for shifting gears in a motor vehicle transmission with a sliding sleeve device, which can be trained and developed as described above. By means of the plateau section, an axial support which is secured against movement by means of the arresting device can be achieved over a larger angular range, so that a robust synchronizing device for shifting transmission gears in a motor vehicle transmission is made possible.

In particular, the synchronizer for synchronizing between a shaft and a idler gear which is rotatably mounted on the shaft, is provided, wherein the synchronizing means comprises an actuating device and a coupling device, wherein a locking device, the blocking effect between which, with respect to the idler gear, from radially externally operable actuator and arranged radially within a running gear of the idler gear synchronizer is received radially within the running gear of the idler gear. The locking device is advantageously arranged overlapping in the axial direction to the idler gear. As a result, axial space can be saved. The locking device prevents too early engagement of the clutch device. Only when a differential speed between the shaft and the idler gear is reduced substantially to zero, the locking device allows an actuating movement in the axial direction, which is converted from an actuating movement in the circumferential direction and transmitted to the coupling device. The actuating movement in the circumferential direction is advantageously applied via an actuating element, such as a gear, radially outside the idler gear. The synchronizer comprises a synchronizer ring package having synchronizer rings which are frictionally contacted by application of an axial actuation force to generate a frictional torque, also referred to as synchronous torque. The coupling device is preferably designed as a form-locking coupling, for example as a dog clutch. In order to make the axial structure of the device compact and secure, the locking device, by means of which the synchronizing device can be actuated, is arranged between an actuating element of the actuating device and a synchronizing ring of the synchronizing device.

A further preferred embodiment is characterized in that the locking device comprises at least one blocking element. The locking element is against rotation of the idler gear, for example by a transmission element, secured against rotation. The blocking element can be designed as a locking ring. The blocking element may also comprise a plurality of blocking segments. The locking device may also comprise more than one blocking element.

Another preferred embodiment is characterized in that the blocking element is provided with actuating slopes. The operating bevels, which are also referred to as roof slopes, are advantageously also provided on the synchronizer and / or the coupling device. When the device is actuated by the actuating device, power is transmitted via the roof slopes or guide slopes to the synchronizer ring packet. When synchronizing, a synchronizing ring of the synchronizing ring packet can rotate relative to the synchronizing device by a width of a sloping roof or guide slope and thus prevent a further shifting of the synchronizing device. When synchronism of idler gear and shaft reached the synchronizer rotates a synchronizer ring of the synchronizer ring packet back and shifts further in the axial direction, but advantageously only by the amount of a wear reserve.

A further preferred embodiment is characterized in that the blocking element is axially movable via ramps. If the actuator is rotated relative to the idler gear, then the locking member is displaced axially over the ramps in the direction of the synchronizer. The ramps thus act between the actuating element and the blocking element, which is non-rotatably but axially displaceable, coupled to the idler gear.

A further preferred embodiment is characterized in that a spring device between the locking element and a synchronizer ring of the synchronizer is arranged. The spring device is designed for example as a spring ring. The spring device may also comprise a plurality of spring segments, for example, three spring segments or spring arches. About the executed, for example, as a wire spring form spring device, the synchronizer rings of the synchronizer ring packet are applied, that is brought into frictional contact. As a result, a slight friction torque is generated, wherein the synchronizer ring is rotated relative to the blocking element. The guide slopes or roof slopes are then axially next to each other. About the guide slopes or roof slopes, a relatively large force can be transmitted to the synchronizer ring.

A further preferred embodiment is characterized in that the blocking element is designed as a locking ring. The guide slopes or roof slopes are, for example, mounted radially on the outside of the locking ring. In addition, actuating ramps are attached to the locking ring. By way of the actuating ramps, in cooperation with corresponding counter-ramps provided on an actuating element, for example a planetary carrier, an actuating movement of the actuating element in the circumferential direction can be converted into an axial movement of the blocking ring.

A further preferred embodiment is characterized in that the locking device comprises three locking elements. The three blocking elements are advantageously distributed uniformly in the circumferential direction. At the locking elements guide slopes or sloping roofs are mounted, which cooperate with corresponding guide slopes or sloping roofs on the synchronizer ring of the synchronizer. Due to the interaction of the guide bevels or sloping roofs of the synchronizer ring is easily twisted in an axial movement of the locking elements.

A further preferred embodiment is characterized in that the actuating device comprises a planetary gear element of a planetary gear.

An actuating element of the actuating device is, for example, a planet carrier, a ring gear or a sun gear of the planetary gear. The Actuator may be integrally connected to the planet carrier, the ring gear or the sun gear of the planetary gear. Depending on the design, the ring gear, the sun gear or the planet carrier but also represent the actuating element of the actuator. The planetary gear element is defined for actuating the device rotated or pivoted to produce a relative rotation. This relative rotation is converted, preferably by ramps, into an axial actuating movement of the sliding sleeve device.

A further preferred embodiment is characterized in that the sliding sleeve of the sliding sleeve device, for example, radially inside, is provided with a toothing, which cooperates with a complementary toothing, which is for example provided radially on the outside of a coupling body, in order to transmit torque when the coupling device is closed between the shaft and the idler gear. The toothing is designed, for example, as a spline so that the sliding sleeve in the axial direction is movable relative to the coupling body. At the mutually facing ends of the sliding sleeve and the coupling body advantageously guide bevels or sloping roofs are provided. As a result, the engagement of the teeth between the sliding sleeve and the coupling body is simplified.

A further preferred embodiment is characterized in that the blocking element is rotatably connected by at least one transmission element with the idler gear. The transmission element may be positively connected to the idler gear, for example via a pin which engages in a recess. The transmission element can also be designed as a nose or tab. Depending on the design, the transmission element is attached to the sliding sleeve, for example. The transmission element advantageously allows a return of an actuating movement, which were caused by the previously described ramps. Advantageously, a plurality of transmission elements are distributed uniformly in the circumferential direction.

A further preferred exemplary embodiment is characterized in that stops with a torsional backlash act between a synchronizing ring of the synchronizing device and the transmitting element.

A further preferred embodiment is characterized in that the coupling device is designed as a self-opening form-fitting coupling. This means that the clutch device is open in the unactuated state, so no torque between the idler gear and the shaft is transmitted.

• 1: eine schematische perspektivische Ansicht einer ersten Ausführungsform einer Synchronisiereinrichtung,
• 2: eine schematische perspektivische Ansicht einer zweiten Ausführungsform einer Synchronisiereinrichtung in eingefahrener Stellung und
• 3: eine schematische perspektivische Ansicht der Synchronisiereinrichtung aus 2 in ausgefahrener Stellung.

The invention will now be described by way of example with reference to the accompanying drawings with reference to preferred embodiments, wherein the features shown below, both individually and in combination may represent an aspect of the invention. Show it:

• 1 FIG. 2 is a schematic perspective view of a first embodiment of a synchronizer, FIG.
• 2 : A schematic perspective view of a second embodiment of a synchronizer in the retracted position and
• 3 : A schematic perspective view of the synchronizer from 2 in extended position.

In the 1 illustrated synchronizer 10 for a gear ratio of a motor vehicle transmission has a loose wheel 12 on, with the help of a sliding sleeve device 14 with a rotationally fixed with a gear shaft verbunenen acting as a hub hub 16 can be coupled. For actuating the sliding sleeve device 14 an actuatable only partially illustrated planetary gear is provided, the one with a ramp ring 18 the sliding sleeve device 14 connected planet carrier 20 having. At the ramp ring 18 can in a relative rotation a sliding sleeve 22 slide off and thereby be displaced axially to a designed in this embodiment as an axial toothing form-fitting coupling 24 close. About the form-locking coupling 24 can the sliding sleeve 22 with the hub 16 rotatably connected. The sliding sleeve 22 can be at one with the idler gear 12 coupled tangential stop, allowing torque from the gear shaft through the hub 16 , the positive coupling 24 and the sliding sleeve 22 to the idler gear 12 or vice versa can be transmitted. In the illustrated embodiment also has a locking device 26 provided in the extended position of the sliding sleeve 22 when the positive clutch 24 is closed, the sliding sleeve 22 with the loose wheel 12 locked. For this purpose, the locking device 26 one in the sliding sleeve 22 provided ball pressure piece 28 put in one in a pipe socket 30 of the idler gear 12 provided recess 32 can intervene.

At the in 2 illustrated embodiment of the synchronizer 10 is compared to the in 1 illustrated embodiment of the synchronizer 10 the form-locking coupling 24 not designed as an axial toothing, but as a spline. In addition, it can be seen that the sliding sleeve 22 radially protruding bolts 34 that has tangential stops 36 one with the ramp ring 18 or with the loose wheel 12 connected return plate 38 can strike. The tangential stops 36 are over a jetty 40 interconnected, whereby in a piece of pipe of the return plate 38 a window is limited, in which the respective bolt 34 is used. The jetty 40 has one to the bolt 34 pointing up slope, that of the slope of the ramp ring 18 trained ramps 42 equivalent. The bolt 34 and thus the sliding sleeve 22 can between the jetty 40 of the return plate 38 and the ramps 42 of the ramp ring 18 be taken captive.

When the sliding sleeve 22 for example, due to a relative rotation of the return plate 38 relative to the ramp ring 18 can be twisted, counter ramps 44 the sliding sleeve 22 at the ramps 42 of the ramp ring 18 Slip in the circumferential direction, whereby the sliding sleeve 22 in the axial direction in the in 3 shown extended position can be moved. The ramp 42 forms at its highest point in the axial direction a circumferentially without slope extending plateau section 46 in which the sliding sleeve 22 can lie flat with a significant extension in the circumferential direction. In this relative position of the sliding sleeve 22 relative to the ramp ring 18 in which the entire plateau section 46 of the ramp ring 18 on the sliding sleeve 22 is applied, the locking device 26 the sliding sleeve 22 for example with the ramp ring 18 , with the return plate 38 or with the loose wheel 12 lock. Optionally, the locking device 26 the sliding sleeve 22 even in the retracted position, as in 1 is shown.

LIST OF REFERENCE NUMBERS

10

synchronizer

12

Losrad

14

Sliding sleeve device

16

hub

18

ramp ring

20

planet carrier

22

sliding sleeve

24

Positive coupling

26

locking

28

Ball pressure piece

30

pipe extension

32

deepening

34

bolt

36

tangential stop

38

Rückholblech

40

web

42

ramp

44

counter-ramp

46

plateau section

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 19982494 C1 [0002]
• DE 102009027438 A1 [0003]
• DE 102010002932 A1 [0004]

Claims (4)

Sliding sleeve device for a synchronizing device (10) for shifting transmission gears in a motor vehicle transmission, with a circumferential ramp (42) having ramp ring (18), a sliding sleeve (22) which can be displaced relative to the ramp ring (18) between a retracted position and an extended position and which is slidable on the ramps (42) in the circumferential direction to produce positive locking with a synchronizer body (16) assigned to a gear . wherein the ramp (42) and / or the counter ramp (44) has an effective in the extended position plateau portion (46), and a locking device (26) for releasably locking the sliding sleeve (22), in particular with the ramp ring (18), in the extended position. Sliding sleeve device according to Claim 1 characterized in that a maximum relative torsion angle between the sliding sleeve (22) and the ramp ring (18) by a, in particular with the ramp ring (18) fixedly connected, return plate (38) between the retracted position and an extended position is limited, wherein the return plate (38) allows sweeping over at least a majority of the plateau section (46). Sliding sleeve device according to Claim 1 or 2 characterized in that the locking device (26) is designed such that a locking and releasing the locking device (26) takes place by an exclusively circumferential direction relative rotation of, in particular as a recess (32) and latching lug (28) designed latching elements. Sliding sleeve device according to one of Claims 1 to 3 characterized in that in a common radius region with the plateau portion (46), in particular as a recess (32) or latching lug (28) ausgestaltetes, locking element of the locking device (26) is formed.

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