EP3701162A1

EP3701162A1 - Device and method for synchronisation

Info

Publication number: EP3701162A1
Application number: EP18786665.2A
Authority: EP
Inventors: Oswald Friedmann; Wolfgang Haas; Dominik Hans
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2017-10-26
Filing date: 2018-10-08
Publication date: 2020-09-02
Also published as: WO2019080960A1; CN111527320A; CN111527320B; DE102018124681A1; DE112018004976A5

Abstract

The invention relates to a device (11, 12) for synchronisation between a shaft (2) and an idler (7) mounted rotatably on the shaft (2), said device having an actuation mechanism (9), a synchronisation mechanism (21) and a clutch mechanism (20). To optimise the device in terms of the required installation space, a locking mechanism is held radially inside the running teeth of the idler (7), said locking mechanism being arranged in a locking manner between the actuation mechanism (9), which can be actuated radially from the outside in relation to the idler (7, 8), and the synchronisation mechanism (21), which is arranged radially inside the running teeth of the idler (7).

Description

Apparatus and method for synchronizing

The invention relates to a device for synchronizing between a shaft and a loose wheel, which is rotatably mounted on the shaft, with an actuating device, a synchronizer and a coupling device. The invention further relates to a transmission with pairs of wheels, each comprising a fixed gear and a loose wheel to represent gears in the transmission. The invention further relates to a method for synchronizing between a transmission shaft and a loose wheel, which is rotatably mounted on the transmission shaft, with a device previously described.

From the German patent DE 99 82 494 C1 a synchronizer for a transmission with a rotationally fixed on a gear shaft in the circumferential direction of the transmission shaft synchronizer body is known, with a slidably mounted on the synchronizer body along the longitudinal center axis of the transmission shaft sliding sleeve, with at least one rotatable on the transmission shaft mounted and connected to the synchronizer body gear, which is connected to a coupling body or provided with a coupling toothing and can be coupled via the coupling body or the coupling teeth by means of the sliding sleeve with the synchronizer body. German Offenlegungsschrift DE 0 2009 027 438 A1 discloses a synchronizing device for a manual transmission with a synchronizer body and at least one synchronizer ring, which can be fixed relative to one another in the circumferential direction by means of an indexing, wherein the indexing of at least one arranged on the synchronizer ring and in Substantially extending in the axial direction projection is formed, which engages in at least one 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 has a sliding sleeve, a synchronizer ring, a clutch comprises at least one inclined surface on 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, the one generates 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 a force acting in the direction of the synchronizer body force component arises. The object of the invention is to optimize a device for synchronizing between a shaft and a loose wheel, which is rotatably mounted on the shaft, with an actuating device, a synchronizer and a coupling device with respect to the required space. The object is in a device for synchronizing between a shaft and a loose wheel, which is rotatably mounted on the shaft, with an actuator, a synchronizer and a coupling device, achieved in that a locking device, the barrier effect between the, with respect to the idler gear , Is arranged radially outwardly operable actuator and the radially arranged within the idler gear synchronizer, is received radially within 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 lock pure direction, via which the synchronizer can be actuated, arranged between an actuating element of the actuating device and a synchronizer ring of the synchronizer. A preferred embodiment of the device is characterized in that the locking means is actuated by ramps to convert a rotational movement of an actuating element of the actuating device into an axial actuating movement. Once the shaft and the idler gear have substantially the same speed, an actuating force generated by the actuating element overcomes the oppositely acting blocking force of the locking device and the coupling device rotatably connects the shaft with the idler gear.

A further preferred embodiment of the device is characterized in that the locking device comprises at least one blocking element. The locking element is secured against rotation with respect to the idler gear, for example by a transmission element. 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. A further preferred embodiment of the device is characterized in that the blocking element is provided with operating bevels. 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, a force 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 roof slope or guide slope and thus prevent a further shifting of the synchronizing device. When synchronism of the idler gear and shaft is achieved, the synchronizer device rotates back a synchronizer ring of the synchronizer ring packet and shifts further in the axial direction, but advantageously only by the amount of a wear reserve. A further preferred embodiment of the device 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.

Another preferred exemplary embodiment of the device is characterized in that a spring device is arranged between the blocking element and a synchronizing ring of the synchronizing device. 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 of the device 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 of the device is characterized in that the locking device comprises three blocking 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. Through the cooperation of the management sloping or sloping roofs of the synchronizer ring is easily twisted in an axial movement of the locking elements.

A further preferred embodiment of the device 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 actuating element 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 into an axial actuating movement, preferably by ramps.

A further preferred embodiment of the device is characterized in that the synchronizing device comprises a sliding sleeve. The sliding sleeve is provided, for example radially inward, with a toothing which cooperates with a complementary toothing, which is provided radially on the outside of a coupling body, in order to enable torque transmission between the shaft and the idler gear when the coupling device is closed. 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 Kupplungsungskör- pers bevels or sloping roofs are advantageously provided. As a result, the engagement of the teeth between the sliding sleeve and the coupling body is simplified.

A further preferred embodiment of the device 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, for example, attached to the sliding sleeve. brought. Advantageously, the transmission element allows a return movement 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.

Another preferred embodiment of the device is characterized in that act between a synchronizer ring of the synchronizer and the transmission element stops with a torsional backlash. A further preferred embodiment of the device is characterized in that the coupling device is designed as a self-opening positive locking 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. A further preferred embodiment of the device is characterized in that the coupling device is locked in a closed state. The locking is advantageously represented by the ramps, in particular by corresponding plateaus on the ramps. A further preferred embodiment of the device is characterized in that the sliding sleeve comprises a ball pressure piece, which cooperates with a return ramp to hold the sliding sleeve in an end position.

In a transmission with pairs of wheels, each comprising a fixed gear and a loose wheel to represent gears in the transmission, the above object is alternatively or additionally achieved in that at least one previously described device for synchronizing between two on a transmission shaft adjacent idler gears of the transmission is arranged. The planetary gear is preferably arranged between the two loose wheels. A relative rotation of an actuating element of the planetary gear, that is, for example, a sun gear, a ring gear or a planet carrier of the planetary gear, generates a synchronization of the corresponding idler gear. The actuators can be coupled for example via stops with the associated idler gear, wherein only one in each case a predetermined direction of rotation, the one or the other idler gear from the stop or the attacks is released. This can be safely prevented in a simple manner an undesirable simultaneous insertion of two courses.

In a method for synchronizing between a transmission shaft and a loose wheel, which is rotatably mounted on the transmission shaft, with a device described above, in particular in a previously described transmission, the above object is alternatively or additionally achieved in that the synchronizer and the coupling device be displaced successively by a relative movement of the actuator to the idler gear so that the idler gear is rotatably connected to the transmission shaft, the locking device ensures that the corresponding idler gear is then connected to the transmission shaft rotationally fixed when the transmission shaft and the idler gear substantially the same Have speed. Further advantages, features and details of the invention will become apparent from the following description in which, with reference to the drawings, various embodiments are described in detail. Show it:

1 shows a transmission with a transmission input shaft, on which two fixed wheels are arranged, and with a transmission output shaft, on which two loose wheels are arranged, which mesh with the fixed wheels;

Figure 2 shows a detail of Figure 1 with a device for synchronizing between the transmission output shaft and the two loose wheels;

FIG. 3 shows an enlarged detail from FIG. 2, in which an actuation of the left-hand idler gear shown in FIG. 3 is illustrated;

Figure 4A is a perspective view of a sliding sleeve of the device of Figures 1 to 3 with the clutch device open;

FIG. 4B shows the same illustration as in FIG. 4A with the coupling device closed; Figure 5 is a perspective view of a planet carrier of the device of Figures 1 to 3 with a blocking element designed as a locking element;

Figure 6 is an exploded view of the device of Figures 1 to 3 with the

Transmission output shaft and the two loose wheels;

Figure 7 is a similar view as in Figure 2 with a device according to a second embodiment with a ball pressure piece and a return ramp;

FIG. 8 shows an enlarged detail from FIG. 7;

9 is a perspective sectional view of the left idler wheel in FIG. 7 with the clutch device open; FIG.

Figure 10 is the same view as in Figure 9 with closed and locked

Coupling device;

Figure 1 1 is a perspective view of a synchronizer ring with a locking device;

Figure 12 is a perspective sectional view of a planet carrier with the synchronizer ring and the locking device of Figure;

Figure 3 is a similar view as in Figure 2 with a complete longitudinal section through the two idler gears according to a further embodiment;

Figure 14 is an enlarged detail of Figure 13;

Figure 15A is a perspective view of a sliding sleeve with a movement device for the sliding sleeve with the coupling device open;

FIG. 15B shows the same illustration as in FIG. 15B with the door closed and locked

Coupling device; Figure 16 is an exploded view of a two-part planetary carrier with a locking device; Figure 17 is a partially cutaway perspective view of a moving means for synchronization with a sun gear and a locking device;

Figure 18 is an exploded view of the locking device of Figure 17 with a

Sliding sleeve, a synchronizer ring and a movement element for the

Locking device; and

Figure 19, the locking device of Figure 18 with the synchronizer ring in the assembled state.

FIG. 1 shows a transmission 10 with a transmission input shaft 1 and a transmission output shaft 2. The transmission output shaft 2 is rotatably mounted with the aid of two bearing devices 3, 4 parallel to the transmission input shaft 1 and in Figure 1 about a horizontally extending axis of rotation.

On the transmission input shaft 1, two fixed wheels 5, 6 are arranged. The fixed wheels 5, 6 are rotatably connected to the transmission input shaft 1. On the transmission output shaft 2, two idler gears 7, 8 are arranged. The idler gear 7 meshes with the fixed gear 5. The idler gear 8 meshes with the fixed gear. 6

The idler gears 7, 8 are rotatably mounted relative to the transmission output shaft 2, but can be rotatably connected to the transmission output shaft 2 at an actuation to represent a gear in the transmission 10 together with the corresponding fixed gear 5, 6. The actuation takes place via an actuating device 9 radially outside the idler gears 7, 8.

In FIGS. 2, 7 and 13, in the illustrated sections, which illustrate various exemplary embodiments, the transmission designated by 10 in FIG. 1 comprises two synchronizing devices 1 1, 12. The device for synchronizing 1 1 is assigned to the idler gear 7 arranged on the left in FIGS. 2, 7 and 13. The device for synchronizing 12 is assigned to the idler wheel 8 arranged on the right in FIGS. 2, 7 and 13. The actuating device 9 comprises an actuating wheel 13, which is provided on an outer diameter with a toothing. The outer diameter of the actuating wheel 13 is greater than the outer diameter of the two loose wheels 7, 8. In the axial direction, the operating wheel 13 between the two loose wheels 7, 8 is arranged.

The devices 1 1, 12 are received in corresponding recesses radially within the idler gears 7, 8. The operating wheel 13 is led out between the two loose wheels 7, 8 from the receiving space for the devices 1 1, 12 within the idler gears 7, 8 radially outward. Thus, the operating wheel 13, for example by means of a driven gear, radially outside the idler gears 7, 8 are actuated. When pressing the operating wheel 13 is rotated or pivoted.

In FIGS. 2, 3, 7, 8 and 13, 14 it can be seen that the actuating device 9 comprises a planetary gear 14. The planetary gear 14 is disposed in a cavity radially inwardly and axially between the adjacent idler gears 7, 8. By the planetary gear 14, the axial space for the actuator 9 can be reduced in the transmission.

The planetary gear 14 comprises a sun gear 15, a ring gear 16 and Planetenrä- 7. The planet gears 7 are rotatably mounted in a planet carrier The sun gear 15 meshes with the planet gears 17, which in turn mesh with the ring gear 16. The planet carrier 18 rotates in an unactuated state of the devices, 12 substantially synchronously with the idler gear 7. The sun gear 5 rotates in the unactuated state of the devices 1 1, 12 substantially synchronously with the idler gear.

The term substantially synchronous in this context also means that the sun gear 15 and the planetary carrier 18 after actuation by the actuator 9 by a limited angle relative to the idler gears 7, the eighth can rotate to trigger a clutch, switching and / or synchronizing.

When operating the actuator 9, the ring gear 16 is rotated. In the actuated and unactuated state of the actuator 9, the ring gear 16 is fixed. Then the ring gear 16 has the same speed as the transmission, which is established. Thus, the ring gear 16 of the planetary gear 14 in the unactuated state of the actuator 9 has a speed of zero. When the ring gear 16 is rotated, then either the planet carrier 18 or the sun or the sun gear 15 rotates relative to the associated idler gear 7, 8. This relative twist angle is then used in an operation of one of the devices 1 1, 12 for synchronization. The devices 1 1, 12 for synchronization comprise a coupling device 20 and a synchronizer 21. The coupling device 20 comprises a coupling body 22, which serves to represent a rotationally fixed connection between the shaft 2 and one of the idler gears 7, 8. In the embodiment shown in Figures 1 to 6, the left idler gear 7 associated device 1 1 also comprises a locking device 23 with a locking element 24. The locking device 23 is interlocking between the actuator 9 and a sliding sleeve 25, which in turn the coupling device 20th and the synchronization device 21 is assigned. The synchronization device 21 comprises a synchronizer ring packet with synchronizer rings, of which the outer, that is the radially outer, synchronizer ring is provided with the reference numeral 26.

In FIG. 2 below, it can be seen that the device 1 1 further comprises a movement device 27 or an actuating device 27 for the blocking element 24. The actuation of the locking element 24 via an actuating ramp 28. A provision of the locking element 24 via a return element 29, which is designed for example as a return plate. FIG. 3 shows that the synchronizing device 21 is assigned a movement device or actuating device 30. The movement device or actuating device 30 comprises a ramp 28. The blocking element 24 comprises a groove 32 for showing a rotationally fixed connection to the idler gear 7. The groove 32 secures the locking element 24 from rotating with respect to the idler gear 7. For this purpose, for example, access engages implemented as a pin transmission element 33 in the groove 32 a. The transmission element 33 projects radially outwards from the sliding sleeve 25. The device 1 1 further comprises a spring means 34 which is designed as a spring ring or as a wire form spring. The spring device 34 ensures that the synchronizer rings of the synchronizer ring packet of the synchronizer 21 are applied in order to generate a slight frictional torque. This results in that the synchronizer ring 26 is rotated relative to the blocking element 24, until guide bevels, which are also referred to as actuating bevels or sloping roofs, lie axially next to one another. About this roof slopes then a large force can be transmitted to the synchronizer ring 26.

In FIGS. 4A, 4B and 6 it can be seen that a plurality of transmission elements 33, 35 designed as a pin are provided on the sliding sleeve 25 radially on the outside. Advantageously, a total of three transmission elements 33, 35 distributed uniformly over the circumference of the sliding sleeve 25. Radially inside the sliding sleeve 25 has a spline, which serves for producing a rotationally fixed connection with the coupling body 22 of the coupling device 20. For this purpose, the Kupplungsungskör- per 22 and the hub portion of the idler gear 7 radially outside a complementary spline.

The transmission elements 33 and 35 engage in recesses of the dashed line in Figures 4A and 4B indicated return member 42. The recesses are equipped with return ramps 36, 37, 35 together with the transmission elements 33, 35 cause a reset of the sliding sleeve 25.

The blocking element 24 serves to actuate the synchronization between the actuating element 19, the planet carrier 18 and the synchronizer ring 26. Between the actuating element 19 and the blocking element 24 act ramps, which are designated in Figure 5 with 28 and 46. The blocking element 24 is secured against rotation by the transmission elements 33, 35 via the sliding sleeve 25 with respect to the idler gear 7. If the actuating element 19 is rotated relative to the idler gear 7, then the blocking element 24 is displaced axially via the ramps 28, 46 in the direction of the synchronization device 21, which is also referred to as the synchronizing device 21 in abbreviated form.

At the beginning of an operation, the spring ring 34 takes the synchronizer ring 26, until the clearance of the synchronizer ring packet is closed and the synchronizer rings abut each other. The synchronizer ring 26 is rotated by a certain angle of rotation, so that the roof slopes 44 of the locking element 24 are located in front of the roof slopes or operating bevels 43 of the synchronizer ring 26. As long as a synchronizing moment acts, the blocking element 24 designed as a blocking ring blocks the further movement of the actuating element 19.

The rotation of the locking element 24 relative to the idler gear 7 and thus the torque transmission from the locking element 24 to the idler gear 7 via the transmission elements 33, 35 which are provided on the sliding sleeve 25 and in the grooves 32, 45 radially inward on the locking element 24th intervention.

After completion of the synchronization of the synchronizer ring 26 can be turned back over the roof slopes or operating slopes 43, 44. Upon further rotation of the actuating element 19 relative to the idler gear 7 (not shown) entrainment on the actuating element 9 comes into abutment with the lower stop 38 of the recess on the return element 42 of the actuator or movement device 27 for the sliding sleeve 25, as shown in Figures 4A and 4B sees. The return element 42 designed as a return plate and the ramp ring 31 are connected to one another in a material or form-fitting manner. By rotation of the actuating device or movement device 27 for the sliding sleeve 25, the sliding sleeve 25 is brought into engagement with the coupling body 22 of the coupling device 20. In the final position, the plateau locks 41 at the end of the ramp 40, which is in FIG. 4B shows the synchronizer ring 26, so that the sliding sleeve 25 does not need an undercut in order to remain securely engaged.

When laying the gear, the actuator 19 rotates back until the entrainment at the upper stop 39 of the recess on the return plate 42 of the actuator 27 abuts the sliding sleeve 25. About the ramps 36, 37 on the return plate 42, the sliding sleeve 25 is then withdrawn. Next, the locking element 24 is brought via the tab 49 and the ramps 48 on the return plate 29 in its initial position.

In the embodiment illustrated in FIGS. 7 to 12, the synchronizing device or synchronizing device 21 has a common outer synchronizing ring 81 for the two synchronizing ring packets of the devices 11 and 12. The device 11 associated with the left-hand idler 7 in FIG. 7 comprises in addition to the synchronizing device 21 and the coupling device 20 is a locking device 83. The locking device 83 is combined with a transmission element 84 and cooperates with a sliding sleeve 85. The sliding sleeve 85 is combined with a ball pressure piece 87, which bears against a return ramp 86 which is formed on a hub body 92 of the idler gear 7.

In Figure 8, the coupling device 20 and the synchronizer 21 are shown enlarged. The coupling element 88 is rotatably connected via an axial toothing with the sliding sleeve 85. As can be seen in FIG. 8, the transmission element 84 is arranged in the axial direction between an inner synchronizer ring 89 and the actuating element 9 of the actuating device 9 and firmly connected to the idler gear 7 at least in the circumferential direction (not visible).

FIGS. 9 and 10 show an actuating device or movement device 90 for the sliding sleeve 85 in an opened or closed state. The movement means or actuator 90 for the sliding sleeve 85 comprises a ramp 91 of a plurality of ramps on the sliding sleeve 85. The sliding sleeve 85 and the coupling element 88 have an axial toothing 95 for the rotationally fixed connection of the sliding sleeve 85 with the Coupling 88 on. The coupling element 88 is rotatably connected to the shaft 2 via the coupling body 20.

In Figure 1 1, the locking device 83 is shown with the synchronizer ring 89 in a plan view. The synchronizer ring 89 is applied to a lower stop 1 13 of the transmission element 84. The roof slopes or operating slopes 101 and 102 are in contact with the complementary roof slopes of the locking element 1 1 1. The blocking element 1 1 1 is moved in the axial direction to the left. The dashed ring ramp ring 106 with the ramp for Ansynchronisierung 107 comes with its right face on the synchronizer ring 89 to the plant.

In Figure 12, the moving means for Ansynchronisierung 1 5 and the moving means for synchronizing 1 12 is shown in a partially sectioned view. One of a plurality of ball thrust pieces 93 is accommodated in a bore in the plane carrier 1 18, which is firmly connected to the planet carrier 18 and forms the actuating element 19. The ball of the ball pressure piece is in an initial state in one of a plurality of detents 1 17 of an actuating ring for the Ansynchronisierung 120th

The sliding sleeve is not shown in Figures 1 1 and 12 for reasons of clarity.

For Ansynchronisieren is taken from the actuator 9, here the planet carrier 18, via the ball pressure piece 93, an actuating ring for the Ansynchronisierung 20.

This actuating ring 120 displaces via a ramp 107 the ramp ring 106, which is indicated transparently in FIG. 11, in the axial direction, which in turn axially displaces the synchronizer ring 89. If the Ansynchronisierkraft is reached, the ball pressure piece 93 disengages from the latch 1 17. The synchronizer ring 89 has been applied to one of the stops 108 or 1 13 of the transmission element 84 depending on the effective direction of the Ansynchronisiermoments. Roof slopes or operating bevels 101 to 103 of a total of three locking elements 1 1 1 of the locking device 83 come to the operating slopes or roof slopes 104 of the synchronizer ring 89 to the plant. Thieves- actuating ramp of the movement device for synchronizing 1 12 on the actuating element 19 comes to the operating ramp 1 10 of the locking element 1 1 1 to the plant. The synchronizing torque is here partially supported by the roof slopes on the blocking element 11, and this in turn by the stop 108, 113 of the transmission element 84, and partially by the synchronizing ring 89 on the transmission element 84. The angles of the roof slopes or operating bevels 101 to 104 are designed so that the axial counterforce generated by the synchronizing torque on the operating slopes is greater than the axial force required to generate the synchronizing torque. As a result, the blocking elements 1 1 1 lock the further rotation of the actuating element 19 during the synchronization.

After completion of the synchronization of the synchronizer ring 89 can be turned back over the roof slopes 101 to 104 by the locking element 1 1 1 is displaced axially in the direction of the synchronizer ring 89 by a rotation of the actuating element via the actuating ramp. Upon further rotation of the actuating element 19 relative to the idler gear 7, the sliding sleeve 85 is axially displaced via the ramp 91.

The sliding sleeve 85 has a self-opening axial toothing 95. If the coupling device 20 designed as a form-locking coupling is closed, then the sliding sleeve 85, as can be seen in FIG. 10, is locked via a plateau 98 at the end of the ramp 91.

When opening, now only the lock must be opened. The sliding sleeve 85 is pushed back by a small torque between the transmission shaft 2 and the idler gear 7. Several ball thrust pieces 87, which act on the ramps or return ramps 86 in the idler gear 7, then move the sliding sleeve 85 into its end position. FIGS. 13 to 19 show an exemplary embodiment in which the synchronization device 21 comprises two outer synchronizer rings 161, 162. The synchronizer ring 161 is associated with the device 1 1 for the left idler gear 7 in FIG. The synchronizer ring 162 is associated with the device 12 for the right-hand idler 8 in FIG. The devices 1 1, 12 are designed substantially the same, wherein the actuation tion in the device 1 1 via the planet carrier 18 and in the device 12 via the sun gear 15 is introduced.

The device 1 1 comprises a sliding sleeve 164 and a locking device 165. The locking device 165 comprises a blocking element 166. The blocking element 166 is assigned a return device 167. The return device 167 cooperates with a counter-ramp (197 in FIG. 16) on the blocking element 166. As can also be seen in FIG. 16, a ramp 168 on the blocking element 166 interacts with a counter ramp 169 on a planetary carrier part 191.

A movement device or actuating device for the sliding sleeve 164 is denoted by 170 in FIGS. 13, 14 and 15. As shown in FIG. 13, the movement device 170 for the sliding sleeve 164 comprises a movement element 171 for the sliding sleeve 164.

A movement device for the synchronizing device or synchronization device 21 is designated by 173 in FIG. An anti-rotation is designated in Figure 14 with 178. A recess in the sliding sleeve 164 is designated 179 in FIG.

In FIGS. 15A and 15B, it can be seen that the moving element 71 of the movement device 170 for the sliding sleeve 164 comprises transmission elements 181 and 182. The sliding sleeve 64 has a recess 79. On the sliding sleeve 164 beyond a groove 180 is provided, the planet carrier side-flank forms a return ramp 85, and the coupling body-side edge forms an actuating ramp 186. The transmission elements 181, 182 of the movement element 171 engage in the groove 180 of the sliding sleeve 164.

On the movement element 171, a nose 183 is attached to the torque drive. The nose 183 serves to represent the rotation against the planet carrier 18th In Figure 15A, the positive coupling of the coupling device 20 is shown open. In Figure 15B, the positive coupling of the coupling device 20 is shown closed and locked. In FIG. 16 it can be seen that the planet carrier 18 is composed of a planet carrier part 191 and a planet carrier part 192. Return elements 193, 194 and 195 are equipped with ramps 196 which cooperate with counter-ramps 197 on the blocking element 166. The return elements 193 to 195 are fixed in rivet-like manner in the planet carrier 18 between the planet carrier part 191 and 192 with the aid of pins 199. On the blocking element 166 guide slopes or sloping roofs or operating slopes 198 are provided.

The actuating ramps 168 provide, in cooperation with the counter ramps 169 on the planet carrier part 191 for an axial displacement of the locking element 166 in Figure 16 to the right. When designing a gear, the blocking element 166 is reset via the ramps 196 on the return elements 193 to 195 in cooperation with the counter ramps 197.

FIGS. 17 to 19 show how the device 12 assigned to the right-hand gearwheel 8 in FIG. 13 is actuated via the sun gear 15 as an actuating element. The actuation takes place in the same manner as in the exemplary embodiment illustrated in FIGS. 5 and 16 via a movement element 225. The movement element 225 interacts with a blocking device 205, which comprises a blocking element 206 with ramps 207. On the blocking element 206, guide inclines or sloping roofs 209 are provided. Furthermore, the blocking element 206 comprises a plurality of torque supports 21 1, which engage in recesses 228 of the sliding sleeve 204 and serve to prevent rotation of the blocking element 206.

For actuation of the sliding sleeve 204 serve as a transmission element tabs 210. The tabs or transmission elements 210 are integral with the moving member 225 and this in turn firmly connected to the sun gear 15. The transmission elements 210 engage in a groove 227 provided in the sliding sleeve 204. In FIG. 18 it can be seen that the locking device 205 is combined with a spring device 215. The spring device 215 comprises three wire-form springs 216 to 218. The wire-form springs 216 to 218 each have a hook-like bent end 231, 232. In the middle, the wire form springs 216 to 218, as shown by the example of the wire form spring 217, a nose 233 on. The wire form springs 216 are arranged in the assembled state in the groove 221 in the synchronizer ring 162. The nose 233 of the wire-forming spring 216 to 2 8 engages in a recess 234 of the locking element 206. The nose 233 is biased radially there and thus forms a detent. In Figure 19, the locking member 206 is shown with the synchronizer ring 162 in perspective in the assembled state. In addition, in Figure 19 stops 238, 239 shown with backlash.

Upon actuation, the actuator, the planet carrier 18, or the sun gear 15 is rotated relative to the idler gears 7 or 8. As a result, the counter ramp 169 or 226 is rotated relative to the ramp 168 or 207 of the blocking element 166 or 206 and displaces it in the axial direction until the clearance of the synchronizing ring packet is closed. In this case, the spring device 215 prevents the synchronizer ring 161 or 162 from shifting axially relative to the blocking element 166 or 206. The transfer member 181, 182 or 210 of the moving member 171 or 225 moves in this phase in a portion of the groove 80 or 227 of the sliding sleeve 164 or 204, which has no slope.

With closed clearance of the synchronizer ring packet is due to the Rastie- tion of the spring means 2 5 and the axial displacement of the locking member 166 or 206 a Ansynchronisiermoment, due to which the synchronizer ring 161 or 162 in the circumferential direction until it rests against one of the stops 238 or 239. As a result, the guide bevels or roof slopes 198 or 209 of the blocking element come into contact with the guide slopes 220 of the synchronizer ring 161 or 162. The angle of the guide bevels is selected so that the axial counterforce generated by the synchronous torque on the guide slopes greater than that required to generate the synchronous torque axial force. As a result, the blocking element 166 or 206 blocks the further rotation of the actuating element. Is a synchronism of idler gear and shaft reached, then the synchronous torque drops to zero, and the actuator can be further rotated relative to the idler gear. In this case, the blocking element 166 or 206 is further displaced in the axial direction via the ramp 168 or 207, wherein the blocking element pushes further on the synchronizer ring, while the idler gear 7 or 8 on the guide slopes 198 or 209 and 220 rotates back by a small angle of rotation. The wire-form springs 216 to 218 thereby snap out of the recess 234 of the locking element 66 or 206.

After reaching the ramp end of the ramps 168 or 207 and their counter ram 169 or 226, the blocking element 166 or 206 is released in the axial direction. At the same time, the transmission element 181, 182 or 210 of the movement element 171 or 225 reaches the area of the actuation ramp 186 in the groove 180 or 227 of the sliding sleeve 164 or 204. Further rotation of the actuation element displaces the sliding sleeve 164 or 204 in the axial direction and via the actuation ramp 186 thus creates the positive connection between idler shaft.

Finally, the sliding sleeve is locked by rotating the plateau 188 of the transmission element 181, 182 or the transmission element 210 into a further section of the groove 180 or 227 of the sliding sleeve 164 or 204, which has no pitch.

When laying the gear, the actuator, the planet carrier 18, or the sun gear 5 is rotated relative to the idler gears 7 or 8 in the opposite direction. The transmission element 181, 182 or 210 pulls the sliding sleeve 64 or 204 via the return ramp 185 in the direction of the idler gear 7 or 8. Upon further reverse rotation of the actuating element relative to the idler gears 7 or 8, the ramp 196 of the return elements 193 to 195, or the return ramp 212 in engagement with the counter ramp 197 or 229. As a result, the blocking element 166 or 206 in the axial direction to the idler gear 7 or 8 is pulled. Once the clearance is restored in the synchronizer ring package, the synchronizer ring 161 or 162 abuts the planet carrier member 191 or the moving member 225. As a result of further axial displacement of the blocking element 166 or 206, the wire-forming spring 216 to 218 again engages in the recess 234 of the blocking element 166 or 206. LIST OF REFERENCE NUMBERS

Transmission input shaft

Transmission output shaft

Storage facility

fixed gear

Losrad

actuator

transmission

Device for synchronization

operating wheel

planetary gear

sun

ring gear

planet

planet carrier

actuator

coupling device

1 synchronization device

clutch body

3 locking device

4 blocking element

5 sliding sleeve

6 synchronizer ring

7 movement device

8 operating ramp

9 return element

0 movement device ramp ring

groove

Transmission element Spring device Transmission element Return ramp

Rückholrampe

attack

Operating ramp plateau

Return element Operating slope Operating slope Nut

Operating ramp ramp

flap

synchronizer ring

Locking device Transmission element Sliding sleeve

Rückholrampe

Ball pressure element Coupling element Inner synchronizer ring Movement device Ramp

hub body

Ball pressure return ramp

Axial spline plateau

1 operating slope 102 operating slope

103 operating slope

104 operating slope

106 ramp ring

107 Ramp for ansynchronization

108 stop

1 10 actuation ramp

1 1 1 blocking element

1 12 Movement device for synchronization

1 13 stop

1 15 Movement device for synchronization

1 17 catch

1 18 planet carrier

120 actuation ring for Ansynchronisierung

161 synchronizer ring

162 synchronizer ring

164 sliding sleeve

165 locking device

166 blocking element

167 return device

168 ramp

169 counter ramp

70 movement device

171 movement element

73 movement device

175 actuation ramp

178 anti-rotation lock

179 recess

180 groove

181 transmission element

182 transmission element

183 nose

185 return ramp

186 actuation ramp 188 plateau

191 planet carrier part

192 planet carrier part

193 return element

194 return element

195 return element

196 ramp

197 counter ramp

198 guide slope

199 pen

204 sliding sleeve

205 blocking device

206 blocking element

207 actuation ramp

209 guide slope

210 transmission element

21 1 Torque support

212 return ramp

213 movement device

215 spring device

216 wire form spring

217 wire form spring

2 8 wire form spring

220 guide slope

221 groove

225 movement element

226 Gegenram e

227 groove

228 recess

229 counter ramp

231 end

132 end

233 nose

234 recess 238 stop

239 stop

Claims

claims

1 . Device (1 1, 12) for synchronizing between a shaft (2) and a loose wheel (7, 8), which is rotatably mounted on the shaft (2), with an actuating device (9), a synchronizing device (21) and a coupling device (20), characterized in that a locking device

(23; 83; 165,205), the blocking effect between, with respect to the idler gear (7,8), from radially outwardly operable actuator (9) and the radially within a running toothing of the idler gear (7,8) arranged synchronizer (21) is arranged radially within the running gear of the idler gear (7,8) is added.

2. Device according to claim 1, characterized in that the locking device (23; 83; 165,205) can be actuated via ramps (48; 1 10,168) in order to effect a rotational movement of an actuating element (19) of the actuating device (9) into an axial actuating movement convert.

3. Device according to one of the preceding claims, characterized in that the blocking device (23; 83; 165,205) comprises at least one blocking element (24; 1 1 1; 166,206).

4. Device according to claim 3, characterized in that the blocking element (23; 83; 165, 205) is provided with actuating bevels (44; 101, 102, 103, 198; 221).

5. Device according to one of claims 3 and 4, characterized in that the blocking element (23; 83; 165,205) via ramps (48; 0; 168,207) is axially movable.

6. Device according to one of claims 3 to 5, characterized in that a spring means (34; 215) between the blocking element (23; 83; 165,205) and a synchronizer ring (26; 81) of the synchronizer (21).

7. Device according to one of claims 3 to 6, characterized in that the blocking element (24; 166; 206) is designed as a locking ring.

8. Device according to one of claims 3 to 7, characterized in that the locking device (83) comprises three locking elements (1 1 1).

9. gear with pairs of wheels, each comprising a fixed gear (5,6) and a loose wheel (7,8) for representing gears in the transmission, characterized in that at least one device (1 1, 12) for synchronizing according to one of preceding claims between two on a transmission shaft (2) adjacent idler gears (7,8) of the transmission is arranged.

10.Verfahren for synchronizing between a transmission shaft (2) and a loose wheel (7,8) which is rotatably mounted on the transmission shaft (2), with a device (1 1, 12) according to one of claims 1 to 8, in particular A transmission according to claim 9, characterized in that the synchronizing device (21) and the coupling device (20) by a relative movement of the actuating device (9) to the idler gear (7,8) are successively shifted so that the idler gear (7,8 ), wherein the locking device (23; 83; 165,205) ensures that the corresponding idler gear (7, 8) is not connected in a rotationally fixed manner to the gear shaft (2) when the gear shaft (2) and the idler gear (7,8) have substantially the same speed.