WO2018072786A2

WO2018072786A2 - Method and device for synchronising a gearbox shaft and two idler gears

Info

Publication number: WO2018072786A2
Application number: PCT/DE2017/100876
Authority: WO
Inventors: Oswald Friedmann; Dominik Hans
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2016-10-21
Filing date: 2017-10-16
Publication date: 2018-04-26
Also published as: DE102017123962A1; WO2018072786A3; DE112017005290A5

Abstract

The invention relates to a device for synchronising a gearbox shaft and two idler gears (75, 76) rotatably mounted on the gearbox shaft, the device having an actuation system (85). The invention is characterised in that the actuation system (85) comprises two actuation elements (95) that are rotatable relative to each other and the idler gears (75, 76), and have a locking mechanism (207) that prevents two speeds from being engaged at the same time.

Description

Apparatus and method for synchronizing between a transmission shaft and two idler gears

The invention relates to an apparatus and a method for synchronizing between a transmission shaft and two idler wheels, which are rotatably mounted on the transmission shaft, with an actuating 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.

From the German patent DE 199 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. From the German patent application DE 10 2009 027 438 A1 a synchronizing device for a manual transmission with a synchronizer body and at least one synchronizer ring is known, which by means of indexing in the circumferential direction against each other can be fixed, wherein the indexing of at least one arranged on the synchronizer ring and substantially in axial projection extending 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 comprises a sliding sleeve, a synchronizer ring, a coupling body and a synchronizer body, wherein at least one inclined surface is provided on the synchronizer body and on the synchronizer ring, at those engage the synchronizer body and the synchronizer ring surface, and at least one acting between the synchronizer body and the synchronizer ring elastic element is provided which generates a circumferentially acting force that the inclined surfaces of synchronizer body and synchronizer ring press each other so that the synchronizer ring in an Direction of the synchronizer body acting force component arises.

The object of the invention is the switching performance in the operation of a transmission with pairs of wheels, each comprising a fixed gear and a loose wheel to represent gears in the transmission, and with a device for synchronizing between a transmission shaft and two loose wheels, rotatably mounted on the transmission shaft are, with an actuator to improve.

The object is achieved in a device for synchronizing between a transmission shaft and two idler wheels, which are rotatably mounted on the transmission shaft, with an actuating device, characterized in that the actuating device comprises two relatively rotatable and associated with the idler gears actuating elements with a blocking mechanism which prevents simultaneous insertion of two gears. The device for synchronizing advantageously comprises a planetary gear within the idler gears of the transmission. The planetary gear is preferably arranged axially between the two loose wheels. A relative rotation of an actuating element of the planetary gear, so for example a sun 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 one or the other idler gear is released from the stop or the stops only in each case a predetermined direction of rotation. The claimed locking mechanism ensures in a simple manner that only one direction of rotation is possible. This reliably prevents unwanted simultaneous insertion of two gears.

A preferred embodiment of the device is characterized in that ramp-shaped stops are provided on the actuators, the rotation of the actuating elements relative to the associated idler gear only in allow one direction of rotation. The ramp-shaped stops cooperate with counter-stops, which are provided on the respective associated idler gear.

As a result, twisting in the other directions of rotation is blocked in a simple manner.

A further preferred embodiment of the device is characterized in that over a circumference of the actuating elements a plurality of ramp-shaped stops are distributed unevenly. As a result, after a striking of the actuating element on the associated idler gear in a simple manner larger twist angle can be displayed up to a renewed striking.

A further preferred embodiment of the device is characterized in that the actuating elements relative to each other are axially displaceable so that an actuating element coupled to the transmission shaft idler gear prevents the simultaneous insertion of a second gear. Due to the axial displacement of the one actuating element, the other actuating element is pressed against the associated idler gear in such a way that the ramp-shaped stops engage in recesses of the associated idler gear with the counterstops. In an apparatus for synchronizing between a transmission shaft and two idler wheels, which are rotatably mounted on the transmission shaft, with an actuating device, in particular a device described above, the above object is alternatively or additionally achieved in that the actuating device rotatable relative to each other and two Losrädern associated actuating elements with an anti-rattle device comprises. The actuators are acted upon, for example via a suitable actuator, with a preload moment. As a result, an undesirable noise in the operation of a transmission with the device for synchronization is reliably prevented.

A further preferred embodiment of the device is characterized in that the anti-rattle device comprises a biasing device, is biased by the at least one of the actuating elements in an axial direction. The biasing device comprises, for example, a spring device. The spring device comprises, for example, at least one spring which, preferably in one axial direction, is clamped between the actuator to the associated idler gear. Alternatively or additionally, the spring device may comprise at least one spring, which is biased between the actuating device, in particular one of the actuating elements, and a stationary housing, for example a gearbox housing.

A further preferred embodiment of the device is characterized in that the anti-rattle device comprises a latching device which is arranged between at least one of the actuating elements and a stationary housing body. About the locking device, a desired preload torque can be generated on the actuator or the actuators. A detent on the idler gear and a detent on the actuating element cooperate advantageously according to a further embodiment with a small angular offset to achieve a preload torque on a ramp of one of the two notifications together.

A further preferred embodiment of the device is characterized in that the anti-rattle device comprises a biasing device which is effective between at least one of the actuating elements and the associated idler gear. The biasing means advantageously comprises at least one spring.

A synchronizing device and a coupling device are arranged overlapping in the axial direction. Due to the overlapping arrangement of the synchronizing device and the coupling device, it is possible in a simple manner to save on axial structural space.

A preferred exemplary embodiment of the device is characterized in that the synchronizing device and the coupling device can be actuated via a slotted guide by an actuating device. The slide guide is advantageously used to convert relative rotations in axial movements, which in turn are used for synchronization between the transmission shaft and the idler gear. The slotted guide advantageously comprises at least one sliding block, in particular a guide pin, which is guided in a slot, in particular a slide track or a groove. The actuating device advantageously comprises a planetary gear member, which is defined rotated or pivoted to generate the relative rotation.

A further preferred embodiment of the device is characterized in that the coupling device comprises a coupling sleeve, which cooperates with a coupling link. The coupling link advantageously comprises at least one guide groove, at least one thread and / or at least one ramp. According to a preferred embodiment, the coupling link comprises a thread and a guide groove. The thread is achieved in a simple manner, a better power distribution. However, a similarly good force distribution can also be achieved with a ramp or with a plurality of ramps distributed in the circumferential direction.

A further preferred exemplary embodiment of the device is characterized in that the synchronizing device comprises a synchronizing sleeve which cooperates with a synchronizing slide. The Synchronisierkulisse advantageously comprises at least one guide, at least one thread and / or a ramp. According to a particularly preferred embodiment, the synchronizing link comprises a thread and a guide groove or slide track. In the guide groove or slide track engages a sliding block, in particular a guide pin. Through the sliding block, in particular the guide pin re-threading the thread is considerably simplified.

Another preferred exemplary embodiment of the device is characterized in that the synchronizing sleeve and the synchronizing slide are radially connected to the

Coupling sleeve and the clutch link are nested. As a result, axial space can be saved in a simple manner. The coupling sleeve is advantageously arranged radially inward. The synchronizing sleeve is advantageously arranged radially on the outside. The coupling sleeve associated with the coupling sleeve is advantageously arranged radially therebetween, together with the synchronizing sleeve associated with the synchronizing sleeve.

A further preferred exemplary embodiment of the device is characterized in that the synchronizing link is thus coupled to the coupling link, the synchronizing sleeve can be displaced in the axial direction to a limited extent independently of the coupling sleeve. As a result, a stable operation of the synchronizing device in a transmission is made possible in a simple manner. Another preferred embodiment of the device is characterized in that the coupling sleeve is rotatably connected to the idler gear. The rotationally fixed connection is represented, for example, with at least one sliding toothing. The sliding toothing allows a simple axial movement of the coupling sleeve relative to the idler gear.

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 by arranging two previously described devices for synchronization between two on a transmission shaft idler gears of the transmission are. As a result, the transmission can be made very compact. The transmission is preferably a dual-clutch transmission. The dual-clutch transmission is preferably installed in a front-transverse arrangement in a motor vehicle, in particular in a motor vehicle having a hybrid drive.

In a method for synchronizing between a transmission shaft and two idler gears, which are 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 coupled to the transmission shaft. The synchronizing movement and the coupling movement are carried out particularly advantageously in the same axial space. The coupling of the idler gear with the transmission shaft is advantageously carried out via a rotation transmission element, which is also referred to as a coupling body.

A preferred embodiment of the method is characterized in that an actuation of the Synchronisierkulisse and the clutch linkage takes place by a relative rotation relative to the idler gear. The relative rotation is advantageous haft provided by a planetary gear member of a planetary gear, which is associated with the two adjacent to the transmission shaft idler gears of the transmission. The planetary gear elements are advantageously placed to save space radially within teeth of the idler gears. In addition, the planetary gear elements are advantageously radially nested between the two adjacent idler gears. A centrally arranged sun gear of the planetary gear is advantageously made hollow. In the cavity advantageously at least one device described above is housed. Advantageously, in the cavity radially inside the sun gear and between the idler gears, two devices for synchronization, which are described above, are accommodated in a particularly space-saving manner.

According to a further embodiment of the method, a biasing torque or preload torque is applied to the idler gears to counteract undesirable noise during operation. The preload torque or prestressing torque is applied, for example, by an actuator system or by a previously described anti-rattle device and / or pretensioning device.

If appropriate, the invention also relates to an actuating device, an actuating element, a blocking mechanism, a ratchet device, a prestressing device, a latching device, a synchronizing device, in particular a synchronizing sleeve and / or a synchronizing link, and / or a coupling device, in particular a coupling sleeve and / or a coupling device Coupling link, for a previously described device for synchronization. The parts mentioned are separately tradable.

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. FIG. 1 shows a conventional device for synchronizing;

Figure 2 is a schematic representation of an axially short device for

Synchronize; a somewhat more detailed, but still simplified representation of an axially short design device for synchronization with a slotted guide; a view of the device of Figure 3 with a view of the slotted guide; similar representations as in Figures 3 and 4 with an additional spring ring and indicated roof slopes or guide slopes; a transmission with two transmission input shafts, on which two pairs of fixed gears are arranged, and a transmission output shaft with two pairs of loose wheels, which mesh with the fixed wheels, partially in section; an enlarged detail of Figure 7; an exploded view of a section of Figure 8; an exploded view of a synchronizer and a clutch device, and an exploded view of the transmission output shaft with two loose wheels and two synchronizing devices; a view similar to Figure 8 with a locking mechanism that prevents simultaneous insertion of two courses; the view of a section along a line 200 in Figure 12, wherein a viewing direction is indicated by two arrows 201, 202, with the blocking mechanism; the Figures 14 to 17 the locking mechanism or locking mechanism of Figures 12 and 13 in different switching states;

Figure 18 is a perspective view of an actuating element

FIG. 12;

FIG. 19 is a perspective view of a loose-wheel assigned to the actuating element from FIG. 18; Figure 20 is an exploded view of two idler gears with an actuator and the locking mechanism or locking mechanism;

Figure 21 is a similar exploded view as in Figure 20 additionally with a transmission output shaft;

Figure 22 is a similar view as in Figure 12 with an additional

Anti-rattle device and an additional locking device and Figure 23 shows a loose wheel with an actuating device and an additional spring device in half section.

In Figure 2, a device 10 for synchronizing between a transmission shaft and a loose wheel, which is rotatably mounted on the transmission shaft, shown greatly simplified. The device 10 comprises two sub-devices 1 1, 12, which are radially interleaved and arranged overlapping in the axial direction. The axial direction corresponds to a horizontal line in FIG.

The sub-device 1 1 is combined with a synchronizer 15. The sub-device 12 is combined with a coupling device 16. The synchronizer 15 and the coupling device 16 are also radially interleaved and arranged overlapping in the axial direction. An actuating path during synchronization is indicated in FIG. 2 by an arrow 17. By an arrow 18, an actuating path during coupling is indicated in Figure 2. The corresponding displacements of the sub-devices 1 1, 12 during synchronization and coupling are indicated in Figure 2 by dashed lines.

By a double arrow 19, the axial space requirement for the device 10 in Figure 2 is indicated. In order to reduce the axial space requirement, the functions of a synchronization operation and a Verkoppeins or Kuppeins are separated from each other and radially arranged one above the other.

FIG. 1 also shows in principle a conventional device 20 for synchronization for comparison with FIG. The device 20 comprises a synchronizing device 25 and a coupling device 26. The synchronizing device 25 is spaced apart from the coupling device 26 in the axial direction. By an arrow 27 an actuating path during synchronization is indicated. By an arrow 28, an actuating path during coupling is indicated.

By a double arrow 29, an axial length of the device 20 with the synchronizer 25 and the coupling device 26 is indicated. The corresponding displacement paths of the device 20 during synchronization and coupling are indicated in FIG. 1 by dashed lines.

In the device 20, a sliding sleeve is first moved axially, wherein the sliding sleeve presses first on a synchronizer ring. Once a synchronism of a loose wheel and a gear shaft is reached, the sliding sleeve can be pushed over the synchronizer ring on a coupling body.

In Figure 3, a device 30 for synchronization is shown in more detail than in Figure 2, but still simplified. The device 30 serves to synchronize between a gear shaft 31 and a loose wheel 32. The idler gear 32 is rotatably mounted on the gear shaft 31 by means of a bearing device 33.

An actuating device 35 for actuating the device 30 advantageously comprises a planetary gear element of a planetary gear (not shown in Figure 3). The device 30 comprises a synchronizer ring package 40, a synchronizer 41 and a coupling device 42. The synchronizer 41 and the coupling device 42 are arranged axially overlapping and radially nested. A sliding block 43 is provided radially inwardly of the synchronizer 41. A sliding block 44 is provided radially on the outside of the coupling device 42.

In Figure 4 it can be seen that the sliding blocks 43, 44 are guided in guide grooves 46, 47 or slide tracks of a slide guide 45. An arrow 48 in FIG. 4 indicates a movement of the slotted guide 45 when actuated by the actuating device (35 in FIG. 3).

The axial displacement paths of the synchronizing device 41 and the coupling device 42 when actuated by the actuating device 35 are indicated by dashed lines in FIG. When actuated by the actuator 35 relative rotations are converted into axial movements of the synchronizer 41 and the coupling device 42.

The term axially refers to an axis of rotation 49 of the transmission shaft 31 within the scope of the claimed device 10, 30. In the transmission shaft 31 is a transmission output shaft of a gear equipped with the idler gear 32.

Referring now to Figures 5 and 6, there is shown a synchronizing apparatus 50 which is similar to the synchronizing apparatus 30 shown in Figures 3 and 4. To denote the same or similar parts, the same reference numerals as in Figures 3 and 4 are used. To avoid repetition, reference is made to the preceding description of Figures 3 and 4. In the following, only the differences between the devices 30 and 50 will be discussed. In FIG. 5, roof pitches or guide bevels 51, 52 are indicated on the synchronizer 41 and on the synchronizer ring packet 40. In addition, 31 sloping slopes or guide slopes 53, 54 are indicated on the coupling device 42 and the transmission shaft. Finally, a spring ring between the synchronizer 41 and the synchronizer ring packet 40 is indicated by a circle 55. When the device 50 is actuated by the actuating device 35, power is transmitted from the synchronizer 41 to the synchronizer ring packet

When synchronizing, a synchronizing ring of the synchronizing ring package 40 can rotate relative to the synchronizing device 41 by the width of a roof slope or guide bevel 51, 52 and thus prevent a further displacement of the synchronizing device 41. When synchronism of idler gear 32 and gear shaft 31 is reached, the synchronizer 41 rotates a synchronizer ring of the synchronizer ring packet 40 back and shifts further in the axial direction, but only by the amount of a wear reserve.

After unlocking, the coupling device 42 can be pushed onto a rotary transmission element 58, which is also referred to as a coupling body. The rotation transmission element 58 is integrally connected in Figure 5 with the transmission shaft or transmission output shaft 31. The axial movements of the synchronizer 41 and the coupling device 42 are controlled by the slide guide (45 in Figure 6). To illustrate the sliding blocks 43, 44, for example, pins are attached to the synchronizer 41 and the coupling device 42, which engage in the guide grooves or cam tracks 46, 47 of the slide guide 45. Upon actuation / rotation of the slotted guide 45 is first the synchronizer

41 axially displaced over an inclined portion of the slide track 46. The pin 44 of the coupling device 42 runs in a tangential path and is therefore not axially displaced. The slide track 47 is indicated by dashed lines in Figure 6.

As soon as the pin 43 of the synchronizing device 41 changes from its oblique section into a tangential section of the slide track 46, the pin 44 of the coupling device 42 comes into an oblique section of the guide track 47 and displaces the coupling device 42 axially.

In Figure 7, a transmission 60 with an inner transmission input shaft 61 and an outer transmission input shaft 62 is shown partially in section. At a drive output 64, an output stage 65 is arranged to a differential (not shown). The power amplifier 65 is referred to as Final Drive.

On its right side in FIG. 7, the transmission 60 has two bearing points 66, 67. At the transmission output 64, the transmission 60 has a bearing journal 68. On the inner transmission input shaft 61 two fixed wheels 73, 74 are arranged. On the outer transmission input shaft 62, two fixed wheels 71, 72 are arranged.

The fixed gear 71 meshes, for example, to illustrate a first gear, with a loose wheel 75. The fixed gear 72 meshes, for example, to represent a third gear, with a loose wheel 76. The fixed gear 73 meshes, for example, to display a second gear, with The idler gear 74 meshes, for example, to illustrate a fourth gear, with a loose wheel 78. The idler gears 75 to 78 are rotatably mounted by means of suitable storage facilities on a transmission output shaft 80, which is also referred to as transmission shaft 80 shortened. The idler gears 75, 76 represent a first idler gear pair. The idler gears 77, 78 represent a second idler gear pair. The first idler gear pair 75, 76 are associated with two devices 81, 82 for synchronization. To actuate the devices 81, 82 for synchronization is an actuator 85. The idler gear 77, 78 are associated with corresponding devices which are actuated by an actuator 86. The actuator 85 includes a planetary gear 84. The planetary gear 84 is disposed in a cavity radially inwardly and axially between the adjacent idler gears 75, 76. By the planetary gear 84, the axial space can be reduced via the actuator 85 in the transmission. In Figure 8 it can be seen that the planetary gear 84 includes a ring gear 87, a sun gear 90 and planetary gears 91, 92 (see Figure 1 1). The planet gears 91, 92 are rotatably mounted on a planet carrier 93 with a web. The sun gear 90 meshes with the planet gears 91, 92, which in turn mesh with the ring gear 87. The planet carrier 93 with the web rotates in the unactuated state of the devices 81, 82 substantially synchronously with the idler gear 75. The sun gear 90 rotates in the unactuated state of the devices 81, 82 substantially synchronously with the idler gear 76th

The term substantially synchronous in this context also means that the sun gear 90 and the planet carrier 93 can rotate with the web after actuation by the actuator 85 to a limited extent relative to the idler gears 75, 76 to provide a clutch, shift - and / or synchronizing to trigger.

Upon actuation of the actuator 85, the ring gear 87 is rotated. In the unactuated state of the actuator 85, the ring gear 87 is fixed. Then the ring gear 87 has the same speed as the gear 60, which is fixed. Thus, the ring gear 87 in the unactuated state of the actuator 85 has a speed of zero.

When the ring gear 87 is rotated, then either the planetary carrier 93 rotates with the web or the sun or the sun gear 90 relative to the associated idler gear 75, 76. This relative rotation is then used to actuate one of the devices 81, 82 for synchronization.

The idler gear 75 is rotatably supported by a bearing device 88 on the transmission output shaft 80. The idler gear 76 is rotatably supported by a bearing device 89 on the transmission output shaft 80. The planet carrier 93 with the web is coupled by a coupling element 94 to the device 81. The coupling element 94 is part of the planetary carrier 93, which is also referred to as a web. The sun gear 90 is coupled to the device 82 via a coupling element 95. A rotation transmission element 98 is rotatably connected via a spline 101 to the transmission shaft 80. The spline 101, which is also referred to as a toothing 101 shortened, allows torque transmission between the transmission shaft 80 and the rotation transmission member 98, and vice versa. The rotation transmission member 98 is radially outwardly at its ends with guide slopes 99, 100 equipped. The guide bevels 99, 100 cooperate with complementary guide bevels, which will be explained below. The guide bevel 99 is associated with the left in Figure 8 device 81. The guide slope 100 is assigned to the device 82 arranged on the right in FIG.

The rotational transmission member 98, which may also be referred to as a coupling body, extends radially outwardly into a cavity which is recessed between the two idler gears 75, 76. Radially outward, the rotation transmission element 98 between the guide slopes 99, 100 a toothing 102, which is also designed as a sliding toothing.

In the sliding teeth 102 radially outwardly arranged synchronizer rings 121, 131 of synchronizer ring packets 120, 130 mounted. By the sliding teeth 102, a torque transmission between the rotation transmission member 98 and the outer synchronizer rings 121, 131 allows, and vice versa. An axial displacement of the outer synchronizer rings 121, 131 relative to the rotation transmission element 98 is prevented by a retaining ring, in particular a spring ring or detonator ring, and axial abutment surfaces on the rotation transmission element or coupling body 98.

The term axial refers to an axis of rotation 103 of the gear shaft 80 or of the loose wheels 75, 76. Axial means in the direction or parallel to the axis of rotation 103. Analogously, the term radially extends transversely to the axis of rotation 103.

The devices 81, 82 are particularly space-saving in the cavity between the idler gears 75, 76 housed. Only the actuating device 85 for the two devices 81, 82 protrudes radially outward out of the cavity between the idler wheels 75, 76. As a result, a cooperation of the actuating device 85, in particular the ring gear 87 of the planetary gear 84, with a corresponding actuator device, for example a gear, which is driven by an electric motor, in a simple manner allows. The devices 81, 82 each comprise a synchronizing device 104, 106 and a coupling device 105, 107. The device 81 with the synchronizing device 104 and the coupling device 105 arranged on the left in FIG. 8 is associated with the idler gear 75, which is likewise arranged on the left in FIG. The device 82 with the synchronizing device 106 and the coupling device 107 arranged on the right in FIG. 8 is assigned to the idler gear 76 likewise arranged on the right in FIG.

The synchronizers 104, 106 and the coupling devices 105, 107 are combined with slotted guides 108, 109. The slide guides 108, 109 serve to convert relative rotations defined into axial movements, which are used to synchronize and couple or couple the respective idler gear 75, 76 with the gear shaft 80.

The coupling devices 105, 107 each comprise a coupling sleeve 1 10, 1 12 and a coupling link 1 1 1, 1 13. The synchronizers 104, 106 each comprise a synchronizing sleeve 1 14, 1 16 and a synchronizing linkage 1 15, 1 17.

The coupling sleeve 1 10, the clutch link 1 1 1, the synchronizing sleeve 1 14 and the Synchronisierkulisse 1 15 of the left in Figure 8 arranged device 81 are radially interleaved and arranged overlapping in the axial direction.

The coupling sleeve 1 12, the clutch linkage 1 13, the synchronizing sleeve 1 16 and the synchronizing linkage 17 of the device 82 arranged on the right in FIG. 8 are likewise radially interleaved and arranged in an overlapping manner in the axial direction.

The synchronizer ring packets 120, 130 each comprise a total of four synchronizer rings 121 to 124, 131 to 134. The synchronizer rings 121 to 124 of the device 81 arranged on the left in FIG. 8 are arranged radially outside the synchronizer 104 and the clutch device 105. However, the synchronizer rings 121 to 124 are arranged in the axial direction overlapping the clutch device 105 and the synchronizer 104. Analogously, the synchronizer rings 131 to 134 of the device 82 arranged on the right in FIG. 8 are arranged radially outside the synchronizing device 106 and the coupling device 107. However, the synchronizer rings 131 to 134 are arranged axially overlapping with the synchronizer 106 and the clutch device 107.

The radially outer synchronizer rings 121, 131 are in the middle between the devices 81, 82 to each other and engage together in the teeth 102 of the rotation transmission member 98 a. The radially inwardly arranged synchronizer rings 124, 134 of the synchronizer ring packets 120, 130 are, as will be explained below, with the synchronizing sleeves 1 14, 1 16 coupled.

Between the synchronizing sleeves 1 14, 1 16 and the radially inner synchronizing rings 124, 134 is in each case a spring means in the form of a spring ring 1 18, 1 19 arranged. The spring means with the spring rings 1 18, 1 19 serve to synchronize, as will be explained below.

In Figure 9, parts of the devices 81, 82 are shown in perspective. The parts of the device 82, which is arranged on the right in FIG. 8 and assigned to the loose wheel 76, are additionally shown in exploded view in FIG. In Figure 10, the parts of the device 82, which are shown partially together in Figure 9, shown in exploded view.

In Figure 9 it can be seen that on the radially inner synchronizer ring 134 of the synchronizer ring packet 130 radially inward guide elements 140 are provided. The guide elements 140 each have two guide slopes 141, 142. At the Synchronisierhülse 1 16 complementary trained guide elements 145, each with two guide slopes 146, 147 are provided. The guide elements 140 on the radially inner synchronizer ring 134 are designed as projections which project radially inwards. The guide elements 145 on the synchronizing sleeve 1 16 are designed as recesses in the synchronizing sleeve 1 16, which are open in Figure 9 on their left side. By the engagement of the guide elements 140 in the guide elements 145, a coupling of the synchronizing sleeve 1 16 with the radially inner synchronizing ring 132 is made possible. By the spring ring 1 19 a certain bias for synchronizing between the synchronizing sleeve 1 16 and the radially inner synchronizer ring 134 is generated.

On the right side in FIGS. 9 and 10, the synchronizing sleeve 16 has a total of four anti-rotation elements 151 to 154. The anti-rotation elements 151 to 154 extend in the axial direction. The coupling sleeve 1 12 has on its right in Figures 9 and 10 page four Umgriffe 155 to 158 on.

The Umgriffe 155 to 158 on the coupling sleeve 1 12 in the axial direction stops for the Synchronisierkulisse 1 17 represents. In addition, the Umgriffe 155 to 158 on the coupling sleeve 1 12 in the circumferential direction with the anti-rotation elements 151 to 154 on the synchronizing sleeve 1 16 act together.

A total of four driver elements 161 to 164, which extend in the axial direction, are provided on the synchronizing link 17 on the right-hand side in FIGS. 9 and 10. In Figure 9 it can be seen that the Umgriffen 155 to 158 of the coupling sleeve 1 12 are arranged in the circumferential direction between one of the anti-rotation elements 151 to 154 of the synchronizing sleeve 1 16 and one of the driving elements 161 to 164 of the Synchronisierkulisse 1 17. At the Synchronisierkulisse 1 17, a guide pin 166 is further attached. The guide pin 166 is radially inwardly from the Synchronisierkulisse 1 17 from that he engages in a slide track, which, as seen in Figure 10, outside of the synchronizing sleeve 1 16 is combined with an external thread 171. A complementary trained internal thread 172 is formed radially inwardly of the Synchronisierkulisse 1 17.

The external thread 171 is delimited on the synchronizing sleeve 16 on the right-hand side in FIG. 10 by a slide track 173 which, in contrast to the outside wind 171 has no slope. About the engaging in the slide track 173 guide pin 166 threading the threads 171, 172 is simplified.

The threads 171, 172, together with the guide track 173 and the guide pin 166 166 form part of the slide guide 109. The slide guide 109 may alternatively or additionally include ramps.

On the coupling sleeve 1 12, an external thread 175 is provided, which cooperates with a complementary internal thread 176, which is provided on the coupling link 1 13. Instead of the threads 175, 176 ramps can be attached to represent the slide guide 109.

FIG. 11 shows the transmission shaft 80 with the two idler wheels 75, 76, with the Final Drive 65 and with the two devices 81, 82 accommodated between the idler wheels 75, 76 for synchronization in an exploded view. The devices 81, 82 are actuated via the ring gear 87 of the planetary gear. For this purpose, the ring gear 87 has a toothing on the outside.

A rotary input via the planetary gear 84. The left device 81 for synchronization is actuated by the planet carrier 93. The right-hand device 82 for synchronization is actuated by the sun gear 90 of the planetary gear 84.

The coupling sleeve 1 10, 1 12 and the respective synchronizing sleeve 1 14, 1 16 are secured on the associated idler gear 75, 76 against rotation. If, for actuation, the planet carrier 93 or the sun gear 90 is rotated relative to the idler gear 75, 76, the synchronizing sleeve 1 14, 1 16 is moved axially in the direction of the radially inner synchronizing ring 124, 134 via the slotted guides 108, 109 and the threaded lamps.

In this case, the spring ring 1 18, 1 19 initially provides for an axial contact pressure of the radially inner synchronizer ring 124, 134, so that the radially inner synchronizer ring 124, 134 can rotate within a limited circumferential clearance. This is also called Ansynchronisieren. The guide bevels 141, 142 on the radially inner synchronizer ring 124 come to lie in front of the guide bevels 146, 147 of the synchronizing sleeve 1 16 during the synchronization. Upon further actuation, the synchronizing sleeve 16 presses the radially inner synchronizing ring 124 via the guide bevels 146, 147 and 141, 142.

At synchronous speed of idler gear 75 and gear shaft 80 of the synchronizer ring 124 can be rotated back. Upon further actuation, the guide pin 166 arrives at the synchronizing linkage 17 in the guide track 173 without incline and the thread 171, 172 has moved apart.

In this position, the driver elements 161 to 164 of the Synchronisierkulisse 1 17 come to the grips 155 to 158 of the clutch linkage 1 13 to the system, as can be seen in Figure 9. Upon further actuation, only the coupling sleeve 1 12 is then axially displaced by turning the coupling slot 1 13 to its final position.

In Figure 9 is indicated by an arrow 181, as the driver elements 161 to 164 of the synchronizing gate 1 17 abut the grips 155 to 158 of the coupling slot 1 13. Thereafter, then the inner parts, so the clutch link 1 13 and the coupling sleeve 1 12, set in rotation.

An arrow 182 indicates in FIG. 9 that the anti-rotation elements 151 to 154 on the synchronizing sleeve 161 prevent the synchronizing sleeve 16 from being twisted during rotation. By the anti-rotation elements 151 to 154, the synchronizing sleeve 1 16 is practically held.

FIG. 12 shows a similar detail as in FIG. 8 with a blocking mechanism 207. The coupling element 94 represents a left-hand actuating element of the actuating device 85 in FIG. 12. The coupling element 95 represents a right-hand actuating element of the actuating device 85 in FIG. 12. The actuating element 94 is assigned the idler gear 75 on the left in FIG. The actuating element 95 is associated with the right idler gear 76 in FIG. In FIG. 13, the view of a section along a line 200 in FIG. 12 is shown enlarged, with arrows 201, 202 indicating the viewing direction. In the sectional view it can be seen that the actuating device 85 is designed as an actuating wheel 205 with an external toothing. An inner portion 206 of the idler gear 76 is shown broken away in the illustrated sectional view to make the blocking mechanism 207, also referred to as a locking mechanism, visible.

As can be seen in FIG. 13, the blocking mechanism or locking mechanism 207 comprises on the actuating element 95 a ramp-shaped stop 208 with a ramp 210. The ramp-shaped stop 208 of the actuating element 95 interacts with a counter-stop 209 in the form of a recess in the inner region 206 of the idler gear 76 , The interaction between stop 208 and counter-stop 209 is illustrated in FIGS. 14 to 17. In a stationary state, when not being switched, rotate the actuators 94, 95 of the synchronizers, here planet carrier or sun, with the same rotational speed as the respective idler gears 75, 76. Between the actuators 94, 95 and the idler gears 75, 76 are Stops for both directions of rotation.

In Figure 13 it can be seen that the stop 208 on the actuating element 95 in one of the two directions of rotation, down in Figure 13, formed as a ramp 210 and is thereby traversable. If a circuit is now introduced via the actuating wheel 205, one of the two actuating elements 94, 95 rotates relative to the associated idler gear 75, 76.

In the figures 14 to 16, the movements of the actuating elements 94, 95 relative to the associated idler wheels 75, 76 are shown schematically. In Figure 15, the neutral position is shown. The actuators 94, 95 are in a basic position to the idler gears 75, 76, in which all stops 208, 209 coincide.

When the actuating wheel 205 is rotated, a torque is introduced into the two actuating elements 94, 95 via the planetary gear. The torques in the actuators 95, 95 are respectively opposite, so that, for example, the left in Figures 14 to 16 actuator 94 relative to the idler gear 75 wants to move down, and the right in Figures 14 to 16 actuator 95 relative to the idler gear 76th up.

Since between the right actuating element 95 and the right idler gear 76 but not overrun stop 208 and counter-stop 209 acts, the right-hand actuator 95 can not escape. The left actuator 94 must therefore drive over the ramp-shaped stop. In this case, the left actuating element 94 displaces in the axial direction by the width of the stop covering, as indicated in FIG. 14 by arrows 21 1, 212.

The mutually facing end faces of the actuating elements 94, 95 approach each other. The relative rotation between the actuator 94 and the idler gear 75 is used to actuate the synchronization and engage the gear.

In Figure 16, the right idler gear 76 is connected. The left idler gear 75 is engaged with the left operating member 94.

To lay out the gear, the operating wheel 205 is rotated in the opposite direction. Accordingly, the torsional moments in the actuators 94, 95 now also act in the other direction. Now it must be achieved that the first gear is laid out, and not the other gear is additionally inserted.

In FIG. 17, arrows 124, 215 symbolize the peripheral force or the torque in the actuating elements 94, 95. In the right-hand actuating element 95 in FIG. 17, the torque is supported on the ramp-shaped stop 208 or counter-stop 209. The axially displaced left actuating element 94 prevents the right-hand actuating element 95 from being able to drive over the ramp-shaped stop 210, since the two facing end faces of the actuating elements 94, 95 touch each other. In Figures 18 and 19, the actuator 95 and the idler gear 76 are shown in perspective. In FIG. 18, double arrows 218 to 220 indicate that stops 221, 222, 223 and 208 are distributed unevenly over a circumference of actuating element 95. As a result, a possibly largest possible angle of rotation on the actuating element 95 can be achieved in an advantageous manner, for example one hundred and eighty degrees, which leads to lower tooth forces on the planet.

With a uniform distribution of the attacks, the stops would come to rest again after the rotation about the pitch angle and the axial displacement would no longer be ensured. Due to the uneven distribution, it is possible that only after a full turn all attacks or counter-attacks are superimposed again.

Figures 20 and 21 show the construction in exploded views. In FIG. 20, it can be seen that an inner region 226 of the idler gear 75 is provided with counterstops 229 in the same manner as the inner region 206 of the idler gear 76. FIG. 21 shows the associated ramp-shaped stops 228 with the ramps 230 on the actuating element 94, which is associated with the idler gear 75. FIG. 22 shows a similar detail as in FIG. 12 with a latching device 238 and an anti-rattle device 244. The anti-rattle device 244 comprises a biasing device 233, by which the actuating element 95 is biased against the associated idler gear 76 in the axial direction. The biasing device 233 comprises a plate-spring-like spring 234. The spring 234 is radially outwardly supported on a support ring 235, which in turn engages in an annular groove of the idler gear 76. The spring 234 is supported radially inwardly on a support structure 236 which is provided on the actuating element 95. To eliminate unwanted gear rattle, make sure that the no-load gear teeth roll neatly and do not bounce from one edge to the other within the backlash. For this purpose, the gears of a idler gear pair 75, 76 are slightly biased by a preload torque. The preload torque is, for example, by an unillustrated Ak- tormotor applied to the actuator 205. The preload torque is supported via the actuating element 205 and the anti-rattle device 244 on the idler gear 76 or via a suitable stop on the idler gear 75. Alternatively, the preload torque may be generated by a detent mechanism 238, also referred to as detent 238.

The latching device 238 comprises a latching body 239, which essentially has the shape of a spherical section. The locking body 239 engages in a complementarily shaped recess in the actuating wheel 205 of the actuating device 85. By a spring 240 of the locking body 239 is biased against the actuating wheel 205. The spring 240 is supported on a fixed housing (not shown in FIG. 22). An icon to the left of the actuating wheel 205 indicates in FIG. 22 that the actuating wheel 205 can not move to the left in the axial direction.

The latching device comprises at least one not shown Rastierungsrampe and / or inclined surface. The position of the Rastierungsrampe and / or the inclined surface is selected so that the locking body 239 rests in the circumferential direction of the Rastie- rungsrampe or the inclined surface when the anti-rattle device 244 and the biasing means 233 the ramp-shaped stop 208 and the counter-stop 209 together.

FIG. 23 shows a pretensioning device 245. The biasing device 245 includes a spring 246 which is attached with its free ends on the idler gear 76. The spring 246 has a centrally projecting nose 247 in FIG. The nose 247 engages in a recess 248, which is recessed in the actuating element 95. LIST OF REFERENCES

Device for synchronization

partial device

synchronizer

coupling device

arrow

double arrow

Device for synchronization

synchronizer

coupling device

arrow

double arrow

Device for synchronization

gear shaft

Losrad

Storage facility

actuator

Synchronizer ring package

synchronizer

coupling device

sliding block

link guide

Guide groove (slide track)

arrow

axis of rotation

Device for synchronization Guide bevel Guide bevel

guide slope

circle

Rotary transmission element gear

inner transmission input shaft outer transmission input shaft transmission output

final stage

depository

pivot

fixed gear

Losrad

Transmission output shaft

Device for synchronizing device for synchronizing planetary gear

actuator

ring gear

Storage facility

sun

planet

planet 93 planet carrier

94 Coupling element -> Actuator (Ii)

95 Coupling element -> Actuator (right)

98 Rotary transmission element

99 guide slope

100 guide slope

101 toothing

102 toothing

103 axis of rotation

104 Synchronizer

105 coupling device

106 Synchronizer

107 coupling device

08 Sliding guide

109 Sliding guide

1 10 coupling sleeve

1 1 1 Coupling link

1 12 Coupling sleeve

1 13 Coupling link

1 14 synchronizing sleeve

1 15 Synchronizing scenery

1 16 synchronizing sleeve

1 17 Synchronizing scenery

1 18 spring washer

9 spring washer

120 synchronizer ring package

121 synchronizer ring

122 synchronizer ring

123 synchronizer ring

124 synchronizer ring

130 synchronizer ring package

131 synchronizer ring

132 synchronizer ring

133 synchronizer ring 134 synchronizer ring

140 guide element

141 guide slope

142 guide slope

145 guide element

146 guide slope

147 guide slope

151 Anti-rotation element

152 anti-rotation element

153 anti-rotation element

154 anti-rotation element

155 Umgriff

156 Umgriff

157 Umgriff

158 Umgriff

161 driver element

162 driver element

163 driver element

164 Driving element 166 Guide pin

171 external thread

172 female thread

173 slide track

175 external thread

176 internal thread

181 arrow

182 arrow

201 arrow

202 arrow

205 operating wheel

206 indoor area

207 locking mechanism

208 ramp-shaped stop

209 counter-attack 210 ramp

21 1 arrow

212 arrow

214 arrow

215 arrow

218 double arrow

219 double arrow

220 double arrow

221 stop

222 stop

223 stop

226 indoor area

228 ramp-shaped stop

229 Counter-attack

230 ramp

233 biasing device

234 spring

235 support ring

236 support structure

238 latching device

239 catch body

240 spring

244 anti-rattle device

245 biasing device

246 spring

247 nose

248 recess

Claims

claims

1 . Apparatus (10; 50; 81,82) for synchronizing between a transmission shaft (31; 80) and two idler wheels (75,76) rotatably mounted on the transmission shaft (31; 80) with actuator means (85) therethrough characterized in that the actuating device (85) comprises two actuating elements (94, 95), which are rotatable relative to one another and assigned to the idler wheels, having a blocking mechanism (207) which prevents a simultaneous engagement of two gears.

2. Apparatus according to claim 1, characterized in that on the actuating elements (94,95) ramp-shaped stops (208,228) are provided, the rotation of the actuating elements (94,95) relative to the associated idler gear (75,76) only in one Allow direction of rotation.

3. Apparatus according to claim 2, characterized in that over a circumference of the actuating elements (94,95) a plurality of ramp-shaped stops (208,221 -223) are distributed unevenly.

4. Device according to one of the preceding claims, characterized in that the actuating elements (94,95) are axially displaceable relative to each other so that an actuating element (94,95) of a with the transmission shaft (31; 80) coupled idler gear (75,75 ) prevents the simultaneous insertion of a second gear.

5. Apparatus (10, 50, 81, 82) for synchronizing between a transmission shaft (31, 80) and two idler wheels (75, 76), which are rotatably mounted on the transmission shaft (31, 80), with an actuating device (94, 95), in particular according to one of the preceding claims, characterized in that the actuating device (94,95) comprises two actuating elements (94,95) which can be rotated relative to one another and are assigned to the idler wheels (75,76) with an anti-scrubbing device. leinrichtung (244).

6. Apparatus according to claim 5, characterized in that the anti-rattle device (244) comprises a biasing means (233; 245) by which at least one of the actuating elements (94,95) is biased in a particular axial or radial direction.

7. The device according to claim 5 or 6, characterized in that the antira- sseleinrichtung (244) comprises a latching device (238) which is arranged between at least one of the actuating elements (94,95) and a fixed housing body.

8. Apparatus according to claim 5 or 6, characterized in that the antira- sseleinrichtung comprises a biasing means (245) which is effective between at least one of the actuating elements (95) and the associated idler gear (76).

9. gearboxes (60) with pairs of wheels, each comprising a fixed gear (71-74) and a loose wheel (75,76) for representing gears in the gearbox (60), characterized in that a device (10; 50; 81 , 82) for synchronization according to one of the preceding claims, two on a transmission shaft (31; 80) adjacent idler gears (75,76) of the transmission (60) is arranged.

A method of synchronizing between a gear shaft (31; 80) and two idler gears (75,76) rotatably mounted on the gear shaft (31; 80) with a device (10; 50; 81,82) according to any one of Claims 1 to 8, in particular in a transmission (60) according to claim 9, characterized in that a synchronizer and a coupling device by a relative movement of the actuator (94,95) to the idler gear (75,76) are successively shifted so that the idler gear (75,76) is coupled to a corresponding fixed gear (71-74), wherein in particular a biasing moment is applied to the idler gears (75,76) to counteract undesirable noise during operation.