Device and method for synchronizing between a transmission shaft and two loose gears

Abstract

Device (10; 50; 81, 82) for synchronizing between a transmission shaft (31; 80) and two loose gears (75, 76) rotatably arranged on the transmission shaft (31; 80), comprising an actuating device (85) comprising two actuating elements (94, 95) rotatable relative to each other and associated with the loose gears (75, 76), with an anti-rattle device (244), characterized in that the anti-rattle device (244) comprises a detent device (238) arranged between at least one of the actuating elements (94, 95) and a stationary housing body, and a locking mechanism (207) that prevents the simultaneous engagement of two gears.

Description

[0001] The invention relates to a device and a method for synchronizing between a transmission shaft and two idler gears rotatably mounted on the transmission shaft, with an actuating device. The invention further relates to a transmission with gear pairs, each comprising a fixed gear and an idler gear to represent gears in the transmission.

[0002] From the German patent specification DE 199 82 494 C1 a synchronizing device for a manual transmission is known with a synchronizer body arranged on a transmission shaft in a rotationally fixed manner in the circumferential direction of the transmission shaft, with a sliding sleeve arranged on the synchronizer body so as to be displaceable along the longitudinal center axis of the transmission shaft, with at least one gear wheel which is rotatably mounted on the transmission shaft and adjoins the synchronizer body, which gear wheel is connected to a clutch body or is provided with clutch teeth and can be coupled to the synchronizer body via the clutch body or the clutch teeth by means of the sliding sleeve.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 can be fixed relative to one another in the circumferential direction by means of an indexing, wherein the indexing is formed from at least one projection arranged on the synchronizer ring and extending substantially in the axial direction, which projection engages in at least one recess of the synchronizer body, wherein the recess has at least one oblique surface section on which the projection rests in a sliding manner when the synchronizer ring is rotated relative to the synchronizer body.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 clutch body and a synchronizer body, wherein at least one inclined surface is provided on the synchronizer body and on the synchronizer ring, on which the synchronizer body and the synchronizer ring are in surface contact, and at least one elastic element is provided which acts between the synchronizer body and the synchronizer ring and generates a force acting in the circumferential direction, which presses the inclined surfaces of the synchronizer body and the synchronizer ring against one another in such a way that a force component acting on the synchronizer ring in the direction of the synchronizer body is generated.

[0003] Another relevant synchronization device is known from DE 101 01 864 A1.

[0004] The object of the invention is to improve the shifting performance during operation of a transmission with gear pairs, each comprising a fixed gear and a loose gear to represent gears in the transmission, and with a device for synchronizing between a transmission shaft and two loose gears, which are rotatably arranged on the transmission shaft, with an actuating device.

[0005] The object is achieved in a device for synchronizing between a transmission shaft and two idler gears which are rotatably arranged on the transmission shaft, with an actuating device by the characterizing features of claim 1.

[0006] In a further development, it can be provided that the actuating device comprises two actuating elements which are rotatable relative to one another and assigned to the idler gears, each having a blocking mechanism which prevents two gears from being engaged simultaneously. The synchronization device advantageously comprises a planetary gear within the idler gears of the transmission. The planetary gear is preferably arranged axially between the two idler gears. A relative rotation of an actuating element of the planetary gear, for example a sun gear or a planet carrier of the planetary gear, creates a synchronization of the corresponding idler gear. The actuating elements can be coupled to the assigned idler gear, for example via stops, whereby one or the other idler gear is released from the stop(s) only in a given direction of rotation.The claimed locking mechanism ensures in a simple manner that only one direction of rotation is possible at a time.

[0007] This reliably prevents unwanted simultaneous engagement of two gears.

[0008] A preferred embodiment of the device is characterized in that ramp-shaped stops are provided on the actuating elements, which only allow rotation of the actuating elements relative to the associated idler gear in one direction of rotation. The ramp-shaped stops interact with counter-stops provided on the respective associated idler gear. This easily blocks rotation in the other directions of rotation.

[0009] A further preferred embodiment of the device is characterized in that several ramp-shaped stops are unevenly distributed over the circumference of the actuating elements. This allows for larger angles of rotation to be easily achieved after the actuating element has struck the associated idler gear until it strikes again.

[0010] A further preferred embodiment of the device is characterized in that the actuating elements are axially displaceable relative to one another such that an actuating element of an idler gear coupled to the transmission shaft prevents the simultaneous engagement of a second gear. The axial displacement of one actuating element presses the other actuating element against the associated idler gear such that the ramp-shaped stops engage the counter-stops in recesses of the associated idler gear.

[0011] In a device for synchronizing a transmission shaft with two idler gears rotatably mounted on the transmission shaft, comprising an actuating device, the above-mentioned object is achieved in that the actuating device comprises two actuating elements, each rotatable relative to the idler gears, with an anti-rattle device. The actuating elements are subjected to a preload torque, for example, via a suitable actuator. This reliably prevents unwanted noise during operation of a transmission with the synchronizing device.

[0012] A further preferred embodiment of the device is characterized in that the anti-rattle device comprises a pretensioning device by which at least one of the actuating elements is pretensioned in an axial direction. The pretensioning device comprises, for example, a spring device. The spring device comprises, for example, at least one spring that is clamped, preferably in an axial direction, between the actuating element and the associated idler gear. Alternatively or additionally, the spring device can comprise at least one spring that is pretensioned between the actuating device, in particular one of the actuating elements, and a stationary housing, for example, a gear housing.

[0013] The embodiment of the device according to the invention is characterized in that the anti-rattle device comprises a locking device arranged between at least one of the actuating elements and a stationary housing body. A desired preload moment can be generated on the actuating element(s) via the locking device. According to a further embodiment, a locking mechanism on the idler gear and a locking mechanism on the actuating element advantageously interact with a small angular offset to achieve a preload moment via a ramp of one of the two locking mechanisms.

[0014] A further preferred embodiment of the device is characterized in that the anti-rattle device comprises a pretensioning device that acts between at least one of the actuating elements and the associated idler gear. The pretensioning device advantageously comprises at least one spring.

[0015] A synchronizer and a clutch assembly are arranged so that they overlap in the axial direction. The overlapping arrangement of the synchronizer and clutch assembly allows for a simple way to save axial installation space.

[0016] A preferred embodiment of the device is characterized in that the synchronizing device and the clutch device can be actuated via a slotted guide by an actuating device. The slotted guide advantageously serves to convert relative rotations into 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 slotted pin, which is guided in a slotted guide, in particular a slotted track or a groove. The actuating device advantageously comprises a planetary gear element that is rotated or pivoted in a defined manner to generate the relative rotation.

[0017] A further preferred embodiment of the device is characterized in that the coupling device comprises a coupling sleeve that interacts with a coupling slot. The coupling slot advantageously comprises at least one guide groove, at least one thread, and / or at least one ramp. According to a preferred embodiment, the coupling slot comprises a thread and a guide groove. The thread provides a simple way to achieve better force distribution. However, a similarly good force distribution can also be achieved with a ramp or with several ramps distributed in the circumferential direction.

[0018] A further preferred embodiment of the device is characterized in that the synchronizing device comprises a synchronizing sleeve that interacts with a synchronizing link. The synchronizing link advantageously comprises at least one guide groove, 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 link track. A link block, in particular a link pin, engages in the guide groove or link track. The link block, in particular the link pin, significantly simplifies rethreading the thread.

[0019] A further preferred embodiment of the device is characterized in that the synchronizing sleeve and the synchronizing gate are radially nested with the clutch sleeve and the clutch gate. This allows for a simple saving of axial installation space. The clutch sleeve is advantageously arranged radially inward. The synchronizing sleeve is advantageously arranged radially outward. The clutch gate associated with the clutch sleeve, together with the synchronizing sleeve associated with the synchronizing gate, is advantageously arranged radially between them.

[0020] A further preferred embodiment of the device is characterized in that the synchronizing link is coupled to the clutch link in such a way that the synchronizing sleeve can be displaced to a limited extent in the axial direction independently of the clutch sleeve. This enables stable operation of the synchronizing device in a transmission in a simple manner.

[0021] Another preferred embodiment of the device is characterized in that the coupling sleeve is connected to the idler gear in a rotationally fixed manner. The rotationally fixed connection is achieved, for example, by at least one sliding gear. The sliding gear enables axial movement of the coupling sleeve relative to the idler gear in a simple manner.

[0022] In a transmission with gear pairs, each comprising a fixed gear and an idler gear to represent gears in the transmission, the above-mentioned object is achieved alternatively or additionally by arranging two previously described synchronization devices between two adjacent idler gears of the transmission on a transmission shaft. This allows the transmission to be designed particularly compactly. 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 with a hybrid drive.

[0023] In a method for synchronizing between a transmission shaft and two idler gears rotatably mounted on the transmission shaft, using a device described above, particularly in a transmission described above, the above-mentioned object is achieved alternatively or additionally in that the synchronizing device and the coupling device are successively displaced by a relative movement of the actuating device to the idler gear such that the idler gear is coupled to the transmission shaft. The synchronizing movement and the coupling movement are particularly advantageously carried out in the same axial installation space. The coupling of the idler gear to the transmission shaft is advantageously achieved via a rotation transmission element, also referred to as a coupling body.

[0024] A preferred embodiment of the method is characterized in that the synchronization link and the clutch link are actuated by a relative rotation relative to the idler gear. The relative rotation is advantageously provided by a planetary gear element of a planetary gear, which is assigned to the two adjacent idler gears of the transmission on the transmission shaft. The planetary gear elements are advantageously positioned radially within the toothings of the idler gears in a space-saving manner. Furthermore, the planetary gear elements are advantageously nested radially between the two adjacent idler gears. A centrally arranged sun gear of the planetary gear is advantageously hollow. At least one device as described above is advantageously accommodated in the cavity.Advantageously, two previously described synchronization devices are accommodated in the cavity radially inside the sun gear and between the idler gears in a particularly space-saving manner.

[0025] According to a further embodiment of the method, a preload torque or pretension torque is applied to the idler gears to counteract undesirable noise generation during operation. The preload torque or pretension torque is applied, for example, by an actuator or by a previously described anti-rattle device and / or pretension device.

[0026] The invention may also relate to an actuating device, an actuating element, a blocking mechanism, an anti-rattle device, a pretensioning device, a locking device, a synchronizing device, in particular a synchronizing sleeve and / or a synchronizing gate, and / or a coupling device, in particular a coupling sleeve and / or a coupling gate, for a synchronizing device described above. These parts are available separately.

[0027] Further advantages, features, and details of the invention will become apparent from the following description, in which various embodiments are described in detail with reference to the drawings. They show: Fig. 1 a conventional synchronization device; Fig. 2 a schematic diagram of an axially short synchronization device; Fig. 3 a somewhat more detailed, but still simplified representation of an axially short device for synchronization with a slotted guide; Fig. 4 a view of the device from Fig. 3 with a view of the scenery; Fig. 5 and Fig. 6 similar representations as in the Fig. 3 and Fig. 4 with an additional spring ring and indicated roof slopes or guide slopes; Fig. 7 a gearbox with two gearbox input shafts on which two pairs of fixed gears are arranged, and a gearbox output shaft with two pairs of loose gears that mesh with the fixed gears, partly in section; Fig. 8 an enlarged section on Fig. 7; Fig. 9 an exploded view of a section of Fig. 8; Fig. 10 an exploded view of a synchronizer and a clutch device, and Fig. 11 an exploded view of the transmission output shaft with two idler gears and two synchronizing devices; Fig. 12 a similar representation as in Fig. 8 with a locking mechanism that prevents two gears from being engaged simultaneously; Fig. 13 the view of a section along a line 200 in Fig. 12, wherein a viewing direction is indicated by two arrows 201, 202, with the blocking mechanism; the Fig. 14 to 17 the blocking mechanism or locking mechanism from the Fig. 12 and Fig. 13 in different switching states; Fig. 18 a perspective view of an actuating element from Fig. 12; Fig. 19 a the actuating element from Fig. 18 associated idler gear in perspective view; Fig. 20 an exploded view of two idler gears with an actuating device and the blocking mechanism or locking mechanism; Fig. 21 a similar exploded view as in Fig. 20 additionally with a gearbox output shaft; Fig. 22 a similar representation as in Fig. 12 with an additional anti-rattle device and an additional locking device and Fig. 23 a loose wheel with an actuating device and an additional spring device in half section.

[0028] In Fig. Figure 2 shows a highly simplified representation of a device 10 for synchronizing between a transmission shaft and an idler gear rotatably mounted on the transmission shaft. The device 10 comprises two sub-devices 11, 12 that are radially nested and overlapping in the axial direction. The axial direction corresponds to Fig. 2 a horizontal line.

[0029] The dividing device 11 is combined with a synchronizing device 15. The dividing device 12 is combined with a clutch device 16. The synchronizing device 15 and the clutch device 16 are also radially nested and arranged to overlap in the axial direction.

[0030] An arrow 17 indicates Fig. 2 shows the actuation path during synchronization. An arrow 18 indicates Fig. 2 shows an actuation path when coupling. The corresponding displacements of the sub-devices 11, 12 during synchronization and coupling are shown in Fig. 2 indicated by dashed lines.

[0031] The axial space requirement for the device 10 is indicated by a double arrow 19 in Fig. 2. In order to reduce the axial space requirement, the functions of a synchronization actuation and a coupling or clutch are separated from each other and arranged radially one above the other.

[0032] In Fig. 1 is a conventional synchronizing device 20 for comparison with Fig. 2. The device 20 comprises a synchronizing device 25 and a clutch device 26. The synchronizing device 25 is spaced axially from the clutch device 26. An arrow 27 indicates an actuating path during synchronization. An arrow 28 indicates an actuating path during clutch engagement.

[0033] A double arrow 29 indicates the axial length of the device 20 with the synchronizing device 25 and the coupling device 26. The corresponding displacement paths of the device 20 during synchronization and coupling are shown in Fig. 1 indicated by dashed lines.

[0034] In device 20, a sliding sleeve is first axially displaced, with the sliding sleeve initially pressing against a synchronizer ring. Once synchronization of an idler gear and a transmission shaft is achieved, the sliding sleeve can be pushed over the synchronizer ring onto a clutch body.

[0035] In Fig. 3, a device 30 for synchronizing is shown in more detail than in Fig. 2, but still shown in a simplified manner. The device 30 serves to synchronize between a transmission shaft 31 and an idler gear 32. The idler gear 32 is rotatably mounted on the transmission shaft 31 by means of a bearing device 33.

[0036] An actuating device 35 for actuating the device 30 advantageously comprises a planetary gear element of a (in Fig. 3 not shown) planetary gear.

[0037] The device 30 comprises a synchronizer ring assembly 40, a synchronizer 41, and a clutch 42. The synchronizer 41 and the clutch 42 are arranged axially overlapping and radially nested. A sliding block 43 is provided radially inward on the synchronizer 41. A sliding block 44 is provided radially outward on the clutch 42.

[0038] In Fig. 4 shows 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 a movement of the link guide 45 when actuated by the actuating device (35 in Fig. 3) indicated.

[0039] Dashed lines indicate Fig. 3 shows the axial displacement paths of the synchronizing device 41 and the clutch device 42 when actuated by the actuating device 35. When actuated by the actuating device 35, relative rotations are converted into axial movements of the synchronizing device 41 and the clutch device 42.

[0040] In the context of the claimed device 10, 30, the term axial refers to a rotational axis 49 of the gear shaft 31. The gear shaft 31 is a gear output shaft of a gear equipped with the idler gear 32.

[0041] In the Fig. 5 and Fig. 6 shows a device 50 for synchronizing, which corresponds to the one shown in the Fig. 3 and Fig. 4. To designate identical or similar parts, the same reference numerals are used as in the Fig. 3 and Fig. 4. To avoid repetition, reference is made to the previous description of the Fig. 3 and Fig. 4. In the following, only the differences between devices 30 and 50 will be discussed.

[0042] In Fig. 5, sloped roofs or guide slopes 51, 52 are indicated on the synchronizing device 41 and the synchronizing ring pack 40. Furthermore, sloped roofs or guide slopes 53, 54 are indicated on the clutch device 42 and the transmission shaft 31. Finally, a circle 55 indicates a spring washer between the synchronizing device 41 and the synchronizing ring pack 40.

[0043] When the device 50 is actuated by the actuating device 35, force is transmitted from the synchronizing device 41 to the synchronizer ring pack 40 via the roof slopes or guide slopes 51, 52. During synchronization, a synchronizer ring of the synchronizer ring pack 40 can rotate relative to the synchronizing device 41 by the width of a roof slope or guide slope 51, 52 and thus prevent further displacement of the synchronizing device 41. Once synchronization of the idler gear 32 and the transmission shaft 31 has been achieved, the synchronizing device 41 rotates a synchronizer ring of the synchronizer ring pack 40 back and continues to move in the axial direction, but only by the amount of a wear reserve.

[0044] After unlocking, the coupling device 42 can be pushed onto a rotation transmission element 58, which is also referred to as the coupling body. The rotation transmission element 58 is in Fig. 5 is connected in one piece with the transmission shaft or transmission output shaft 31. The axial movements of the synchronizing device 41 and the coupling device 42 are guided by the slotted guide (45 in Fig. 6) controlled.

[0045] To represent the sliding blocks 43, 44, pins are attached to the synchronizing device 41 and the coupling device 42, for example, which engage in the guide grooves or guide tracks 46, 47 of the guide track 45. Upon actuation / rotation of the guide track 45, the synchronizing device 41 is initially displaced axially over an inclined section of the guide track 46. The pin 44 of the coupling device 42 runs in a tangential path and is therefore not displaced axially. The guide track 47 is in Fig. 6 indicated by dashed lines.

[0046] 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 slide track 47 and displaces the coupling device 42 axially.

[0047] In Fig. Figure 7 shows a transmission 60 with an inner transmission input shaft 61 and an outer transmission input shaft 62, partially in section. A final drive stage 65 is arranged at a transmission output 64, connecting a differential (not shown). The final drive stage 65 is referred to as the final drive.

[0048] On his in Fig. 7 On the right side, the transmission 60 has two bearing points 66, 67. At the transmission output 64, the transmission 60 has a bearing journal 68. Two fixed gears 73, 74 are arranged on the inner transmission input shaft 61. Two fixed gears 71, 72 are arranged on the outer transmission input shaft 62.

[0049] The fixed gear 71 meshes with an idler gear 75, for example to represent a first gear. The fixed gear 72 meshes with an idler gear 76, for example to represent a third gear. The fixed gear 73 meshes with an idler gear 77, for example to represent a second gear. The fixed gear 74 meshes with an idler gear 78, for example to represent a fourth gear.

[0050] The idler gears 75 to 78 are rotatably mounted on a transmission output shaft 80, also referred to as the transmission shaft 80, by means of suitable bearings. The idler gears 75, 76 represent a first idler gear pair. The idler gears 77, 78 represent a second idler gear pair.

[0051] Two synchronizing devices 81, 82 are assigned to the first pair of idler gears 75, 76. An actuating device 85 is used to actuate the synchronizing devices 81, 82. Corresponding devices are assigned to the pair of idler gears 77, 78, which are actuated via an actuating device 86.

[0052] The actuating device 85 comprises a planetary gear 84. The planetary gear 84 is arranged in a hollow space radially within and axially between the adjacent idler gears 75, 76. The planetary gear 84 allows the axial installation space in the gear to be reduced via the actuating device 85.

[0053] In Fig. 8 you can see that the planetary gear 84 has a ring gear 87, a sun gear 90 and planet gears 91, 92 (see Fig. 11). 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.

[0054] The planet carrier 93 with the web rotates essentially synchronously with the idler gear 75 in the unactuated state of the devices 81, 82. The sun gear 90 rotates essentially synchronously with the idler gear 76 in the unactuated state of the devices 81, 82.

[0055] The term essentially synchronous in this context also means that the sun gear 90 and the planet carrier 93 with the web can rotate to a limited extent relative to the idler gears 75, 76 after actuation by the actuating device 85 in order to trigger a clutch, shifting and / or synchronization process.

[0056] When the actuating device 85 is actuated, the ring gear 87 is rotated. When the actuating device 85 is not actuated, the ring gear 87 is stationary. The ring gear 87 then has the same rotational speed as the gear 60, which is stationary. Thus, when the actuating device 85 is not actuated, the ring gear 87 has a rotational speed of zero.

[0057] When the ring gear 87 is rotated, either the planet carrier 93 with the web or the sun or the sun gear 90 rotates relative to the associated idler gear 75, 76. This relative rotation is then used to actuate one of the synchronization devices 81, 82.

[0058] The idler gear 75 is rotatably mounted on the transmission output shaft 80 by a bearing device 88. The idler gear 76 is rotatably mounted on the transmission output shaft 80 by a bearing device 89. The planet carrier 93 with the web is coupled to the device 81 by a coupling element 94. The coupling element 94 is part of the planet carrier 93, which is also referred to as the web. The sun gear 90 is coupled to the device 82 via a coupling element 95.

[0059] A rotation transmission element 98 is connected to the gear shaft 80 in a rotationally fixed manner via a spline 101. The spline 101, also referred to as gearing 101 for short, enables torque transmission between the gear shaft 80 and the rotation transmission element 98, and vice versa.

[0060] The rotary transmission element 98 is provided with guide bevels 99, 100 on its radial outer ends. The guide bevels 99, 100 interact with complementary guide bevels, which are explained below. The guide bevel 99 is the Fig. 8 left device 81. The guide bevel 100 is the one in Fig. 8 assigned to the device 82 arranged on the right.

[0061] The rotation transmission element 98, which can also be referred to as the clutch body, extends radially outward into a cavity formed between the two idler gears 75, 76. Radially outward, the rotation transmission element 98 has a toothing 102 between the guide bevels 99, 100, which is also designed as a sliding toothing.

[0062] Synchronizing rings 121, 131 of synchronizing ring packs 120, 130, arranged radially outward, are suspended in the sliding toothing 102. The sliding toothing 102 enables torque transmission between the rotation transmission element 98 and the outer synchronizing rings 121, 131, and vice versa. Axial displacement of the outer synchronizing rings 121, 131 relative to the rotation transmission element 98 is prevented by a retaining ring, in particular a spring ring or snap ring, and axial contact surfaces on the rotation transmission element or clutch body 98.

[0063] The term axial refers to a rotational axis 103 of the gear shaft 80 or the idler gears 75, 76. Axial means in the direction of or parallel to the rotational axis 103. Analogously, the term radial means transverse to the rotational axis 103.

[0064] The devices 81, 82 are housed in a particularly space-saving manner in the cavity between the idler gears 75, 76. Only the actuating device 85 for the two devices 81, 82 protrudes radially outward from the cavity between the idler gears 75, 76. This enables a simple interaction 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 driven by an electric motor.

[0065] The devices 81, 82 each comprise a synchronizing device 104, 106 and a coupling device 105, 107. The Fig. 8 left-hand arranged device 81 with the synchronizing device 104 and the coupling device 105 is the one in Fig. 8 is assigned to the idler gear 75, also located on the left. Fig. 8 right-hand arranged device 82 with the synchronizing device 106 and the coupling device 107 is the one in Fig. 8 is also assigned to the loose wheel 76, which is also arranged on the right.

[0066] The synchronizing devices 104, 106 and the coupling devices 105, 107 are combined with guide rails 108, 109. The guide rails 108, 109 serve to convert relative rotations into defined axial movements, which are used for synchronizing and coupling the respective idler gear 75, 76 with the transmission shaft 80.

[0067] The coupling devices 105, 107 each comprise a coupling sleeve 110, 112 and a coupling gate 111, 113. The synchronizing devices 104, 106 each comprise a synchronizing sleeve 114, 116 and a synchronizing gate 115, 117.

[0068] The coupling sleeve 110, the coupling link 111, the synchronizing sleeve 114 and the synchronizing link 115 of the Fig. 8 left-hand arranged device 81 are radially nested and arranged overlapping in the axial direction.

[0069] The coupling sleeve 112, the coupling link 113, the synchronizing sleeve 116 and the synchronizing link 117 of the Fig. 8 device 82 arranged on the right are also radially nested and arranged overlapping in the axial direction.

[0070] The synchronizer ring packages 120, 130 each comprise a total of four synchronizer rings 121 to 124, 131 to 134. The synchronizer rings 121 to 124 of the Fig. 8, the device 81 arranged on the left are arranged radially outside the synchronizing device 104 and the clutch device 105. However, the synchronizing rings 121 to 124 are arranged in an axial direction overlapping the clutch device 105 and the synchronizing device 104.

[0071] Analogously, the synchronizer rings 131 to 134 of the Fig. 8, the device 82 arranged on the right is arranged radially outside the synchronizing device 106 and the clutch device 107. However, the synchronizing rings 131 to 134 are arranged axially overlapping the synchronizing device 106 and the clutch device 107.

[0072] The radially outer synchronizer rings 121, 131 abut one another in the center between the devices 81, 82 and jointly engage the toothing 102 of the rotation transmission element 98. The radially inner synchronizer rings 124, 134 of the synchronizer ring packs 120, 130 can be coupled to the synchronizer sleeves 114, 116, as will be explained below.

[0073] A spring device in the form of a spring ring 118, 119 is arranged between the synchronizing sleeves 114, 116 and the radially inner synchronizing rings 124, 134. The spring devices with the spring rings 118, 119 serve for synchronization, as will be explained below.

[0074] In Fig. 9, parts of the devices 81, 82 are shown in perspective. The parts of the device 82, which in Fig. 8 is arranged on the right and assigned to the idler gear 76, are in Fig. 9 is also shown in exploded view. In Fig. 10 are the parts of the device 82 which are shown in Fig. 9 are partially shown together, shown in exploded view.

[0075] In Fig. 9 shows that guide elements 140 are provided radially on the inner side of the radially inner synchronizer ring 134 of the synchronizer ring assembly 130. The guide elements 140 each have two guide bevels 141, 142. Complementary guide elements 145, each with two guide bevels 146, 147, are provided on the synchronizer sleeve 116.

[0076] The guide elements 140 on the radially inner synchronizer ring 134 are designed as projections that project radially inward. The guide elements 145 on the synchronizer sleeve 116 are designed as recesses in the synchronizer sleeve 116, which Fig. 9 are open on their left side.

[0077] The engagement of the guide elements 140 with the guide elements 145 enables coupling of the synchronizing sleeve 116 with the radially inner synchronizing ring 132. The spring ring 119 creates a certain preload for synchronization between the synchronizing sleeve 116 and the radially inner synchronizing ring 134.

[0078] On the in the Fig. 9 and Fig. 10 right side, the synchronizing sleeve 116 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 112 has on its Fig. 9 and Fig. 10 right side has a total of four wraps 155 to 158.

[0079] The engagement elements 155 to 158 on the coupling sleeve 112 represent stops for the synchronizing link 117 in the axial direction. In addition, the engagement elements 155 to 158 on the coupling sleeve 112 interact in the circumferential direction with the anti-rotation elements 151 to 154 on the synchronizing sleeve 116.

[0080] At the synchronization backdrop 117, on the in the Fig. 9 and Fig. 10 right side, a total of four driver elements 161 to 164 are provided, which extend in the axial direction. Fig. 9 it can be seen that the engagements 155 to 158 of the coupling sleeve 112 are arranged in the circumferential direction between one of the anti-rotation elements 151 to 154 of the synchronizing sleeve 116 and one of the driver elements 161 to 164 of the synchronizing link 117.

[0081] Furthermore, a link pin 166 is attached to the synchronizing link 117. The link pin 166 protrudes radially inward from the synchronizing link 117 in such a way that it engages in a link track which, as can be seen in Fig. 10, is combined with an external thread 171 on the outside of the synchronizing sleeve 116. A complementary internal thread 172 is formed radially inside the synchronizing link 117.

[0082] The external thread 171 is mounted on the synchronizing sleeve 116 on the Fig. 10 right side by a guide track 173, which, unlike the external thread 171, has no pitch. The guide pin 166 engaging in the guide track 173 simplifies threading of the threads 171, 172.

[0083] The threads 171, 172 together with the slide track 173 and the slide pin 166 constitute part of the slide guide 109. The slide guide 109 may alternatively or additionally comprise ramps.

[0084] An external thread 175 is provided on the coupling sleeve 112, which interacts with a complementary internal thread 176 provided on the coupling link 113. Instead of the threads 175, 176, ramps can also be attached to represent the link guide 109.

[0085] In Fig. Figure 11 shows an exploded view of the transmission shaft 80 with the two idler gears 75, 76, the final drive 65, and the two synchronizing devices 81, 82 located between the idler gears 75, 76. The devices 81, 82 are actuated via the ring gear 87 of the planetary gear. For this purpose, the ring gear 87 has external teeth.

[0086] A rotary induction is achieved via the planetary gear 84. The left synchronizing device 81 is actuated by the planetary carrier 93. The right synchronizing device 82 is actuated by the sun gear 90 of the planetary gear 84.

[0087] The clutch sleeves 110, 112 and the respective synchronizing sleeves 114, 116 are secured against rotation on the associated idler gear 75, 76. If the planet carrier 93 or the sun gear 90 is rotated relative to the idler gear 75, 76 to actuate it, the synchronizing sleeves 114, 116 are moved axially toward the radially inner synchronizing ring 124, 134 via the slotted guides 108, 109 and the threaded ramps.

[0088] The spring ring 118, 119 initially ensures axial pressure on the radially inner synchronizer ring 124, 134, allowing the radially inner synchronizer ring 124, 134 to rotate within a limited circumferential clearance. This is also referred to as synchronization.

[0089] During synchronization, the guide bevels 141, 142 on the radially inner synchronizer ring 124 come to rest in front of the guide bevels 146, 147 of the synchronizer sleeve 116. Upon further actuation, the synchronizer sleeve 116 presses the radially inner synchronizer ring 124 via the guide bevels 146, 147 and 141, 142.

[0090] At synchronous speed of idler gear 75 and gear shaft 80, synchronizer ring 124 can be turned back. Upon further actuation, the guide pin 166 on the synchronizing guide 117 moves into the guide track 173 without a pitch, and the threads 171, 172 are moved apart.

[0091] In this position, the driver elements 161 to 164 of the synchronizing link 117 come into contact with the engagement elements 155 to 158 of the coupling link 113, as can be seen in Fig. 9. Upon further actuation, only the coupling sleeve 112 is then axially displaced into its end position by rotating the coupling link 113.

[0092] In Fig. 9, an arrow 181 indicates how the driver elements 161 to 164 of the synchronizing link 117 engage the engagement elements 155 to 158 of the coupling link 113. The inner parts, i.e., the coupling link 113 and the coupling sleeve 112, are then rotated.

[0093] An arrow 182 indicates Fig. 9 indicates that the anti-rotation elements 151 to 154 on the synchronizing sleeve 116 prevent the synchronizing sleeve 116 from rotating during rotation. The anti-rotation elements 151 to 154 practically hold the synchronizing sleeve 116 in place.

[0094] In Fig. 12 is a similar section as in Fig. 8 with a blocking mechanism 207. The coupling element 94 represents a Fig. 12 left actuating element of the actuating device 85. The coupling element 95 represents a Fig. 12 right actuating element of the actuating device 85. The actuating element 94 is Fig. 12 left idler gear 75. The actuating element 95 is Fig. 12 assigned to right idler gear 76.

[0095] In Fig. 13 is a view of a section along a line 200 in Fig. 12 is shown enlarged, with arrows 201, 202 indicating the viewing direction. The sectional view shows that the actuating device 85 is designed as an actuating wheel 205 with external teeth. An inner region 206 of the idler gear 76 is shown broken away in the sectional view to reveal the blocking mechanism 207, which is also referred to as the locking mechanism.

[0096] The blocking mechanism or locking mechanism 207 comprises, as shown in Fig. 13, 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 area 206 of the idler gear 76. The interaction between stop 208 and counter-stop 209 is shown in the Fig. 14 to 17 illustrates.

[0097] In a stationary state, when no gear is being shifted, the actuating elements 94, 95 of the synchronizers, here planet carriers or suns, rotate at the same rotational speed as the respective idler gears 75, 76. Between the actuating elements 94, 95 and the idler gears 75, 76 there are stops for both directions of rotation.

[0098] In Fig. 13 shows that the stop 208 on the actuating element 95 can be rotated in one of the two directions, in Fig. 13 downwards, designed as a ramp 210 and thus traversable. If a switching operation is initiated via the actuating wheel 205, one of the two actuating elements 94, 95 rotates relative to the associated idler gear 75, 76.

[0099] In the Fig. 14 to 16, the movements of the actuating elements 94, 95 relative to the associated idler gears 75, 76 are shown schematically. Fig. The neutral position is shown in Figure 15. The actuating elements 94, 95 are in a basic position relative to the idler gears 75, 76, in which all stops 208, 209 coincide.

[0100] 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 actuating elements 95, 95 are opposite, so that, for example, the torque in the Fig. 14 to 16 left actuating element 94 wants to move downwards relative to the idler gear 75, and that in the Fig. 14 to 16 right actuating element 95 relative to the idler gear 76 upwards.

[0101] However, since the non-overridable stop 208 and counter-stop 209 act between the right actuating element 95 and the right idler gear 76, the right actuating element 95 cannot deflect. The left actuating element 94 must therefore travel over the ramp-shaped stop. In doing so, the left actuating element 94 is displaced in the axial direction by the width of the stop overlap, as shown in Fig. 14 is indicated by arrows 211, 212.

[0102] The facing end surfaces of the actuating elements 94, 95 approach each other. The relative rotation between the actuating element 94 and the idler gear 75 is used to activate the synchronization and engage the gear.

[0103] In Fig. 16, the right idler gear 76 is engaged. The left idler gear 75 is engaged with the left actuating element 94.

[0104] To disengage the gear, the actuating wheel 205 is turned in the opposite direction. Accordingly, the torques in the actuating elements 94, 95 now also act in the other direction. The goal now is to ensure that the engaged gear is disengaged first, and not that the other gear is engaged additionally.

[0105] In Fig. 17, arrows 124, 215 symbolize the circumferential force and the torque in the actuating elements 94, 95. In the Fig. 17 The torque of the right actuating element 95 is supported by the ramp-shaped stop 208 or counter-stop 209. The axially displaced left actuating element 94 prevents the right actuating element 95 from overrunning the ramp-shaped stop 210, since the two facing end surfaces of the actuating elements 94, 95 touch each other.

[0106] In the Fig. 18 and Fig. 19, the actuating element 95 and the idler gear 76 are shown in perspective. In Fig. In Figure 18, double arrows 218 to 220 indicate that stops 221, 222, 223, and 208 are distributed unevenly over a circumference of the actuating element 95. This advantageously allows the largest possible angle of rotation to be achieved on the actuating element 95, for example, 180 degrees, which leads to lower tooth forces on the planets.

[0107] If the stops were evenly distributed, they would re-align after rotation by the pitch angle, and axial displacement would no longer be ensured. Due to the uneven distribution, it is possible that all stops or counter-stops would only re-align after a full rotation.

[0108] The Fig. 20 and Fig. 21 show the construction in exploded views. In Fig. 20 shows that an inner region 226 of the idler gear 75 is equipped with counter stops 229 in the same way as the inner region 206 of the idler gear 76. In 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.

[0109] In Fig. 22 is a similar section as in Fig. 12 with a locking device 238 and an anti-rattle device 244. The anti-rattle device 244 comprises a preloading device 233, by which the actuating element 95 is preloaded against the associated idler gear 76 in the axial direction.

[0110] The pretensioning device 233 comprises a disc spring-like spring 234. The spring 234 is supported radially outwardly 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 provided on the actuating element 95.

[0111] To eliminate unwanted gear rattle, it is necessary to ensure that the load-free gear teeth roll smoothly and do not sway back and forth from one flank to the other within the flank clearance. For this purpose, the gears of a pair of idler gears 75, 76 are slightly preloaded by a preload torque. The preload torque is applied to the actuating element 205, for example, by an actuator motor (not shown). 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.

[0112] Alternatively, the preload torque may be generated by a locking mechanism 238, which is also referred to as a locking device 238.

[0113] The locking device 238 comprises a locking body 239, which essentially has the shape of a spherical segment. The locking body 239 engages in a complementarily shaped recess in the actuating wheel 205 of the actuating device 85. The locking body 239 is preloaded against the actuating wheel 205 by a spring 240. The spring 240 is supported on a (in Fig. 22 not shown) fixed housing. A symbol to the left of the operating wheel 205 indicates Fig. 22 indicates that the actuating wheel 205 cannot move to the left in the axial direction.

[0114] The locking device comprises at least one locking ramp and / or inclined surface (not shown). The position of the locking ramp and / or the inclined surface is selected such that the locking body 239 rests circumferentially against the locking ramp or the inclined surface when the anti-rattle device 244 or the pretensioning device 233 presses the ramp-shaped stop 208 and the counter-stop 209 together.

[0115] In Fig. 23 shows a pre-tensioning device 245. The pre-tensioning device 245 comprises a spring 246, which is fastened with its free ends to the idler gear 76. The spring 246 has a central Fig. 23 has a downwardly projecting nose 247. The nose 247 engages in a recess 248 formed in the actuating element 95. List of reference symbols 10 Synchronization device 11 Dividing device 12 Dividing device 15 Synchronization device 16 Coupling device 17 Arrow 18 Arrow 19 Double arrow 20 Synchronization device 25 Synchronization device 26 Coupling device 27 Arrow 28 Arrow 29 Double arrow 30 Synchronization device 31 Gear shaft 32 idler gear 33 Storage facility 35 Actuating device 40 synchronizer ring package 41 Synchronization device 42 Coupling device 43 sliding block 44 Scenery guide 45 Scenery guide 46 Guide groove (sliding track) 47 Guide groove (sliding track) 48 Arrow 49 axis of rotation 50 Synchronization device 51 guide bevel 52 guide bevel 53 guide bevel 54 guide bevel 55 Circle 58 Rotary transmission element 60 gearboxes 61 inner transmission input shaft 62 outer transmission input shaft 64 Gearbox output 65 power amplifier 66 storage location 67 storage location 68 bearing journals 71 Fixed gear 72 fixed gear 73 Fixed gear 74 Fixed gear 75 idler gear 76 idler gear 77 idler gear 78 idler gear 80 Gearbox output shaft 81 Synchronization device 82 Synchronization device 84 planetary gears 85 Actuating device 86 Actuating device 87 ring gear 88 Storage facility 89 Storage facility 90 Sun gear 91 Planetary gear 92 Planetary gear 93 planet carrier 94 Coupling element -> Actuating element (left) 95 Coupling element -> Actuating element (right) 98 Rotary transmission element 99 guide bevel 100 guide bevel 101 Gearing 102 Gearing 103 axis of rotation 104 Synchronization device 105 Coupling device 106 Synchronization device 107 Coupling device 108 Scenery 109 Scenery 110 coupling sleeve 111 Clutch gate 112 coupling sleeve 113 Clutch gate 114 Synchronizing sleeve 115 Synchronization backdrop 116 Synchronizing sleeve 117 Synchronization backdrop 118 spring ring 119 Spring ring 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 bevel 142 guide bevel 145 Guide element 146 guide bevel 147 guide bevel 151 Anti-rotation element 152 Anti-rotation element 153 Anti-rotation element 154 Anti-rotation element 155 Envelope 156 Envelope 157 Envelope 158 Envelope 161 Driving element 162 Driving element 163 Driving element 164 Driving element 166 link pin 171 external thread 172 internal threads 173 Slide track 175 external thread 176 internal threads 181 Arrow 182 Arrow 201 Arrow 202 Arrow 205 Operating wheel 206 Interior 207 Blocking mechanism 208 ramp-shaped stop 209 Counterattack 210 Ramp 211 Arrow 212 Arrow 214 Arrow 215 Arrow 218 Double Arrow 219 Double Arrow 220 Double Arrow 221 attack 222 stop 223 attack 226 Interior 228 ramp-shaped stop 229 Counterattack 230 Ramp 233 Pretensioning device 234 spring 235 support ring 236 Support structure 238 locking device 239 locking body 240 spring 244 Anti-rattle device 245 Pre-tensioning device 246 spring 247 Nose 248 recess

Claims

[1] Device (10; 50; 81, 82) for synchronizing between a transmission shaft (31; 80) and two idler gears (75, 76) which are rotatably arranged on the transmission shaft (31; 80), with an actuating device (85) which comprises two actuating elements (94, 95) which are rotatable relative to one another and associated with the idler gears (75, 76) and which have an anti-rattle device (244), characterized by in that the anti-rattle device (244) comprises a locking device (238) arranged between at least one of the actuating elements (94, 95) and a stationary housing body, with a blocking mechanism (207) that prevents two gears from being engaged simultaneously. [2] Device according to claim 1, characterized by that ramp-shaped stops (208,228) are provided on the actuating elements (94,95), which only allow rotation of the actuating elements (94,95) relative to the associated idler gear (75,76) in one direction of rotation. [3] Device according to claim 2, characterized by that several ramp-shaped stops (208,221-223) are unevenly distributed over a circumference of the actuating elements (94,95). [4] Device according to one of the preceding claims, characterized by that the actuating elements (94,95) are axially displaceable relative to one another in such a way that an actuating element (94,95) of a loose wheel (75,75) coupled to the transmission shaft (31;80) prevents the simultaneous engagement of a second gear. [5] Device according to one of the preceding claims, characterized by that the actuating device (85) comprises two actuating elements (94, 95) which are rotatable relative to one another and assigned to the idler gears (75, 76) and have a blocking mechanism (207) which prevents two gears from being engaged simultaneously. [6] Device according to one of the preceding claims, characterized bythat the anti-rattle device (244) comprises a pretensioning device (233; 245) by which at least one of the actuating elements (94, 95) is pretensioned in an axial or radial direction. [7] Device according to one of the preceding claims, characterized by that the anti-rattle device (244) comprises a pretensioning device (245) which is effective between at least one of the actuating elements (95) and the associated idler gear (76). [8] Gearbox (60) with gear pairs, each comprising a fixed gear (71-74) and a loose gear (75,76) to represent gears in the gearbox (60), characterized by that a device (10; 50; 81, 82) for synchronizing according to one of the preceding claims is arranged on two loose wheels (75, 76) of the transmission (60) adjacent to one another on a transmission shaft (31; 80). [9] Method for synchronizing between a transmission shaft (31; 80) and two idler gears (75, 76) rotatably mounted on the transmission shaft (31; 80), with a device (10; 50; 81, 82) according to one of claims 1 to 7, in a transmission (60) according to claim 8, characterized by in that a synchronizing device and a coupling device are successively displaced by a relative movement of the actuating device (94, 95) to the idler gear (75, 76) in such a way that the idler gear (75, 76) is coupled to a corresponding fixed gear (71-74), a preloading torque being applied to the idler gears (75, 76) in order to counteract undesirable noise development during operation.

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