A group transmission device, in particular a split transmission

Abstract

The invention relates to a group transmission device, in particular a split transmission, comprising a main housing (11) having a main shaft (12), an intermediate shaft (13) and a cylindrical gear pair (14) comprising a first cylindrical gear (15) arranged coaxially and axially overlapping in relation to the main shaft (12) and a second cylindrical gear (16) arranged coaxially and axially overlapping in relation to the intermediate shaft (13), a multiple range sub-housing (17) arranged coaxially in relation to the main shaft (12) in a planetary gear mechanism configuration having a first shaft (18) connected non-rotatably to the main shaft (12), a second shaft (20) connected non-rotatably to a transmission output shaft (19), a third shaft (21) and a linkage shift unit (S5), a first shift unit (S1) provided for non-rotatably connecting the third shaft (21) to a housing (22) and a second shift unit (S2) provided for non-rotatably connecting the third shaft (21) to the first cylindrical gear (15), wherein the main shaft (12) is non-rotatably joined or joinable to a transmission input shaft (23), wherein the group transmission device has a third shift unit (S3) provided for non-rotatably connecting the first cylindrical gear (15) to the first shaft (18) of the multiple range sub-housing (17).

Description

TECHNICAL FIELD

[0001] The invention relates to a group transmission device, in particular a split transmission. BACKGROUND

[0002] A group transmission device is known from DE 103 15 313 A1, which comprises a main box having a main shaft, an intermediate shaft and a cylindrical gear pair comprising a first cylindrical gear arranged coaxially and axially overlapping with respect to the main shaft and a second cylindrical gear arranged coaxially and axially overlapping with respect to the intermediate shaft, a multiple sub-box in the configuration of a planetary gear mechanism arranged coaxially with respect to the main shaft, the multiple sub-box having a first shaft connected to the main shaft against rotation, a second shaft connected to a transmission output shaft against rotation, a third shaft and a linkage shift unit, a first shift unit provided for connecting the third shaft to the box body against rotation and a second shift unit provided for connecting the third shaft to the first cylindrical gear or to the second cylindrical gear against rotation, wherein the main shaft is connected or connectable to a transmission input shaft against rotation.

[0003] Group transmission devices are also known from DE 101 45 519 A1, DE 102 60 179 A1 and DE 10 2004 046 074 A1. Furthermore, a group transmission device, in particular a power-shiftable split transmission, is known from DE 10 2017 007 763 A1. SUMMARY

[0004] The invention is based, inter alia., on the task of providing a preferably versatile and flexible group transmission device. This is achieved by the design according to the invention corresponding to claim 1. Improvements of the invention result from the dependent claims.

[0005] The invention is based on a group transmission device, in particular a split transmission, comprising a main box having a main shaft, an intermediate shaft and a cylindrical gear pair comprising a first cylindrical gear arranged coaxially and axially overlapping with respect to the main shaft and a second cylindrical gear arranged coaxially and axially overlapping with respect to the intermediate shaft, a multiple sub-box in the configuration of a planetary gear mechanism arranged coaxially with respect to the main shaft, the multiple sub-box having a first shaft connected to the main shaft against rotation, a second shaft connected to a transmission output shaft against rotation, a third shaft and a linkage shift unit, a first shift unit provided for connecting the third shaft to the box body against rotation and a second shift unit having exactly one axially movable shift element and provided for connecting the third shaft to the first cylindrical gear against rotation, wherein the main shaft is connected or connectable to a transmission input shaft against rotation.

[0006] It is proposed that the group transmission device has a third shift unit which has exactly one further axially movable shift element and is provided for the rotationally fixed connection of the first cylindrical gear to the first shaft of the range gearbox. By virtue of the design of the group transmission device according to the application, it is possible, inter alia, to provide a group transmission device which can preferably be flexibly shifted. In particular, the cylindrical gear pair can be used for a power-split operation, in which power and in particular torque is transmitted via the countershaft to the range gearbox on the one hand and via the main shaft to the range gearbox on the other hand, in particular at the same time. Furthermore, the cylindrical gear pair can also be used advantageously in a non-power-split operation, in which power is transmitted only via the first power path. Preferably, one of the ring gears can be connected to the planet carrier by means of a linkage shift unit, so that a gear can be provided in the low range and can thus be further used for forming a transmission.

[0007] Preferably, the third shaft is permanently rotationally fixed to a ring gear of the range gearbox. By means of the linkage shift element, preferably in particular by means of a sliding sleeve, the ring gear can be connected to the planetary gear mechanism, so that a gear can be provided in the low range and can thus be further used for forming a transmission. Preferably, the range gearbox is formed by one planetary gear mechanism. In particular, the range gearbox has at least one, in particular exactly one, planetary gear set.

[0008] The "group transmission device" is in particular intended to mean at least a part of a group transmission. Alternatively, the group transmission device can completely form the group transmission. The group transmission device has in particular a main gearbox, preferably a main transmission, which preferably comprises one countershaft. It is also conceivable for the main transmission to be free of a countershaft. The main gearbox has in particular a plurality of gears. Preferably, the main gearbox is provided for the shifting of a plurality of gears. Advantageously, the group transmission device has at least one reduction gear, in particular advantageously two reduction gears, in particular preferably a range gearbox and a front gearbox. Preferably, the group transmission device, in particular for a truck, is provided for the distribution of the drive torque to the main shaft and at least one countershaft, in particular when a power-split group transmission device is designed, wherein the countershaft is in turn connected to the main shaft at one end. Preferably, one of the paths has a switchable gear, wherein the path with the switchable gear has in particular a mechanism for increasing or decreasing the torque of the path. Preferably, at least one switchable gear and / or its path can be made torque-free by means of the mechanism, while the other path always also transmits torque. Thereby, in particular a shift without torque interruption can be achieved. "Provided" is in particular intended to mean designed and / or equipped specifically. "One object is provided for a function" is in particular intended to mean that the object fulfils and / or performs the function in at least one state of use and / or operation.

[0009] In this connection, "cylindrical gear pair" shall mean, in particular, two pairs of cylindrical gears which are permanently meshed with one another. "Planetary gearset" shall mean, in particular, a unit of a planetary gear mechanism which has as a transmission component a sun gear, as a transmission component a ring gear, as a transmission component a planet carrier and a plurality of transmission components which are planetary gears, wherein the transmission components which are planetary gears are arranged along a circular path around the transmission component which is a sun gear. "Planetary transmission" shall mean, in particular, a unit which has at least one planetary gearset, preferably exactly one planetary gearset. Alternatively or additionally, the planetary transmission can be designed to be multi-stage and preferably comprise a plurality of planetary gearsets.

[0010] "Engagement" shall mean, in particular, an engagement or an anti-rotationally, preferably permanently anti-rotationally, engagement, preferably by means of at least one transmission mechanism and / or at least one toothing. Advantageously, "engagement" shall mean an engagement or an anti-rotationally, in particular preferably permanently anti-rotationally, engagement, particularly advantageously by means of at most one transmission mechanism and / or at most one toothing. In particular, "shifting unit" shall mean a unit which has at least two engagement pieces and at least one shifting element which is provided for establishing a switchable connection between the at least two engagement pieces. Preferably, at least one of the shifting units is constituted by a shifting unit which has three engagement pieces. The "shifting element" of the shifting unit shall mean, in particular, a component which is preferably designed to be axially movable and which, in at least one operating state, in particular in at least one gear position of the shifting unit, is provided for anti-rotationally engaging the at least two engagement pieces. The "engagement piece" shall mean, in particular, a component of the shifting unit which is permanently anti-rotationally connected to a transmission component, such as a transmission shaft, a driving gearwheel, a driven gearwheel and / or a bridge axle, which is preferably fixed in the axial and radial direction and which is in particular provided for connecting, in a frictional, force-locking and / or form-locking manner, with a shifting element, such as a driving gearwheel, which has a toothing for connecting with the shifting element. The "shifting unit with three engagement pieces" shall mean, in particular, a shifting unit in which the shifting element is provided for switchably connecting or disconnecting one engagement piece, in particular an inner engagement piece, to or from at least one of the other two engagement pieces. In this connection, "anti-rotation" shall mean, in particular, an anti-rotation connection of a second component.

[0011] "Anti-rotation connection and anti-rotation engagement of two rotationally mounted components" shall mean that the two components are arranged coaxially with one another and are connected to one another in such a way that they rotate with the same angular velocity as one another. "Anti-rotationally connecting a rotationally mounted component to a housing" shall mean connecting the component to the housing in such a way that it cannot rotate relative to the housing.

[0012] It is further proposed that the range derailleur has exactly three shafts, precisely a first shaft, a second shaft and a third shaft. Preferably, the first shaft is connected in a rotationally fixed manner to the main shaft and forms an input shaft of the range derailleur. Preferably, the second shaft is connected in a rotationally fixed manner to the transmission output shaft and forms an output shaft of the range derailleur. Particularly preferably, the third shaft is permanently connected in a rotationally fixed manner to the ring gear of the range derailleur. Thereby, an advantageous range derailleur can be provided, among other things.

[0013] It is further proposed that the group transmission device has a front derailleur arranged in front of the main shaft, which has a further shaft which is connected in a rotationally fixed manner to the main shaft or which can be connected in a rotationally fixed manner to the main shaft by means of a fourth shift element. Thereby, an advantageous group transmission device can be provided. In particular, by means of the front derailleur and the group gearwheel, a shift between the gear steps realized by means of the group gearwheel can be realized without a power interruption.

[0014] It is further proposed that the third shift unit is provided for engaging the main shaft to the second cylindrical gear. Preferably, the third shift unit is formed by a shift unit with three engagement elements, which is provided for engaging the main shaft to the second cylindrical gear or to the fourth cylindrical gear. The group transmission device preferably has a second cylindrical gear pair, which comprises a third cylindrical gear which is arranged coaxially and axially overlapping with respect to the main shaft and a fourth cylindrical gear which is arranged coaxially and axially overlapping with respect to the intermediate shaft. Thereby, an advantageous group transmission device can be provided.

[0015] It is further proposed that the range derailleur has a sun gear, wherein the first shaft is connected in a rotationally fixed manner to the sun gear. Preferably, the range derailleur has a sun gear, a ring gear, a planet carrier and a plurality of planet gears, wherein the planet gears are arranged by the planet carrier along a circular path around the sun gear. It is further proposed that the range derailleur has a planet carrier, wherein the second shaft is connected in a rotationally fixed manner to the planet carrier. It is further proposed that the range derailleur has a ring gear, wherein the third shaft is connected in a rotationally fixed manner to the ring gear. Thereby, an advantageous group transmission device can be provided.

[0016] It is further proposed that the linkage shift unit is provided for engaging the second shaft to the third shaft in a rotationally fixed manner. The linkage shift unit is in particular provided for interlocking the range derailleur. Thereby, a linkage can be advantageously achieved, among other things.

[0017] It is further proposed that the main shaft is designed as a solid shaft. In connection therewith, a "solid shaft" shall mean in particular a shaft which, although it can have cavities, if appropriate, at least locally, for reasons of weight reduction or oil transport, does not have another shaft arranged coaxially within the cavities and axially therethrough. Thereby, an advantageous compact and stable group transmission device can be provided, among other things.

[0018] It is also proposed that the first shift unit and the linkage shift unit are combined into a double shift unit having a single sliding sleeve. Preferably, the double shift unit is designed as a shift unit having three engagement elements. Thereby, an especially compact group transmission arrangement can be provided, among others.

[0019] The terms "axial" and "radial" in this case relate to the main rotational axis of the group transmission arrangement, in particular of the main shaft, and therefore the expression "axial" refers, among others, to a direction which extends parallel or coaxially with respect to the main rotational axis. Furthermore, the expression "radial" refers, among others, to a direction which runs perpendicular to the main rotational axis. "Arranged on the transmission input side" is to be understood as meaning that the component is arranged on the side of another component which faces the transmission input and / or the combustion engine. "Arranged on the transmission output side" is to be understood as meaning that the component is arranged on the side of another component which faces away from the transmission input and / or the combustion engine, even if the other component is arranged axially behind the transmission output. BRIEF DESCRIPTION OF DRAWINGS

[0020] Further advantages and features result from the following description of the figures. In the figures, an embodiment of the application is shown, wherein:

[0021] Figure 1 A motor vehicle group transmission arrangement according to the application is shown in a schematic view. DETAILED DESCRIPTION

[0022] Figure 1 A motor vehicle group transmission arrangement 10 is shown schematically. The group transmission arrangement 10 forms part of a multi-speed transmission, in particular of a group transmission. The group transmission arrangement 10 has a housing 22.

[0023] The group transmission arrangement 10 is designed as a split transmission. The group transmission arrangement 10 is composed of a power split transmission. The group transmission arrangement 10 has a range sub-transmission 17. The range sub-transmission 17 is designed as a rear sub-transmission. The range sub-transmission 17 is provided for switching between at least two, in particular at least three, gear groups. The group transmission arrangement 10 has a front sub-transmission 24. The group transmission arrangement 10 also has a main transmission 11. The main transmission 11 is arranged between the front sub-transmission 24 and the range sub-transmission 17.

[0024] The group transmission device 10 comprises a transmission input shaft 23. The transmission input shaft 23 is arranged in front of a front sub-transmission 24. The transmission input shaft 23 is provided on the drive side for connection to a clutch, in particular a powershift clutch, which cannot be seen further. The group transmission device 10 is connectable to a drive unit, which is not shown further, by means of the clutch, in particular the powershift clutch. The group transmission device 10 has a transmission output shaft 19. The transmission output shaft 19 is arranged coaxially with respect to the transmission input shaft 23. The transmission output shaft 19 has a driven gearwheel 30. The driven gearwheel 30 is connected, for example, to a main drive, which is not shown further.

[0025] The group transmission device 10 has a main shaft 12. The main transmission 11 has the main shaft 12. The main shaft 12 is arranged coaxially with respect to the transmission input shaft 23. The main shaft 12 is non-rotatably joined to the transmission input shaft 23. The main shaft 12 is arranged between the transmission input shaft 23 and the transmission output shaft 19. The main shaft 12 is designed as a solid shaft. The group transmission device 10 comprises an intermediate shaft 13. The main transmission 11 has the intermediate shaft 13. The intermediate shaft 13 is arranged parallel offset with respect to the main shaft 12. The intermediate shaft 13 is designed as a solid shaft.

[0026] The group transmission device 10 comprises at least three gearwheel planes Z1, Z2, Z3.

[0027] The main transmission 11 has a cylindrical gearwheel pair 14. The cylindrical gearwheel pair 14 is arranged in the second gearwheel plane Z2. The cylindrical gearwheel pair 14 has a first cylindrical gearwheel 15 which is arranged coaxially and axially overlapping with respect to the main shaft 12. The first cylindrical gearwheel 15 is composed of a driving gearwheel. The cylindrical gearwheel pair 14 also has a second cylindrical gearwheel 16 which is arranged coaxially and axially overlapping with respect to the intermediate shaft 13. The second cylindrical gearwheel 16 is composed of a driven gearwheel. The second cylindrical gearwheel 16 is permanently connected non-rotatably to the intermediate shaft 13. The first cylindrical gearwheel 15 of the cylindrical gearwheel pair 14 and the second cylindrical gearwheel 16 of the cylindrical gearwheel pair 14 are permanently connected meshingly with one another. The first cylindrical gearwheel 15 of the cylindrical gearwheel pair 14 is permanently meshed with the second cylindrical gearwheel 16 of the cylindrical gearwheel pair 14. The main transmission 11 also has a further cylindrical gearwheel pair 26. The further cylindrical gearwheel pair 26 is arranged in the first gearwheel plane Z1. The further cylindrical gearwheel pair 26 has a third cylindrical gearwheel 27 which is arranged coaxially and axially overlapping with respect to the main shaft 12. The third cylindrical gearwheel 27 is composed of a driving gearwheel. In addition, the further cylindrical gearwheel pair 26 has a fourth cylindrical gearwheel 28 which is arranged coaxially and axially overlapping with respect to the intermediate shaft 13. The fourth cylindrical gearwheel 28 is composed of a driven gearwheel. The fourth cylindrical gearwheel 28 is permanently connected non-rotatably to the intermediate shaft 13. The third cylindrical gearwheel 27 of the further cylindrical gearwheel pair 26 and the fourth cylindrical gearwheel 28 of the further cylindrical gearwheel pair 26 are permanently connected meshingly with one another. The third cylindrical gearwheel 27 of the further cylindrical gearwheel pair 26 is permanently meshed with the fourth cylindrical gearwheel 28 of the further cylindrical gearwheel pair 26.

[0028] The front sub-transmission 24 is arranged at the front of the main shaft 12. The front sub-transmission 24 is only shown schematically. The transmission input shaft 23 forms an input side of the front sub-transmission 24. The front sub-transmission 24 has a further shaft 25, which is connected to the main shaft 12 in a rotationally fixed manner or can be connected to the main shaft by means of a fourth shift unit S4. The group transmission device 10 has a fourth shift unit S4. The fourth shift unit S4 is formed by a clutch. The further shaft 25 can be connected to the main shaft 12 in a rotationally fixed manner by means of the fourth shift unit S4. The fourth shift unit S4 is provided for engaging the further shaft 25 to the main shaft 12. The further shaft 25 forms a first output shaft of the front sub-transmission 24. The further shaft 25 forms a first power path of the group transmission device 10 from the front sub-transmission 24. The front sub-transmission 24 also has a second power path 29. The front sub-transmission 24 can be directly engaged to the intermediate shaft 13 of the main transmission 11 via the second power path 29. The force transmission of the group transmission device 10, which is designed as a power split transmission, is split in the front sub-transmission 24. At least one part of the force transmission reaches the main shaft 12 via the first power path. An alternative further part of the force transmission reaches the intermediate shaft 13 via the second power path 29.

[0029] The range sub-transmission 17 is arranged at the output side of the main transmission 11. The range sub-transmission 17 is arranged coaxially with respect to the main shaft 12. The range sub-transmission 17 has exactly three shafts 18, 20, 21, precisely a first shaft 18, a second shaft 20 and a third shaft 21. The range sub-transmission 17 has the first shaft 18, which is connected to the main shaft 12 in a rotationally fixed manner. The first shaft 18 is designed as a solid shaft. The first shaft 18 is advantageously designed as an integral part of the main shaft 12. To this end, the first shaft 18 is arranged coaxially with respect to the main shaft 12 and is connected thereto in a rotationally fixed manner. Furthermore, the range sub-transmission 17 has the second shaft 20, which is connected to the transmission output shaft 19 in a rotationally fixed manner. The second shaft 20 is formed by a solid shaft. In addition, the range sub-transmission 17 has the third shaft 21. The third shaft 21 is formed by a hollow shaft. The range sub-transmission 17 is designed as a planetary gear mechanism configuration. The range sub-transmission 17 has a planetary gear set PI. The planetary gear set PI is designed as a single planetary gear set. The planetary gear set PI is arranged in a third gear plane Z3 of the gear planes Z1, Z2, Z3. The first planetary gear set PI forms the third gear plane Z3. The range sub-transmission 17 has a sun wheel PI 1. The first shaft 18 is connected to the sun wheel PI 1 in a rotationally fixed manner. The range sub-transmission 17 has a planet carrier PI 2. The second shaft 20 is connected to the planet carrier PI 2 in a rotationally fixed manner. The range sub-transmission 17 has a ring gear PI 3. The third shaft 21 is connected to the ring gear PI 3 in a rotationally fixed manner. In addition, the range sub-transmission 17 has a plurality of planet gears PI 4, which are arranged by the planet carrier PI 2 along a circular path around the sun wheel PI 1. The range sub-transmission 17 also has a linkage shift unit S5. The linkage shift unit S5 is provided for engaging the second shaft 20 to the third shaft 21 in a rotationally fixed manner. The linkage shift unit S5 is provided for engaging the second shaft 20 to the third shaft 21 in a rotationally fixed manner in order to interlock the planetary gear set PI.

[0030] The first gear plane Z1 of the gear planes Z1, Z2, Z3 is closest to the transmission input shaft 23 with regard to the remaining gear planes Z2, Z3. The first gear plane Z1 is designed as a single cylindrical gear plane. The second gear plane Z2 of the gear planes Z1, Z2, Z3 is closest to the first gear plane Z1 with regard to the remaining gear plane Z3. The second gear plane Z2 is designed as a single cylindrical gear plane. The third gear plane Z3 is designed as a planetary gear set plane.

[0031] The group transmission device 10 comprises a plurality of shift units S1, S2, S3, S4. The group transmission device 10 comprises four shift units S1, S2, S3, S4 and one linkage shift unit S5. The linkage shift unit S5 is arranged axially behind the planetary gear set P1 of the third gear plane Z3 seen in the torque flow direction 31. The linkage shift unit S5 is arranged axially between the planetary gear set P1 and the driven gear 30 seen in the torque flow direction 31. The linkage shift unit S5 is arranged coaxially with regard to the main shaft 12.

[0032] The group transmission device 10 further has a first shift unit S1. The first shift unit S1 is arranged axially behind the planetary gear set P1 of the third gear plane Z3 seen in the torque flow direction 31. The first shift unit S1 is arranged axially between the planetary gear set P1 and the driven gear 30 seen in the torque flow direction 31. The first shift unit S1 is arranged coaxially with regard to the main shaft 12. The first shift unit S1 is provided for connecting the third shaft 21 in a rotationally fixed manner to the housing 22.

[0033] The first shift unit S1 and the linkage shift unit S5 combine to a double shift unit with a unique sliding sleeve S11. The double shift unit is designed as a dog shift unit. The double shift unit has the sliding sleeve S11 as a shift element. The sliding sleeve S11 is designed to be axially movable by a further not visible actuator. The double shift unit has three engagement pieces 32, 33, 34. A first engagement piece 32 of the engagement pieces 32, 33, 34 is arranged axially in front of a second engagement piece 33 of the engagement pieces 32, 33, 34 seen in the torque flow direction 31. The second engagement piece 33 is arranged axially in front of a third engagement piece 34 of the engagement pieces 32, 33, 34 seen in the torque flow direction 31. The first engagement piece 32 of the double shift unit is permanently connected in a rotationally fixed manner to the housing 22. The second engagement piece 33 of the double shift unit is permanently connected in a rotationally fixed manner to the third shaft 21. The third engagement piece 34 is permanently connected in a rotationally fixed manner to the transmission output shaft 19 and the second shaft 20.

[0034] The double shift unit has a third shift position. The double shift unit is configured to connect the third shaft 21 to the housing 22 in the third shift position. In the third shift position of the double shift unit, the first engagement element 32 and the third engagement element 34 are engaged by the shift sleeve Sll.

[0035] The double shift unit has a second shift position. The double shift unit is configured to interlock the planetary gear set Pl in the second shift position. The double shift unit is configured to connect the planet carrier P12 of the planetary gear set Pl to the ring gear P13 of the planetary gear set Pl in the second shift position. In the second shift position of the double shift unit, the second engagement element 33 and the third engagement element 34 are engaged by the shift sleeve Sll.

[0036] The double shift unit has a neutral position. In the neutral position, the double shift unit is not active. In the neutral position of the double shift unit, no engagement of the engagement elements 32, 33, 34 of the double shift unit by the shift sleeve Sll takes place. In the neutral position of the double shift unit, the shift sleeve Sll of the double shift unit is only engaged to the second engagement element 33 of the double shift unit.

[0037] The group transmission device 10 comprises a second shift unit S2. The second shift unit S2 is arranged axially in front of the planetary gear set Pl in the torque flow direction 31. The second shift unit S2 is arranged axially behind the second gear plane Z2 in the torque flow direction 31. The second shift unit S2 is arranged coaxially with respect to the main shaft 12. The second shift unit S2 has a shift element S21. The shift element S21 is designed as a shift sleeve. The second shift unit S2 is configured for connecting the third shaft 21 to the first cylindrical gear 15 in a rotationally fixed manner. The second shift unit S2 is configured to connect the ring gear P13 of the range gear set 17 to the first cylindrical gear 15 of the cylindrical gear set 14 in a rotationally fixed manner. The second shift unit S2 is configured for engaging the ring gear P13 of the range gear set 17 to the second cylindrical gear 16 of the cylindrical gear set 14. The second shift unit S2 has two shift positions. The second shift unit S2 has a first shift position. The second shift unit S2 is configured to connect the ring gear P13 of the range gear set 17 to the first cylindrical gear 15 of the cylindrical gear set 14 in a rotationally fixed manner in the first shift position of the second shift unit S2, in turn engaging the ring gear P13 of the range gear set 17 to the intermediate shaft 13. The second shift unit S2 has a neutral position. In the neutral position, the second shift unit S2 is not active.

[0038] The group transmission device 10 comprises a third shift unit S3. The third shift unit S3 is arranged axially behind the further cylindrical gear pair 26 seen in the direction of the torque flow 31. The third shift unit S3 is arranged axially in front of the cylindrical gear pair 14 seen in the direction of the torque flow 31. The third shift unit S3 is arranged coaxially with respect to the main shaft 12. The third shift unit S3 is designed to connect the first cylindrical gear wheel 15 to the first shaft 18 of the range gear 17 against rotation. The third shift unit S3 is designed to join the main shaft 12 to the second cylindrical gear wheel 16.

[0039] The third shift unit S3 is designed as a dog shift unit. The third shift unit S3 has a further shift element S31. The further shift element S31 is composed of a sliding sleeve. The third shift unit S3 has three engaging pieces 35, 36, 37. A first engaging piece 35 of the engaging pieces 35, 36, 37 is arranged axially in front of a second engaging piece 36 of the engaging pieces 35, 36, 37 seen in the direction of the torque flow 31. The second engaging piece 36 is arranged axially in front of a third engaging piece 37 of the engaging pieces 35, 36, 37 seen in the direction of the torque flow 31. The first engaging piece 35 of the third shift unit S3 is permanently connected against rotation to the third cylindrical gear wheel 27 of the further cylindrical gear pair 26. The second engaging piece 36 of the third shift unit S3 is permanently connected against rotation to the main shaft 12. The third engaging piece 37 is permanently connected against rotation to the first cylindrical gear wheel 15 of the cylindrical gear pair 14.

[0040] The third shift unit S3 has three shift positions. The third shift unit S3 has a first shift position. The third shift unit S3 is designed to connect the third cylindrical gear wheel 27 of the further cylindrical gear pair 26 to the main shaft 12 against rotation in the first shift position. In the first shift position of the third shift unit S3, the first engaging piece 35 and the second engaging piece 36 are joined by the further shift element S31.

[0041] The third shift unit S3 has a second shift position. The third shift unit S3 is designed to connect the first cylindrical gear wheel 15 of the cylindrical gear pair 14 to the main shaft 12 against rotation in the second shift position. In the second shift position of the third shift unit S3, the second engaging piece 36 and the third engaging piece 37 are joined by the further shift element S31.

[0042] The third shift unit S3 has a neutral position. In the neutral position, the third shift unit S3 is not active. In the neutral position of the third shift unit S3, no joining of the engaging pieces 35, 36, 37 of the third shift unit S3 by the further shift element S31 takes place. In the neutral position of the third shift unit S3, the further shift element S31 of the third shift unit S3 is only joined to the second engaging piece 36 of the third shift unit S3.

[0043] The group transmission device 10 has a plurality of gear formation possibilities. The group transmission device 10 has at least four gear formation possibilities, wherein further not executed gears depending on the gear formation possibility can be switched, in particular by the front sub-transmission 24.

[0044] In the first gear formation possibility, the double shift element is in the second gear, the second shift element S2 is in the first gear and the fourth shift element S4 is open, so that a power transmission via the intermediate shaft 13 takes place.

[0045] In the second gear formation possibility, the double shift element is in the neutral, the second shift element S2 is in the first gear and the fourth shift element S4 is closed. The second gear formation possibility forms a power split gear, wherein the power split takes place in a not further shown front planetary gear set of the front sub-transmission 24 and the power combination takes place in the planetary gear set PI of the double sub-transmission 17.

[0046] In the third gear formation possibility, the double shift element is in the first gear, so that the ring gear PI 3 is braked, the second shift element S2 is in the first gear, so that the intermediate shaft 13 is also braked, and the fourth shift element S4 is closed. The third gear formation possibility forms a fast gear via the main shaft 12.

[0047] In the fourth gear formation possibility, the double shift element is in the first gear, so that the ring gear PI 3 is braked, the second shift element S2 is in the neutral and the fourth shift element S4 is open, so that a power transmission via the intermediate shaft 13 takes place.

[0048] Thus, the cylindrical gear pair 14 is available not only for the power split gear, in particular the second gear formation possibility, but also for the conventional gear, in particular the fourth gear formation possibility.

[0049] If the double shift element is in the first gear, the double sub-transmission 17 is in the "low gear" state. The gear stage can be used here as an independent gear by the third shift element S3. In order to prepare the double sub-transmission 17 for the switching of the high gear, the cylindrical gear pair 14 is engaged to the ring gear PI 3 in the group transmission device 10 by means of the shift element S21 of the second shift element S2. Thus, the intermediate shaft 13 is also directly engaged to the ring gear PI 3 and indirectly to the housing 22. The high gear of the main transmission 11 is now present.

[0050] When the gear is shifted over, the double shift element is placed in the neutral without torque. This is either carried out by adjusting the engine torque to zero or by increasing the torque on the intermediate shaft 13 or reducing the torque on the main shaft 12. Then, the number of revolutions is adjusted to the next target gear and the double shift element is shifted to the second gear.

[0051] The shifting in the high-speed gear group takes place in particular by switching the second shift unit S3 into neutral. The power shift can take place at this time by means of a torque reduction at the countershaft 13.

[0052] The downshifting takes place in particular in the reverse order.

[0053] List of reference signs

[0054] 10 Group transmission device

[0055] 11 Main box

[0056] 12 Main shaft

[0057] 13 Countershaft

[0058] 14 Cylinder gear pair

[0059] 15 Cylinder gear

[0060] 16 Cylinder gear

[0061] 17 Multiplication sub-box

[0062] 18 Shaft

[0063] 19 Transmission output shaft

[0064] 20 Shaft

[0065] 21 Shaft

[0066] 22 Box body

[0067] 23 Transmission input shaft

[0068] 24 Front sub-box

[0069] 25 Shaft

[0070] 26 Cylinder gear pair

[0071] 27 Cylinder gear

[0072] 28 Cylinder gear

[0073] 29 Power path

[0074] 30 Driven gear

[0075] 31 Torque flow direction

[0076] 32 Engagement

[0077] 33 Engagement

[0078] 34 Engagement

[0079] 35 Engagement

[0080] 36 joint

[0081] 37 joint

[0082] P1 planetary gearset

[0083] P11 sun gear

[0084] P12 planet carrier

[0085] P13 ring gear

[0086] P14 planet gear

[0087] S1 shift unit

[0088] S11 sliding sleeve

[0089] S2 shift unit

[0090] S21 shift element

[0091] S3 shift unit

[0092] S31 further shift element

[0093] S4 shift unit

[0094] S5 linkage shift unit

[0095] Z1 gear plane

[0096] Z2 gear plane

[0097] Z3 gear plane

Claims

1. A group transmission device, which is a split transmission, comprising a main box (11) having a main shaft (12), an intermediate shaft (13) and a cylindrical gear pair (14) comprising a first cylindrical gear (15) arranged coaxially and axially overlapping in relation to the main shaft (12) and a second cylindrical gear (16) arranged coaxially and axially overlapping in relation to the intermediate shaft (13), a multiple range sub-box (17) in a planetary gear mechanism configuration arranged coaxially in relation to the main shaft (12), the multiple range sub-box having a first shaft (18) permanently rotationally fixed to the main shaft (12), a second shaft (20) rotationally fixed to a transmission output shaft (19), a third shaft (21) and a linkage shift unit (S5), a first shift unit (SI) arranged for rotationally fixing the third shaft (21) to a box body (22) and a second shift unit (S2) having exactly one axially movable shift element (S21) and arranged for rotationally fixing the third shaft (21) to the first cylindrical gear (15), wherein The main shaft (12) is non-rotatably joined or joinable to a transmission input shaft (23), characterized in that a third shift element (S3) is provided, which has exactly one further axially movable shift element (S31) and is designed to non-rotatably connect the first cylindrical gear (15) to a first shaft (18) of the range gearbox (17), a front gearbox (24) is provided, which is arranged upstream of the main shaft (12) and has a further shaft (25) that is connectable to the main shaft by means of a fourth shift element (S4), the further shaft forms a first output shaft of the front gearbox and a first power path from the front gearbox of the group transmission arrangement, the first shift element (S1) and the linkage shift element (S5) form a double shift element with a unique sliding sleeve (S11), the front gearbox (24) has a second power path (29), wherein the front gearbox (24) can be directly joined to the intermediate shaft (13) of the main gearbox (11) by means of the second power path (29), the force transmission of the group transmission arrangement designed as a power split transmission is split in the front gearbox, at least one part of the force transmission reaching the main shaft via the first power path and another part of the force transmission reaching the intermediate shaft via the second power path, a power split gear is formed in such a way that the double shift element is in neutral, the second shift element (S2) non-rotatably connects the third shaft to the first cylindrical gear, and the fourth shift element (S4) is closed, the further shaft being connected to the main shaft.

2. The group transmission device according to claim 1, characterized in that The range gearbox (17) has exactly three shafts (18; 20; 21), namely the first shaft (18), the second shaft (20) and the third shaft (21).

3. A group transmission device according to claim 1 or 2, characterized in that The further shift element (S31) of the third shift element (S3) is designed to join the main shaft (12) to the second cylindrical gear (16).

4. A group transmission device according to claim 1 or 2, characterized in that The range gearbox (17) has a sun gear (P11), wherein the first shaft (18) is non-rotatably connected to the sun gear (P11).

5. A group transmission device according to claim 1 or 2, characterized in that The range gearbox (17) has a planet carrier (P12), wherein the second shaft (20) is non-rotatably connected to the planet carrier (P12).

6. The group transmission device according to claim 1 or 2, characterized in that The range gearbox (17) has a ring gear (P13), wherein the third shaft (21) is non-rotatably connected to the ring gear (P13).

7. The group transmission device according to claim 1 or 2, characterized in that The linkage shift element (S5) is designed to non-rotatably join the second shaft (20) to the third shaft (21).

8. The group transmission device according to claim 1 or 2, characterized in that The main shaft (12) is designed as a solid shaft.

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