DE102010063503B4 - Planetary multi-stage gearbox - Google Patents

Abstract

Multi-stage transmission of planetary design, in particular splitter transmission of a working machine, with a housing (1) in which four planetary sets (4, 5, 6, 7) and several shafts are accommodated, and with shifting elements which are activated by at least one brake (8, 9) and Couplings (10, 11, 12; 10, 11, 23; 10, 11, 26) are formed and by means of their targeted actuation eight different transmission ratios between an input (2; 20; 22) and an output shaft (3; 19) can be represented are, wherein a third shaft (13; 25) is connected to a sun gear of a third planetary gear set (6) and can be coupled by means of a first clutch (10) to a fourth shaft (14) which is connected to a carrier of a second planetary gear set (5) in A fifth shaft (15) connects a ring gear of the second planetary gearset (5) to a ring gear of the third planetary gearset (6) and can be releasably coupled to the output shaft (3; 19) via a second clutch (11), wherein furthermore a sixth shaft (16; 21) is coupled to a sun wheel of the second planetary gear set (5) and can be fixed to the housing (1) by means of a first brake (8), the drive shaft (2; 20; 22) being connected to a carrier of the third planetary gear set (6), wherein a sun gear of a fourth planetary gear set (7) is connected to an eighth shaft (18) which can be fixed to the housing (1) via a second brake (9), wherein a carrier of the fourth planetary gear set (7) is connected to the output shaft (3) and a ring gear of the fourth planetary gear set (7) is coupled to the fourth shaft (14) and either the sixth shaft (16) can also be connected by means of a third clutch (12) to a seventh shaft (17) which is connected to a ring gear of a first planetary gear set (4), with a carrier of the first planetary gear set (4) being connected to the third shaft (13) and a sun wheel of the first planetary gear set (4) being connected to the drive shaft (2), or the drive shaft (22) also being connected by means of a third Coupling (23) can be connected to a seventh shaft (24) which is coupled to a sun gear of a first planetary gear set (4), a carrier of the first planetary gear set (4) being connected to the third shaft (13) and a ring gear of the first planetary gear set ( 4) is connected to the sixth shaft (21) or the third shaft (25) can also be connected by means of a third clutch (26) to a seventh shaft (27) which is coupled to a carrier of a first planetary gear set (4), wherein a ring gear of the first planetary set (4) is connected to the sixth shaft (21) and a sun gear of the first planetary set (4) is connected to the drive shaft (2).

Description

The invention relates to a multi-stage transmission in planetary design, in particular a splitter transmission of a work machine, with a housing in which four planetary gear sets and several shafts are accommodated, and with shifting elements, which are formed by at least one brake and clutches and, by means of their targeted actuation, eight different transmission ratios between a drive shaft and a driven shaft can be represented.

Such a multi-stage transmission is preferably used as a splitter transmission in working machines, with the gears that can be displayed in the splitter transmission being defined by a targeted actuation of shifting elements and a power flow that is effective within planetary sets. A “splitter gearbox” is usually used to describe a gearbox unit with which several transmission ratios with small increments can be represented. In an overall transmission of an agricultural working machine, such as a tractor, such a splitter transmission is usually combined as a powershift transmission with another multi-speed transmission in the form of a group transmission with high increments, so that this combination results in an overall transmission with a large number of gears that can be represented while at the same time being higher spread is achievable. Additional transmission units in the form of a crawler gear unit and/or a turning unit are often added.

From the EP 0495942 B1 is a multi-stage transmission in planetary design, which is combined as a splitter transmission of an agricultural machine with a group transmission. In this case, this splitter transmission has a housing in which four planetary gear sets and a plurality of shafts are arranged, one of which represents the input shaft and the other represents the output shaft of the multi-stage transmission. In addition, several shifting elements are provided in the area of the shafts, by means of which the power flow varies within the four planetary gearsets and different transmission ratios between the input and output shafts can be defined by means of their targeted actuation. A total of eight transmission ratios of the multi-stage transmission can be represented as a result.

The DE 10 2008 015 919 A1 discloses an automatic transmission having an input member, an output member, four planetary gear sets, multiple coupling members, and multiple torque-transmitting devices. Each of the planetary gear sets includes a first, second, and third member. The torque-transmitting devices can be either clutches or brakes.

US 2010/0 144 486 A1 describes a multiple element transmission to provide at least nine forward gears and one reverse gear. The transmission includes four planetary gear sets, six torque-transmitting devices, and four fixed connections. The six torque-transmitting devices provide connections between various gear elements and the transmission housing and operate in combinations of three.

It is the object of the present invention to propose a multi-speed transmission of the type mentioned at the beginning, by means of which a large number of transmission ratios can be realized with a small number of components and thus with a low weight and low manufacturing costs. Furthermore, an almost geometric gear ratio series should be possible, and the loads on the individual gear elements should be reduced. In addition, small and almost geometric increments between the individual transmission ratios and a compact design should be possible. Finally, high gearing efficiencies should be achievable.

This object is solved by claims 1 and 2. The dependent claims that follow reflect advantageous developments of the invention.

Accordingly, in a first alternative, a multi-stage transmission according to the invention in planetary design is proposed, in particular a splitter transmission of a working machine, with a housing in which four planetary gear sets and several shafts are accommodated, and with shifting elements, which are formed by at least one brake and clutches and by means of which they can be shifted more specifically Actuation eight different transmission ratios between an input and an output shaft can be represented, with a third shaft connected to a sun gear of a third planetary gear set and by means of a first clutch with a fourth shaft can be coupled, which is connected to a carrier of a second planetary gear set, wherein a fifth shaft connects a ring gear of the second planetary gearset with a ring gear of the third planetary gearset and can be releasably coupled to the output shaft via a second clutch, wherein a sixth shaft is also coupled to a sun gear of the second planetary gearset and can be fixed to the housing by means of a first brake, wherein the Drive shaft is connected to a web of the third planetary gear set and where either
the sixth shaft can also be connected to a seventh shaft by means of a third clutch, which is connected with a ring gear of a first planetary gear set is coupled, wherein a carrier of the first planetary gear set is connected to the third shaft and a sun gear of the first planetary gear set is connected to the drive shaft or
the sixth shaft can also be connected by means of a third clutch to a seventh shaft, which is coupled to a ring gear of a first planetary gear set, with a carrier of the first planetary gear set being connected to the third shaft and a sun gear of the first planetary gear set being connected to the drive shaft and a sun gear a fourth planetary gear set is connected to an eighth shaft, which can be fixed to the housing via a second brake,
wherein a carrier of the fourth planetary gear set is coupled to the output shaft and a ring gear of the fourth planetary gear set is coupled to the fourth shaft or
the drive shaft can also be connected to a seventh shaft by means of a third clutch, which is coupled to a sun gear of a first planetary set, with a carrier of the first planetary set being connected to the third shaft and a ring gear of the first planetary set being connected to the sixth shaft and a sun gear a fourth planetary gear set is connected to an eighth shaft, which can be fixed to the housing via a second brake, with a carrier of the fourth planetary gear set being coupled to the output shaft and a ring gear of the fourth planetary gear set being coupled to the fourth shaft or
the third shaft can also be connected by means of a third clutch to a seventh shaft, which is coupled to a carrier of a first planetary set, with a ring gear of the first planetary set being connected to the sixth shaft and a sun gear of the first planetary set being connected to the drive shaft and a sun gear a fourth planetary gear set is connected to an eighth shaft, which can be fixed to the housing via a second brake, a web of the fourth planetary gear set being coupled to the output shaft and a ring gear of the fourth planetary gear set to the fourth shaft.

Furthermore, in a second alternative, a multi-stage transmission according to the invention in planetary design is proposed, in particular a splitter transmission of a working machine, with a housing in which four planetary gear sets and several shafts are accommodated, and with shifting elements, which are formed by at least one brake and clutches and by means of which Actuation eight different transmission ratios between an input and an output shaft can be represented, with a third shaft connected to a sun gear of a third planetary gear set and by means of a first clutch with a fourth shaft can be coupled, which is connected to a carrier of a second planetary gear set, wherein a fifth shaft connects a ring gear of the second planetary gearset with a ring gear of the third planetary gearset and can be releasably coupled to the output shaft via a second clutch, wherein a sixth shaft is also coupled to a sun gear of the second planetary gearset and can be fixed to the housing by means of a first brake, wherein the drive shaft is connected to a carrier of the third planetary gearset, the sixth shaft also being connectable by means of a third clutch to a seventh shaft which is coupled to a ring gear of a first planetary gearset, a carrier of the first planetary gearset being connected to the third shaft and a sun gear of the first planetary gear set is connected to the drive shaft and where either
the output shaft can be releasably connected via a fourth clutch to an eighth shaft which is coupled to a carrier of a fourth planetary set, with a ring gear of the fourth planetary set being non-rotatably connected to the fourth shaft and a sun gear of the fourth planetary set being connected to the housing or
the fourth shaft can be releasably connected via a fourth clutch to an eighth shaft, which is coupled to a ring gear of a fourth planetary set, with a carrier of the fourth planetary set being connected to the output shaft and a sun gear of the fourth planetary set being connected to the housing in a rotationally fixed manner.

As is known, a simple minus planetary gearset comprises a sun gear, a ring gear and a carrier which carries planetary gears in a rotatable manner, which respectively mesh with the sun gear and the ring gear. When the web is fixed, the ring gear rotates in the opposite direction to the sun gear.

In contrast to this, a simple plus planetary gearset comprises a sun gear, a ring gear and a carrier which carries inner and outer planetary gears in a rotatably mounted manner. All inner planetary gears mesh with the sun gear and all outer planetary gears with the ring gear, with each inner planetary gear also meshing with one outer planetary gear. If the web is stuck, the ring gear rotates in the same direction as the sun gear.

The drive shaft preferably serves as a drive for the multi-speed transmission, ie for introducing a torque into the multi-speed transmission. It can therefore be driven in particular by a drive motor, for example an internal combustion engine or an electric motor. Accordingly, the output shaft preferably serves as an output of the multi-speed transmission, ie for tapping off a torque from the multi-speed transmission, in particular for operating a unit, for example a pump or an electric generator, or a vehicle drive, for example a vehicle wheel or a vehicle crawler track.

According to the first alternative, a first transmission ratio is obtained by engaging both brakes and the first clutch, whereas a second transmission ratio can be shifted by actuating both brakes and the third clutch. A third gear ratio is selected by engaging the second brake and the first and third clutches. In addition, a fourth transmission ratio is obtained by actuating the second brake and the second and third clutch, and a subsequent fifth transmission ratio by engaging the second brake and the first and second clutch. A sixth gear ratio is shifted by actuating all clutches, while a seventh gear ratio can be achieved by engaging the first brake and the first and second clutches. Finally, an eighth gear ratio is obtained by actuating the first brake and the second and third clutches.

According to the second alternative, a first transmission ratio is obtained by engaging the first brake and the first and fourth clutches, whereas a second transmission ratio is shifted by actuating the first brake and the third and fourth clutches. A further, third transmission ratio can be achieved by engaging the first, third and fourth clutch. Furthermore, a fourth transmission ratio is obtained by actuating the second, third, and fourth clutch, and a fifth transmission ratio can be selected by engaging the first, second, and fourth clutch. Furthermore, a sixth transmission ratio is switched by actuating the first, second and third clutch, while a seventh transmission ratio can be achieved by engaging the first brake and the first and second clutch. Finally, an eighth gear ratio is obtained by actuating the first brake and the second and third clutches.

Preferably, a stationary gear ratio of the first planetary gearset is -2.776, a stationary gear ratio of the second planetary gearset is -1.600, a stationary gear ratio of the third planetary gearset is -2.136 and a stationary gear ratio of the fourth planetary gearset is -1.629.

In a further development of the invention, the drive shaft of the multi-speed transmission is passed through the multi-speed transmission to implement an auxiliary output and serves as an additional second output in addition to the output shaft, for example in the sense of a PTO output for interchangeable auxiliary units.

In principle, the invention also includes versions of the multi-speed transmission in which the input and output are kinematically interchanged. In this case, the named output shaft of the multi-speed gearbox serves as its drive, i.e. for introducing a torque into the multi-speed gearbox, for example by means of a drive motor, and the named drive shaft of the multi-speed gearbox serves as its output, i.e. for tapping a torque from the multi-speed gearbox, for example for operating a unit or vehicle drive. In a shift pattern of the multi-speed transmission, the sequence of the transmission ratios is then reversed accordingly.

• 1 eine schematische Ansicht einer ersten bevorzugten Ausführungsform eines erfindungsgemäßen Mehrstufengetriebes;
• 2 ein beispielhaftes Schaltschema für ein Mehrstufengetriebe gemäß 1;
• 3 eine schematische Ansicht einer zweiten bevorzugten Ausführungsform eines erfindungsgemäßen Mehrstufengetriebes;
• 4 eine schematische Ansicht einer dritten bevorzugten Ausgestaltung eines erfindungsgemäßen Mehrstufengetriebes;
• 5 eine schematische Ansicht einer weiteren, vierten bevorzugten Ausführungsform eines erfindungsgemäßen Mehrstufengetriebes;
• 6 eine schematische Darstellung einer fünften bevorzugten Ausgestaltung eines erfindungsgemäßen Mehrstufengetriebes;
• 7 eine schematische Ansicht einer weiteren, sechsten bevorzugten Ausführungsform eines erfindungsgemäßen Mehrstufengetriebes.

Further measures improving the invention are presented in more detail below together with the description of preferred embodiments of the invention. It shows:

• 1 a schematic view of a first preferred embodiment of a multi-speed transmission according to the invention;
• 2 an exemplary shift pattern for a multi-speed transmission according to 1 ;
• 3 a schematic view of a second preferred embodiment of a multi-speed transmission according to the invention;
• 4 a schematic view of a third preferred embodiment of a multi-speed transmission according to the invention;
• 5 a schematic view of another, fourth preferred embodiment of a multi-speed transmission according to the invention;
• 6 a schematic representation of a fifth preferred embodiment of a multi-speed transmission according to the invention;
• 7 a schematic view of a further, sixth preferred embodiment of a multi-speed transmission according to the invention.

Out of 1 shows a first preferred embodiment of a multi-speed transmission according to the invention, which is preferably a splitter transmission of an overall transmission of an agricultural machine. Within the overall transmission, such a splitter transmission is used as a powershift transmission, usually in combination with a group transmission, so that the splitter transmission with low increments in combination with the group transmission with usually large increments a very high number of transmission ratios that can be represented and a large achievable spread of the overall transmission is possible. Due to this large number of gears that can be represented, an overall transmission formed in this way is suitable for use in an agricultural working machine, in particular in a farm tractor. Furthermore, a combination with a crawler gear unit and/or a turning unit is also preferred. In principle, a geometric sequence of the individual transmission units in the overall transmission can be freely selected.

How now 1 As can be seen, the multi-speed transmission according to the invention has a housing 1 in which an input shaft 2, an output shaft 3 and four planetary gearsets 4, 5, 6 and 7 are accommodated. In the illustrated embodiment, the planetary gearsets 4, 5, 6 and 7 are each designed as negative planetary gearsets, but it is just as conceivable within the scope of the invention to design at least one of the negative planetary gearsets as a positive planetary gearset. All you have to do is swap a spider and ring gear connection at the same time and increase the static ratio by one compared to the version as a negative planetary gear set. Furthermore, the planetary gearsets 4, 5, 6 and 7 are arranged in the order 4, 5, 6, 7, viewed axially.

Furthermore is off 1 It can be seen that the multi-speed transmission according to the invention comprises a total of five shifting elements, which are composed of two brakes 8 and 9 and three clutches 10, 11 and 12. A spatial arrangement of these switching elements can be arbitrary and is only limited by their dimensions and the external shape. In the present case, the brakes 8 and 9 and the clutches 10, 11 and 12 are each designed as multi-plate shifting elements, although it is also conceivable within the scope of the invention to design these as positive-locking shifting elements or as other frictional shifting elements.

Selective actuation of the shifting elements makes it possible to selectively shift different gear ratios, in this case a total of eight gears, between the input shaft 2 and the output shaft 3 . Furthermore, a total of eight rotatable shafts are accommodated in the housing 1, which in addition to the input shaft 2 and the output shaft 3 by a third shaft 13, a fourth shaft 14, a fifth shaft 15, a sixth shaft 16, a seventh shaft 17 and an eighth Wave 18 are formed.

According to the invention, the third shaft 13 connects a carrier of the first planetary gearset 4 with a sun gear of the third planetary gearset 6 and can also be coupled via the first clutch 10 to the fourth shaft 14, which is connected to a carrier of the second planetary gearset 5 and a ring gear of the fourth planetary gearset 7 is connected. Furthermore, the fifth shaft 15 connects ring gears of the second planetary gear set 5 and the third planetary gear set 6 and can be coupled via the second clutch 11 to the output shaft 3 , which is also connected to a carrier of the fourth planetary gear set 7 .

Furthermore, the sixth shaft 16 is coupled to a sun gear of the second planetary gearset 5 and can be fixed to the housing 1 by means of the first brake 8 and, on the other hand, can be connected via the third clutch 12 to the seventh shaft 17, which is connected to a ring gear of the first planetary gearset 4 is coupled. The eighth shaft 18 is coupled to a sun gear of the fourth planetary gear set 7 and can be connected to the housing 1 in a rotationally fixed manner via the second brake 9 . Finally, the drive shaft 2 connects a sun gear of the first planetary gearset 4 with a carrier of the third planetary gearset 6.

Out of 2 1 shows an exemplary shift pattern of a multi-speed transmission 1 whereby each of the total of eight gear ratios that can be displayed can be displayed by closing three of the five shifting elements and the state of two shifting elements can be varied in order to shift into the respective adjacent gear. The respective transmission ratios i in the individual gear stages, as well as the resulting gear increments φ to the next higher gear in each case, can be taken as an example from the exemplary shift pattern. In principle, the level of the individual transmissions can be freely selected via the level of the standard transmissions of the planetary sets 4, 5, 6 and 7, with the first planetary set 4 preferably having a standard transmission of -2.776, the second planetary set 5 having a standard transmission of -1.600, and the third planetary set 6 has a stationary gear ratio of -2.136 and the fourth planetary gearset 7 has a stationary gear ratio of -1.629. Out of 2 a total spread of 3.093 for the multi-speed gearbox can also be read.

How out 2 shows, there is a first transmission ratio by closing both brakes 8 and 9, as well as the first clutch 10, wherein to switch to the next, second transmission ratio, the first clutch 10 is to be opened and the third clutch 12 is to be actuated. A third transmission ratio, which follows the second transmission ratio, is shifted by opening the first brake 8 and closing the first clutch 10 . Starting from the third gear ratio, there is a fourth gear ratio ratio by reopening the first clutch and actuating the second clutch 11. A fifth transmission ratio can be represented by the third clutch 12 being released and the first clutch 10 being closed, starting from the fourth transmission ratio. Furthermore, a sixth transmission ratio is selected by opening the second brake 9 and closing the third clutch 12. To switch to the next, seventh transmission ratio, the third clutch 12 must be opened again and the first brake 8 must be actuated. Finally, an eighth gear ratio results in that, starting from the seventh gear ratio, the first clutch 10 is opened and the third clutch 12 is actuated.

Out of 3 shows a schematic view of a second preferred embodiment of a multi-speed transmission according to the invention. In contrast to the variant described above, an output runs via an output shaft 19 in this case transversely to the drive via a drive shaft 20, the latter also being extended axially in the direction of the second brake 9. In this way, a front-transverse design of a multi-speed transmission according to the invention is formed, with the planetary gearsets 4, 5, 6 and 7 being connected to one another in accordance with the embodiment according to FIG 1 remain. Accordingly, a circuit diagram of the in 3 shown multi-speed transmission also after 2 .

Furthermore goes out 4 a third preferred embodiment of a multi-speed transmission. In contrast to the embodiment according to 1 In this case, a sixth shaft 21 connects, in addition to a possible coupling to the housing 1 by means of the first brake 8, the ring gear of the first planetary gear set 4 to the sun gear of the second planetary gear set 5. In addition, a drive shaft 22 can be connected to the carrier of the third Planetary gear set 6 are coupled via a third clutch 23 to a seventh shaft 24 which is in communication with the sun gear of the first planetary gear set 4

Here, the structure according to the embodiment 4 equivalent in effect to the design according to 1 , so that in the individual gear ratios and for the same stationary translations of the planetary gearsets 4, 5, 6 and 7, the translations i and the gear jumps φ according to the exemplary shift pattern 2 be reached. The switching of the individual transmission ratios also differs from the description 2 only to the extent that instead of the third clutch 12 in 1 each the third clutch 23 in 4 is to be actuated.

Furthermore, in 5 a fourth preferred embodiment of a multi-speed transmission according to the invention is shown. In contrast to the embodiment according to 1 a third shaft 25 can be connected to a seventh shaft 27 by means of a third clutch 26, which is connected to the carrier of the first Planetary set 4 is coupled. Furthermore, a sixth shaft 21 connects the ring gear of the first planetary gear set 4 to the sun gear of the second planetary gear set 5 and can be fixed to the housing 1 via the first brake 8 .

Also in the case of the fourth embodiment of the multi-speed transmission according to the invention 5 the translations i in the individual transmission ratios, as well as the gear jumps φ according to the exemplary shift pattern, are again shown for the same stationary translations of the planetary gearsets 4 to 7 2 reached. With regard to shifting the individual gears, the description applies 2 to be modified in such a way that instead of the third clutch 12 in 1 each the third clutch 26 in 5 is to be actuated.

In 6 a fifth preferred embodiment of a multi-speed transmission according to the invention is shown. In contrast to the embodiment according to 1 an output shaft 28 , in addition to a possible coupling by means of the second clutch 11 to the fifth shaft 15 , can also be connected via a fourth clutch 29 to an eighth shaft 30 which is coupled to the carrier of the fourth planetary gearset 7 . Furthermore, the sun gear of the fourth planetary gear set 7 is connected to the housing 1 in a torque-proof manner.

Here, the structure according to the embodiment is shown in FIG 6 again have the same effect as in the embodiment according to FIG 1 , so that in the individual gear ratios and with the same stationary translations of the planetary gearsets 4, 5, 6 and 7, the translations i and the gear jumps φ according to the exemplary shift pattern 2 be reached. A circuit of the individual gears also differs from the description 2 only in that instead of the second brake 9 in 1 each the fourth clutch 29 in 6 is to be actuated.

Finally goes out 7 a sixth preferred embodiment of a multi-speed transmission according to the invention. In contrast to the embodiment according to 1 can a fourth shaft 31, in addition to a connection to the carrier of the second planetary gear set 5 and a possible coupling to the third shaft 13 via the first clutch 10, by means of a fourth clutch 32 are connected to an eighth shaft 33. This eighth shaft 33 is further coupled to the ring gear of the fourth planetary gear set 7 . In addition, the sun gear of the fourth planetary gear set 7 is again connected to the housing 1 in a rotationally fixed manner.

Also in the case of the sixth preferred embodiment of the multi-speed transmission according to the invention 7 the translations i in the individual gear steps and the gear jumps φ according to the exemplary shift pattern are shown for the same stationary translations 2 reached. With regard to the switching of the individual transmission ratios, the present variant differs from the one described 2 in that instead of the second brake, 9 in 1 each fourth clutch 32 in 7 is to be actuated.

A splitter transmission for a work vehicle can be achieved with low manufacturing costs and low weight by means of the individual configurations of a multi-speed transmission according to the invention. In addition, the multi-speed transmissions according to the invention have low absolute and relative speeds, as well as low torques for the planetary gear set and shifting elements. Finally, a good gear ratio series and good gearing efficiencies are achieved with almost geometric increments at the same time.

In addition to the embodiments shown in the figures, further configurations of a multi-speed transmission according to the invention are conceivable here, in particular by the various possibilities for arranging the third clutch 4 and 5 with the different positions of a fourth clutch 6 and 7 be combined in each case.

In addition, the multi-speed transmission according to the invention are preferably constructed coaxially, but the output can also, as in the case of the embodiment according to 3 , to the side of the gearbox (parallel to the axis).

According to the invention, it is also possible to provide additional freewheels at any suitable point of the multi-speed transmission, for example between a shaft and the housing, or to connect two shafts if necessary. Furthermore, the output can in principle be arranged anywhere on the respective output shaft and the drive can in principle also be arranged anywhere on the respective drive shaft.

As part of an advantageous development, the respective drive shaft can be separated from a drive motor by a coupling element as required, with a hydrodynamic torque converter, a hydrodynamic clutch, a dry starting clutch, a wet starting clutch, a magnetic particle clutch, a centrifugal clutch, etc. being usable as the clutch element. In addition, it is also possible to arrange such a starting element behind the transmission in the direction of power flow, in which case the respective drive shaft is permanently connected to the crankshaft of the drive motor. Alternatively, one of the shifting elements of the multi-speed transmission can also be used as an internal starting element. This internal launch element should preferably be closed in the potential launch gears, i. H. it is closed during the start-up process.

In addition, it is possible to arrange a torsional vibration damper between the drive motor and the transmission.

Finally, it is also conceivable within the scope of the invention to arrange an electric machine as a generator and/or as an additional drive machine on each of the shafts, preferably on the respective drive shaft or the respective output shaft.

Reference List

1

Housing

2

drive shaft

3

output shaft

4

first set of planets

5

second set of planets

6

third planetary set

7

fourth planetary set

8th

first brake

9

second brake

10

first clutch

11

second clutch

12

third clutch

13

third wave

14

fourth wave

15

fifth wave

16

sixth wave

17

seventh wave

18

eighth wave

19

output shaft

20

drive shaft

21

sixth wave

22

drive shaft

23

third clutch

24

seventh wave

25

third wave

26

third clutch

27

seventh wave

28

output shaft

29

fourth clutch

30

eighth wave

31

fourth wave

32

fourth clutch

33

eighth wave

Claims (6)

Multi-stage transmission of planetary design, in particular splitter transmission of a working machine, with a housing (1) in which four planetary sets (4, 5, 6, 7) and several shafts are accommodated, and with shifting elements which are activated by at least one brake (8, 9) and Couplings (10, 11, 12; 10, 11, 23; 10, 11, 26) are formed and by means of their targeted actuation, eight different transmission ratios can be generated between an input shaft (2; 20; 22) and an output shaft (3; 19), a third shaft (13; 25) having a sun gear of a third planetary gear set (6) connected and can be coupled by means of a first clutch (10) to a fourth shaft (14) which is connected to a carrier of a second planetary gear set (5), a fifth shaft (15) being a ring gear of the second planetary gear set (5) with a ring gear of the third planetary gear set (6) and can be detachably coupled to the output shaft (3; 19) via a second clutch (11), a sixth shaft (16; 21) also being coupled to a sun gear of the second planetary gear set (5) and connected by means a first brake (8) can be fixed on the housing (1), the drive shaft (2; 20; 22) being connected to a carrier of the third planetary gear set (6), a sun wheel of a fourth planetary gear set (7) being connected to an eighth shaft ( 18) which can be fixed to the housing (1) via a second brake (9), a carrier of the fourth planetary gear set (7) being connected to the output shaft (3) and a ring gear of the fourth planetary gear set (7) being connected to the fourth shaft ( 14) is coupled and where either the sixth shaft (16) can also be connected to a seventh shaft (17) by means of a third clutch (12), which is coupled to a ring gear of a first planetary gearset (4), a carrier of the first planetary gearset (4) being connected to the third shaft (13) and a sun gear of the first planetary gear set (4) is connected to the drive shaft (2) or the drive shaft (22) can also be connected by means of a third clutch (23) to a seventh shaft (24) which is coupled to a sun gear of a first planetary gear set (4), a carrier of the first planetary gear set (4) being connected to the third shaft ( 13) and a ring gear of the first planetary gear set (4) is connected to the sixth shaft (21) or the third shaft (25) can also be connected to a seventh shaft (27) by means of a third clutch (26), which is coupled to a carrier of a first planetary gear set (4), with a ring gear of the first planetary gear set (4) being connected to the sixth shaft (21) and a sun gear of the first planetary gear set (4) is connected to the drive shaft (2). Multi-stage transmission of planetary design, in particular splitter transmission of a working machine, with a housing (1) in which four planetary sets (4, 5, 6, 7) and several shafts are accommodated, and with switching elements which are controlled by at least one brake (8) and clutches ( 10, 11, 12, 29; 10, 11, 12, 32) and by means of their targeted actuation, eight different transmission ratios can be achieved between an input (2) and an output shaft (3; 28), with a third shaft (13th ) is connected to a sun gear of a third planetary gear set (6) and can be coupled by means of a first clutch (10) to a fourth shaft (14; 31), which is connected to a carrier of a second planetary gear set (5), a fifth shaft ( 15) connects a ring gear of the second planetary gear set (5) to a ring gear of the third planetary gear set (6) and can be detachably coupled to the output shaft (3; 28) via a second clutch (11), a sixth shaft (16) also having a sun wheel of the second planetary gear set (5) and can be fixed to the housing (1) by means of a first brake (8), the drive shaft (2) being connected to a carrier of the third planetary gear set (6), the sixth shaft (16) also being can be connected to a seventh shaft (17) by means of a third clutch (12), which is coupled to a ring gear of a first planetary gear set (4), a carrier of the first planetary gear set (4) being connected to the third shaft (13) and a sun gear of the first planetary gear set (4) is connected to the drive shaft (2) and either the output shaft (28) can be detachably connected via a fourth clutch (29) to an eighth shaft (30) which is connected to a carrier of a fourth planetary gear set (7) is coupled, wherein a ring gear of the fourth planetary gearset (7) is non-rotatably connected to the fourth shaft (14) and a sun gear of the fourth planetary gearset (7) to the housing (1) or the fourth shaft (31) via a fourth clutch ( 32) can be detachably connected to an eighth shaft (33) which is connected to a ring gear of a fourth planetary gearset (7) is coupled, wherein a web of the fourth planetary gearset (7) is non-rotatably connected to the output shaft (3) and a sun gear of the fourth planetary gearset (7) to the housing (1). multi-speed gearbox claim 1 , characterized in that a first transmission ratio is achieved by engaging both brakes (8, 9) and the first clutch (10), a second transmission ratio by actuating both brakes (8, 9) and the third clutch (12; 23; 26th ), a third transmission ratio by engaging the second brake (9) and the first (10) and third clutch (12; 23; 26), a fourth transmission ratio by actuating the second brake (9) and the second (11) and third clutch (12; 23; 26), a fifth transmission ratio by engaging the second brake (9) and the first (10) and second clutch (11), a sixth transmission ratio by actuating all clutches (10, 11, 12; 10 , 11, 23; 10, 11, 26), a seventh transmission ratio by engaging the first brake (8) and the first (10) and second clutch (11), and an eighth transmission ratio by actuating the first brake (8), and the second (11) and third clutch (12; 23; 26) results. multi-speed gearbox claim 2 , characterized in that a first transmission ratio by engaging the first brake (8) and the first (10) and fourth clutch (29; 32), a second transmission ratio by actuating the first brake (8) and the third (12th ) and fourth clutch (29; 32), a third transmission ratio by closing the first (10), third (12) and fourth clutch (29; 32), a fourth transmission ratio by actuating the second (11), third (12) and fourth clutch (29; 32), a fifth transmission ratio by engaging the first (10), second (11) and fourth clutch (29; 32), a sixth transmission ratio by actuating the first (10), second (11) and third clutch (12), a seventh gear ratio by engaging the first brake (8) and the first (10) and second clutch (11), and an eighth gear ratio by actuating the first brake (8) and the second (11) and third Clutch (12) results. Multi-stage transmission according to one of the preceding claims, characterized in that a stationary translation of the first planetary gearset (4) -2.776, a stationary translation of the second planetary gearset (5) -1.600, a stationary translation of the third planetary gearset (6) -2.136 and a stationary translation of the fourth planetary gearset ( 7) -1.629. Multi-stage transmission according to one of the preceding claims, characterized in that the output shaft (3; 19; 28) serves as input and the drive shaft (2; 20; 22) as output of the multi-stage transmission.

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