DE102010063498B4 - Planetary multi-speed 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 formed by at least one brake and clutches and by means different transmission ratios between an input shaft (2) and an output shaft (3; 23; 24) can be achieved when they are actuated in a targeted manner, with a third shaft (14) connecting a carrier of a second planetary gearset (5) with a carrier of a third planetary gearset (6). and can also be coupled to the drive shaft (2) via a first clutch (10) and to a fourth shaft (15) by means of a second clutch (11), which shaft is connected to a ring gear of a first planetary gear set (4). and can be connected to the output shaft (3; 23; 24) via a third clutch (12), a fifth shaft (16) connecting a sun gear of the second planetary gearset (5) to a sun gear of the third planetary gearset (6) and by means of a first Brake (8) can be fixed on the housing (1), with a sixth shaft (17) also being coupled to a sun gear of the first planetary gearset (4) and a ring gear of the second planetary gearset (5), and a ring gear of the third planetary gearset (6) with a seventh shaft (18; 20; 27) and a carrier of the first planetary set (4) is connected to the drive shaft (2) and either the seventh shaft (18) is also connected to a sun gear of a fourth planetary set (7) and connected to the output shaft ( 3) can be coupled, which is also connected to a carrier of the fourth planetary gear set (7), a ring gear of the fourth planetary gear set (7) being connected to an eighth shaft (19) which is connected to the housing (19) via a second brake (9) 1) can be fixed or the seventh shaft (20) is also connected to a sun gear of a fourth planetary gear set (7) and can be coupled via a fourth clutch (21) to an eighth shaft (22), which in the further course is connected to a ring gear of the fourth planetary gear set ( 7) and can be fixed on the housing (1) by means of a second brake (9), the output shaft (23) also being connected to a carrier of the fourth planetary gearset (7) or the output shaft (24) also being connected to a carrier of a fourth planetary gearset (7) and can be coupled by means of a fourth clutch (25) to an eighth shaft (26), which is connected to a ring gear of the fourth planetary gearset (7) on the one hand and via a second brake (9) on the housing on the other hand (1) can be fixed, wherein the seventh shaft (27) is connected to a sun gear of the fourth planetary gearset (7).

Description

The invention relates to a multi-stage transmission in planetary design, 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 their targeted actuation, different transmission ratios between one Input and an output shaft can be displayed.

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 the shifting elements and via a power flow that is effective in each case within the planetary gearsets. 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 often combined as a powershift transmission with another multi-speed transmission unit in the form of a group transmission with high increments, so that this combination results in an overall transmission with a high number of gears that can be represented with a large one at the same time 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 035 083 A1 discloses a 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 include clutches.

The DE 10 2009 025 608 A1 describes a transmission unit, in particular a motor vehicle transmission unit, with four planetary gears arranged one behind the other along a main axis of rotation, with six coupling units which are provided for shifting at least nine forward gears, with a drive unit, a coupling element, a second planetary gear carrier of the second planetary gearing and a third planetary gear carrier of the third planetary gear, all four of which are non-rotatably connected to each other, and with an output unit, a fourth planetary gear carrier of the fourth planetary gear and a coupling element, all three of which are non-rotatably connected to each other.

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 different transmission ratios between an input and an output shaft can be represented, with a third shaft connecting a carrier of a second planetary gearset with a carrier of a third planetary gearset and also on the one hand via a first clutch with the drive shaft and on the other hand by means of a second clutch with a fourth Shaft can be coupled, which is connected to a ring gear of a first planetary gear set and can be connected to the output shaft via a third clutch, with a fifth shaft connecting a sun gear of the second planetary gear set to a sun gear of the third planetary gear set and can be fixed to the housing by means of a first brake, a sixth shaft being coupled to a sun gear of the first planetary gearset and a ring gear of the second planetary gearset, and a ring gear of the third planetary gearset being connected to a seventh shaft and a carrier of the first planetary gearset being connected to the drive shaft and wherein either the seventh shaft is also connected to a sun gear of a fourth planetary gear set and can be coupled to the output shaft by means of a fourth clutch, which is also connected to a carrier of the fourth planetary gear set, wherein a ring gear of the fourth planetary gear set is connected to an eighth shaft, which can be fixed to the housing via a second brake or the seventh shaft is also connected to a sun gear of a fourth planetary gear set and can be coupled via a fourth clutch to an eighth shaft, which is further connected to a ring gear of the fourth planetary gear set and by means of a second Brake can be fixed on the housing, the output shaft also being connected to a carrier of the fourth planetary gearset or the output shaft also being connected to a carrier of a fourth planetary gearset and being able to be coupled to an eighth shaft by means of a fourth clutch, which on the one hand is connected to a ring gear of the fourth planetary gearset is in connection and on the other hand can be fixed via a second brake on the housing, wherein the seventh shaft is connected to a sun gear of the fourth planetary gear set.

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 different transmission ratios between an input and an output shaft can be represented, with a third shaft connecting a carrier of a second planetary gearset with a carrier of a third planetary gearset and also on the one hand via a first clutch with the drive shaft and on the other hand by means of a second clutch with a fourth Shaft can be coupled, which is connected to a ring gear of a first planetary gear set and can be connected to the output shaft via a third clutch, with a fifth shaft connecting a sun gear of the second planetary gear set to a sun gear of the third planetary gear set and being fixable on the housing by means of a first brake , further wherein a sixth shaft is coupled to a sun gear of the first planetary set and a ring gear of the second planetary set and wherein a ring gear of the third planetary set is connected to a seventh shaft and a carrier of the first planetary set is connected to the drive shaft and either the seventh shaft is also connected to the one can be releasably connected to the output shaft by means of a fourth clutch and the other to an eighth shaft via a fifth clutch, which is then coupled to a sun gear of a fourth planetary gear set, the output shaft being connected to a carrier of the fourth planetary gear set and a The ring gear of the fourth planetary gear set is non-rotatably connected to the housing or the output shaft can also be connected to the seventh shaft via a fourth clutch and to an eighth shaft by means of a fifth clutch, which is coupled to a carrier of a fourth planetary gear set, wherein the seventh shaft is also connected to a sun gear of the fourth planetary gearset and a ring gear of the fourth planetary gearset is non-rotatably connected to the housing.

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, i.e. 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 is preferably used as an output of the multi-speed transmission, i.e. for tapping 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 the second brake and the first and second clutch, whereas a second transmission ratio is shifted by actuating the first and second brake and the second clutch. A third gear ratio is by closing the first and second brake, and the first clutch can be displayed. Furthermore, a fourth gear ratio results from actuating the first and second brakes and the third clutch, and a subsequent fifth gear ratio results from engaging the first brake and the first and third clutch. Furthermore, a sixth transmission ratio is switched by actuating the first brake and the second and third clutch, while a seventh transmission ratio can be represented by closing the second, third and fourth clutch. Alternatively, the seventh transmission ratio can also be shifted by actuating the first, second and fourth clutches. An eighth gear ratio is achieved by engaging the first brake and the second and fourth clutches. Finally, a ninth transmission ratio is obtained by actuating the first brake and the first and fourth clutches. Consequently, a multi-speed transmission according to the invention can be realized with a total of nine gears that can be represented.

In a further development of the invention, a first additional transmission ratio is obtained by engaging the second brake and the second and third clutch, whereas a second additional transmission ratio is engaged by actuating the second brake and the first and third clutch. Another, third, additional transmission ratio can be achieved by engaging the first brake and the third and fourth clutches. Accordingly, the number of gear ratios that can be displayed can be expanded to a maximum of twelve gears.

According to the second alternative, a first transmission ratio is obtained by engaging the first, second and fifth clutches, whereas a subsequent, second transmission ratio is shifted by actuating the first brake and the second and fifth clutch. A third gear ratio can be achieved by engaging the first brake and the first and fifth clutches. Furthermore, a fourth gear ratio results from actuating the first brake and the third and fifth clutch, and another, fifth gear ratio, by engaging the first brake and the first and third clutch. A sixth gear ratio can be achieved by actuating the first brake and the second and third clutches. Furthermore, a seventh gear ratio is shifted by engaging the second, third and fourth clutches or alternatively by actuating the first, second and fourth clutches. An eighth transmission ratio can be achieved by engaging the first brake and the second and fourth clutches, whereas a ninth transmission ratio results from actuating the first brake and the first and fourth clutches. In this case, too, a multi-speed transmission according to the invention can be implemented with a total of nine gears that can be represented.

In a development of this embodiment, a first additional transmission ratio results from closing the second, third and fifth clutch. Furthermore, a further, second, additional transmission ratio can be achieved by actuating the first, third, and fifth clutches, while a third, additional transmission ratio is engaged by engaging the first brake and the third and fourth clutches. This again makes it possible to increase the number of selectable transmission ratios to a maximum of twelve.

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 Darstellung einer zweiten bevorzugten Ausgestaltung eines erfindungsgemäßen Mehrstufengetriebes;
• 4 eine schematische Ansicht einer weiteren, dritten bevorzugten Ausführungsform eines erfindungsgemäßen Mehrstufengetriebes;
• 5 eine schematische Ansicht einer vierten bevorzugten Ausgestaltung eines erfindungsgemäßen Mehrstufengetriebes; und
• 6 eine schematische Ansicht einer weiteren, fünften bevorzugten Ausgestaltung 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 representation of a second preferred embodiment of a multi-speed transmission according to the invention;
• 4 a schematic view of a further, third preferred embodiment a multi-speed transmission according to the invention;
• 5 a schematic view of a fourth preferred embodiment of a multi-speed transmission according to the invention; and
• 6 a schematic view of a further, fifth preferred embodiment of a multi-speed transmission according to the invention.

In 1 a first preferred embodiment of a multi-speed transmission according to the invention is shown, which is preferably a splitter transmission of an overall transmission of a working machine. Within the overall transmission, this splitter transmission is preferably combined as a powershift transmission with another transmission unit in the form of a group transmission, so that this combination of the splitter transmission with low increments and the group transmission with high increments enables a large number of transmission ratios to be displayed and a large gear spread of the entire transmission. Due to the number of gears that can be achieved in this way, such an overall transmission is particularly suitable for use in an agricultural working vehicle, in particular a farm tractor. Furthermore, an additional combination with further transmission units in the form of a crawler gear unit and/or a turning unit preferably takes place. A geometric juxtaposition of the individual transmission units in the overall transmission can in principle be freely selected.

How out 1 shows, takes a - here only partially shown - housing 1 in the multi-speed transmission according to the invention an input shaft 2, an output shaft 3, and three planetary gear sets 4, 5, 6 and 7 on. The multi-speed transmission is designed here in a front-transverse design, in which an output via the output shaft 3 takes place laterally to the drive via the input shaft 2 .

In the present case, the planetary gearsets 4, 5, 6 and 7 are each designed as negative planetary gearsets, although 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 if a spider and a ring gear connection are swapped with one another at the same time and the amount of the Stand ratio is increased by one compared to running as a minus planet set. How further from 1 As can be seen, the planetary gearsets 4, 5, 6 and 7 are arranged in the order 4, 5, 6, 7 when viewed axially, with another axial arrangement also being conceivable.

As also in 1 shown, the multi-speed transmission according to the invention comprises a total of six shifting elements, which are formed by two brakes 8 and 9 and four clutches 10, 11, 12 and 13. 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, 12 and 13 are each designed as multi-plate shifting elements, but an embodiment as positive-locking shifting elements or other frictional shifting elements is also conceivable according to the invention. Selective actuation of these shifting elements enables different transmission ratios to be shifted between the input shaft 2 and the output shaft 3 .

Furthermore, the housing 1 accommodates a total of eight rotatable shafts, which in addition to the input shaft 2 and the output shaft 3 are connected by a third shaft 14, a fourth shaft 15, a fifth shaft 16, a sixth shaft 17, a seventh shaft 18 and an eighth shaft 19 are formed.

According to the invention, the third shaft 14 connects a carrier of the second planetary gearset 5 with a carrier of the third planetary gearset 6 and can also be coupled to the drive shaft 2 via the first clutch 10 and to the fourth shaft 15 by means of the second clutch 11. The fourth shaft 15 is further connected to a ring gear of the first planetary gear set 4 and can be releasably connected to the output shaft 3 via the third clutch 12 . Furthermore, the fifth shaft 16 connects a sun gear of the second planetary gear set 5 to a sun gear of the third planetary gear set 6 and can be fixed on the housing 1 via the first brake 8 .

How further from 1 shows, the sixth shaft 17 connects a sun gear of the first planetary gearset 4 with a ring gear of the second planetary gearset 5. In addition, the output shaft 3 is coupled to a carrier of the fourth planetary gearset 7 and can be connected by means of the fourth clutch 13 to the seventh shaft 18, which in the further course with a ring gear of the third planetary gearset 6 and a sun gear of the fourth planetary gearset 7 is connected. A ring gear of the fourth planetary gear set 7 is also coupled to the eighth shaft 19 which can be fixed to the housing 1 by means of the second brake 9 . Finally, the drive shaft 2 is connected to a web of the first planetary gearset 4 and is also designed to be extended axially in the direction of the fourth planetary gearset 7 . In this case, the drive shaft 2 extends beyond the axial position of the first brake 8 .

Out of 2 1 shows an exemplary shift pattern of a multi-speed transmission 1 out, whereby it can be seen that for representation ment of each individual transmission ratio, three of the six shifting elements are closed and the state of two shifting elements has to be changed in order to switch to the respectively adjacent transmission ratio. The respective transmission ratios i in the individual gear stages and the resulting gear jumps φ for the respectively adjacent transmission ratio can be taken from the example shifting scheme. 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 -2.098, the second planetary set 5 having a standard transmission of -1.778, and the third planetary set 6 has a stationary translation of -2.563 and the fourth planetary gear set 7 has a stationary translation of -1.611. In this case, a transmission spread of 3.631 is sufficient 2 readable.

How also from 2 can be seen, with the multi-speed transmission according to the invention 1 realize a total of nine regular transmission ratios, as well as three additional transmission ratios designated Z1 to Z3. In addition, a seventh gear ratio can be achieved by a further alternative actuation of the shifting elements, which is shown in 2 is denoted by M1.

A first transmission ratio is obtained by engaging the second brake 9 and the first clutch 10 and the second clutch 11, with the first clutch 10 being opened and the first brake 8 being actuated in order to switch to a next, second transmission ratio. Starting from the second transmission ratio, a third transmission ratio that follows the second transmission ratio is shifted by opening the second clutch 11 and actuating the first clutch 10, while for further upshifting into a fourth transmission ratio the first clutch 10 has to be opened again and the third clutch 12 closed is close. Proceeding from this, a fifth transmission ratio is shown in that the second brake 9 is released and the first clutch 10 is closed again. A subsequent sixth transmission ratio is shifted starting from the fifth transmission ratio by again opening the first clutch 10 and actuating the second clutch 11 . The seventh gear ratio is then obtained by opening the first brake 8 and actuating the fourth clutch 13. Alternatively, the seventh gear ratio can also be achieved by actuating the first clutch 10, the second clutch 11 and the fourth clutch 13.

Furthermore, an eighth transmission ratio is obtained by engaging the first brake 8 and the second clutch 11 and the fourth clutch 13, with the second clutch 11 being opened and the first clutch 10 being actuated to shift into a next, ninth transmission ratio.

A first additional transmission ratio, denoted by Z1, can be represented by the second brake 9, as well as the second clutch 11 and the third clutch 12 being closed. Another additional, in 2 The transmission ratio marked Z2 is shifted by engaging the second brake 9 and the first clutch 10 and the third clutch 12, while a further, third additional transmission ratio can be represented by actuating the first brake 8 and the third clutch 12 and the fourth clutch 13 and is denoted by Z3. However, these additional transmission ratios are only to be provided as an option, since placing them in the existing transmission range would lead to increments that are no longer geometric.

In 3 is a schematic view of another, second preferred embodiment of a multi-speed transmission according to the invention. In contrast to the embodiment according to 1 a seventh shaft 20, in addition to being coupled to the ring gear of the third planetary gear set 6 and the sun gear of the fourth planetary gear set 7, can be connected via a fourth clutch 21 to an eighth shaft 22, which is then coupled to the ring gear of the fourth planetary gear set 7 and can be fixed on the housing 1 via the second brake 9 . Furthermore, an output shaft 23 is only connected to the carrier of the fourth planetary gear set 7 and can be coupled to the third shaft 15 by means of the third clutch 12 .

The structure according to the second embodiment 3 simulates a variant of the multi-speed gearbox with the same effect 1 is, so that in the individual gears with the same stationary translations of the planetary sets 4 to 7, the translations i and the gear jumps φ according to the exemplary shift pattern 2 be reached. With regard to the switching of the individual transmission ratios, the description applies 2 to be modified in such a way that instead of the fourth clutch 13 in 1 the fourth clutch 21 in 3 is to be actuated.

A third preferred embodiment of a multi-speed transmission according to the invention is in 4 shown. Different from the variant after 1 is here that an output shaft 24, in addition to a coupling to the web of the fourth planetary gear set 7 and a possible connection to the third shaft 15 by means of the third clutch 12, via a fourth clutch 25 can be coupled to an eighth shaft 26 . This eighth shaft 26 is further connected to the ring gear of the fourth planetary gearset 7 and can be fixed to the housing 1 by means of the second brake 9 . Furthermore, a seventh shaft 27 only connects the ring gear of the third planetary gear set 6 to the sun gear of the fourth planetary gear set 7.

Also the design 4 in turn reproduces a transmission variant with the same effect as the version 1 due to this fact, if the ratios of the planetary gearsets 4 to 7 are the same, the in 2 given values for the translations i, as well as the gear jumps φ achieved. With regard to shifting the individual gears, the description is closed 2 however, to be modified in such a way that instead of the fourth clutch 13 in 1 each fourth clutch 25 in 4 is to be actuated.

Furthermore goes out 5 another, fourth embodiment of a multi-speed transmission according to the invention. This differs from the variant according to 1 to the effect that a seventh shaft 28 is only connected to a ring gear of the third planetary gear set 6 and can be coupled to the output shaft 3 via the fourth clutch 13 and to an eighth shaft 30 by means of a fifth clutch 29 . This eighth shaft 30 is then connected to the sun gear of the fourth planetary gear train 7 in the further course. In addition, the ring gear of the fourth planetary gear set 7 is connected to the housing 1 in a rotationally fixed manner.

The design according to 5 also reproduces an embodiment of a multi-stage transmission that is identical in effect to the design 1 . Consequently, the transmission scheme is according to 2 also for the design according to 5 applicable, with regard to the switching of the individual gear ratios, the actuation of the second brake 9 in 1 in each case by actuating the fifth clutch 29 in 5 is to be replaced.

Finally goes out 6 a fifth preferred embodiment of a multi-speed transmission according to the invention. In contrast to the design according to 1 an eighth shaft 32 is placed between the carrier of the fourth planetary gear set 7 and an output shaft 31 , which is connected to the carrier of the fourth planetary gear set 7 and can be coupled to the output shaft 31 via a fifth clutch 33 . Furthermore, the ring gear of the fourth planetary gear set 7 is connected to the housing 1 in a rotationally fixed manner.

Also the variant according to 6 again represents a transmission design with the same effect as the embodiment 1 represents, so that the example circuit diagram from 2 in principle also for them 6 can be used. However, with regard to the switching of the individual transmission ratios, this switching scheme must be modified in such a way that instead of the second brake 9 in 1 each the fifth clutch 33 in 6 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.

According to the invention, it is also conceivable to either omit individual shifting elements or to replace them with a rigid connection, resulting in a multi-stage transmission with a reduced number of transmission ratios that can be represented. Would be preferred in the case of the design 1 to make an omission of the fourth clutch 13, which would result in a multi-speed transmission with six gears representable.

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. However, an additional starting clutch, an integrated starting clutch or brake, an additional electric motor or a power shuttle unit/power reversing unit can also be considered as a starting 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 switching elements of the Multi-speed transmission can be used as an internal starting element. This internal starting element should preferably be closed in the potential starting gears, ie it is closed during the starting process.

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

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

fourth clutch

14

third wave

15

fourth wave

16

fifth wave

17

sixth wave

18

seventh wave

19

eighth wave

20

seventh wave

21

fourth clutch

22

eighth wave

23

output shaft

24

output shaft

25

fourth clutch

26

eighth wave

27

seventh wave

28

seventh wave

29

fifth clutch

30

eighth wave

31

output shaft

32

eighth wave

33

fifth clutch

Claims (7)

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 formed by at least one brake and clutches and by means different transmission ratios between an input shaft (2) and an output shaft (3; 23; 24) can be achieved when they are actuated in a targeted manner, with a third shaft (14) connecting a carrier of a second planetary gearset (5) with a carrier of a third planetary gearset (6). and can also be coupled to the drive shaft (2) via a first clutch (10) and to a fourth shaft (15) by means of a second clutch (11), which shaft is connected to a ring gear of a first planetary gear set (4). and can be connected to the output shaft (3; 23; 24) via a third clutch (12), a fifth shaft (16) connecting a sun gear of the second planetary gearset (5) to a sun gear of the third planetary gearset (6) and by means of a first Brake (8) can be fixed on the housing (1), with a sixth shaft (17) also being coupled to a sun gear of the first planetary gearset (4) and a ring gear of the second planetary gearset (5), and a ring gear of the third planetary gearset (6) with a seventh shaft (18; 20; 27) and a carrier of the first planetary gear set (4) is connected to the drive shaft (2) and either the seventh shaft (18) is also connected to a sun gear of a fourth planetary gear set (7) and by means of a fourth clutch (13) to the output shaft (3) can be coupled, which is also connected to a carrier of the fourth planetary gearset (7), a ring gear of the fourth planetary gearset (7) being connected to an eighth shaft (19) which has a second brake (9) on the housing (1) can be fixed or the seventh shaft (20) can also be connected to a sun gear of a fourth planetary gear set (7) and can be coupled via a fourth clutch (21) to an eighth shaft (22), which in the further course can be connected to a ring gear of the fourth planetary gear set (7) and can be fixed to the housing (1) by means of a second brake (9), the output shaft (23) also being connected to a web of the fourth planetary gear set (7) or the output shaft (24) also being connected to a Carrier of a fourth planetary gear set (7) and can be coupled by means of a fourth clutch (25) to an eighth shaft (26), which is connected on the one hand to a ring gear of the fourth planetary gear set (7) and on the other hand via a second brake (9th ) on the housing (1) can be fixed, the seventh wave (27) is connected to a sun gear of the fourth planetary gearset (7). 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 formed by at least one brake and clutches and by means whose targeted actuation various transmission ratios between an input shaft (2) and an output shaft (3; 31) can be represented, with a third shaft (14) connecting a carrier of a second planetary gearset (5) with a carrier of a third planetary gearset (6) and also on the one hand via a first clutch (10) to the drive shaft (2) and on the other hand by means of a second clutch (11) to a fourth shaft (15) which is connected to a ring gear of a first planetary gearset (4) and via a third clutch (12) can be connected to the output shaft (3; 31), a fifth shaft (16) connecting a sun gear of the second planetary gearset (5) to a sun gear of the third planetary gearset (6) and by means of a first brake (8) can be fixed to the housing (1), with a sixth shaft (17) being coupled to a sun gear of the first planetary gearset (4) and a ring gear of the second planetary gearset (5), and a ring gear of the third planetary gearset (6) being coupled to a seventh shaft (18; 28) and a web of the first planetary gearset (4) is connected to the drive shaft (2) and either the seventh shaft (28) can also be releasably connected to the output shaft (3) by means of a fourth clutch (13) and to an eighth shaft (30) via a fifth clutch (29), which is then connected to a sun gear a fourth planetary gear set (7), the output shaft (3) being connected to a carrier of the fourth planetary gear set (7) and a ring gear of the fourth planetary gear set (7) being non-rotatably connected to the housing (1) or the output shaft (31) can also be connected to the seventh shaft (18) via a fourth clutch (13) and to an eighth shaft (32) by means of a fifth clutch (33), which is connected to a carrier of a fourth planetary gear set (7) is coupled, wherein the seventh shaft (18) is also connected to a sun gear of the fourth planetary gearset (7) and a ring gear of the fourth planetary gearset (7) is non-rotatably connected to the housing (1). multi-speed gearbox claim 1 , characterized in that a first transmission ratio by closing the second brake (9) and the first (10) and second clutch (11), a second transmission ratio by actuating the first (8) and second brake (9) and the second clutch (11), a third transmission ratio by closing the first (8) and second brake (9) and the first clutch (10), a fourth transmission ratio by actuating the first (8) and second brake (9) and the third clutch (12), a fifth transmission ratio by engaging the first brake (8) and the first (10) and third clutch (12), a sixth transmission ratio by actuating the first brake (8) and the second (11) and third clutch (12), a seventh transmission ratio by closing the second (11), third (12) and fourth clutch (13; 21; 25) or by actuating the first (10), second (11) and fourth clutch (13); 21; 25), an eighth transmission ratio by closing the first brake (8) and the second (11) and fourth clutch (13; 21; 25), and a ninth transmission ratio by actuating the first brake (8) and the first (10) and fourth clutch (13; 21; 25). multi-speed gearbox claim 3 , characterized in that a first additional transmission ratio by closing the second brake (9) and the second (11) and third clutch (12), a second additional transmission ratio by actuating the second brake (9) and the first (10th ) and third clutch (12), and a third additional transmission ratio by closing the first brake (8), and the third (12) and fourth clutch (13; 21; 25). multi-speed gearbox claim 2 , characterized in that a first transmission ratio by closing the first (10), second (11) and fifth clutch (29; 33), a second transmission ratio by actuating the first brake (8), and the second (11) and fifth Clutch (29; 33), a third transmission ratio by engaging the first brake (8) and the first (10) and fifth clutch (29; 33), a fourth transmission ratio by actuating the first brake (8) and the third ( 12) and fifth clutch (29; 33), a fifth transmission ratio by engaging the first brake (8) and the first (10) and third clutch (12), a sixth transmission ratio by actuating the first brake (8) and the second (11) and third clutch (12), a seventh transmission ratio by closing the second (11), third (12) and fourth clutch (13) or by actuating the first (10), second (11) and fourth clutch (13 ), an eighth transmission ratio by engaging the first brake (8) and the second (11) and fourth clutch (13), and a ninth transmission ratio by actuating the first brake (8) and the first (10) and fourth clutch ( 13) results. multi-speed gearbox claim 5 , characterized in that a first additional transmission ratio by closing the second (11), third (12) and fifth clutch (29; 33), a second additional transmission ratio by actuating the first (10), third (12) and fifth clutch (29; 33), and a third additional transmission ratio by closing the first brake (8) and the third (12) and fourth clutch (13). Multi-stage transmission according to one of the preceding claims, characterized in that the output shaft (3; 23; 24; 31) serves as input and the drive shaft (2) as output of the multi-stage transmission.

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