EP2841801A1

EP2841801A1 - Multi-speed gearbox

Info

Publication number: EP2841801A1
Application number: EP13709418.1A
Authority: EP
Inventors: Stefan Beck; Christian Sibla; Wolfgang Rieger
Original assignee: ZF Friedrichshafen AG
Current assignee: ZF Friedrichshafen AG
Priority date: 2012-04-27
Filing date: 2013-03-13
Publication date: 2015-03-04
Also published as: CN104204610B; WO2013159988A1; US20150119188A1; DE102012207085A1; DE102012207085B4; CN104204610A; US9377085B2

Abstract

The invention relates a four-speed multi-speed gearbox in which a planet carrier (12) of the first planetary gear set (1) is connected to a sun gear (41) of the fourth planetary gear set (4), a ring gear (43) of the fourth planetary gear set (4) is connected to the output shaft (71), a ring gear (13) of the first planetary gear set (1) and a planet carrier (22) of the second planetary gear set (2) can be coupled to the housing (72) by means of a first brake (51), a sun gear (11) of the first planetary gear set (1) can be coupled to the housing (72) by means of a second brake (52), and the ring gear (43) can be coupled to the sun gear (41) respectively of the fourth planetary gear set (4) by means of a first clutch (61). By varying other clutches within the multi-speed gearbox, a set of gearboxes which have similar characteristics are provided.

Description

Mehrstufenqetriebe

The invention relates to a multi-speed planetary gear, in particular for a motor vehicle.

Such multistage transmissions are preferably used as automatic transmissions of motor vehicles, wherein the power flow which is effective in the respective gear ratio within the planetary gear sets is defined by a specific actuation of the shifting elements. The planetary gear sets are usually also connected in an automatic transmission with a slipping action underlying and optionally provided with a lock-up clutch starting element, such as about a hydrodynamic torque converter or a fluid coupling.

From DE 10 2008 000 428 A1 a multi-speed transmission in planetary construction is known, in which four planetary gear sets, and a total of eight rotatable shafts are arranged, one of which represents the drive shaft and another the output shaft of the multi-speed transmission. Furthermore, at least six switching elements are provided in the region of the shafts, by means of whose targeted actuation the power flow within the four planetary gear sets varies and thus different gear ratios between the input and output shafts can be defined. Altogether this means nine forward gears and one reverse gear can be engaged.

The object of the invention is to provide an alternative multi-step transmission, preferably with improved efficiency and sufficiently large and sufficiently uniformly distributed translation series.

The object of the invention is achieved by a multistage transmission according to claim 1. In particular, by a multi-stage transmission, comprising at least four planetary gear sets, a housing, a drive shaft and an output shaft, wherein a web of the first planetary gear set with a sun gear of the fourth planetary gear set netenradsatzes is connected,

a ring gear of the fourth planetary gear set is connected to the output shaft,

a ring gear of the first planetary gear set and a web of the second planetary gear set can be coupled to the housing via a first brake,

a sun gear of the first planetary gear set can be coupled to the housing via a second brake,

the ring gear with the sun gear or the ring gear with the web or the sun gear with the web of each of the fourth planetary gear set can be coupled via a first clutch,

three of the following five connections are constantly executable and two of these five connections are detachable by means of at least one switching element:

Connection of the drive shaft with a sun gear of the second planetary gear set,

Connecting the drive shaft to a sun gear of the third planetary gear set,

Connection of the ring gear of the third planetary gear set with the web of the second planetary gear set,

Connecting the web of the third planetary gear set with a web of the fourth planetary gear set,

Connection of the ring gear of the second planetary gear set with the web of the first planetary gear and

the drive shaft connected to a coupling part of a coupling and the other coupling part with

the bridge of the third planetary gear and the bridge of the fourth planetary gear or

the bridge of the fourth planetary gear or

the ring gear of the third planetary gear set,

constantly connected.

A planetary gear set is understood in particular to mean a wheel set which comprises at least one sun wheel, in that one or more planetary gears mesh, a web which determines the axes of the planetary gears and a ring gear in which the planet gears mesh. Preferably, the ring gear has an internal toothing and the sun gear has an external toothing.

An advantage of the invention may be that the switching elements of the multi-speed transmission, so the gearbox-side brakes and clutches, are easily accessible from the outside. Thus, the actuators such as electric motors, hydraulic valves, hydraulic pumps and the like may be disposed in the vicinity of the switching elements, whereby mechanical and / or hydraulic losses are reduced and a lower energy for the actuation of the switching element may be necessary. Also, less energy may be necessary to keep the switching element in its respective current operating state, ie open or closed, for example, because short lines and the pressure losses are lower. It is also possible to arrange switching elements on the housing and thus at least partially against rotation, whereby seals which connect a stationary line with a rotating line, can be avoided in whole or in part. ,

Also, the spatial arrangement of the easily accessible switching elements simplifies the replacement of the usual hydraulically actuated multi-plate clutches or - brakes by, for example, electro-mechanical or electro-hydraulically actuated brakes and clutches, which are comparatively easy to use driven. Well achievable switching elements are on the one hand brakes, which rotatably couple a shaft with the housing, but also switching elements on outer shafts of the multi-speed transmission, preferably on input or output shaft, which can be supplied comparatively easy to operate hydraulic fluid.

In addition to this property, the multi-speed transmission also has a good toothing efficiency, only small loads on the components, in particular low Planetenensatz- and switching element moments, low absolute and relative speeds and / or low construction costs. The latter allows the realization of the multi-speed transmission with only low weight and low cost. Finally, the multi-speed transmission also allows a good translation series, so a well usable gradation of the gears. Generally, a preferred embodiment of the multi-speed transmission includes four planetary gear sets, four clutches, two brakes, and no fixed housing coupling.

By operating two switching elements (brakes and / or clutches), nine forward gears and one reverse gear can be shifted, with another alternative shift position being available for the fifth gear. In addition, the transmission allows the circuit of an additional forward gear and an additional reverse gear.

As starting elements, a hydrodynamic torque converter, a hydrodynamic clutch, an additional starting clutch, an integrated starting clutch or brake and / or an additional electric motor can be used.

In principle, an electric motor or another power / power source can be arranged on each shaft. Desweitern can be arranged on each shaft in principle a freewheel to the housing or to another shaft.

Preferably, the multi-speed transmission is realized as a standard drive, but also conceivable is a front-transverse construction.

All switching elements can act frictionally or positively. Preferably, however, the first clutch and / or the third clutch are designed as positive clutches, in particular as jaw clutches, resulting in a significantly improved efficiency and thus significant consumption advantages.

It was recognized that the first and the third clutch must be actuated only once when switching from the first to the ninth gear and therefore that these switching elements are particularly suitable for being designed as a dog clutch. It has thus been further recognized that the advantage of better efficiency outweighs the disadvantage of more difficult handling in these switching elements due to their comparatively rare operation. In addition, it was recognized that the operation of the third clutch at comparatively high Ganges can take place, whereby the speed difference of the waves can be low and thus is favorable for the operation of a dog clutch.

The geometric position (order) of the individual wheelsets and switching elements is freely selectable, as long as it allows the bindability of the elements. Thus, individual elements can be moved arbitrarily in their position.

Further advantageous variants of the multi-speed transmission result from the subclaims and from the description in conjunction with the figures. These all have the same functional properties as the main system, in particular similar efficiency, similar gradation, etc.

For a better understanding of the invention, this will be explained in more detail with reference to the following figures.

Each shows in a highly schematically simplified representation:

1 shows a first schematically illustrated exemplary variant of a multi-speed transmission according to the invention;

FIG. 2 shows a second schematically illustrated exemplary variant of a multistage transmission according to the invention; FIG.

3 shows a third schematically illustrated exemplary variant of a multistage transmission according to the invention;

4 shows a fourth schematically illustrated exemplary variant of a multistage transmission according to the invention;

5 shows a fifth schematically illustrated exemplary variant of a multistage transmission according to the invention; 6 shows a sixth exemplary illustrated variant of a multi-speed transmission according to the invention;

7 shows a seventh schematically illustrated exemplary variant of a multi-speed transmission according to the invention;

Fig. 8 shows an eighth schematically illustrated exemplary variant of a multi-speed transmission according to the invention and

9 shows a ninth schematically illustrated exemplary variant of a multistage transmission according to the invention;

10 shows a tenth schematically illustrated exemplary variant of a multistage transmission according to the invention;

Fig. 1 1 is a table which indicates the closed switching elements for the transmission variants shown in Figures 1 to 3 in each gear stage.

By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and are to be transferred to the new situation mutatis mutandis when a change in position. Furthermore, individual features or combinations of features from the illustrated and described different embodiments may represent for themselves, inventive or inventive solutions.

1 shows a multi-speed transmission comprising four planetary gear sets 1, 2, 3, 4, a drive shaft 70, an output shaft 71, six further rotatable shafts 73, 74, 75, 76, 77, 78, six switching elements 51, 52, 61, 62, 63, 64, two of which are sen 51, 52 and four clutches 61, 62, 63, 64. The four planetary gear sets 1, 2, 3, 4 are arranged one after the other in the order of the first planetary gear set 1, second planetary gear set 2, third planetary gear set 3, fourth planetary gear set 4. The first planetary gear set 1, the second planetary gear set 2, the third planetary gear set 3 and the fourth planetary gear set 4 are designed as a minus planetary gearset. The planetary gear sets 1, 2, 3, 4, are jointly surrounded by a housing 72. In the variant of the multi-speed transmission of Figure 1 are

a web 12 of the first planetary gear set 1 is connected to a sun gear 41 of the fourth planetary gear set 4,

a ring gear 43 of the fourth planetary gear set 4 is connected to the output shaft 71,

a ring gear 13 of the first planetary gear set 1 and a web 22 of the second planetary gear set 2 can be coupled to the housing 72 via a first brake 51, a sun gear 1 1 of the first planetary gear set 1 can be coupled to the housing 72 via a second brake 52,

the ring gear 43 can be coupled to the sun gear 41 of the fourth planetary gear set 4 via a first clutch 61,

the ring gear 23 of the second planetary gear set 2 is permanently connected to the web 12 of the first planetary gear set 1,

the drive shaft 70 can be coupled to the sun gear 21 of the second planetary gear set 2 via a second clutch 62,

the ring gear 33 of the third planetary gear set 3 is permanently connected to the web 22 of the second planetary gear set 2,

the drive shaft 70 can be coupled to the sun gear 31 of the third planetary gear set 3 via a third clutch 63,

the web 32 of the third planetary gear set 3 with the web 42 of the fourth planetary gear set 4 is constantly connected and

the drive shaft 70 with the web 32 of the third planetary gear set 3 respectively with the web 42 of the fourth planetary gear 4 via a fourth clutch 64 coupled.

Fig. 2 shows a multi-speed transmission, which is the multi-speed transmission 1 is very similar and differs from the embodiment of FIG. 1 in the following points:

the sun gear 41 of the fourth planetary gear set 4 can not be coupled with the ring gear 43 of the fourth planetary gear set 4 but with the web 42 of the fourth planetary gear set 4 via a first clutch 61.

3 shows a multi-stage transmission, which is very similar to the multi-stage transmission of FIG. 1 and differs from the embodiment of FIG. 1 in the following points:

the ring gear 43 of the fourth planetary gear 4 is not coupled to the sun gear 41 of the fourth planetary gear 4 but with the web 42 of the fourth planetary gear set 4 via a first clutch 61.

It should be noted at this point that the variants shown in FIGS. 2 and 3 with respect to the position of the first clutch 61 are also applicable to the following transmission variants. That is, the first clutch 61 is not necessarily arranged in the following transmission variants between the ring gear 43 and the sun gear 41, but may also be arranged between the sun gear 41 and the web 42 or between the ring gear 43 and the web 41.

4 shows a multistage transmission, which is very similar to the multistage transmission of FIG. 1 and differs from the embodiment of FIG. 1 in the following points:

the ring gear 33 of the third planetary gear set 3 can be coupled to the web 22 of the second planetary gear set 2 via a fifth clutch 65 and

the drive shaft 70 is permanently connected to the sun gear 31 of the third planetary gear set 3.

FIG. 5 shows a multistage transmission, which is very similar to the multistage transmission of FIG. 4 and differs from the embodiment of FIG. 4 in the following points:

the drive shaft 70 is not on the fourth clutch 64 with the web 32 of the third planetary gear set (3) coupled, but with the ring gear 33 of the third planetary gear set 3 via a sixth clutch 66 coupled.

Fig. 6 shows a multi-stage transmission, which is very similar to the multi-stage transmission of Fig. 1 and differs in the following points from the embodiment of Fig. 1:

the drive shaft 70 is permanently connected to the sun gear 31 of the third planetary gear set 3,

the drive shaft 70 is coupled to the web 42 of the fourth planetary gear 4 via a fourth clutch 64 and

the web 32 of the third planetary gear set 3 can be coupled to the web 42 of the fourth planetary gear set 4 via a seventh clutch 67.

FIG. 7 shows a further variant of a multistage transmission comprising four planetary gear sets 1, 2, 3, 4, a drive shaft 70, an output shaft 71, six further rotatable shafts 73, 74, 75, 76, 77, 78, six shift elements 51, 52 , 61, 63, 64, 68 of which two brakes 51, 52 and four clutches 61, 63, 64, 68. The four planetary gear sets 1, 2, 3, 4 are in order first planetary gear set 1, second planetary gear set 2, third planetary gear 3rd Fourth planetary gear 4 arranged one behind the other. The first planetary gear set 1, the second planetary gear set 2, the third planetary gear set 3 and the fourth planetary gear set 4 are designed as a minus planetary gearset. The planetary gear sets 1, 2, 3, 4, are jointly surrounded by a housing 72. In the variant of the multi-speed transmission of Figure 7 are

the ring gear 43 can be coupled to the sun gear 41 of the fourth planetary gear set 4 via a first clutch 61, the ring gear 23 of the second planetary gear set 2 can be coupled to the web 12 of the first planetary gear set 1 via an eighth clutch 68,

the drive shaft 70 is continuously connected to the sun gear 21 of the second planetary gear set 2,

8 shows a multi-stage transmission, which is very similar to the multi-stage transmission of FIG. 7 and differs from the embodiment of FIG. 7 in the following points:

a ring gear 33 of the third planetary gear set 3 can be coupled to the web 22 of the second planetary gear set 2 via a fifth clutch 65,

9 shows a multistage transmission, which is very similar to the multistage transmission of FIG. 8 and differs from the embodiment of FIG. 8 in the following points:

the drive shaft 70 can be coupled to the ring gear 33 of the third planetary gearset 3 via a sixth clutch 66.

10 shows a multistage transmission, which is very similar to the multistage transmission of FIG. 7 and differs from the embodiment of FIG. 7 in the following points:

the drive shaft 70 is permanently connected to the sun gear 31 of the third planetary gear set 3, the web 32 of the third planetary gear set 3 can be coupled to the web 42 of the fourth planetary gear set 4 via a seventh clutch 67 and

In all multi-speed transmissions illustrated in FIGS. 1, 2, and 3, the following gears may be shiftable:

A first gear can be realized by the closed first brake 51, the closed first clutch 61 and the closed third clutch 63.

A second gear can be realized by the closed first brake 51, the closed second brake 52 and the closed third clutch 63.

A third gear can be realized by the closed first brake 51, the closed second clutch 62 and the closed third clutch 63.

A fourth gear can be realized by the closed second brake 52, the closed second clutch 62 and the closed third clutch 63.

A fifth gear is through the closed second clutch 62, the closed third clutch 63 and the closed fourth clutch 64 or

by the closed first brake 51, the closed first clutch 61 and the closed fourth clutch 64 feasible.

A sixth gear can be realized by the closed second brake 52, the closed third clutch 63 and the closed fourth clutch 64.

A seventh gear can be realized by the closed second brake 52, the closed second clutch 62 and the closed fourth clutch 64.

An eighth gear can be realized by the closed first brake 51, the closed second brake 52 and the closed fourth clutch 64.

A ninth gear can be realized by the closed first brake 51, the closed second clutch 62 and the closed fourth clutch 64.

A reverse gear can be realized by the closed first brake 51, the closed first clutch 61 and the closed second clutch 62.

An additional forward gear can be realized by the closed second brake 52, the closed first clutch 61 and the second clutch 62.

An additional reverse gear is provided by the closed second brake 52, which closed first clutch 61 and the closed third clutch 63 feasible. The switching elements not mentioned in each case are opened.

This is also shown in the table in Figure 1 1, which also represents the ratios of the respective gear stages.

The shift positions of the multi-speed transmission illustrated in FIG. 7 are quite similar to those of the multi-speed transmission illustrated in FIGS. 1 to 3, but with the eighth clutch 68 replacing the second clutch 62.

The shift positions of the multi-speed transmission illustrated in FIG. 4 are quite similar to those of the multi-speed transmission illustrated in FIGS. 1 to 3, but with the fifth clutch 65 replacing the third clutch 63.

The shift positions of the multi-speed transmission illustrated in FIG. 8 are quite similar to those of the multi-speed transmission illustrated in FIG. 4, but with the eighth clutch 68 replacing the second clutch 62.

The shift positions of the multi-speed transmission illustrated in FIG. 5 are quite similar to those of the multi-speed transmission illustrated in FIG. 4, but with the sixth clutch 66 replacing the fourth clutch 64.

The shift positions of the multi-speed transmission illustrated in FIG. 9 are quite similar to those of the multi-speed transmission illustrated in FIG. 5, but with the eighth clutch 68 replacing the second clutch 62.

The shift positions of the multi-speed transmission illustrated in FIG. 6 are quite similar to those of the multi-speed transmission illustrated in FIG. 4, but with the seventh clutch 67 replacing the fifth clutch 65.

The shift positions of the multi-speed transmission illustrated in FIG. 10 are quite similar to those of the multi-speed transmission illustrated in FIG. 6, but with the eighth clutch 68 replacing the second clutch 62. Preferably, all wheel sets 1, 2, 3, 4 are designed as Minusradsätze in the multi-speed transmissions shown.

In an advantageous variant, the transmission ratio is:

of the first set of wheels 1 between the sun gear 1 1 and ring gear 13 -2,017 and / or

of the second set of wheels 2 between sun gear 21 and ring gear 23 -3,218 and / or

of the third set of wheels 3 between sun gear 31 and ring gear 33 -3,900 and / or

of the fourth gear 4 between the sun gear 41 and ring gear 43 -1, 600 is.

In general, instead of a first mentioned connection / coupling to a web 12, 22, 32, 42 of a wheel set 1, 2, 3, 4 and a second mentioned connection / coupling to a ring gear 13, 23, 33, 43 of this wheelset 1, 2nd , 3, 4 the first mentioned connection / coupling to said ring gear 13, 23, 33, 43 of this wheel set 1, 2, 3, 4 and the second said connection / coupling to said web 12, 22, 32, 42 of this wheel set 1, 2, 3, 4 executed, this wheelset 1, 2, 3, 4 instead of a minus wheel as a plus wheel or instead of a plus wheel as a negative wheel is executed. In other words, the connections / couplings to the web 12, 22, 32, 42 and the ring gear 13, 23, 33, 43 of a wheelset 1, 2, 3, 4 exchanged and the direction of rotation between the sun gear 1 1, 21, 31, 41 and ring gear 13, 23, 33, 43 of this wheel 1, 2, 3, 4 vice versa. In the design of the multi-speed transmission is in addition to ensure that the amount of stationary translation of this wheel is increased or decreased by 1, if the switchable ratios between drive 70 and output 71 otherwise remain the same. By said variation of the wheelsets 1, 2, 3, 4 so the connection / coupling between the individual transmission elements can be changed without changing the characteristics of the transmission. This is a variety of structural configurations available, which can simplify the realization of the transmission in an individual case. The mentioned exchange of the Connection / coupling is not limited to a wheelset 1, 2, 3, 4, but can also be applied to several sets of wheels 1, 2, 3, 4 at the same time.

The embodiments show possible embodiments of a multi-speed transmission according to the invention, it being noted at this point that the invention is not limited to the specifically illustrated embodiments thereof, but rather also various combinations of the individual embodiments are possible with each other and this possibility of variation due to the teaching of technical action representational invention in the skill of those skilled in this technical field. In particular, the possibilities resulting from the combinatorics and the patent claim 1, but not explicitly illustrated in the figures, are also included in the scope of protection. In addition, all conceivable embodiments, which are possible by combinations of individual details of the embodiment variant shown and described, are also included in the scope of protection.

For the sake of order, it should finally be pointed out that for a better understanding of the construction of the multi-speed transmission this is shown schematically in the figures and in reality therefore more components than shown, fewer components than shown or may include other components. In general, the concrete constructive design lies within the scope of expert knowledge.

The task underlying the independent inventive solutions can be taken from the description.

First transmission gear set

second gear wheel set

third gear wheel set

fourth gear wheel set

Sun gear of the first gear wheel set Web of the first gear wheel set Ring gear of the first gear wheel set Sun gear of the second gear wheel set Web of the second gear wheel set Ring gear of the second gear wheel set Sun gear of the third gear wheel set Bridge of the third gear wheel set ring gear of third gear wheel set sun gear of the fourth gear wheel set bridge of the fourth gear wheel set ring gear of the fourth gear wheel set first brake

second brake

first clutch

second clutch

third clutch

fourth clutch

fifth clutch

sixth clutch

seventh clutch

eighth clutch

drive

output

casing

wave

Claims

claims

1 . Multi-speed transmission,

comprising at least four planetary gear sets (1, 2,3,4), a housing (72), a drive shaft (70) and an output shaft (71), wherein

a web (12) of the first planetary gear set (1) is connected to a sun gear (41) of the fourth planetary gear set (4),

a ring gear (43) of the fourth planetary gear set (4) is connected to the output shaft (71),

a ring gear (13) of the first planetary gear set (1) and a web (22) of the second planetary gear set (2) can be coupled to the housing (72) via a first brake (51),

a sun gear (1 1) of the first planetary gear set (1) can be coupled to the housing (72) via a second brake (52),

the ring gear (43) with the sun gear (41) or the ring gear (43) with the web (42) or the sun gear (41) with the web (42) respectively of the fourth planetary gear set (4) via a first clutch (61) coupled is

Connection of the drive shaft (70) with a sun gear (21) of the second planetary gear set (2),

Connection of the drive shaft (70) with a sun gear (31) of the third planetary gear set (3),

Connection of the ring gear (33) of the third planetary gear set (3) with the web (22) of the second planetary gear set (2),

Connecting the web (32) of the third planetary gear set (3) with a web (42) of the fourth planetary gear set (4),

Connection of the ring gear (23) of the second planetary gear set (2) with the web (12) of the first planetary gear set (1) and

the drive shaft (70) connected to a coupling part of a coupling (64, 66) and the other coupling part with

the web (32) of the third planetary gear set (3) and the web (42) of the fourth planetary gear set (4) or

the web (42) of the fourth planetary gear set (4) or

the ring gear (33) of the third planetary gear set (3),

constantly connected.

2. Multi-step transmission according to claim 1, characterized in that, the ring gear (23) of the second planetary gear set (2) with the web (12) of the first planetary gear set (1) is constantly connected and

the drive shaft (70) with the sun gear (21) of the second planetary gear set

(2) via a second coupling (62) can be coupled.

3. Multi-speed transmission according to claim 2, characterized in that, the ring gear (33) of the third planetary gear set (3) with the web (22) of the second planetary gear set (2) is constantly connected,

the drive shaft (70) with the sun gear (31) of the third planetary gear set

(3) can be coupled via a third coupling (63),

the web (32) of the third planetary gear set (3) is permanently connected to the web (42) of the fourth planetary gear set (4) and

the drive shaft (70) with the web (32) of the third planetary gear set (3) and with the web (42) of the fourth planetary gear set (4) via a fourth clutch (64) is coupled.

4. Multi-speed transmission according to claim 2, characterized in that, the ring gear (33) of the third planetary gear set (3) with the web (22) of the second planetary gear set (2) via a fifth clutch (65) can be coupled,

the drive shaft (70) with the sun gear (31) of the third planetary gear set

(3) is constantly connected,

the web (32) of the third planetary gear set (3) with the web (42) of the fourth

Planetary gear set (4) is constantly connected and

the drive shaft (70) with the web (32) of the third planetary gear set (3) and with the web (42) of the fourth planetary gear set (4) via a fourth

Coupling (64) can be coupled.

5. Multi-speed transmission according to claim 2, characterized in that, the ring gear (33) of the third planetary gear set (3) with the web (22) of the second planetary gear set (2) via a fifth clutch (65) can be coupled,

the drive shaft (70) with the sun gear (31) of the third planetary gear set

(3) is constantly connected,

Planetary gear set (4) is constantly connected and

the drive shaft (70) with the ring gear (33) of the third planetary gear set (3) via a sixth clutch (66) can be coupled.

6. Multi-speed transmission according to claim 2, characterized in that, the ring gear (33) of the third planetary gear set (3) with the web (22) of the second planetary gear set (2) is constantly connected,

the drive shaft (70) is permanently connected to the sun gear (31) of the third planetary gear set (3),

the drive shaft (70) with the web (42) of the fourth planetary gear set (4) via a fourth clutch (64) is coupled and

the web (32) of the third planetary gear set (3) can be coupled to the web (42) of the fourth planetary gear set (4) via a seventh coupling (67).

7. Multi-speed transmission according to claim 1, characterized in that, the ring gear (23) of the second planetary gear set (2) with the web (12) of the first planetary gear set (1) via an eighth clutch (68) can be coupled and

the drive shaft (70) with the sun gear (21) of the second planetary gear set

(2) is constantly connected.

8. Multi-speed transmission according to claim 7, characterized in that, the ring gear (33) of the third planetary gear set (3) with the web (22) of the second planetary gear set (2) is constantly connected,

the drive shaft (70) with the sun gear (31) of the third planetary gear set

(3) can be coupled via a third coupling (63),

the web (32) of the third planetary gear set (3) is permanently connected to the web (42) of the fourth planetary gear set (4) and the drive shaft (70) with the web (32) of the third planetary gear set (3) and with the web (42) of the fourth planetary gear set (4) via a fourth clutch (64) is coupled.

9. Multi-speed transmission according to claim 7, characterized in that, a ring gear (33) of the third planetary gear set (3) with the web (22) of the second planetary gear set (2) via a fifth clutch (65) can be coupled,

a web (32) of the third planetary gear set (3) is permanently connected to a web (42) of the fourth planetary gear set (4) and

10. Multi-speed transmission according to claim 7, characterized in that, the ring gear (33) of the third planetary gear set (3) with the web (22) of the second planetary gear set (2) via a fifth clutch (65) is coupled,

the drive shaft (70) with the sun gear (31) of the third planetary gear set

(3) is constantly connected,

Planetary gear set (4) is constantly connected and

1 1. Multi-speed transmission according to Claim 7, characterized in that the ring gear (33) of the third planetary gear set (3) is permanently connected to the web (22) of the second planetary gear set (2),

the web (32) of the third planetary gear set (3) can be coupled to the web (42) of the fourth planetary gear set (4) via a seventh coupling (67) and the drive shaft (70) with the web (42) of the fourth planetary gear set (4) via a fourth clutch (64) is coupled.

12. Multi-speed transmission according to claim 3 or 8, characterized in that the following gears are switchable by closing the indicated elements :, a first gear by first brake (51), first clutch (61) and third clutch (63),

a second gear through first brake (51), second brake (52) and third clutch (63),

a third gear through first brake (51), second clutch (62) / eighth clutch (68) and third clutch (63),

a fourth gear through second brake (52), second clutch (62) / eighth clutch (68) and third clutch (63),

a fifth course:

by the second clutch (62) / eighth clutch (68), third clutch (63) and fourth clutch (64) or

by first brake (51), first clutch (61) and fourth clutch (64), a sixth gear by second brake (52), third clutch (63) and fourth

Coupling (64),

a seventh gear by second brake (52), second clutch (62) / eighth clutch (68) and fourth clutch (64),

an eighth gear through first brake (51), second brake (52) and fourth clutch (64),

a ninth gear through first brake (51), second clutch (62) / eighth clutch (68) and fourth clutch (64),

a reverse gear through first brake (51), first clutch (61) and second clutch (62) / eighth clutch (68),

an additional forward gear through second brake (52), first clutch (61) and second clutch (62) / eighth clutch (68) and

an additional reverse gear through second brake (52), first clutch (61) and third clutch (63),

wherein the respective elements not mentioned are unactuated or opened.

13. Multi-speed transmission according to claim 4 or 9, characterized in that the following gears are switchable by closing the specified elements :, a first gear by first brake (51), first clutch (61) and fifth clutch (65),

a second gear through first brake (51), second brake (52) and fifth clutch (65),

a third gear through first brake (51), second clutch (62) / eighth clutch (68) and fifth clutch (65),

a fourth gear through second brake (52), second clutch (62) / eighth clutch (68) and fifth clutch (65),

a fifth course:

by the second clutch (62) / eighth clutch (68), fifth clutch (65) and fourth clutch (64) or

by first brake (51), first clutch (61) and fourth clutch (64), a sixth gear by second brake (52), fifth clutch (65) and fourth

Coupling (64),

an additional reverse gear through second brake (52), first clutch (61) and fifth clutch (65),

wherein the respective elements not mentioned are unactuated or opened.

14. Multi-speed transmission according to claim 5 or 10, characterized in that the following gears are switchable by closing the specified elements :, a first gear by first brake (51), first clutch (61) and fifth clutch (65),

a fifth course:

by the second clutch (62) / eighth clutch (68), fifth clutch (65) and sixth clutch (66) or

by first brake (51), first clutch (61) and sixth clutch (66), a sixth gear by second brake (52), fifth clutch (65) and sixth clutch (66),

a seventh gear by second brake (52), second clutch (62) / eighth clutch (68) and sixth clutch (66),

an eighth gear through first brake (51), second brake (52) and sixth clutch (66),

a ninth gear through first brake (51), second clutch (62) / eighth clutch (68) and sixth clutch (66),

wherein the respective elements not mentioned are unactuated or opened.

15. Multi-speed transmission according to claim 6 or 1 1, characterized in that the following gears are switchable by closing the specified elements :, a first gear through first brake (51), first clutch (61) and seventh clutch (67),

a second gear through first brake (51), second brake (52) and seventh clutch (67),

a third gear through first brake (51), second clutch (62) / eighth clutch (68) and seventh clutch (67),

a fourth gear through second brake (52), second clutch (62) / eighth clutch (68) and seventh clutch (67),

a fifth course:

by the second clutch (62) / eighth clutch (68), seventh clutch (67) and fourth clutch (64) or

by first brake (51), first clutch (61) and fourth clutch (64), a sixth gear by second brake (52), seventh clutch (67) and fourth clutch (64),

an additional reverse gear through second brake (52), first clutch (61) and seventh clutch (67),

wherein the respective elements not mentioned are unactuated or opened.

1 6. Multi-speed transmission according to one of claims 1 to 15, characterized in that all wheelsets (1, 2, 3, 4) are designed as Minusradsätze.

17. Multi-speed transmission according to claim 1 6, characterized in that the transmission ratio :,

of the first gear set (1) between sun gear (1 1) and ring gear (13) -2,017 and / or

of the second set of wheels (2) between sun gear (21) and ring gear (23) -3,218 and / or

of the third wheel set (3) between sun gear (31) and ring gear (33) -3,900 and / or

of the fourth gear set (4) between sun gear (41) and ring gear (43) -1, 600 is.

18. Multi-step transmission according to one of claims 1 6 or 17, characterized in that instead of a first mentioned connection / coupling to a web (12, 22, 32, 42) of a wheelset (1, 2, 3, 4) and a second mentioned Connection / coupling to a ring gear (13, 23, 33, 43) of this wheel set (1, 2, 3, 4), the first-mentioned connection / coupling to said ring gear (13, 23, 33, 43) of this wheel set (1 , 2, 3, 4) and the second said connection / coupling to the said web (12, 22, 32, 42) of this wheel set (1, 2, 3, 4) is executed, said wheel set (1, 2, 3 , 4) instead of a minus wheel as a plus wheel or instead of a plus wheel as a negative wheel is executed.

19. Multi-speed transmission according to one of claims 1 to 18, characterized in that the first clutch (61) and the third, fifth or seventh clutch (63, 65, 67) are designed as jaw clutches.