DE102009047277A1 - Multi-speed transmission in planetary design, particularly automatic transmission for motor vehicle, has drive shaft, output shaft, four planetary gear sets arranged in housing, nine rotatable shafts and six switching elements - Google Patents

Abstract

The multi-speed transmission has a drive shaft (1), an output shaft (2), four planetary gear sets (P1,P2,P3,P4) arranged in a housing (G), nine rotatable shafts (3-9) and six switching elements. A sun wheel of the former planetary gear set is operatively connected with the fifth shaft, which is connected with a hollow wheel of the third planetary gear set.

Description

The present invention relates to a planetary gear multi-speed transmission, in particular an automatic transmission for a motor vehicle, according to the preamble of patent claim 1.

Automatic transmissions, particularly for motor vehicles, include, in the prior art, planetary gear sets that are switched by means of friction elements, such as clutches and brakes, and usually with a slip element and optionally a lockup clutch, such as a hydrodynamic torque converter or a fluid coupling connected.

Such a transmission goes out of the EP 0 434 525 A1 out. It essentially comprises a drive shaft and an output shaft, which are arranged parallel to one another, a double planetary gearset arranged concentrically with the output shaft and five shifting elements in the form of three clutches and two brakes, whose optional blocking determines in pairs the different gear ratios between the drive shaft and the output shaft , Here, the transmission has a Vorschaltradsatz and two power paths, so that six forward gears are achieved by the selective pairwise intervention of the five shift elements.

In this case, two clutches are required for transmitting the torque from the transfer gearset to two elements of the double planetary gearset in the first power path. These are arranged in the direction of power flow essentially behind the transfer gearset in the direction of the double planetary gear set. In the second power path, a further clutch is provided which removably connects this with another element of the double planetary gear set. Here, the clutches are arranged such that the inner disc carrier forms the output.

Automatically switchable vehicle transmissions in planetary construction in general are already widely described in the prior art and are subject to permanent development and improvement. So these transmissions require a low construction cost, in particular a small number of switching elements and avoid sequential switching double circuits, so that in circuits in defined gear groups only one switching element is changed.

From the DE 10 2008 000 428 A1 The applicant is a planetary gear multi-speed transmission known which has a drive and an output, which are arranged in a housing. In the known transmission at least four planetary gear sets, hereinafter referred to as the first, second, third and fourth planetary gear set, at least eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft - and at least six switching elements, comprising brakes and clutches, provided, the selective engagement causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.

In this case, the first and the second planetary gear set, which are preferably designed as minus planetary gear sets, form a switchable transfer gearset, the third and the fourth planetary gear set forming a main gearset.

In the known multi-speed transmission is provided that the webs of the first and second planetary gear sets are coupled to each other via the fourth shaft, which is connected to an element of the main gearset that the ring gear of the first planetary gear set coupled to the sun gear of the second planetary gear via the eighth shaft is, which is detachably connectable via a first clutch to the drive shaft and that the sun gear of the first planetary gear by means of the third shaft via a first brake to a housing of the transmission can be coupled and releasably connected via a second clutch to the drive shaft, wherein the ring gear of second planetary gear set by means of the fifth shaft via a second brake to a housing of the transmission can be coupled. In addition, the seventh shaft is permanently connected to at least one element of the main gearset and can be coupled to a housing of the transmission via a third brake, wherein the sixth shaft is permanently connected to at least one further element of the main gearset and can be detachably connected to the drive shaft via a third clutch ; the output shaft is permanently connected to at least one further element of the main gearset.

Preferably, in the known transmission, the fourth shaft is constantly connected to the ring gear of the third planetary gear set, wherein the sixth shaft is continuously connected to the ring gear of the fourth planetary gear set and the web of the third planetary gear and releasably connectable via the third clutch to the drive shaft. Furthermore, the seventh shaft is constantly connected to the sun gears of the third and fourth planetary gear set and can be coupled via the third brake to a housing of the transmission. The output takes place here via the output shaft permanently connected to the web of the fourth planetary gear set. Furthermore, the third and the fourth planetary gear set to a Ravigneaux set with a common bridge and a common ring gear composed or reduced.

The present invention has for its object to propose a multi-speed transmission of the type mentioned, which has nine forward gears and at least one reverse gear with sufficient translation, in which the construction cost and size, in particular the length or the weight are optimized and also the efficiency in terms the drag and gearing losses is improved. In addition, in the multistage transmission according to the invention, small supporting moments act on the shifting elements. In particular, the transmission according to the invention should be suitable for a drive in standard longitudinal design.

This object is achieved by the features of claim 1. Further advantages and advantageous embodiments will become apparent from the dependent claims.

Accordingly, a multi-speed transmission according to the invention is proposed planetary design, which has a drive and an output, which are arranged in a housing. Furthermore, at least four planetary gear sets, hereinafter referred to as first, second, third and fourth planetary gear set, nine rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh, eighth and ninth wave - and at least six Switching elements, comprising brakes and clutches, provided, the selective intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.

The planetary gear sets are axially arranged in the order of the first planetary gear set, second planetary, third planetary, fourth planetary gear, wherein the first, second and third planetary gear set are preferably designed as minus planetary gear sets and the fourth planetary gear set is designed as a plus planetary gear set.

A simple minus planetary gear known to include a sun gear, a ring gear and a web on which planet gears are rotatably mounted, each meshing with the sun gear and ring gear. In this way, the ring gear at a fixed web on a sun gear opposite direction of rotation. In contrast, a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, wherein all inner planetary gears mesh with the sun gear and all outer planetary gears with the ring gear, each inner planetary gear each having an outer Planet wheel meshes. As a result, the ring gear has the same direction of rotation when holding the web as the sun gear.

According to a preferred embodiment of the invention, the sun gear of the first planetary gear set is operatively connected to the fifth shaft connected to the ring gear of the third planetary gear set, which is detachably connectable via a first clutch with the eighth wave, which is connected to the web of the second planetary gear set and via a second Clutch is detachably connectable to the ninth shaft, wherein the ninth shaft is connected to the sun gear of the third planetary gear set and the sun gear of the fourth planetary gear set.

Further, the web of the first planetary gear set is connected to the drive shaft, which is detachably connectable via a third clutch to the sixth shaft connected to the second planetary gear set sixth, wherein the ring gear of the first planetary gear set is operatively connected to the driven shaft connected to the ring gear of the fourth planetary gear set , Furthermore, the third shaft is connected to the sun gear of the second planetary gear set and the bridge of the third planetary gear set and coupled via a first brake to a housing of the transmission, wherein the fourth shaft connected to the web of the fourth planetary gear set and via a second brake to a housing the transmission can be coupled.

Here, the fifth shaft may be directly connected to the sun gear of the first planetary gear, in which case the output shaft with the ring gear of the first planetary gear via a connected to the ring gear of the first planetary gear seventh shaft and the seventh shaft to the output shaft releasably connecting fourth clutch is detachably connectable.

In the context of a further embodiment of the invention, the fifth shaft with the sun gear of the first planetary gear set via a further connected to the sun gear of the first planetary gear and a further wave with the fifth shaft releasably connecting further coupling be releasably connected, wherein the output shaft with the ring gear of the first planetary gear set is directly connected.

The inventive design of the multi-speed transmission results in particular for passenger cars suitable translations and increased total spread of the multi-speed transmission, whereby an improvement in ride comfort and a significant consumption reduction can be effected.

In addition, the construction cost is considerably reduced with the multi-stage transmission according to the invention by a small number of switching elements. Advantageously, it is possible with the multistage transmission according to the invention to carry out a start with a hydrodynamic converter, an external starting clutch or other suitable external starting elements. It is also conceivable to enable a starting operation with a start-up element integrated in the transmission. Preferably, a switching element which is actuated in the first forward gear and in reverse is suitable.

Furthermore, in the multistage transmission according to the invention, a good efficiency in the main drives with respect to the drag and gear losses.

Furthermore, there are small moments in the switching elements and in the planetary gear sets of the multi-speed transmission, whereby the wear is reduced in the multi-step transmission in an advantageous manner. In addition, a correspondingly small dimensions are made possible by the low moments, whereby the required space and the corresponding costs are reduced. In addition, there are also low speeds at the shafts, the switching elements and the planetary gear sets.

In addition, the transmission according to the invention is designed such that an adaptability to different drive train configurations is made possible both in the power flow direction as well as in space.

The invention will be explained in more detail below by way of example with reference to the attached figures. These are:

1 a schematic view of a first preferred embodiment of a multi-speed transmission according to the invention;

2 : an exemplary circuit diagram for a multi-step transmission according to 1 ;

3 a schematic view of a second preferred embodiment of a multi-speed transmission according to the invention;

4 : an exemplary circuit diagram for a multi-step transmission according to 2 ; 5 a schematic view of a third preferred embodiment of a multi-speed transmission according to the invention;

6 : an exemplary circuit diagram for a multi-step transmission according to 5 ;

7 a schematic view of a fourth preferred embodiment of a multi-speed transmission according to the invention;

8th : an exemplary circuit diagram for a multi-step transmission according to 7 ;

9 a schematic view of a fifth preferred embodiment of a multi-speed transmission according to the invention;

10 : an exemplary circuit diagram for a multi-step transmission according to 9 ;

11 a schematic view of a sixth preferred embodiment of a multi-speed transmission according to the invention; and

12 : an exemplary circuit diagram for a multi-step transmission according to 11 ,

In 1 is an inventive multi-stage transmission with a drive shaft 1 , an output shaft 2 and four planetary gear sets P1, P2, P3 and P4, which are arranged in a housing G. The planetary gear sets P1, P2 and P3 are in the in 1 shown example designed as negative planetary gear sets, wherein the fourth planetary gear P4 is designed as a plus-planetary gear set.

According to the invention, at least one planetary gear set can be designed as a positive planetary gear set, if at the same time the web and Hohlradanbindung exchanged and the amount of stationary translation of the planetary gear is increased by 1 compared to the design as a minus planetary gear. Furthermore, the fourth planetary gear set P4 designed as a plus planetary gearset can be designed as a minus planetary gear set if the web and ring gear connection are exchanged at the same time and the amount of stationary gear ratio of the planetary gearset is reduced by 1 compared to the negative planetary gearset design.

In the embodiment shown, the planetary gear sets are arranged axially in the order P1, P2, P3, P4.

How out 1 can be seen, six switching elements, namely two brakes 03 . 04 and four clutches 16 . 27 . 58 and 89 intended. The spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape. The clutches and the brake of the transmission are preferably designed as Reibschaltelemente or lamellar switching elements.

With these switching elements is a selective switching of nine forward gears and one Reverse gear feasible. The multistage transmission according to the invention has a total of nine rotatable shafts, namely the waves 1 . 2 . 3 . 4 . 5 . 6 . 7 . 8th and 9 wherein the drive shaft is the first shaft 1 and the output shaft 2 forms the second shaft of the transmission.

According to a preferred embodiment of the invention, the subject of the 1 is, is the sun gear of the first planetary gear P1 with the fifth shaft connected to the ring gear of the third planetary gear P3 5 connected, which via a first clutch 58 with the eighth wave 8th is releasably connectable, which is connected to the web of the second planetary gear set P2 and a second clutch 89 with the ninth wave 9 is releasably connectable, which is connected to the sun gear of the third planetary gear set P3 and the sun gear of the fourth planetary gear set P4.

How out 1 can be seen the web of the first planetary gear set P1 with the drive shaft 1 connected via a third clutch 16 with the sixth shaft connected to the ring gear of the second planetary gear set P2 6 is detachably connectable, wherein the ring gear of the first planetary gear P1 with the output shaft connected to the ring gear of the fourth planetary gear set P4 2 via a seventh shaft connected to the ring gear of the first planetary gear set P1 7 and the seventh wave 7 with the output shaft 2 releasably connecting fourth clutch 27 is detachably connectable. Further, the third wave 3 connected to the sun gear of the second planetary gear set P3 and the bridge of the third planetary gear set P3 and a first brake 03 can be coupled to a housing G of the transmission, wherein the fourth shaft 4 connected to the web of the fourth planetary gear set P4 and a second brake 04 can be coupled to a housing G of the transmission.

In the context of another embodiment of the invention, the subject of the 3 is the fifth wave 5 not directly connected to the sun gear of the first planetary gear set P1 but via a further shaft connected to the sun gear of the first planetary gear P1 7 ' and one the further wave 7 ' with the fifth wave 5 detachably connecting further coupling 57 be designed detachably connectable, wherein the output shaft is directly connected to the ring gear of the first planetary gear set.

In 2 is an exemplary circuit diagram of a multi-speed transmission according to 1 shown. For each gear four switching elements are closed. The shift scheme, the respective ratios of the individual gear ratios i and the step to be determined therefrom or increments phi are taken to the next higher gear example, the value of 8.994 represents the spread of the transmission.

Typical values for the stationary ratios of the planetary gear sets P1, P2, P3 and P4 are -2.051, -1.6, -1.6 and +3.306, respectively. Out 2 As can be seen, in the case of sequential switching, double circuits or group circuits are avoided since two adjacent gear stages share three switching elements. Further, it will be seen that a large spread is achieved with small gear jumps.

The first forward speed is achieved by closing the first and second brakes 03 . 04 and the second and third clutches 89 . 16 , the second forward speed by closing the second brake 04 and the first, second and third clutches 58 . 89 . 16 , the third forward by closing the second brake 04 and the second, third and fourth clutches 89 . 16 . 27 , the fourth forward by closing the second brake 04 and the first, second and fourth clutches 58 . 89 . 27 , the fifth forward by closing the second brake 04 and the first, third and fourth clutches 58 . 16 . 27 preferably the sixth forward gear, designed as a direct gear, by closing the first, second, third and fourth clutch 58 . 89 . 16 . 27 , the seventh forward by closing the first brake 03 and the first, third and fourth clutches 58 . 16 . 27 , the eighth forward by closing the first brake 03 and the first, second and fourth clutches 58 . 89 . 27 and the ninth forward speed is achieved by closing the first brake 03 and the second, third and fourth clutches 89 . 16 . 27 wherein the reverse gear by closing the first and second brake 03 . 04 and the first and third clutches 58 . 16 results.

Characterized in that the first and second brake in first forward gear and in reverse 03 . 04 and the third clutch 16 are closed, these switching elements can be used as starting elements.

This according to the embodiment 3 appropriate circuit diagram is the subject of 4 , It corresponds to the circuit diagram according to 2 with the difference that the fourth clutch 27 through the further coupling 57 is replaced.

At the in 5 illustrated embodiment, the sun gear of the first planetary gear P1 with the fourth shaft connected to the ring gear of the third planetary gear P3 4 connected, which via a fifth clutch 49 with the ninth wave 9 is releasably connectable, which is connected to the web of the second planetary gear set P2 and a second clutch 89 with the eighth wave 8th is releasably connectable, which is connected to the sun gear of the third planetary gear set P3 and the sun gear of the fourth planetary gear set P4.

How out 5 can be seen, is the web of the first planetary gear P1 with the drive shaft 1 connected via a sixth clutch 15 with the fifth shaft connected to the ring gear of the second planetary gear set P2 5 is detachably connectable, wherein the ring gear of the first planetary gear set P1 with the connected to the ring gear of the fourth planetary gear set P4 via a connected to the ring gear of the fourth planetary gear set P4 seventh shaft 7 and the seventh wave 7 with the output shaft 2 releasably connecting eighth clutch 27 ' releasably connectable output shaft 2 via a sixth shaft connected to the ring gear of the first planetary gear set P1 6 and one the sixth wave 6 with the output shaft 2 releasably connecting seventh coupling 26 is detachably connectable. Further, the third wave 3 connected to the sun gear of the second planetary gear set P3 and the bridge of the third planetary gear set P3 and a first brake 03 can be coupled to a housing G of the transmission, wherein the web of the fourth planetary gear set P4 is coupled to a housing G of the transmission (shaft 0 ).

This in 6 shown circuit diagram of in 5 shown transmission corresponds to the circuit diagram 2 with the difference that the second brake 04 through the eighth clutch 27 ' , the third clutch 16 through the sixth clutch 15 , the fourth clutch 27 through the seventh clutch 26 , and that the first clutch 58 through the fifth clutch 49 is replaced.

This in 7 The embodiment shown differs from the exemplary embodiment 5 in that the output shaft 2 is directly connected to the ring gear of the fourth planetary gear set P4 and that the eighth wave 8th not directly connected to the sun gear of the fourth planetary gear set P4 but via a further shaft connected to the sun gear of the fourth planetary gear set P4 7 ' and one the further wave 7 ' with the eighth wave 8th releasably connecting ninth clutch 78 is detachably connectable.

This according to the embodiment 7 corresponding circuit diagram is in 8th shown. It corresponds to the circuit diagram according to 6 with the difference that the eighth clutch 27 ' through the ninth clutch 78 is replaced.

Another embodiment of a transmission according to the invention is in 9 shown. Here, the sun gear of the first planetary gear P1 is the ninth wave 9 connected, which has a tenth clutch 59 with the fifth wave 5 is releasably connectable, which is connected to the ring gear of the third planetary gear set P3 and a first clutch 58 with the eighth wave 8th detachably connectable, which is connected to the web of the second planetary gear P2 and an eleventh clutch 78 ' with the seventh shaft connected to the sun gear of the third planetary gear set P3 and the sun gear of the fourth planetary gear set P4 7 is detachably connectable.

Further, the web of the first planetary gear set P1 with the drive shaft 1 connected via a twelfth clutch 14 with the fourth shaft connected to the ring gear of the second planetary gear set P2 4 is releasably connectable, wherein the ring gear of the first planetary gear set P1 with the connected to the ring gear of the fourth planetary gear set P4 via a connected to the ring gear of the fourth planetary gear set P4 sixth shaft 6 and one the sixth wave 6 with the output shaft 2 releasably connecting thirteenth coupling 26 ' releasably connectable output shaft 2 connected is. Further, the third wave 3 connected to the sun gear of the second planetary gear set P3 and the bridge of the third planetary gear set P3 and a first brake 03 can be coupled to a housing G of the transmission, wherein the web of the fourth planetary gear set P4 is coupled to a housing G of the transmission (shaft 0 ).

This in 10 shown circuit diagram of in 9 shown transmission corresponds to the circuit diagram 2 with the difference that the second brake 04 through the thirteenth clutch 26 ' , the third clutch 16 through the twelfth clutch 14 , the second clutch 89 through the eleventh clutch 78 ' and that the fourth clutch 27 through the tenth clutch 59 is replaced.

This in 11 illustrated embodiment differs from the exemplary embodiment 9 in that the output shaft 2 is directly connected to the ring gear of the fourth planetary gear set P4 and that the seventh shaft 7 not directly connected to the sun gear of the fourth planetary gear set P4 but via a further shaft connected to the sun gear of the fourth planetary gear set P4 6 ' and one the further wave 6 ' with the seventh wave 7 detachably connecting fourteenth coupling 67 is detachably connectable.

This according to the embodiment 11 corresponding circuit diagram is in 12 shown. It differs from the circuit diagram according to 10 in that the thirteenth clutch 26 ' through the fourteenth clutch 67 is replaced.

According to the invention, different gear jumps may result even with the same transmission scheme depending on the switching logic, so that an application- or vehicle-specific variation is made possible.

According to the invention, it is possible to provide additional freewheels at any suitable point of the multi-speed transmission, for example between one Shaft and housing or to connect two shafts if necessary.

On the drive side or on the output side, an axle differential and / or a distributor differential can be arranged according to the invention.

In the context of an advantageous development, the drive shaft 1 be separated by a coupling element of a drive motor as needed, with a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch can be used as a coupling element. It is also possible to arrange such a starting element in the power flow direction behind the transmission, in which case the drive shaft 1 constantly connected to the crankshaft of the engine.

The multistage transmission according to the invention also allows the arrangement of a torsional vibration damper between the engine and transmission.

In the context of a further, not shown embodiment of the invention can on each shaft, preferably on the drive shaft 1 or the output shaft 2 , a wear-free brake, such. As a hydraulic or electrical retarder or the like, be arranged, which is particularly important for use in commercial vehicles of particular importance. Furthermore, for driving additional units on each shaft, preferably on the drive shaft 1 or the output shaft 2 be provided a power take-off.

The friction shift elements used can be designed as a load-shifting clutches or brakes. In particular, non-positive clutches or brakes such. B. multi-plate clutches, band brakes and / or cone clutches are used.

Another advantage of the multistage transmission presented here is that an electric machine can be attached to each shaft as a generator and / or as an additional drive machine.

LIST OF REFERENCE NUMBERS

0

wave

1

first shaft, drive shaft

2

second shaft, output shaft

3

third wave

4

fourth wave

5

fifth wave

6

sixth wave

6 '

another wave

7

seventh wave

7 '

another wave

8th

eighth wave

9

ninth wave

03

brake

04

brake

14

twelfth clutch

15

sixth clutch

16

third clutch

26

seventh clutch

26 '

thirteenth clutch

27

fourth clutch

27 '

eighth clutch

49

fifth clutch

57

further coupling

58

first clutch

59

tenth clutch

67

fourteenth clutch

78

ninth clutch

78 '

eleventh clutch

89

second clutch

P1

first planetary gear set

P2

second planetary gear set

P3

third planetary gear set

P4

fourth planetary gear set

i

translation

phi

increment

G

casing

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 0434525 A1 [0003]
• DE 102008000428 A1 [0006]

Claims (4)

Multi-stage transmission in planetary construction, in particular automatic transmission for a motor vehicle, comprising a drive shaft ( 1 ), an output shaft ( 2 ) and four planetary gear sets (P1, P2, P3, P4), which are arranged in a housing (G), a total of nine rotatable shafts ( 1 . 2 . 3 . 4 . 5 . 6 . 7 . 7 ' . 8th . 9 ) and at least six switching elements ( 03 . 04 . 16 . 27 . 57 . 58 . 89 ), comprising two brakes ( 03 . 04 ) and couplings ( 16 . 27 . 57 . 58 . 89 ), whose selective engagement different transmission ratios between the drive shaft ( 1 ) and the output shaft ( 2 ), so that nine forward gears and one reverse gear can be realized, wherein the sun gear of the first planetary gear set (P1) with the fifth shaft connected to the ring gear of the third planetary gear set (P3) ( 5 ) operatively connected via a first clutch ( 58 ) with the eighth wave ( 8th ) is releasably connectable, which is connected to the web of the second planetary gear set (P2) and via a second clutch ( 89 ) with the ninth wave ( 9 ) releasably connectable, the ninth wave ( 9 ) is connected to the sun gear of the third planetary gear set (P3) and the sun gear of the fourth planetary gear set (P4), wherein the web of the first planetary gear set (P1) with the drive shaft (P) ( 1 ) connected via a third clutch ( 16 ) connected to the ring gear of the second planetary gear set (P2) sixth shaft ( 6 ) is releasably connectable, wherein the ring gear of the first planetary gear set (P1) with the output shaft connected to the ring gear of the fourth planetary gear set (P4) ( 2 ), the third wave ( 3 ) connected to the sun gear of the second planetary gear set (P4) and the bridge of the third planetary gear set (P3) and via a first brake ( 03 ) can be coupled to a housing (G) of the transmission and wherein the fourth shaft ( 4 ) connected to the web of the fourth planetary gear set (P4) and via a second brake ( 04 ) can be coupled to a housing (G) of the transmission. Multi-step transmission according to claim 1, characterized in that the fifth shaft ( 5 ) is directly connected to the sun gear of the first planetary gear set (P1), in which case the output shaft ( 2 ) with the ring gear of the first planetary gear set (P1) via a connected to the ring gear of the first planetary gear set (P1) seventh shaft ( 7 ) and a seventh wave ( 7 ) with the output shaft ( 2 ) detachably connecting fourth coupling ( 27 ) is releasably connectable. Multi-step transmission according to claim 1, characterized in that the fifth shaft ( 5 ) with the sun gear of the first planetary gear set (P1) via a further shaft connected to the sun gear of the first planetary gear set (P1) ( 7 ' ) and one the further wave ( 7 ' ) with the fifth wave ( 5 ) detachably connecting further coupling ( 57 ) is detachably connectable, wherein the output shaft ( 2 ) is directly connected to the ring gear of the first planetary gear set (P1). Multi-step transmission according to claim 2 or 3, characterized in that in the event that the fifth shaft ( 5 ) is directly connected to the sun gear of the first planetary gear set (P1), the first forward gear by closing the first and second brake ( 03 . 04 ) and the second and third clutches ( 89 . 16 ), the second forward gear by closing the second brake ( 04 ) and the first, second and third clutches ( 58 . 89 . 16 ), the third forward speed by closing the second brake ( 04 ) and the second, third and fourth clutch ( 89 . 16 . 27 ), the fourth forward gear by closing the second brake ( 04 ) and the first, second and fourth coupling ( 58 . 89 . 27 ), the fifth forward gear by closing the second brake ( 04 ) and the first, third and fourth clutch ( 58 . 16 . 27 ), the sixth forward gear by closing the first, second, third and fourth clutch ( 58 . 89 . 16 . 27 ), the seventh forward speed by closing the first brake ( 03 ) and the first, third and fourth clutch ( 58 . 16 . 27 ), the eighth forward by closing the first brake ( 03 ) and the first, second and fourth coupling ( 58 . 89 . 27 ) and that the ninth forward by closing the first brake ( 03 ) and the second, third and fourth clutch ( 89 . 16 . 27 ), wherein the reverse gear by closing the first and second brake ( 03 . 04 ) and the first and third clutch ( 58 . 16 ), where, in the event that the fifth wave ( 5 ) with the sun gear of the first planetary gear set (P1) via a further shaft connected to the sun gear of the first planetary gear set (P1) ( 7 ' ) and one the further wave ( 7 ' ) with the fifth wave ( 5 ) detachably connecting further coupling ( 57 ) is detachably connectable, the fourth clutch ( 27 ) through the further coupling ( 57 ) is replaced.

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