DE102014207463A1 - Multi-stage automatic transmission - Google Patents

Abstract

The automatic transmission according to the invention has nine rotatable shafts (1 to 9), four planetary gear sets (RS1 to RS4) and at least six switching elements (A to F) for switching of several forward gears and one reverse gear. A second element (ST4) of the fourth planetary gear set (RS4) forms the first shaft (1) designed as drive shaft (AN), a second element (ST3) of the third planetary gearset (RS3) forms the second shaft (2) designed as output shaft (AB). a third element (HO1) of the first planetary gear set (RS1), the fourth shaft (4), a third element (HO2) of the second planetary gear set (RS2), the fifth shaft (5), a second element (ST2) of the second planetary gear set (RS2 ) the eighth wave (8), a first element (SO3) of the third planetary gear set (RS3) the ninth wave (9). A first element (SO1) of the first planetary gearset RS1 and a first element (SO4) of the fourth planetary gearset (RS4) are interconnected as a third shaft (3). A second element (ST1) of the first planetary gear set (RS1) and a third element (HO3) of the third planetary gear set (RS3) are connected together as the sixth shaft (6). A first element (SO2) of the second planetary gear set (RS2) and a third element (HO4) of the fourth planetary gear set (RS4) are connected together as a seventh shaft (7). The third shaft (3) can be fixed via the first switching element (A). The fourth shaft (4) can be fixed via the second switching element (B). The second shaft (2) can be connected via the fourth switching element (D) with the eighth shaft (8). The second planetary gear set (RS2) can be linked via the fifth switching element (E). The ninth wave (9) can be connected via the third switching element (C) to the first shaft (1) and via the sixth switching element (F) to the fifth shaft (5).

Description

The present invention relates to a multi-stage automatic transmission in planetary construction according to the preamble of patent claim 1.

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 should have a sufficient number of forward gears and a reverse gear and a very suitable for motor vehicles translation with a high overall spread, favorable increments and a sufficiently large for the application starting ratio. In addition, these transmissions are the lowest possible construction costs, in particular require a small number of switching elements and avoid sequential switching so-called group circuits, so that in circuits in the next higher or next lower gear only one previously closed switching element opened and closed a previously opened switching element becomes.

Such a multi-speed automatic transmission, for example, from the generic DE 10 2005 002 337 A1 the applicant. It essentially comprises a drive shaft, an output shaft, a total of four individual planetary gear sets and five shift elements. By selectively blocking each of three of the five running as clutches and brakes switching elements a total of eight forward gears are switchable group circuit.

From the DE 10 2010 041 575 B3 the applicant is an alternative transmission scheme to that of DE 10 2005 002 337 A1 known 8-speed automatic transmission known. Herein, a transmission with four individual planetary gear sets, five switching elements and a total of nine waves is proposed, in which, in contrast to DE 10 2005 002 337 A1 the ring gear of the first planetary gear set arranged close to drive is firmly connected to the transmission housing and the sun gear of this first planetary gear set via the second switching element with the third shaft is connectable, which in turn via the first switching element on the gear housing can be fixed.

From the DE 10 2009 001 253 B3 the applicant is a further development of the DE 10 2005 002 337 A1 known 8-speed automatic transmission known. Here could be represented by adding a trained as a clutch sixth switching element in the power flow between the drive shaft and the second planetary gear set blockable by closing the fifth of the previously existing five switching elements, an additional forward gear, which is greater by its translation ago than the previous first gear of the 8-speed Gear, so an additional starting gear below the previous first gear of the 8-speed transmission.

The present invention has for its object to provide a multi-step transmission of the type mentioned above with a total of four planetary gear sets, which has at least nine group circuit switched switchable forward gears by means of a comparatively slightly modified transmission scheme.

This object is achieved by an automatic transmission with the features of claim 1. Further advantageous embodiments and developments will become apparent from the dependent claims.

Accordingly, an automatic transmission is proposed, which has a housing, including a drive shaft and including an output shaft a total of at least nine rotatable shafts, four individual planetary gear sets and at least six switching elements whose selective engagement different ratios between the drive shaft and output shaft effect switching multiple forward gears and at least one reverse. Each of the four planetary gear sets has three different elements, so in each case a sun gear, a planet carrier and a ring gear.

 The second element of the fourth planetary gear set forms the first shaft designed as a drive shaft. The second element of the third planetary gear set forms the output shaft designed as the second shaft. The first element of the first planetary gear set and the first element of the fourth planetary gear set are permanently rotationally fixed or rotationally elastic connected to each other and form (in the manner of a first coupling shaft), the third wave. The third element of the first planetary gear set forms the fourth wave. The third element of the second planetary gear set forms the fifth shaft. The second element of the first planetary gear set and the third element of the third planetary gear set are permanently rotationally fixed or rotationally elastic connected to each other and form (in the manner of a second coupling shaft), the sixth wave. The first element of the second planetary gear set and the third element of the fourth planetary gear set are permanently rotatably or rotationally connected to each other and form (in the manner of a third coupling shaft), the seventh shaft. The second element of the second planetary gear set forms the eighth wave. The first element of the third planetary gear set forms the ninth wave.

The first switching element is in the power flow between the third shaft and the housing (the third shaft is thus fixable via the first switching element, the first switching element is thus constantly and directly connected both to the first element of the first planetary gear set and the first element of the fourth planetary gear set and to the transmission housing). The second switching element is arranged in the power flow between the fourth shaft and the housing (the fourth shaft is thus fixable via the second switching element, ie the second switching element is permanently and directly connected both to the third element of the first planetary gear set and to the transmission housing). The third switching element is arranged in the power flow between the first shaft (drive shaft) and the ninth shaft (the third switching element is therefore constantly and directly connected both to the first shaft and to the first element of the third planetary gear set). The fourth switching element is arranged in the power flow between the second shaft (output shaft) and the eighth shaft (the output shaft is thus connectable via the fourth switching element with the eighth wave, the fourth switching element is thus constantly and directly with both the second element of the third planetary gear as also connected to the second element of the second planetary gear set). The fifth shift element is arranged in the power flow either between the fifth and the seventh shaft or between the fifth and the eighth shaft or between the seventh and the eighth shaft (the second planetary gear is thus blockable via the fifth switching element, in the blocked state - that is when the fifth shift element is closed - rotate all three elements of the second planetary gear set at the same speed). The sixth switching element is arranged in the power flow between the fifth and the ninth shaft (the fifth shaft is thus connectable via the sixth switching element with the ninth shaft, the sixth switching element is thus constantly and directly with both the third element of the second planetary gear set and with the connected to the first element of the third planetary gear set). Thus, the fifth shaft by simultaneous closing of the third and sixth switching element with the first shaft (drive shaft) can be connected.

Here, the term "directly connected" in connection with the coupling of a switching element to a planetary gear to understand that the input or output element of the respective switching element is connected via a rotationally fixed or torsionally elastic connection directly to one of the elements of the respective planetary gear, so it always gives a fixed speed relationship between this Planetenradsatzelement and the input and output element of this switching element.

In connection with the coupling of a switching element to a shaft is to be understood by the phrase "directly connected" that the input or output element of the respective switching element is connected via a rotationally fixed or torsionally elastic connection directly to the respective shaft, so that there is always a fixed speed relationship between this shaft and the input or output element of this switching element is.

In connection with the coupling of a planetary gear set to another planetary gear is under the phrase "directly connected" to understand that one of the elements of each planetary gear set is connected via a rotationally fixed or torsionally elastic connection directly with one of the elements of the other planetary gear set, so it always There is a fixed speed relationship between this shaft and the input and output element of this switching element.

Thus, the automatic transmission according to the invention over the prior art on a completely independent kinematics. Using six shift elements, nine forward gears and one reverse gear are shiftable.

Is an additional seventh switching element provided starting from this automatic transmission with six switching elements, this seventh switching element is arranged in the power flow between the first and the eighth wave. In this case, with a total of seven switching elements ten forward gears and one reverse gear can be switched.

Preferably, in the automatic transmission according to the invention in each gear four of the switching elements are closed. If six switching elements are provided, then preferably only two of the switching elements are not closed in each gear. If seven switching elements are provided, then preferably only three of the switching elements are not closed in each gear. When changing from one gear to the next higher or lower gear only one of the previously closed switching elements is opened and a previously open switching element is closed, so that when sequential upshifting and downshifting by one gear so-called group circuits are avoided.

To represent at least nine forward gears and at least one reverse gear, such a transmission may have the following shift logic or gear logic: In the first forward gear, the first, second, third and sixth shift element are closed or torque transmitting. In the second forward gear, the first, second, fifth and sixth switching element are closed or torque transmitting. In the third forward gear are the second, third, fifth and sixth switching element closed or torque transmitting. In the fourth forward gear, the second, fourth, fifth and sixth switching element are closed or torque transmitting. In the fifth forward gear, the second, third, fourth and fifth switching element are closed or torque transmitting. In the sixth forward gear, the second, third, fourth and sixth switching element are closed or torque transmitting. In the seventh forward gear, the third, fourth, fifth and sixth switching element are closed or torque transmitting. In the eighth forward gear, the first, third, fourth and sixth shift element are closed or torque transmitting. In the ninth forward gear, the first, fourth, fifth and sixth switching element are closed or torque transmitting. In reverse, the first, second, fourth and sixth switching element are closed or torque transmitting.

Is an additional seventh switching element present in the power flow between the first and eighth shaft, so compared to the transmission design with only six switching elements an additional forward gear below the first gear of the transmission design with only six switching elements feasible, ie an additional forward gear with a translation greater than that of the translation first gear of the gearbox design with only six switching elements. Thus, this additional forward gear is well suited as a so-called crawler with a small overall ratio for a large traction. As switching logic or gear logic can be provided that in such an additional forward gear, the first, second, sixth and seventh switching element are closed or torque transmitting, while in all other forward gears and in reverse, the seventh switching element is not closed or torque transmitting.

Advantageously, it is possible to accommodate the additional seventh switching element in the same space or in a little larger space, which is needed for the inventive transmission with only five or only six switching elements.

All four planetary gear sets can be designed as a so-called minus planetary gear sets, their respective planet gears mesh with sun gear and ring gear of the respective planetary gear set.

As an alternative to the design of the wheelset system with four individual minus planetary gear sets, individual ones of the minus planetary gear sets may be replaced by a so-called plus planetary gearset. As is well known, a positive planetary gearset includes a planet carrier ("land") having inner and outer planetary gears rotatably mounted thereon, each of the inner planetary gears meshing respectively with an outer planetary gear and the sun gear of the plus planetary gear while each of the outer planetary gears mesh with, respectively an inner planetary gear and meshes with the ring gear of the plus planetary gear set. As an alternative to the design of the wheelset system with four individual minus planetary gear sets also several of the negative planetary gear sets may be replaced by plus planetary gear sets.

To ensure the same kinematics of the claimed Radsatzsystems is provided that the first element of each minus planetary gear and the first element of each plus planetary gear is designed as a sun gear, that the second element of each negative planetary gear set is designed as a planet, while the second element each Plus planetary gear set is designed as a ring gear, and that the third element of each negative planetary gear set is designed as a ring gear, while the third element of each plus planetary gear set is designed as a planet carrier.

With regard to the spatial arrangement of the four planetary gear sets in the housing of the automatic transmission is proposed in an embodiment, all four planetary gear coaxial with each other side by side in the defined order "first, fourth, second, third planetary gear" to order, which makes it possible, all couplings in a simple way lickagearm to supply the necessary pressure for hydraulic actuation pressure medium. For an application with coaxially extending drive and output shaft, it is expedient in this case that the first planetary gear set of the drive of the automatic transmission facing planetary gear is the planetary gear set. In another embodiment, it is proposed with respect to the spatial arrangement of the four planetary gear sets in the housing of the automatic transmission, all four planetary gear coaxial with each other in the order defined "second, fourth, first, third planetary gear" to arrange, in which case for an application in a Vehicle with so-called "standard drive" is appropriate to turn to the second planetary gear set the drive side of the automatic transmission, while it is appropriate for an application in a vehicle with so-called "front-transverse drive", the third planetary gear set the drive side of the automatic transmission ,

• • das erste Schaltelement räumlich gesehen in einem Bereich axial zwischen dem ersten und vierten Planetenradsatz anzuordnen;
• • das zweite Schaltelement zumindest teilweise in einem Bereich radial über dem ersten Planetenradsatz anzuordnen, wobei das zweite Schaltelement auch als Klauenkupplung ausgeführt sein kann;
• • das dritte Schaltelement in einem Bereich axial zwischen dem zweiten und vierten Planetenradsatz anzuordnen, oder alternativ zumindest teilweise in einem Bereich radial über dem zweiten Planetenradsatz, oder alternativ auf der dem vierten Planetenradsatze abgewandten Seite des zweiten Planetenradsatzes, oder alternativ auf der dem ersten Planetenradsatze abgewandten Seite des dritten Planetenradsatzes;
• • das vierte Schaltelement in einem Bereich axial zwischen dem ersten und dritten Planetenradsatz anzuordnen, oder alternativ auf der dem vierten Planetenradsatz abgewandten Seite des zweiten Planetenradsatzes;
• • das fünfte Schaltelement in einem Bereich axial zwischen dem zweiten und vierten Planetenradsatz axial benachbart zum zweiten Planetenradsatz anzuordnen, oder alternativ auf der dem vierten Planetenradsatz abgewandten Seite des zweiten Planetenradsatzes;
• • das sechste Schaltelement in einem Bereich axial zwischen dem zweiten und vierten Planetenradsatz anzuordnen, oder alternativ zumindest teilweise in einem Bereich axial über dem zweiten Planetenradsatz, oder alternativ auf der dem vierten Planetenradsatz abgewandten Seite des zweiten Planetenradsatzes;
• • sofern vorhanden, das siebte Schaltelement in einem Bereich axial zwischen dem vierten und zweiten Planetenradsatz axial angrenzend an den zweiten Planetenradsatz anzuordnen.

In conjunction with the planetary gear set sequence "second, fourth, first, third planetary gear set" is proposed as an advantageous spatial arrangement of the switching elements,

• Spatially seen to arrange the first switching element in a region axially between the first and fourth planetary gear set;
• • to arrange the second switching element at least partially in a region radially above the first planetary gear, wherein the second switching element can also be designed as a dog clutch;
• • Arrange the third switching element in a range axially between the second and fourth planetary gear set, or alternatively at least partially in a region radially above the second planetary gear set, or alternatively on the fourth planetary gear opposite side of the second planetary gear set, or alternatively facing away from the first Planetenradsatz Side of the third planetary gear set;
• • to arrange the fourth switching element in a range axially between the first and third planetary gear set, or alternatively on the side remote from the fourth planetary gear set side of the second planetary gear set;
• • to arrange the fifth shift element in a region axially between the second and fourth planetary gear set axially adjacent to the second planetary gear set, or alternatively on the side of the second planetary gear set facing away from the fourth planetary gear set;
• • to arrange the sixth shift element in a region axially between the second and fourth planetary gear set, or alternatively at least partially in a region axially above the second planetary gear set, or alternatively on the side remote from the fourth planetary gear set side of the second planetary gear set;
• If present, to arrange the seventh shift element in a region axially between the fourth and second planetary gear set axially adjacent to the second planetary gear set.

• • erste Schaltelement räumlich gesehen auf derjenigen Seite des ersten Planetenradsatzes anzuordnen, die dem vierten Planetenradsatz abgewandt ist;
• • das zweite Schaltelement zumindest teilweise in einem Bereich radial über dem ersten Planetenradsatz anzuordnen, wobei das zweite Schaltelement auch als Klauenkupplung ausgeführt sein kann;
• • das dritte Schaltelement in einem Bereich axial zwischen dem zweiten und dritten Planetenradsatz anzuordnen;
• • das vierte Schaltelement in einem Bereich axial zwischen dem zweiten und dritten Planetenradsatz axial benachbart zum dritten Planetenradsatz anzuordnen, oder alternativ zumindest teilweise in einem Bereich axial zwischen dem zweiten und vierten Planetenradsatz;
• • das fünfte Schaltelement in einem Bereich axial zwischen dem zweiten und dritten Planetenradsatz axial benachbart zum zweiten Planetenradsatz anzuordnen, oder alternativ auf der dem dritten Planetenradsatz abgewandten Seite des zweiten Planetenradsatzes;
• • das sechste Schaltelement in einem Bereich axial zwischen dem zweiten und dritten Planetenradsatz anzuordnen;
• • sofern vorhanden, das siebte Schaltelement in einem Bereich axial zwischen dem vierten und zweiten Planetenradsatz axial angrenzend an den vierten Planetenradsatz anzuordnen, oder alternativ in einem Bereich axial zwischen dem ersten und vierten Planetenradsatz axial angrenzend an den vierten Planetenradsatz, oder alternativ in einem Bereich axial zwischen dem zweiten und dritten Planetenradsatz axial angrenzend an den zweiten Planetenradsatz.

In connection with the planetary gear set sequence "first, fourth, second, third planetary gear set" is proposed as an advantageous spatial arrangement of the switching elements,

• Spatially arranged to arrange the first switching element on that side of the first planetary gear set, which faces away from the fourth planetary gear set;
• • to arrange the second switching element at least partially in a region radially above the first planetary gear, wherein the second switching element can also be designed as a dog clutch;
• • To arrange the third switching element in a range axially between the second and third planetary gear set;
• • to arrange the fourth shift element in a region axially between the second and third planetary gear set axially adjacent to the third planetary gear set, or alternatively at least partially in a region axially between the second and fourth planetary gear set;
• • axially to arrange the fifth switching element in a range axially between the second and third planetary gear set to the second planetary gear set, or alternatively on the side remote from the third planetary gear set side of the second planetary gear set;
• • to arrange the sixth switching element in a range axially between the second and third planetary gear set;
• If present, axially locating the seventh shift element in a region axially between the fourth and second planetary gear set adjacent to the fourth planetary gear set, or alternatively axially adjacent the fourth planetary gear set axially between the first and fourth planetary gear set, or alternatively axially within a range between the second and third planetary gear set axially adjacent to the second planetary gear set.

In conjunction with both proposed planetary gear set sequences can be provided that the third and sixth switching element are spatially seen immediately adjacent to each other, and / or that the fifth and sixth switching element are spatially seen immediately adjacent to each other. This allows the use of common plate carriers in production technology advantageously.

All proposed embodiments and embodiments of an automatic transmission according to the invention have in particular for passenger cars in practice useful translations with very large overall spread in terms of driveability acceptable grading, which has a positive effect on the desired low fuel consumption. In addition, the automatic transmission according to the invention is characterized by a small number of switching elements measured on the number of gears and a comparatively low construction cost. Furthermore, results in the automatic transmission according to the invention in all gears a good efficiency, on the one hand due to low towing losses, since in each gear each of the switching elements are engaged, on the other hand due to low Verzahnungsverluste in the simple design single planetary gear sets.

Advantageously, it is possible with the automatic transmission according to the invention to realize a start of the motor vehicle both with a gear-external starting element and with a transmission-internal friction switching element. A gear-external starting element can in a conventional manner, for example, as a hydrodynamic converter, as a so-called dry starting clutch, as a so-called wet start-up clutch, as Magnetic powder clutch or be designed as a centrifugal clutch. As an alternative to the arrangement of such a starting element in the direction of power flow between the drive motor and the transmission, the gear-external starting element can also be arranged behind the transmission in the direction of the flow of force, in which case the drive shaft of the transmission is connected to the crankshaft of the drive motor in a rotationally fixed or rotationally elastic manner. For example, the first and second switching element, in particular the second switching element which carries the torque in many forward gears and in the reverse gear, are suitable as an internal gear starting element.

In addition, the automatic 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. Thus, with the same transmission scheme, depending on the stationary gear ratio of the individual planetary gear sets, different gear jumps result, so that an application- or vehicle-specific variation is made possible. Furthermore, it is possible without special design measures to arrange drive and output of the transmission either coaxially or axially parallel to each other. On the drive side or on the output side of the transmission, an axle differential and / or a distributor differential can be arranged. It is also possible to provide additional freewheels, for example, between a shaft and the housing or optionally to connect two shafts at any suitable point of the multi-speed transmission. Also, on each shaft, preferably on the drive shaft or on the output shaft, a wear-free brake, e.g. a hydraulic or electric retarder or the like may be arranged, which is of particular importance for use in commercial vehicles. Also may be provided to drive additional units on each shaft, preferably on the drive shaft or the output shaft, a power take-off. Another advantage of the automatic transmission according to the invention is that on each shaft additionally an electric machine as a generator and / or as an additional drive machine can be attached.

The switching elements used can be designed as a load-shifting clutches or brakes. In particular, non-positive clutches or brakes, such as e.g. Multi-plate clutches, band brakes and / or cone clutches are used. As switching elements but also positive brakes and / or clutches, such. Synchronizations or jaw clutches are used.

The invention will be explained in more detail below with reference to the drawings by way of example. Identical or comparable components are also provided with the same reference numerals. Show it:

1 a schematic representation of a first embodiment of a 9-speed automatic transmission according to the invention;

2 an exemplary circuit diagram for the transmission according to 1 ;

3 an alternative component arrangement for the transmission according to 1 ;

4 a table with variants of the transmission according to 1 ;

5 a schematic representation of a first alternative to the transmission according to 1 ;

6 a schematic representation of a second alternative to the transmission according to 1 ;

7 a schematic representation of a third alternative to the transmission according to 1 ;

8th a schematic representation of a second embodiment of a 9-speed automatic transmission according to the invention, derived from the transmission according to 1 ;

9 a schematic representation of a first alternative to the transmission according to 8th ;

10 a schematic representation of a second alternative to the transmission according to 8th ;

11 a schematic representation of a third alternative to the transmission according to 8th ;

12 a schematic representation of a third embodiment of a 9-speed automatic transmission according to the invention, derived from the transmission according to 1 ;

13 a schematic representation of a first alternative to the transmission according to 12 ;

14 a schematic representation of a second alternative to the transmission according to 12 ;

15 a schematic representation of a third alternative to the transmission according to 12 ;

16 a schematic representation of a first embodiment of a 10-speed automatic transmission according to the invention;

17 an exemplary circuit diagram for the transmission according to 16 ;

18 an alternative component arrangement for the transmission according to 16 ;

19 a table with variants of the transmission according to 16 ;

20 a schematic representation of a first alternative to the transmission according to 16 ;

21 a schematic representation of a second alternative to the transmission according to 16 ;

22 a schematic representation of a second embodiment of a 10-speed automatic transmission according to the invention, derived from the transmission according to 16 ;

23 a schematic representation of a first alternative to the transmission according to 22 ;

24 a schematic representation of a second alternative to the transmission according to 22 ;

25 a schematic representation of a third embodiment of a 10-speed automatic transmission according to the invention, derived from the transmission according to 16 ;

26 a schematic representation of a first alternative to the transmission according to 25 ; and

27 a schematic representation of a second alternative to the transmission according to 25 ,

In 1 the Radsatzschema a first embodiment of a 9-speed automatic transmission according to the invention is shown. Including a drive shaft AN and including an output shaft AB, the transmission comprises nine rotatable shafts 1 to 9 , four planetary gear sets RS1, RS2, RS3, RS4 and six switching elements A, B, C, D, E, F, which are all arranged in a housing GG of the transmission. All four planetary gear sets RS1, RS2, RS3, RS4 are formed as simple minus planetary gear sets, each comprising a first, a second and a third element. A minus planetary gearset has known planetary gears that mesh with sun and ring gear of this planetary gear set. The respective third elements of the four planetary gear sets RS1, RS2, RS3, RS4 are all formed as ring gears and designated HO1, HO2, HO3 and HO4. The respective first elements of the four planetary gear sets RS1, RS2, RS3, RS4 are all formed as sun gears and designated SO1, SO2, SO3 and SO4. The respective second elements of the four planetary gear sets RS1, RS2, RS3, RS4 are all designed as planet carrier and designated ST1, ST2, ST3 and ST4. The rotatably mounted on the planet carrier ST1, ST2, ST3 and ST4 planetary gears are designated PL1, PL2, PL3 and PL4.

The switching elements A and B are designed as brakes, which are executed in the illustrated embodiment as frictionally switchable disk brakes, in another embodiment can also be designed as frictionally engageable band brake or, for example, as a form-locking switchable claw or cone brake. The other switching elements C, D, E and F are designed as clutches, which are all executed in the illustrated embodiment as frictionally switchable multi-plate clutch, in another embodiment, for example, as a form-fitting switchable claw or cone clutch can be performed. With these six switching elements A to F is a selective switching of nine forward gears and one reverse gear feasible, which will be described later 2 will be explained in more detail.

With regard to the coupling of the individual elements of the four planetary gear sets RS1, RS2, RS3, RS4 with each other and to the drive and output shafts AN, AB is in the embodiment according to 1 The following is provided: The planet ST4 of the fourth planetary gear set RS4 and the drive shaft AN are rotationally fixed or rotationally elastic connected to each other and form the with 1 designated first shaft of the automatic transmission. The planet carrier ST3 of the third planetary gearset RS3 and the output shaft AB are rotatably or rotationally elastic connected to each other and form the with 2 designated second shaft of the automatic transmission. The sun gear SO1 of the first planetary gear set RS1 and the sun gear SO4 of the fourth planetary gearset RS4 are rotationally fixed or rotationally elastic constantly connected to each other and form - in the manner of a first coupling shaft - with 3 designated third shaft of the automatic transmission. The ring gear HO1 of the first planetary gear set RS1 forms with 4 designated fourth wave of the automatic transmission. The ring gear HO2 of the second planetary gear set RS2 forms with 5 designated fifth shaft of the automatic transmission. The planet carrier ST1 of the first planetary gearset RS1 and the ring gear HO3 of the third planetary gearset RS3 are rotationally fixed or rotationally elastic constantly connected to each other and form - in the manner of a second coupling shaft - with 6 designated sixth shaft of the automatic transmission. The ring gear HO4 of the fourth planetary gearset RS4 and the sun gear SO2 of the second planetary gearset RS2 are rotationally fixed or torsionally permanently connected to each other and form - in the manner of a third coupling shaft - with 7 designated seventh shaft of the automatic transmission. The planet carrier ST2 of the second planetary gear set RS2 forms with 8th designated eighth wave of the automatic transmission. The sun gear SO3 of the third planetary gearset RS3 forms with 9 designated ninth shaft of the automatic transmission.

With regard to the coupling of the six switching elements A to F to the nine waves thus described 1 to 9 of the gearbox and to the gearbox GG is in the in 1 illustrated automatic transmission according to the invention provided the following: The first switching element A is in the power flow between the third shaft 3 and the transmission housing GG arranged. The second switching element B is in the power flow between the fourth shaft 4 and the transmission housing GG arranged. The third switching element C is in the power flow between the first shaft 1 and the ninth wave 9 arranged. The fourth switching element D is in the power flow between the eighth wave 8th and the second wave 2 arranged. The fifth switching element E is exemplary in the power flow between the seventh shaft 7 and the eighth wave 8th arranged and used for selectively blocking the second planetary gearset RS2. The sixth switching element F is in the power flow between the fifth shaft 5 and the ninth wave 9 arranged. Thus, the fifth wave 5 by simultaneously closing the third and the sixth switching element C, F with the first shaft 1 (Drive shaft AN) connectable.

In the in 1 illustrated embodiment, the four planetary gear sets RS1, RS2, RS3, RS4 are arranged axially in the defined order "RS1, RS4, RS2, RS3" arranged coaxially one behind the other, wherein drive shaft AN and output shaft AB are arranged coaxially to each other and the first planetary gearset RS1 the drive wheel set of the automatic transmission and the third planetary gear set RS3 forms the driven wheel set of the automatic transmission. This arrangement "RS1, RS4, RS2, RS3" advantageously makes it possible for the four planetary gear sets RS1, RS2, RS3, RS4 to be penetrated centrically in the axial direction only by a maximum of one shaft of the automatic transmission.

In principle, the spatial arrangement of the switching elements within the transmission is arbitrary and is limited only by the dimensions and the external shape of the gear housing GG. Accordingly, the in 1 illustrated component assembly to understand expressly as only one of numerous possible component arrangement variants. Numerous suggestions for this find the expert, for example, in the above-mentioned document DE 10 2005 002 337 A1 , This in 1 illustrated embodiment is particularly well suited for installation in a motor vehicle with so-called "standard drive" due to the slim housing structure. In the 1 shown component assembly is based on the in 4 of the DE 10 2005 002 337 A1 revealed automatic transmission.

How out 1 As can be seen, the two planetary gear sets RS1 and RS4 directly adjoin one another. The brake A is in the illustrated embodiment spatially seen axially adjacent to the (arranged on the drive side of the transmission housing) first planetary gear set RS1, on the side of the planetary gearset RS1, which faces away from the planetary gearset RS4. The brake A is arranged on a comparatively large diameter, on a diameter larger than the diameter of the ring gear HO1. Can be supplied with pressure and coolant, the brake A in a simple way from the housing GG ago. The brake A can also be structurally easily integrated in a drive-close housing wall of the transmission housing GG.

How out 1 Furthermore, as can be seen, at least the disk set of the brake B is spatially arranged in a region radially above the first planetary gearset RS1. The brake B can be supplied with pressure and lubricant in a simple manner from the housing GG. The brake B can also be structurally easily integrated in the transmission housing GG or in a drive-close housing wall of the transmission housing GG.

How out 1 Furthermore, as can be seen, the four clutches C, D, E and F are spatially located in a region axially between the second planetary gear set RS2 (arranged on the side of the fourth planetary gear set RS4 facing away from the first planetary gear set RS1) and (arranged on the output side of the transmission housing). third planetary gearset RS3 arranged. The three clutches C, E and F are arranged axially next to each other on at least similar and large diameter, while the clutch D is arranged on a slightly larger diameter than the clutches C, E, F immediately adjacent to the third planetary gear set RS3. In this case, the clutch C axially adjoins the clutch D, while the clutch E axially adjacent to the second planetary gearset RS2. Thus, the clutch F is disposed axially between the clutch C and clutch E. In manufacturing technology advantageously, a common plate carrier is provided for the two clutches E and F, as part of the shaft 5 Here, by way of example, the outer disk carrier of the clutch E and the inner disk carrier of the clutch F is formed, so that the clutch E completely within the through the shaft 5 formed cylinder space is arranged. In manufacturing technology advantageously, a common plate carrier is provided for the two clutches C and F, as a section of the ninth wave 9 Here, for example, as a common outer disk carrier of the clutches C and F is formed, wherein the clutch C completely within the through the shaft 9 formed cylinder space is arranged. The eighth wave 8th , which forms the operative connection between the planet carrier ST2 of the second planetary gear set RS2 and the clutch D, surrounds the planetary gearset RS2 and the three Clutches E, F and C in the axial direction completely, so that the three clutches E, F and C is disposed within a cylinder space through the eighth shaft 8th is formed. Can be supplied with pressure and lubricant, the clutch C in advantageously simple manner from the drive shaft AN ago. With pressure and lubricant can be supplied to the clutch E, for example, coming from the drive shaft AN forth on the rotatably mounted on the drive shaft AN seventh shaft 7 , The clutch F can be supplied with pressure and lubricant, for example coming from the output shaft AB, via the ninth shaft rotatably mounted on the output shaft AB 9 , Can be supplied with pressure and lubricant, the clutch D in a structurally simple way leakage leakage from the output shaft AB forth on the constantly connected to the output shaft AB planet carrier ST3 of the third planetary gearset RS3.

As already indicated, the in 1 illustrated spatial arrangement of the switching elements to be understood as exemplary. Thus, depending on the installation space available for installing the transmission in the vehicle, it may be expedient, for example, to arrange the disk set of the clutch D spatially radially above the disk set of the adjacent clutch C in order to save axial transmission length.

How out 1 Furthermore, it can be seen that the planetary gear sets RS1, RS4 and RS2 are only each of the drive shaft AN (or shaft 1 ) is completely centered in the axial direction. This is particularly advantageous on the one hand for the dimensioning of the drive shaft AN and the wheelsets, on the other hand, for the comparatively simple lubricant supply to the planetary gears of the four planetary gear sets RS1 to RS4 and for the comparatively simple pressure and lubricant supply to the clutches. In its axial course, the drive shaft AN passes through the third shaft 3 and the seventh wave 7 centric. How out 1 as can be seen, the shaft overlaps 6 of the transmission, which forms the operative connection between the planet carrier ST1 of the (arranged on the drive side of the transmission housing) first planetary gearset RS1 and the ring gear HO3 of the (arranged on the output side of the transmission housing) third planetary gear set RS3, in its axial course, the second and fourth planetary gear set RS2, RS4 and the four clutches E, F, CD complete.

In 2 is an exemplary circuit diagram of the 9-speed automatic transmission according to the invention according to 1 shown. In each gear, four switching elements are closed and two switching elements open, which - has a very positive effect on the efficiency of the transmission - as a result of minimizing the drag losses that are obligatory on open friction shift elements. In addition to the switching logic, it can also be seen from the circuit diagram that so-called group switching is avoided in a sequential shift mode - that is to say when shifting up or down by one gear in each case, since two gear stages adjacent to one another in the shift logic always use two shift elements together. The seventh forward gear is designed as a direct gear, so that two so-called overdrive forward gears are available.

In the 1 proposed kinematics of the transmission is also possible with a different spatial arrangement of the four planetary gear sets RS1, RS2, RS3, RS4. 3 shows an example of an alternative in which the four planetary gear sets RS1, RS2, RS3, RS4 coaxial side by side with the defined order "second, fourth, first, third planetary gear set" (ie arrangement "RS2-RS4-RS1-RS3") are arranged , This arrangement is well suited for a transmission in which the drive shaft AN and output shaft AB are not arranged coaxially with each other, as is the case for example in a so-called front-transverse installation in the vehicle.

Here, the first planetary gear set RS1 is seen in the axial direction immediately adjacent to the (connected to the output shaft AB) third planetary gearset RS3 arranged such that the two planetary gear sets RS1, RS3 only through a portion leading to the clutch D of the second shaft 2 axially separated from each other. Of the (connected to the drive shaft AN) fourth planetary gearset RS4, which is arranged on the third planetary gearset RS3 side facing away from the first planetary gearset RS1, the first Planetenradsatze RS1 is separated by the inner disc carrier of the brake A. The brake A is thus both in one Arranged axially between the two central planetary gear sets RS4 and RS1, the brake B is arranged at least with its disc pack in a region radially above the first planetary gear set RS1.

How out 3 Furthermore, it can be seen that the clutches C, F and E form a production and assembly-technically favorable assembly, which is spatially arranged in a region axially between the second planetary gear set RS2 and the fourth planetary gear set RS4. Here, at least the disk sets of these three clutches C, F, E spatially arranged radially superimposed, wherein the disk set of the clutch C forms the radially outer disk set, the disk set of the clutch F the radially middle and the disk set of the clutch E the radially inner. For the two clutches C, F a common plate carrier is provided, which the inner plates of the disk set of the (radially outer) clutch C and the Outer plate of the disk pack of the (radially middle) clutch F receives and a portion of the ninth shaft 9 forms. For the two clutches F, E, a common plate carrier is provided, which receives the inner plates of the disk set of the (radially middle) clutch F and the outer disks of the disk set of the (radially inner) clutch E and a portion of the fifth shaft 5 forms. The second planetary gearset RS2 is splittable by closing the clutch E for connecting ring gear HO2 and sun gear SO2.

As seen in the axial direction, the first shaft connected to the planetary carrier ST4 of the fourth planetary gear set RS4 surrounds 1 First, the fourth planetary gearset RS4, the clutch assembly C / F / E and the second planetary gearset RS2 completely. Then the shaft passes through 1 the second planetary gearset RS2, the clutch assembly C / F / E, the fourth planetary gearset RS4, the brake A, the first planetary gearset RS1 (together with the brake B) and the third planetary gearset RS3 in this order centric complete, wherein the shaft 9 (As an operative connection between the sun gear SO3 and the clutches C, F) this section of the shaft 1 encloses radially.

How out 3 Furthermore, it can be seen, the clutch D is spatially arranged on that side of the second planetary gearset RS2, which faces away from the fourth planetary gearset RS4. Thus, that section of the second shaft passes through 2 , which is exemplarily connected to the inner disk carrier of the clutch D, in its axial course, the first planetary gearset RS1, the fourth planetary gearset RS4, the clutch assembly C / F / E and the second planetary gearset RS2 and encloses that portion of the ninth shaft 9 who is the first wave 1 encloses radially. This section of the second wave 2 turn, both from the shaft 7 (Coupling shaft between sun gear SO2 and ring gear HO4) and from the shaft 3 (Coupling shaft between the sun gears SO4 and SO1) radially enclosed.

At this point I would like to point out the exemplary character of the in 3 indicated spatial arrangement of the switching elements. alternative to 3 For example, the brake B can be designed as a form-locking switching element.

alternative to 3 can clutch C, which is in the power flow between shaft 1 (Drive shaft AN) and shaft 9 is spatially, for example, at least partially disposed in a region radially above the second planetary gear set RS2; or alternatively be arranged completely on that side of the second planetary gear set RS2, which faces away from the fourth planetary gear set RS4; or alternatively be arranged completely on that side of the third planetary gear set RS3, which faces away from the first planetary gear set RS1.

alternative to 3 can clutch D, which is in the power flow between shaft 2 (Planet carrier ST3 or output shaft AB) and shaft 8th (Planetenradträger ST2) is spatially, for example, in a range axially between the first planetary gear set RS1 and the third planetary gear set RS3 to be arranged.

alternative to 3 can the clutch E, which is in the power flow here between shaft 7 and wave 5 located spatially seen, for example, in a region radially above the ring gear HO4 of the fourth planetary gearset RS4 or alternatively be arranged in a region radially above the ring gear HO2 of the second planetary gear set RS2.

Based on the finding that it is possible in principle to replace a so-called minus planetary gear set by a kinematic equivalent plus planetary gear, provided that the coupling of sun, planet and ring gear of this planetary gear set to the other planetary gear sets and the switching elements and optionally to the Housing permits, shows 4 a table in which technically meaningful combinations of planetary gear set types for the in 1 gearbox scheme are listed. All variants listed in the table can be used via the in 2 shown switching logic nine forward gears and one reverse gear.

As is well known, in a negative planetary gear set, each of its planetary gears mesh with both the sun gear and the ring gear, while in a plus planetary gear set, each of its inner planet gears mesh with one of its outer planet gears and the sun gear and each of its outer planetary gears mesh with one of its inner gears Planet gears and the ring gear is in meshing engagement. Out 4 it can be seen that it is not technically meaningful to carry out the third planetary gear set RS3 permanently connected to the output shaft as a plus planetary gear set, while the formation of one or more of the other three planetary gear sets RS1, RS2 and RS4 leads to technically useful results. In the following, three examples of these variations are explained in more detail.

5 shows a schematic representation of a first alternative to the in 1 illustrated transmission scheme. In contrast to the transmission scheme according to 1 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 5 the first planetary gear set RS1 designed as a plus planetary gear set, while the other three planetary gear sets RS2, RS3, RS4 are unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 5 across from 1 unchanged, as well as the spatial arrangement of all six switching elements A to F.

To the kinematics of the wheelset according to 1 to maintain is in 5 The following is provided: Unchanged, the sun gear SO1 forms the first element of the first planetary gearset RS1, which transmits via the third shaft (acting as a first coupling shaft) 3 the automatic transmission is constantly directly connected both to the sun gear SO4 of the fourth planetary gear set RS4 and to the brake A, ie via this brake A (together with the sun gear SO4) to the transmission housing GG can be fixed. Now, the ring gear HO1 forms the second element of the first planetary gearset RS1, which via the (acting as a second coupling shaft) sixth shaft 6 is constantly connected to the third element (ring gear HO3) of the third planetary gear set RS3. Now, the planet carrier ST1 forms the third element of the first planetary gear set RS1, which is constantly connected directly to the brake B and via this brake B to the transmission housing GG can be fixed.

6 shows a schematic representation of a second alternative to the in 1 illustrated transmission scheme. In contrast to the transmission scheme according to 1 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 6 the fourth planetary gear set RS4 designed as a plus planetary gear, while the other three planetary gear sets RS1, RS2, RS3 are designed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 6 across from 1 unchanged, as well as the spatial arrangement of all six switching elements A to F.

To the kinematics of the wheelset according to 1 to maintain is in 6 The following is provided: unchanged, the sun gear SO4 forms the first element of the fourth planetary gear set RS4, which via the third (acting as the first coupling shaft) third wave 3 of the automatic transmission with both the sun gear SO1 of the first planetary gear set RS1 and the brake A is constantly connected directly, so this brake A (together with the sun gear SO1) on the transmission housing GG can be fixed. Now, the ring gear HO4 forms the second element of the fourth planetary gearset RS4, which as the first wave 1 the automatic transmission is designed as a drive shaft AN or is constantly connected to the drive shaft AN. Now, the planet carrier ST4 forms the third element of the fourth planetary gearset RS4, which via the (seventh coupling shaft acting) seventh wave 7 the automatic transmission is constantly connected to the first element (sun gear SO2) of the second planetary gear set RS2.

7 shows a schematic representation of a third alternative to the in 1 illustrated transmission scheme. In contrast to the transmission scheme according to 1 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 7 the second planetary gear set RS2 designed as a plus planetary gear set, while the other three planetary gear sets RS1, RS3, RS4 are performed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 7 across from 1 unchanged, as well as the spatial arrangement of all six switching elements A to F.

To the kinematics of the wheelset according to 1 to maintain is in 7 The following is provided: The sun gear SO2, unchanged, forms the first element of the second planetary gearset RS2, which transmits via the seventh shaft (acting as the third coupling shaft) 7 the automatic transmission is constantly connected to the third element (ring gear HO4) of the fourth planetary gearset RS4. Now, the ring gear HO2 forms the second element of the second planetary gear set RS2, which is the eighth wave 8th the automatic transmission constantly connected directly to the clutch D and via this clutch D with the second shaft 2 or the second element (planet carrier ST3) of the third planetary gear set RS3 is connectable. Now, the planet carrier ST2 forms the third element of the second planetary gearset RS2, which is the fifth shaft 5 the automatic transmission constantly connected directly to the clutch F and this clutch F with the ninth shaft 9 or the first element (sun gear SO3) of the third planetary gear set RS3 is connectable. If the second planetary gear set RS2 is to be locked, so that all three elements of the planetary gear set RS2 rotate at the same speed, the then closed clutch E now connects the sun gear SO2 and the planet carrier ST2 of the second planetary gearset RS2 to one another.

In consideration of these three exemplified alternatives to the in 1 illustrated transmission scheme, the skilled artisan easily the others in the table 4 generate listed alternatives with multiple plus planetary gear sets. In order to retain the kinematics of the wheelset system, only the first element of each negative Planetary gear set as a sun gear, the second element of each negative planetary gear as a planet and the third element of each negative planetary gear set as a ring gear, while the first element of each plus planetary as sun, the second element of each plus planetary as a ring gear and the third element Each plus planetary gear set must be designed as a planet carrier.

In principle, in the automatic transmissions according to the invention, the second planetary gear set RS2 can be linked in three different ways, by means of which two of the elements of the planetary gear set RS2 can be connected to one another via clutch E. While in the embodiments of the 1 . 3 . 5 and 6 is provided that the planetary gearset RS2 is blockable by selectively connecting the sun gear SO2 and ring gear HO2, the other two options are explained below.

8th shows a schematic representation of a second embodiment of a 9-speed automatic transmission according to the invention, derived from the transmission according to 1 , In contrast to 1 is provided here that the second planetary gear set RS2 is connectable by selectively connecting the planet carrier ST2 and ring gear HO2. The clutch E provided for blocking the planetary gearset RS2 is therefore now arranged in the power flow between the planet carrier ST2 and the ring gear HO2. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 8th across from 1 unchanged, as well as the spatial arrangement of all six switching elements A to F.

In the 8th shown embodiment of all four planetary gear sets RS1, RS2, RS3, RS4 as a simple minus planetary gear sets is again considered to be exemplary. Without changing the kinematics of the wheelset system, one or more of the negative planetary gear sets can be substituted by plus planetary gear sets. According to shows 9 a schematic representation of a first alternative to the in 8th illustrated transmission scheme. In contrast to the transmission scheme according to 8th in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 9 (similar to in 5 ), the first planetary gear set RS1 designed as a plus planetary gear, while the other three planetary gear sets RS2, RS3, RS4 are performed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 9 across from 1 and 8th unchanged, as well as the spatial arrangement of all six switching elements A to F. The structural changes due to the interchange of the connection of the planet carrier and ring gear of the plus planetary gear set with respect to the negative planetary gear set were already based on 5 explained and therefore need no repetition at this point.

10 shows a schematic representation of a second alternative to the in 8th illustrated transmission scheme. In contrast to the transmission scheme according to 8th is in the transmission scheme according to 10 the fourth planetary gear set RS4 designed as a plus planetary gear, while the other three planetary gear sets RS1, RS2, RS3 are designed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 10 across from 1 and 8th unchanged, as well as the spatial arrangement of all six switching elements A to F. The structural changes due to the interchange of the connection of the planet carrier and ring gear of the plus planetary gear set with respect to the negative planetary gear set were already based on 6 explained and therefore need no repetition at this point.

11 shows a schematic representation of a third alternative to the in 8th illustrated transmission scheme. In contrast to the transmission scheme according to 8th is in the transmission scheme according to 11 the second planetary gear set RS2 designed as a plus planetary gear set, while the other three planetary gear sets RS1, RS3, RS4 are performed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 11 across from 1 and 8th unchanged, as well as the spatial arrangement of the six switching elements A to F. The structural changes due to the interchange of the connection of planet carrier and ring gear of the plus planetary gear set with respect to the negative planetary gear set were already based on 7 explained and therefore need no repetition at this point.

12 shows a schematic representation of a third embodiment of a 9-speed automatic transmission according to the invention, also derived from the transmission according to 1 , In contrast to 1 is provided here that the second planetary gear set RS2 is blockable by selectively connecting the planet carrier ST2 and sun gear SO2. The clutch E provided for blocking the planetary gear set RS2 is therefore now arranged in the power flow between the planet carrier ST2 and the sun gear SO2. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 12 across from 1 unchanged, as well as the spatial arrangement of the switching elements A, B, C, D and F. In contrast to 1 the clutch E is spatially arranged now in a range axially between the fourth planetary gearset RS4 and the second planetary gearset RS2, but may alternatively also, for example, on the third Planetary gearset RS3 facing side of the second planetary gearset RS2 in the range axially between the planetary gearset RS2 and clutch F or in the range axially between the planetary gearset RS2 and clutch C radially below the clutch F be arranged.

In the 12 illustrated embodiment of all four planetary gear sets RS1, RS2, RS3, RS4 as a simple minus planetary gear sets is again only exemplary. Without changing the kinematics of the wheelset system, one or more of the negative planetary gear sets can be substituted by plus planetary gear sets. According to shows 13 a schematic representation of a first alternative to the in 12 illustrated transmission scheme. In contrast to the transmission scheme according to 12 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 13 the first planetary gear set RS1 designed as a plus planetary gear set, while the other three planetary gear sets RS2, RS3, RS4 are performed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 13 across from 12 unchanged, as well as the spatial arrangement of all six switching elements A to F. The structural changes due to the interchange of the connection of the planet carrier and ring gear of the plus planetary gear set with respect to the negative planetary gear set were already based on 5 explained and therefore need no repetition at this point.

14 shows a schematic representation of a second alternative to the in 12 illustrated transmission scheme. In contrast to the transmission scheme according to 12 is in the transmission scheme according to 14 the fourth planetary gear set RS4 designed as a plus planetary gear, while the other three planetary gear sets RS1, RS2, RS3 are designed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 14 across from 12 unchanged, as well as the spatial arrangement of all six switching elements A to F. The structural changes due to the interchange of the connection of the planet carrier and ring gear of the plus planetary gear set with respect to the negative planetary gear set were already based on 6 explained and therefore need no repetition at this point.

15 shows a schematic representation of a third alternative to the in 12 illustrated transmission scheme. In contrast to the transmission scheme according to 12 is in the transmission scheme according to 15 the second planetary gear set RS2 designed as a plus planetary gear set, while the other three planetary gear sets RS1, RS3, RS4 are performed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 15 across from 12 unchanged, as well as the spatial arrangement of all six switching elements A to F. The structural changes due to the interchange of the connection of the planet carrier and ring gear of the plus planetary gear set with respect to the negative planetary gear set were already based on 7 explained and therefore need no repetition at this point.

In 16 the Radsatzschema a first embodiment of a 10-speed automatic transmission according to the invention is shown. The wheelset scheme shown here is a further development of the in 1 illustrated 9-speed automatic transmission. With the goal of another forward, without the in 1 significantly change the specified transmission structure and to have to increase the required length of the transmission significantly, is based on the in 1 shown transmission scheme in the transmission according to 16 provided an additional seventh switching element G, which is designed as a coupling and in the power flow between the first shaft 1 (Drive shaft AN) and the eighth shaft 8th the transmission is arranged. As a result, an additional forward gear below the 2 achieved first gear known the 9-speed transmission, so an additional starting gear with a translation greater than the translation of 2 known first gear.

As in 1 are at the in 16 illustrated embodiment, all four planetary gear sets RS1, RS2, RS3, RS4 formed as a simple minus planetary gear sets, each of which has a first, a second and a third element, that is, each a sun gear, a planet carrier and a ring gear. The first elements are all designed as sun gears, the second elements all as planet carrier and the third elements all as ring gears. The spatial arrangement of the four planetary gear sets RS1, RS2, RS3, RS4 coaxial side by side with the defined order "first, fourth, second, third planetary gear" (ie arrangement "RS1-RS4-RS2-RS3") is off 1 unchanged. Out 1 also adopted is the spatial arrangement of the six switching elements A to F.

How out 16 Furthermore, the force flow between the drive shaft AN (or shaft 1 ) and the planet carrier ST2 (shaft 8th ) arranged spatially arranged in a range axially between the first planetary gear set RS1 and the fourth planetary gear set RS4. This allows the arrangement of the Disc packs of the clutch G, which - as will be explained later, is closed only in the first forward gear and then has to transmit a relatively large torque - on a comparatively large diameter, similar to the diameter of the two ring gears HO1 and HO4. Correspondingly, the section of the eighth shaft connected here by way of example with the outer disk carrier of the clutch G and the planet carrier ST2 of the second planetary gearset RS2 overlaps 8th the fourth planetary gearset RS4 complete, whereby the planetary gearset RS4 and the clutch G are arranged within a cylinder space, which passes through this portion of the shaft 8th is formed. The pressure and lubricant supply to the clutch G can be realized in a structurally simple manner with low leakage loss via the drive shaft AN and the planet carrier ST4 of the fourth planetary gear set RS4, which is constantly connected to the drive shaft.

The spatial arrangement of the clutch G shown here is exemplary in nature; Of course, the expert can also place the clutch G spatially elsewhere. For example, spatially seen, the clutch G may also be arranged axially in a region between the second planetary gearset RS2 and the fourth planetary gearset RS4. In particular, when the clutch G is designed in the form of a dog clutch, it is advisable to arrange the clutch G axially adjacent to the second planetary gearset RS2 in a range axially between the second planetary gearset RS2 and the third planetary gearset RS3, for example, near the clutch F (Which presupposes that the clutch E is arranged either in the power flow between ring gear HO2 and planet carrier ST2 of the second planetary gearset RS2 or spatially axially between the second planetary gearset RS2 and the fourth planetary gearset RS4), or for example below the clutch E (which requires the clutch E is arranged in the power flow between ring gear HO2 and planet carrier ST2 of the second planetary gear set RS2).

In 17 is an exemplary circuit diagram of the inventive 10-speed automatic transmission according to 16 shown. In each gear four switching elements are closed and three switching elements open. Furthermore, it can be seen from the circuit diagram that in the case of sequential switching operation, double circuits or group circuits are avoided since two gear stages adjacent to one another in the shifting logic always use two switching elements in common. The first forward gear is well suited as a so-called crawler with a small overall ratio for a large traction. The eighth forward gear is designed as a direct gear, so see three forward gears with overdrive character available.

In the 16 proposed kinematics of the transmission with the extension of a seventh switching element G is also possible with a different spatial arrangement of the four planetary gear sets RS1, RS2, RS3, RS4. 18 shows an example of an alternative in which the four planetary gear sets RS1, RS2, RS3, RS4 coaxial side by side with the defined order "second, fourth, first, third planetary gear set" (ie arrangement "RS2-RS4-RS1-RS3") are arranged , Drive shaft AN and output shaft AB are not arranged coaxially with each other; Drive and output of the transmission are in the illustrated embodiment on the same side of the transmission, namely "before" the third planetary RS3, ie on the side facing away from the first planetary gearset RS1 side of the third planetary gearset RS3. This in 18 illustrated embodiment is derived from the in 3 illustrated embodiment.

The spatial arrangement of the two brakes A, B and the clutch D is unchanged 3 accepted. To the opposite 3 additional clutch G in the power flow between the first shaft 1 (Drive shaft AN) and the eighth shaft 8th (Planet carrier ST2) to arrange, is the off 3 known assembly with the three clutches C, F, E has now been modified.

How out 18 it can be seen, the additional clutch G is spatially arranged in the region axially between the second planetary gear set RS2 and the fourth planetary gear set RS4. This arrangement requires that the clutch E provided for blocking the second planetary gearset RS2 is now arranged between the ring gear HO2 and the planet carrier ST2 of the second planetary gearset RS2 in the flux of force.

How out 18 further evident is - similar to in 3 - Provided for the two clutches C and F, a common plate carrier, which is a portion of the ninth wave 9 forms, the arrangement of the disk set of the clutch C radially over the disk set of the clutch F allows and this is adapted to receive the inner disks of the disk set of the clutch C and for receiving the outer disk of the disk set of the clutch F. Deviating from 3 However, this common plate carrier C / F is now spatially arranged radially above the second planetary gear set RS2. Similar to in 3 is also provided for the two clutches F and E, a common plate carrier, which is a portion of the fifth shaft 5 and for receiving the inner disk of the disk set of the clutch F and for receiving the outer disk of the disk set of the clutch E is formed, but now such that the disk set of the clutch E seen in the axial direction next to the Disc pack of the clutch F is arranged. Spatially, the disk set of the clutch E is on that side of the second planetary gearset RS2, which is applied to the fourth planetary gear set RS4. This allows in manufacturing and assembly technology favorable way another common plate carrier, namely a common plate carrier for the clutches E and D, which allows the arrangement of the disk set of the clutch E radially above the disk set of the clutch D and this for receiving the inner disks of the disk set Clutch E and designed to accommodate the outer disk of the disk set of the clutch D and as a section of the eighth shaft 8th is connected to the planet carrier ST2 of the second planetary gear set RS2.

Of course, the expert can arrange the seven switching elements A to G within the housing GG other than as in 18 shown. For example, possible alternatives have already been provided in the context of 3 and 18 discussed. In the 33 shown arrangement variant is well suited for a so-called front-transverse installation of the automatic transmission in the vehicle due to its compact design.

In the 16 illustrated embodiment of all four planetary gear sets RS1, RS2, RS3, RS4 as a simple minus planetary gear sets is to be understood as exemplary. Without changing the kinematics of the wheelset system, one or more of the negative planetary gear sets can be substituted by plus planetary gear sets. 19 shows a table with such planetary gear set type variations, which lead to a technically meaningful transmission structure. In the following, two of these examples are explained in more detail. All variants listed in the table can be used via the in 17 shown switching logic ten forward gears and one reverse gear.

20 shows a schematic representation of a first alternative to the in 31 illustrated transmission scheme. In contrast to the transmission scheme according to 16 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 20 the first planetary gear set RS1 designed as a plus planetary gear set, while the other three planetary gear sets RS2, RS3, RS4 are performed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 20 across from 16 unchanged, as well as the spatial arrangement of the seven switching elements A to G.

To the kinematics of the wheelset according to 16 to maintain is in 20 provided that unchanged the sun gear SO1 as the first element of the first planetary gear set RS1 on the (as the first coupling shaft acting) third wave 3 of the automatic transmission with both the sun gear SO4 of the fourth planetary gear set RS4 and the brake A constantly connected directly and via this brake A (together with the sun gear SO4) to the transmission housing GG can be fixed, but that now the ring gear HO1 as the second element of first planetary gearset RS1 via the (acting as a second coupling shaft) sixth shaft 6 is constantly connected to the third element (ring gear HO3) of the third planetary gearset RS3, and that now the planet ST1 as the third element of the first planetary gear set RS1 is constantly connected directly to the brake B and this brake B to the transmission housing GG can be fixed.

21 shows a schematic representation of a second alternative to the in 16 illustrated transmission scheme. In contrast to the transmission scheme according to 16 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 21 the second planetary gear set RS2 designed as a plus planetary gear set, while the other three planetary gear sets RS1, RS3, RS4 are performed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 21 across from 16 unchanged, as well as the spatial arrangement of the seven switching elements A to G.

To the kinematics of the wheelset according to 16 to maintain is in 21 provided that unchanged the sun gear SO2 as the first element of the second planetary gear set RS2 on the (seventh wave acting as the third coupling shaft) 7 the automatic transmission with the third element (ring gear HO4) of the fourth planetary gearset RS4 is connected, but that now the ring gear HO2 as the second element of the second planetary gear set RS2 (the eighth shaft directly connected to the clutches D and G) 8th of the automatic transmission, and that now the planet carrier ST2 as the third element of the second planetary gearset RS2 the (via the clutch F with the ninth wave 9 connectable) fifth wave 5 of the automatic transmission forms. If the second planetary gear set RS2 is to be locked, so that all three elements of the planetary gear set RS2 rotate at the same speed, the then closed clutch E now connects the sun gear SO2 and the planet carrier ST2 of the second planetary gearset RS2 to one another.

In consideration of these two exemplified alternatives to the in 16 illustrated transmission scheme, the skilled artisan easily the others in the table 19 generate listed alternatives with multiple plus planetary gear sets. To maintain the kinematics of the wheelset system, only the first element of each negative planetary gear set as sun gear, the second element of each negative planetary gear set as planet carrier and the third element of each negative planetary gear set must be formed as a ring gear, while the first element of each plus planetary gear as Sun gear, the second element of each plus planetary gear set must be designed as a ring gear and the third element of each plus planetary gear as a planet carrier.

As already explained above, in the automatic transmissions according to the invention, the second planetary gear set RS2 can be blocked in three different ways, by means of which two of the elements of the planetary gear set RS2 can be connected to one another via clutch E. While in the embodiments of the 16 and 20 is provided that the planetary gearset RS2 is blockable by selectively connecting the sun gear SO2 and ring gear HO2, the other two options are explained below.

22 shows a schematic representation of a second embodiment of a 10-speed automatic transmission according to the invention, derived from the transmission according to 16 , In contrast to 16 is provided here that the second planetary gear set RS2 is connectable by selectively connecting the planet carrier ST2 and ring gear HO2. The clutch E provided for blocking the planetary gearset RS2 is therefore now arranged in the power flow between the planet carrier ST2 and the ring gear HO2. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 22 across from 16 unchanged, as well as the spatial arrangement of the seven switching elements A to G.

In the 22 illustrated embodiment of all four planetary gear sets RS1, RS2, RS3, RS4 as a simple minus planetary gear sets is again only exemplary. Without changing the kinematics of the wheelset system, one or more of the negative planetary gear sets can be substituted by plus planetary gear sets. According to shows 23 a schematic representation of a first alternative to the in 22 illustrated transmission scheme. In contrast to the transmission scheme according to 22 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 23 the first planetary gear set RS1 designed as a plus planetary gear set, while the other three planetary gear sets RS2, RS3, RS4 are performed unchanged as negative planetary gear sets. 24 shows a schematic representation of a second alternative to the in 22 illustrated transmission scheme. In contrast to the transmission scheme according to 22 is in the transmission scheme according to 24 the second planetary gear set RS2 designed as a plus planetary gear set, while the other three planetary gear sets RS1, RS3, RS4 are performed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in the 23 and 24 across from 22 unchanged, as well as the spatial arrangement of the seven switching elements A to G.

25 shows a schematic representation of a third embodiment of a 10-speed automatic transmission according to the invention, also derived from the transmission according to 16 , In contrast to 16 is provided here that the second planetary gear set RS2 is blockable by selectively connecting the planet carrier ST2 and sun gear SO2. The clutch E provided for blocking the planetary gear set RS2 is therefore now arranged in the power flow between the planet carrier ST2 and the sun gear SO2. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 25 across from 16 unchanged, as well as the spatial arrangement of the switching elements A to D and F and G. In contrast to 16 the clutch E spatially arranged now in a range axially between the fourth planetary gearset RS4 and the second planetary gear set RS2, but may alternatively also, for example on the third planetary gearset RS3 side facing the second planetary gear set RS2 in the range axially between the planetary gear set RS2 and clutch F or be arranged in the region radially below the clutch F.

In the 25 illustrated embodiment of all four planetary gear sets RS1, RS2, RS3, RS4 as a simple minus planetary gear sets is again only exemplary. Without changing the kinematics of the wheelset system, one or more of the negative planetary gear sets can be substituted by plus planetary gear sets. According to shows 26 a schematic representation of a first alternative to the in 25 illustrated transmission scheme. In contrast to the transmission scheme according to 25 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 26 the first planetary gearset RS1 designed as a plus planetary gear set, while the other three planetary gear sets RS2, RS3, RS4 unchanged as negative planetary gear sets are executed. 27 shows a schematic representation of a second alternative to the in 25 illustrated transmission scheme. In contrast to the transmission scheme according to 25 is in the transmission scheme according to 27 the second planetary gear set RS2 designed as a plus planetary gear set, while the other three planetary gear sets RS1, RS3, RS4 are performed unchanged as negative planetary gear sets. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in the 26 and 27 across from 25 unchanged, as well as the spatial arrangement of the seven switching elements A to G.

LIST OF REFERENCE NUMBERS

1

first wave

2

second wave

3

third wave, first coupling shaft

4

fourth wave

5

fifth wave

6

sixth shaft, second coupling shaft

7

seventh wave, third coupling wave

8th

eighth wave

9

ninth wave

A

first switching element, first brake

B

second switching element, second brake

C

third switching element, first clutch

D

fourth switching element, second clutch

e

fifth switching element, third clutch

F

sixth switching element, fourth clutch

G

seventh switching element, fifth clutch

AT

drive shaft

FROM

output shaft

GG

casing

RS1

first planetary gear set

SO1

Sun gear of the first planetary gear set

ST1

Planetary carrier of the first planetary gear set

PL1

Planetary gears of the first planetary gear set

HO1

Ring gear of the first planetary gear set

RS2

second planetary gear set

SO2

Sun gear of the second planetary gear set

ST2

Planet carrier of the second planetary gear set

PL2

Planetary gears of the second planetary gear set

HO2

Ring gear of the second planetary gear set

RS3

third planetary gear set

SO3

Sun gear of the third planetary gear set

ST3

Planet carrier of the third planetary gear set

PL3

Planetary gears of the third planetary gear set

HO3

Ring gear of the third planetary gear set

RS4

fourth planetary gear set

SO4

Sun gear of the fourth planetary gear set

ST4

Planet carrier of the fourth planetary gear set

PL4

Planetary gears of the fourth planetary gear set

HO4

Ring gear of the fourth planetary gear set

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

• DE 102005002337 A1 [0003, 0004, 0004, 0005, 0064, 0064]
• DE 102010041575 B3 [0004]
• DE 102009001253 B3 [0005]

Claims (41)

Automatic transmission, in particular for a motor vehicle, having a housing (GG), with a plurality of rotatable shafts ( 1 to 9 Including a drive shaft (AN) and including an output shaft (AB), with four planetary gear sets (RS1, RS2, RS3, RS4), each having a first, second and third element, and with a plurality of switching elements (A to F, A to G), whose selective closing different ratios between drive shaft (AN) and output shaft (AB) cause switching of several forward gears and at least one reverse gear, wherein • the second element (ST4, HO4) of the fourth planetary gear set (RS4) as a drive shaft (AN ) executed first wave ( 1 ), the second element (ST3) of the third planetary gear set (RS3) has a second shaft designed as output shaft (AB) ( 2 ), • the first element (SO1) of the first planetary gear set (RS1) and the first element (SO4) of the fourth planetary gear set (RS4) are permanently rotationally fixed or torsionally elastic connected to each other and a third wave ( 3 ), the third element (HO1, ST1) of the first planetary gear set (RS1) has a fourth shaft (FIG. 4 ), the third element (HO2, ST2) of the second planetary gear set (RS2) has a fifth shaft (FIG. 5 ), the second element (ST1, HO1) of the first planetary gear set (RS1) and the third element (HO3, ST3) of the third planetary gear set (RS3) are permanently connected to one another in a rotationally fixed or torsionally flexible manner and a sixth shaft ( 6 ), the first element (SO2) of the second planetary gear set (RS2) and the third element (HO4; ST4) of the fourth planetary gear set (RS4) are permanently rotationally fixed or rotationally elastically connected to one another and a seventh shaft ( 7 ), the second element (ST2, HO2) of the second planetary gearset (RS2) has an eighth shaft (FIG. 8th ), • a first switching element (A) in the force flow between the third wave ( 3 ) and the housing (GG) is arranged, • a second switching element (B) in the power flow between and the fourth wave ( 4 ) and the housing (GG) is arranged, • a fourth switching element (D) in the power flow between the second shaft ( 2 ) and the eighth wave ( 8th ) is arranged and • a fifth switching element (E) in the power flow either between the fifth wave ( 5 ) and the seventh wave ( 7 ) or between the fifth wave ( 5 ) and the eighth wave ( 8th ) or between the seventh wave ( 7 ) and the eighth wave ( 8th ), characterized in that • the first element (SO3) of the third planetary gear set (RS3) has a ninth wave ( 9 ), • a third switching element (C) in the force flow between the first shaft ( 1 ) and the ninth wave ( 9 ) is arranged, and • a sixth switching element (F) in the power flow between the fifth shaft ( 5 ) and the ninth wave ( 9 ), so that the fifth wave ( 5 ) by simultaneously closing the third and sixth switching elements (C, F) with the first shaft ( 1 ) is connectable. Automatic transmission according to claim 1, characterized in that the third and sixth switching element (C, F) are directly connected to each other. Automatic transmission according to claim 1 or 2, characterized in that the fifth and sixth switching element (E, F) are connected directly to each other. Automatic transmission according to claim 1, 2 or 3, characterized in that a seventh switching element (G) in the power flow between the first shaft ( 1 ) and the eighth wave ( 8th ) is arranged. Automatic transmission according to one of claims 1 to 4, characterized in that in each gear four of the switching elements are closed, wherein when changing from a gear in the following higher or lower gear only one of the previously closed switching elements open and closed a previously open switching element becomes. Automatic transmission according to one of claims 1 to 3 and 5, characterized in that nine forward gears and one reverse gear are switchable, wherein - in the first forward gear, the first, second, third and sixth switching element (A, B, C, F) are torque-conducting, - in the second forward gear, the first, second, fifth and sixth shift elements (A, B, E, F) are torque-conducting, - in the third forward gear, the second, third, fifth and sixth shift element (B, C, E, F) are torque-conducting, - in the fourth forward gear, the second, fourth, fifth and sixth shift element (B, D, E, F) are torque-conducting, - in the fifth forward gear, the second, third, fourth and fifth shift element (B, C, D, E) are torque-conducting, - in the sixth forward gear, the second, third, fourth and sixth shift elements (B, C, D, F) are torque-conducting, - in the seventh forward gear, the third, fourth, fifth and sixth shift elements C, D, E, F) are torque-conducting, In the eighth forward gear, the first, third, fourth and sixth shift elements (A, C, D, F) are torque-conducting, in the ninth forward gear the first, fourth, fifth and sixth shift elements (A, D, E, F) are torque-conducting, and - in reverse, the first, second, fourth and sixth switching element (A, B, D, F) are torque-conducting. Automatic transmission according to claim 4 and 5, characterized in that ten forward gears and one reverse gear are switchable, wherein - in the first forward gear, the first, second, sixth and seventh switching element (A, B, F, G) are torque-conducting, - in the second forward gear that first, second, third and sixth switching elements (A, B, C, F) are torque-conducting, - in the third forward gear, the first, second, fifth and sixth switching element (A, B, E, F) are torque-conducting, - in the fourth forward gear second, third, fifth and sixth switching element (B, C, E, F) are torque-conducting, - in the fifth forward the second, fourth, fifth and sixth switching element (B, D, E, F) are torque-conducting, - in the sixth forward gear that second, third, fourth and fifth shift elements (B, C, D, E) are torque-conducting, - in the seventh forward gear, the second, third, fourth and sixth shift elements (B, C, D, F) are torque-conducting, - in the eighth forward gear Ang the third, fourth, fifth and sixth switching element (C, D, E, F) are torque-conducting, - in the ninth forward gear, the first, third, fourth and sixth switching element (A, C, D, F) are torque-conducting, - in the tenth Forward, the first, fourth, fifth and sixth switching element (A, D, E, F) are torque-conducting, and - in reverse, the first, second, fourth and sixth switching element (A, B, D, F) are torque-conducting. Automatic transmission according to one of claims 1 to 7, characterized in that all four planetary gear sets (RS1, RS2, RS3, RS4) are designed as negative planetary gear sets. Automatic transmission according to one of claims 1 to 7, characterized in that one of the four planetary gear sets (RS1, RS2, RS3, RS4) is designed as a positive planetary gear, while the other three planetary gear sets are each formed as a minus planetary gear. Automatic transmission according to claim 9, characterized in that the first or the second or the fourth planetary gear set (RS1, RS2, RS4) is designed as a positive planetary gear set. Automatic transmission according to one of claims 1 to 7, characterized in that two of the planetary gear sets are each formed as plus planetary gear set and the other two planetary gear sets each as a minus planetary gear. Automatic transmission according to one of claims 1 to 7, characterized in that the third planetary gear set (RS3) is designed as a minus planetary gear, while the first, second and fourth planetary gear set (RS1, RS2, RS4) are each formed as a positive planetary gear. Automatic transmission according to one of the preceding claims, characterized in that - the first element of each negative planetary gear set and the first element of each plus planetary gear set is formed as a sun gear, - the second element of each negative planetary gear set is formed as a planet carrier, while the second element each Plus planetary gear set is designed as a ring gear, - the third element of each negative planetary gear set is designed as a ring gear, while the third element of each plus planetary gear set is designed as a planet carrier. Automatic transmission according to one of Claims 1 to 13, characterized in that the planetary gear sets (RS1, RS2, RS3, RS4) are arranged coaxially with one another and one behind the other in the axial direction in an order "second, fourth, first, third planetary gearset"("RS2, RS4, RS1, RS3 ") are arranged. Automatic transmission according to claim 14, characterized in that the first switching element (A) spatially in a range axially between the first and fourth planetary gear set (RS1, RS4) is arranged. Automatic transmission according to claim 14 or 15, characterized in that the third switching element (C) spatially seen in a range axially between the second and fourth planetary gear set (RS2, RS4) is arranged. Automatic transmission according to claim 14 or 15, characterized in that the third switching element (C) spatially seen at least partially in a region radially above the second planetary gear set (RS2) is arranged. Automatic transmission according to claim 14 or 15, characterized in that the third switching element (C) spatially on the side of the second planetary gear set (RS2) is arranged facing away from the fourth Planetenradsatze (RS4). Automatic transmission according to claim 14 or 15, characterized in that the third switching element (C) is arranged spatially on that side of the third planetary gear set (RS3) which faces away from the first planetary gear set (RS1). Automatic transmission according to one of claims 14 to 19, characterized in that the fourth switching element (D) spatially in a range axially between the first and third planetary gear set (RS1, RS3) is arranged. Automatic transmission according to one of claims 14 to 19, characterized in that the fourth switching element (D) spatially arranged on that side of the second planetary gear set (RS2), which faces away from the fourth planetary gear set (RS4). Automatic transmission according to one of claims 14 to 21, characterized in that the fifth switching element (E) spatially in a range axially between the second and fourth planetary gear set (RS2, RS4) is arranged axially adjacent to the second planetary gear set (RS2). Automatic transmission according to one of claims 14 to 21, characterized in that the fifth switching element (E) spatially arranged on that side of the second planetary gear set (RS2), which faces away from the fourth planetary gear set (RS4). Automatic transmission according to claim any one of claims 14 to 23, characterized in that the sixth switching element (F) spatially in a range axially between the second and fourth planetary gear set (RS2, RS4) is arranged. Automatic transmission according to claim any one of claims 14 to 23, characterized in that the sixth switching element (F) spatially, at least partially in a region axially above the second planetary gear set (RS2) is arranged. Automatic transmission according to claim any one of claims 14 to 23, characterized in that the sixth switching element (F) spatially arranged on that side of the second planetary gear set (RS2), which is remote from the fourth planetary gear set (RS4). Automatic transmission according to one of claims 14 to 26, characterized in that the seventh switching element (G) spatially in a range axially between the fourth and second planetary gear set (RS4, RS2) is arranged axially adjacent to the second planetary gear set (RS2). Automatic transmission according to one of claims 1 to 13, characterized in that the planetary gear sets are arranged coaxially to each other and in the axial direction one behind the other in an order "first, fourth, second, third planetary gearset"("RS1, RS4, RS2, RS3"). Automatic transmission according to claim 28, characterized in that the first switching element (A) spatially arranged on that side of the first planetary gear set (RS1), which is remote from the fourth planetary gear set (RS4). Automatic transmission according to one of claims 1 to 29, characterized in that the second switching element (B) spatially seen at least partially in a region radially above the first planetary gear set (RS1) is arranged. Automatic transmission according to one of claims 1 to 30, characterized in that the second switching element (B) is designed as a form-locking switching element. Automatic transmission according to one of claims 28 to 31, characterized in that the third switching element (C) spatially in a range axially between the second and third planetary gear set (RS2, RS3) is arranged. Automatic transmission according to one of claims 28 to 32, characterized in that the fourth switching element (D) spatially seen in a range axially between the second and third planetary gear set (RS2, RS3) is disposed axially adjacent to the third planetary gear set (RS3). Automatic transmission according to one of claims 28 to 33, characterized in that the fifth switching element (E) spatially in a range axially between the second and third planetary gear set (RS2, RS3) is arranged axially adjacent to the second planetary gear set (RS2). Automatic transmission according to one of claims 28 to 33, characterized in that the fifth switching element (E) spatially arranged on that side of the second planetary gear set (RS2), which faces away from the third planetary gear set (RS3). Automatic transmission according to claim any one of claims 28 to 35, characterized in that the sixth switching element (F) spatially in a range axially between the second and third planetary gear set (RS2, RS3) is arranged. Automatic transmission according to one of claims 28 to 36, characterized in that the seventh switching element (G) spatially in a range axially between the second and fourth planetary gear set (RS2, RS4) is arranged. Automatic transmission according to one of claims 28 to 36, characterized in that the seventh switching element (G) spatially in a range axially between the first and fourth planetary gear set (RS1, RS4) is arranged, axially adjacent to the fourth planetary gear set (RS4). Automatic transmission according to one of claims 28 to 36, characterized in that the seventh switching element (G) is spatially arranged in a region axially between the second and third planetary gear set (RS2, RS3), axially adjacent to the second planetary gear set (RS2). Automatic transmission according to one of claims 1 to 14 or 28, characterized in that the third and sixth switching element (C, F) are arranged spatially seen immediately adjacent to each other. Automatic transmission according to one of claims 1 to 14 or 28, characterized in that the fifth and sixth switching element (E, F) are arranged spatially seen immediately adjacent to each other.

Images