DE102014207453A1 - 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 seven shift elements (A to G) for switching multiple 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 eighth shaft (8) can be connected to the sixth shaft (6) via the fourth shifting element (D) and to the first shaft (1) via the seventh shifting element (G). 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 further develop a multi-speed transmission of the type mentioned above with a total of four planetary gear sets with respect to the number switchable forward gears without group circuit, without having to significantly modify the underlying 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 nine rotatable shafts, four individual planetary gear sets and seven switching elements whose selective engagement different ratios between the drive shaft and output shaft effect switching multiple forward gears and at least one reverse gear. 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 RS1 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 arranged in the power flow between the third shaft and the housing (the third shaft is thus over the first Switchable element fixable; 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 shift element is arranged in the power flow between the sixth and the eighth shaft (the sixth shaft is thus connectable via the fourth shift element with the eighth shaft, the fourth shift element is thus both with the second element of the first planetary gear set and with the second element of second planetary gear set and the third element of the third planetary gear set constantly and directly connected). 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 shift element is arranged in the power flow between the fifth and the ninth shaft (the fifth shaft can thus be connected to the ninth shaft via the sixth shift element), the sixth shift element thus being connected both to the third element of the second planetary gear set and to the first element of the second planetary gear set third planetary gear set constantly and directly connected). Thus, the fifth shaft by simultaneous closing of the third and sixth switching element with the first shaft (drive shaft) can be connected. The seventh shift element is arranged in the power flow between the first shaft (drive shaft and the eighth shaft) (ie, the first shaft or the drive shaft can be connected to the eighth shaft via the seventh shift element, ie, the seventh shift element is connected both to the second element of the second planetary gearset and constantly and directly connected to the second element of the fourth planetary gear set).

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, which allows the switching of at least eleven forward gears and at least one reverse gear. Advantageously, this requires the separation of in the DE 10 2010 041 575 B3 provided between the third element of the second planetary gear set and the first element of the third planetary gear coupling shaft provided sixth switching element only comparatively little additional space. It is even possible to accommodate the additional sixth switching element by clever nesting of the switching elements in the gear housing space neutral. 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 generic automatic transmission with fewer switching elements.

Preferably, in the automatic transmission according to the invention four shift elements are 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 eleven forward gears and one reverse gear, such a transmission may have the following shift logic or gear logic: In the first forward gear, the first, second, sixth and seventh shift element are closed or transmit torque. In the second forward gear, the first, second, third and sixth switching element are closed or torque transmitting. In the third forward gear, the first, second, fifth and sixth switching element are closed or torque transmitting. In the fourth forward gear, the second, third, fifth and sixth switching element are closed or torque transmitting. In the fifth forward gear, the second, fourth, fifth and sixth shift element are closed or torque-transmitting. In the sixth forward gear, the second, third, fourth and fifth switching element are closed or torque transmitting. In the seventh forward gear, the second, third, fourth and sixth switching element are closed or torque transmitting. In the eighth forward gear, the third, fourth, fifth and sixth shift element are closed or transmit torque. In the ninth forward gear, the first, third, fourth and sixth switching element are closed or torque transmitting. In the tenth forward gear, the first, third, fourth and fifth switching element are closed or torque transmitting. In the eleventh 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.

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;
• • 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;
• • To arrange the seventh switching element in a region axially between the fourth and second planetary gear 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 vierten Planetenradsatz anzuordnen, oder alternativ in einem Bereich axial zwischen dem ersten 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;
• • 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;
• • Arrange the fourth switching element in a range axially between the second and fourth planetary gear set, or alternatively in a range axially between the first 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;
• • to arrange the seventh shift element in an area axially between the fourth and second planetary gear set axially adjacent to the fourth planetary gear set, or alternatively in an area axially between the first and fourth planetary gear set axially adjacent to the fourth planetary gear set, or alternatively in a range axially 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 arranged immediately adjacent to each other, and / or that the fifth and sixth switching elements are spatially seen immediately adjacent to each other, and / or that the fourth and Seventh switching element 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 be configured in a manner known per se, for example as a hydrodynamic converter, as a so-called dry starting clutch, as a so-called wet starting clutch, as a magnetic powder clutch or as a centrifugal clutch. As an alternative to the arrangement of such a starting element in the power flow direction between the drive motor and gearbox, 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, such as a hydraulic or electric retarder or the like, be arranged, which is particularly important for use in commercial vehicles of particular importance. 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 an 11-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 second embodiment of an 11-speed automatic transmission according to the invention, derived from the transmission according to 1 ;

8th a schematic representation of a first alternative to the transmission according to 7 ;

9 a schematic representation of a second alternative to the transmission according to 7 ;

10 a schematic representation of a third embodiment of an 11-speed automatic transmission according to the invention, derived from the transmission according to 1 ;

11 a schematic representation of a first alternative to the transmission according to 10 ; and

12 a schematic representation of a second alternative to the transmission according to 10 ,

In 1 the Radsatzschema a first embodiment of an 11-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 seven switching elements A, B, C, D, E, F, G, 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 designed in the illustrated embodiment as frictionally switchable disk brakes, in another Design 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, F and G are formed 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 seven total switching elements A to G, a selective switching of eleven forward gears and one reverse gear can be realized, 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 seven switching elements A to G 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 sixth shaft 6 and the eighth wave 8th 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. The seventh switching element G is in the power flow between the first shaft 1 (Drive shaft AN) and the eighth shaft 8th arranged.

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 already mentioned writings DE 10 2005 002 337 A1 and DE 10 2007 055 808 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 axially adjacent to the (arranged on the drive side of the gear housing) arranged 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 three clutches C, E and F are spatially located axially between the second planetary gearset RS2 (located on the side of the fourth planetary gearset RS4 facing away from the first planetary gearset RS1) and the third planetary gearset (disposed on the output side of the transmission housing) RS3 arranged. The three clutches C, E and F are arranged axially next to each other on at least similar and large diameter. In this case, the clutch C is axially adjacent to the third planetary gearset RS3, while the clutch E is 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, for example, the outer disk carrier of the clutch E and the inner disk carrier of the clutch F is formed, wherein 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 sixth wave 6 , which indeed forms the operative connection between the planet carrier ST1 of the first planetary gear set RS1 and the ring gear HO3 of the third planetary gearset RS3, completely encloses in its axial course, inter alia, the second planetary gear set RS2 and the three clutches E, F and C, so that the three clutches E , F and C are disposed within a cylinder space passing through the sixth shaft 6 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 ,

How out 1 Furthermore, as can be seen, the clutch D is spatially arranged in a region axially between the second planetary gearset RS2 and the fourth planetary gearset RS4, in this case directly axially adjacent to the second planetary gearset RS2. In this case forms a section of the sixth wave 6 a cylinder space within which the clutch D is arranged. With pressure and lubricant can be supplied to the clutch D, for example, coming from the drive shaft AN forth on the rotatably mounted on the drive shaft AN seventh shaft 7 and the seventh wave 7 rotatably mounted planet carrier ST2 of the second planetary gearset RS2.

How out 1 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, while directly axially adjacent to the fourth planetary gear set RS4. This allows the arrangement of the disk set 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 sixth wave 6 , which forms the operative connection between the planet carrier ST1 of the (arranged on the drive side of the transmission housing) first planetary gear set RS1 and the ring gear HO3 of the arranged (on the output side of the transmission housing) third planetary gearset RS3, encloses in its axial course, the eighth shaft 8th and thus also the clutch G and the fourth planetary RS4 completely. Can be supplied with pressure and lubricant, the clutch G in a structurally simple manner Leakageverlustarm of the drive shaft AN forth on the constantly connected to the drive shaft AN planet carrier ST4 of the fourth planetary gearset RS4.

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 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.

As already indicated, the in 1 illustrated spatial arrangement of the switching elements to be understood as exemplary. For example, as an alternative to 1 the clutch D spatially seen in a range axially between the first planetary gearset RS1 and the fourth planetary gearset RS4 be arranged adjacent to the clutch G. This allows in manufacturing and assembly technology favorable way a common for these two clutches D and G plate carrier, wherein the disk set the clutch D can be arranged axially adjacent to the disk set of the clutch G (on the side of the disk set of the clutch G facing the first planetary gearset RS1), but alternatively can also be arranged radially over the disk set of the clutch G, so as to save gearbox length.

alternative to 1 the clutch G spatially seen, for example, in a range axially between the second planetary gearset RS2 and the fourth planetary gearset RS4 be arranged, the clutch G then arranged depending on the arrangement of the clutches D and E adjacent to the clutch D and / or adjacent to the clutch E. can be.

In particular, when the clutch G is designed in the form of a dog clutch, it offers itself as another alternative to 1 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, ie near the clutch F, which presupposes, however, that the clutch E is either in the power flow between the ring gear HO2 and the planet carrier ST2 of the second planetary gear set RS2 or spatially arranged axially between the second planetary gear set RS2 and the fourth planetary gear set RS4.

In 2 is an exemplary circuit diagram of the 11-speed automatic transmission according to the invention according to 1 shown. In each gear, four of the shift elements are closed, which - has a very positive effect on the efficiency of the transmission - due to the minimization of the drag friction elements on open friction shift occurring occurring. 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 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 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.

In this case, the first planetary gear set RS1 is arranged in the axial direction immediately adjacent to the (connected to the output shaft AB) third planetary gearset RS3, such that the two planetary gear sets RS1, RS3 only through a portion leading to the clutch D of the sixth shaft 6 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 form the four multi-plate clutches C, F, E and D a production and assembly technically favorable assembly, which is spatially arranged on that side of the second planetary gearset RS2, which faces away from the fourth planetary gearset RS4. By way of example, all four plate packs are in axial Direction seen in the same plane - ie radially superimposed - arranged. Spatially, the disk set of the clutch F is located radially below the disk set of the clutch C, the disk set of the clutch E radially below the disk set of the clutch F and the disk set of the clutch D radially below the disk set of the clutch E. For the two clutches C, F a common plate carrier is provided, which receives the inner plates of the disk set of the (radially outermost) clutch C and the outer disks of the disk set of the clutch F and a portion of the ninth shaft 9 forms, that is constantly connected to the sun gear SO3 of the third planetary gear set RS3. For the two clutches F, E, a common plate carrier is also provided, which now receives the inner disks of the disk set of the clutch F and the outer disk of the disk set of the clutch E and a portion of the fifth shaft 5 forms, that is constantly connected to the ring gear HO2 of the second planetary gear set RS2. Also for the two clutches E, D a common plate carrier is provided, which now receives the inner disks of the disk set of the clutch E and the outer disks of the disk set of the (radially innermost) clutch D and a portion of the eighth wave 8th forms, that is constantly connected to the planet carrier ST2 of the second planetary gear set RS2.

How out 3 Furthermore, it can be seen that is in the power flow between the first shaft 1 (Drive shaft AN) and the eighth shaft 8th (Planet carrier ST2) arranged clutch G spatially in the range axially between the second planetary gearset RS2 and the fourth planetary gearset 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 force flow, as previously described.

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 G, the second planetary gearset RS2 and the clutch assembly C / F / E / D completely. Then the shaft passes through 1 seen in the axial direction, the clutch assembly C / F / E / D, the second planetary gear set RS2, the clutch G, the fourth planetary RS4, the brake A, the first planetary gear set RS1 (together with the brake B) and the third planetary gear set RS3 in this Order centric complete, with 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. The ninth wave 9 in turn runs centrally within the connected to the inner disk carrier of the clutch D gate of the sixth shaft 6 , this section of the sixth wave 6 in turn, from both the seventh wave 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) is enclosed radially.

At this point I would like to point out the exemplary character of the in 3 indicated spatial arrangement of the switching elements. If necessary, the skilled person will also provide another suitable arrangement of the switching elements, which is based for example on an outer contour of the gear housing GG, which allows the installation of the automatic transmission in a predetermined engine compartment of the motor vehicle.

• • Ausbildung der Bremse B als formschlüssiges Schaltelement;
• • Verlegung der Kupplung C auf einen kleineren Durchmesser axial neben die Kupplung F, auf diejenige Seite der Kupplung F, die den Planetenradsätzen abgewandt ist;
• • Verlegung der Kupplung C auf diejenige Seite des ersten Planetenradsatzes RS1, die dem vierten Planetenradsatz abgewandt ist;
• • Verlegung der Kupplung D in den Bereich axial zwischen dem vierten Planetenradsatz RS4 und dem dritten Planetenradsatz RS3, vorzugsweise auf einen größeren Durchmesser;
• • Verlegung der Kupplung F auf einen kleineren Durchmesser axial neben die Kupplung E, auf diejenige Seite der Kupplung E, die den Planetenradsätzen abgewandt ist.

Examples of meaningful modifications are

• • Training the brake B as a form-locking switching element;
• • Laying the clutch C to a smaller diameter axially adjacent to the clutch F, on that side of the clutch F, which faces away from the planetary gear sets;
• • Laying the clutch C on that side of the first planetary gear set RS1, which faces away from the fourth planetary gear set;
• • Laying the clutch D in the area axially between the fourth planetary gear set RS4 and the third planetary gear set RS3, preferably to a larger diameter;
• • Laying the clutch F to a smaller diameter axially adjacent the clutch E, on that side of the clutch E, which faces away from the planetary gear sets.

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 switch eleven forward gears and one reverse gear.

As is well known, in a minus planetary gear set, each of its planet gears meshes with both the sun gear and the ring gear, while each of its inner planet gears is meshed with one of its outer planet gears and the sun gear with each of its outer planetary gears and one of its outer planet gears inner 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 two 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 performed 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 seven switching elements A to G.

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 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 6 across from 1 unchanged, as well as the spatial arrangement of the seven switching elements A to G.

To the kinematics of the wheelset according to 1 to maintain is in 6 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 this clutch D with the sixth shaft 6 or with the second element (planet carrier ST1) of the first planetary gearset RS1 and the third element (HO3) of the third planetary gearset 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 two 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. 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.

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 embodiment of the 1 and 5 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.

7 shows a schematic representation of a second embodiment of a 11-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 7 across from 1 unchanged, as well as the spatial arrangement of all seven switching elements A to G.

In the 7 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 8th a schematic representation of a first alternative to the in 7 illustrated transmission scheme. In contrast to the transmission scheme according to 7 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 8th (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 8th across from 1 and 7 unchanged, as well as the spatial arrangement of the seven switching elements A to G. 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.

9 shows a schematic representation of a second alternative to the in 7 illustrated transmission scheme. In contrast to the transmission scheme according to 7 is in the transmission scheme according to 9 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 9 across from 1 and 7 unchanged, as well as the spatial arrangement of the seven switching elements A to G. 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.

10 shows a schematic representation of a third embodiment of an 11-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, F and G. In contrast to 1 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 axially between the planetary gearset RS2 and clutch C radially below the clutch F.

In the 10 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 11 a schematic representation of a first alternative to the in 10 illustrated transmission scheme. In contrast to the transmission scheme according to 10 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 11 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 11 across from 10 unchanged, as well as the spatial arrangement of all seven switching elements A to G. The conditional by the interchange of the connection of the planet carrier and ring gear of the positive planetary gear set with respect to the negative planetary gear set have already been based on 5 explained and therefore need no repetition at this point.

12 shows a schematic representation of a second alternative to the in 10 illustrated transmission scheme. In contrast to the transmission scheme according to 10 is in the transmission scheme according to 12 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 12 across from 10 unchanged, as well as the spatial arrangement of all seven switching elements A to G. The conditional by the interchange of the connection of the planet carrier and ring gear of the positive planetary gear set with respect to the negative planetary gear set have already been based on 6 explained and therefore need no repetition at this point.

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, 0046, 0046]
• DE 102010041575 B3 [0004, 0014]
• DE 102009001253 B3 [0005]
• DE 102007055808 A1 [0046]

Claims (41)

Automatic transmission, in particular for a motor vehicle, with a housing (GG), with nine 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 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) designed as a drive shaft (AN) first shaft ( 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, 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 ), a fourth switching element (D) in the force flow between the sixth shaft ( 6 ) and the eighth wave ( 8th ), a sixth switching element (F) in the force flow between the fifth shaft (FIG. 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, and • 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 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 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 claim 4, characterized in that eleven forward gears and one reverse gear are switchable, wherein - in the first forward gear, the first, second, sixth and seventh shift element (A, B, F, G) are torque-conducting, - in the second forward gear, the first, second, third and sixth shift elements (A, B, C, F) are torque-conducting, - in the third forward gear, the first, second, fifth and sixth shift element (A, B, E, F) are torque-conducting, - in the fourth forward gear, the 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, the second, Third, fourth and fifth switching element (B, C, D, E) are torque-conducting, - in the seventh forward gear, the second, third, fourth and sixth switching element (B, C, D, F) are torque-conducting, - in the eighth forward gear that 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 gear the first, third, fourth and fifth shift elements (A, C, D, E) are torque-conducting, in the eleventh 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 one of claims 1 to 5, 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 5, characterized in that one of the four planetary gear sets (RS1, RS2, RS3, RS4) is designed as a plus planetary gear, while the other three planetary gear sets are each formed as a minus planetary gear. Automatic transmission according to claim 7, 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 5, characterized in that two of the planetary gear sets are each formed as plus planetary gear and the other two planetary gear sets each as a minus planetary gear set. Automatic transmission according to one of claims 1 to 5, 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 plus 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 11, characterized in that the planetary gear sets (RS1, RS2, RS3, RS4) coaxial with each other and in the axial direction one behind the other in an order "second, fourth, first, third planetary gear set"("RS2, RS4, RS1, RS3 ") are arranged. Automatic transmission according to claim 12, 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 12 or 13, 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 12 or 13, 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 12 or 13, characterized in that the third switching element (C) is spatially arranged on that side of the second planetary gear set (RS2), which faces away from the fourth Planetenradsatze (RS4). Automatic transmission according to claim 12 or 13, characterized in that the third switching element (C) spatially arranged on that side of the third planetary gear set (RS3), which faces away from the first Planetenradsatze (RS1). Automatic transmission according to one of claims 12 to 17, characterized in that the fourth switching element (D) is spatially arranged in a range axially between the first and third planetary gear set (RS1, RS3). Automatic transmission according to one of claims 12 to 17, characterized in that the fourth switching element (D) 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 12 to 19, 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 12 to 19, 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 one of claims 12 to 21, characterized in that the sixth shifting element (F) is seen in space an area axially between the second and fourth planetary gear set (RS2, RS4) is arranged. Automatic transmission according to claim any one of claims 12 to 21, characterized in that the sixth switching element (F) spatially seen 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 12 to 21, characterized in that the sixth switching element (F) 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 12 to 24, 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 11, 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 gear set"("RS1, RS4, RS2, RS3"). Automatic transmission according to claim 26, characterized in that the first switching element (A) is arranged spatially 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 27, 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 28, characterized in that the second switching element (B) is designed as a form-locking switching element. Automatic transmission according to one of claims 26 to 29, characterized in that the third switching element (C) spatially seen in a range axially between the second and third planetary gear set (RS2, RS3) is arranged. Automatic transmission according to one of claims 26 to 30, characterized in that the fourth switching element (D) spatially seen in a range axially between the second and fourth planetary gear set (RS2, RS4) is arranged, axially adjacent to the third planetary gear set (RS3). Automatic transmission according to one of claims 26 to 30, characterized in that the fourth switching element (D) is arranged spatially in a range axially between the first and fourth planetary gear set (RS1, RS4), axially adjacent to the third planetary gear set (RS3). Automatic transmission according to one of claims 26 to 32, 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 26 to 32, 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 26 to 34, 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 26 to 35, 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 fourth planetary gear set (RS4). Automatic transmission according to one of claims 26 to 35, 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 26 to 35, 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 12 or 26, characterized in that the third and sixth switching element (C, F) are spatially arranged immediately adjacent to each other. Automatic transmission according to one of claims 1 to 12 or 26, characterized in that the fifth and sixth switching element (E, F) are arranged spatially seen immediately adjacent to each other. Automatic transmission according to one of claims 1 to 12 or 26, characterized in that the fourth and seventh switching element (D, G) are arranged spatially seen immediately adjacent to each other.

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