DE102014205052A1 - Multi-stage automatic transmission - Google Patents

Abstract

The invention relates to a multi-stage automatic transmission with a drive shaft (AN), an output shaft (AB), four planetary gear sets (RS1 to RS4) and a plurality of switching elements (A to F) whose selective closing different ratios between drive shaft (AN) and output shaft (AB ) cause switching of at least nine forward gears. The drive shaft (AN) is constantly connected to the fourth planetary gear set (RS4). The output shaft (AB) is constantly connected to the third planetary gear set (RS3). There are only two coupling shafts (5, 6) are provided over the individual of the planetary gear sets (RS1 to RS4) with another of the planetary gear sets (RS1 to RS4) are constantly directly connected. The fourth planetary gear set (RS4) connected to the drive shaft (AN) is constantly directly connected to at least five switching elements (A, B, C, E, F).

Description

The present invention relates to an 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 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.

From the not pre-published DE 10 2013 218 941.9 the applicant is another evolution of the from the DE 10 2005 002 337 A1 known 8-speed automatic transmission, in which is arranged by adding a sixth switching element in the power flow between the sun gear of the second planetary gear set and the ring gear of the fourth planetary gear set. The seventh wave of the 8-shaft transmission of DE 10 2005 002 337 A1 So now is separated, causing the second planetary now only by simultaneous closing of two of the now six switching elements - specifically by closing the fifth and additional sixth switching element - can block. In the locked state, the speeds of the sun gear, planet carrier and ring gear of this planetary are known to be identical. The additional sixth switching element allows group-circuit-free switching of now a total of nine forward gears, wherein in each gear now four of the switching elements are closed, so that still only two switching elements are not closed in each gear.

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 drive shaft, an output shaft, four individual planetary gear sets and at least six switching elements whose selective intervention different transmission ratios between the drive shaft and output shaft effect for switching at least nine forward gears. The drive shaft is constantly connected to the fourth planetary gear set while the output shaft is constantly connected to the third planetary gear set. According to the invention, only two coupling shafts are provided, via which individual planetary gear sets are constantly directly connected to another of the planetary gear sets. According to the fourth planetary gear set connected to the drive shaft is constantly directly connected to at least five switching elements

It may be provided that the first coupling shaft constantly connects the second planetary gear set to the third planetary gear set, while the second coupling shaft constantly connects the third planetary gear set to the first planetary gear set.

 It can be provided that the first planetary gear is directly connected to a maximum of two switching elements, that the second planetary gear is directly connected to at least four switching elements, and that the third planetary gear set connected to the output shaft is directly connected to two switching elements.

 It can also be provided that the drive shaft is constantly connected directly to at least one switching element, while the output shaft is constantly connected directly with a maximum of one switching element.

In one embodiment, it is proposed that exactly six switching elements are provided. In this case, the second planetary is constantly connected directly with exactly four switching elements, the third planetary continuously connected with exactly two switching elements, the fourth planetary gear constantly connected with exactly five switching elements and the drive shaft constantly connected to exactly one switching element.

In an alternative embodiment, it is proposed that exactly seven switching elements are provided. In this case, the second planetary gear set is constantly directly connected to exactly five switching elements, the third planetary continuously connected with exactly two switching elements, the fourth planetary gear constantly connected with exactly six switching elements and the drive shaft constantly connected with exactly two switching elements.

In one embodiment, it is proposed that the first planetary gear set is constantly directly connected to exactly one switching element, and that the output shaft is constantly directly connected to exactly one other switching element.

In an alternative embodiment, it is proposed that the first planetary gear is constantly connected directly to exactly two switching elements, while the output shaft is connected directly to any switching element.

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.

Preferably, each of the four planetary gear sets each has three elements, namely a sun gear, a planet carrier and a ring gear. The automatic transmission can have a total of nine rotatable shafts. Preferably, then forms the second element of the fourth planetary gear set as the drive shaft first shaft, the second element of the third planetary gear designed as the output shaft second shaft, the first element of the fourth planetary gear, the third shaft, the first element of the first planetary gear, the fourth wave third element of the fourth planetary gear set, the seventh shaft, the second element of the second planetary gear set, the eighth shaft, the first element of the second planetary gear set, the ninth wave. Preferably then connects the fifth shaft (as the first coupling shaft) the third element of the second planetary gear set with the first element of the third planetary gear set, while the sixth shaft (as a second coupling shaft) connects the second element of the first planetary gear set constantly with the third element of the third planetary gear set , Preferably, the third element of the first planetary gear set is constantly fixed to a housing of the automatic transmission.

With regard to the coupling of the switching elements to the individual shafts can be provided that the first switching element is arranged in the power flow between the third shaft and the housing, that the second switching element is arranged in the power flow between the third and fourth shaft, that the third switching element in the power flow is arranged between the first and fifth wave, that the fourth switching element is arranged either in the power flow between the second and eighth shaft or in the power flow between the sixth and eighth shaft, that the fifth switching element is arranged in the power flow between the seventh and eighth shaft, and that the sixth switching element in the power flow between the seventh and ninth wave is arranged. If a seventh switching element is provided, then this seventh switching element can be arranged in the force flow between the first and eighth shaft.

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

Preferably, in the transmission according to the invention in each gear four of the switching elements are closed. If six switching elements are provided, only two switching elements are not closed in each gear. If seven switching elements are provided, three switching elements are not closed in each gear. In a change from a gear in the subsequent higher or lower gear only one of the previously closed switching elements is opened and a previously open switching element is closed, so that the sequential upshift and downshift by one gear 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 reverse, the first, second, fourth and sixth shift element are closed or torque transmitting. 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, the second, third, fifth and sixth switching element are 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 a first variant, in the ninth forward gear, the first, fourth, fifth and sixth shift element are closed or transmit torque. In a second variant, the ninth forward gear, the first, third, fourth and fifth shifting element closed or torque transmitting, in which case a tenth forward gear is switchable, in which the first, fourth, fifth and sixth shifting element is closed or torque transmitting.

If an additional seventh switching element is present, an additional forward gear below the first gear of the transmission design with only six switching elements can be realized compared to the transmission design with only six switching elements, ie an additional forward gear with a ratio greater than that translation of the first gear of the transmission 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 required for the transmission according to the invention with six switching elements.

Preferably, the fourth switching element is directly connected to the fifth switching element. Preferably, the fifth switching element is also directly connected to the sixth switching element.

In a preferred embodiment of the second planetary gear set by simultaneous closing of the fifth and sixth switching element is blockable, such that the rotational speeds of the three elements (sun, planet, ring gear) of the second planetary gear set are identical in the locked state of the second planetary gear set.

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") with inner and outer planetary gears rotatably mounted thereon, wherein each of the inner planetary gears meshes with an outer planetary gear and with the sun gear of the positive planetary gear set, while each of the outer planetary gears meshes with an inner planetary gear and with the ring gear of the plus planetary gearset. 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 ,

As a spatial arrangement for the fifth shift element within the transmission housing, the range between the fourth and second planetary gear set axially, alternatively the range axially between the second and third planetary gear set proposed. Both arrangements are possible both for the planetary gearset sequence "first, fourth, second, third planetary gear set" and for the planetary gear set "second, fourth, first, third planetary gear set" and favorable in terms of the pressure and lubricant supply.

As a spatial arrangement for the sixth shift element within the transmission housing, the region between the fourth and second planetary gear sets, alternatively the region axially between the second and third planetary gear sets, or alternatively the region centrally within the sun gear of the second planetary gear set, is preferably instantaneous in all three cases adjacent to the second planetary gear set. The third proposed arrangement is very short construction for the transmission. All three arrangements are both for the planetary gear set order "first, fourth, second, third planetary gear" and for the planetary gear set "second, fourth, first, third planetary gear set" possible and favorable in terms of pressure and lubricant supply.

In conjunction with the planetary gear set order "second, fourth, first, third planetary gearset" is an advantageous spatial arrangement for the seventh switching element, the area axially between the fourth and second planetary gear, axially adjacent to the second planetary gear.

For both planetary gear set sequences "first, fourth, second, third planetary" and "second, fourth, first, third planetary" is also possible that seventh switching element spatially in a range axially between the fourth and second planetary gear to arrange, then preferably axially adjacent to the fourth planetary gear set. Alternatively, the seventh switching element spatially seen in the area between the first and fourth planetary be arranged axially, then preferably axially adjacent to the fourth planetary gear set; alternatively also in the area axially between the second and third planetary gear set, then preferably axially adjacent to the second planetary gear set.

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 lower Towing losses, since in each gear always four 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, 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 an 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 an automatic transmission according to the invention;

9 an exemplary circuit diagram for the transmission according to 8th ;

10 an alternative component arrangement for the transmission according to 8th ;

11 a table with variants of the transmission according to 8th ;

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

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

14 a schematic representation of a third embodiment of an automatic transmission according to the invention;

15 an exemplary circuit diagram for the transmission according to 14 ;

16 a table with variants of the transmission according to 14 ;

17 a schematic representation of a first alternative to the transmission according to 14 ;

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

19 a schematic representation of a third alternative to the transmission according to 14 ;

20 a schematic representation of a fourth embodiment of an automatic transmission according to the invention;

21 an exemplary circuit diagram for the transmission according to 20 ;

22 a table with variants of the transmission according to 20 ;

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

24 a schematic representation of a second alternative to the transmission according to 20 ,

In 1 is shown as the first embodiment of an automatic transmission according to the invention the Radsatzschema a 9-speed automatic transmission. The transmission comprises a drive shaft AN, an output shaft AB, four planetary gear sets RS1, RS2, RS3, RS4 and six shift 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.

Including drive shaft AN and output shaft AB, the automatic transmission according to the invention has a total of nine rotatable shafts with 1 to 9 are designated.

The switching element A is designed as a brake, which is executed in the illustrated embodiment as frictionally switchable multi-disc brake, 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 switching elements B, 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 ring gear HO1 of the first planetary gearset RS1 is fixedly connected to the transmission housing GG. The planet carrier ST4 of the fourth planetary gear set RS4 and the drive shaft AN are rotationally fixed or rotationally 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 SO4 of the fourth planetary gearset RS4 forms with 3 designated third shaft of the automatic transmission. The sun gear SO1 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 and the sun gear SO3 of the third planetary gearset RS3 are rotationally fixed or rotationally connected to each other and form the with 5 designated fifth wave - also called "first coupling shaft" - the automatic transmission. The planet carrier ST1 of the first planetary gear set RS1 and the ring gear HO3 of the third planetary gearset RS3 are rotationally fixed or rotationally connected to each other and form the with 6 designated sixth wave - also called "second coupling shaft" - the automatic transmission. The ring gear HO4 of the fourth planetary gear set RS4 forms 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 SO2 of the second planetary gear set RS2 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 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 third shaft 3 and the fourth wave 4 arranged. The third switching element C is in the power flow between the fifth shaft 5 and the first wave 1 arranged. The fourth switching element D is in the power flow between the eighth wave 8th and the second wave 2 is arranged. The fifth switching element E is in the power flow between the seventh shaft 7 and the eighth wave 8th arranged. Finally, the sixth switching element F is in the power flow between the seventh shaft 7 and the ninth wave 9 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 and the clutch B are in the illustrated embodiment spatially seen axially adjacent to the drive-near 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. Seen spatially, the brake A adjacent clutch B is gearbox-length saving arranged in a region radially below the brake A. Can be supplied with pressure and lubricant, the clutch B from the drive shaft AN forth on the radially surrounding the drive shaft third shaft 3 ,

How out 1 Furthermore, as can be seen, the two clutches C and D are spatially arranged in a region axially between the second planetary gearset RS2 adjacent to the fourth planetary gearset RS4 and the third planetary gearset RS3 close to the output. The two clutches C and D are arranged substantially axially next to each other on at least similar and large diameter, wherein the clutch D is disposed immediately adjacent to the third planetary gearset RS3, while the clutch C is disposed immediately adjacent to the second planetary gearset RS2. The shaft engages around 8th , which forms the operative connection between the planet carrier ST2 of the second planetary gear set RS2 and the clutch D, the planetary gear set RS2 and the clutch C in the axial direction completely, whereby parts of the shaft 5 and the one with the wave 5 connected outer disc carrier of the clutch C is disposed within a cylinder space, through the shaft 8th is formed. The clutch C in turn is disposed within a cylinder space passing through the shaft 5 which forms the operative connection between the ring gear HO2 of the second planetary gearset RS2 and the sun gear SO3 of the third planetary gearset RS3, forming a portion of the shaft 5 simultaneously forms the outer disk carrier of the clutch C.

As already indicated, the in 1 shown spatial arrangement of the two clutches C and D to be understood as exemplary. Thus, depending on the installation space available for the installation of the gearbox, it may be expedient to arrange the disk set of the clutch D spatially approximately radially above the disk set of the clutch C, whereby both clutches C and D axially to the third planetary gear set RS3 (on the second planetary gear set RS2 side facing) adjacent.

How out 1 Furthermore, as can be seen, the two clutches E and F are spatially in an area axially between the fourth Planetary gear set RS4 and the second planetary gear set RS2 arranged axially adjacent to each other preferably equal diameter with a common outer disk carrier, which is a portion of the shaft 7 forms. In this case, the clutch E is arranged closer to the second planetary gear set RS2 than the clutch F, which in turn directly adjoins the fourth planetary gear set RS4.

Also for the spatial arrangement of the two clutches E and F at this point on the exemplary character of in 1 selected representation pointed. Of course, the expert can also place the two clutch E, F spatially elsewhere, especially when the clutch F, which is open only in the fifth forward gear and closed in all other gears, is designed in the form of a small-build dog clutch. Running as a dog clutch, the clutch F spatially seen, for example, be arranged in the area centrally within the sun gear SO2 of the second planetary gearset RS2. Running as a dog clutch or as a multi-plate clutch, the clutch F seen in the axial direction may be arranged, for example, in the region radially below the disk set of the clutch E.

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 five clutches B, F, E, C, D. In its axial course, the drive shaft AN passes through the third shaft 3 and the ninth wave 9 and a portion of the fifth wave 5 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 first planetary gearset RS1 and the ring gear HO3 of the third planetary gearset RS3, in its axial course the fourth and second planetary gearset RS4, RS2 and the four clutches F, E, C, D completely.

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, exemplary values for the respective gear ratios i of the individual gear stages and the incremental stages phi to be determined from them can also be taken from the circuit diagram. The specified ratios i result from the (typical) stationary gear ratios of the four planetary gear sets RS1, RS4, RS2, RS3 of minus 2.0; minus 1.70; minus 1.61 and minus 4.30. Furthermore, it can be seen from the circuit diagram that with sequential shift operation - that is to say when shifting up or down by one gear in each case - so-called group shifting is avoided 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.

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 , 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 gear set RS3, while the first planetary gearset RS1 seen in the axial direction by the planetary gearset RS1 adjacent to the clutch B and the clutch to the B adjacent inner disc carrier of the brake A is separated from the (connected to the drive shaft AN) fourth planetary gearset RS4.

In 3 is the clutch C, which is in the power flow between shaft 1 (Drive shaft AN) and shaft 5 (Coupling shaft between ring gear HO2 and sun SO3), spatially arranged at least partially in a region radially above the second planetary gear set RS2. Alternatively, the clutch C can be spatially arranged on a smaller diameter in a region axially adjacent to the second planetary gear set RS2 on its side facing away from the third planetary gearset RS3 or in a region axially adjacent to the third planetary gear set RS3 on its side facing away from the second planetary gear set RS2.

In 3 is the clutch D, which is in the power flow between shaft 2 (Output shaft AB) and shaft 8th (Planet ST2) is located, spatially arranged axially adjacent to the second planetary gearset RS2 on the fourth planetary gearset RS4 side facing away. Alternatively, the clutch D may for example also be arranged in a region axially between the first planetary gearset RS1 and the third planetary gearset RS3.

In 3 are the clutches E and F spatially in a range axially between the (connected to the drive shaft AN) fourth Planetary gear set RS4 and the second planetary gear set RS2 arranged and have a common plate carrier. An example is the clutch F, which is in the power flow between the shaft 7 (Ring gear HO4) and shaft 9 (Sun gear SO2), spatially seen in a region radially below the clutch E, resulting in the power flow between shaft 7 (Ring gear HO4) and shaft 8th (Planet carrier ST2) is located. Alternatively, the clutches E and F may for example also be arranged axially next to each other, wherein the clutch E is then arranged axially adjacent to the second planetary gear set RS2 and the clutch F axially adjacent to the fourth planetary gear set RS4.

In the 3 shown arrangement variant is well suited for an automatic transmission due to its short axial transmission length, in which drive shaft AN and output shaft AB are not arranged coaxially to each other, which is the case for example in a so-called front-transverse installation of the transmission in the vehicle.

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 as the first embodiment of a transmission according to the invention shown 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 the six switching elements A to F.

To the kinematics of the wheelset according to 1 to maintain is in 5 provided that unchanged the sun gear SO1 as the first element of the first planetary gear set RS1 (via the clutch B with the third wave 3 connectable) fourth wave 4 of the automatic transmission, but now that the ring gear HO1 as the second element of the first planetary gear set RS1 on the (as a second coupling shaft acting) sixth wave 6 the automatic transmission is constantly connected to the ring gear HO3 of the third planetary gearset RS3, and that now the planet carrier ST1 is connected as a third element of the first planetary gearset RS1 fixed to the transmission housing GG.

6 shows a schematic representation of a second alternative to the in 1 as the first embodiment of a transmission according to the invention shown 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 the six switching elements A to F.

To the kinematics of the wheelset according to 1 to maintain is in 6 provided that unchanged the sun gear SO4 as the first element of the fourth planetary gear set RS4 (via the brake A on the gear housing GG fixable and clutch B with the fourth wave 4 connectable) third wave 3 of the automatic transmission, but now that the ring gear HO4 as the second element of the fourth planetary gearset RS4 designed as the drive shaft AN first shaft 1 of the automatic transmission, and that now the planet carrier ST4 as the third element of the fourth planetary gear set RS4 (constantly connected to the clutches E and F) seventh wave 7 of the automatic transmission forms.

7 shows a schematic representation of a third alternative to the in 1 as the first embodiment of a transmission according to the invention shown 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 the six switching elements A to F.

To the kinematics of the wheelset according to 1 to maintain is in 7 provided that the sun gear SO2 as the first element of the second planetary gearset RS2 unchanged (via the clutch F with the shaft 7 connectable) ninth wave 9 of the automatic transmission, but now that the ring gear HO2 as the second element of the second planetary gearset RS2 the (constantly connected to the clutches D and E) eighth wave 8th of the automatic transmission, and that now the planet carrier ST2 as a third element of the second planetary gearset RS2 on the (acting as the first coupling shaft) fifth wave 5 the automatic transmission is constantly connected to the sun gear SO3 of the third planetary gear set RS3.

In consideration of these three exemplified alternatives to the in the 1 As a first embodiment of a transmission according to the invention shown transmission scheme, the skilled artisan will also be the others in the table of 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.

8th shows a second embodiment of an automatic transmission according to the invention. 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 8th 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 8th 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, so each a sun gear, a planetary 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, B, C, D, E and F.

How out 8th 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 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 gear set RS4 in the axial direction completely, whereby the planetary gear set 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 the clutch G also spatially place elsewhere. For example, the clutch G may be spatially disposed in a region axially between the second planetary gear set RS2 and the fourth planetary RS4, adjacent to the coupling D and / or adjacent to the clutch E. In particular, when the clutch G is designed in the form of a dog clutch , It makes sense 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 C.

In 9 is an exemplary circuit diagram of the inventive 10-speed automatic transmission according to 8th 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 8th 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. 10 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 , To here the connection of the clutch G from the first shaft 1 (Drive shaft ON) off to the eighth shaft 8th (To realize planet carrier ST2), the clutch G may be arranged in a region axially between the second planetary gearset RS2 and the fourth planetary gearset RS4, preferably axially adjacent to the second planetary gearset RS2, viewed in the axial direction next to the clutch C and exemplarily radially beyond Clutch E.

In the 8th 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. 11 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 9 shown switching logic ten forward gears and one reverse gear.

12 shows a schematic representation of a first alternative to the in 8th as a second embodiment of a transmission according to the invention shown 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 12 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 12 across from 8th unchanged, as well as the spatial arrangement of the seven switching elements A to G.

To the kinematics of the wheelset according to 8th to maintain is in 12 provided that unchanged the sun gear SO1 as the first element of the first planetary gear set RS1 (via the clutch B with the third wave 3 connectable) fourth wave 4 of the automatic transmission, but now that the ring gear HO1 as the second element of the first planetary gear set RS1 on the (as a second coupling shaft acting) sixth wave 6 the automatic transmission is constantly connected to the ring gear HO3 of the third planetary gearset RS3, and that now the planet carrier ST1 is connected as a third element of the first planetary gearset RS1 fixed to the transmission housing GG.

13 shows a schematic representation of a second alternative to the in 8th as a second embodiment of a transmission according to the invention shown 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 13 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 13 across from 8th unchanged, as well as the spatial arrangement of the seven switching elements A to G.

To the kinematics of the wheelset according to 8th to maintain is in 13 provided that the sun gear SO2 unchanged as the first Element of the second planetary gearset RS2 the (via the clutch F with the shaft 7 connectable) ninth wave 9 of the automatic transmission, but now that the ring gear HO2 as the second element of the second planetary gearset RS2 the (constantly connected to the clutches D and E) eighth wave 8th of the automatic transmission, and that now the planet carrier ST2 as a third element of the second planetary gearset RS2 on the (acting as the first coupling shaft) fifth wave 5 the automatic transmission is constantly connected to the sun gear SO3 of the third planetary gear set RS3.

In consideration of these two exemplified alternatives to the one described in 8th As a second embodiment of a transmission according to the invention illustrated transmission scheme, the expert will easily the others in the table of 11 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.

14 shows a third embodiment of an automatic transmission according to the invention. The wheelset scheme shown here is a modification of the in 1 illustrated 9-speed automatic transmission. The only difference to the wheelset scheme according to 1 is that in the wheelset scheme according to 14 the executed as a clutch fourth switching element D in the power flow now between the sixth wave 6 and the eighth wave 8th the automatic transmission is arranged. This is the sixth wave 6 unchanged the second coupling shaft of the automatic transmission and connects the second element (here planet ST1) of the first planetary gear set RS1 constantly with the third element (here ring gear HO3) of the (constantly connected to the output shaft AB) third planetary gearset RS3. Furthermore, the eighth wave 8th unchanged formed by the second element (here planet carrier ST2) of the second planetary gearset RS2.

As in 1 are at the in 14 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, so each a sun gear, a planetary 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 essentially taken over is the spatial arrangement of the switching elements A, B, C, E and F. The spatial arrangement of the clutch D, however, is opposite 1 changed, conditioned by the opposite 1 modified kinematic connection of the clutch D.

How out 14 it can be seen that in the power flow is now between shaft 8th (Planet carrier ST2) and shaft 6 (second coupling shaft, connecting planet carrier ST1 and ring gear HO3) arranged clutch D spatially in a range axially between the (continuously connected to the drive shaft AN) fourth planetary gear set RS4 and the second planetary gear set RS2, while directly axially adjacent to the second planetary gear set RS2. This allows a structurally comparatively simple and low leakage leaking supply of pressure and lubricant to the clutch D out, namely coming from the drive shaft AN forth via only one rotary feedthrough in the planet ST1 and from there to the pressure chamber / pressure compensation chamber / disk set of the clutch D.

According to this spatial arrangement of the clutch D, the clutch E, which is likewise arranged (together with the clutch C) in a region axially between the fourth planetary gearset RS4 and the second planetary gearset RS2, no longer directly adjoins the second planetary gearset RS2 axially. Now the clutch D is located axially between clutch E and planetary gearset RS2.

According to the new spatial arrangement of the clutch D, the clutch C is now the only switching element, which is arranged axially between the second planetary gearset RS2 and the third planetary gear set RS3 (always connected to the output shaft AB).

It should not go unmentioned that the in 14 proposed spatial arrangement of the four planetary gear sets RS1, RS2, RS3, RS4 is to be understood as exemplary. Alternatively, without changing the kinematics of the wheelset system, the four planetary gear sets RS1, RS2, RS3, RS4 can also be arranged in a different order, for example coaxially next to one another with the defined sequence "second, fourth, first, third planetary gear set" (ie in arrangement "RS2 -RS4-RS1-RS3 ").

Nevertheless, the number of switching elements compared 1 has not been changed, allows the automatic transmission according to 14 advantageously the group circuit-free switching of ten forward gears, which is described below with reference to 15 is explained in more detail.

In 15 is an exemplary circuit diagram of the inventive 10-speed automatic transmission according to 14 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 opposite of the in the 1 and 2 discussed first embodiment of the invention additional forward speed is in the 14 shown third embodiment of the invention from the translation between the eighth and ninth forward gear of the 9-speed transmission according to 1 , Here, the shifting logic of the forward gears is one to eight and the shift logic of the reverse gear for the 9-speed transmission according to 1 and for the 10-speed transmission according to 14 identical, while the switching logic of the ninth forward gear for the 9-speed automatic transmission according to 1 is identical to the switching logic of the tenth forward gear for the 10-speed transmission according to 14 , The seventh forward gear is designed as a direct gear, so that with the eighth to tenth forward gear now three overdrive gears are available.

In the 14 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. 16 shows a table with such planetary gear set type variations, which lead to a technically meaningful transmission structure. In the following, three of these examples are explained in more detail. All variants listed in the table can be used via the in 15 shown switching logic ten forward gears and one reverse gear.

17 shows a schematic representation of a first alternative to the in 14 as a third embodiment of a transmission according to the invention shown transmission scheme. In contrast to the transmission scheme according to 14 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 17 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 17 across from 14 unchanged, as well as the spatial arrangement of the six switching elements A to F.

To the kinematics of the wheelset according to 14 to maintain is in 17 provided that unchanged the sun gear SO1 as the first element of the first planetary gear set RS1 (via the clutch B with the third wave 3 connectable) fourth wave 4 of the automatic transmission, but now that the ring gear HO1 as the second element of the first planetary gear set RS1 on the (as a second coupling shaft acting) sixth wave 6 the automatic transmission is constantly connected to the ring gear HO3 of the third planetary gearset RS3, and that now the planet carrier ST1 is connected as a third element of the first planetary gearset RS1 fixed to the transmission housing GG.

18 shows a schematic representation of a second alternative to the in 14 as a third embodiment of a transmission according to the invention shown transmission scheme. In contrast to the transmission scheme according to 14 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 18 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 18 across from 14 unchanged, as well as the spatial arrangement of the six switching elements A to F.

To the kinematics of the wheelset according to 14 to maintain is in 18 provided that unchanged the sun gear SO4 as the first element of the fourth planetary gear set RS4 (via the brake A on the gear housing GG fixable and clutch B with the fourth wave 4 connectable) third wave 3 of the automatic transmission, but now that the ring gear HO4 as the second element of the fourth planetary gearset RS4 designed as the drive shaft AN first shaft 1 of the automatic transmission, and that now the planet carrier ST4 as the third element of the fourth planetary gear set RS4 (constantly connected to the clutches E and F) seventh wave 7 of the automatic transmission forms.

19 shows a schematic representation of a third alternative to the in 14 as a third embodiment of a transmission according to the invention shown transmission scheme. In contrast to the transmission scheme according to 14 in which all four planetary gear sets are designed as negative planetary gear sets is in the transmission scheme according to 19 the second planetary gearset RS2 designed as a plus planetary gear 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 19 across from 14 unchanged, as well as the spatial arrangement of the six switching elements A to F.

To the kinematics of the wheelset according to 14 to maintain is in 19 provided that the sun gear SO2 as the first element of the second planetary gearset RS2 unchanged (via the clutch F with the shaft 7 connectable) ninth wave 9 of the automatic transmission, but now that the ring gear HO2 as the second element of the second planetary gearset RS2 the (constantly connected to the clutches D and E) eighth wave 8th of the automatic transmission, and that now the planet carrier ST2 as a third element of the second planetary gearset RS2 on the (acting as the first coupling shaft) fifth wave 5 the automatic transmission is constantly connected to the sun gear SO3 of the third planetary gear set RS3.

In consideration of these three exemplified alternatives to the in the 14 As a third embodiment of a transmission according to the invention shown transmission scheme, the expert will easily be the others in the table of 15 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.

20 shows a fourth embodiment of an automatic transmission according to the invention. The wheelset scheme shown here is a further development of the in 14 illustrated 10-speed automatic transmission. With the goal of another forward, without the in 14 significantly change the specified transmission structure and to have to increase the required length of the transmission significantly, is based on the in 14 shown transmission scheme in the transmission according to 20 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 15 achieved first gear known the 10-speed transmission, so an additional starting gear with a translation greater than the translation of 15 known first gear.

In 21 is an exemplary circuit diagram of the 11-speed automatic transmission according to the invention according to 20 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. Now, the eighth forward gear is designed as a direct gear, so see three forward gears with overdrive character available.

As in 14 are at the in 20 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, so each a sun gear, a planetary 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 14 unchanged. Out 14 also adopted is the spatial arrangement of the six switching elements A, B, C, D, E and F.

How out 20 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. Thus corresponds to the spatial position of the clutch G of that position, already based on 8th was discussed. In that sense, all are for 8th Comments made that relate to the arrangement and structural design of the clutch G, mutatis mutandis, for the in 20 illustrated embodiment transferable.

In the 20 proposed extension of the transmission to a seventh switching element G is also possible with a different spatial arrangement of the four planetary gear sets RS1, RS2, RS3, RS4. Without changing the kinematics of the wheelset system, the four planetary gear sets RS1, RS2, RS3, RS4 can also be coaxially arranged side by side with the order "second, fourth, first, third planetary gear set "(" RS2-RS4-RS1-RS3 ").

In the 20 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. 22 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 21 shown switching logic switch eleven forward gears and one reverse gear.

23 shows a schematic representation of a first alternative to the in 20 As a fourth embodiment of a transmission according to the invention shown transmission scheme. In contrast to the transmission scheme according to 20 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. Seen spatially, the sequence of four individual, coaxial with each other side by side arranged Planetenradsätze in 23 across from 20 unchanged, as well as the spatial arrangement of the seven switching elements A to G.

To the kinematics of the wheelset according to 20 to maintain is in 23 provided that unchanged the sun gear SO1 as the first element of the first planetary gear set RS1 (via the clutch B with the third wave 3 connectable) fourth wave 4 of the automatic transmission, but now that the ring gear HO1 as the second element of the first planetary gear set RS1 on the (as a second coupling shaft acting) sixth wave 6 the automatic transmission is constantly connected to the ring gear HO3 of the third planetary gearset RS3, and that now the planet carrier ST1 is connected as a third element of the first planetary gearset RS1 fixed to the transmission housing GG.

24 shows a schematic representation of a second alternative to the in 20 As a fourth embodiment of a transmission according to the invention shown transmission scheme. In contrast to the transmission scheme according to 20 in which all four planetary gear sets are designed as negative planetary gear sets 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 24 across from 20 unchanged, as well as the spatial arrangement of the seven switching elements A to G.

To the kinematics of the wheelset according to 20 to maintain is in 24 provided that the sun gear SO2 as the first element of the second planetary gearset RS2 unchanged (via the clutch F with the shaft 7 connectable) ninth wave 9 of the automatic transmission, but now that the ring gear HO2 as the second element of the second planetary gearset RS2 the (constantly connected to the clutches D, E and G) eighth wave 8th of the automatic transmission, and that now the planet carrier ST2 as a third element of the second planetary gearset RS2 on the (acting as the first coupling shaft) fifth wave 5 the automatic transmission is constantly connected to the sun gear SO3 of the third planetary gear set RS3.

In consideration of these two exemplified alternatives to the one described in 20 As a fourth embodiment of a transmission according to the invention shown transmission scheme, the expert will easily be the others in the table of 21 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.

LIST OF REFERENCE NUMBERS

1

first wave

2

second wave

3

third wave

4

fourth wave

5

fifth shaft, first coupling shaft

6

sixth shaft, second coupling shaft

7

seventh wave

8th

eighth wave

9

ninth wave

A

first switching element, first brake

B

second switching element, first clutch

C

third switching element, second clutch

D

fourth switching element, third clutch

e

fifth switching element, fourth clutch

F

sixth switching element, fifth clutch

G

seventh switching element, sixth 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

i

translation

phi

increment

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, 0006, 0006, 0072, 0072]
• DE 102010041575 B3 [0004]
• DE 102009001253 B3 [0005]
• DE 102013218941 [0006]
• DE 102007055808 A1 [0072]

Claims (32)

Automatic transmission, in particular for a motor vehicle, with a drive shaft (AN), an output shaft (AB), four planetary gear sets (RS1, RS2, RS3, RS4) and at least six switching elements (A to F; A to G) whose selective closing different transmission ratios between the input shaft (AN) and the output shaft (AB) to shift at least nine forward gears, the drive shaft (AN) is constantly connected to the fourth planetary gear set (RS4), and wherein the output shaft (AB) with the third planetary gear set (RS3) is connected, characterized in that only two coupling shafts ( 5 . 6 ) are provided over the individual of the planetary gear sets (RS1 to RS4) with another of the planetary gear sets (RS1 to RS4) are constantly directly connected, and that the fourth planetary gear set (RS4) constantly with at least five switching elements (A, B, C, E , F; A, B, C, E, F, G) is directly connected. Automatic transmission according to claim 1, characterized in that the first coupling shaft ( 5 ) continuously connects the second planetary gearset (RS2) to the third planetary gearset (RS3), and that the second coupling shaft (RS2) 6 ) continuously interconnects the third planetary gear set (RS3) with the first planetary gear set (RS1). Automatic transmission according to claim 1 or 2, characterized in that the first planetary gear set (RS1) is directly connected to a maximum of two switching elements (B; B, D) that the second planetary gear set (RS2) with at least four switching elements (C, D, E, F, C, D, E, F, G) is directly connected, and that the third planetary gear set (RS3) is directly connected to two switching elements (C, D). Automatic transmission according to claim 1, 2 or 3, characterized in that the drive shaft (AN) is constantly directly connected to at least one switching element (C; C, G), and that the output shaft (AB) continuously with a maximum of one switching element (D) directly connected is. Automatic transmission according to one of claims 1 to 4, characterized in that exactly six switching elements (A to F) are provided, wherein • the second planetary gear set (RS2) is constantly directly connected to exactly four switching elements (C, D, E, F), • the third planetary gear set (RS3) is constantly directly connected to exactly two switching elements (C, D), • the fourth planetary gear set (RS4) is permanently connected to exactly five switching elements (A, B, C, E, F), and • the drive shaft (AN) is constantly directly connected to exactly one switching element (C). Automatic transmission according to one of claims 1 to 4, characterized in that exactly seven switching elements (A to G) are provided, wherein • the second planetary gear set (RS2) constantly with exactly five switching elements (C, D, E, F, G) directly connected is, • the third planetary gear set (RS3) constantly with exactly two switching elements (C, D) is directly connected, • the fourth planetary gear set (RS4) constantly with exactly six switching elements (A, B, C, E, F, G) directly connected is, and • the drive shaft (AN) is permanently connected to exactly two switching elements (C, G). Automatic transmission according to one of claims 1 to 6, characterized in that the first planetary gear set (RS1) is constantly directly connected to exactly one switching element (B) and that the output shaft (AB) is constantly directly connected to exactly one other switching element (D). Automatic transmission according to one of claims 1 to 6, characterized in that the first planetary gear set (RS1) is constantly directly connected to exactly two switching elements (B, D) and that the output shaft (AB) is connected directly to any switching element. Automatic transmission according to claim 5, 7 or 8, characterized in that a total of nine rotatable shafts ( 1 to 9 ) and that each of the four planetary gear sets (RS1, RS2, RS3, RS4) each have three elements (SO1, ST1, HO1, SO2, ST2, HO2, SO3, ST3, HO3, SO4, ST4, HO4), wherein the second element (ST4; HO4) of the fourth planetary gear set (RS4) has the first shaft (FIG. 1 ), the second element (ST3) of the third planetary gear set (RS3) has the second shaft (FIG. 2 ), the first element (SO4) of the fourth planetary gear set (RS4) the third wave ( 3 ), • the first element (SO1) of the first planetary gear set (RS1) the fourth wave ( 4 ), • the fifth wave ( 5 ) as the first coupling shaft, the third element (HO2, ST2) of the second planetary gear set (RS2) is constantly connected to the first element (SO3) of the third planetary gear set (RS3), 6 ) as the second coupling shaft, the second element (ST1; HO1) of the first planetary gearset (RS1) constantly connects to the third element (HO3) of the third planetary gearset (RS3), • the third element (HO4; ST4) of the fourth planetary gearset (RS4) seventh wave ( 7 ), the second element (ST2, HO2) of the second planetary gear set (RS2) the eighth wave (FIG. 8th forms, The first element (SO2) of the second planetary gear set (RS2) the ninth wave ( 9 ), • the third element (HO1; ST1) of the first planetary gear set (RS1) is permanently fixed to a housing (GG) of the automatic transmission, • the first switching element (A) is in the force flow between the third shaft ( 3 ) and the housing (GG) is arranged, • the second switching element (B) in the power flow between the third wave ( 3 ) and the fourth wave ( 4 ), the third switching element (C) in the force flow between the first shaft ( 1 ) and the fifth wave ( 5 ), the fourth switching element (D) either in the power flow between the second shaft ( 2 ) and the eighth wave ( 8th ) or in the power flow between the sixth wave ( 6 ) and the eighth wave ( 8th ), the fifth switching element (E) in the force flow between the seventh shaft ( 7 ) and the eighth wave ( 8th ), the sixth switching element (F) in the force flow between the seventh shaft ( 7 ) and the ninth wave ( 9 ) is arranged. Automatic transmission according to one of claims 6 to 9, characterized in that the 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 the preceding claims, characterized in that the second planetary gear set (RS2) by simultaneous closing of the fifth and sixth switching element (E, F) is blockable, such that the rotational speeds of the three elements (SO2, ST2, HO2) of the second Planetary gear set (RS2) in the locked state of the second planetary gear set (RS2) are identical. Automatic transmission according to one of the preceding claims, characterized in that in each gear four of the switching elements are closed and opened at a change of a gear in the following higher or lower gear each only one of the previously closed switching elements and a previously open switching element is closed. Automatic transmission according to one of claims 5, 7, 8, 9, 11, 12, characterized in that nine forward gears and one reverse gear are switchable, wherein • in the first forward gear, the first, second, third and sixth shifting element (A, B, C, F) are torque-conducting, • in the second forward gear, the first, second, fifth and sixth shifting element (A, B, E, F) are torque-conducting, • in the third forward gear, the second, third, fifth and sixth shifting 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 switching element (B, C, D, F) are torque-conducting, • in the seventh forward gear, the third, fourth, fifth and sixth switching element (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 one of claims 6 to 12, 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, the first, second, third and sixth switching element (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, the second, third, fifth and sixth switching element (B, C, E, F) are torque-conducting, • in the fifth forward gear, 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 shift element (B, C, D, E) are torque-conducting, • in the seventh forward gear, the second, third, fourth and sixth shift element (B, C, D, F) are torque-conducting, • in the eight in forward gear, the third, fourth, fifth and sixth shift elements (C, D, E, F) are torque conducting, • in ninth forward gear, the first, third, fourth and sixth shift elements (A, C, D, F) are torque conducting, • im tenth forward gear, 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 5, 7, 8, 9, 11, 12, characterized in that ten forward gears and one reverse gear are switchable, wherein • in the first forward gear, the first, second, third and sixth shifting element (A, B, C, F) are torque-conducting, • in the second forward gear, the first, second, fifth and sixth shifting element (A, B, E, F) are torque-conducting, • in the third forward gear, the second, third, fifth and sixth shifting 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 switching element (B, C, D, F) are torque-conducting, • in the seventh forward gear, the third, fourth, fifth and sixth switching element (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, third, fourth and fifth shift elements (A, C, D, E) are torque-conducting, • in the tenth forward gear, 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 6 to 12, characterized in that eleven forward gears and one reverse gear are switchable, wherein • the first forward, the first, second, sixth and seventh switching element (A, B, F, G) are torque-conducting, • in the second Forward, the first, second, third and sixth switching element (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, the second, third, fifth and sixth switching element (B, C, E, F) are torque-conducting, • in the fifth forward gear, the second, fourth, fifth and sixth switching element (B, D, E, F) are torque-conducting, • in the sixth Forward, 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 n forward gear, 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, • im tenth forward gear, the first, third, fourth and fifth switching element (A, C, D, E) are torque-conducting, • in the eleventh forward gear, 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 16, 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 16, characterized in that one of the four planetary gear sets (RS1, RS2, RS3, RS4) is designed as a positive planetary gear set, while the other three planetary gear sets are each formed as a minus planetary gear set. Automatic transmission according to claim 18, 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 16, 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. Automatic transmission according to one of claims 1 to 16, 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 planetary carrier while the second element of each plus planetary gear set is designed as a ring gear, • the third element of each negative planetary gear set is formed 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 22, characterized in that the planetary gear sets (RS1, RS2, RS3, RS4) are arranged coaxially to each other and in the axial direction one behind the other in an order "RS2, RS4, RS1, RS3". Automatic transmission according to one of claims 1 to 22, characterized in that the planetary gear sets (RS1, RS2, RS3, RS4) are arranged coaxially to each other and in the axial direction one behind the other in an order "RS1, RS4, RS2, RS3". Automatic transmission according to one of the preceding claims, characterized in that the fourth and fifth switching element (D, E) are directly connected to each other. Automatic transmission according to one of the preceding claims, characterized in that the fifth and sixth switching element (E, F) are directly connected to each other. Automatic transmission according to one of claims 23 to 26, characterized in that fifth switching element (E) spatially seen in a range axially between the fourth and second planetary gear set (RS4, RS2) or in a region axially between the second and third planetary gear set (RS2, RS3 ) is arranged. Automatic transmission according to one of claims 23 to 27, characterized in that the sixth shifting element (F) is arranged spatially immediately adjacent to the second planetary gearset (RS2), in a region axially between the fourth and second planetary gearset (RS4, RS2) or in FIG an area axially between the second and third planetary gear set (RS2, RS3) or in a region centrally within the sun gear (SO2) of the second planetary gear set (RS2). Automatic transmission according to claim 23 or any one of claims 25 to 28, characterized in that the seventh switching element (G) is arranged spatially in a region axially between the fourth and second planetary gear set (RS4, RS2), axially adjacent to the second planetary gear set (RS2). , Automatic transmission according to one of claims 24 to 28, characterized in that seventh switching element (G) spatially in a range axially between the fourth and second planetary gear set (RS4, RS2) is disposed adjacent to the fourth switching element (D) and / or adjacent to fifth switching element (E). Automatic transmission according to one of claims 24 to 28, characterized in that 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 24 to 28, characterized in that seventh switching element (G) 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).

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