DE102008000207A1 - Multi-step reduction gear for use in planetary construction, particularly for automatic gear for a motor vehicle, has planetary gear set, which is formed as plus-planetary gear set with sun wheel - Google Patents

Abstract

The multi-step reduction gear has a planetary gear set (RS1), which is formed as plus-planetary gear set with a sun wheel (SO1). Another planetary gear set (RS2) is formed as plus planetary gear set with a bar (ST2). Third planetary gear set (RS3) is formed as minus-planetary gear set with another bar (ST3). Fourth planetary gear set (RS4) is formed as minus-planetary gear set with third bar (ST4).

Description

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

Automatic transmission, in particular for motor vehicles, include the state the technology planetary gear sets, which by means of friction or Switching elements, such as clutches and brakes are switched and usually with a slip effect and optionally with a lock-up clutch provided starting element, such as a hydrodynamic torque converter or a fluid coupling are connected. such Automatic transmissions in general are already known in the art often described and subject to permanent development and improvement. So should this gear a sufficient number from forward gears as well as a reverse gear and a well-suited for motor vehicles translation with high overall spread and favorable increments exhibit. In addition, these transmissions are a small Construction costs, in particular a small number of switching elements require and avoid sequential switching double circuits, so that in circuits in defined gear groups only one Switching element is changed.

So is from the generic DE 10 2005 002 337 A1 the Applicant a multi-speed transmission with a drive shaft, an output shaft, four interconnected individual planetary gear sets and five switching elements known in which eight forward gears are group-switching-free switchable, so such that when changing from one forward gear in the next higher or lower forward gear each only one of previously closed switching elements open and only one of the previously open th switching elements is closed. The multi-speed transmission also has a reverse gear. In all forward gears and in reverse gear each three switching elements are closed. All four planetary gear sets are designed as so-called simple minus planetary gear sets. A minus planetary gear known to include a sun gear, a ring gear and a planet carrier with planetary gears, each of these planetary gears is in meshing with sun gear and ring gear. Such a minus planetary gear set is also referred to as a simple planetary gear set. With regard to the kinematic coupling of the four planetary gear sets with each other and the drive and output shaft is provided here that a web of the fourth planetary gear set and the drive shaft are interconnected and form a first shaft of the transmission, a web of the third planetary gear and the output shaft are connected together and forming a second shaft of the transmission, a sun gear of the first planetary gear and a sun gear of the fourth planetary gear are connected to each other and form a third shaft of the transmission, a ring gear of the first planetary gear forms a fourth shaft of the transmission, a ring gear of the second planetary gear set and a sun gear of the third planetary gear set are connected to each other and form a fifth shaft of the transmission, a web of the first planetary gear and a ring gear of the third planetary gear are connected to each other and form a sixth shaft of the transmission, a sun gear of the second planet enradsatzes and a ring gear of the fourth planetary gear set are connected to each other and form a seventh shaft of the transmission and a web of the second planetary gear set forms an eighth shaft of the transmission. With regard to the kinematic coupling of the five switching elements to the four planetary gear sets and the input and output shafts is provided that the first switching element in the power flow between the third shaft and a housing of the transmission, the second switching element between the fourth shaft and the housing of the transmission, the third switching element between the first and fifth shaft, the fourth switching element either between the eighth and second shaft or between the eighth and sixth shaft, and the fifth switching element either between the seventh and fifth shaft or between the seventh and eighth or between the fifth and eighth Wave is arranged.

conditioned by which to achieve a favorable for motor vehicles large overall spread of the transmission required stand translations of the Single planetary gear sets, this 8-speed automatic transmission in the planetary gear sets one, two and four depending on the actual one Stand translation and operating point comparatively high planetary speeds on. For example, in the fifth forward gear the planetary gear speed in the first planetary gear set to about 2.8 times the transmission input speed and the planetary speed in the fourth Planetary gear set up to about 2.3 times the transmission input speed be. In reverse, the planetary gear speed in the second planetary gear even up to about 6 times the transmission input speed be.

Furthermore, from the prior art, several 8-speed automatic transmission known on the wheelset of the multi-speed transmission according to DE 10 2005 002 337 A1 Each of the four simple minus planetary gear sets is replaced by a so-called plus planetary gear set. A plus planetary gearset is known to include a sun gear, a ring gear, and a planet carrier having inner and outer planetary gears, each of these inner planet gears having the sun gear and an outer planetary gear is in meshing engagement, and wherein each of these outer planet gears is in mesh with the ring gear and with an inner planet gear. Such a plus planetary gear set is also referred to as Doppelplanetenradsatz.

So was the case of the DE 20 2006 009 123 U1 known multi-step transmission over the DE 10 2005 002 337 A1 replaced the first minus planetary gear set by a plus planetary gear set and changed the transmission kinematics in that the fourth of the eight shafts of the transmission is now formed by the web of the first planetary gear, and now that the ring gears of the first and third planetary gear set constantly as the sixth wave of Gearboxes are interconnected.

In the from the DE 20 2006 011 432 U1 known multi-step transmission was compared to DE 10 2005 002 337 A1 the second minus planetary gear set replaced by a plus planetary gear set and the gearbox kinematics changed so that now the fifth gear of the transmission, the web of the second planetary gear and the sun gear of the third planetary gear set are constantly connected, and that the eighth shaft of the transmission now by the Ring gear of the second planetary gear set is formed.

In the from the DE 20 2006 008 815 U1 well-known multi-step transmission was finally compared to the DE 10 2005 002 337 A1 replaced the fourth minus planetary gear set by a plus planetary gear set and the gearbox kinematics changed so that now the ring gear of the fourth planetary gear set and the drive shaft are constantly connected to each other as the first shaft of the transmission, and now that the sun gear of the second planetary gear set and the bridge of the fourth Planetenradsatzes are constantly connected to each other as the seventh shaft of the transmission.

Of the present invention is based on the object, a stand the technology alternative multi-speed transmission of the aforementioned Art with at least eight group circuit switchable forward gears and at least propose a reverse gear, using a total of four planetary gear sets requires the smallest possible number of switching elements becomes. The gear should be comparable to the state of the art large spread with comparatively harmonic ratio have, however, the planetary gears of the speed critical Plan tenradsätze on one opposite the stand the technology operated lower speed level.

These The object is achieved by a multi-step transmission with the features of claim 1 and the claim 2 or of claim 3 or of claim 4. Further advantageous embodiments and further developments are based the dependent claims.

The multi-speed transmission according to the invention in planetary design is in all four proposed solutions of the transmission scheme of the generic DE 10 2005 002 337 A1 and has a drive shaft, an output shaft, four planetary gear sets coupled together, at least eight rotatable shafts and five shift elements (two brakes and three clutches) whose selective engagement causes different ratios between the drive shaft and the output shaft, so that eight forward gears and one reverse gear are feasible. In each course, three of the five shift elements are closed, wherein when changing from one forward gear in the next higher or lower forward gear only one of the previously closed switching elements open and only one of the previously opened switching elements is closed.

• • ein erstes Element des vierten Planetenradsatzes ständig mit der Antriebswelle verbunden ist als die erste Welle des Getriebes,
• • ein erstes Element des dritten Planetenradsatzes ständig mit der Abtriebswelle verbunden ist als die zweite Welle des Getriebes,
• • ein zweites Element des vierten Planetenradsatzes ständig mit einem ersten Element des ersten Planetenradsatzes verbunden ist als die dritte Welle des Getriebes,
• • ein zweites Element des ersten Planetenradsatzes die vierte Welle des Getriebes bildet,
• • ein erstes Element des zweiten Planetenradsatzes ständig mit einem zweiten Element des dritten Planetenradsatzes verbunden ist als die fünfte Welle des Getriebes,
• • ein drittes Element des ersten Planetenradsatzes ständig mit einem dritten Element des dritten Planetenradsatzes verbunden ist als die sechste Welle des Getriebes,
• • ein drittes Element des vierten Planetenradsatzes ständig mit einem zweiten Element des zweiten Planetenradsatzes verbunden ist als die siebte Welle des Getriebes,
• • ein drittes Element des zweiten Planetenradsatzes die achte Welle des Getriebes bildet,
• • das erste Schaltelement im Kraftfluss zwischen der dritten Welle und einem Gehäuse des Getriebes angeordnet ist,
• • das zweite Schaltelement im Kraftfluss zwischen der vierten Welle und dem Gehäuse des Getriebes angeordnet ist,
• • das dritte Schaltelement im Kraftfluss zwischen der ersten und der fünften Welle angeordnet ist,
• • das vierte Schaltelement im Kraftfluss entweder zwischen der zweiten und achten Welle oder zwischen der sechsten und achten Welle angeordnet ist, und
• • das fünfte Schaltelement im Kraftfluss entweder zwischen der fünften und siebten Welle oder zwischen der fünften und achten Welle oder zwischen der siebten und achten Welle angeordnet ist.

As in the generic DE 10 2005 002 337 A1 is provided in all four solutions according to the invention that

• • a first element of the fourth planetary gear set is continuously connected to the drive shaft as the first shaft of the transmission,
• A first element of the third planetary gear set is continuously connected to the output shaft as the second shaft of the transmission,
• • a second element of the fourth planetary gear set is continuously connected to a first element of the first planetary gear set as the third shaft of the transmission,
• A second element of the first planetary gear set forms the fourth shaft of the transmission,
• • a first element of the second planetary gear set is continuously connected to a second element of the third planetary gear set as the fifth shaft of the transmission,
• • a third element of the first planetary gear set is continuously connected to a third element of the third planetary gear set as the sixth shaft of the transmission,
• • a third element of the fourth planetary gear set is continuously connected to a second element of the second planetary gear set as the seventh shaft of the transmission,
• A third element of the second planetary gear set forms the eighth shaft of the transmission,
• The first switching element is arranged in the power flow between the third shaft and a housing of the transmission,
• The second switching element is arranged in the power flow between the fourth shaft and the housing of the transmission,
• The third switching element is arranged in the force flow between the first and the fifth shaft,
• • The fourth switching element is arranged in the power flow either between the second and eighth shaft or between the sixth and eighth shaft, and
• • The fifth switching element is arranged in the power flow either between the fifth and seventh shaft or between the fifth and eighth shaft or between the seventh and eighth shaft.

• • der erste Planetenradsatz als Plus-Planetenradsatz ausgebildet ist mit einem Sonnenrad als erstes Element und einem gekoppelten Steg als zweites Element und einem Hohlrad als drittes Element,
• • der zweite Planetenradsatz als Plus-Planetenradsatz ausgebildet ist mit einem gekoppelten Steg als erstes Element und einem Sonnenrad als zweites Element und einem Hohlrad als drittes Element,
• • der dritte Planetenradsatz als Minus-Planetenradsatz ausgebildet ist mit einem Steg als erstes Element und einem Sonnenrad als zweites Element und einem Hohlrad als drittes Element, und
• • der vierte Planetenradsatz als Minus-Planetenradsatz ausgebildet ist mit einem Steg als erstes Element und einem Sonnenrad als zweites Element und einem Hohlrad als drittes Element.

In the first solution according to claim 1, the invention provides that

• The first planetary gear set is designed as a plus planetary gear set with a sun gear as a first element and a coupled web as a second element and a ring gear as a third element,
• The second planetary gear set is designed as a plus planetary gear set with a coupled web as a first element and a sun gear as a second element and a ring gear as a third element,
• The third planetary gear set is designed as a minus planetary gear set with a web as a first element and a sun gear as a second element and a ring gear as a third element, and
• • The fourth planetary gear set is designed as a minus planetary gear set with a web as a first element and a sun gear as a second element and a ring gear as a third element.

• • der erste Planetenradsatz als Plus-Planetenradsatz ausgebildet ist mit einem Sonnenrad als erstes Element und einem gekoppelten Steg als zweites Element und einem Hohlrad als drittes Element,
• • der zweite Planetenradsatz als Minus-Planetenradsatz ausgebildet ist mit einem Hohlrad als erstes Element und einem Sonnenrad als zweites Element und einem Steg als drittes Element,
• • der dritte Planetenradsatz als Minus-Planetenradsatz ausgebildet ist mit einem Steg als erstes Element und einem Sonnenrad als zweites Element und einem Hohlrad als drittes Element, und
• • der vierte Planetenradsatz als Plus-Planetenradsatz ausgebildet ist mit einem Hohlrad als erstes Element und einem Sonnenrad als zweites Element und einem gekoppelten Steg als drittes Element.

In the second solution according to claim 2, the invention provides that

• The first planetary gear set is designed as a plus planetary gear set with a sun gear as a first element and a coupled web as a second element and a ring gear as a third element,
• The second planetary gear set is designed as a minus planetary gear set with a ring gear as a first element and a sun gear as a second element and a web as a third element,
• The third planetary gear set is designed as a minus planetary gear set with a web as a first element and a sun gear as a second element and a ring gear as a third element, and
• • The fourth planetary gear set is designed as a plus planetary gear set with a ring gear as the first element and a sun gear as a second element and a coupled web as a third element.

• • der erste Planetenradsatz als Minus-Planetenradsatz ausgebildet ist mit einem Sonnenrad als erstes Element und einem Hohlrad als zweites Element und einem Steg als drittes Element,
• • der zweite Planetenradsatz als Plus-Planetenradsatz ausgebildet ist mit einem gekoppelten Steg als erstes Element und einem Sonnenrad als zweites Element und einem Hohlrad als drittes Element,
• • der dritte Planetenradsatz als Minus-Planetenradsatz ausgebildet ist mit einem Steg als erstes Element und einem Sonnenrad als zweites Element und einem Hohlrad als drittes Element, und
• • der vierte Planetenradsatz als Plus-Planetenradsatz ausgebildet ist mit einem Hohlrad als erstes Element und einem Sonnenrad als zweites Element und einem gekoppelten Steg als drittes Element.

In the third solution according to claim 3, the invention provides that

• The first planetary gear set is designed as a minus planetary gear set with a sun gear as a first element and a ring gear as a second element and a web as a third element,
• The second planetary gear set is designed as a plus planetary gear set with a coupled web as a first element and a sun gear as a second element and a ring gear as a third element,
• The third planetary gear set is designed as a minus planetary gear set with a web as a first element and a sun gear as a second element and a ring gear as a third element, and
• • The fourth planetary gear set is designed as a plus planetary gear set with a ring gear as the first element and a sun gear as a second element and a coupled web as a third element.

• • der erste Planetenradsatz als Plus-Planetenradsatz ausgebildet ist mit einem Sonnenrad als erstes Element und einem gekoppelten Steg als zweites Element und einem Hohlrad als drittes Element,
• • der zweite Planetenradsatz als Plus-Planetenradsatz ausgebildet ist mit einem gekoppelten Steg als erstes Element und einem Sonnenrad als zweites Element und einem Hohlrad als drittes Element,
• • der dritte Planetenradsatz als Minus-Planetenradsatz ausgebildet ist mit einem Steg als erstes Element und einem Sonnenrad als zweites Element und einem Hohlrad als drittes Element, und
• • der vierte Planetenradsatz als Plus-Planetenradsatz ausgebildet ist mit einem Hohlrad als erstes Element und einem Sonnenrad als zweites Element und einem gekoppelten Steg als drittes Element.

In the fourth solution according to claim 4, the invention provides that

• The first planetary gear set is designed as a plus planetary gear set with a sun gear as a first element and a coupled web as a second element and a ring gear as a third element,
• The second planetary gear set is designed as a plus planetary gear set with a coupled web as a first element and a sun gear as a second element and a ring gear as a third element,
• The third planetary gear set is designed as a minus planetary gear set with a web as a first element and a sun gear as a second element and a ring gear as a third element, and
• • The fourth planetary gear set is designed as a plus planetary gear set with a ring gear as the first element and a sun gear as a second element and a coupled web as a third element.

• • entweder der Steg oder das Hohlrad des vierten Planetenradsatzes ständig mit der Antriebswelle verbunden ist als die erste Welle des Getriebes,
• • stets der Steg des dritten Planetenradsatzes ständig mit der Abtriebswelle verbunden ist als die zweite Welle des Getriebes,
• • stets die Sonnenräder des vierten und ersten Planetenradsatzes ständig miteinander verbunden sind als die dritte Welle des Getriebes,
• • entweder der Steg oder das Hohlrad des ersten Planetenradsatzes die vierte Welle des Getriebes bildet,
• • entweder der Steg oder das Hohlrad des zweiten Planetenradsatzes ständig mit dem Sonnenrad des dritten Planetenradsatzes verbunden ist als die fünfte Welle des Getriebes,
• • entweder der Steg oder das Hohlrad des ersten Planetenradsatzes ständig mit einem Hohlrad des dritten Planetenradsatzes verbunden ist als die sechste Welle des Getriebes,
• • entweder der Steg oder das Hohlrad des vierten Planetenradsatzes ständig mit einem Sonnenrad des zweiten Planetenradsatzes verbunden ist als die siebte Welle des Getriebes, und
• • entweder der Steg oder das Hohlrad des zweiten Planetenradsatzes die achte Welle des Getriebes bildet.

All four solutions according to the invention therefore have in common that

• Either the web or the ring gear of the fourth planetary gear set is continuously connected to the drive shaft as the first shaft of the transmission,
• Always the web of the third planetary gear set is always connected to the output shaft as the second shaft of the gearbox,
• Always the sun gears of the fourth and first planetary gear sets are constantly connected to each other as the third shaft of the transmission,
• Either the web or the ring gear of the first planetary gear set forms the fourth shaft of the transmission,
• Either the web or the ring gear of the second planetary gear set is continuously connected to the sun gear of the third planetary gear set as the fifth shaft of the transmission,
• Either the web or the ring gear of the first planetary gear set is continuously connected to a ring gear of the third planetary gear set as the sixth shaft of the transmission,
• • either the bridge or the ring gear of the fourth Planetenradsatzes is constantly connected to a sun gear of the second planetary gear set as the seventh shaft of the transmission, and
• Either the web or the ring gear of the second planetary gear set forms the eighth shaft of the transmission.

All four solutions according to the invention pursue the same goal, namely the representation of a generic DE 10 2005 002 337 A1 alternative wheelset concept with reduced speed level for the planetary wheels of the conceptually critical speed planetary gear sets. For this purpose, provided in all four solutions according to the invention as a common approach that at least two of the four planetary gear sets are each designed as plus planetary gear (in Doppelplanetenbauweise) and at least one of the four planetary gear sets as a minus planetary gear set (in Einfachplanetenbauweise) is formed. In this case, the four solutions according to the invention differ from each other by different combinations of plus planetary gear sets.

As in the generic multistage transmission according to the DE 10 2005 002 337 A1 applies also to the multi-speed transmission according to the invention that the first forward speed by closing the first, second and third switching element, the second forward speed by closing the first, second and fifth switching element, the third forward speed by closing the second, third and fifth switching element, the fourth Forward speed by closing the second, fourth and fifth shift elements, the fifth forward speed by closing the second, third and fourth shift element, the sixth forward speed by closing the third, fourth and fifth shift element, the seventh forward speed by closing the first, third and fourth shift element, the eighth forward speed by closing the first, fourth and fifth shift element and the reverse speed by closing the first, second and fourth shift element results.

Due to the inventive design of the multi-speed transmission resulting in particular for passenger cars suitable translations with large overall spread in relatively harmonious gear gradation. A significant advantage of the multistage transmission according to the invention is that the planetary gear speeds in the speed-critical planetary gear sets one, two and four compared to the generic multistage transmission according to the DE 10 2005 002 337 A1 Depending on the inventive design of the wheelset a reduction of Planetenraddrehzahlniveaus in the first planetary gear set from 2.8 times the transmission input speed can be achieved at less than 2.2 times the transmission input speed in the fifth forward gear. For the fourth planetary gear set, a reduction in the planetary gear speed levels from 2.3 times the transmission input speed to less than 1.8 times the transmission input speed can be achieved. Due to the concept, the second planetary gear set in reverse is particularly speed-critical. Depending on the inventive design of the wheelset can be achieved in reverse gear, a significant reduction of the planetary speed from 6 times the transmission input speed to less than 3.7 times the transmission input speed. In accordance with this considerable reduction of the planetary gear speeds in the various planetary gear sets of the design effort for the lubrication of the planet gears relative to the generic multistage transmission according to the DE 10 2005 002 337 A1 be significantly reduced, which has a beneficial effect on the transmission costs and on the development time. In addition, can be avoided by the inventive measures drive motor side measures to limit the transmission input speed or at least limited to a minimum.

About that In addition, in the multi-speed transmissions according to the invention the construction cost due to the small number of switching elements, namely two brakes and three clutches, comparatively low. moreover is efficiency in all gears due to low drag losses good, because in each gear only two switching elements are not engaged are.

Regarding the spatial arrangement of the four planetary gear sets in the housing of the transmission is in an advantageous embodiment proposed, the four planetary gear coaxial with each other next to each other in an order "first, fourth, second, third Planetary gear set. "Such an arrangement enables that all four planetary gear sets at most be penetrated centrally by a shaft of the transmission in the axial direction and is particularly suitable for a motor vehicle with so-called standard drive and along the direction of travel built-in gearbox.

The spatial arrangement of the switching elements of the multi-speed transmission according to the invention within the transmission housing is limited in principle only by the dimensions and the outer shape of the transmission housing. Numerous suggestions regarding the spatial arrangement and structural design of the switching elements are, for example, the generic DE 10 2005 002 337 A1 and their international subsequent application can be removed.

Thus, for example, in a favorable for a standard drive variant in terms of Switching element arrangement may be provided that the first and the second switching element spatially seen are at least partially disposed in a region radially above the first or fourth planetary gear set, ie adjacent to the first planetary gear. Seen spatially, the third and fifth shifting elements can be arranged, for example, at least partially in a region axially between the second and third planetary gear set, wherein the fifth shifting element provided for blocking the second planetary gearset preferably directly adjoins the second planetary gearset axially. However, the fifth switching element can also be arranged on the side facing away from the third planetary gear set of the second planetary gear set, ie in a range axially between the second and fourth planetary gear set, then also preferably immediately adjacent axially to the second planetary gear set. Seen spatially, the fourth shifting element can be arranged, at least partially, in an area axially between the second and third planetary gear set or spatially at least partially in a region axially between the fourth and second planetary gear set. For example, the disk set of this fourth switching element may be arranged adjacent to the third planetary gearset or adjacent to the second planetary gearset.

Comparable to the generic multistage transmission according to the DE 10 2005 002 337 A1 It is also possible with the multi-speed transmission according to the invention to provide for starting the motor vehicle either a hydrodynamic converter, an external starting clutch or other suitable external starting elements, or to realize the starting operation with a built-in gear starting element. As such a gear-internal starting element for this one of the two brakes is particularly well, as they transmit torque in the first and second forward gear and in reverse.

Furthermore are the multistage transmissions according to the invention designed such that adaptability to different powertrain configurations both in the direction of force flow as well as in space is possible. So it is for example without special constructive measures possible, drive and output the gearbox either coaxial or axially parallel to each other to order.

For an application with coaxially extending drive and Output shaft, for example, it is appropriate that the first planetary gear set facing the drive of the transmission planetary gear the planetary gear set according to the invention is. For an application with axis-parallel or angled to each other extending input and output shaft, the first or the third planetary gear set arranged on the side of the transmission case be that which is operatively connected to the drive shaft drive motor facing the transmission.

In Connection with the proposed spatial arrangement of the four planetary gear coaxial side by side in the Order "first, fourth, second, third planetary gearset" and the proposed spatial arrangement of the five Switching elements within the gearbox it is constructive advantageously possible that a maximum of three of the four Planetary gear sets in each case at most of one shaft of the transmission are centered in the axial direction. Correspondingly simple is the structural design of the pressure and lubricant supply to the servos of each Switching elements. In conjunction with coaxial with each other Drive and output shaft, for example, only passes through the first Shaft of the gearbox the first, fourth and second planetary gear set centric. In conjunction with axis-parallel or angled to each other running drive and output shaft and drive motor close first planetary gear set, for example, only passes through the first wave of the transmission, the first, fourth and second planetary gear centric. In conjunction with axially parallel or angled drive units and output shaft and drive motor close to the third planetary gear set For example, it may be provided that only the third and second Planetary gear set of only one shaft of the transmission, namely only from the drive shaft or only from the first shaft of the transmission be penetrated centrally.

The invention will be described below with reference to the in the 1 to 32 illustrated embodiments explained in more detail. Identical or comparable components are also provided with the same reference numerals.

It demonstrate:

1 a schematic representation of a first embodiment of a multi-stage transmission according to the first solution according to the invention;

2 an exemplary first thrust bearing assembly for the multi-speed transmission according to 1 ;

3 an exemplary second thrust bearing assembly for the multi-stage transmission according to 1 ;

4 an exemplary third thrust bearing assembly for the multi-speed transmission according to 1

5 an exemplary fourth thrust bearing order for the multi-speed transmission according to 1

6 an exemplary fifth thrust bearing assembly for the multi-speed transmission according to 1

7 an exemplary sixth thrust bearing assembly for the multi-speed transmission according to 1

8th a schematic representation of a second embodiment of a multi-stage transmission according to the first solution according to the invention;

9 a schematic representation of a third embodiment of a multi-speed transmission according to the first solution according to the invention;

10 a schematic representation of a fourth embodiment of a multi-stage transmission according to the first solution according to the invention;

11 a schematic representation of a fifth embodiment of a multi-speed transmission according to the first solution according to the invention;

12 a schematic representation of a sixth embodiment of a multi-speed transmission according to the first solution according to the invention;

13 a schematic representation of a first embodiment of a multi-speed transmission according to the second inventive solution;

14 a schematic representation of a second embodiment of a multi-speed transmission according to the second inventive solution;

15 a schematic representation of a third embodiment of a multi-speed transmission according to the second inventive solution;

16 a schematic representation of a fourth embodiment of a multi-speed transmission according to the second inventive solution;

17 a schematic representation of a fifth embodiment of a multi-stage transmission according to the second inventive solution;

18 a schematic representation of a sixth embodiment of a multi-stage transmission according to the second inventive solution;

19 a schematic representation of a first embodiment of a multi-speed transmission according to the third inventive solution;

20 a schematic representation of a second embodiment of a multi-speed transmission according to the third inventive solution;

21 a schematic representation of a third embodiment of a multi-speed transmission according to the third inventive solution;

22 a schematic representation of a fourth embodiment of a multi-speed transmission according to the third inventive solution;

23 a schematic representation of a fifth embodiment of a multi-speed transmission according to the third inventive solution;

24 a schematic representation of a sixth embodiment of a multi-speed transmission according to the third inventive solution;

25 a schematic representation of a first embodiment of a multi-speed transmission according to the fourth inventive solution;

26 a schematic representation of a second embodiment of a multi-speed transmission according to the fourth inventive solution;

27 a schematic representation of a third embodiment of a multi-speed transmission according to the fourth inventive solution;

28 a schematic representation of a fourth embodiment of a multi-speed transmission according to the fourth inventive solution;

29 a schematic representation of a fifth embodiment of a multi-speed transmission according to the fourth inventive solution;

30 a schematic representation of a sixth embodiment of a multi-stage gear according to the fourth inventive solution;

31 an exemplary circuit diagram and exemplary gear ratios for the multi-speed transmission according to 1 - 6 . 13 - 15 . 19 - 21 and 25 - 27 ; and

32 an exemplary circuit diagram and exemplary gear ratios for the multi-speed transmission according to 7 - 12 . 16 - 18 . 22 - 24 and 28 - 30 ,

1 now shows a schematic representation of a transmission scheme as a first embodiment of a multi-speed transmission according to the first inventive solution. The transmission comprises a drive shaft AN and an output shaft AB, and four planetary gear sets RS1, RS2, RS3, RS4 and five switching elements A, B, C, D, E, which are all arranged in a housing GG of the transmission. In this exemplary embodiment, the four planetary gear sets RS1, RS2, RS3, RS4 are arranged coaxially behind one another in the axial direction in the order "RS1, RS4, RS2, RS3." The planetary gear set RS1 and the planetary gearset RS2 are both each a simple plus planetary gear set in double planetary construction A positive planetary gear set is known to mesh with inner and outer planet gears, these inner planetary gears also meshing with the sun gear of this planetary gear set, and with these outer planetary gears meshing with the ring gear of this planetary gearset , the sun gear with SO1, the inner planetary gears with PL1i, the outer planetary gears with PL1a, the bridge on which the inner and outer planetary gears PL1i, PL1a are rotatably supported, ST1 corresponding to this nomenclature is the ring gear of the planetary gear set RS2 with HO2 denotes the sun gear with SO2, d The inner planetary gears with PL2i, the outer planetary gears with PL2a, the bridge on which the inner and outer planetary gears PL2i, PL2a are rotatably mounted, with ST2. The other two planetary gear sets RS3 and RS4 are each designed as simple minus planetary gear sets. A minus planetary gearset has known planetary gears that mesh with sun and ring gear of this planetary gear set. The ring gear of the planetary gearset RS3 is denoted by HO3, the sun gear with SO3, the planetary gears with PL3 and the web on which said planet gears PL3 are rotatably mounted, with ST3. Corresponding to this nomenclature is the ring gear of the planetary gear set RS4 denoted by HO4, the sun gear with SO4, the planetary gears with PL4 and the web on which said planet gears PL4 are rotatably mounted, with ST4.

Like in this one 1 Furthermore, it can be seen, the switching elements A and B are designed as brakes, which are both executed in the illustrated embodiment as frictionally switchable disk brake, of course, in another embodiment as frictionally switchable band brake or, for example, can be designed as a form-locking switchable claw or cone brake. The switching elements C, D and E are designed as clutches, which are all executed in the illustrated embodiment as frictionally switchable multi-plate clutch, of course, in another embodiment, for example, as a form-fitting switchable claw or cone clutch can be performed. With these five switching elements A to E, a selective switching of eight forward gears and at least one reverse gear can be realized, which will be explained later in more detail. The multi-speed transmission according to the invention has a total of at least eight rotatable shafts that with 1 to 8th are designated.

With regard to the kinematic 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 provided in the multi-speed transmission according to the first inventive solution: the web ST4 of the fourth planetary gear set RS4 and the drive shaft AN are as a wave 1 constantly connected. The web ST3 of the third planetary gearset RS3 and the output shaft AB are as a shaft 2 constantly connected. The sun gears SO1, SO4 of the first and fourth planetary gear sets RS1, RS4 are as a shaft 3 constantly connected. The coupled web ST1 of the first planetary gear set RS1 forms the shaft 4 , The coupled web ST2 of the second planetary gearset RS2 and the sun gear SO3 of the third planetary gearset RS3 are as a shaft 5 constantly connected. The ring gear HO1 of the first planetary gearset RS1 and the ring gear HO3 of the third planetary gearset RS3 are a shaft 6 constantly connected. The sun gear SO2 of the second planetary gearset RS2 and the ring gear HO4 of the fourth planetary gearset RS4 are as a shaft 7 constantly connected. The ring gear HO2 of the second planetary gear set RS2 forms the shaft 8th ,

With regard to the kinematic coupling of the five switching elements A to E to the waves thus described 1 to 8th In the case of the multistage transmission according to the first solution according to the invention, the following is provided in the transmission: The brake A as the first shifting element of the transmission is in the force flow between the shaft 3 and a housing GG of the transmission arranged and sets in the closed or closed state, the interconnected sun gears SO1 and SO4 of the first and fourth planetary gear set RS1, RS4. The brake B as a second switching element of the transmission is in the power flow between the shaft 4 and the housing GG arranged and sets in the closed or closed state, the coupled web ST1 of the first planetary gear set RS1. The clutch C as the third switching element of the transmission is in the power flow between the shaft 1 and the wave 5 arranged and connects in the switched or closed state, the drive shaft AN with the coupled web ST2 of the second planetary gearset RS2 and with the sun gear SO3 of the third planetary gearset RS3. The clutch D as the fourth switching element of the transmission is in the power flow between the shaft 2 and the wave 8th arranged and connected in the closed or closed state, the ring gear HO2 of the second planetary gearset RS2 with the web ST3 of the third planetary gear set RS3 and thus the ring gear HO2 also with the output shaft AB. The clutch E as fifth switching element of the transmission is in the power flow between the shaft 5 and the wave 7 arranged and connects in the closed or closed state, the sun gear SO2 and the coupled bridge ST2 of the second planetary gear set RS2 with each other.

In the in 1 illustrated embodiment, the first planetary gearset RS1 of the gearset close to the transmission and the third planetary gearset RS3 of the output gearset of the transmission, wherein drive shaft AN and output shaft AB are arranged for example coaxially to each other. It is readily apparent to those skilled in the art that this transmission can be modified without special effort in such a way that the input and output shafts are no longer arranged coaxially with one another, for example parallel to the axis or at an angle to one another. In such an arrangement, the person skilled in the art will also arrange the drive of the transmission near the third planetary gear set RS3, that is to say on the side of the third planetary gear set RS3 facing away from the first planetary gear set RS1.

In principle, the spatial arrangement of the switching elements of the in 1 illustrated embodiment of a multi-speed transmission according to the invention within the transmission be arbitrary and is limited only by the dimensions and the outer shape of the gear housing GG.

In the in 1 illustrated embodiment, the two brakes A, B spatially in the region of the drive-near first planetary gear set RS1 arranged, while axially next to each other, the kinematic connection of the two brakes A, B to the first planetary gear set RS1 conditionally, that the brake B closer to the the first planetary gear set RS1 adjacent fourth planetary gear set RS4 is arranged as the brake A, or that the brake A is closer to the drive of the transmission angeord net than the brake B. Spatially seen the brake B is at least partially in a region radially above the first planetary gearset RS1 arranged and the brake A accordingly on the fourth planetary gearset RS4 facing away from (drive near) side of the first planetary gearset RS1. An inner disc carrier of the brake A forms a portion of the shaft 3 of the transmission and is rotationally connected on the fourth planetary gearset RS4 side remote from the first planetary gear set RS1 with the sun gear SO1. Sectionwise is the wave 3 formed as a kind of sun wave, which connects the sun gears SO1, SO4 of the planetary gear sets RS1, RS4 together. It can be the wave 3 both at the drive shaft AN and at a (in 1 not shown) gearbox fixed hub of a housing wall to be rotatably mounted. An inner disc carrier of the brake B is as a shaft 4 of the transmission with the coupled web ST1 of the first planetary gear set RS1 rotationally connected. The necessary for the actuation of the friction elements of the two brakes A, B servos are in 1 for simplicity not shown in detail and can be integrated or axially displaceable, for example, in the transmission housing GG or in a gear housing fixed housing wall or in a releasably connected to the transmission housing GG housing cover.

Of the One skilled in the art will exemplify this exemplary spatial arrangement Both brakes A, B modify if necessary without special inventive effort. Thus, the brake A, for example, at least partially radially over the first planetary gear set RS1 and the brake B at least partially arranged radially over the fourth planetary gear set RS4 be. In yet another embodiment, the two Brakes A, B, for example, in radial superimposed axially adjacent to the first planetary gearset RS1 on the fourth planetary gear set RS4 facing away from, wherein the brake B then, for example, on a larger Diameter is arranged as the brake A.

How out 1 Furthermore, as can be seen, all three clutches C, D, E are arranged at least partially in a region axially between the second and third planetary gearset RS2, RS3, the servo device required for actuating the respective disk sets of the clutches C, D, E 1 for simplicity are not shown in detail.

The clutch E is immediately adjacent axially to the second planetary gear set RS2. In this case, an outer disk carrier of the clutch E forms a portion of the shaft 5 of the transmission and on the one hand on its side facing the second planetary gearset RS2 side with the coupled web ST2 of the second planetary gearset RS2 and on the other hand its side facing away from the second planetary gear set RS2 (via an outer disk carrier of the adjacent clutch C) with the sun gear SO3 of the third planetary gearset RS3 rotationally connected. An inner disk carrier of the clutch E forms a portion of the shaft 7 of the transmission and is rotationally connected to the sun gear SO2 of the second planetary gearset RS2, which in turn is constantly connected rotationally fixed to the ring gear HO4 of the fourth planetary gearset RS4. The necessary for the actuation of the disk set of the clutch servo E may be axially displaceably mounted, for example, on said inner disk carrier of the clutch E and then rotates constantly with speed of the shaft 7 , However, it can also be provided that the servo device of the clutch E is disposed within the cylindrical space formed by the outer disk carrier of the clutch E, that the servo device of the clutch E is mounted axially displaceably on this outer disk carrier of the clutch E and then constantly with rotational speed of the shaft 5 rotates. To compensate for the rotational pressure of its rotating pressure chamber, the servo device of the clutch E in a known manner have a dynamic pressure compensation.

How out 1 Furthermore, it can be seen that the clutch C adjoins axially on the side of the clutch E, which faces away from the second planetary gearset RS2 and faces the third planetary gearset RS3. In this case, the outer disk carrier of the clutch C forms a portion of the shaft 5 of the transmission and on the one hand on its side facing the second planetary gear set RS2 (via the outer disc carrier of the clutch E) with the coupled web ST2 of the second planetary gearset RS2 and on the other hand on its second planetary gearset RS2 side facing the sun gear SO3 of the third planetary gear set RS3 rotationally connected , An inner disk carrier of the clutch C forms a portion of the shaft 1 of the transmission and is rotationally connected to the web ST4 of the fourth planetary gearset RS4 and to the drive shaft AN. The necessary for the actuation of the disk set of the clutch C servo can be axially displaceably mounted, for example, on the inner disk carrier of the clutch C and then rotates constantly with speed of the shaft 1 or the drive shaft AN. However, it can also be provided that the servo device of the clutch C is arranged within the cylinder space formed by the outer disk carrier of the clutch C, that the servo device of the clutch C is mounted axially displaceably on this outer disk carrier of the clutch C and then constantly with rotational speed of the shaft 5 rotates. To compensate for the rotational pressure of its rotating pressure chamber, the servo device of the clutch C in a known manner have a dynamic pressure compensation.

When a favorable for the use of identical parts design is provided by way of example that the disk packs of the two adjacent couplings C, E arranged on the same diameter are. In manufacturing technology advantageously can for the two adjacent clutches C, E also a common one-piece Be provided outer disk carrier.

In one of 1 Deviating structural design, for example, but also be provided that the disk sets of the two clutches C, E are spatially arranged radially superimposed. Is this the disk set of the clutch E spatially at least partially arranged radially over the disk set of the clutch C, so is a common for both clutches C, E plate carrier suitably for the (radially outer) clutch E as an inner disk carrier and for the (radially inner) Form coupling C as an outer disk carrier and to connect on the third planetary gear set RS3 side facing the disk sets C, E with the coupling shaft which connects the coupled web ST2 and the sun gear SO3 together. If, on the other hand, the disk set of the clutch C is spatially arranged at least partially radially above the disk set of the clutch E, a disk carrier common to both clutches C, E is expediently for the (radially outer) clutch C as the inner disk carrier and for the (radially inner) clutch E form as an outer disk carrier and on the side facing the second planetary gearset RS2 side of the disk sets C, E connect to the coupling shaft, which connects the coupled web ST2 and the sun gear SO3 together.

How out 1 Furthermore, as can be seen, the clutch D is arranged spatially adjacent to the third planetary gearset RS3. In this case, an inner disk carrier of the clutch D forms a portion of the shaft 8th of the transmission and is rotationally connected to the ring gear HO2 of the second planetary gear set RS2. The shaft overreaches 8th the second planetary gear set RS2 and the two clutches C, E in the axial direction completely. An outer disc carrier of the clutch D forms a portion of the shaft 2 of the transmission and is rotationally fixed on the side facing the third planetary gear set RS3 side of the disk set of the clutch D to the web ST3 of the third planetary gearset RS3, said web ST3 is in turn connected to the output shaft AB of the transmission. To compensate for the rotational pressure of the rotating pressure chamber necessary for the actuation of the disk set of the clutch D servo device of the clutch D in known manner have a dynamic pressure compensation. In this case, the servo device of the clutch D, for example be arranged within the cylinder space, through the outer disk carrier of the clutch D or through the shaft 2 is formed on the outer disk carrier of the clutch D or on the shaft 2 be axially displaceable and then rotates constantly with speed of this wave 2 , In this case, the servo device of the clutch D, the required pressure and lubricant can be fed in a favorable manner via the web ST3. But it can also be provided that the servo device of the clutch D on said inner disk carrier of the clutch D or on the shaft 8th is mounted axially displaceable and constantly with speed of the shaft 8th In this case, the pressure space of the servo device of the clutch D can be arranged, for example, near the disk set of the clutch D or near the third planetary gearset RS3, in which case the servo device of the clutch D the required pressure and lubricant on the rotating shaft 5 must be supplied. In yet another embodiment, the pressure chamber of a on the inner disk carrier of the clutch D or on the shaft 8th axially displaceably mounted servo device of the clutch D in a range axially between the planetary gear sets RS2 and RS4 be arranged near the second planetary gearset RS2, but also in a region axially between the planetary gear sets RS4 and RS1.

It is readily apparent to those skilled in the art that the spatial arrangement of the clutch D within the transmission housing GG comparatively simple compared to the in 1 illustrated embodiment is modifiable. So can in one of 1 deviating configuration, for example, be provided that the disk set of the clutch D spatially seen in a region radially above the disk sets of the other two clutches C, E is arranged. In yet another embodiment, the clutch D may, for example, at least partially be disposed in a region radially above the second planetary gearset RS2, in which case a portion of the shaft 2 the two clutches C, E in the axial direction at least largely overlaps. In a further embodiment, for example, be vorgese hen that the clutch D spatially in a range axially between the second and fourth planetary gear set RS2, RS4 is arranged, in which case a portion of the shaft 2 the two clutches C, E in the axial direction completely and the second planetary gearset RS2 in the axial direction at least partially overlaps.

How out 1 as can be seen, the shaft overlaps 6 as a coupling shaft between the two ring gears HO1, HO3 of the first and third planetary gear sets RS1, RS3 in their axial course, the fourth and second planetary gearset RS4, RS2 and the clutches E, C, D completely.

It should be expressly understood that the above-written arrangement of the three clutches C, D, E is to be regarded as exemplary only. If necessary, the skilled person will also modify this exemplary spatial arrangement of the three clutches C, D, E, numerous suggestions for this purpose are, for example, the generic DE 10 2005 002 337 A1 and their international subsequent application can be removed. For example, without the component structure of the in 1 Substantially to be changed - provided that the disk set of the clutch E spatially is at least partially disposed radially above the disk set of the clutch C, that is so that the clutch E spatially seen at least partially radially disposed over the clutch C.

In the following, constructive meaningful thrust bearing concepts for the in 1 received multistage transmission. It should be mentioned that the thrust bearing concept also has an effect on the structural design of the teeth of the planetary gear sets, which is the expert, especially for acoustic reasons usually run as helical gears. In this case, the expert will interpret the helix angle, tooth flank corrections and helical direction in a conventional manner, taking into account the present on the respective teeth Verzahnungskräfte and also taking into account the thrust bearing concept of the transmission. In this respect, the thrust bearing concept for the gear design is of major importance.

2 now shows an exemplary first thrust bearing concept for the in 1 illustrated multistage transmission. In total, a total of eleven thrust bearings are provided by which the individual wheelset elements and plate carrier of the shift elements within the gear housing GG are fixed in the axial direction and supported. The exemplarily barrel-shaped transmission housing GG is closed on the drive side of the transmission by a housing-side housing wall designated GW to the outside, wherein the drive shaft AN centrally penetrates this housing wall GW. Of course, other housing forms are possible. The individual thrust bearings are designated L1 to L11, starting from the drive side of the transmission continuously ascending numbering.

It is provided that in the axial region between a gear housing fixed housing wall GW and the sun gear SO1 of the first planetary gearset RS1 a thrust bearing (L1) is provided in the range axially between the sun gears SO1, SO4 of the first and fourth planetary RS1, RS4 four thrust bearings (L2 , L3, L4, L5) are provided in the area axially between the sun gears SO4, SO2 of the fourth and second planetary gearset RS4, RS2 two thrust bearings (L6, L7) are provided in the region axially between the sun gears SO2, SO3 of the second and third planetary gearset RS2, RS3 two thrust bearings (L8, L9) are provided and in the area axially between the sun gear SO3 of the third planetary gearset RS3 and a transmission housing wall two thrust bearings (L10, L11) are provided.

How out 2 As can be seen, the first thrust bearing L1 is arranged axially between the gear housing fixed housing wall GW and a radial portion of the inner disk carrier of the brake A, which in turn a portion of the shaft 3 forms. The second thrust bearing L2 is axially between the sun gear SO1 of the first planetary gearset RS1, which is also a portion of the shaft 3 forms, and that web plate of the web ST1 of the first planetary gear set RS1 which faces the fourth planetary gear set RS4 and a portion of the shaft 4 forms. The third thrust bearing L3 is located axially between said web plate of the web ST1 facing the fourth planetary gearset RS4 and a portion of the shaft 6 arranged, which extends axially adjacent to the web ST1 approximately parallel to the web ST1 in the radial direction and is connected on its side facing the first planetary gearset RS1 side with the ring gear HO1 for torque transmission. The fourth thrust bearing L4 is axially between said radial portion of the shaft 6 and a section of the shaft 8th arranged, which extends axially adjacent to the fourth planetary gearset RS4 approximately parallel to the web ST4 in the radial direction and is connected on its side facing the second planetary gearset RS2 side with the ring gear HO2 for torque transmission. The fifth thrust bearing L5 is axially between said radial portion of the shaft 8th and the sun gear SO4 of the fourth planetary gear set RS4, which also includes a portion of the shaft 3 forms and is connected in the manner of a sun shaft with the sun gear SO1 and the inner disk carrier of the brake A for transmitting torque. In this case, this sun wave extends spatially concentrically within the axial bearing arrangement formed from the first five axial bearings L1 to L5.

How out 2 Furthermore, the sixth thrust bearing L6 is arranged axially between the sun gear SO4 of the fourth planetary gearset RS4 and that web plate of the web ST4 of the fourth planetary gearset RS4, which faces the second planetary gearset RS2 and in the region axially between the planetary gearset RS4 and RS2 as a section of the wave 1 of the transmission is connected to the drive shaft AN for torque transmission. The seventh axial bearing L7 is axially between said web plate of the web ST4 and a portion of the shaft 7 arranged, which extends axially between the web ST4 and the second planetary gearset RS2 approximately parallel to the web ST4 in the radial direction and on its fourth planetary gearset RS4 side facing the ring gear HO4 and on its second planetary gearset RS2 side facing the sun gear SO2 is connected for torque transmission.

How out 2 Further, the eighth thrust bearing L8 is disposed axially between a radially extending portion of the inner disk carrier of the clutch E which axially adjoins the second planetary gearset RS on the side facing the third planetary gearset RS3 and a radially extending portion of the inner disk carrier of the clutch C which in turn is arranged axially next to the inner disk carrier of the clutch E on its side facing the third planetary gear set RS3. The inner disk carrier of the clutch E forms a portion of the shaft 7 of the transmission and is connected on its side facing the second planetary gearset RS2 side with its sun gear SO2 for torque transmission. The inner disk carrier of the clutch C forms a portion of the shaft 1 of the transmission and is connected on its second planetary gearset RS2 side facing the drive shaft AN of the transmission for torque transmission. The ninth thrust bearing L9 is axially between said radial portion of the inner disk carrier of the clutch C and a radial portion of the shaft 5 arranged on the one hand on its third planetary gearset RS3 side facing the sun gear SO3 and on the other hand on its second planetary gearset RS2 side facing in the manner of a clutch cylinder with the outer disk carrier of the clutch C for torque transmission. In this case, the outer disk carrier of the clutch C is connected to the outer disk carrier of the clutch E and via this outer disk carrier of the clutch E to the web ST2 of the second planetary gear set RS2 for torque transmission.

The tenth thrust bearing L10 is axially between the sun gear SO3 of the third planetary gearset RS3, which is a portion of the shaft 5 forms of the gear, and that web plate of the web ST3 of the third planetary gear set RS3, which is opposite to the second planetary gear set RS2 and the output side housing wall of the transmission housing GG faces. This called web plate of the bridge ST3 is also called section of the shaft 2 of the transmission connected to the output shaft AB for torque transmission. Finally, the eleventh thrust bearing L11 is located axially between the designated web plate of the web ST4 and the output-side housing wall of the gearbox GG assigns.

In summary, this can be done in 2 illustrated first thrust bearing concept are described by the following thrust bearing assembly, wherein the numbers denote the respective shafts of the transmission:
"GW-L1-3-L2-4-L3-6-L4-8-L5-3-L6-1-L7-7-L8-1-L9-5-L10-2-L11-GG".

3 shows an exemplary second thrust bearing concept for the in 1 illustrated multistage transmission, derived from the in 2 illustrated first thrust bearing concept. In total, a total of twelve thrust bearings are now provided by which the individual wheelset elements and plate carrier of the switching elements within the gear housing GG are fixed in the axial direction and supported. The individual thrust bearings are designated L1 to L12, starting from the drive side of the transmission continuously ascending numbering.

there It is now envisaged that in the area axially between a housing wall fixed to the transmission housing GW and the sun gear SO1 of the first planetary gear set RS1 a thrust bearing (L1) is provided, in the area axially between the sun gears SO1, SO4 of the first and fourth planetary gear set RS1, RS4 three Axial bearings (L2, L3, L4) are provided, in the range between axially the sun gears SO4, SO2 of the fourth and second planetary gear set RS4, RS2 four thrust bearings (L5, L6, L7, L8) are provided and in the Axially between the sun gears SO2, SO3 of the second, third planetary gearset RS2, RS3 two thrust bearings (L9, L10) provided are and in the area axially between the sun gear SO3 of the third Planetary wheel set RS3 and a transmission housing wall two Thrust bearing (L11, L12) are provided.

How out 3 can be seen, the arrangement of the thrust bearings L1, L2 and L3 is made 2 unchanged. Across from 2 are in the range axially between the two sun gears SO1 and SO4 in 3 only three thrust bearings - so a thrust bearing less - provided. Accordingly, the fourth thrust bearing L4 is according to 3 axially between the radial portion of the shaft 6 , which extends axially adjacent to the web ST1 in the radial direction and is connected on its side facing the first planetary gearset RS1 side with its ring gear for transmitting torque, and arranged the sun gear SO4 of the fourth planetary gear set RS4. In the 3 Axial bearings designated L5 and L6 correspond to those in 2 Axial bearings designated L6 and L7.

How out 3 Further, the seventh thrust bearing L7 is axially between the radial portion of the shaft 7 which extends adjacent to the drive remote and connected to the drive shaft AN web plate of the web ST4, and a radial portion of the shaft 8th arranged, which extends in the manner of a Hohlradträgers axially adjacent to the second planetary gearset RS2 on the fourth planetary gearset RS4 side facing and is connected on its side facing the planetary gearset RS2 side with its ring gear HO2. The eighth thrust bearing L8 is axially between said radial portion of the shaft 8th and the sun gear SO2 of the second planetary gear set RS2.

How out 3 further apparent, correspond to in 3 with L9 to L12 designated thrust bearing the in 2 Axial bearings designated L8 to L11.

In summary, this can be done in 3 illustrated second thrust bearing concept are described by the following thrust bearing assembly, wherein the numbers denote the respective shafts of the transmission:
"GW-L1-3-L2-4-L3-6-L4-3-L5-1-L6-7-L7-8-L8-7-L9-1-L10-5-L11-2-L12-GG ".

4 shows an exemplary third thrust bearing concept for the in 1 illustrated multistage transmission, derived from the in 3 illustrated second thrust bearing concept. In total, a total of twelve thrust bearings are provided by which the individual wheelset elements and disk carrier of the shift elements within the gearbox GG are fixed and supported as seen in the axial direction. The individual thrust bearings are designated L1 to L12, starting from the drive side of the transmission continuously ascending numbering.

there It is now envisaged that in the area axially between a housing wall fixed to the transmission housing GW and the sun gear SO1 of the first planetary gearset RS1 three thrust bearings (L1, L2, L3) are provided, in the area axially between the sun gears SO1, SO4 of the first and fourth planetary gearset RS1, RS4 no Thrust bearing is provided in the area axially between the sun gears SO4, SO2 of the fourth and second planetary gear set RS4, RS2 five Axial bearings (L4, L5, L6, L7, L8) are provided, in the range axial between the sun gears SO2, SO3 of the second and third Planetary gear set RS2, RS3 two thrust bearings (L9, L10) provided are and in the area axially between the sun gear SO3 of the third Planetary wheel set RS3 and a transmission housing wall two Thrust bearing (L11, L12) are provided.

The first thrust bearing L1 is - as in 3 - Arranged axially between the gear housing fixed housing wall GW and a radial portion of the inner disk carrier of the brake A, which turn a section of the shaft 3 forms. The second axial bearing L2 is arranged axially between the housing wall GW facing web plate of the web ST1 of the first planetary gearset RS1, said web plate a portion of the shaft 4 forms. The third thrust bearing L3 is arranged axially between said housing-wall web plate of the web ST1 and the sun gear SO1 of the first planetary gearset RS1, wherein this sun gear SO1 in turn a portion of the shaft 3 forms.

This in 4 denoted by L4 fourth thrust bearing corresponds to the in 3 L5 designated fifth thrust bearing and is arranged axially between the sun gear SO4 of the fourth planetary gear set RS4 and the web plate of the web ST4 of the fourth planetary gearset RS4, which is the first planetary gearset ST1 and axially between the Planetenradsätzens RS4 and RS2 as a portion of the shaft 1 is connected to the drive shaft AN for torque transmission. This in 4 L5 designated fifth thrust bearing corresponds to the in 3 L6 is the sixth thrust bearing and is axially between said RS1-distal land of the web ST4 and a portion of the shaft 7 arranged, which extends axially between the web ST4 and the second planetary gearset RS2 in the radial direction and is connected on its fourth planetary gearset RS4 side facing the ring gear HO4 and on its second planetary gearset RS2 side facing the sun gear SO2 for torque transmission. This in 4 The sixth thrust bearing denoted by L6 is axially between said RS4-proximal radial portion of the shaft 7 and a section of the shaft 6 which, starting from the coupling shaft, which connects the ring gears HO1 and HO3 of the first and third planetary gear set for torque transmission and radially overlaps the fourth and second planetary gear set RS2, RS4 and the three clutches E, C and D in the axial direction, in Art a Hohlradträgers in the region axially between the planetary gear sets RS4 and RS2 extends radially inwardly. The seventh thrust bearing L7 is axially between said radial portion of the shaft 6 and a section of the shaft 8th arranged, which - as in 3 - Starting from the ring gear HO2 of the second planetary gearset RS2 axially adjacent to the planetary gearset RS2 on the fourth planetary gearset RS4 side facing radially inwardly extending. The eighth thrust bearing L8 is - as in 3 Axially between said radial portion of the shaft 8th and the sun gear SO2 of the second planetary gear set RS2.

How out 4 further apparent, the arrangement of the other four thrust bearings L9 to L12 is made 3 unchanged.

In summary, this can be done in 4 illustrated third thrust bearing concept are described by the following thrust bearing assembly, wherein the numbers denote the respective shafts of the transmission:
"GW-L1-3-L2-4-L3-3-L4-1-L5-7-L6-6-L7-8-L8-7-L9-1-L10-5-L11-2-L12-GG ".

5 shows an exemplary fourth thrust bearing concept for the in 1 illustrated multistage transmission. In total, a total of ten axial bearings and two axially acting thrust washers are provided by which the individual wheelset elements and plate carrier of the switching elements within the gear housing GG are fixed in the axial direction and supported. The individual thrust bearings are designated L1 to L10, starting from the drive side of the transmission continuously ascending numbering. The two thrust washers are labeled A1 and A2. Of course, these thrust washers usually made of bearing metal can also be replaced by thrust bearings in Wälzkörperausführung.

Starting from the in 4 shown third thrust bearing concept is in the Axiallagerkonzept according to 5 modified the axial support of the transmission components in the area of the adjacently arranged planetary gear sets RS1 and RS4. According to 5 It is provided that in the area axially between a gear housing fixed housing wall GW and the first planetary gearset RS1 a thrust bearing (L1) and a thrust washer (A1) are provided, in the region axially between the webs ST1, ST4 of the first and fourth planetary RS1, RS4 a thrust washer (A2) is provided in the region axially between the sun gears SO4, SO2 of the fourth and second planetary RS4, RS2 five thrust bearings (L2, L3, L4, L5, L6) are provided, in the region axially between the sun gears SO2, SO3 of the second and the third planetary gearset RS2, RS3 two thrust bearings (L7, L8) are provided and in the region axially between the sun gear SO3 of the third planetary gearset RS3 and a transmission housing wall two thrust bearings (L9, L10) are provided.

As in 5 As can be seen, the first axial bearing L1 forms the first axial support element within the transmission housing GG, viewed from the drive side of the transmission, and is, as in FIG 4 - Axially disposed between the gear housing fixed housing wall GW and a radial portion of the inner disk carrier of the brake A, which in turn a portion of the shaft 3 forms. As a second axial support member, the first thrust washer A1 is provided, which is arranged axially between said radial portion of the inner disk carrier of the brake A and the housing wall GW facing web plate of the web ST1 of the first planetary gearset RS1. As a third axial Supporting the second thrust washer A2 is provided which axially between the housing wall facing away from the housing wall GW web of the web ST1 of the first planetary gearset RS1 and the housing wall GW facing web plate of the web ST4 of the fourth planetary gearset RS4 arranged.

As in 5 further seen, all other axial support elements within the transmission housing GG of the thrust bearing according to 4 accepted. Thus, the second thrust bearing L2 forms the fourth axial support element and the tenth thrust bearing L10 forms the twelfth axial support element. It can easily be seen that the arrangement of the in 5 with L2 to L10 designated nine thrust bearing of the arrangement of in 4 corresponds to L4 to L12 designated thrust bearings.

In summary, this can be done in 5 illustrated fourth thrust bearing concept are described by the following thrust bearing assembly, wherein the numbers denote the respective shafts of the transmission:
"GW-L1-3- (A1-4-A2 parallel to L2) -1-L3-7-L4-6-L5-8-L6-7-L7-1-L8-5-L9-2-L10- GG ".

6 shows an exemplary fifth thrust bearing concept for the in 1 illustrated multistage transmission, based on the in 5 illustrated fourth thrust bearing concept. In total, here again a total of ten axial bearings and two axially acting thrust washers are provided by which the individual wheelset elements and plate carrier of the switching elements within the gear housing GG are fixed in the axial direction and supported. The individual thrust bearings are designated L1 to L10, starting from the drive side of the transmission continuously ascending numbering. The two thrust washers are labeled A1 and A2. Of course, these thrust washers usually made of bearing metal can be replaced by thrust bearings in Wälzkörperausführung here.

at the fifth thrust bearing concept is provided that in the field axially between a gear housing fixed housing wall GW and the first planetary gearset RS1 a thrust bearing (L1) and a thrust washer (A1), in the area axially between the webs ST1, ST4 of the first and fourth planetary gear set RS1, RS4 a thrust washer (A2) is provided, in the area axially between the sun gears SO4, SO2 of the fourth and second planetary gear set RS4, RS2 four Axial bearings (L2, L3, L4, L5) are provided, in the area between axially the sun gears SO2, SO3 of the second and third planetary gear set RS2, RS3 four thrust bearings (L6, L7, L8, L9) are provided and in Range axially between the sun gear SO3 of the third planetary gear set RS3 and one transmission case wall two thrust bearings (L10, L11) are provided.

The difference between the fourth thrust bearing concept according to 5 and the fifth thrust bearing concept according to FIG 6 consists of at which point in Axiallagerverbund the shaft 8th or the ring gear HO2 of the second planet carrier is arranged.

Out 6 It is easy to see that the axial support of the shaft 8th no longer seen in the axial direction near the ring gear HO2 on the planetary gearset RS4 side facing the planetary gearset RS2, but now seen in the axial direction near the disk set of the clutch D axially adjacent to the planetary gearset RS3. Thus, the arrangement of the first four thrust bearings L1 to L4 and the two thrust washers A1 and A2, as in 6 provided, identical to 5 , By laying the radial section of the shaft 8th could in 6 the in 5 provided axial composite with the designated there with L5 and L6 two thrust bearings are replaced by a single thrust bearing, which in 6 denoted by L5. This in 6 denoted by L6 sixth thrust bearing corresponds to the in 5 denoted by L7 seventh thrust bearing. This in 6 denoted by L7 seventh thrust bearing corresponds to the in 5 eighth thrust bearing designated L8. This in 6 Tenth axial bearing designated L10 corresponds to the one in FIG 5 ninth thrust bearing designated L9. This in 6 The eleventh thrust bearing denoted by L11 corresponds to the one in FIG 5 Tenth thrust bearing designated L10. According to 6 is provided that the axial support of the shaft 8th spatially seen in the area axially between the radial portion of the shaft 5 , against which the thrust bearing 17 axially supported and which is connected to the outer disk carrier of the clutch C, and the sun gear SO3 of the third planetary gear set RS3 is incorporated in the thrust bearing assembly of the transmission. For this purpose, the two thrust bearings L8, L9 are provided, which are arranged on both sides of a radial portion of the inner disk carrier of the clutch D, which also includes a portion of the shaft 8th forms. In this case, the eighth thrust bearing L8 is axially between said radial portion of the shaft 5 and the said radial portion of the inner disk carrier of the clutch D arranged on the inner disk carrier of the clutch D so RS2-sided. The ninth thrust bearing L9 is arranged axially between said radial portion of the inner disk carrier of the clutch D and the sun gear SO3 of the third planetary gearset RS3, relative to the inner disk carrier of the clutch D so RS3 side.

In summary, this can be done in 6 illustrated fifth Axiallagerkonzept be described by the following thrust bearing assembly, wherein the numbers denote the respective shafts of the transmission:
"GW-L1-3- (A1-4-A2 parallel to L2) -1-L3-7-L4-6-L5-7-L6-1-L7-5-L8-8-L9-5-L10- 2-L1 1-GG ".

7 Finally, an exemplary sixth thrust bearing concept for the in 1 illustrated multistage transmission, based on the in 4 illustrated third thrust bearing concept. In total, a total of twelve thrust bearings are provided by which the individual wheelset elements and disk carrier of the shift elements within the gearbox GG are fixed and supported as seen in the axial direction. The individual thrust bearings are designated L1 to L12, starting from the drive side of the transmission continuously ascending numbering.

there It is now envisaged that in the area axially between a housing wall fixed to the transmission housing GW and the sun gear SO1 of the first planetary gearset RS1 three thrust bearings (L1, L2, L3) are provided, in the area axially between the sun gears (SO1, SO4) of the first and fourth planetary gear set RS1, RS4 no Thrust bearing is provided in the area axially between the sun gears SO4, SO2 of the fourth and second planetary gear set RS4, RS2 two Axial bearings (L4, L5) are provided, in the area axially between the Sun gears SO2, SO3 of the second and third planetary gear set RS2, RS3 four thrust bearings (L6, L7, L8, L9) are provided and in Range axially between the sun gear SO3 of the third planetary gear set RS3 and one transmission case wall three thrust bearings (L10, L11, L12) are provided.

The difference between the third thrust bearing concept according to 4 and the sixth thrust bearing concept according to 7 is at which point in Axiallagerverbund the coupling shafts 6 and 8th are arranged. Out 6 It is easy to see that the axial support of the shaft 6 no longer seen in the axial direction approximately centrally between the two adjacent planetary gear sets RS4 and RS2, but now seen in the axial direction on the transmission output side facing the planetary gear set RS3. Out 6 is still easy to see that the axial support of the shaft 8th no longer seen in the axial direction near the ring gear HO2 on the planetary gearset RS4 side facing the planetary gearset RS2, but now seen in the axial direction near the disk set of the clutch D axially adjacent to the planetary gearset RS3.

Thus, the arrangement of the first five thrust bearings L1 to L5 is as in FIG 7 provided, identical to 4 , By laying the for axial support of the waves 6 and 8th provided radial sections omitted in 7 the in 4 intended axial bond with the designated there with L6, L7 and L8 three thrust bearings. This in 7 denoted by L6 sixth thrust bearing corresponds to the in 4 Axial bearings designated L9. This in 7 denoted by L7 seventh thrust bearing corresponds to the in 4 Axial bearings designated L10. This in 7 Tenth axial bearing designated L10 corresponds to the one in FIG 4 designated with L11 thrust bearing.

For axial support of the shaft 8th , which according to the transmission scheme, the ring gear HO2 of the second planetary gearset RS2 connects with a plate carrier of the clutch D is, according to 7 - as well as in 6 - Provided that the inner disk carrier of the clutch D as a section of the shaft 8th is formed, which extends from the disk set of the clutch D radially inwardly, and that on both sides of this radial portion of the inner disk carrier of the clutch D each have a thrust bearing L8, L9 is arranged. In this case, the eighth thrust bearing L8 is axially between said radial portion of the shaft 5 and the said radial portion of the inner disk carrier of the clutch D arranged on the inner disk carrier of the clutch D so RS2-sided. The ninth thrust bearing L9 is arranged axially between said radial portion of the inner disk carrier of the clutch D and the sun gear SO3 of the third planetary gearset RS3, relative to the inner disk carrier of the clutch D so RS3 side. Thus, the axial support of the shaft 8th spatially seen in the area axially between the radial portion of the shaft 5 against which the thrust bearing L7 is axially supported and which is connected to the outer disk carrier of the clutch C, and the sun gear SO3 of the third planetary gear set RS3 incorporated into the thrust bearing assembly of the transmission.

For axial support of the coupling shaft 6 , which connects the ring gears HO1 and HO3 of the two planetary gear sets RS1 and RS4 according to the wheelset scheme, is according to 7 provided that starting from the ring gear HO3 on the side facing away from the clutch D of the third planetary gear set RS3, a portion of the shaft 6 extends radially inwardly approximately parallel to the web ST3, and that on both sides of this radial portion of the shaft 6 in each case a thrust bearing L11, L12 is arranged. In this case, the eleventh thrust bearing L11 is located axially between the driven-side web plate of the web ST3 of the third planetary gearset RS3, which also includes a portion of the shaft 2 of the transmission, and said radial portion of the shaft 6 whereas the twelfth thrust bearing L12 extends axially between said radial portion of the shaft 6 and the transmission housing wall is arranged. Thus, the axial support of the shaft 6 spatially seen on the side facing away from the other Planetenradsätzen side of the third planetary gear set RS3, incorporated axially between the web ST3 and the gear housing wall in the thrust bearing assembly of the transmission.

In summary, this can be done in 7 illustrated sixth Axiallagerkonzept be described by the following thrust bearing assembly, wherein the numbers denote the respective shafts of the transmission:
"GW-L1-3-L2-4-L3-3-L4-1-L5-7-L6-1-L7-5-L8-8-L9-5-L10-2-L11-6-L12-GG ".

At It is expressly stated that all previously discussed in detail thrust bearing concepts mutatis mutandis to the following other embodiments for a multistage transmission according to the invention are transferable.

Based on the consideration that the clutch E as the fifth switching element of the transmission in the switched or closed state blocks the second planetary gear set RS2, two other possibilities are shown in the following two embodiments for a multistage transmission according to the invention, said second planetary gear set RS2 by means of said clutch E to lock. 8th shows a second embodiment and 9 a third embodiment of a multi-stage transmission according to the first inventive solution, again in a simplified schematic representation, both based on the previously based 1 explained in detail first embodiment.

This in 8th schematically illustrated transmission scheme - as a second embodiment of a multi-speed transmission according to the first inventive solution - differs from the in 1 shown multistage transmission mainly by the fact that the clutch E now in the power flow between the shaft 7 and the wave 8th is arranged. In the switched or closed state, the clutch E now connects sun gear SO2 and ring gear HO2 of the planetary gear set RS2 with one another.

Another difference to the transmission according to 1 consists in the spatial arrangement of the clutch E. In the multi-stage transmission according to 8th the clutch E spatially seen (by way of example) in a range axially between the fourth planetary gearset RS4 and the second planetary gearset RS2 arranged, while axially immediately adjacent to the second planetary gearset RS2. In this case, the disk set of the clutch E is arranged on a comparatively large diameter in the region of the ring gear HO2 of the second planetary gearset RS2, wherein an outer disk carrier of the clutch E is connected rotationally fixed with this ring gear HO2. A simplification in 3 not shown servo device for actuating the disk set of the clutch E can be mounted axially displaceably on the inner disk carrier of the clutch E and then always rotates at rotational speed of the shaft 7 of the transmission, wherein the servo device in this case, the required pressure and lubricant on the rotating shaft 1 or via the rotating drive shaft AN must be supplied.

Deviating from 8th can be provided in another structural configuration of the transmission, for example, that the clutch E is spatially arranged in a range axially between the second planetary gearset RS2 and the third planetary gearset RS3, while axially directly adjacent to the second planetary gearset RS2, similar to the spatial arrangement of Clutch E in 1 ,

This in 9 schematically illustrated transmission scheme - as a third embodiment of a multi-speed transmission according to the first inventive solution - differs from the in 1 shown multistage transmission mainly by the fact that the clutch E now in the power flow between the shaft 5 and the wave 8th is arranged. In the switched or closed state, the clutch E now connects the coupled web ST2 and the ring gear HO2 of the planetary gear set RS2 with one another.

Another difference to the transmission according to 1 consists in the spatial arrangement of the clutch E. In the multi-stage transmission according to 9 is - similar to the transmission according to 8th - The clutch E spatially seen (for example) in a range axially between the fourth planetary gearset RS4 and the second planetary gear set RS2, while axially adjacent to the second planetary gear set RS2. In this respect, those in the context of the description of 8th mutatis mutandis made to the clutch construction also on the transmission according to 9 transferable.

10 shows a fourth embodiment of a multi-speed transmission according to the first inventive solution, wherein the transmission scheme is again shown schematically. Based on the transmission scheme according to 1 , that is different in 10 illustrated multistage transmission according to the invention of the in 1 shown gearbox substantially by a modified kinematic coupling of the clutch D, which forms the fifth switching element of the transmission. According to 10 is now provided that the clutch D in the frictional connection between the sixth and eighth wave 6 . 8th the transmission is arranged. In the switched or closed state, the clutch D now connects so the ring gear HO2 of the second planetary gearset RS2 with the verbun which interconnected ring gears HO1 and HO3 of the first and third planetary gearset RS1, RS3.

Corresponding to the opposite 1 modified kinematic connection of the clutch D also differs in 10 exemplified spatial arrangement of the clutch D of the in 1 illustrated embodiment. In 10 is provided by way of example that the disk set of the clutch D spatially is at least partially disposed in a region radially above the second planetary gearset RS2, wherein the inner disk carrier of the clutch D as a portion of the shaft 8th of the transmission and the ring gear HO2 of the second planetary gear set RS2 can be combined as a common component. A provided for actuating the disk set of the clutch D servo device is to simplify the illustration in 10 not shown and can be arranged on both sides of this disk set, so a pressure chamber of this servo device spatially seen for example lamella package in a range axially between the planetary gear sets RS4 and RS2 be arranged in another embodiment but also lamellenpaketfern in a range axially between the Planetenradsätzen RS1 and RS4, in yet another embodiment also near the planetary gear set RS3 in a range axially between the planetary gear sets RS2 and RS3.

The in the context of the description of 1 given suggestions for alternative spatial arrangements of the switching elements and planetary gear sets are of course also on the in 10 illustrated multistage transmission mutatis mutandis transferable.

Based on the consideration that the clutch E as the fifth switching element of the transmission in the switched or closed state blocks the second planetary gear set RS2, two other possibilities are shown in the following two embodiments for a multistage transmission according to the invention, said second planetary gear set RS2 by means of said clutch E to lock. 11 shows a fifth embodiment and 12 a sixth embodiment of a multi-speed transmission according to the first inventive solution, again in a simplified schematic representation, both based on the above based 10 explained first embodiment.

This in 11 schematically illustrated transmission scheme - as a fifth embodiment of a multi-speed transmission according to the first inventive solution - differs from the in 10 shown multistage transmission mainly by the fact that the clutch E now in the power flow between the shaft 7 and the wave 8th is arranged. In the switched or closed state, the clutch E now connects sun gear SO2 and ring gear HO2 of the planetary gear set RS2 with one another.

Another difference to the transmission according to 10 consists in the spatial arrangement of the clutches D and E. In the multi-stage transmission according to 11 the clutch E spatially seen (by way of example) in a range axially between the fourth planetary gearset RS4 and the second planetary gearset RS2 arranged, while axially immediately adjacent to the second planetary gearset RS2. In this case, the disk set of the clutch E is arranged radially below the disk set of the clutch D. Thus, a common plate carrier can be provided for the clutches D and E, which is rotationally connected to the ring gear HO2 of the second planetary gearset RS2.

The previously, for example, in the context of the description of 8th given suggestions for training and spatial arrangement of a provided for operating the disk set of the clutch E servo are also on the in 11 illustrated multistage transmission mutatis mutandis transferable as that, for example, in the context of the description of

10 given suggestions for training and spatial arrangement of a provided for operating the disk set of the clutch D servo device.

This in 12 schematically illustrated transmission scheme - as a sixth embodiment of a multi-speed transmission according to the first inventive solution - differs from that in 10 shown multistage transmission mainly by the fact that the clutch E now in the power flow between the shaft 5 and the wave 8th is arranged. In the switched or closed state, the clutch E now connects the coupled web ST2 and the ring gear HO2 of the planetary gear set RS2 with one another.

Another difference to the transmission according to 10 consists in the spatial arrangement of the clutch E. In the multi-stage transmission according to 12 is - similar to the transmission according to 11 - The clutch E spatially seen (for example) in a range axially between the fourth planetary gearset RS4 and the second planetary gear set RS2, while axially adjacent to the second planetary gear set RS2. In this respect, those in the context of the description of 11 mutatis mutandis made to the clutch construction also on the transmission according to 12 transferable.

13 now shows a schematic representation of a transmission scheme as a first Ausfüh Example of a multi-stage transmission according to the second inventive solution. The transmission in turn comprises a drive shaft AN, an output shaft AB, four planetary gear sets RS1, RS2, RS3, RS4 and five switching elements A, B, C, D, E. The four planetary gear sets RS1, RS2, RS3, RS4 are in this embodiment in axial Direction in turn in the order "RS1, RS4, RS2, RS3" coaxially arranged one behind the other, as an example of a favorable construction for a vehicle in the longitudinal axis of the vehicle built-in automatic transmission In contrast to the multi-speed transmissions according to the first inventive solution according to the second inventive solution provided that the two spatially adjacent planetary gear sets RS1 and RS4 are each designed as a simple plus planetary gear in Doppelplanetenbauweise, whereas the other two planetary gear sets RS2 and RS3 are each formed as a simple minus planetary gear sets.The nomenclature of the individual elements of the planetary gear sets are the same or derived from the previously v Thus, the ring gears of the four planetary gear sets RS1 to RS4 are designated HO1 to HO4, the sun gears with SO1 to SO4 and the webs ST1 to ST4. The inner planet gears of the two plus planetary gear sets RS1 and RS4 are denoted by PL1i and PL4i, the outer planetary gears by PL1a and PL4a. The planet gears of the two minus planetary gear sets RS2 and RS3 are denoted by PL2 and PL3.

As in 1 are also in 13 the switching elements A and B designed as disc brakes and the switching elements C, D and E as multi-plate clutches. With these five switching elements A to E, a selective switching of eight forward gears and at least one reverse gear can be realized, which will be explained later in more detail. The multi-speed transmission according to the invention has a total of at least eight rotatable shafts that with 1 to 8th are designated.

With regard to the kinematic 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 provided in the multi-speed transmission according to the second inventive solution: the ring gear HO4 of the fourth planetary gearset RS4 and the drive shaft AN are as a wave 1 constantly connected. The web ST3 of the third planetary gearset RS3 and the output shaft AB are as a shaft 2 constantly connected. The sun gears SO1, SO4 of the first and fourth planetary gear sets RS1, RS4 are as a shaft 3 constantly connected. The coupled web ST1 of the first planetary gear set RS1 forms the shaft 4 , The ring gear HO2 of the second planetary gearset RS2 and the sun gear SO3 of the third planetary gearset RS3 are as a shaft 5 constantly connected. The ring gear HO1 of the first planetary gearset RS1 and the ring gear HO3 of the third planetary gearset RS3 are a shaft 6 constantly connected. The sun gear SO2 of the second planetary gearset RS2 and the coupled bridge ST4 of the fourth planetary gearset RS4 are in the form of a shaft 7 constantly connected. The web ST2 of the second planetary gear set RS2 forms the shaft 8th of the transmission.

From the speed plan, the positive planetary gearset RS4 is according to 13 kinematically equivalent to the minus planetary gearset RS4 according to 1 , Analogous to this, the minus planetary gearset RS2 is according to 13 kinematically equivalent to the positive planetary gear set RS2 according to the speed plan forth 1 ,

With regard to the kinematic coupling of the five switching elements A to E to the waves thus described 1 to 8th of the transmission is in the multi-step transmission according to 13 The following is provided: The brake A as the first switching element of the transmission is in the power flow between the shaft 3 and the housing GG of the transmission arranged and sets in the closed or closed state, the interconnected sun gears SO1 and SO4 of the first and fourth planetary gear set RS1, RS4. The brake B as the second switching element of the transmission is in the power flow between the shaft 4 and the housing GG arranged and sets in the closed or closed state, the coupled web ST1 of the first planetary gear set RS1. The clutch C as the third switching element of the transmission is in the power flow between the shaft 1 and the wave 5 arranged and connects in the switched or closed state, the drive shaft AN with the ring gear HO2 of the second planetary gear set RS2 and with the sun gear SO3 of the third Pla netenradsatzes RS3. The clutch D as the fourth switching element of the transmission is in the power flow between the shaft 2 and the wave 8th arranged and connects in the switched or closed state the web ST2 of the second planetary gearset RS2 with the web ST3 of the third planetary gearset RS3 and thus the web ST2 also with the output shaft AB. The clutch E as fifth switching element of the transmission is in the power flow between the shaft 7 and the wave 8th arranged and connects in the closed or closed state sun gear SO2 and web ST2 of the second planetary gear set RS2 with each other.

In the in 13 illustrated embodiment, the first planetary gear set RS1 - as in 1 - The drive gear wheelset of the transmission and the third planetary gearset RS3 of the gearset close to the output of the transmission, wherein drive shaft AN and output shaft AB are arranged, for example coaxially to each other. The person skilled in the art can easily see that this transmission is without any special effort is modifiable such that drive and output shaft are no longer coaxial with each other, for example, parallel to the axis or at an angle to each other. In such an arrangement, the person skilled in the art will also arrange the drive of the transmission near the third planetary gear set RS3, that is to say on the side of the third planetary gear set RS3 facing away from the first planetary gear set RS1.

In principle, the spatial arrangement of the switching elements of the in 13 illustrated embodiment of a multi-speed transmission according to the invention within the transmission be arbitrary and is limited only by the dimensions and the outer shape of the gear housing GG. In this respect, the in 13 illustrated spatial arrangement of the switching elements A to E relative to each other and relative to the four planetary gear sets RS1 to RS4 expressly to be understood as exemplary only.

As in 13 easily seen, the spatial arrangement of the two multi-disc brakes A and B from the embodiment according to 1 and therefore need not be explained again. The spatial arrangement of the multi-plate clutch D is also from the embodiment according to 1 taken over, and therefore need not be explained again. The spatial arrangement of the two other multi-plate clutches E and C is similar to in 1 , but with according to the transmission scheme modified kinematic connection to the planetary gear set RS2. The clutch E provided for situational blocking of the planetary gearset RS2 directly adjoins it axially, here by way of example on the side of the second planetary gearset RS2 facing the third planetary gearset RS3. The clutch C is also arranged in the region axially between the planetary gear sets RS2 and RS3, wherein the disk set of the clutch C is here for example arranged axially between the disk sets of the clutches E and D. As a modification to this, it makes sense to either the disk set of the clutch C spatially seen radially over the disk set of the clutch E or E but completely to arrange the clutch E on the other side - ie on the fourth planetary gear set RS4 side - of the second planetary gearset RS2 ,

14 shows a second embodiment of a multi-speed transmission according to the second inventive solution, wherein the transmission scheme is again shown schematically and in the embodiment according to 13 based. Based on the consideration that the clutch E is provided to block the second planetary gearset RS2 when needed, is according to 14 provided that the clutch E in the power flow now between the shaft 5 and the wave 7 is arranged of the transmission and in the switched or closed state now ring gear HO2 and sun gear SO2 of the planetary gearset RS2 connects to each other.

15 shows a third embodiment of a multi-speed transmission according to the second inventive solution, the transmission scheme is again shown schematically and also in the embodiment according to 13 based. Again, starting from the consideration that the clutch E is provided to block the second planetary gearset RS2 when needed, is according to 15 provided that the clutch E in the power flow now between the shaft 5 and the wave 8th of the transmission is arranged and in the switched or closed state now ring gear HO2 and web ST2 of the planetary gearset RS2 connects to each other.

16 shows a fourth embodiment of a multi-speed transmission according to the second inventive solution, the transmission scheme is again shown schematically. Based on the transmission scheme according to 13 , that is different in 16 illustrated multistage transmission according to the invention of the in 13 shown gearbox substantially by a modified kinematic coupling of the clutch D, which forms the fifth switching element of the transmission. According to 16 is now provided that the clutch D in the frictional connection between the sixth and eighth wave 6 . 8th the transmission is arranged. In the switched or closed state, the clutch D now connects the web ST2 of the second planetary gearset RS2 with the interconnected ring gears HO1 and HO3 of the first and third planetary gearset RS1, RS3. In the 16 exemplary selected spatial arrangement of the five switching elements A to E is similar to the switching element arrangement of 11 , of course, taking into account the different kinematic connection of the clutches D and E to the planetary gearset RS2.

17 shows a fifth embodiment of a multi-speed transmission according to the second inventive solution, the transmission scheme is again shown schematically and in the embodiment according to 16 based. Based on the consideration that the clutch E is provided to block the second planetary gearset RS2 when needed, is according to 17 provided that the clutch E in the power flow now between the shaft 5 and the wave 7 is arranged of the transmission and in the switched or closed state now ring gear HO2 and sun gear SO2 of the planetary gearset RS2 connects to each other. The spatial arrangement of the five Schaltelemen te A to E according to 17 is derived from the switching element arrangement according to 16 , wherein the clutch E is now arranged axially to the second planetary gearset RS2 on its side facing the clutch C and the third planetary gearset RS3, similar to in FIG 14 ,

18 Finally, shows a sixth embodiment of a multi-speed transmission according to the second inventive solution, wherein the transmission scheme is again shown schematically and also in the embodiment according to 16 based. Again, starting from the consideration that the clutch E is provided to block the second planetary gearset RS2 when needed, is according to 18 provided that the clutch E in the power flow now between the shaft 5 and the wave 8th of the transmission is arranged and in the switched or closed state now ring gear HO2 and web ST2 of the planetary gearset RS2 connects to each other. In the 18 exemplary selected spatial arrangement of the five switching elements A to E is similar to that in 19 illustrated switching element arrangement, wherein the kinematic coupling of the inner disk carrier of the clutch E to the opposite 17 modified transmission kinematics has been adjusted.

19 now shows a schematic representation of a transmission scheme as a first embodiment of a multi-speed transmission according to the third inventive solution. The transmission in turn comprises a drive shaft AN, an output shaft AB, four planetary gear sets RS1, RS2, RS3, RS4 and five switching elements A, B, C, D, E. The four Planetenradsät ze RS1, RS2, RS3, RS4 are in this embodiment in axial direction in turn in the order "RS1, RS4, RS2, RS3" arranged coaxially one behind the other, as an example of a favorable construction for an automatic transmission installed in the longitudinal axis of the motor vehicle In contrast to the multi-speed transmissions according to the first and second inventive solution according to the third According to the invention, the two spatially adjacent planetary gear sets RS4 and RS2 are each designed as a simple plus planetary gear set in double planetary design, whereas the other two planetary gear sets RS1 and RS3 are each designed as simple minus planetary gear sets or derived from the nomenclature used previously. Thus, the ring gears of the four planetary gear sets RS1 to RS4 are designated by HO1 to HO4, the sun gears by SO1 to SO4 and the webs by ST1 to ST4. The inner planet wheels of the two plus planetary gear sets RS2 and RS4 are denoted by PL2i and PL4i, the outer planetary gears by PL2a and PL4a. The planet gears of the two minus planetary gear sets RS1 and RS3 are denoted by PL1 and PL3.

As in 1 are also in 19 the switching elements A and B designed as disc brakes and the switching elements C, D and E as multi-plate clutches. With these five switching elements A to E, a selective switching of eight forward gears and at least one reverse gear can be realized, which will be explained later in more detail. The multi-speed transmission according to the invention has a total of at least eight rotatable shafts that with 1 to 8th are designated.

With regard to the kinematic 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 provided in the multi-speed transmission according to the third inventive solution: the ring gear HO4 of the fourth planetary gearset RS4 and the drive shaft AN are as a wave 1 constantly connected. The web ST3 of the third planetary gearset RS3 and the output shaft AB are as a shaft 2 constantly connected. The sun gears SO1, SO4 of the first and fourth planetary gear sets RS1, RS4 are as a shaft 3 constantly connected. The ring gear HO1 of the first planetary gearset RS1 forms the shaft 4 , The coupled web ST2 of the second planetary gearset RS2 and the sun gear SO3 of the third planetary gearset RS3 are as a shaft 5 constantly connected. The web ST1 of the first planetary gearset RS1 and the ring gear HO3 of the third planetary gearset RS3 are designed as a shaft 6 constantly connected. The sun gear SO2 of the second planetary gearset RS2 and the coupled bridge ST4 of the fourth planetary gearset RS4 are in the form of a shaft 7 constantly connected. The ring gear HO2 of the second planetary gear set RS2 forms the shaft 8th ,

From the speed plan, the minus planetary gearset RS1 is according to FIG 19 kinematic equivalent to the plus planetary gear set RS1 according to 1 , Analogously, the positive planetary gearset RS4 is according to 19 kinematically equivalent to the minus planetary gearset RS4 according to FIG 1 ,

With regard to the kinematic coupling of the five switching elements A to E to the waves thus described 1 to 8th of the transmission is in the multi-step transmission according to 19 The following is provided: The brake A as the first switching element of the transmission is in the power flow between the shaft 3 and the housing GG of the transmission arranged and sets in the closed or closed state, the interconnected sun gears SO1 and SO4 of the first and fourth planetary gear set RS1, RS4. The brake B as the second switching element of the transmission is in the power flow between the shaft 4 and the Ge housing GG arranged and sets in the switched or closed state, the ring gear HO1 of the first planetary gear set RS1. The clutch C as the third switching element of the transmission is in the power flow between the shaft 1 and the wave 5 arranged and connects in the closed or ge closed state, the drive shaft AN with the coupled web ST2 of the second planetary gearset RS2 and with the sun gear SO3 of the third planetary gearset RS3. The clutch D as the fourth switching element of the transmission is in the power flow between the shaft 2 and the wave 8th arranged and connected in the closed or closed state, the ring gear HO2 of the second planetary gearset RS2 with the web ST3 of the third planetary gear set RS3 and thus the ring gear HO2 also with the output shaft AB. The clutch E as fifth switching element of the transmission is in the power flow between the shafts 5 and 7 arranged and connects in the closed or closed state, the sun gear SO2 and the coupled bridge ST2 of the second planetary gear set RS2 with each other.

In the in 19 illustrated embodiment, the first planetary gear set RS1 - as in 1 - The drive gear wheelset of the transmission and the third planetary gearset RS3 of the gearset close to the output of the transmission, wherein drive shaft AN and output shaft AB are arranged, for example coaxially to each other. It is readily apparent to those skilled in the art that this transmission can be modified without special effort in such a way that the input and output shafts are no longer arranged coaxially with one another, for example parallel to the axis or at an angle to one another. In such an arrangement, the person skilled in the art will also arrange the drive of the transmission near the third planetary gear set RS3, that is to say on the side of the third planetary gear set RS3 facing away from the first planetary gear set RS1.

In principle, the spatial arrangement of the switching elements of the in 19 illustrated embodiment of a multi-speed transmission according to the invention within the transmission be arbitrary and is limited only by the dimensions and the outer shape of the gear housing GG. In this respect, the in 19 illustrated spatial arrangement of the switching elements A to E relative to each other and relative to the four planetary gear sets RS1 to RS4 expressly to be understood as exemplary only. As in

19 readily apparent, the spatial arrangement of the five switching elements A to E from the embodiment according to 1 and therefore need not be explained again.

20 shows a second embodiment of a multi-speed transmission according to the third inventive solution, wherein the transmission scheme is again shown schematically and in the embodiment according to 19 based. Based on the consideration that the clutch E is provided to block the second planetary gearset RS2 when needed, is according to 20 provided that the clutch E in the power flow now between the shaft 5 and the wave 7 is arranged of the transmission and in the switched or closed state now ring gear HO2 and sun gear SO2 of the planetary gearset RS2 connects to each other. The spatial arrangement of the five switching elements A to E according to 20 is exemplary 8th accepted.

21 shows a third embodiment of a multi-speed transmission according to the third inventive solution, wherein the transmission scheme is again shown schematically and also in the embodiment according to 19 based. Again, starting from the consideration that the clutch E is provided to block the second planetary gearset RS2 when needed, is according to 21 provided that the clutch E in the power flow now between the shaft 5 and the wave 8th of the transmission is arranged and in the switched or closed state now ring gear HO2 and web ST2 of the planetary gearset RS2 connects to each other. The spatial arrangement of the five switching elements A to E according to 21 is exemplary 9 accepted.

22 shows a fourth embodiment of a multi-speed transmission according to the third inventive solution, the transmission scheme is again shown schematically. Based on the transmission scheme according to 19 , that is different in 22 illustrated multistage transmission according to the invention of the in 19 shown gearbox substantially by a modified kinematic coupling of the clutch D, which forms the fifth switching element of the transmission. According to 22 is now provided that the clutch D in the frictional connection between the sixth and eighth wave 6 . 8th the transmission is arranged. In the switched or closed state, the clutch D now connects the ring gear HO2 of the second planetary gearset RS2 with the interconnected ring gears HO1 and HO3 of the first and third planetary gearset RS1, RS3. In the 22 exemplary selected spatial arrangement of the five switching elements A to E is essentially of 10 accepted. Due to the kinematic connection of the inner disk carrier of the brake B now to the ring gear HO1 of here arranged close to the drive arranged first planetary gearset RS1, the disk set of the brake B - as well as in 19 provided - arranged in a structurally particularly simple manner spatially in the region radially above the first planetary gear set RS1.

23 shows a fifth embodiment of a multi-speed transmission according to the third inventive solution, wherein the transmission scheme is again shown schematically and in the embodiment according to 22 based. Based on the consideration that the clutch E is provided to block the second planetary gearset RS2 when needed, is according to 23 provided that the clutch E in the power flow now between the shaft 5 and the wave 7 is arranged of the transmission and in the switched or closed state now ring gear HO2 and sun gear SO2 of the planetary gearset RS2 connects to each other. The spatial arrangement of the five switching elements A to E according to 23 is exemplary 11 accepted.

24 Finally, shows a sixth embodiment of a multi-speed transmission according to the third inventive solution, the Ge operating scheme is again shown schematically and also on the embodiment according to 22 based. Again, starting from the consideration that the clutch E is provided to block the second planetary gearset RS2 when needed, is according to 24 provided that the clutch E in the power flow now between the shaft 5 and the wave 8th of the transmission is arranged and in the switched or closed state now ring gear HO2 and web ST2 of the planetary gearset RS2 connects to each other. The spatial arrangement of the five switching elements A to E according to 24 is exemplary 12 accepted.

25 now shows a schematic representation of a transmission scheme as a first embodiment of a multi-speed transmission according to the fourth inventive solution. The transmission in turn comprises a drive shaft AN, an output shaft AB, four planetary gear sets RS1, RS2, RS3, RS4 and five switching elements A, B, C, D, E. The four planetary gear sets RS1, RS2, RS3, RS4 are in this embodiment in axial Direction in turn in the order "RS1, RS4, RS2, RS3" coaxially arranged one behind the other, as an example of a favorable construction for a built-in longitudinal axis of the motor vehicle automatic transmission 1 to 24 described embodiments are now three of the four planetary gear sets - specifically the planetary gear sets RS1, RS2 and RS4 - designed as a simple plus planetary gear sets in Doppelplanetenbauweise. The third planetary gearset RS3, however, is designed as a simple minus planetary gear set. The nomenclature of the individual elements of the planetary gear sets are the same or derived from the previously used nomenclature. Thus, the ring gears of the four planetary gear sets RS1 to RS4 are designated by HO1 to HO4, the sun gears by SO1 to SO4 and the webs by ST1 to ST4. The inner planetary gears of the three plus planetary gear sets RS1, RS2 and RS4 are denoted by PL1i, PL2i and PL4i, the outer planetary gears by PL1a, PL2a and PL4a. The planet gears of the single minus planetary gearset RS3 is denoted by PL3.

As in 1 are also in 25 the switching elements A and B designed as disc brakes and the switching elements C, D and E as multi-plate clutches. With these five switching elements A to E, a selective switching of eight forward gears and at least one reverse gear can be realized, which will be explained later in more detail. The multi-speed transmission according to the invention has a total of at least eight rotatable shafts that with 1 to 8th are designated.

Kinematic seen is the multi-stage transmission according to the fourth solution according to the invention a synthesis from the wheelset schemes according to the first and second solution according to the invention or a synthesis from the Radsatzschemata according to the second and third inventive solution or a synthesis of the Radsatzschemata according to the first and third inventive solution.

Thus, with regard to the kinematic coupling of the individual elements of the four planetary gear sets RS1, RS2, RS3, RS4 with each other and to the input and output shafts AN, AB in the multi-speed transmission according to the fourth inventive solution provided the following: The ring gear HO4 of the fourth planetary gear set RS4 and the drive shaft ON are as wave 1 constantly connected. The web ST3 of the third planetary gearset RS3 and the output shaft AB are as a shaft 2 constantly connected. The sun gears SO1, SO4 of the first and fourth planetary gear sets RS1, RS4 are as a shaft 3 constantly connected. The coupled web ST1 of the first planetary gear set RS1 forms the shaft 4 , The coupled web ST2 of the second planetary gearset RS2 and the sun gear SO3 of the third planetary gearset RS3 are as a shaft 5 constantly connected. The ring gear HO1 of the first planetary gearset RS1 and the ring gear HO3 of the third planetary gearset RS3 are a shaft 6 constantly connected. The sun gear SO2 of the second planetary gearset RS2 and the coupled bridge ST4 of the fourth planetary gearset RS4 are in the form of a shaft 7 constantly connected. The ring gear HO2 of the second planetary gear set RS2 forms the shaft 8th of the transmission.

With regard to the kinematic coupling of the five switching elements A to E to the waves thus described 1 to 8th of the transmission is in the multi-step transmission according to 25 The following is provided: The brake A as the first switching element of the transmission is in the power flow between the shaft 3 and the housing GG of the transmission arranged and sets in the closed or closed state, the interconnected sun gears SO1 and SO4 of the first and fourth planetary gear set RS1, RS4. The brake B as the second switching element of the transmission is in the power flow between the shaft 4 and the housing GG arranged and sets in the closed or closed state, the coupled web ST1 of the first planetary gear set RS1. The clutch C as the third switching element of the transmission is in the power flow between the shaft 1 and the wave 5 arranged and connects in the switched or closed state, the drive shaft AN with the coupled web ST2 of the second planetary gearset RS2 and with the sun gear SO3 of the third planetary gearset RS3. The clutch D as the fourth switching element of the transmission is in the power flow between the shaft 2 and the wave 8th arranged and connects in the closed or closed state, the ring gear HO2 of the second planetary gearset RS2 with the web ST3 of the third planetary gear set RS3 and the output shaft AB. The clutch E as fifth switching element of the transmission is in the power flow between the shaft 7 and the wave 8th arranged and connects in the closed or closed state, the sun gear SO2 and the coupled bridge ST2 of the second planetary gear set RS2 with each other.

In the in 25 shown gear is the first planetary RS1 - as in 1 - By way of example, the drive wheel and the third planetary gearset of the third planetary gear set RS3 of the output gear close to the transmission, wherein drive shaft AN and output shaft AB are arranged as an example coaxially to each other. It is readily apparent to those skilled in the art that this transmission can be modified without special effort in such a way that the input and output shafts are no longer arranged coaxially with one another, for example parallel to the axis or at an angle to one another. In such an arrangement, the person skilled in the art will also arrange the drive of the transmission near the third planetary gear set RS3, that is to say on the side of the third planetary gear set RS3 facing away from the first planetary gear set RS1.

In principle, the spatial arrangement of the switching elements of the in 25 illustrated embodiment of a multi-speed transmission according to the invention within the transmission be arbitrary and is limited only by the dimensions and the outer shape of the gear housing GG. In this respect, the in 25 illustrated spatial arrangement of the switching elements A to E relative to each other and relative to the four planetary gear sets RS1 to RS4 expressly to be understood as exemplary only. As in 25 readily apparent, the spatial arrangement of the five switching elements A to E from the embodiment according to 1 and therefore need not be explained again.

26 shows a second embodiment of a multi-speed transmission according to the fourth inventive solution, wherein the transmission scheme is again shown schematically and on the transmission diagram of the multi-speed transmission according to 25 based. Similar to the differences between the embodiments according to the 8th and 1 the multi-step transmission differs according to 26 from the multi-stage transmission according to 25 essentially by the kinematic connection and arrangement of the clutch E, which is provided for situational blocking of the second planetary gear set RS2. As in 26 it can be seen, the clutch E is now in the power flow between the shaft 7 and the wave 8th arranged. In the switched or closed state, the clutch E now connects sun gear SO2 and ring gear HO2 of the planetary gear set RS2 with one another. The clutch is E - as in 8th - Spatially seen (for example) arranged in a range axially between the fourth planetary gear set RS4 and the second planetary gear set RS2, while axially adjacent to the second planetary gear set RS2. In this respect, those in the context of the description of 8th explanations and instructions for the coupling construction also apply to the multi-speed transmission according to 26 mutatis mutandis transferable.

27 shows a third embodiment of a multi-speed transmission according to the fourth inventive solution, wherein the transmission scheme is again shown schematically and also on the transmission diagram of the multi-speed transmission according to 25 based. Similar to the differences between the embodiments according to the 9 and 1 the multi-step transmission differs according to 27 from the multi-stage transmission according to 25 essentially by the kinematic connection and arrangement of the clutch E, which is provided for situational blocking of the second planetary gear set RS2. As in 27 it can be seen, the clutch E is now in the power flow between the shaft 5 and the wave 8th is arranged. In the switched or closed state, the clutch E now connects the coupled web ST2 and the ring gear HO2 of the planetary gear set RS2 with one another. The clutch is E - as in 8th and in 9 - Spatially seen (for example) arranged in a range axially between the fourth planetary gear set RS4 and the second planetary gear set RS2, while axially adjacent to the second planetary gear set RS2. In this respect, those in the context of the description of 9 mutatis mutandis made to the clutch construction also on the transmission according to 27 transferable.

28 shows a fourth embodiment of a multi-speed transmission according to the fourth inventive solution, wherein the transmission scheme is again shown schematically and also on the transmission diagram of the multi-speed transmission according to 25 based. Similar to the differences between the embodiments according to the 10 and 1 the multi-step transmission differs according to 28 from the multi-stage transmission according to 25 essentially by the kinematic connection and arrangement of the clutch D. As in 10 is according to 28 now provided that the clutch D in the frictional connection between the sixth and eighth shaft 6 . 8th the transmission is arranged. In the switched or closed state, the clutch D now connects the ring gear HO2 of the second planetary gearset RS2 with the interconnected ring gears HO1 and HO3 of the first and third planetary gearset RS1, RS3.

Corresponding to the opposite 25 modified kinematic connection of the clutch D also differs in 28 exemplified spatial arrangement of the clutch D of the in 25 illustrated embodiment. Comparable to 10 , is in 28 provided by way of example that the disk set of the clutch D spatially is at least partially disposed in a region radially above the second planetary gear set RS2, wherein the inner disk carrier of the clutch D as a portion of the shaft 8th of the transmission and the ring gear HO2 of the second planetary gear set RS2 can be combined as a common component. The in the context of the description of 10 given suggestions for constructive training and spatial arrangement of a provided for operating the disk set of the clutch D servo device are of course also on the in 28 illustrated multi-step transmission mutatis mutandis transferable, as well as the previously given suggestions for possible alternative arrangement options of the switching elements within the gear housing.

29 shows a fifth embodiment of a multi-speed transmission according to the fourth inventive solution, wherein the transmission scheme is again shown schematically and on the on the transmission diagram of the multi-speed transmission according to 28 based. Similar to the differences between the embodiments according to the 8th and 1 the multi-step transmission differs according to 29 from the multi-stage transmission according to 28 essentially by the kinematic connection and arrangement of the clutch E, which is provided for situational blocking of the second planetary gear set RS2. As in 29 it can be seen, the clutch E is now in the power flow between the shaft 7 and the wave 8th arranged. In the switched or closed state, the clutch E now connects sun gear SO2 and ring gear HO2 of the planetary gear set RS2 with one another. The clutch is E - as in 8th - Spatially seen (for example) arranged in a range axially between the fourth planetary gear set RS4 and the second planetary gear set RS2, while axially adjacent to the second planetary gear set RS2. In this respect, those in the context of the description of 8th explanations and instructions for the coupling construction also apply to the multi-speed transmission according to 29 mutatis mutandis transferable.

30 Finally, shows a sixth embodiment of a multi-speed transmission according to the fourth inventive solution, wherein the transmission scheme is again shown schematically and also on the transmission diagram of the multi-speed transmission according to 28 based. Similar to the differences between the embodiments according to the 9 and 1 the multi-step transmission differs according to 30 from the multi-stage transmission according to 28 essentially by the kinematic connection and arrangement of the clutch E, which is provided for situational blocking of the second planetary gear set RS2. As in 30 it can be seen, the clutch E is now in the power flow between the shaft 5 and the wave 8th is arranged. In the switched or closed state, the clutch E now connects the coupled web ST2 and the ring gear HO2 of the planetary gear set RS2 with one another. The clutch is E - as in 8th and in 9 - Spatially seen (for example) arranged in a range axially between the fourth planetary gear set RS4 and the second planetary gear set RS2, while axially adjacent to the second planetary gear set RS2. In this respect, those in the context of the description of 9 mutatis mutandis made to the clutch construction also on the transmission according to 30 transferable.

• • RS1: plus 3,00 wenn als Plus-Planetenradsatz ausgeführt (1–7, 8, 9, 13, 14, 15, 25, 26, 27), minus 2,00 wenn als Minus-Planetenradsatz ausgeführt (19, 20, 21);
• • RS2: plus 2,70 wenn als Plus-Planetenradsatz ausgeführt (1–7, 8, 9, 19, 20, 21, 25, 26, 27), minus 1,70 wenn als Minus-Planetenradsatz ausgeführt (13, 14, 15),
• • RS3: minus 3,70;
• • RS4: plus 3,00 wenn als Plus-Planetenradsatz ausgeführt (13, 14, 15, 19, 20, 21, 25, 26, 27), minus 2,00 wenn als Minus-Planetenradsatz ausgeführt (1–7, 8, 9).

31 shows an exemplary circuit diagram, as is the case for the multi-speed transmission according to the invention 1 to 9 . 13 to 15 . 19 to 21 and 25 to 27 can be provided. In each gear three switching elements are closed and two switching elements open. In addition to the switching logic, exemplary values for the respective gear ratios i of the individual gear stages and the incremental steps φ to be determined from them can also be taken from the circuit diagram. The specified ratios i result from the following (typical) stationary gear ratios of the four planetary gear sets:

• • RS1: plus 3.00 when running as a plus planetary gear set ( 1 - 7 . 8th . 9 . 13 . 14 . 15 . 25 . 26 . 27 ), minus 2.00 when running as a minus planetary gear set ( 19 . 20 . 21 );
• • RS2: plus 2.70 if designed as a plus planetary gear set ( 1 - 7 . 8th . 9 . 19 . 20 . 21 . 25 . 26 . 27 ), minus 1.70 when running as a minus planetary gear set ( 13 . 14 . 15 )
• • RS3: minus 3.70;
• • RS4: plus 3.00 when running as a plus planetary gear set ( 13 . 14 . 15 . 19 . 20 . 21 . 25 . 26 . 27 ), minus 2.00 when running as a minus planetary gear set ( 1 - 7 . 8th . 9 ).

Of Further can be seen from the circuit diagram that when sequential Switching double circuits or group circuits avoided be, since two in the shift logic adjacent gear stages te two Schaltelemen use together. The sixth gear is more efficient than formed direct gear.

• • RS1: plus 3,00 wenn als Plus-Planetenradsatz ausgeführt (10, 11, 12, 16, 17, 18, 28, 29, 30) und minus 2,00 wenn als Minus-Planetenradsatz ausgeführt (22, 23, 24);
• • RS2: plus 2,55 wenn als Plus-Planetenradsatz ausgeführt (10, 11, 12, 22, 23, 24, 28, 29, 30) und minus 1,55 wenn als Minus-Planetenradsatz ausgeführt (16, 17,18),
• • RS3: minus 3,70;
• • RS4: plus 3,00 wenn als Plus-Planetenradsatz ausgeführt (16, 17, 18, 22, 23, 24, 28, 29, 30) und minus 2,00 wenn als Minus-Planetenradsatz ausgeführt (10, 11, 12).

32 Finally, shows an exemplary circuit diagram, as is the case for the multistage transmission according to the invention 10 to 12 . 16 to 18 . 22 to 24 and 28 to 30 can be provided. In each gear three switching elements are closed and two switching elements open. In addition to the switching logic, exemplary values for the respective gear ratios i of the individual gear stages and the incremental steps φ to be determined from them can also be taken from the circuit diagram. The specified ratios i result from the following (typical) stationary gear ratios of the four planetary gear sets:

• • RS1: plus 3.00 when running as a plus planetary gear set ( 10 . 11 . 12 . 16 . 17 . 18 . 28 . 29 . 30 ) and minus 2.00 when running as a minus planetary gear set ( 22 . 23 . 24 );
• • RS2: plus 2.55 if designed as a plus planetary gear set ( 10 . 11 . 12 . 22 . 23 . 24 . 28 . 29 . 30 ) and minus 1.55 when running as a minus planetary gear set ( 16 . 17 . 18 )
• • RS3: minus 3.70;
• • RS4: plus 3.00 when running as a plus planetary gear set ( 16 . 17 . 18 . 22 . 23 . 24 . 28 . 29 . 30 ) and minus 2.00 when running as a minus planetary gear set ( 10 . 11 . 12 ).

Of Further can be seen from the circuit diagram that when sequential Switching double circuits or group circuits avoided be because two adjacent in the switching logic gears two switching elements use together. The sixth gear is more efficient than formed direct gear.

In both schematics according to 31 and 32 The first forward speed is obtained by closing the brakes A and B and the clutch C, the second forward speed by closing the brakes A and B and the clutch E, the third forward speed by closing the brake B and the clutches C and E, the fourth forward speed by closing the brake B and the clutches D and E, the fifth forward speed by closing the brake B and the clutches C and D, the sixth forward speed by closing the clutches C, D and E, the seventh forward speed by closing the brake A and Clutches C and D, as well as the eighth forward gear by closing the brake A and the clutches D and E. As can be seen from the wiring diagram, the reverse gear is obtained by closing the brakes A and B and the clutch D.

at all previously explained inventive Multi-speed transmission is a start of the motor vehicle with a in the transmission integrated switching element possible. in this connection is a switching element particularly suitable, both in the first forward gear as well as in reverse is needed, So here preferably the brake A or the brake B, as these both brakes A, B both in the first and in the second forward gear needed. If the brake B as integrated in the transmission Used starting element, so it is even a start in the first five forward gears and reverse gear possible. As can be seen from the wiring diagram, it can be used to approach in the forward direction also the clutch C and to start in the reverse direction the clutch D can be used as a gear-internal starting element. Is a start of the motor vehicle by means of an internal gear Switching provided, so is the drive shaft of the transmission constantly rotationally stiff or torsionally elastic with the crankshaft connected to the drive motor.

For all exemplary embodiments described or described above for a multistage transmission according to the invention, the following also applies:
According to the invention, unterschiedli che gear jumps can result even with the same transmission scheme, depending on the stationary gear ratio of the individual planetary gear sets, so that an application or vehicle-specific variation is possible.

It is also possible, at any suitable point of the multi-speed transmission provide additional freewheels, for example between a shaft and the housing or around two shafts if necessary to connect.

On the drive side or on the output side can a Axle differential and / or a distribution differential can be arranged.

As part of a further training, the An drive shaft to be separated by a starting element of a drive motor as needed, as such a starting element, a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch can be used. It is also possible to arrange such a starting element in the power flow direction behind the transmission, in which case the drive shaft AN is constantly connected to the crankshaft of the drive motor.

The inventive multi-speed transmission allows also the arrangement of a torsional vibration damper between drive motor and gearbox.

in the Within the scope of a further embodiment of the invention on each shaft, preferably on the drive shaft AN or the output shaft AB, a wear-free brake, such. B. a hydraulic or electric retarder or the like, which are arranged in particular for use in commercial vehicles of is of particular importance. Furthermore, to drive additional Units on each shaft, preferably on the drive shaft AN or the output shaft AB, a power take-off may be provided.

The used switching elements can be used as load-shifting couplings or brakes be formed. In particular, non-positive Clutches or brakes, such as. B. multi-plate clutches, band brakes and / or cone clutches. Furthermore you can as switching elements also positive brakes and / or clutches, such as B. synchronizers or dog clutches are used.

One Another advantage of the presented here multistage transmission consists in that on each shaft in addition an electrical Machine as a generator and / or as an additional drive machine attachable.

1

first wave

2

second wave

3

third wave

4

fourth wave

5

fifth wave

6

sixth wave

7

seventh wave

8th

eighth wave

A

first Switching element, first brake

B

second Switching element, second brake

C

third Switching element, first clutch

D

fourth Switching element, second clutch

e

fifth Switching element, third clutch

FROM

output shaft

AT

drive shaft

GG

casing

GW

housing wall

A1

first thrust washer

A2

second thrust washer

L1

first axial bearing

L2

second axial bearing

L3

third axial bearing

L4

fourth axial bearing

L5

fifth axial bearing

L6

sixth axial bearing

L7

seventh axial bearing

L8

eighth axial bearing

L9

ninth axial bearing

L10

tenth axial bearing

L11

eleventh axial bearing

L12

twelfth axial bearing

RS1

first planetary gear

HO1

ring gear of the first planetary gear set

SO1

sun of the first planetary gear set

ST1

web of the first planetary gear set

PL1

planetary gears of the first planetary gear set

PL1i

inner Planetary gears of the first planetary gear set

PL1a

outer Planetary gears of the first planetary gear set

RS2

second planetary gear

HO2

ring gear of the second planetary gear set

SO2

sun of the second planetary gear set

ST2

web of the second planetary gear set

PL2

planetary gears of the second planetary gear set

PL2i

inner Planetary gears of the second planetary gear set

PL2a

outer Planetary gears of the second planetary gear set

RS3

third planetary gear

HO3

ring gear of the third planetary gear set

SO3

sun of the third planetary gear set

ST3

web of the third planetary gear set

PL3

planetary gears of the third planetary gear set

RS4

fourth planetary gear

HO4

ring gear of the fourth planetary gear set

SO4

sun of the fourth planetary gear set

ST4

web of the fourth planetary gear set

PL4

planetary gears of the fourth planetary gear set

PL4i

inner Planetary gears of the fourth planetary gear set

PL4a

outer Planetary gears of the fourth planetary gear set

i

translation

φ

increment

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - DE 102005002337 A1 [0003, 0005, 0006, 0007, 0008, 0011, 0012, 0018, 0019, 0020, 0020, 0023, 0025, 0079]
• - DE 202006009123 U1 [0006]
• - DE 202006011432 U1 [0007]
• - DE 202006008815 U1 [0008]

Claims (12)

Multi-stage transmission in planetary design, in particular automatic transmission for a motor vehicle, comprising a drive shaft (AN), an output shaft (AB), four planetary gear sets (RS1, RS2, RS3, RS4), at least eight rotatable shafts ( 1 . 2 . 3 . 4 . 5 . 6 . 7 . 8th ), and five switching elements (A, B, C, D, E), the selective engagement causes different ratios between the drive shaft (AN) and output shaft (AB), so that eight forward gears and at least one reverse gear can be realized, wherein • a first element ( ST4, HO4) of the fourth planetary gear set (RS4) is constantly connected to the drive shaft (AN) as the first shaft ( 1 ) of the transmission, • a first element (ST3) of the third planetary gear set (RS3) is constantly connected to the output shaft (AB) as the second shaft ( 2 ) of the transmission, • a second element (SO4) of the fourth planetary gear set (RS4) is permanently connected to a first element (SO1) of the first planetary gear set (RS1) as the third shaft ( 3 ) of the transmission, • a second element (ST1, HO1) of the first planetary gear set (RS1), the fourth shaft ( 4 ) of the transmission, • a first element (ST2, HO2) of the second planetary gear set (RS2) is constantly connected to a second element (SO3) of the third planetary gear set (RS3) as the fifth shaft ( 5 ) of the transmission, • a third element (HO1, ST1) of the first planetary gear set (RS1) is permanently connected to a third element (HO3) of the third planetary gear set (RS3) as the sixth shaft ( 6 ) of the transmission, • a third element (HO4, ST4) of the fourth planetary gear set (RS4) is permanently connected to a second element (SO2) of the second planetary gear set (RS2) as the seventh shaft ( 7 ) of the transmission, • a third element (HO2, ST2) of the second planetary gear set (RS2) the eighth wave ( 8th ) of the transmission, • the first switching element (A) in the power flow between the third shaft ( 3 ) and a housing (GG) of the transmission is arranged, • the second switching element (B) in the power flow between the fourth shaft ( 4 ) and the housing (GG) of the transmission is arranged, • the third switching element (C) in the power flow between the first shaft ( 1 ) and the fifth wave ( 5 ), the fourth switching element (D) in the force flow either between the second and eighth wave ( 2 . 8th ) or between the sixth and eighth wave ( 6 . 8th ), and • the fifth switching element (E) in the power flow either between the fifth and seventh shaft ( 5 . 7 ) or between the fifth and eighth wave ( 5 . 8th ) or between the seventh and eighth wave ( 7 . 8th ), characterized in that • the first planetary gear set (RS1) is formed as a plus planetary gear set with a sun gear (SO1) as a first element and a coupled land (ST1) as a second element and a ring gear (HO1) as the third element, The second planetary gear set (RS2) is designed as a plus planetary gear set with a coupled land (ST2) as the first element and a sun gear (SO2) as the second element and a ring gear (HO2) as the third element, • the third planetary gear set (RS3) as Minus planetary gear is formed with a web (ST3) as a first element and a sun gear (SO3) as the second element and a ring gear (HO3) as the third element, and • the fourth planetary gear set (RS4) is formed as a minus planetary gear set with a web (ST4) as a first element and a sun gear (SO4) as a second element and a ring gear (HO4) as a third element. [ 1 - 12 ] Multi-speed transmission according to the preamble of claim 1, characterized in that • the first planetary gear set (RS1) is designed as a plus planetary gear set with a sun gear (SO1) as a first element and a coupled web (ST1) as a second element and a ring gear (HO1) as third element, • the second planetary gear set (RS2) is designed as a minus planetary gear set with a ring gear (HO2) as a first element and a sun gear (SO2) as a second element and a bridge (ST2) as the third element, • the third planetary gear set ( RS3) is designed as a minus planetary gear set with a web (ST3) as a first element and a sun gear (SO3) as the second element and a ring gear (HO3) as a third element, and • the fourth planetary gear set (RS4) is designed as a plus planetary gear set with a ring gear (HO4) as a first element and a sun gear (SO4) as a second element and a coupled web (ST4) as a third element. [ 13 - 18 ] Multi-speed transmission according to the preamble of claim 1, characterized in that • the first planetary gear set (RS1) is designed as a minus planetary gear set with a sun gear (SO1) as a first element and a ring gear (HO1) as a second element and a web (ST1) as third element, • the second planetary gear set (RS2) is formed as a plus planetary gear with a coupled land (ST2) as the first element and a sun gear (SO2) as the second element and a ring gear (HO2) as the third element, • the third planetary gear set ( RS3) as a minus tarpaulin tenradsatz is formed with a web (ST3) as the first element and a sun gear (SO3) as the second element and a ring gear (HO3) as a third element, and • the fourth planetary gear set (RS4) is formed as a plus planetary gear with a ring gear (HO4 ) as a first element and a sun gear (SO4) as a second element and a coupled land (ST4) as a third element. [ 19 - 24 ] Multi-speed transmission according to the preamble of claim 1, characterized in that • the first planetary gear set (RS1) is designed as a plus planetary gear set with a sun gear (SO1) as a first element and a coupled web (ST1) as a second element and a ring gear (HO1) as the third element, the second planetary gear set (RS2) is designed as a plus planetary gear set with a coupled land (ST2) as the first element and a sun gear (SO2) as the second element and a ring gear (HO2) as the third element, the third planetary gear set (RS3) is designed as a minus planetary gear set with a web (ST3) as the first element and a sun gear (SO3) as a second element and a ring gear (HO3) as a third element, and • the fourth planetary gear set (RS4) formed as a plus planetary gear set is provided with a ring gear (HO4) as a first element and a sun gear (SO4) as a second element and a coupled land (ST4) as a third element. [ 25 - 30 ] Multi-step transmission according to one of the claims 1 to 4, characterized in that • the first Forward gear by closing the first, second and third switching element (A, B, C), • the second Forward gear by closing the first, second and fifth switching element (A, B, E), • of the third forward by closing the second, third and fifth switching element (B, C, E), • of the fourth forward by closing the second, fourth and fifth switching element (B, D, E), • of the fifth forward by closing the second, third and fourth switching elements (B, C, D), • of the sixth forward by closing the third, fourth and fifth switching element (C, D, E), • of the seventh forward by closing the first, third and fourth switching element (A, C, D), • of the eighth forward by closing the first, fourth and fifth switching element (A, D, E) and • one Reverse by closing the first, second and fourth switching element (A, B, D). Multi-step transmission according to one of the claims 1 to 5, characterized in that the planetary gear sets (RS1, RS2, RS3, RS4) coaxial with each other and in the axial direction consecutively in an order "RS1, RS4, RS2, RS3" are arranged, with all four planetary gear sets (RS1, RS2, RS3, RS4) in each case at most of one shaft of the transmission are centered in the axial direction. Multi-speed transmission according to claim 6, characterized in that for the axial component support in the transmission a total of eleven thrust bearings (L1 to L11) are provided, wherein in the axial region between a gear housing fixed housing wall (GW) and the sun gear (SO1) of the first planetary gear set (RS1) a thrust bearing (L1), in the region axially between the sun gears (SO1, SO4) of the first and fourth planetary gear sets (RS1, RS4) four thrust bearings (L2, L3, L4, L5) are provided, in the region axially between the sun gears (SO4, SO2) of the fourth and second planetary gear set (RS4, RS2) two thrust bearings (L6, L7) are provided, in the region axially between the sun gears (SO2, SO3) of the second and third planetary gear set (RS2, RS3) two thrust bearings (L8, L9) are provided and in the axial region between the sun (SO3) of the third planetary gear set (RS3) and a transmission housing wall two thrust bearings (L10, L11) are provided. [ 2 ] Multi-speed transmission according to claim 6, characterized in that for the axial component support in the transmission a total of twelve thrust bearings (L1 to L12) are provided, wherein in the axial region between a gear housing fixed housing wall (GW) and the sun gear (SO1) of the first planetary gear set (RS1) a thrust bearing (L1) is provided, in the region axially between the sun gears (SO1, SO4) of the first and fourth planetary gear set (RS1, RS4) three thrust bearings (L2, L3, L4) are provided, in the region axially between the sun gears (SO4, SO2) four thrust bearings (L5, L6, L7, L8) are provided in the region and axially between the sun gears (SO2, SO3) of the second, third planetary gear set (RS2, RS3) two thrust bearings (L9, L10) are provided and in the region axially between the sun gear (SO3) of the third planetary gear set (RS3) and a transmission housing wall, two thrust bearings (L11, L12) are provided. [ 3 ] Multi-speed transmission according to claim 6, characterized in that for the axial component support in the transmission a total of twelve thrust bearings (L1 to L12) are provided, wherein axially in the range between a gear housing fixed housing wall (GW) and the sun gear (SO1) of the first planetary gear set (RS1) three thrust bearings (L1, L2, L3) are provided, in the region axially between the sun gears (SO1, SO4) of the first and fourth planetary gear set (RS1, RS4) no thrust bearing is provided in the range axially between the sun gears (SO4, SO2) of the fourth and second planetary gear set (RS4, RS2) five thrust bearings (L4, L5, L6, L7, L8) are provided, in the range axially two thrust bearings (L9, L10) are provided between the sun gears (SO2, SO3) of the second and third planetary gear set (RS2, RS3) and two axial thrust bearings (L11) in the region axially between the sun gear (SO3) of the third planetary gear set (RS3) and a transmission housing wall , L12) are provided. [ 4 ] Multi-speed transmission according to claim 6, characterized in that for the axial component support in the transmission a total of ten thrust bearings (L1 to L10) and two thrust washers (A1, A2) are provided, wherein in the range axially between a gear housing fixed housing wall (GW) and the first planetary gear set (RS1 ) an axial bearing (L1) and a thrust washer (A1) are provided, in the region axially between the webs (ST1, ST4) of the first and fourth planetary gear set (RS1, RS4) a thrust washer (A2) is provided, in the region axially between the sun gears (SO4, SO2) of the fourth and second planetary gear set (RS4, RS2) five thrust bearings (L2, L3, L4, L5, L6) are provided, in the region axially between the sun gears (SO2, SO3) of the second and third planetary gear set (RS2, RS3) two thrust bearings (L7, L8) are provided and in the region axially between the sun gear (SO3) of the third planetary gear set (RS3) and a transmission housing wall, two thrust bearings (L9, L10) are provided. [ 5 ] Multi-speed transmission according to claim 6, characterized in that for the axial component support in the transmission a total of eleven thrust bearings (L1 to L11) and two thrust washers (A1, A2) are provided, wherein in the range axially between a gear housing fixed housing wall (GW) and the first planetary gear set (RS1 ) an axial bearing (L1) and a thrust washer (A1) are provided, in the region axially between the webs (ST1, ST4) of the first and fourth planetary gear set (RS1, RS4) a thrust washer (A2) is provided, in the region axially between the sun gears (SO4, SO2) of the fourth and second planetary gear set (RS4, RS2) four thrust bearings (L2, L3, L4, L5) are provided, in the range axially between the sun gears (SO2, SO3) of the second and third planetary gear set (RS2, RS3) four thrust bearings (L6, L7, L8, L9) are provided and in the region axially between the sun gear (SO3) of the third planetary gear set (RS3) and a transmission housing wall, two thrust bearings (L10, L11) are provided. [ 6 ] Multi-speed transmission according to claim 6, characterized in that for the axial component support in the transmission a total of twelve thrust bearings (L1 to L12) are provided, wherein axially in the range between a gear housing fixed housing wall (GW) and the sun gear (SO1) of the first planetary gear set (RS1) three thrust bearings (L1, L2, L3) are provided, in the region axially between the sun gears (SO1, SO4) of the first and fourth planetary gear set (RS1, RS4) is provided no thrust bearing in the range axially between the sun gears (SO4, SO2) of the fourth and second planetary gear set (RS4, RS2) two thrust bearings (L4, L5) are provided, in the region axially between the sun gears (SO2, SO3) of the second and third planetary gear set (RS2, RS3) four thrust bearings (L6, L7, L8, L9) are provided and in the region axially between the sun gear (SO3) of the third planetary gear set (RS3) and a transmission housing wall, three thrust bearings (L10, L11, L12) are provided. [ 7 ]