DE102014110245B4 - Transmission arrangement for a motor vehicle - Google Patents

Abstract

Transmission arrangement for a motor vehicle, comprising- a first planetary set (10) with a first sun (101), a first ring gear (102) and a first carrier (103) on which a set of first planetary gears, which on the one hand are connected to the first sun (101 ) and on the other hand mesh with the first ring gear (102), - a second planetary set (20) with a second sun (201), a second ring gear (202) and an input shaft (1st ) connected second web (203), on which a set of second planet gears, which mesh with the second sun (201) on the one hand and with the second ring gear (202) on the other hand, is rotatably mounted, - a third planetary gear set (30) with a third sun and - A fourth planetary gear set (40) with a fourth sun (401), a fourth ring gear (402) and a fourth web (403) which can be connected to an output shaft of the motor vehicle (2) and on which a set of fourth planetary gears, the on the one hand mesh with the fourth sun (401) and on the other hand with the fourth ring gear (402), wherein- the first sun (101) with the second sun (201), the first web (103) with the fourth ring gear ( 402) and the second ring gear (202) is connected to the third sun (301), - the first sun (101) is switchably coupled to a transmission housing by means of a first brake (B1), - the first by means of a second brake (B2). Ring gear (102) is switchably coupled to the transmission housing, - the second web (203) is switchably coupled to the fourth sun (401) by means of a first clutch (K1), - the third sun (301) by means of a second clutch (K2) is switchably coupled to the fourth sun (401), - the third ring gear (302) is switchably coupled to the fourth sun (401) by means of a third clutch (K3) and the third web (103) is connected to the fourth ring gear (402). , characterized in that the second planetary gear set (20) is arranged radially inside the third planetary gear set (30).

Description

• - einen ersten Planetensatz mit einer ersten Sonne, einem ersten Hohlrad und einem ersten Steg, auf dem ein Satz erster Planetenräder, die einerseits mit der ersten Sonne und andererseits mit dem ersten Hohlrad kämmen, drehbar gelagert ist,
• - einen zweiten Planetensatz mit einer zweiten Sonne, einem zweiten Hohlrad und einem mit einer an ein Antriebsaggregat eines Kraftfahrzeugs anschließbaren Eingangswelle verbundenen, zweiten Steg, auf dem ein Satz zweiter Planetenräder, die einerseits mit der zweiten Sonne und andererseits mit dem zweiten Hohlrad kämmen, drehbar gelagert ist,
• - einen dritten Planetensatz mit einer dritten Sonne, einem dritten Hohlrad und einem dritten Steg, auf dem ein Satz dritter Planetenräder, die einerseits mit der dritten Sonne und andererseits mit dem dritten Hohlrad kämmen, drehbar gelagert ist, und
• - einen vierten Planetensatz mit einer vierten Sonne, einem vierten Hohlrad und einem mit einer an einen Abtrieb des Kraftfahrzeugs anschließbaren Ausgangswelle verbundenen, vierten Steg, auf dem ein Satz vierter Planetenräder, die einerseits mit der vierten Sonne und andererseits mit dem vierten Hohlrad kämmen, drehbar gelagert ist, sowie

wobei

• - die erste Sonne mit der zweiten Sonne, der erste Steg mit dem vierten Hohlrad und das zweite Hohlrad mit der dritten Sonne verbunden ist,
• - mittels einer ersten Bremse die erste Sonne schaltbar mit dem Getriebegehäuse gekoppelt ist,
• - mittels einer zweiten Bremse das erste Hohlrad schaltbar mit dem Getriebegehäuse gekoppelt ist,
• - mittels einer ersten Kupplung der zweite Steg mit der vierten Sonne schaltbar gekoppelt ist,
• - mittels einer zweiten Kupplung die dritte Sonne mit der vierten Sonne schaltbar gekoppelt ist,
• - mittels einer dritten Kupplung ein weiteres Element des dritten Planetensatzes mit einem Element des vierten Planetensatzes schaltbar gekoppelt und ein weiteres Element des dritten Planetensatzes mit einem Element des vierten Planetensatzes verbunden ist.

The invention relates to a transmission arrangement for a motor vehicle, comprising

• - a first planetary gearset with a first sun, a first ring gear and a first carrier, on which a set of first planetary gears, which mesh on the one hand with the first sun and on the other hand with the first ring gear, is rotatably mounted,
• - a second planetary gearset with a second sun, a second ring gear and a second web connected to an input shaft that can be connected to a drive unit of a motor vehicle, on which a set of second planetary gears meshing on the one hand with the second sun and on the other hand with the second ring gear, rotatably is stored
• - a third planetary gearset with a third sun, a third ring gear and a third carrier, on which a set of third planetary gears, which mesh on the one hand with the third sun and on the other hand with the third ring gear, is rotatably mounted, and
• - a fourth planetary gearset with a fourth sun, a fourth ring gear and a fourth web connected to an output shaft that can be connected to an output shaft of the motor vehicle, on which a set of fourth planetary gears, which mesh on the one hand with the fourth sun and on the other hand with the fourth ring gear, can rotate is stored, as well

whereby

• - the first sun is connected to the second sun, the first web is connected to the fourth ring gear and the second ring gear is connected to the third sun,
• - the first sun is switchably coupled to the transmission housing by means of a first brake,
• - the first ring gear is shiftably coupled to the transmission housing by means of a second brake,
• - the second web is switchably coupled to the fourth sun by means of a first coupling,
• - the third sun is switchably coupled to the fourth sun by means of a second coupling,
• - Another element of the third planetary gearset is coupled to an element of the fourth planetary gearset in a switchable manner by means of a third clutch, and another element of the third planetary gearset is connected to an element of the fourth planetary gearset.

The invention further relates to a motor vehicle with such a transmission arrangement.

Such transmission assemblies and motor vehicles are in the post DE 10 2014 103 115 A1 disclosed. A similar gear arrangement is from DE 10 2006 026 604 A1 known. In this case, in particular, the third web and the fourth web are coupled to one another in a switchable manner by means of the third clutch, while the third ring gear and the fourth sun are firmly connected to one another.

In the context of the present description, the term “connect” or “connection” is used for fixed connections between two elements that cannot be separated during normal operation. Occasionally, such a connection is also referred to here as a "fixed connection" to emphasize its fixed character, without this implying a difference in meaning to "connection" as defined above. In contrast, the term “couple” or “coupling” is used in a more general way and includes both the aforementioned connections and couplings that can be released during normal operation, with the latter being explicitly referred to as “switchably coupled” if necessary. In the context of the present description, the term “shifting element” includes both “brakes”, which each switchably couple a rotating element to the transmission housing, and “clutches”, which each switchably couple two rotating elements relative to the transmission housing. This choice of term is to be understood as completely independent of the structural design of the corresponding elements. In particular, both the brakes mentioned and the clutches mentioned can be implemented, for example, as switchable freewheels, multi-plate clutches, synchronizers or in some other way. With the terms "sun", "ring gear" and "bar" used here, the person skilled in the art will understand that this can mean both the respective planetary gearset element and the associated shaft, with the specific meaning resulting from the context in each case.

That from the DE 10 2014 103 115 A1 Previously known transmissions realized a well-stepped, progressive translation series of eight forward gears and one reverse gear, with exactly two of the five switching elements being open in each gear and the others being closed.

The disadvantage of the known transmission is that it forms a largely self-contained unit, in particular because of the nested shifting process disclosed in the cited publication, for which it was designed Realize ten and twelve-speed gearboxes. From an economic point of view, however, it is desirable to be able to serve a wide range of customer requirements with minimized parts logistics.

That in the post-release DE 10 2014 103 115 A1 Although the transmission described offers a solution for this; it builds axially but disadvantageously long.

It is the object of the present invention to further develop such a transmission arrangement in such a way that it is axially shorter. It is also an object of the invention to provide ten-speed and twelve-speed transmission arrangements that can be built on the basis of such a transmission arrangement.

This object is achieved in connection with the features of the preamble of claim 1 in that the second planetary gear set is arranged radially inside the third planetary gear set.

Preferred embodiments of the invention are the subject matter of the dependent claims.

A design in which the second planetary gear set is arranged radially inside the third planetary gear set is considered to be expedient with regard to reducing the axial installation space compared to the subsequently published prior art. The second ring gear can be designed in one piece with the third sun as a ring gear that is toothed both internally and externally, which is advantageous with regard to the number of parts, weight and assembly.

Although the changes made compared to the transmission arrangement known from the previously published prior art are limited to the fact that two of the three couplings between the third and fourth planetary gear set are changed, the associated effect is significant and surprising. Because a transmission modified in this way has a quality that is comparable to the known transmission in terms of efficiency and gear spacing, but can also easily be expanded to a ten or twelve-speed transmission by simply adding further shifting elements, which is not the case with the known transmission not possible.

Thus, in a preferred embodiment as a ten-speed transmission, it is provided that the third ring gear is switchably coupled to the fourth carrier by means of a fourth clutch.

For an embodiment as a twelve-speed transmission, different variants are possible, but they have in common that one element of the third planetary gearset is switchably coupled to another element of the third planetary gearset by means of a fifth clutch. This generally leads to a blocking of the third planetary gear set, which then rotates as a block without internal relative movement.

In a first variant, this is realized in that the third web is switchably coupled to the third sun by means of the fifth clutch. Alternatively, in a second variant, provision can be made for the third carrier to be switchably coupled to the third ring gear by means of the fifth clutch. Further alternatively, to achieve the same purpose, namely the blocking of the third planetary gear set, it can be provided in a third variant that the third sun is switchably coupled to the third ring gear by means of the fifth clutch.

To couple the transmission arrangement according to the invention within a motor vehicle, it is provided, as is also known from the previously published prior art, that the second web is connected to an input shaft that can be connected to a drive assembly of the motor vehicle, and that the fourth web is connected to an output shaft of the Motor vehicle connectable output shaft is connected.

A motor vehicle with a transmission arrangement according to the invention coupled in this way or in some other way is an independent part of the present invention.

Table 1 below shows the activation of the shifting elements required to represent the individual gears in an eight-gear transmission according to the invention. The columns correspond to the individual shifting elements, namely first brake B1, second brake B2, first clutch K1, second clutch K2 and third clutch K3. The shifting elements that are closed in the respective gear are marked with an “X”. Empty cells in the table indicate open switching elements. The last column gives the translations in the respective gears to illustrate the gear arrangement that can be achieved with a preferred design. Table 1 gear / mode B1 B2 K1 K2 K3 translation Backward X X X -6.67 1st gear X X X 5.00 2nd gear X X X 3.33 3rd gear X X X 2:12 4th gear X X X 1.67 5th gear X X X 1.22 6th gear X X X 1.00 7th gear X X X 0.88 8th gear X X X 0.67

Table 2 below shows the activation of the shifting elements required to represent the individual gears in a ten-speed transmission according to the invention. The columns correspond to the individual shifting elements, namely first brake B1, second brake B2, first clutch K1, second clutch K2, third clutch K3 and fourth clutch K4. The shifting elements that are closed in the respective gear are marked with an “X”. Empty cells in the table indicate open switching elements. The last column gives the translations in the respective gears to illustrate the gear arrangement that can be achieved with a preferred design. Table 2 gear / mode B1 B2 K1 K2 K3 K4 translation Backward X X X -7.70 1st gear X X X 4.80 2nd gear X X X 3.35 3rd gear X X X 2:12 4th gear X X X 1.61 5th gear X X X 1.33 6th gear X X X 1:18 7th gear X X X 1.00 8th gear X X X 0.91 9th gear X X X 0.81 10th gear X X X 0.67

Table 3 below shows the activation of the shifting elements required to represent the individual gears in a twelve-gear transmission according to the invention. The columns correspond to the individual shifting elements, namely first brake B1, second brake B2, first clutch K1, second clutch K2, third clutch K3, fourth clutch K4 and fifth clutch K5. The shifting elements that are closed in the respective gear are marked with an “X”. Empty cells in the table indicate open switching elements. The last column gives the translations in the respective gears to illustrate the gear arrangement that can be achieved with a preferred design. Table 3 gear / mode B1 B2 K1 K2 K3 K4 K5 translation Backward X X X -7.70 1st gear X X X 4.80 2nd gear X X X 3.35 3rd gear X X X 2:12 4th gear X X X 1.61 5th gear X X X 1.43 6th gear X X X 1.33 7th gear X X X 1:18 8th gear X X X 1.00 9th gear X X X 0.91 10th gear X X X 0.81 11th gear X X X 0.74 12th gear X X X 0.70

Those skilled in the art will understand that the transmission arrangement according to the invention can be implemented in various isomorphisms.

Further features and advantages of the invention result from the following specific description and the drawings.

• 1 eine schematische Darstellung eines nicht erfindungsgemäße Acht-Gang-Getriebes,
• 2 eine schematische Darstellung eines nicht erfindungsgemäße Zehn-Gang-Getriebes,
• 3a eine schematische Darstellung eines nicht erfindungsgemäße Zwölf-Gang-Getriebes in einer ersten Variante,
• 3b eine schematische Darstellung eines nicht erfindungsgemäße Zwölf-Gang-Getriebes in einer zweiten Variante,
• 3c eine schematische Darstellung eines nicht erfindungsgemäße Zwölf-Gang-Getriebes in einer dritten Variante,
• 4 eine schematische Darstellung einer nicht erfindungsgemäßen, ersten isomorphen Konfiguration des Getriebes von 1,
• 5 eine schematische Darstellung einer nicht erfindungsgemäßen, zweiten isomorphen Konfiguration des Getriebes von 1,
• 6 eine schematische Darstellung einer erfindungsgemäßen, dritten isomorphen Konfiguration des Getriebes von 1,
• 7 eine schematische Darstellung einer nicht erfindungsgemäßen, ersten isomorphen Konfiguration des Getriebes von 2,
• 8 eine schematische Darstellung einer nicht erfindungsgemäßen, zweiten isomorphen Konfiguration des Getriebes von 2,
• 9 eine schematische Darstellung einer erfindungsgemäßen, dritten isomorphen Konfiguration des Getriebes von 2,
• 10 eine schematische Darstellung einer nicht erfindungsgemäßen, ersten isomorphen Konfiguration des Getriebes von 3a,
• 11 eine schematische Darstellung einer nicht erfindungsgemäßen, zweiten isomorphen Konfiguration des Getriebes von 3a,
• 12 eine schematische Darstellung einer erfindungsgemäßen, dritten isomorphen Konfiguration des Getriebes von 3a,
• 13 eine schematische Darstellung einer nicht erfindungsgemäßen, ersten isomorphen Konfiguration des Getriebes von 3b,
• 14 eine schematische Darstellung einer nicht erfindungsgemäßen, zweiten isomorphen Konfiguration des Getriebes von 3b,
• 15 eine schematische Darstellung einer erfindungsgemäßen, dritten isomorphen Konfiguration des Getriebes von 3b,
• 16 eine schematische Darstellung einer nicht erfindungsgemäßen, ersten isomorphen Konfiguration des Getriebes von 3c,
• 17 eine schematische Darstellung einer nicht erfindungsgemäßen, zweiten isomorphen Konfiguration des Getriebes von 3c,
• 18 eine schematische Darstellung einer erfindungsgemäßen, dritten isomorphen Konfiguration des Getriebes von 3c.

Show it:

• 1 a schematic representation of an eight-speed transmission not according to the invention,
• 2 a schematic representation of a ten-speed transmission not according to the invention,
• 3a a schematic representation of a twelve-speed transmission not according to the invention in a first variant,
• 3b a schematic representation of a twelve-speed transmission not according to the invention in a second variant,
• 3c a schematic representation of a twelve-speed transmission not according to the invention in a third variant,
• 4 a schematic representation of a non-inventive, first isomorphic configuration of the transmission of 1 ,
• 5 a schematic representation of a non-inventive, second isomorphic configuration of the transmission of 1 ,
• 6 a schematic representation of an inventive, third isomorphic configuration of the transmission of 1 ,
• 7 a schematic representation of a non-inventive, first isomorphic configuration of the transmission of 2 ,
• 8th a schematic representation of a non-inventive, second isomorphic configuration of the transmission of 2 ,
• 9 a schematic representation of an inventive, third isomorphic configuration of the transmission of 2 ,
• 10 a schematic representation of a non-inventive, first isomorphic configuration of the transmission of 3a ,
• 11 a schematic representation of a non-inventive, second isomorphic configuration of the transmission of 3a ,
• 12 a schematic representation of an inventive, third isomorphic configuration of the transmission of 3a ,
• 13 a schematic representation of a non-inventive, first isomorphic configuration of the transmission of 3b ,
• 14 a schematic representation of a non-inventive, second isomorphic configuration of the transmission of 3b ,
• 15 a schematic representation of an inventive, third isomorphic configuration of the transmission of 3b ,
• 16 a schematic representation of a non-inventive, first isomorphic configuration of the transmission of 3c ,
• 17 a schematic representation of a non-inventive, second isomorphic configuration of the transmission of 3c ,
• 18 a schematic representation of an inventive, third isomorphic configuration of the transmission of 3c .

The same reference numbers in the figures indicate the same or analogous elements.

1 shows a schematic representation of an eight-speed transmission not according to the invention, which has four simple planetary gear sets, namely the first planetary gear set 10 , the second planetary gear set 20 , the third planetary gear set 30 and the fourth planetary gear set 40 . The first planetary gearset 10 comprises, as its planetary gearset elements, the first sun 101, the first ring gear 102 and the first carrier 103, on which a set of planetary gears not provided with separate reference numbers, which are connected in the usual way on the one hand to the first sun 101 and on the other hand to the first ring gear 102 mesh. The second planetary gear set 20 comprises, as its planetary gear set elements, the second sun 201, the second ring gear 202 and the second carrier 203, on which a set of planetary gears not provided with separate reference numbers, which are connected in the usual way on the one hand to the second sun 201 and on the other hand to the second ring gear 202 mesh. The third planetary gearset 30 comprises, as its planetary gearset elements, the third sun 301, the third ring gear 302 and the third carrier 303, on which a set of planetary gears not provided with separate reference symbols, which are connected in the usual way on the one hand to the third sun 301 and on the other hand to the third ring gear 302 mesh. The fourth planetary gear set 40 comprises as its planetary gear set elements the fourth sun 401, the fourth ring gear 402 and the fourth carrier 403, on which a set of planetary gears not provided with separate reference symbols, which are connected in the usual way on the one hand to the fourth sun 401 and on the other hand to the fourth ring gear 402 mesh.

The second web 203 is connected to the input shaft 1 of the transmission, via which this can be coupled to a drive unit of the motor vehicle. The fourth web 403 is connected to the output shaft 2 of the transmission, via which this can be coupled to the output of the motor vehicle.

Within the transmission there are fixed connections between the first sun 101 and the second sun 201, between the first carrier 103, the third carrier 303 and the fourth ring gear 402 and between the second ring gear 202 and the third sun 301.

Switchable couplings exist between the first sun 101 and the transmission housing shown without a separate reference number, namely by means of the first brake B1, between the first ring gear 102 and the housing, namely by means of the second brake B2, between the second web 203 and the fourth sun 401, namely by means of the first clutch K1, between the third sun 301 and the fourth sun 401, namely by means of the second clutch K2, and between the third ring gear 302 and the fourth sun 401, namely by means of the third clutch K3.

2 shows a non-inventive ten-speed transmission, which by simply adding a fourth clutch K4, which couples the third ring gear 302 switchable with the fourth carrier 403, from the transmission arrangement of 1 is derivable. Incidentally, to the above 1 said to be referenced.

The 3a , 3b and 3c each show a twelve-speed transmission not according to the invention, which by simply adding a fifth clutch K5, which couples one element of the third planetary gear set 30 switchable with another of its elements, from the transmission arrangement of FIG 2 is derivable. Through this coupling of two of its elements, the third planetary gear set 30 can be blocked in itself, so that it rotates as a block without internal relative movement. At the in 3a The embodiment shown are the elements that can be coupled in a switchable manner by means of the fifth clutch K5, the third sun 301 and the third web 303. In the case of FIG 3b The embodiment shown are the elements that can be coupled in a switchable manner by means of the fifth clutch K5, the third ring gear 302 and the third web 303. In the case of FIG 3c In the embodiment shown, the elements that can be coupled in a switchable manner by means of the fifth clutch K5 are the third sun gear 301 and the third ring gear 302. Incidentally, the same can be said for the above 1 said to be referenced.

In the 4 until 6 are isomorphisms of the gear arrangement of 1 shown. They have the same internal and external coupling scheme, but differ in the relative arrangement of the planetary gear sets to one another. The arrangement according to 4 is, as well as the arrangement of 1 , intended for the in-line installation of the drive unit, gearbox and output. The input shaft 1 and the output shaft 2 are therefore coupled on different sides of the transmission. Compared to the embodiment of 1 the first and second as well as the third and fourth planetary gear sets are swapped in pairs. The embodiments of 5 and 6 are intended for front-transverse installation. The input shaft 1 and the output shaft 2 are therefore coupled on the same side of the transmission. In the embodiment of 5 the planetary sets are arranged in an axial sequence to one another, as in the previously explained embodiments. In the embodiment of 6 on the other hand, the second planetary gear set 20 and the third planetary gear set 30 are arranged in a radially nested manner. In particular, the second planetary gear set 20 is arranged radially inside the third planetary gear set 30 . This is associated with an axial space saving.

The 7 until 9 represent corresponding isomorphisms to the gear arrangement of 2 In order to avoid repetition, reference is made here to the above on the one hand 2 and on the other hand to the 4 until 6 said referenced.

The 10 until 12 represent corresponding isomorphisms to the gear arrangement of 3a In order to avoid repetition, reference is made here to the above on the one hand 3a and on the other hand to the 4 until 6 said referenced.

The 13 until 15 represent corresponding isomorphisms to the gear arrangement of 3b In order to avoid repetition, reference is made here to the above on the one hand 3b and on the other hand to the 4 until 6 said referenced.

The 16 until 18 represent corresponding isomorphisms to the gear arrangement of 3c In order to avoid repetition, reference is made here to the above on the one hand 3c and on the other hand to the 4 until 6 said referenced.

Of course, the embodiments discussed in the specific description and shown in the figures only represent illustrative exemplary embodiments of the present invention. In particular, the special design of the individual planetary gear sets and the realization of special individual or group switching methods can take place in view of the requirements of the specific individual case.

Reference List

1

input shaft

2

output shaft

10

first set of planets

101

first sun

102

first ring gear

103

first jetty

20

second set of planets

201

second sun

202

second ring gear

203

second jetty

30

third planetary set

301

third sun

302

third ring gear

303

third jetty

40

fourth planetary set

401

fourth sun

402

fourth ring gear

403

fourth jetty

B1

first brake

B2

second brake

K1

first clutch

K2

second clutch

K3

third clutch

K4

fourth clutch

K5

fifth clutch

Claims (7)

Transmission arrangement for a motor vehicle, comprising - a first planetary set (10) with a first sun (101), a first ring gear (102) and a first carrier (103), on which a set of first planetary gears, which on the one hand are connected to the first sun (101 ) and on the other hand mesh with the first ring gear (102), - a second planetary set (20) with a second sun (201), a second ring gear (202) and an input shaft (1st ) connected second web (203), on which a set of second planetary gears, which mesh with the second sun (201) on the one hand and with the second ring gear (202) on the other hand, is rotatably mounted, - a third planetary gear set (30) with a third sun and - A fourth planetary gear set (40) with a fourth sun (401), a fourth ring gear (402) and a fourth web (403) which can be connected to an output shaft of the motor vehicle (2) and on which a set of fourth planetary gears, the on the one hand mesh with the fourth sun (401) and on the other hand with the fourth ring gear (402), is rotatably mounted, wherein - the first sun (101) with the second sun (201), the first web (103) with the fourth ring gear ( 402) and the second ring gear (202) is connected to the third sun (301), - the first sun (101) is shiftably coupled to a transmission housing by means of a first brake (B1), - the first sun gear by means of a second brake (B2). ring gear (102) is shiftably coupled to the transmission housing, - the second carrier (203) is shiftably coupled to the fourth sun (401) by means of a first clutch (K1), - the third sun (301) by means of a second clutch (K2) is switchably coupled to the fourth sun (401), - the third ring gear (302) is switchably coupled to the fourth sun (401) by means of a third clutch (K3) and the third carrier (103) is connected to the fourth ring gear (402). , characterized in that the second planetary gear set (20) is arranged radially inward of the third planetary gear set (30). Gear arrangement according to claim 1 , characterized in that by means of a fourth clutch (K4), the third ring gear (302) is switchably coupled to the fourth web (403). Gear arrangement according to claim 2 , characterized in that by means of a fifth clutch (K5) an element of the third planetary gearset (30) is switchably coupled to another element of the third planetary gearset (30). Gear arrangement according to claim 3 , characterized in that the third web (303) is switchably coupled to the third sun (301) by means of the fifth clutch (K5). Gear arrangement according to claim 3 , characterized in that by means of the fifth clutch (K5), the third web (303) is switchably coupled to the third ring gear (302). Gear arrangement according to claim 3 , characterized in that by means of the fifth clutch (K5), the third sun (301) is switchably coupled to the third ring gear (302). Motor vehicle with a drive train comprising a transmission arrangement which is coupled to a drive unit on the input side and to an output on the output side, characterized in that the transmission arrangement is designed as a transmission arrangement according to one of the preceding claims.

Images