EP3011200A1

EP3011200A1 - Multi-stage gear mechanism for a motor vehicle

Info

Publication number: EP3011200A1
Application number: EP14730753.2A
Authority: EP
Inventors: Tobias Schilder; Klaus Riedl; Jürgen Schweitzer; Tobias Härter; Thomas Kull
Original assignee: Daimler AG
Current assignee: Mercedes Benz Group AG
Priority date: 2013-06-22
Filing date: 2014-06-17
Publication date: 2016-04-27
Also published as: EP3011196B1; EP3011199A1; CN105229337B; EP3011199B1; US10323697B2; CN105324587A; WO2014202166A1; WO2014202211A1; WO2014202195A3; DE102013011566A1; DE102013011567A1; US9624985B2; US20160146309A1; EP3011195B1; JP6190050B2; JP2016524682A; JP6144830B2; WO2014202211A8; JP2016522375A; EP3011196A2

Abstract

The invention relates to a multi-stage gear mechanism for a motor vehicle, having a gear input shaft (10a; 10b; 10c; 10d) for connecting an internal combustion engine in a rotationally fixed fashion, having at least four planetary gear stages (P1a, P2a, P3a, P4a; P1b, P2b, P3b, P4b; P1c; P1d) arranged one behind the other along a main rotational axis (11a; 11b; 11c; 11 d), and at least one combined shifting unit (S2a; S2b; S2c; S2d) which is embodied as a brake and which has a rotatable coupling element (S21a; S21b; S21c; S21d) and a frictionally locking unit (12a; 12b; 12c; 12d) and a positively locking unit (13a; 13b; 13c; 13d) which is connected parallel to the frictionally locking unit (12a; 12b; 12c; 12d), which are each provided to connect the rotatable coupling element (S21a; S21b; S21c; S21d) so that it is fixed to the housing, wherein one of the planetary gear stages (P1a; P1b; P1c; P1d) is assigned to the combined shifting unit (S2a; S2b; S2c; S2d) and comprises a transmission element (P12a; P12b; P12c; P12d) which is permanently connected in a rotationally fixed fashion to the rotatable coupling element (S21a; S21b; S21c; S21d) of the combined shifting unit (S2a; S2b; S2c; S2d), wherein the planetary gear stage (P1a; P1b; P1c; P1d) which is assigned to the combined shifting unit (S2a; S2b; S2c; S2d) comprises a further transmission element (P11a; P11b; P11c; P11d) which is permanently connected to the transmission input shaft (10a; 10b; 10c; 10d) in a rotationally fixed fashion.

Description

Multi-speed transmission for a motor vehicle

The invention relates to a multistage transmission according to the preamble of claim 1.

From DE 10 201 1 108 024 A1 a multi-speed transmission for a motor vehicle is already known, which has a transmission input shaft for the rotationally fixed connection of a

Internal combustion engine, four along a main axis of rotation arranged successively planetary gear and a combined switching unit. The switching unit is designed as a brake and has a rotatable coupling element and a Reibschlusseinheit and a parallel to the Reibschlusseinheit switched

Forming unit, which are each provided to the rotatable

Coupling element fixed to the housing. One of the planetary gears of the

Multi-speed transmission from DE 10 201 1 108 024 A1 is associated with the combined switching unit and has a transmission element which is permanently connected in a rotationally fixed manner to the rotatable coupling element of the combined switching unit.

The invention is in particular the object of a power loss of

To reduce multi-stage transmission particularly space-neutral. This object is achieved by an inventive multi-stage transmission according to claim 1.

Further developments of the invention will become apparent from the dependent claims.

The invention is based on a multi-speed transmission for a motor vehicle, with a transmission input shaft for the rotationally fixed connection of an internal combustion engine, with at least four along a main axis of rotation arranged one behind the other

Planetary gear and at least one combined switching unit, which is formed as a brake and a rotatable coupling element and a Reibschlusseinheit and a parallel to the Reibschlusseinheit switched form-locking unit, which are each provided to connect the rotatable coupling element fixed to the housing, having one of the planetary gear stages of the combined Switching unit is assigned and a Includes transmission element which is permanently connected non-rotatably connected to the rotatable coupling element of the combined switching unit.

It is proposed that the combined switching unit associated

Planet wheel includes a further transmission element which is permanently connected in rotation with the transmission input shaft. As a result, a transmission element of a planetary gear stage embodied as an input stage can be connected to a transmission housing in a particularly advantageous frictional and / or positive-locking manner, so that switchable transmission gears with different torque requirements can be optimally switched loss-adjusted and conveniently by holding the transmission element. By assigning the combined switching unit to the planetary gear, which has a permanently non-rotatably connected to the transmission input shaft gear member, a space can be better utilized, whereby the multi-stage transmission can be made very compact. As a result, a power loss, in particular a towing power of the multi-speed transmission, can be reduced in a particularly space-neutral manner, in particular without provision of additional installation space. By "additional" should in particular additionally in comparison to a multi-stage transmission, which is a combined switching unit, the one formed as an input stage

Planet wheel is assigned missing. Under a "trained as a brake

Switching unit "should be understood in particular a switching unit, the

is operatively disposed between one of the planetary gear and the gear housing and which is intended to rotatably connect their rotatable coupling element in a closed state with the gear housing of the multi-speed transmission. In this context, a "form-locking unit" is to be understood as meaning, in particular, a part of the combined switching unit which has toothing and / or claws for the connection fixed to the housing and which engage in a form-fitting manner to produce a rotationally fixed coupling, such as, in particular, a coupling

Claws switching unit. In this context, a "friction-locking unit" is to be understood as meaning, in particular, a part of the combined shifting unit which has frictional elements, in particular slats, which are frictionally connected to one another to produce a rotationally fixed coupling, such as, in particular, a multiple-disk shift unit

Form-fitting unit are preferably arranged operatively between the gear housing and the rotatable coupling element of the combined switching unit. By "non-rotatably connected" is meant in particular a connection in which a power flow averaged over a complete revolution with an unchanged torque, an unchanged direction of rotation and / or an unchanged speed is transmitted. Under a "combined switching unit" is intended in particular a

Switching unit to be understood that for producing a rotationally fixed connection a Reibschlusseinheit and a frictional connection unit connected in parallel

Form-fitting unit, wherein the rotationally fixed connection through the

Ratchet unit alone, can be made by the form-locking unit alone or together by the Reibschlusseinheit and the form-locking unit. A "planetary gear stage associated with the combined shifting unit" is to be understood in particular as meaning a planetary gear wheel having at least one transmission element which is permanently connected in a rotationally fixed manner to the rotatable coupling element of the combined shifting unit. the at least one

Having transmission element which is permanently connected rotationally fixed to the transmission input shaft. "Provided" is to be understood in particular specially programmed, equipped, designed and / or arranged.

It is also proposed that the transmission element, which is permanently connected in a rotationally fixed manner to the transmission input shaft, assigned to the combined shifting unit

Planet wheel is designed as a sun gear. This can be one of the

Combustion engine provided drive torque over that of the combined

Switching unit associated planetary gear advantageous in the multi-stage transmission.

be initiated.

It is also proposed that the permanently rotatable with the rotatable

Coupling element of the combined switching unit connected gear element of the combined switching unit associated planetary gear is designed as a planet carrier, whereby the formed as an input stage planetary gear can be connected advantageously.

In particular, it is advantageous if the combined switching unit associated with the planetary gear has a trained as a ring gear member which is non-rotatably connected to a transmission element at least one other planetary gear at least, whereby the interconnection of the combined switching unit

associated planetary gear can be further improved. By "at least connectable" is to be understood in particular that the connection is either produced by a switching unit or permanently made. Further, it is advantageous if the rotatable coupling element of the combined

Switching unit rotatably with a transmission element at least one of the other

Planetenradstufen is at least connectable, whereby the combined switching unit can act on at least one other planetary gear.

Furthermore, it is advantageous if the multistage transmission has a drive-side

Housing end wall, wherein the combined switching unit associated planetary gear with respect to the other Planetenradstufen is arranged immediately adjacent to the drive-side housing end wall. As a result, the planetary gear stage assigned to the combined switching unit can be arranged on the drive side, as a result of which the combined switching unit can be allocated in a space-neutral manner to the planetary gear stage designed as an input stage. Under a "drive-side

Housing end wall "is to be understood in particular a housing end wall, which is arranged closer to the combustion engine compared to an axially opposite, output side housing end wall axially and / or along an emanating from the engine power flow closer to" arranged with respect to the other Planetenradstufen immediately adjacent to the housing end wall " in particular be understood that axially missing between the drive-side housing end wall and the combined switching unit associated planetary gear planetary gear. The term "axial" is particularly related to the main axis of rotation, so that the term "axial" refers to a direction that extends on the main axis of rotation or parallel to it.

In an advantageous embodiment, the Reibschlusseinheit and / or the

Form-fitting unit of the combined switching unit axially between the drive-side housing end wall and the combined switching unit associated

Planetenradstufe arranged, whereby a particularly compact multi-step transmission can be provided.

It is particularly advantageous if the form-fitting unit of the combined switching unit is located axially between the friction-locking unit and that of the combined switching unit

associated planetary gear is arranged, whereby the form-fitting unit can be designed particularly space-saving.

It is advantageous to place the form-locking unit on a small radius.

Optionally, the form-locking unit on an equal radius as the

Friction element be arranged. It is further proposed that the form-locking unit be radially inside the

Reibschlusseinheit is arranged, whereby a peripheral speed of a

Form-fitting teeth of the form-locking unit can be kept low. The term "radial" and the term "radius" are particularly related to the main axis of rotation, so that the term "radially" denotes a direction that is perpendicular to the main axis of rotation a form-locking unit are understood, the teeth and / or claws circulate on a circular path having a mean diameter which is smaller than a mean diameter of a circular path on the friction surfaces of the friction elements rotate.

It is also proposed that the multistage transmission comprises a further, designed as a clutch switching unit having a rotatable coupling element which is permanently connected in rotation with the transmission input shaft and a

Has outer disk carrier, at least partially in one piece with a

Inner disc carrier of Reibschlusseinheit the combined switching unit is formed. As a result, a space-saving design of the combined switching unit and the other switching unit can be realized. A "switching unit designed as a clutch" is to be understood in particular as meaning a switching unit which is provided to non-rotatably interconnect its two rotatably arranged coupling elements, which are independently rotatable in an open state, in a closed state trained switching unit in a power flow between at least two

Planet wheel arranged. The term "integral" should be understood to mean, in particular, a single piece, such as, for example, a single-piece production

Outer disk carrier formed inner disk carrier for receiving inner disk of Reibschlusseinheit the combined switching unit and for receiving

Outer blades of a Reibschlusseinheit the other switching unit provided.

In particular, it is advantageous if the form-fitting unit of the combined

Switching unit is arranged axially between the drive-side housing end wall and the further switching unit, whereby an alternative arrangement of the form-locking unit can be provided. Furthermore, it is advantageous if the combined switching unit has a first actuating unit provided for actuating the friction-locking unit and a second actuating unit provided for actuating the positive-locking unit and the further switching unit has a third actuating unit, wherein the first actuating unit and the third actuating unit axially between the drive-side housing end wall and the second actuating unit are arranged. This allows an advantageous operation of the combined switching unit and the other switching unit can be realized without providing additional space.

In an alternative embodiment, it is advantageous if the combined switching unit has a first actuating unit provided for actuating the friction-locking unit and a second actuating unit provided for actuating the positive-locking unit and the further switching unit has a third actuating unit

Actuator, the second actuator and the third actuator unit are arranged axially between the drive-side housing end wall and the Reibschlusseinheit the combined switching unit. Thereby, the form-fitting unit of the combined switching unit can be arranged radially inside the Reibschlusseinheit the combined switching unit and radially within a Reibschlusseinheit the other switching unit, whereby the peripheral speed of the form-fitting toothing can be further reduced. Furthermore, it can be realized that closing directions of the actuating units are all rectified, whereby a supply of the

Actuator with an actuating means for closing the

Reibschlusseinheiten and the form-locking unit can be simplified. A "closing direction" should be understood in particular a direction in which a

Actuator of the actuator unit must be moved to the

To close the frictional engagement unit or the form-locking unit. In this context, the term "rectified" should be understood to mean in particular that the closing directions point in the same direction. <br/> <br/> An "actuating element" is to be understood to mean, in particular, an axially movable element that presses the inner and outer disks of a friction-locking unit against one another to close the friction-locking unit or a form-fitting toothing of a form-locking unit moves into a corresponding positive-locking toothing of the form-fitting unit for closing the form-fitting unit.

In a further alternative embodiment, it is advantageous if the combined switching unit has a first one provided for actuating the friction-locking unit

Actuator and provided for actuating the form-locking unit second Actuating unit and the further switching unit comprises a third actuating unit, wherein the second actuating unit and the third actuating unit are arranged axially between the drive-side housing end wall and the first actuating unit. As a result, the form-fitting unit of the combined switching unit can be arranged in a particularly space-neutral manner radially inside the friction-locking unit of the further switching unit.

In addition, it is advantageous if, with respect to an axial sequence starting from the internal combustion engine, the one associated with the combined switching unit

Planetary gear as a first planetary gear and one of the combined switching unit associated planetary gear adjacent planetary gear as a second

Planetary gear is formed, wherein the adjacent planetary gear as a

Planet gear carrier has trained gear member which is permanently connected rotationally fixed with a gear formed as a ring gear of the combined switching unit associated planetary gear, and designed as a ring gear

Having gear element having a trained as a sun gear element of a third planetary gear and a trained as a sun gear

Transmission element of a fourth planetary gear is permanently connected rotationally fixed and rotatably connected to the planetary gear formed as a gear member of the combined switching unit associated planetary gear. As a result, a particularly advantageous interconnection of the planetary gear stages can be realized. With respect to the axial order of the planetary gear stages along an axial direction starting from the internal combustion engine, the first planetary gear stage is located in the first place, the second planetary gear stage second, the third planetary gear stage in third place and the fourth planetary gear stage in fourth place. A "planetary gear stage associated with the planetary gear stage associated with the combined switching unit" is to be understood in particular as meaning a planetary gear stage which is arranged axially next to the planetary gear stage associated with the combined switching unit.

The embodiment of a multi-speed transmission described below represents a special embodiment, to which there are basically further kinematically equivalent embodiments. For example, in particular the planetary gear stages can be formed by means of Einfachplanetenradsätzen, as shown below. In kinematically equivalent manner, one of

Have Planetenradstufen but also a Doppelplanetenradsatz, which must be adjusted for a same mode of action only a state translation of the planetary gear. In addition, a connection of a sun gear and a Are replaced by a ring gear or a ring gear and a planet carrier without a kinematics of the multi-speed transmission changes.

Further advantages will become apparent from the following description of the figures. In the figures, four embodiments of the invention are shown. The figures, the

DESCRIPTION OF THE FIGURES AND THE CLAIMS INCLUDE MULTIPLE FEATURES IN COMBINATION The person skilled in the art will expediently also consider the features individually and combine them into meaningful further combinations.

Showing:

1 is a transmission diagram of a multi-speed transmission according to the invention,

2 schematically shows the multi-stage transmission,

3 shows an alternately formed multistage transmission schematized,

Fig. 4 shows schematically a part of a multi-speed transmission in a third

Embodiment and

Fig. 5 shows schematically a part of a multi-speed transmission in a fourth

Embodiment.

Figures 1 and 2 show a multi-speed transmission of a motor vehicle. The motor vehicle has an internal combustion engine, not shown, for driving the motor vehicle and driving wheels not shown in detail. The multistage transmission is arranged in a power flow between the internal combustion engine and the drive wheels. The multistage transmission connects the combustion engine with the drive wheels. By means of the multi-speed transmission, a transmission ratio between the engine and the drive wheels is set. The multi-speed transmission can be connected to a hybrid drive module, by means of which a drive torque can be changed. Further, by means of the hybrid drive module and the multi-speed transmission, a CVT can be realized, whereby the transmission ratio can be adjusted continuously, at least in some areas.

To set ten gears, the multi-speed transmission has a gear 17a. The gear set 17a has nine forward gears and one reverse gear. The forward gears have sequential gear ratios. In this case, the first forward gear has the largest gear ratio and the last, in this embodiment ninth forward gear on the smallest gear ratio, wherein the gear ratio from the low to the high forward gear. The reverse gear has a direction of rotation reversal compared to the forward gears.

The multistage transmission furthermore has a transmission housing 18a, which comprises a drive-side housing end wall 14a, an output-side housing front wall 19a located axially opposite the drive-side housing end wall 14a, and a housing peripheral wall 20a arranged axially between the housing end walls 14a, 19a. In this embodiment, the housing end walls 14a, 19a and the housing peripheral wall 20a are formed integrally with each other. The gear set 17a is disposed inside the transmission case 18a. The transmission housing 18a is arranged stationary. In principle, at least one of the housing end walls 14a, 19a may be formed separately from the housing peripheral wall 20a.

To initiate a drive torque provided by the internal combustion engine in the gearset 17a, the multi-stage transmission has a transmission input shaft 10a. The transmission input shaft 10a passes through the drive-side housing end wall 14a and ends within the transmission housing 18a between the two housing end walls 14a, 19a. The transmission input shaft 10a is disposed in a power flow from the engine after the engine and before the gear train 17a. It is provided for the rotationally fixed connection of the internal combustion engine and thus for the rotationally fixed connection of a crankshaft of the internal combustion engine to the gear set 17a. The transmission input shaft 10a drivingly connects the engine with the gear set 17a. The transmission input shaft 10a may be preceded by a module not shown in detail, which in particular provides a start-up functionality. As an upstream module, for example, a torque converter or a wet starting clutch is conceivable. In principle, however, the module provided for starting can also be integrated in the gear set 17a.

To derive a translated drive torque, the multi-speed transmission has a transmission output shaft 21 a. The transmission output shaft 21 a passes through the output-side housing end wall 19 a and ends outside the transmission housing 18 a. The transmission output shaft 21a is disposed in the power flow from the engine after the gear train 17a and before the drive wheels. The transmission output shaft 21 a connects the gear set 17 a drive technology with the drive wheels of the motor vehicle. The transmission output shaft 21 a may be connected downstream of a module not shown in detail, by means of which the output from the gear set 17 a driven torque can be distributed to the drive wheels, such as example, a planetary gear, which is provided for a speed compensation between the drive wheels, or an all-wheel drive unit that distributes the drive torque to two different drive axles. The transmission input shaft 10a and the transmission output shaft 21a can basically be arranged arbitrarily to each other.

The gear set 17a has four planetary gear stages Pi a, P2a, P3a, P4a, which are operatively connected to each other for switching the gears. The first planetary gear stage Pi a, the second planetary gear P2a, the third planetary gear P3a and the fourth planetary gear P4a are arranged one behind the other along a main axis of rotation 1 1 a. An axis of rotation of the transmission input shaft 10a coincides with the main axis of rotation 1 1 a. All planetary gear stages Pi a, P2a, P3a, P4a of the gear set 17a have a Einfachplanetenradsatz. The terms "first", "second", "third" and "fourth" indicate an axial order of the planetary gear stages Pi a, P2a, P3a, P4a starting from the internal combustion engine. Accordingly, the first planetary gear Pi is compared to the other planetary gear P2a, P3a, P4a at the first axial position, the second planetary gear P2a compared to the other planetary gear stages Pi a, P3a, P4a at the second axial position, the third planetary gear P3a in comparison to the other planetary gear stages Pi a, P2a, P4a arranged at the third axial position and the fourth planetary gear P4a compared to the other planetary gear stages Pi a, P2a, P3a at fourth axial position.

The first planetary gear stage Pi a and the second planetary gear P2a are arranged adjacent to each other, the second planetary gear P2a and the third planetary gear P3a are adjacent to each other and the third planetary gear P3a and the fourth planetary gear P4a are adjacent to each other. The first planetary gear stage Pi a is disposed immediately adjacent to the drive-side housing end wall 14a with respect to the planetary gear stages P2a, P3a, P4a, i. the first planetary gear stage Pi a is arranged closest to the drive-side housing end wall 14a in comparison with the other planetary gear stages P2a, P3a, P4a. The fourth planetary gear P4a is arranged with respect to the planetary gear stages Pi a, P2a, P3a immediately adjacent to the drive-side housing end wall 19a, i. the fourth planetary gear P4a is compared to the other planetary gear stages Pi a, P2a, P3a closest to the drive-side housing end wall 19a arranged.

In the following, the four planetary gear stages Pi a, P2a, P3a, P4a are described in more detail. The four planetary gear stages Pi a, P 2 a, P 3 a, P 4 a each have a gear element designed as a sun gear, a gear element designed as a planet carrier and a trained as a ring gear element. For the sake of simplicity, a "first to fourth planetary gear carrier", a "first to fourth sun gear" and a "first to fourth ring gear" are to be understood as one of the first to fourth planetary gear carriers or a sun gear or a ring gear, ie, for example Under the first planet carrier designed as a planet carrier gear element of the first planetary gear to be understood.

The first planetary gear Pia is arranged on the input side. The first planetary gear Pia includes a first sun gear P1 1 a, a first ring gear P13a and a first planet P12a. The first planet carrier P12a leads planetary gears P14a of the first planetary gear Pia on a circular path. The planetary gears P14a mesh with the first sun gear P1 1 a and with the first ring gear P13a. The planetary gears P14a are rotatably supported on the first planet carrier P12a.

The second planetary gear P2a is arranged centrally on the input side. The second planetary gear P2a includes a second sun gear P21a, a second ring gear P23a, and a second planetary gear carrier P22a. The second planet carrier P22a leads planetary gears P24a of the second planetary gear P2a on a circular path. The planet gears P24a mesh with the second sun gear P21a and with the second ring gear P23a. The planetary gears P24a are rotatably supported on the second planet carrier P22a.

The third planetary gear P3a is arranged centrally on the output side. The third planetary gear P3a includes a third sun gear P31a, a third ring gear P33a, and a third planetary gear P32a. The third planet carrier P32a leads planetary gears P34a of the third planetary gear P3a on a circular path. The planetary gears P34a mesh with the third sun gear P31a and with the third ring gear P33a. The planetary gears P34a are rotatably supported on the third planet carrier P32a.

The fourth planetary gear P4a is arranged on the output side. The fourth planetary gear P4a includes a fourth sun gear P41a, a fourth ring gear P43a and a fourth planet carrier P42a. The fourth planet carrier P42a leads planetary gears P44a of the fourth planetary gear P4a on a circular path. The planet gears P44a mesh with the fourth sun gear P41a and with the fourth ring gear P43a. The planet gears P44a are rotatably supported on the fourth planet carrier P42a.

A part of the transmission elements of the planetary gear stages Pi a, P2a, P3a, P4a are permanently connected to each other in a rotationally fixed manner. The first ring gear P13a is permanently rotatable with the second planet carrier P22a connected. The second ring gear P23a is permanently non-rotatably connected to the third sun P31a and permanently rotatably connected to the fourth sun gear P41a. The third sun P31a and the fourth sun P41a are permanently connected to each other rotatably. To initiate the drive torque provided by the internal combustion engine, the first planetary gear stage Pia and the fourth planetary gear stage P4a are each designed as an input stage. To form the first planetary gear Pia as an input stage, the first sun P11a permanently connected rotationally fixed to the transmission input shaft 10a. To form the fourth planetary gear P4a as an input stage of the fourth planet P42a is permanently connected rotationally fixed to the transmission input shaft 10a. For discharging the drive torque translated by the gear set 17a, the third planetary gear P3a and the fourth planetary gear P4a are each formed as an output stage. To form the third planetary gear P3a as the output stage, the third planet P32a permanently connected rotationally fixed to the transmission output shaft 21a. To form the fourth planetary gear P4a as an output stage, the fourth ring gear P43a rotatably connected to the transmission output shaft 21 a connectable.

To shift the gears, the gear set 17a has six switching units S1a, S2a, S3a, S4a, S5a, S6a. The switching units S1a, S2a, S3a, S4a, S5a, S6a transmit different torques in the transmission gears. The gear set 17a defines for the switching units S1a, S2a, S3a, S4a, S5a, S6a torque factors in the transmission gears. By the torque factors in the gear trains of the switching units S1a, S2a, S3a, S4a, S5a, S6a transmitted torques defined in the gear set 17a. The torque factors are dependent on a position of the switching units S1a, S2a, S3a, S4a, S5a, S6a in the gear set 17a. The torques transmitted by the switching units S1a, S2a, S3a, S4a, S5a, S6a are dependent on a switched gear, the torque factor and a drive torque. The six switching units S1 a, S2a, S3a, S4a, S5a, S6a each have a total design torque. The respective overall design moments are based on a maximum torque to be transmitted from the respective shift unit S1 a, S2a, S3a, S4a, S5a, S6a in the associated transmission gears. The overall design torques are adapted to the gear shifts and may differ from switching unit S1a, S2a, S3a, S4a, S5a, S6a to switching unit S1a, S2a, S3a, S4a, S5a, S6a.

The three switching units S1 a, S3a, S6a are each formed as a coupling. They respectively have a first rotatable coupling element S11a, S31a, S61a and a second rotatable coupling element S11a. tes rotatable coupling element S12a, S32a, S62a. The three switching units S1 a, S3a, S6a are each provided to connect their two coupling elements S1 1 a, S12a, S31a, S32a, S61a, S62a rotation with each other.

The three switching units S2a, S4a, S5a are each formed as a brake. They each have a rotatable coupling element S21a, S41a, S51a. The switching units S2a, S4a, S5a are each provided to their rotatable coupling element S21 a, S41a, S51a fixed to the housing and thus rotatably connected to the transmission housing 18a to connect.

The first switching unit S1 a has the first rotatable coupling element S1 1 a and the second rotatable coupling element S12a. The first rotatable coupling element S11 a of the first switching unit S1a is permanently non-rotatably connected to the transmission input shaft 10a. The second rotatable coupling element S12a of the first switching unit S1a is permanently connected in a rotationally fixed manner to the rotatable coupling element S21a of the second switching unit S2a. The second rotatable coupling element S12a of the first switching unit S1a is further permanently non-rotatably connected to the first planet carrier P12a. Furthermore, the second rotatable coupling element S12a of the first switching unit S1a is permanently connected in a rotationally fixed manner to the first rotatable coupling element S31a of the third switching unit S3a. The first switching unit S1 a is provided to rotatably connect the first planet P12a with the transmission input shaft 10a.

The second switching unit S2a has the rotatable coupling element S21a. The rotatable coupling element S21 a of the second switching unit S2a is permanently connected in a rotationally fixed manner to the first planet carrier P12a. Further, the rotatable coupling element S21 a of the second switching unit S2a permanently non-rotatably connected to the first rotatable coupling element S31 a of the third switching unit S3a. The second switching unit S2a is provided to connect the first planet P12a fixed to the housing.

The third switching unit S3a has the first rotatable coupling element S31a and the second rotatable coupling element S32a. The first rotatable coupling element S31a of the third switching unit S3a is permanently connected in a rotationally fixed manner to the first planet carrier P12a. The second rotatable coupling element S32a of the third switching unit S3a is permanently connected in a rotationally fixed manner to the second ring gear P23a. The second rotatable coupling element S32a of the third switching unit S3a is further permanently non-rotatably connected to the third sun gear P31 a. Furthermore, the second rotatable coupling element S32a of the third switching unit S3a is permanently non-rotatably connected to the fourth sun gear P41 a connected. The third switching unit S3a is provided for non-rotatably connecting the first planet carrier P12a, the second ring gear P23a, the third sun gear P31a and the fourth sun gear P41a.

The fourth switching unit S4a has the rotatable coupling element S41a. The rotatable coupling element S41a of the fourth switching unit S4a is permanently connected in a rotationally fixed manner to the second sun gear P21a. The fourth switching unit S4a is provided to connect the second sun gear P21a fixed to the housing.

The fifth switching unit S5a has the rotatable coupling element S51a. The rotatable coupling element S51a of the fifth switching unit S5a is permanently connected in a rotationally fixed manner to the third ring gear P33a. The fifth switching unit S5a is provided to connect the third ring gear P33a fixed to the housing.

The sixth switching unit S6a has the first rotatable coupling element S61a and the second rotatable coupling element S62a. The first rotatable coupling element S61 a of the sixth switching unit S6a is permanently non-rotatably connected to the fourth ring gear P43a. The second rotatable coupling element S62a of the sixth switching unit S6a is permanently connected in a rotationally fixed manner to the third planet carrier P32a. The second rotatable coupling element S62a of the sixth switching unit S6a is further permanently non-rotatably connected to the transmission output shaft 21 a. The sixth switching unit S6a is provided for non-rotatably connecting the fourth ring gear P43a, the third planet carrier P32a and the transmission output shaft 21a.

The three switching units S1 a, S3a, S6a designed as a coupling have only one friction-locking unit 22a, 23a, 24a for the non-rotatable connection of their coupling elements S11a, S12a, S31a, S32a, S61a, S62a. The frictional engagement units 22a, 23a, 24a each comprise a disk pack. The fourth switching unit S4a and the fifth switching unit S5a point to the housing-fixed connection of their rotatable

Coupling elements S41 a, S51 a each only one Reibschlusseinheit 25a, 26a on. The frictional engagement units 25a, 26a each comprise a disk pack.

The Reibschlusseinheit 22 a of the first switching unit S1 a is axially between the

Drive-side housing end wall 14a and the first planetary gear Pi a

arranged. The first switching unit S1 a further comprises an inner disk carrier which is permanently connected in a rotationally fixed manner to the first rotatable coupling element S11 a of the first switching unit S1 a, and an outer disk carrier which is permanently non-rotatable is connected to the rotatable second coupling element S12a of the first switching unit S1 a, on. The inner disk carrier of the first switching unit S1 a is permanently non-rotatably connected to the transmission input shaft 10a. The Außeniameilenträger the first switching unit S1 a is permanently connected rotationally fixed to the first planet P12a.

The frictional engagement unit 23a of the third shift unit S3a is arranged axially between the first planetary gear stage Pia and the second planetary gear P2a. The first planetary gear stage Pi a is axially between the Reibschlusseinheit 22 a of the first

Switching unit S1a and the Reibschlusseinheit 23a of the third switching unit S3a arranged. The third switching unit S3a further comprises an inner disc carrier, which is permanently connected in a rotationally fixed manner to the second rotatable coupling element S32a of the third shift unit S3a, and an outer cam carrier, which is permanently connected in a rotationally fixed manner to the first rotatable coupling element S31a of the third shift unit S3a. The inner disk carrier of the third switching unit S3a is permanently connected in a rotationally fixed manner to the ring gear P23a. The outer mate carrier of the third

Switching unit S3a is permanently connected in a rotationally fixed manner to the first planet carrier P12a. Thus, the Außeniameilenträger the first switching unit S1 a and the Außeniameilenträger the third switching unit S3a permanently non-rotatably connected to each other.

The frictional engagement unit 25a of the fourth shift unit S4a is arranged axially between the first planetary gear stage Pi a and the third planetary gear P3a. The

Frictional engagement unit 25a of the fourth switching unit S4a is axially in the amount of the second

Planet wheel P2a arranged. The frictional engagement unit 25a of the fourth shift unit S4a is disposed axially between the frictional engagement unit 23a of the third shift unit S3a and the frictional engagement unit 26a of the fifth shift unit S5a. The second

Planetary gear P2a is axially between the Reibschlusseinheit 23a of the third

Switching unit S3a and the Reibschlusseinheit 26a of the fifth switching unit S5a arranged. The first planetary gear stage Pi a is arranged axially between the first switching unit S1 a and the fourth switching unit S4a. The first planetary gear stage Pi a is axially between the Reibschlusseinheit 22 a of the first switching unit S1 a and the

Reibschlusseinheit 25a of the fourth switching unit S4a arranged. The fourth switching unit S4a further comprises an inner disk carrier, which is permanently connected in a rotationally fixed manner to the rotatable coupling element S41a of the fourth switching unit S4a, and a

Außeniameilenträger which is permanently connected rotationally fixed to the transmission housing 18a, on. The inner disk carrier of the fourth switching unit S4a is permanently non-rotatable with the second sun P21 a connected. The outer disc carrier of the fourth

Switching unit S4a is connected to the housing peripheral wall 20a. It is attached to the housing peripheral wall 20a.

The frictional engagement unit 26a of the fifth shift unit S5a is disposed axially between the second planetary gear P2a and the fourth planetary gear P4a. The

Reibsschlussseinheit 26a of the fifth switching unit S5a is axially equal to the third

Planet wheel P3a arranged. The frictional engagement unit 26a of the fifth shift unit S5a is disposed axially between the frictional engagement unit 25a of the fourth shift unit S4a and the frictional engagement unit 24a of the sixth shift unit S6a. The third

Planetary gear P3a is axially between the Reibschlusseinheit 25a of the fourth

Switching unit S4a and the Reibschlusseinheit 24a of the sixth switching unit S6a arranged. The fifth switching unit S5a further comprises an inner disc carrier, which is permanently connected in a rotationally fixed manner to the rotatable coupling element S51a of the fifth shift unit S5a, and an outer disc carrier which is permanently connected in a rotationally fixed manner to the transmission housing 18a. The inner disc carrier of the fifth

Switching unit S5a is permanently rotatably connected to the third ring gear P33a. The outer disk carrier of the fifth shift unit S5a is connected to the housing peripheral wall 20a. It is attached to the housing peripheral wall 20a.

The frictional engagement unit 24a of the sixth shift unit S6a is located axially between the output-side housing front wall 19a and the fourth planetary gear P4a

arranged. The fourth planetary gear P4a is axially between the frictional engagement unit 26a of the fifth shift unit S5a and the frictional engagement unit 24a of the sixth

Switching unit S6a arranged. The sixth switching unit S6a also has a

Inner disc carrier, permanently rotatable with the first rotatable

Coupling element S61 a of the sixth switching unit S6a is connected, and an outer disk carrier, the permanent rotation with the second rotatable

Coupling element S62a of the sixth switching unit S6a is connected, on. Of the

Inner disk carrier of the sixth switching unit S6a is permanently connected in a rotationally fixed manner to the fourth ring gear P43a. The outer disk carrier of the sixth switching unit S6a is permanently non-rotatably connected to the third planetary P32a and permanently rotatably connected to the transmission output shaft 21a.

The second switching unit S2a is formed in combination and thus has a

Reibschlusseinheit 12a and in the power flow parallel to the Reibschlusseinheit 12a connected form-fitting unit 13a. The Reibschlusseinheit 12 a and the parallel switched form-fitting unit 13a are respectively provided to the rotatable

Coupling element S21 a of the second switching unit S2a fixed to the housing and thus rotatably connected to the transmission housing 18a to connect. The second switching unit S2a is formed as a combined switching unit. The first planetary gear stage Pi a is formed as one of the combined switching unit S2a associated planetary gear.

The combined switching unit S2a is the first formed as an input stage

Planetary gear stage associated with Pi a. The rotatable coupling element S21 a of

combined switching unit S2a is permanently rotatably connected to the planet P12a of the input stage designed as a first planetary gear Pia. The trained as input stage planetary gear Pi a is axially between the

Friction unit 12a of the combined switching unit S2a and the Reibschlusseinheit 25a of the fourth switching unit S4a arranged. The frictional engagement unit 12a transmits the torque applied to the first planet carrier P12a to the switched eighth forward gear and the switched ninth forward gear. The form-fitting unit 13a transmits the torque applied to the first planet carrier P12a only in the switched reverse gear.

The friction-locking unit 12a and the form-fitting unit 13a of the combined switching unit S2a each have a design moment. The design moment of the frictional engagement unit 12a and the design moment of the form-fitting unit 13a are different. The design torque of the frictional engagement unit 12a is smaller than the total design torque of the second shift unit S2a. The design moment of the form-fitting unit 13a corresponds to the total design moment of the second switching unit S2a. Thus, the design moment of the frictional engagement unit 12a is smaller than the design moment of the form-fitting unit 13a.

The second switching unit S2a transmits in the switched reverse gear, a torque which is greater than the design torque of the Reibschlusseinheit 12a and in the switched eighth and ninth forward gear, a torque which is smaller than the design torque of the Reibschlusseinheit 12a. In the eighth and ninth forward gear in which the applied torque is smaller than the design torque of the friction engagement unit 12a, the friction engagement unit 12a transmits the applied torque completely. In this embodiment, in the reverse gear in which the applied torque is larger than the design torque of the frictional engagement unit 12a, the form-fitting unit 13a also completely transmits the torque. In principle, it is also conceivable that the interlocking unit 13a in at least one of the gears, in which the applied torque is greater than the design torque of the Reibschlusseinheit 12a, only transmits an excess torque. Here, the excess torque is approximately a difference between the applied torque and the design torque of the frictional engagement unit 12a.

The frictional engagement unit 12a of the combined shift unit S2a is formed as a multi-disc brake. The frictionally engaging unit 12a comprises a disk pack for the housing-fixed connection of the rotatable coupling element S21a. Furthermore, the friction-locking unit 12a of the combined switching unit S2a has an outer disk carrier 15a, which is permanently connected in a rotationally fixed manner to the transmission housing 18a, and an inner disk carrier 16a, which is permanently connected in a rotationally fixed manner to the rotatable coupling element S21a. The inner disk carrier 16a of the combined switching unit S2a is permanently connected in a rotationally fixed manner to the planet carrier P12a of the first planetary gear stage Pi a designed as an input stage. The inner disk carrier 16a of the combined switching unit S2a is formed integrally with the outer disk carrier of the first switching unit S1a. The friction-locking unit 12a is operatively arranged between the drive-side housing end wall 14a and the rotatable coupling element S21a. The outer plate carrier 15a of the combined switching unit S2a is connected to the drive-side housing end wall 14a. It is attached to the drive-side housing end wall 14a. Alternatively, the outer disk carrier 15a may also be connected in a more radial direction to a housing peripheral wall of the transmission housing 18a.

The form-fitting unit 13a of the combined switching unit S2a is designed as a claw brake. The form-fitting unit 13a comprises a first form-fitting element 27a and a second form-fitting element 28a. The first positive locking element 27a is permanently connected in a rotationally fixed manner to the rotatable coupling element S21 of the combined switching unit S2a. It is rotatably connected to the inner disk carrier 16a of the combined switching unit S2a. The first positive locking element 27a has a dog toothing. The dog teeth are fixedly mounted on the rotatable coupling element S21 a of the combined switching unit S2a. The first positive engagement element 27a is formed integrally with the rotatable coupling element S21a of the combined shift unit S2a. The second positive locking element 28a is non-rotatably, but axially displaceably connected to the transmission housing 18a. It is rotationally fixed, but axially slidably connected to the housing peripheral wall 20a. The form-fitting unit 13a is operatively disposed between the housing peripheral wall 20a and the rotatable coupling member S21a. The second positive locking element 28a has a dog toothing, which is formed corresponding to the dog teeth of the first positive-locking element 27a. The dog teeth are each formed as a spur toothing. The second positive locking element 28a is arranged to be axially movable relative to the first positive locking element 27a.

The Reibschlusseinheit 12 a and the form-fitting unit 13 a of the combined

Switching unit S2a are arranged axially between the drive-side housing end wall 14a and the first planetary gear stage Pia designed as an input stage. The

Disc pack of Reibschlusseinheit 12a and the claw toothing of

Form-fitting unit 13a are arranged axially between the housing end wall 14a and formed as an input stage first planetary gear Pi a.

The frictional engagement unit 12a of the combined shift unit S2a is arranged axially at the level of the frictional engagement unit 22a of the first shift unit S1a. The disk set of the friction engagement unit 12a of the combined shift unit S2a is radially above

Disk set of Reibschlusseinheit 22a of the first switching unit S1 a arranged. The disk set of the friction engagement unit 22a of the first shift unit 5a is arranged radially inside the disk pack of the friction engagement unit 12a of the combined shift unit S2a. A mean diameter of a through a friction surface of the

Lamella packages of the combined switching unit S2a formed annular surface is greater than a mean diameter of an annular surface formed by a friction surface of the disk set of the first switching unit S1 a.

The form-fitting unit 13a of the combined switching unit S2a is arranged axially between the friction-locking unit 12a of the combined switching unit S2a and the first planetary gear stage Pia designed as an input stage. The frictional engagement unit 12a of the combined shift unit S2a is disposed axially between the drive-side housing end wall 14a and the form-fitting unit 13a of the combined shift unit S2a. The form-fitting unit 13a of the combined switching unit S2a is arranged axially between the first switching unit S1a and the first planetary gear stage Pia designed as an input stage.

The form-fitting unit 13a of the combined switching unit S2a is arranged radially inside the friction-locking unit 12a of the combined switching unit S2a. The

Form-fitting unit 13a of the combined switching unit S2a is radially in the amount of

Disc packs of Reibschlusseinheit 22a of the first switching unit S1 a arranged. An average diameter of one through the dog teeth of the combined switching unit S2a formed annular surface is smaller than the average diameter of the through

Friction surface of the disk set of the combined switching unit S2a formed

Annular surface. The mean diameter of the annular surface formed by the dog teeth of the second switching unit S2a is between an inner and

Outer diameter of the annular surface formed by the friction surface of the disk set of the first switching unit S1 a.

For actuating the friction-locking unit 12a and the form-locking unit 13a, the combined switching unit S2a has two independent actuating units 29a, 30a. The first operation unit 29a operates the friction engagement unit 12a. The first actuating unit 29a has an axially movable actuating element, which presses against the housing-fixed connection of the rotatable coupling element S21 a of the combined switching unit S2a axially against the disk set of the Reibschlusseinheit 12a of the combined switching unit S2a, which move slats of the disk set axially relative to each other until they lie against each other and are positively connected with each other. The first operating unit 29a is on the drive side

Housing end wall 14a connected. It is attached to the drive-side housing end wall 14a. The first operating unit 29a is disposed axially between the frictional engagement unit 12a of the combined switching unit S2a and the drive-side housing end wall 14a. It is axially between the form-locking unit 13 a of the combined

Switching unit S2a and the drive-side housing end wall 14a arranged. The first operating unit 29a is axially between the Reibschlusseinheit 22a of the first

Switching unit S1 a and the drive-side housing end wall 14a arranged.

The second operating unit 30a actuates the form-locking unit 13a. The second

Actuator 30a has an axially movable actuator which is fixedly connected to the second positive locking element 28a and axially displaceable, but rotatably connected to the transmission housing 18a. For housing-fixed connection of the rotatable coupling element S21a of the combined switching unit S2a moves the

Actuating element of the second actuating unit 30a and thereby the second

Positive locking element 28a axially in the direction of the first positive locking element 27a until the correspondingly formed to each other dog teeth of the form-locking unit 13a of the combined switching unit S2a intermesh positively. to

fixed to the housing connection of the rotatable coupling element S21 a of the combined switching unit S2a, the second positive locking element 28a is axially in the direction

Reibschlusseinheit 12a of the combined switching unit S2a shifted. The second operating unit 30a is connected to the housing peripheral wall 20a. She is at the Housing peripheral wall 20a attached. The second operating unit 30a is arranged axially between the third switching unit S3a and the drive-side housing end wall 14a. It is axially between the Reibschlusseinheit 12 a of the combined

Switching unit S2a and the third switching unit S3a arranged. The second

Actuator 30a radially surrounds partially the first switching unit S1 a. The rotatable coupling element S21 a of the combined switching unit S2a or the rotatable

Coupling element S12a of the first switching unit S1a are partially disposed within the second operating unit 30a. The second operating unit 30a of the combined switching unit S2a partially surrounds the rotatable coupling element S21a of FIG

combined switching unit S2a and the rotatable coupling element S12a of the first switching unit S1 a.

For actuating the friction-locking unit 22a of the first switching unit S1a, the first switching unit S1a has an actuating unit 31a. The operating unit 31a of the first switching unit S1a and the first operating unit 29a of the combined switching unit S2a are arranged axially between the drive-side housing end wall 14a and the second actuating unit 30a of the combined switching unit S2a. The

Actuator 31 a of the first switching unit S1 a is axially between the

Reibschlusseinheit 22a of the first switching unit S1 a and the drive side

Housing end wall 14a arranged. It is arranged axially between the form-locking unit 13a of the combined switching unit S2a and the drive-side housing end wall 14a. The operating unit 31a of the first switching unit S1a is disposed radially inside the first operating unit 29a of the combined switching unit S2a. The actuating element of the first actuating unit 29a of the combined switching unit S2a radially surrounds the actuating unit 31a of the first switching unit S1a.

The actuating units 29a, 30a, 31a each have an axial closing direction into which the corresponding actuating element for closing the friction-locking unit 12a or the form-locking unit 13a is moved. The closing direction of the first

Actuating unit 29a of the combined switching unit S2a and the closing direction of the operating unit 31 a of the first switching unit S1 a are the same direction. The

Closing direction of the first operating unit 29a of the combined switching unit S2a and the closing direction of the actuating unit 31 a of the first switching unit S1a point away from the drive-side housing end wall 14a and to the output side

Housing end wall 19a out. The closing direction of the second operating unit 30a of the combined switching unit S2a is the closing direction of the first operating unit 29a of the combined switching unit S2a and the closing direction of the operating unit 31a the first switching unit S1 a opposite. The closing direction of the second

Operating unit 30a of the combined switching unit S2a points away from the output-side housing end wall 19a and toward the drive-side housing end wall 14a.

The actuator units 29a, 30a, 31a are each formed hydraulically.

In principle, however, the actuating units 29a, 30a, 31a can also be designed electrically or pneumatically. The switching units S1a, S2a, S3a, S4a, S5a, S6a and the actuator units 29a, 30a, 31a are within the transmission housing 18a

arranged. Basically, the combined switching unit S2a for actuating the Reibschlusseinheit 12a and the form-locking unit 13a a common

Actuating unit or two mutually dependent actuation units. In this case, the friction-locking unit 12a and the form-fitting unit 13a are actuated in succession, wherein the friction-locking unit 12a preferably engages in front of the form-locking unit 13a.

Three further embodiments of the invention are shown in FIGS. The following descriptions are essentially limited to the differences between the exemplary embodiments, with regard in principle also to the figures and / or the description of the other embodiments, in particular of the embodiment in Figures 1 and 2, can be referenced. to

Distinction of the embodiments, the letter a in the reference numerals of the embodiment in Figures 1 and 2 is replaced by the letter b, c and d in the reference numerals of the embodiments in Figures 3 to 5.

FIG. 3 shows a second exemplary embodiment of a multistage transmission

Motor vehicle shown. The multistage transmission comprises a transmission input shaft 10b, four along a main axis of rotation 1 1 b arranged one behind the other

Planetenradstufen P1 b, P2b, P3b, P4b and six switching units S1 b, S2b, S3b, S4b, S5b, S6b. The planetary gear stages P1b, P2b, P3b, P4b each have a sun gear P11b, P21b, P31b, P41b, a planet carrier P12b, P22b, P32b, P42b, and a ring gear P13b, P23b, P33b, P43b. The multi-speed transmission continues to point

Transmission housing 18 b, the drive-side housing end wall 14 b, a

Output-side housing end wall 19b and a housing peripheral wall 20b includes.

The first switching unit S1 b is formed as a coupling and has a first rotatable coupling element S1 1 b and a second rotatable coupling element S12b on, wherein the first rotatable coupling element S11 b permanently non-rotatably connected to the transmission input shaft 10b and the second rotatable coupling element S12d permanently rotatably connected to the planet P12d of the first planetary gear P1 b. The second switching unit S2b is formed as a brake and has a rotatable coupling element S21 b, which is fixed to the housing, on. The second switching unit S2b further comprises a Reibschlusseinheit 12b and a parallel to the Reibschlusseinheit 12b connected form-locking unit 13b, which are each provided to connect the rotatable coupling element S21 b fixed to the housing. The second switching unit S2a is formed as a combined switching unit and associated with the first planetary gear Pia, which is formed as an input stage, whereby the first

Planet wheel stage Pi a as one of the combined switching unit S2a assigned

Planet wheel is formed. Furthermore, the second switching unit S2b comprises an inner disk carrier 16b, which is non-rotatably connected to the rotatable coupling element S21b, and an outer disk carrier 15b, which is arranged fixed to the housing. The outer disc carrier 15b is preferably connected to the housing end wall 14b or alternatively to a transmission housing peripheral wall.

In contrast to the previous embodiment, the form-fitting unit 13b of the combined switching unit S2b is axially between the Reibschlusseinheit 12b of

combined switching unit S2b and the drive-side housing end wall 14b arranged. The form-fitting unit 13b of the combined switching unit S2b is arranged axially between the first switching unit S1b and the drive-side housing end wall 14b.

The form-fitting unit 13b has dog teeth, which, in contrast to the previous embodiment, are arranged radially inside a friction-locking unit 22b of the first switching unit S1b. A mean diameter of one through the

Claw teeth of the combined switching unit S2b formed annular surface is smaller than a mean diameter of an annular surface formed by a friction surface of the Reibschlusseinheit 22b of the first switching unit S1 b.

The combined switching unit S2b comprises a first actuating unit 29b, which is provided for actuating the friction-locking unit 12b, and a second actuating unit

Actuator 30b, which is provided for actuating the form-locking unit 13b. In contrast to the previous exemplary embodiment, the second actuating unit 30b is arranged radially within the first actuating unit 29b. The

Claw teeth of the form-fitting unit 13b are radially inward of the first one Actuator 29b of the combined switching unit S2b arranged. One

Actuating member of the first operating unit 29b of the combined switching unit S2b surrounds the form-fitting unit 13b. Unlike the previous one

Embodiment, the form-fitting unit 13b is operatively arranged between the drive-side housing end wall 14b and the rotatable coupling element S21 b. The second operating unit 30b of the combined switching unit S2b is connected to the drive-side housing end wall 14b. It is attached to the drive-side housing end wall 14b. The friction engagement unit 12b and the form-fitting unit 13b are both operatively disposed between the drive-side housing end wall 14b and the rotatable coupling element S21b.

The first switching unit S1 b has an actuating unit 31 b, which is provided for actuating the Reibschlusseinheit 22 b of the first switching unit S1 b. In contrast to the previous embodiment, the form-fitting unit 13b is the

Combined switching unit S2b arranged axially between the actuating unit 31 b of the first switching unit S1 b and the drive-side housing end wall 14b. The first operating unit 29b of the combined switching unit S2b, the second operating unit 30b of the combined switching unit S2b and the operating unit 31b of the first

Switching unit S1 b are arranged axially between the drive-side housing end wall 14b and the Reibschlusseinheit 12b of the combined switching unit S2b. The

Actuator 31 b of the first switching unit S1 a is axially between the

Form-fitting unit 13b of the combined switching unit S2b and the Reibschlusseinheit 22b of the first switching unit S1 b arranged. It is axial between the

Forming connection unit 13b of the combined switching unit S2b and the combined switching unit S2a associated planetary gear P1 b arranged. The

Forming unit 13b of the combined switching unit S2b is disposed axially between the second operating unit 30b of the combined switching unit S2b and the operating unit 31b of the first switching unit S1b.

The actuating units 29b, 30b, 31b each have an axial closing direction into which the corresponding actuating element for closing the friction-locking unit 12b or the form-locking unit 13b is moved. The closing direction of the first

Actuating unit 29b of the combined switching unit S2b, the closing direction of the second operating unit 30b of the combined switching unit S2b and the

Closing direction of the actuating unit 31 b of the first switching unit S1 b are the same direction. The closing direction of the first operating unit 29b of the combined

Switching unit S2b, the closing direction of the second operating unit 30b of Combined switching unit S2b and the closing direction of the actuating unit 31 b of the first switching unit S1 b respectively point away from the drive-side housing end wall 14b and toward the output-side housing front wall 19b.

4 shows a third embodiment of a multi-speed transmission of a

Motor vehicle shown. The multistage transmission comprises a transmission input shaft 10 c, four along a main axis of rotation 11 c arranged one behind the other

Planetary gear stages and six switching units, wherein in the figure 4, only the first planetary gear P1 c, the first switching unit Si c, the second switching unit S2c and the third switching unit S3c are shown. The first planetary gear P1 c has a sun gear P1 1c, a planet P12c and a ring gear P13c. The second switching unit S2c is formed as a combined switching unit and the first planetary gear P1 c, which is formed as an input stage, assigned, whereby the first planetary gear P1 c is formed as one of the combined switching unit S2c associated planetary gear. The multi-speed transmission continues to point

Gear housing 18c, which includes a drive-side housing end wall 14c, a non-illustrated output-side housing end wall and a housing peripheral wall 20c.

The first switching unit Sic is designed as a clutch and has a first rotatable coupling element S11 c and a second rotatable coupling element S12c, wherein the first rotatable coupling element S1 1 c permanently rotatably with the transmission input shaft 10c and the second rotatable coupling element S12c permanently rotatably connected to the planet P12c of the combined switching unit S2c associated planetary gear P1 c is connected. The combined switching unit S2c is formed as a brake and has a rotatable coupling element S21 c, which is fixed to the housing, on. The combined switching unit S2c further comprises a Reibschlusseinheit 12c and a parallel to Reibschlusseinheit 12c connected

Forming unit 13c, which are each provided to the rotatable

Coupling element S21 c fixed to the housing to connect. Furthermore, the combined switching unit S2c comprises an inner disk carrier 16c, which is non-rotatable with the rotatable

Coupling element S21 c is connected, and an outer disk carrier 15 c, which is arranged fixed to the housing. In contrast to the previous embodiment, the Reibschlusseinheit 12c is operatively disposed between the housing peripheral wall 20c and the rotatable coupling element S21 c. The outer disk carrier 15c of the friction engagement unit 12c is advantageously connected to the housing peripheral wall 20c. It is attached to the housing peripheral wall 20c. Alternatively, the

External disk carrier 15c also be connected to the housing end wall 14c.

The combined switching unit S2c includes a first operating unit 29c provided for operating the friction engaging unit 12c, and a second operating unit 30c provided for operating the form-locking unit 13c. In contrast to the previous exemplary embodiment, the first actuating unit 29c of the combined switching unit S2c is arranged axially between the housing end wall 1c and the planetary gear stage P1c associated with the combined switching unit S2c. One

Actuating member of the first operating unit 29c surrounds the second rotatable coupling element S12c of the first switching unit Sic. The second rotatable

Coupling element S12c of the first switching unit Sic is disposed radially inside the first operating unit 29c of the combined switching unit S2c. The

Frictional engagement unit 12c of the combined shift unit S2c is disposed axially between the drive-side housing end wall 14c and the first operation unit 29c of the combined shift unit S2c. The first operating unit 29c of the combined switching unit S2c is connected to the housing peripheral wall 20c. It is attached to the housing peripheral wall 20c.

The first switching unit S1 b has an actuating unit 31 c, which is provided for actuating a Reibschlusseinheit 22 c of the first switching unit Si c. In contrast to the previous embodiment, the second operating unit 30c of the combined switching unit S2c and the actuating unit 31c of the first switching unit Si c are axially between the drive-side housing end wall 14c and the first

Actuator 29 c of the combined switching unit S2 c arranged. The

Frictional engagement unit 12c of the combined shift unit S2c is disposed axially between the first operation unit 29c of the combined shift unit S2c and the operation unit 31c of the first shift unit Sic.

The actuating units 29c, 30c, 31c each have an axial closing direction into which the corresponding actuating element for closing the friction-locking unit 12c or the form-locking unit 13c is moved. In contrast to the previous embodiments, the closing direction of the second operating unit 30c of the combined switching unit S2c and the closing direction of the operating unit 31c of the first switching unit Sic are the same. The closing direction of the second

Actuating unit 30c of the combined switching unit S2c and the closing direction of the operating unit 31c of the first switching unit Sic point from the driving side Housing end wall 14c away and to the output side housing end wall. The

Closing direction of the first operating unit 29c of the combined switching unit Si c is opposite to the closing direction of the second operating unit 30c of the combined switching unit S2c and the closing direction of the operating unit 31c of the first switching unit Si c. The closing direction of the first operating unit 29 c of

combined switching unit S2c shows away from the output-side housing end wall and the drive-side housing end wall 14c out.

FIG. 5 shows a fourth exemplary embodiment of a multistage transmission

Motor vehicle shown. The multistage transmission comprises a transmission input shaft 10d, four along a main axis of rotation 1 1d arranged one behind the other

Planetary gear stages and six switching units, wherein in the figure 5, only the first planetary gear P1d, the first switching unit S1d, the second switching unit S2d and the third switching unit S3d are shown. The first planetary gear P1 d has a sun gear P1 1d, a planet P12d and a ring gear P13d. The second switching unit S2d is designed as a combined switching unit and associated with the first planetary gear P1d, which is formed as an input stage, whereby the first planetary gear P1d is formed as one of the combined switching unit S2d associated planetary gear. The multi-speed transmission continues to point

Gear housing 18d, which comprises a drive-side housing end wall 14d and a housing peripheral wall 20d.

The first switching unit S1d is designed as a clutch and has a first rotatable coupling element S1 1d and a second rotatable coupling element S12d, the first rotatable coupling element S1 1d permanently non-rotatably connected to the transmission input shaft 10d and the second rotatable coupling element S12d permanently rotatably with the planet P12d the planetary gear P1d associated with the combined switching unit S2d is connected. The combined switching unit S2d is formed as a brake and has a rotatable coupling element S21d, which is fixed to the housing connectable on. The combined switching unit S2d further comprises a Reibschlusseinheit 12d and a parallel to Reibschlusseinheit 12d connected

Forming unit 13d, which are each provided to the rotatable

Coupling element S21d fixed to the housing to connect. Furthermore, the combined switching unit S2d comprises an inner disk carrier 16d, which is non-rotatably connected to the rotatable coupling element S21d, and an outer disk carrier 15d, which is arranged fixed to the housing. The combined switching unit S2d comprises a first actuating unit 29d, which is provided for actuating the friction-locking unit 12d, and a second actuating unit 29d

Actuator 30d, which is provided for actuating the form-locking unit 13d. The first switching unit S1d has an actuating unit 31d, which is provided for actuating a friction-locking unit 22d of the first switching unit S1d. The second operating unit 30d of the combined switching unit S2d and the operating unit 31d of the first switching unit S1d are located axially between the drive side

Housing end wall 14 d and the first actuator unit 29 d of the combined

Switching unit S2d arranged. Unlike the previous one

In the embodiment, the second operating unit 30d of the combined switching unit S2d is connected to the housing peripheral wall 20d. Alternatively, the second

Actuator 30d also be connected to the housing end wall 14d. The second operating unit 30d of the combined switching unit S2d is at the

Housing peripheral wall 20d attached. The Reibschlusseinheit 12 d and the

Form-fitting unit 13d are both operatively disposed between the housing peripheral wall 20d and the rotatable coupling member S21d.

The operating unit 31d of the first switching unit S1d is disposed radially inside the second operating unit 30d of the combined switching unit S2d. The second operating unit 30d of the combined switching unit S2d radially surrounds the

Forming unit 13d of the combined switching unit S2d. It is the

Reibschlusseinheit 12d the combined switching unit S2d axially between the

Actuating unit 31 d of the first switching unit S1 a and the first operating unit 29d of the combined switching unit S2d arranged.

Claims

claims

Multi-speed transmission for a motor vehicle, having a transmission input shaft (10a, 10b, 10c, 10d) for non-rotatably connecting an internal combustion engine, having at least four along a main axis of rotation (1 1 a; 1 1 b; 1 1c; 1 1d)

planetary gear stages (Pi, P2a, P3a, P4a; P1b, P2b, P3b, P4b; P1c; P1d) and at least one combined switching unit (S2a; S2b; S2c; S2d) formed as a brake; a rotatable

Coupling element (S21a; S21b; S21c; S21d) and a friction-locking unit (12a; 12b; 12c; 12d) and a form-locking unit (13a; 13b; 13c; 13d) connected in parallel with the friction-locking unit (12a; 12b; 12c; 12d). each of which is provided to connect the rotatable coupling element (S21 a; S21 b; S21 c; S21d) fixed to the housing, wherein one of the planetary gear stages (Pi a; P1 b, P1 c; P1d) of the combined switching unit (S2a; S2b; S2c; S2d) and a

Transmission element (P12a; P12b; P12c; P12d) which is permanently non-rotatably connected to the rotatable coupling element (S21a; S21b; S21c; S21d) of the combined switching unit (S2a; S2b; S2c; S2d),

characterized in that

that associated with the combined switching unit (S2a; S2b; S2c; S2d)

Planetary gear stage (Pi a; P1 b; P1 c; P1d) comprises a further transmission element (P1 1a; P11b; P1 1 c; P11d) which is permanently connected in a rotationally fixed manner to the transmission input shaft (10a; 10b; 10c; 10d). Multi-step transmission according to claim 1,

characterized in that

the gear member (P1a; P11b; P1c; P1dd) permanently connected to the transmission input shaft (10a; 10b; 10c; 10d) of the planetary gear stage (P1a; P1b) associated with the combined shift unit (S2a; S2b; S2c; S2d) b; P1 c P1d) is formed as a sun gear.

Multi-step transmission according to Claim 1 or 2,

characterized in that

permanently rotatably connected to the rotatable coupling element (S21a; S21b; S21c; S21d) of the combined switching unit (S2a; S2b; S2c; S2d)

Gear element (P12a, P12b, P12c, P12d) of the combined switching unit (S2a; S2b; S2c; S2d) associated planetary gear stage (Pi a; P1 b, P1 c, P1 d) is formed as a planet carrier.

Multi-step transmission according to one of the preceding claims,

characterized in that

that associated with the combined switching unit (S2a; S2b; S2c; S2d)

Planetary gear (Pi a, P1 b, P1 c, P1 d) designed as a ring gear

P13a, which is non-rotatably at least connectable to a transmission element (P22a, P22b) of at least one other planetary gear stage (P2a, P2b).

Multi-step transmission according to one of the preceding claims,

characterized in that

the rotatable coupling element (S21a; S21b; S21c; S21d) of the combined switching unit (S2a; S2b; S2c; S2d) is non-rotatably connected to a transmission element (P23a, P31a, P41a, P23b, P31b, P41b) of at least one of the other planetary gear stages (P2a, P3a, P4a, P2b, P3b, P4b) is at least connectable.

6. Multi-step transmission according to one of the preceding claims, characterized by

a planetary gear stage (Pi a; P1b; P1c; P1d) associated with the combined switching unit (S2a; S2b; S2c; S2d) with respect to the other planetary gear stages (P2a, P3a , P4a, P2b, P3b, P4b) immediately adjacent to the drive-side housing end wall (1a, 14b, 14c, 14d).

7. Multi-step transmission according to claim 6,

characterized in that

the frictional engagement unit (12a; 12b; 12c; 12d) and / or the form-locking unit (13a; 13b; 13c; 13d) of the combined switching unit (S2a; S2b; S2c; S2d) are arranged axially between the drive-side housing end wall (14a; 14b; 14c; 14d ) and the planetary gear stage (Pia; P1b; P1c; P1d) associated with the combined switching unit (S2a; S2b; S2c; S2d).

8. Multi-step transmission according to one of the preceding claims,

characterized in that

the form-locking unit (13a) of the combined switching unit (S2a) is arranged axially between the friction-locking unit (12a) and the planetary gear stage (Pia) associated with the combined switching unit (S2a).

9. Multi-step transmission according to one of the preceding claims,

characterized in that

the form-locking unit (13a; 13b; 13c; 13d) is arranged radially inside the friction-locking unit (12a; 12b; 12c; 12d).

10. Multi-step transmission according to one of the preceding claims, characterized by

a further coupling unit (S1a; S1b; Sic; S1d) which has a rotatable coupling element (S1 1a; S1 1 b, S1 1c; S1 1 d) which is permanently non-rotatably connected to the transmission input shaft (10a; 10b 10c; 10d) and having an outer disc carrier which is at least partially integral with an inner disc carrier (16a, 16b; 16c; 16d) of the frictional engagement unit (12a; 12b; 12c; 12d) of the combined shift unit (S2a; S2b; S2c; S2d ) is trained.

11. Multi-speed transmission at least according to claims 6 and 10,

characterized in that

the form-fitting unit (13b; 13c; 13d) of the combined switching unit (S2b; S2c; S2d) is arranged axially between the drive-side housing end wall (14b; 14c; 14d) and the further switching unit (S1b; Si c; S1d).

12. Multi-speed transmission at least according to claims 6 and 10,

characterized in that

the combined switching unit (S2a) comprises a first actuating unit (29a) provided for actuating the friction-locking unit (12a) and a second actuating unit (30a) provided for actuating the form-locking unit (13a) and the further switching unit (S1a) comprises a third actuating unit (31a) wherein the first actuating unit (29a) and the third actuating unit (31a) are arranged axially between the drive-side housing end wall (14a) and the second actuating unit (30a).

13. Multi-speed transmission at least according to claims 6 and 10, characterized in that

the combined switching unit (S2b) comprises a first actuating unit (29b) provided for actuating the friction-locking unit (12b) and a second actuating unit (30b) provided for actuating the form-locking unit (13b) and the further switching unit (S1b) comprises a third actuating unit (31b) wherein the first operating unit (29b), the second operating unit (30a) and the third operating unit (31b) are arranged axially between the drive-side housing end wall (14b) and the Reibschlusseinheit (12b) of the combined switching unit (S2b).

14. Multi-speed transmission at least according to claims 6 and 0,

characterized in that

the combined switching unit (S2c; S2d) comprises a first actuating unit (29c; 29d) provided for actuating the friction-locking unit (12c;

Actuation of the form-locking unit (13c; 13d) provided second

Actuating unit (30c; 30d) and the further switching unit (Si c; S1 d) having a third actuating unit (31c; 31d), the second actuating unit (30c; 30d) and the third actuating unit (31c; the drive-side housing end wall (14c, 14d) and the first actuating unit (29c, 29d) are arranged.

Multi-step transmission according to one of the preceding claims,

characterized in that

concerning an axial order from the internal combustion engine, the planetary gear stage (Pi.sub.a; P1b; P1c; P1d) associated with the combined switching unit (S2a; S2b; S2c; S2d) as a first planetary gear stage and one of the combined switching unit (S2a; S2b; S2c; S2d) associated planetary gear (Pi a; P1 b; P1 c; P1d) adjacent planetary gear (P2a; P2b) is formed as a second planetary gear, wherein the adjacent planetary gear (P2a; P2b) as a

The planetary gear carrier has a gear element (P22a, P22b) which is permanently rotatably connected to a gear element (P13a, P13b) of the combined switching unit (S2a, S2b, S2c, S2d) ), and a transmission element (P23a; P23b) designed as a ring gear, which has a transmission element (P23a;

Sun gear formed transmission element (P31a, P31 b) of a third

Planetenradstufe (P3a; P3b) and formed with a sun gear

P4) is permanently connected non-rotatably to the transmission element (P12a; P12b; P12d) of the planetary gear carrier (P12a, P12b; P12c; P12d) of the planetary gear stage associated with the combined switching unit (S2a; S2b; S2c; S2d) (Pi a; P1 b) is rotatably connected.