WO2017108159A1 - Multi-stage transmission having ten forward transmission gears - Google Patents

Abstract

The invention relates to a multi-stage transmission, in particular for a motor vehicle, which is provided, at least in terms of design, for the shifting of at least ten forward transmission gears (V1a-V10a), comprising: at least four planetary gear stages (P1a-g, P2a-g, P3a-g; P4a-g), which are operatively connected to each other and which each have a sun gear (P11a-g, P21a-g, P31a-g, P41a-g), a ring gear (P13a-g, P23a-g, P33a-g, P43a-g), and a planet gear carrier (P12a-g, P22a-g, P32a-g, P42a-g); at least six shifting units (S1a-g, S2a-g, S3a-g, S4a-g, S5a-g, S6a-g), which each have two coupling elements (S11a-S62g) that can be connected to each other for conjoint rotation; a transmission input element (10a-g) for connecting to an internal combustion engine for conjoint rotation; and a transmission output element (11a-g) for connecting at least one axle drive, wherein the transmission output element (11a-g) and the planet gear carrier (P32a-g) of the third planetary gear stage (P3a-g) are connected to each other for conjoint rotation and the planet gear carrier (P32a-g) of the third planetary gear stage (P3a-g) and the ring gear (P43a-g) of the fourth planetary gear stage (P4a-g) are permanently connected to each other for conjoint rotation.

Description

 Multi-speed transmission with ten forward gears

The invention relates to a multi-speed transmission for a motor vehicle.

From DE 10 2008 055 626 A1 a multistage transmission for a motor vehicle is already known, which is at least constructive for the circuit of at least nine

Forward gears is provided and comprises four operatively interconnected Planetenradstufen and six switching units.

From US 2012/0196718 A1 a generic multi-speed transmission is also known.

The invention is in particular the object of a compact

To provide multi-stage transmission, which preferably has a high flexibility and / or high efficiency. It is achieved according to the invention by the features of claim 1. Further embodiments will be apparent from the

Dependent claims.

It is proposed a multi-speed transmission, in particular for a motor vehicle, which is at least structurally provided for the circuit of at least ten forward gears, with at least four operatively connected to each other

Planetenradstufen, each having a sun gear, a ring gear and a planet carrier, with at least six switching units, each having two rotatably interconnectable coupling elements, with a transmission input element for non-rotatable Än binding to an internal combustion engine and with a

Transmission output element for Änbindung at least one final drive, wherein the transmission output member and the planet carrier of the third planetary gear rotatably connected to each other and the planet carrier of the third

Planetary gear and the ring gear of the fourth planetary gear are permanently connected to each other in a rotationally fixed manner, further wherein the first switching unit is provided to the planet carrier of the third planetary gear and the ring gear of the fourth

 Planetary gear fixed to the housing, and wherein the fourth switching unit is provided to rotatably connect the transmission input member, the ring gear of the first planetary gear and the sun gear of the second planetary gear with each other.

According to the invention, the ring gear of the third planetary gear stage and the sun gear of the fourth planetary gear stage are permanently connected to each other in a rotationally fixed manner.

By such a configuration, a multi-stage transmission can be provided with a basic structure that allows a configuration with a high flexibility and / or a high efficiency. Component loads in the multi-stage transmission can be at least partially reduced by this basic structure, which in particular a lightweight construction can be simplified. In addition, such multi-stage transmissions can be easily hybridized.

The four planetary gear stages are hereinafter referred to as "first planetary gear stage", "second planetary gear stage", "third planetary gear stage" and "fourth planetary gear stage". The terms "first", "second", "third" and "fourth" planetary gear are

in particular provided for determining an axial arrangement, wherein an axial order of the planetary gear stages may differ from the numbering.

In principle, a modified arrangement of the planetary gear stages and / or stacked arrangement, in which the planetary gear stages are at least partially nested radially in one another, is conceivable. In particular, by a spatial rearrangement of

Switching units, by a modified arrangement of transmission elements and / or by interchanging the sun gears, planetary gears and / or ring gears are different kinematically equivalent transmission structures feasible. By "kinematically equivalent transmission structures" gear structures are to be understood, which have an equal number of switching units and identical circuit diagrams for switching the forward gears and the reverse gears.

Preferably, at least two of the six switching units are designed as brakes and at least three of the six switching units as clutches. Under a switching unit, which is designed as a "clutch" is to be understood in particular a switching unit which is arranged in a power flow between two of the planetary gear and which is provided, its two rotatably arranged coupling elements which are independently rotatable in an open state , in a closed state to connect with each other in a rotationally fixed manner under a switching unit, which as a "brake" is formed, should be understood in particular a switching unit, which is operatively disposed between one of the planetary gear and a gear housing and which is intended to rotatable coupling element which is rotatable in an open state regardless of the transmission housing, in a closed state with its rotationally fixed To connect rotatably connected to the transmission housing coupling element. By "non-rotatably connected" is meant in particular a connection in which a power flow over a complete revolution averaged with an unchanged torque, an unchanged direction of rotation and / or an unchanged speed is transmitted.

In this context, a switching unit should in particular not be understood as meaning a coupling which is connected upstream or downstream from a gear set formed by the planetary gear stages. A "clutch upstream of the clutch" should be understood in particular a clutch which in at least one gear in a power flow between the engine and the

Transmission input element is arranged, such as a separating clutch or a starting clutch. A "clutch following the gear set" is to be understood in particular a coupling unit, which in at least one

Transmission gear is arranged in a power flow between the transmission output member and an axle drive, such as an all-wheel clutch. Basically, a shiftability of the multi-speed transmission by a gear set

upstream or downstream coupling unit can be increased. A "transmission input element" is to be understood as meaning, in particular, a transmission element which is at least structurally designed for the rotationally fixed connection of a crankshaft of an internal combustion engine , A "transmission element" is to be understood in particular an embodiment which is provided for permanent non-rotatable connection between the sun gears, planetary carriers, ring gears and / or coupling elements.

The term "at least constructive" is to be understood in particular to mean that a corresponding design is provided, but in a possible exemplary embodiment a functional use of the structural design can be dispensed with in that, by means of the coupling units and / or braking units, a corresponding transmission gear is mechanically in principle can be formed, regardless of whether it is omitted in the context of a shift strategy on the circuit of the transmission gear or not. For example, in one embodiment, the switching units may be structurally provided for switching more forward gears, as it may be useful to switch them as part of an operating strategy for the multi-speed transmission.

Preferably, a part of the switching units is formed positively. As a result, a drag loss can be kept low, whereby a power loss within the multi-speed transmission can be advantageously reduced. In particular, two of the switching units may be formed as claw switching units. In principle, however, it is also conceivable that a different number of the switching units is formed positively. A "form-fitting switching unit" is to be understood in particular a switching unit, which has a toothing and / or claws for connecting their coupling elements or for connecting their coupling element, which intermesh positively to produce a rotationally fixed connection, wherein a transmission of a power flow in a In the fully closed state, at least mainly by means of a form-fitting connection, the switching units can in principle be of frictional or form-fitting design

"Frictionally engaged switching unit" should be understood in particular a switching unit, which has at least two friction partners for connecting their coupling elements or for connecting their coupling element, which frictionally abut each other for producing a rotationally fixed connection, wherein a transmission of a power flow in a fully closed state at least A frictionally engaged coupling unit is preferably designed as a multi-disc clutch unit and a frictionally engaged brake unit is preferably designed as a multi-disc brake unit

trained coupling unit is preferably as a dog clutch unit and a form-locking trained braking unit is preferably as a

Claw brake unit formed. A form-fitting trained switching unit is advantageously switchable via a sliding sleeve. Here, the form-fitting trained switching units are preferably designed without synchronization, can

but in principle also have a synchronization.

The multistage transmission preferably comprises actuators for the automated switching of the switching units. In principle, it is also possible to perform at least a part of the switching units at least partially independently switching. A

independently switching clutch unit or brake unit is preferably as a Freewheel trained. In addition, an embodiment of the Planetenradstufen with Einfachplanetenradsätzen or Doppelplanetenradsätzen of the illustrated

Deviate embodiment. In kinematically equivalent manner, it is for example possible to replace a Einfachplanetenradsatz by a Doppelplanetenradsatz, for a kinematically same mode of action additionally in particular a

Stand translation of the planetary gear must be adjusted. In particular, in a training by means of a Doppelplanetenradsatzes can in principle also a

Connection of a sun gear and a planet carrier, a ring gear and a planet carrier or a sun gear and a ring gear are exchanged, for a kinematically same mode of action additionally in particular a

Stand translation of the planetary gear must be adjusted.

The terms "axial" and "radial" are hereinafter referred to in particular

The axis of rotation of the revolving gear, so that the term "axial" in particular denotes a direction which is parallel or coaxial with the

Main axis of rotation runs. In addition, the term "radial" refers in particular to a direction which is perpendicular to the main axis of rotation

In particular, it should be understood that the said component is arranged on one side of the further component which faces the transmission input element and / or the internal combustion engine Side of the further component is arranged, which faces away from the transmission input element and / or the internal combustion engine, even if the further component is arranged in the axial direction after the transmission output element, for example because the transmission output member is disposed between two planetary gear.

Further advantages will become apparent from the following description of the figures. In the figures, several embodiments of the invention are shown. To distinguish the embodiments, the reference numerals of the following description of the figures are supplemented by the letters a to g. With respect to like-named components, in particular with regard to components having the same reference numerals, reference should be made in principle to the description and / or the drawings of the first embodiment with the letter a. The descriptions of the further embodiments are essentially limited to the differences between the embodiments. The figures, the description of the figures and the claims contain numerous 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 is a circuit diagram for the multi-speed transmission,

3 shows a load shiftability of the multi-speed transmission,

 Fig. 4 is a transmission diagram with a stacked arrangement of planetary gear, Fig. 5 shows another transmission scheme with a stacked arrangement of

 planetary gear,

 6 shows a transmission diagram with a modified arrangement of a switching unit, FIG. 7 shows a transmission diagram with a modified arrangement of a switching unit, FIG. 8 shows a transmission diagram with a modified arrangement of a further one

 Switching unit and

 9 shows a transmission diagram with a modified arrangement of another

 Switching unit.

 FIG. 1 shows a transmission diagram of a multistage transmission. The

Multi-speed transmission is designed as a motor vehicle transmission. It has exactly four planetary gear stages Pi a, P2a, P3a, P4a. The multistage transmission has a

Main axis of rotation, to which the first planetary gear Pi a, the second

Planetary gear P2a, the third planetary gear P3a and the fourth planetary gear P4a are arranged coaxially. The multistage transmission is structurally designed to switch at least ten forward gear ratios V1a, V2a, V3a, V4a, V5a, V6a, V7a, V8a, V9a, V10a and at least one reverse gear R1 a, which are translated in different ways. In particular, a number of the forward gears V1 a-V10a actually used may be limited depending on an operating strategy, for example, electronically by a correspondingly programmed control and

Control unit.

The multi-stage transmission has exactly six switching units S1a, S2a, S3a, S4a, S5a, S6a, which are provided for switching the forward gears V1a, V2a, V3a, V4a, V5a, V6a, V7a, V8a, V9a, V10a and the reverse gear R1a , The multi-stage transmission has a transmission housing 12a that receives the planetary gear stages Pia, P2a, P3a, P4a and the switching units S1a, S2a, S3a, S4a, S5a, S6a. The switching units S1 a, S2a, S3a, S4a, S5a, S6a are operatively arranged within a through the planetary gear Pia, P2a, P3a, P4a gear set, ie the switching units S1 a, S2a, S3a, S4a, S5a, S6a are provided to produce different operative connections between the planetary gear stages Pi, P2a, P3a, P4a with each other and the transmission housing 12a.

The circuit diagram shown in Figure 2 shows how by closing the switching units S1 a, S2a, S3a, S4a, S5a, S6a the forward gears V1 a -V10a and the

Reverse gear R1 a be switched. The forward gears V1 a-V10a are each switched by closing three of the total of six switching units S1 a, S2a, S3a, S4a, S5a, S6a. The load switchability shown in FIG. 3 results directly from the circuit diagram shown in FIG. A load circuit between two of the forward gears V1 a-V10a is in particular always possible if in a shift at most one of the switching units S1 a, S2a, S3a, S4a, S5a, S6a is closed and / or at most one of the switching units S1 a, S2a , S3a, S4a, S5a, S6a, ie when a power flow from one of the switching units S1a, S2a, S3a, S4a, S5a, S6a is given to another of the switching units S1a, S2a, S3a, S4a, S5a, S6a, or when a switching state of only one of

Switching units S1 a, S2a, S3a, S4a, S5a, S6a is changed.

The differently translated forward gears V1 a-V10a, with the exception of a gear change between the second forward gear V2a and the third forward gear V3a, each other at least sequentially power shiftable. In this case, the forward gear V7a is formed as a direct gear to the circuit of the gear set is blocked. In addition, the multi-speed transmission is provided to a further reverse gear R2a in addition to the

Reverse gear R1 a to switch.

The multi-speed transmission is intended to a non-illustrated

Internal combustion engine to connect with at least one axle drive not shown for driving drive wheels of the motor vehicle. By means of the

Multi-speed transmission, a transmission ratio between the internal combustion engine and the final drive can be changed. The multi-stage transmission can be connected to provide a hybrid functionality with a hybrid drive module, by means of which a drive torque can be changed. Next can by means of

Hybrid drive module and the multi-speed transmission a CVT be realized, whereby a multi-stage transmission can be realized, the transmission ratio can be adjusted continuously, at least in some areas. In particular, it is conceivable to integrate at least one electric motor in the gear set to one

To provide hybrid drive module.

The multistage transmission has a transmission input element 10a, which is provided to initiate a drive torque output by the internal combustion engine into the multistage transmission. The transmission input member 10a is provided to be rotatably connected in the assembled state with a crankshaft of the internal combustion engine. In principle, further components, such as a vibration damper, a starting clutch, a separating clutch or a torque converter, may be arranged between the transmission input element 10a and the internal combustion engine. In the illustrated embodiment, it is provided, the crankshaft of

Internal combustion engine and the transmission input member 10a permanently rotatably connected to each other. The transmission input member 10a may be formed differently, such as a shaft or a flange.

Furthermore, the multistage transmission has a transmission output element 11a, which is provided to divert a drive torque from the multistage transmission. The transmission output member 11a is provided to be permanently connected in the assembled state rotationally fixed to the final drive of the motor vehicle. the

Transmission output element 11a can be followed by different modules, by means of which the output from the multistage transmission torque can be distributed to the drive wheels, such as a differential gear, for a

Speed compensation is provided between the drive wheels, or a

Four-wheel drive module that distributes the drive torque to two different drive axles. The transmission output member 11a may be formed differently, such as a shaft, a spur gear or a pinion.

The transmission input member 10a and the transmission output member 1a are arranged coaxially with the main rotation axis. The transmission input member 10a defines a side facing the engine. For the transmission output member 11 a fundamentally different arrangements are conceivable in the axial direction. The

shown multi-stage transmission is particularly for a front-transverse installation

provided in which the transmission output member 1 a between two of

Planetary gear Pia, P2a, P3a, P4a is arranged. For a front-longitudinal installation is fundamentally a rearrangement of the planetary gear Pia, P2a, P3a, P4a possible, in which the planetary gear Pia, P2a, P3a, P4a between the transmission input member 10a and the transmission output member 1 1a are arranged. The planetary gear stages Pia, P2a, P3a, P4a are arranged one behind the other in the axial direction. To redesign the multi-speed transmission it is possible to change the order of the

Change planetary Pia, P2a, P3a, P4a along the main axis of rotation. The multi-stage transmission has four levels in which the planetary gear Pia, P2a, P3a, P4a are arranged. A numbering of the level corresponds to an order of the levels, which in the following is related to the transmission input element 10a. The first plane has a smaller distance to the internal combustion engine than the fourth plane.

The first planetary gear Pia is arranged along the main rotation axis in the first plane. The first planetary gear stage Pi a has a Einfachplanetenradsatz and includes a first sun gear P1 1a, a first ring gear P13a and a first

Planet carrier P12a. The planet carrier P12a leads planetary gears P14a on a circular path. The planetary gears P14a mesh with the sun gear P11a and with the ring gear P13a. The planetary gears P14a are rotatably supported on the planet carrier P12a.

The second planetary gear P2a is arranged along the main rotation axis in the second plane. The second planetary gear P2a is along the main axis of rotation on a side facing away from the transmission input member 10a side of the first

Planet wheel Pia arranged. The second planetary gear P2a has a

A simple sun gear P21a, a second ring gear P23a and a second planet P22a. The planet P22a leads planetary gears P24a on a circular path. The planetary gears P24a mesh with the sun gear P21a and with the ring gear P23a. The planetary gears P24a are rotatably supported on the planet carrier P22a.

The third planetary gear P3a is arranged along the main rotation axis in the third plane. The third planetary gear P3a is arranged along the main axis of rotation on a side facing away from the transmission input member 10a side of the second planetary gear P2a. The third planetary gear P3a has a Einfachplanetenradsatz and includes a third sun P31a, a third ring gear P33a and a third

Planet carrier P32a. The planet carrier P32a leads planetary gears P34a on a circular path. The planet gears P34a mesh with the sun gear P31a and with the ring gear P33a. The planetary gears P34a are rotatably supported on the planet carrier P32a. The fourth planetary gear P4a is arranged along the main rotation axis in the fourth plane. The fourth planetary gear P2a is arranged along the main axis of rotation on a side facing away from the transmission input member 10a side of the third planetary gear P3a. The fourth planetary gear P4a has a Einfachplanetenradsatz and includes a fourth sun P41a, a fourth ring gear P43a and a fourth planet P42a. The planet P42a leads planetary gears P44a on a circular path. The planet gears P44a mesh with the sun gear P41a and with the ring gear P43a. The planetary gears P44a are rotatably supported on the planet carrier P42a.

Three of the switching units S1a, S2a, S3a, S4a, S5a, S6a are formed as clutches. The switching units S4a, S5a, S6a designed as clutches each have a first rotatably mounted coupling element S41a, S51a, S61a and a second rotatably mounted coupling element S42a, S52a, S62a. The switching units S4a, S5a, S6a are each provided for non-rotatably connecting their two coupling elements S31a, S32a, S41a, S42a, S51a, S52a, S61a, S62a. Each of the

Coupling elements S31a, S32a, S41a, S42a, S51a, S52a, S61a, S62a of

Switching units S3a, S4a, S5a, S6a is permanently rotatably connected to at least one of the sun gears P11a, P21a, P31a, P41a, one of the planet P12a, P22a, P32a, P42a and / or one of the ring gears P13a, P23a, P33a, P43a ,

Three of the switching units S1 a, S2a, S3a, S4a, S5a, S6a are designed as brakes. The switching units S1a, S2a, S3a designed as brakes each have a rotatably mounted coupling element S11a, S21a and a housing-fixedly arranged one

Coupling element S12a, S22a on. The switching units S1 a, S2a, S3a are each provided to rotatably support their rotatably mounted coupling element S11 a, S21 a, S31a rotatably connected to the transmission housing 12a. Each of the coupling elements S11a, S21a, S31a of the switching units S1a, S2a, S3a is connected to at least one of the sun gears P1a, P21a, P31a, P41a, one of the planetary carrier P12a, P22a, P32a, P42a and / or one of the ring gears P13a , P23a, P33a, P43a permanently connected rotationally fixed. The housing-mounted coupling elements S12a, S22a, S32a of the switching units S1a, S2a, S3a are permanently connected rotationally fixed to the transmission housing 12a.

For connecting the planetary gear stages Pi a, P2a, P3a, P4a with each other and with the coupling elements S11a-S62a, the multistage transmission comprises a plurality of gear elements 13a, 14a, 15a, 16a, 17a, 18a. The gear elements 13a, 14a, 15a, 16a, 17a, 18a are provided for torques and / or rotational movements to support and / or transmit within the gear set formed by the planetary gear Pia, P2a, P3a, P4a. Each of the transmission elements 13a, 14a, 15a, 16a, 17a, 18a connects at least two of the sun gears P11a, P21a, P31a, P41a, planetary carriers P12a, P22a, P32a, P42a, ring gears P13a, P23a, P33a, P43a, and / or coupling elements S11 a-S62a permanently rotatably with each other or supports at least one of the sun gears P1 1 a, P21a, P31a, P41a, planet P12a, P22a, P32a, P42a and / or ring gears P13a, P23a, P33a, P43a permanently against the gear housing 12a.

The transmission input element 10a forms a transmission input shaft provided for connection to the internal combustion engine, through which the transmission input element 10a, the first coupling element S41a of the fourth shift unit S4a and the first

Coupling element S51 a of the fifth switching unit S5a permanently rotatably connected to each other. The formed by the transmission input member 10 a

Transmission input shaft limits the planetary gear Pia, P2a, P3a, P4a

the input side.

The transmission output member 11 a forms a connection provided for the axle drive transmission output shaft, by which the transmission output member 11a and the planet P32a the third planetary gear P3a permanently connected to each other in a rotationally fixed. The transmission output member 11a is disposed between the third planetary gear P3a and the fourth planetary gear P4a. The transmission output shaft formed by the transmission output member 11a is guided radially outward between the third planetary gear P3a and the fourth planetary gear P4a. The transmission output element 11a can be used for direct connection of the

Achsantriebs be designed as a spur gear or ring gear.

The transmission element 13a forms an intermediate shaft which connects the planet carrier P22a of the second planetary gear P2a, the ring gear P33a of the third planetary gear P3a and the sun P41 a of the fourth planetary gear P4a permanent rotation with each other. The intermediate shaft formed by the transmission element 13a encloses the third planetary gear P3a. Between the third planetary gear P3a and the fourth planetary gear P4a formed by the transmission element 13a intermediate shaft is guided radially inwardly.

The transmission element 14a forms an intermediate shaft, which is the second

Coupling element S62a of the sixth switching unit S6a, the planet P32a of third planetary gear P3a, the first coupling element S11a of the first switching unit S1a and the ring gear P43a of the fourth planetary gear P4a permanently rotatably connected to each other. The intermediate shaft formed by the transmission element 14a is guided, starting from the coupling element S62a, as the planet carrier P32a through the planetary gear P3a, passes through the sun P41a of the fourth planetary gear P4a and is guided on the output side of the fourth planetary gear P4a radially outward.

The transmission element 15a forms an intermediate shaft, which connects the sun gear P11a of the first planetary gear Pia, the sun P31a of the third planetary gear P3a and the first coupling element S21 a of the second switching unit S2a permanent rotation with each other. The intermediate shaft formed by the gear element 5a passes through the three planetary gear stages P2a, P3a, P4a starting from the sun gear P1 1a. The intermediate shaft formed by the transmission element 15a limits the planetary gear stages Pia, P2a, P3a, P4a on the transmission output side.

The transmission element 16a forms a connection, which connects the ring gear P23a of the second planetary gear P2a and the first coupling element S3a of the third shift unit S3a permanently rotatably together. The ring gear P23a and the

Coupling element S31a can also be at least partially made in one piece.

The transmission element 17a forms an intermediate shaft, which is the second

Coupling element S42a of the fourth switching unit S4a, the ring gear P13a of the first planetary gear P3a, the sun gear P21a of the second planetary gear P2a and the first coupling element S61a the sixth switching unit S6a permanently rotatably connected to each other. The intermediate shaft formed by the transmission element 17a encloses the first planetary gear stage Pi a, is guided radially inwardly between the first planetary gear Pia and the second planetary gear P2a and passes through the second planetary gear P2a as the sun gear P21 a. To connect the

Coupling element S61 a is formed by the transmission element 17 a

Intermediate shaft between the second planetary gear P2a and the third

Planet wheel P3a guided radially outward.

The transmission element 18a forms a connection, which is the planet carrier P12a of the first planetary gear P a and the second coupling element S52a of the fifth

Switching unit S5a permanently rotatably connected together. The planet carrier P12a and the coupling element S52a can basically also be formed at least partially in one piece.

The fourth switching unit S4a and the fifth switching unit S5a are arranged on the input side of the first planetary gear stage Pi a. The fourth switching unit S4a is to

provided, the transmission input member 10a, the ring gear P13a of the first

Planet wheel Pia and the sun P21a the second planetary gear P2a rotatably connected to each other. The switching unit S5a is provided to the transmission input member 10a and the planet P12a of the first

Planet wheel Pia rotatably connect with each other.

The third switching unit S3a is arranged at the level of the second planetary gear P2a. The third switching unit S3a is provided to the ring gear P23a of the second

Planetary gear P2a fixed to the housing.

The first switching unit S a and the second switching unit S2a are arranged on the output side of the fourth planetary gear P4a. The first switching unit S1 a is to

provided, the planet carrier P32a the third planetary gear P3a and the ring gear P43a of the fourth planetary gear P4a fixed to the housing to arrange. The second switching unit S2a is provided to the sun gear P11a of the first planetary gear Pia and the sun P31 a of the third planetary gear P3a fixed to the housing to arrange.

In principle, a different arrangement of the switching units S a, S2a, S3a, S4a, S5a, S6a is possible. The switching units S1a, S2a, S3a, S4a are outboard, i. an actuating means supply of the switching units S1a, S2a, S3a, S4a is without carrying out operating medium lines by a rotatably mounted component

realizable. The switching units S5a, S6a are implemented internally, i. the

Actuator supply of the switching units S5a, S6a requires a

Equipment feedthrough by a rotatably mounted component. All

Switching units S1a, S2a, S3a, S4a, S5a, S6a are hydraulically actuated. The

Switching units S1a, S2a or the switching units S1a, S6a can at least partially have a common actuator.

In a hybridization, i. In one embodiment for a hybrid drive train, in particular, the transmission element 15a for a connection of the electric motor

intended. The transmission element 15a is intended to be permanently connected to a rotor of the electric motor in a manner fixed against rotation. The electric motor is preferably arranged on the output side of the fourth planetary gear P4a. In principle, additionally or alternatively, one of the further gear elements 13a, 14a, 16a, 17a, 18a can be provided for a connection of an electric motor.

Figure 4 shows a second embodiment of a transmission scheme of a

Multi-speed transmission for a motor vehicle, which is provided at least constructively for the switching of at least ten forward gears and at least one reverse gear. The transmission scheme corresponds structurally to that of FIG. 1.

The multistage transmission comprises a transmission input element 10b for the rotationally fixed connection of an internal combustion engine and a transmission output element 1 1 b for the rotationally fixed connection of a final drive. In addition, the multi-speed transmission includes a gear set with a first planetary gear P1 b, a second planetary gear P2b, a third planetary gear P3b and a fourth planetary gear P4b, each having a sun P1 1 b, P21 b, P31 b, P41 b, a ring gear P13b, P23b , P33b, P43b and a planet carrier P12b, P22b, P32b, P42b, which planetary gears P14b, P24b, P34b, P44b in a circular orbit about the corresponding sun gear P1 1 b, P21 b, P31 b, P41 b leads. Furthermore, the multi-stage transmission comprises six switching units S1 b, S2b, S3b, S4b, S5b, S6b, each having two coupling elements S1 1 b, S12b, S21b, S22b, S31b, S32b, S41b, S42b, S51b, S52b, S61 b, S62b. For transmitting power flows between the planetary gear sets P1b, P2b, P3b, P4b and / or for supporting against a transmission housing 12b, the multistage transmission comprises a plurality of transmission elements 13b, 14b, 15b, 16b, 16b, 17b, 18b.

The transmission scheme differs in particular in an arrangement of

Planetary gear P1, P2b, P3b, P4b of that of the embodiment in Figure 1. The multi-stage transmission has three levels, in which the four planetary gear P1, P2b, P3b, P4b are arranged. The planetary gear P1 b is arranged in the first plane. The planetary gear P2b is arranged in the second plane. The planetary gear stages P3b, P4b are stacked. The planetary gear stages P3b, P4b are arranged in the third plane. The third planetary gear P3b is disposed radially inside the fourth planetary gear P4b. The ring gear P33b of the third planetary gear stage P3b and the sun gear P41b of the fourth planetary gear stage P4b may be integrally formed

be formed. The switching units S4b, S5b are the input side of the first

Planetary gear P1 b arranged. The switching unit S3b is arranged at the level of the planetary gear P3b. The switching unit S6b is disposed between the second planetary gear P2b and the stacked planetary gears P3b, P4b. The Switching units S1 b, S2b are arranged on the output side of the stacked

 Planetary gear stages P3b, P4b arranged. The transmission output member 11b is disposed between the second planetary gear P2b and the stacked planetary gears P3b, P4b.

Figure 5 shows a third embodiment of a transmission scheme of a

Multi-speed transmission for a motor vehicle, which is provided at least constructively for the switching of at least ten forward gears and at least one reverse gear. The transmission scheme corresponds structurally to that of FIG. 1.

The multistage transmission comprises a transmission input element 10c for the rotationally fixed connection of an internal combustion engine and a transmission output element 1 1 c for the rotationally fixed connection of a final drive. In addition, the multi-stage transmission includes a gear set having a first planetary gear P 1c, a second planetary P 2 c, a third P3 c and a fourth P4 c, each a sun P11c, P21c, P31 c, P41c, a ring gear P13c, P23c, P33c, P43c and a planet carrier P12c, P22c, P32c, P42c, which planetary gears P14c, P24c, P34c, P44c in a circular orbit about the corresponding sun gear P1 c, P21c, P31c, P41c leads. Further, the multi-stage transmission comprises six switching units Sic, S2c, S3c, S4c, S5c, S6c, each having two coupling elements S11c, S12c, S21c, S22c, S31c, S32c, S41c, S42c, S51c, S52c, S61c, S62c. For the transmission of

Power flows between the planetary gear P1 c, P2c, P3c, P4c and / or for support against a transmission housing 12c includes the multi-speed transmission one

Plurality of transmission elements 13c, 14c, 15c, 16c, 16c, 17c, 18c.

The transmission scheme differs in particular in an arrangement of

Planetary gear stages P1c, P2c, P3c, P4c of that of the embodiment in Figure 1. The multi-stage transmission has two levels in which the four planetary gear P1 c, P2c, P3c, P4c are arranged. The planetary gear stages P1c, P2c and the planetary gear stages P3c, P4c are stacked. The planetary gear P1 c, P2c are arranged in the first plane. The first planetary gear P1c is radially within the second

Planet wheel P2c arranged. The ring gear P13c of the first planetary gear P1c and the sun gear P21c of the second planetary gear P2c may be integrally formed

be formed. The planetary gear stages P3c, P4c are in the third plane

arranged. The third planetary gear P3c is radially within the fourth

Planet wheel P4c arranged. The ring gear P33c of the third planetary gear P3c and the sun gear P41 c of the fourth planetary gear P4c can be integrally formed.

The switching units S4c, S5c are arranged on the input side of the stacked

Planetary gear P1c, P2c arranged. The switching unit S3c is arranged at the height of the stacked planetary gear P1 c, P2c. The switching unit S6c is disposed between the planetary gear stages P1c, P2c and the planetary gear stages P3c, P4c. The switching units Sic, S2c are the output side of the stacked

arranged planetary gear P3c, P4c arranged. The transmission output member 11c is disposed between the planetary gear sets P1c, P2c and the planetary gear stages P3c, P4c.

FIG. 6 shows a transmission diagram of a fourth exemplary embodiment

Multi-speed transmission for a motor vehicle, which is provided at least constructively for the switching of at least ten forward gears and at least one reverse gear. The transmission scheme differs structurally from that of FIG. 1. Kinematically, it is equivalent to that of FIG. 1.

The multistage transmission comprises a transmission input element 10d for the rotationally fixed connection of an internal combustion engine and a transmission output element 11d for the rotationally fixed connection of an axle drive. In addition, the multi-speed transmission comprises a gear set with a first planetary gear P1 d, a second planetary gear P2d, a third planetary gear P3d and a fourth planetary gear P4d, each a sun P11d, P21d, P31d, P41d, a ring gear P13d, P23d, P33d, P43d and a planet carrier P12d, P22d, P32d, P42d, which planetary gears P14d, P24d, P34d, P44d in a circular orbit about the corresponding sun gear P1 1d, P21 d, P31d, P41d leads. Further, the multi-stage transmission comprises six switching units S1d, S2d, S3d, S4d, S5d, S6d each having two coupling elements S1 1d, S12d, S21d, S22d, S31d, S32d, S41d, S42d, S51d, S52d, S61d, S62d. For transmitting power flows between the planetary gear stages P1d, P2d, P3d, P4d and / or for supporting against a transmission housing 12d, the multistage transmission comprises a plurality of transmission elements 13d, 1d, 15d, 16d, 16d, 17d, 18d.

The transmission scheme differs in particular in an arrangement of

The switching unit S5d is provided to connect the sun gear P1 1d of the first planetary gear stage and the sun gear P31d of the third planetary gear P3d. The Transmission input element 10d and the planet P12d of the first planetary gear P1d are permanently connected to each other rotatably. The

Transmission input element 10d forms a transmission input shaft, through which the transmission input element 10d, the first coupling element S41d of the fourth

Switching unit S4d and the planet P12d the first planetary gear P1d permanently connected to each other rotatably. The transmission element 18d forms an intermediate shaft, which connects the sun gear P11d of the first planetary gear stage P1d and the first coupling element S51d of the fifth shift unit S5d to one another in a permanently non-rotatable manner. The transmission element 15d forms an intermediate shaft comprising the second coupling element S52d of the fifth switching unit S5d, the sun gear P31d of the third planetary gear P3d and the first coupling element S21d of the second

Switching unit S2d permanently rotatably connected to each other. The switching unit S5d is arranged axially between the first planetary gear P1d and the third planetary P3d.

Figure 7 shows a fifth embodiment of a transmission scheme of a

Multi-speed transmission for a motor vehicle, which is provided at least constructively for the switching of at least ten forward gears and at least one reverse gear. The transmission scheme differs structurally from that of FIG. 1. Kinematically, it is equivalent to that of FIG. 1.

The multistage transmission comprises a transmission input element 10e for the non-rotatable connection of an internal combustion engine and a transmission output element 11e for the rotationally fixed connection of a final drive. In addition, the multi-stage transmission includes a gear set having a first planetary gear P1e, a second planetary P2e, a third planetary P3e and a fourth planetary P4e, each of a sun P1 P1, P21e, P31e, P41e, a ring gear P13e, P23e, P33e, P43e and a planetary carrier P12e, P22e, P32e, P42e, which planetary gears P14e, P24e, P34e, P44e in a circular orbit about the corresponding sun gear P1 1e, P21e, P31e, P41e leads. Further, the multi-stage transmission comprises six switching units, S2e, S3e, S4e, S5e, S6e, each having two coupling elements S1ee, S12e, S21e, S22e, S31e, S32e, S41e, S42e, S51e, S52e, S61e, S62e. For transmitting power flows between the planetary gear stages P1e, P2e, P3e, P4e and / or for supporting against a transmission housing 12e, the multistage transmission comprises a plurality of transmission elements 13e, 14e, 15e, 16e, 16e, 17e, 18e. The transmission scheme differs in particular in an arrangement of the switching unit S5e from that of the embodiment of Figure 1. The switching unit S5e is intended to connect the sun gear P1 1e of the first planetary gear stage and the sun gear P31e of the third planetary gear P3e. The

Transmission input element 10e and the planet P12e of the first

Planetary gear P1e are permanently connected to each other in a rotationally fixed manner. The

Transmission input element 10e forms a transmission input shaft, through which the transmission input element 10e, the first coupling element S41e of the fourth

Switching unit S4e and the planet P12e of the first planetary gear P1e permanently connected to each other rotatably. The transmission element 18e forms a connection, which connects the sun gear P31e of the third planetary gear P1e and the second coupling element S52e of the fifth shift unit S5e permanently rotatably together. The sun gear P31e of the third planetary gear P1e and the second coupling element S52e of the fifth shift unit S5e may be at least partially formed in one piece. The transmission element 15e forms an intermediate shaft which connects the sun gear P11e of the first planetary gear P1e, the first coupling element S51e of the fifth shift unit S5e, and the first coupling element S21e of the second switching unit S2e in a permanently non-rotatable manner. The switching unit S5e is arranged axially in the amount of the third planetary gear P3e.

FIG. 8 shows a transmission diagram of a sixth exemplary embodiment

Multi-speed transmission for a motor vehicle, which is provided at least constructively for the switching of at least ten forward gears and at least one reverse gear. The transmission scheme differs structurally from that of FIG. 1. Kinematically, it is equivalent to that of FIG. 1.

The multistage transmission comprises a transmission input element 10f for the non-rotatable connection of an internal combustion engine and a transmission output element 1 1 f for the rotationally fixed connection of a final drive. In addition, the multi-stage transmission comprises a gear set having a first planetary gear stage P 1f, a second planetary gear stage P 2f, a third planetary gear stage P3f and a fourth planetary gear stage P4f, each including a sun gear P11f, P21f, P31f, P41f, a ring gear P13f, P23f, P33f, P43f and a

Planetary P12f, P22f, P32f, P42f, which planetary gears P14f, P24f, P34f, P44f in a circular orbit about the corresponding sun P11f, P21f, P31f, P41f leads, have. Further, the multi-stage transmission comprises six switching units S1f, S2f, S3f, S4f, S5f, S6f each having two coupling elements S11f, S12f, S21f, S22f, S31f, S32f, S41f, S42f, S51f, S52f, S61f, S62f. For transmission of power flows between the planetary gear stages P1f, P2f, P3f, P4f and / or for support against a transmission housing 12f, the multi-stage transmission comprises a plurality of

Transmission elements 13'f, 13 "f, 14f, 15f, 16f, 16f, 17f, 18f.

The transmission scheme differs in particular in an arrangement of

Switching unit S3f of that of the embodiment of Figure 1. The switching unit S3f is formed as a coupling whose coupling elements S31f, S32f are rotatably arranged. The switching unit S3f is provided to the planet carrier P22f of the second planetary gear P2f, the ring gear P33f of the third planetary gear P3f and the

Sun P41f the fourth planetary gear P4f rotatably connect to each other. The gear housing 12f and the ring gear P23f of the second planetary gear P2f are permanently connected to each other in a rotationally fixed manner. The ring gear P23f is fixed to the housing

arranged.

The gear element 16f forms a housing support, which connects the ring gear P23f of the second planetary gear stage P2f and the gear housing 12f permanently rotatably together. The transmission element 13'f forms an intermediate shaft, which is the planet carrier P22f of the second planetary gear stage P2f and the first

Coupling element S31f the third switching unit S3f permanently rotatably connected to each other. The transmission element 13 "f forms an intermediate shaft which permanently interconnects the second coupling element S32f of the third switching unit S3f, the ring gear P33f of the third planetary gear stage P3f and the sun gear P41f of the fourth planetary gear stage P4f the third planetary gear P3f arranged.

FIG. 9 shows a transmission diagram of a seventh exemplary embodiment

Multi-speed transmission for a motor vehicle, which is provided at least constructively for the switching of at least ten forward gears and at least one reverse gear. The transmission scheme differs structurally from that of FIG. 1. Kinematically, it is equivalent to that of FIG. 1.

The multistage transmission comprises a transmission input element 10g for the non-rotatable connection of an internal combustion engine and a transmission output element 11g for the rotationally fixed connection of a final drive. In addition, the multi-stage transmission comprises a gear set having a first planetary gear stage P 1g, a second planetary gear stage P 2g, a third planetary gear stage P 3g and a fourth planetary gear stage P 4g, each having a sun gear P 1g, P21g, P31g, P41g, a ring gear P13g, P23g, P33g, P43g and P13g one Planetary P12g, P22g, P32g, P42g, which planetary gears P14g, P24g, P34g, P44g in a circular orbit about the corresponding sun P11g, P21g, P31g, P41g leads. Further, the multi-stage transmission comprises six switching units S1g, S2g, S3g, S4g, S5g, S6g each having two coupling elements S1 1g, S12g, S21g, S22g, S31g, S32g, S41g, S42g, S51g, S52g, S61g, S62g. For transmission of power flows between the planetary gear P1g, P2g, P3g, P4g and / or to support against a transmission housing 12g, the multi-speed transmission comprises a plurality of transmission elements 13g, 14g, 15g, 16g, 16g, 17'g, 17 "g, 18g.

The transmission scheme differs in particular in an arrangement of

Switching unit S3g of that of the embodiment of Figure 1. The switching unit S3g is formed as a coupling whose coupling elements S31g, S32g are rotatably arranged. The switching unit S3g is intended to connect the ring gear P 3g of the first planetary gear P3g and the sun P21g of the second planetary gear P2g permanently rotatably together. The gear housing 12g and the ring gear P23g of the second planetary gear P2g are permanently connected to each other in a rotationally fixed manner. The ring gear P23g is fixed to the housing.

The transmission element 16g forms a housing support, which connects the ring gear P23g of the second planetary gear P2g and the transmission housing 12g permanently rotatably together. The transmission element 17'g forms an intermediate shaft which comprises the second coupling element S42g of the fourth switching unit S4g, the ring gear P13g of the first planetary gear P1g and the second coupling element S32g of the third

Switching unit S3g permanently rotatably connected to each other. The transmission element 17 "g forms an intermediate shaft which is the first coupling element S31g of the third

Switching unit S3g, the sun gear P21g of the second planetary gear P2g and the first coupling element S61g the sixth switching unit S6g permanently rotatably connected to each other. The switching unit S3g is disposed between the first planetary gear P1g and the second planetary gear P2g.

The structural changes in the embodiments of Figures 6 and 7 and the structural changes in the embodiments of Figures 8 and 9 are independent of each other. Basically, a transmission scheme is thus conceivable that represents a combination of one of the embodiments of Figures 6 and 7 and one of the embodiments of Figures 8 and 9. LIST OF REFERENCE NUMBERS

10 transmission input element

11 Transmission output element

12 gearbox housing

 13 gear element

 13 'transmission element

 13 "gear element

 14 gear element

 15 gear element

 16 gear element

 17 transmission element

 17 'transmission element

 17 "gear element

 18 gear element

 P1 planetary gear

 P11 sun wheel

 P12 planet carrier

P13 ring gear

 P14 planet wheels

 P2 planetary gear

 P21 sun wheel

 P22 planet carrier

P23 ring gear

 P24 planet gears

 P3 planetary gear

 P31 sun wheel

 P32 planet carrier

P33 ring gear

 P34 planet wheels

 P4 planetary gear

 P41 sun wheel

 P42 planet carrier

P43 ring gear

 P44 planet gears

 S1 switching unit

S11 coupling element S12 coupling element

52 switching unit

 521 coupling element

522 coupling element

53 switching unit

 531 coupling element

532 coupling element

54 switching unit

 541 coupling element

542 coupling element

55 switching unit

 551 coupling element

552 coupling element

56 switching unit

 561 coupling element

562 Coupling element V1 Forward gear V2 Forward gear V3 Forward gear V4 Forward gear V5 Forward gear V6 Forward gear V7 Forward gear V8 Forward gear V9 Forward gear V10 Forward gear R1 Reverse gear R2 Reverse gear

Claims

claims 1. Multi-speed transmission, in particular for a motor vehicle, which is at least constructive for the circuit of at least nine, preferably at least ten  Forward gears (V1a-V10g) is provided, with at least four  operatively interconnected planetary gear stages (P1a-g, P2a-g, P3a-g; P4a-g) each having a sun gear (P11a-d, P21a-g, P31a-g, P41a-g), a ring gear (P13a-g , P23a-g, P33a-g, P43a-g) and a planet carrier (P12a-g, P22a-g, P32a-g, P42a-g) having at least six switching units (S1a-g, S2a-g, S3a g, S4a-g, S5a-g, S6a-g), each having two rotatably interconnectable coupling elements (S1 1a-S62g), with a transmission input member (10a-g) for non-rotatable connection to an internal combustion engine and with a transmission output member (11a -g) for connecting at least one final drive, wherein the transmission output member (1 1a-g) and the planet carrier (P42a-g) of the fourth planetary gear (P4a-g) are rotatably connected to each other and the planet carrier (P32a-g) of the third planetary gear stage ( P3a-g) and the ring gear (P43a-g) of the fourth planetary gear stage (P4a-g) permanently connected to each other in a rotationally fixed manner,  wherein the first switching unit (S1a-g) is arranged to arrange the planet carrier (P32a-g) of the third planetary gear stage (P3a-g) and the ring gear (P43a-g) of the fourth planetary gear stage (P4) fixed to the housing,  and wherein the fourth switching unit (S4a-f) is provided for  Transmission input element (10a-f), the ring gear (P13a-f) of the first planetary gear (P1a-f) and the sun gear (P21 a-f) of the second planetary gear (P2a-f) rotatably connect to each other,  characterized in that the ring gear (P33a-e; P33g) of the third planetary gear stage (P3a-e; P3g) and the sun gear (P41a-e: P41g) of the fourth planetary gear stage (P4a-e; P4g) are permanently connected to each other in a rotationally fixed manner. 2. Multi-step transmission according to claim 1,  characterized in that  the second switching unit (S2a-c; S2e-g) is provided for arranging the sun gear (P11a-c; P1ee-g) of the first planetary gear stage (P1a-c; P1e-g) fixed to the housing. 3. Multi-step transmission according to one of the preceding claims,  characterized in that  the second switching unit (S2a-d; S2f; S2g) is provided to arrange the sun gear (P31a-d; P31f; P31g) of the third planetary gear stage (P3) fixed to the housing. 4. Multi-step transmission according to one of the preceding claims,  characterized in that  the ring gear (P23f; P23g) of the second planetary gear stage (P2f; P2g) is fixed to the housing or the third shift unit (S3a-e) is arranged to locate the ring gear (P23a-e) of the second planetary gear plane (P2a-e) fixed to the housing. 5. Multi-step transmission according to one of the preceding claims,  characterized in that  the fifth switching unit (S5a-c; S5f; S5g) is provided for  Gear input member (10a-c; 10f; 10g) and the planet carrier (P12a-c; P12f; P12g) of the first planetary gear plane (P1a-c; P1f; P1g) rotatably connected to each other. 6. Multi-step transmission according to one of the preceding claims,  characterized in that the sun gear (P11a-c; P1 1f; P11g) of the first planetary gear stage (P1 ac; P1f; P1g) and the sun gear (P31a-c; P31f; P31g) of the third planetary gear stage (P3a-c; P3f; are connected. 7. Multi-step transmission according to one of the preceding claims,  characterized in that  the fifth switching unit (S5d; S5e) is provided for non-rotatably connecting the sun gear (P1 1d; P11e) of the first planetary gear stage (P1d; P1e) and the sun gear (P31d; P31e) of the third planetary gear stage (P3d; P3e) the transmission input element (10d; 10e) and the planet carrier (P12d; P12e) of the first planetary gear stage (P1d; P1e) are permanently connected to one another in a rotationally fixed manner. 8. Multi-step transmission according to one of the preceding claims,  characterized in that  the sixth shift unit (S6a-g) is provided to at least the sun gear (P21 ag) of the second planetary gear (P2a-g), the planet carrier (P32a-g) of the third planetary gear (P3a-g) and the ring gear (P43a-g ) the fourth  Planet wheel (P4a-g) rotatably connected to each other. 9. Multi-step transmission according to one of the preceding claims,  characterized in that  the planetary gear carrier (P22a-e; P22g) of the second planetary gear stage (P2a-e; P2g) and the ring gear (P33a-e; P33g) of the third planetary gear stage (P3a-e; P3g) are permanently connected to each other in a rotationally fixed manner or the third switching unit (S3f ) is provided, the planet carrier (P22f) of the second planetary gear (P2f) and the ring gear (P33f) of the third planetary gear (P3f) rotatably  to connect with each other. 10. Multi-step transmission according to one of the preceding claims,  characterized in that the fourth switching unit (S4g) is provided for non-rotatably interconnecting the transmission input element (10g) and the ring gear (P13g) of the first planetary gear stage (P1g). 1 1. Multi-step transmission according to one of the preceding claims, characterized in that  the ring gear (P13a-f) of the first planetary gear (P1 a-f) and the sun gear (P21 a-f) of the second planetary gear (P2a-f) are permanently connected to each other in a rotationally fixed manner. 12. Multi-step transmission according to one of the preceding claims,  characterized in that  at least one of the switching units (S1 a-g, S3a-g) is formed as a claw switching unit.