DE102017007820A1 - Multi-speed transmission - Google Patents

Abstract

The invention relates to a multistage transmission (17a) with four operatively interconnected Planetenradstufen (P1a-d, P2a-d, P3a-d, P4a-d), each having a sun gear (P11a-d, P21a-d, P31a-d, P41a -d), a ring gear (P13a-d, P23a-d, P33a-d, P43a-d) and a planet carrier (P12a-d, P22a-d, P32a-d, P42a-d) having a transmission input member (10a -d) and with a transmission output member (11a-d), wherein a first switching unit (S1a-d) is provided, the transmission input member (10a-d) with the sun gear (P41a-d) of the fourth planetary gear (P4a-d) rotationally fixed to connect, wherein the sun gear (P21a-d) of the second planetary gear (P2a-d) with the sun gear (P41a-d) of the fourth planetary gear (P4a-d) is permanently connected rotationally fixed and wherein the planet carrier (P42a-d) of the fourth Planetenradstufe (P4a-d) with the transmission output member (11a-d) permanently rotatably connected, wherein the transmission input member (10a-d) permanently rotatably connected to the sun gear (P11a) d) the first planetary gear (P1a-d) is connected and a second switching unit (S2a-d) is provided to the transmission input member (10a-d) with the planet carrier (P22a-d) of the second planetary gear (P2a-d) rotationally fixed connect.

Description

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

From the DE 10 2005 010 210 A1 is already known a multi-speed transmission for motor vehicles. The multistage transmission is designed to shift eight forward gears. It comprises a transmission input element, a transmission output element, four interconnected planetary gear stages and five switching units, which are provided to produce different operative connections between the planetary gear stages and / or a transmission housing.

Furthermore, from the DE 10 2015 203 194 A1 another multi-speed transmission for a vehicle, in particular an electric vehicle or a hybrid vehicle known. The further multi-speed transmission is provided for the switching of two forward gears. It comprises a transmission input element, a transmission output element, two planetary gear stages operatively connected to one another and two switching units which are provided to produce different operative connections between the planetary gear stages.

The invention is in particular the object of providing an improved multi-speed transmission, in particular with regard to a high spread and / or a high number of gears. It is achieved by an embodiment according to the invention according to claim 1. Further developments of the invention will become apparent from the dependent claims.

The invention relates to a multi-speed transmission, in particular for a motor vehicle, with four operatively interconnected Planetenradstufen, each having a sun gear, a ring gear and a planet carrier, with a plurality of switching units, each having in particular two rotatably interconnectable coupling elements, with a transmission input element and with a, advantageously arranged coaxially to the transmission input element, transmission output element, wherein a first switching unit of the switching units is provided to rotatably connect the transmission input element with the sun gear of the fourth planetary gear, wherein the sun gear of the second planetary gear is permanently rotatably connected to the sun gear of the fourth planetary gear and wherein the planet carrier of the fourth planetary gear is permanently rotatably connected to the transmission output member.

It is proposed that the transmission input element is permanently non-rotatably connected to the sun gear of the first planetary gear and a second switching unit of the switching units is provided to rotatably connect the transmission input member with the planet carrier of the second planetary gear. Preferably, at least two planetary gear stages of the four planetary gear stages, preferably three planetary gear stages of the four planetary gear stages, and particularly preferably all planetary gear stages of the four planetary gear stages, are designed as simple planetary gear stages. In addition, the multistage transmission in particular has at least five, advantageously at least six, preferably at least seven and particularly preferably exactly seven switching units. In particular, at least three, advantageously at least four, and particularly advantageously exactly four, of the switching units are designed as clutches. Furthermore, preferably at least two, advantageously at least three and particularly preferably exactly three, of the switching units are designed as brakes.

By an inventive embodiment of the multi-speed transmission, an advantageously high spread can be made possible. Furthermore, in particular a high number of gears, advantageously a high number of independent forward gears, and / or an advantageous gear ratio can be realized. In particular, different gear and spread concepts can be implemented and / or an optional spread and / or gear variation can be achieved. Advantageously, a gear selection kit can be provided. Advantageously, a high switching flexibility, in particular by a high number of further redundant and / or additional gears, can be realized, with particular advantage important circuits can be executed under load. Furthermore, a cancellation of switching units can be compensated by the high number of gears and / or the high number of further courses particularly advantageous. Furthermore, it is advantageously possible to achieve a high gear efficiency, in particular by installing simple planetary gearsets. It can be achieved a high efficiency of individual gears in cycle-relevant operating points. In addition, advantageously low transmission losses, in particular a low power loss can be achieved, in particular since at least one switching unit can be executed as a dog clutch with or without a synchronization unit. Particularly low drag losses and / or low relative speeds between movable transmission components can be realized. It can also be advantageously provided a hybrid and / or four-wheel functionality. Particularly advantageous, an electric machine can be easily and advantageously integrated. Advantageously, a low component load and thus a lightweight and / or low-loss design can be made possible.

In particular, the multi-speed transmission is at least constructive for the circuit of at least provided eleven forward gears. Preferably, the forward gears are implemented differently. Advantageously, the multi-speed transmission is at least constructively provided for the circuit of exactly eleven forward gears. Particularly advantageous exist additional redundant and additional gears. There are preferably six further redundant gears, in particular direct gears. Furthermore, there are preferably six additional additional gears, in particular intermediate gears. Thus, there are preferably seventeen independent forward gears. Advantageously, the multi-speed transmission is provided at least structurally to the circuit of at least one reverse gear. Particularly advantageously, the multi-speed transmission is provided at least constructively for switching exactly one reverse gear. Preferably, the multi-speed transmission has a spread of at least twelve and / or is at least structurally suitable for setting a spread of at least twelve. It is possible to realize an advantageously high spread and / or an advantageous, in particular advantageous uniform, gear gradation. Furthermore, various gear and spread concepts can advantageously be implemented and / or an optional spread and / or gear variation can be achieved. Advantageously, a gear selection kit can be provided. Furthermore, advantageously a high switching flexibility, in particular by a high number of further redundant and / or additional gears, can be realized, wherein particularly advantageously important circuits can be executed in a load-shiftable manner. It can be compensated particularly advantageous elimination of switching units by the high number of gears and / or the high number of other courses.

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" Planetenradstufe are particularly intended to define an axial arrangement, wherein an axial order of the Planetenradstufen may differ from the order of the numbering. In principle, a modified arrangement of the planetary gear stages and / or a 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 the switching units, by a modified arrangement of transmission elements and / or by interchanging of the sun gears, planet gears and / or ring gears different kinematically equivalent transmission structures can be realized. In particular, simple planetary gear sets can be replaced kinematically equivalent by double planetary gear sets, in particular if at the same time the ring gear connection of the associated planetary gear set is replaced by a web connection. 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. The principles known to those skilled in the art for the formation of kinematically equivalent planetary gear sets can be found, inter alia, in VDI Guideline 2157. In addition, an embodiment of the planetary gear stages with simple planetary gearsets or double planetary gearsets of illustrated embodiments may differ. In kinematically equivalent manner, it is for example possible to replace a Einfachplanetenradsatz by a Doppelplanetenradsatz, in addition to a kinematic same mode of action additionally in particular a stationary translation of the planetary gear must be adjusted. In particular, in a training by means of a Doppelplanetenradsatzes basically a connection of a sun gear and a planet, 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 level translation of the planetary must be adjusted.

In particular, a transmission element, which is provided at least structurally for the non-rotatable connection of a crankshaft of an internal combustion engine, should be understood as a "transmission input element". A "transmission output element" is to be understood, in particular, as a transmission element which is provided, at least structurally, for the non-rotatable connection of a final drive. A "transmission element" is to be understood in particular an element which is provided for permanent non-rotatable connection between the sun gears, planet carriers, ring gears and / or coupling elements. Advantageously, the transmission element moves in at least one operating state. By "at least constructive" is to be understood in particular that a corresponding design is provided structurally, but in a possible embodiment of a functional use of the structural design can be dispensed with. In this context, the term "constructively provided for the shifting of a transmission gear" should be understood in particular as meaning that a corresponding gear train can be formed mechanically by means of the shifting units, in particular the clutch units and / or brake units, regardless of whether in the context of a shift strategy to the circuit of Transmission gear is omitted 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. Under "provided" in particular designed specially designed and / or equipped to be understood. The fact that an object is intended for a specific function should in particular mean that the object fulfills and / or executes this specific function in at least one application and / or operating state.

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 to connect in a closed state rotatably with each other. Under a switching unit, which is designed as a "brake" is to 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 in an open state independently of the gear housing rotatable is to connect in a closed state with its rotatably connected to the transmission housing coupling member rotatably. 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 to mean a clutch which is connected upstream or downstream of a gear set formed by the planetary gear stages. A "gearset preceding the clutch" is to be understood in particular a clutch which is arranged in at least one gear in a power flow between the engine and the transmission input member, such as a clutch or a starting clutch. A "gearset downstream of the clutch" should be understood in particular a clutch unit which is arranged in at least one gear in a power flow between the transmission output member and a final drive, such as an all-wheel drive. In principle, a switchability of the multistage transmission can be increased by a clutch unit upstream or downstream of the gear unit.

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. An independently switching switching unit, in particular a coupling unit or brake unit, is preferably designed as a freewheel.

The switching units can in principle be formed frictionally or positively. A "frictionally engaged switching unit" should be understood to mean, in particular, a switching unit which has at least two friction partners for connecting its coupling elements and / or for connecting its coupling element, which frictionally abut one another to produce a rotationally fixed connection, wherein a transmission of a power flow in one completely closed state at least mainly by friction. A frictionally engaged switching unit is preferably designed as a lamella switching unit. A frictionally engaged coupling unit is preferably in the form of a multi-disc clutch unit, and a frictionally engaged brake unit is preferably designed as a multi-disc brake unit. A "form-fitting switching unit" should also be understood in particular a switching unit which has a toothing and / or claws for connecting their coupling elements and / or for connecting their coupling element, which interlock positively to produce a rotationally fixed connection, wherein a transmission of a power flow in a completely closed state is at least mainly done by a positive connection. A form-fitting switching unit is preferably designed as a claw switching unit and preferably switchable via a sliding sleeve. A form-fitting coupling unit is preferably as a dog clutch unit and a form-locking brake unit is preferably designed as a dog brake unit. In addition, the form-fitting trained switching units are preferably carried out without synchronization, but in principle may also have a synchronization.

In the present case, at least a portion of the switching units is advantageously formed positively. In particular, at least one switching unit of the switching units is designed as a claw switching unit. As a result, a drag loss can be kept low, whereby a power loss within the multi-speed transmission can be advantageously reduced. In addition, transmission losses can advantageously be reduced, in particular in comparison to conventional lamellae switching units.

It is also proposed that the ring gear of the third planetary gear is permanently connected rotationally fixed to the ring gear of the fourth planetary gear.

Furthermore, it is proposed that the planet carrier of the second planetary gear is permanently non-rotatably connected to the planet carrier of the third planetary gear. In addition, it is proposed that the ring gear of the first planetary gear is permanently connected to the sun gear of the third planetary gear rotatably. In addition, it is proposed that a third switching unit of the switching units is provided to rotatably connect the planet carrier of the first planetary gear with the ring gear of the second planetary gear. In particular, the third switching unit connects in at least one switching state, the planet carrier of the first planetary gear rotatably connected to the ring gear of the second planetary gear. Advantageously, the third switching unit is designed as a third clutch. It is also proposed that a fourth switching unit of the switching units is provided to arrange the planet carrier of the first planetary gear fixed to the housing. In particular, the fourth switching unit assigns the planetary gear carrier of the first planetary gear set to the housing in at least one switching state. Advantageously, the fourth switching unit is designed as a first brake. Furthermore, it is proposed that a fifth switching unit of the switching units is provided to arrange the planet carrier of the third planetary gear fixed to the housing. In particular, the fifth switching unit assigns the planet carrier of the third planetary gear set fixed to the housing in at least one switching state. Advantageously, the fifth switching unit is designed as a second brake. In addition, it is proposed that a sixth switching unit of the switching units is provided to arrange the ring gear of the first planetary gear fixed to the housing. In particular, in at least one switching state, the sixth switching unit arranges the ring gear of the first planetary gear set fixed to the housing. Advantageously, the sixth switching unit is designed as a third brake. In addition, it is proposed that a seventh switching unit of the switching units is provided to non-rotatably connect the sun gear of the fourth planetary gear with the planet carrier of the fourth planetary gear. The seventh switching unit could in particular also be provided to non-rotatably connect the sun gear of the fourth planetary gear or the planet carrier of the fourth planetary gear with the ring gear of the fourth planetary gear. Advantageously, the seventh switching unit is provided to block the fourth planetary gear. As a result, advantageously a high spread and / or a high number of turns can be provided. Advantageously, a high switching flexibility, in particular by a high number of further redundant and / or additional gears, can be realized.

Alternatively, it would be possible to dispense with a seventh switching unit, which is provided in particular for blocking the fourth planetary gear stage. This could advantageously a high switching flexibility can be achieved. In addition, an advantageously high component efficiency and / or cost efficiency could be achieved.

It is also proposed that the multistage transmission has at least one electric machine which is coupled to at least one, in particular internal gear, transmission element. As a result, in particular a hybrid functionality can be provided. Furthermore, advantageously a Boostfähigkeit many festivals can be realized. Furthermore, infinitely variable transmission ranges can advantageously be set and / or an EVT / EDA capability can be achieved. Particularly advantageous diverse EVT gears can be displayed. Preferably EVT areas can be changed without speed or performance jumps, whereby particularly preferably a high ride comfort can be realized. Preferably, a design-determined speed, in particular of less than 7000 revolutions per minute, preferably for fixed gears and EVT driving ranges, can be achieved. Furthermore, low power flows between electric machines can advantageously be realized with power-neutral EVT travel, as a result of which particularly low electrical transmission losses, high efficiency and / or low consumption can be achieved.

Furthermore, it is proposed that the electric machine has at least one rotor which is permanently connected in a rotationally fixed manner to the ring gear of the first planetary gear stage and to the sun gear of the third planetary gear stage. In particular, a good EVT performance can be achieved by this embodiment. Advantageously, it is possible to dispense with at least one and particularly advantageously at least two switching units, wherein preferably a gear reduction can be compensated by virtual gears of an electrical machine. Preferably can be dispensed with a seventh switching unit and thus an advantageous component efficiency can be achieved. Particularly preferably, a functionality of a sixth switching unit can be taken over by an electric machine, which means that the sixth switching unit can be omitted in a structurally efficient manner and / or an embodiment of the sixth switching unit is made possible as a low-loss jaw clutch. Furthermore, an advantageously low load of an electrical machine can be achieved, whereby a compact, lightweight and torque-reduced / drehmassenreduzierte construction of the electrical machine and thus a low consumption and / or low cost can be realized particularly advantageous.

The terms "axial" and "radial" are in this context in particular related to a main axis of rotation of the multi-speed transmission, so in that the term "axial" refers in particular to a direction which is parallel or coaxial with the main axis of rotation. Further, in the following, the term "radial" refers particularly to a direction that is perpendicular to the main rotation axis. A "transmission input-side arrangement" is to be understood in particular as meaning that the named component is arranged on one side of the further component, which faces the transmission input element and / or the internal combustion engine. A "gear output-side arrangement" is to be understood in particular that said component is arranged on one side of the further component, 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 stages.

The multi-speed transmission should not be limited to the application and embodiment described above. In particular, the multi-stage transmission may have a different number from a number of individual elements, components, and units referred to herein for performing a functionality described herein.

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 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.

• 1 eine schematische Darstellung eines Kraftfahrzeugs mit einer
• Antriebseinheit und mit einem erfindungsgemäßen Mehrstufengetriebe,
• 2 ein Getriebeschema des erfindungsgemäßen Mehrstufengetriebes,
• 3 ein Schaltschema des Mehrstufengetriebes,
• 4 eine Lastschaltbarkeit des Mehrstufengetriebes,
• 5 ein Getriebeschema eines weiteren Ausführungsbeispiels eines erfindungsgemäßen Mehrstufengetriebes mit einer elektrischen Maschine,
• 6 ein Getriebeschema eines weiteren Ausführungsbeispiels eines erfindungsgemäßen Mehrstufengetriebes mit einer elektrischen Maschine und
• 7 ein Getriebeschema eines weiteren Ausführungsbeispiels eines erfindungsgemäßen Mehrstufengetriebes mit einer elektrischen Maschine.

Showing:

• 1 a schematic representation of a motor vehicle with a
• Drive unit and with a multi-speed transmission according to the invention,
• 2 a transmission diagram of the multi-speed transmission according to the invention,
• 3 a circuit diagram of the multi-speed transmission,
• 4 a load shiftability of the multi-speed transmission,
• 5 a transmission diagram of a further embodiment of a multi-speed transmission according to the invention with an electric machine,
• 6 a transmission diagram of another embodiment of a multi-speed transmission according to the invention with an electric machine and
• 7 a transmission diagram of another embodiment of a multi-speed transmission according to the invention with an electric machine.

The 1 schematically shows a motor vehicle 12a. The motor vehicle 12a comprises a drive train, via which driving wheels 15a of the motor vehicle 12a are not further visible. The drive train comprises a drive unit 16a. The drive unit 16a is formed by an internal combustion engine. The drive unit 16a is formed by an internal combustion engine. Furthermore, the motor vehicle 12a has a multi-speed transmission 17a. The drive unit 16a has a driven crankshaft which is connected to a transmission input element 10a of the multi-speed transmission 17a. The multi-stage transmission 17a is formed by a motor vehicle transmission. The multi-stage transmission 17a is provided for the motor vehicle 12a. The multi-stage transmission 17a forms part of the drive train of the motor vehicle 12a. The multi-stage transmission 17a is arranged along the drive train, in particular along a power flow of the drive train, behind the drive unit 16a. The multi-stage transmission 17a is driven in at least one operating state via the drive unit 16a. In principle, the drive unit 16a could also be designed as an electric machine.

The 2 shows a transmission diagram of the multi-speed transmission 17a. The multi-speed transmission 17a is designed as a motor vehicle transmission. The multistage transmission 17a has exactly four planetary gear stages P1a, P2a, P3a, P4a which are connected to one another in terms of effect. The multi-stage transmission 17a has a main rotation axis to which the first planetary gear P1a, the second planetary gear P2a, the third planetary gear P3a, and the fourth planetary gear P4a are coaxially arranged. The first planetary gear P1a, the second planetary gear P2a, the third planetary gear P3a and the fourth planetary gear P4a are arranged in the illustrated embodiment, one behind the other along the main axis of rotation. The four planetary gear stages P1a, P2a, P3a, P4a each have a sun gear P11a, P21a, P31a, P41a. The four planetary gear stages P1a, P2a, P3a, P4a each have a ring gear P13a, P23a, P33a, P43a. The four planetary gear stages P1a, P2a, P3a, P4a each have a planet carrier P12a, P22a, P32a, P42a.

The multi-stage transmission 17a comprises a plurality of switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a. The multistage transmission 17a has exactly seven switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a, in particular a first switching unit S1a, a second switching unit S2a, a third switching unit S3a, a fourth switching unit S4a, a fifth switching unit S5a, a sixth switching unit S6a and a seventh switching unit S7a. The switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a are provided for switching and / or interconnecting the planetary gear P1a, P2a, P3a, P4a.

The multi-stage transmission 17a further includes a transmission housing 18a. The gear housing 18a accommodates the planetary gear stages P1a, P2a, P3a, P4a and the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a.

The switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a are operatively arranged within a gear set formed by the planetary gear sets P1a, P2a, P3a, P4a. The switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a are thus intended to produce different active connections between the planetary gear P1a, P2a, P3a, P4a with each other and / or the transmission housing 18a.

The multistage transmission 17a is structurally designed to switch at least eleven differently translated forward gears V1a, V2a, V3a, V4a, V5a, V6a, V7a, V8a, V9a, V10a, V11a. In the present case, the multistage transmission 17a is structurally designed to switch exactly eleven differently translated forward gears V1a, V2a, V3a, V4a, V5a, V6a, V7a, V8a, V9a, V10a, V11a. Furthermore, there are further redundant and additional gears. In the present case there are six more redundant gears. The six additional redundant gears are designed as direct gears. The six further redundant gears are designed as further seventh forward gears. The six further redundant gears are redundantly formed to the seventh forward gear V7a of the forward gears V1a, V2a, V3a, V4a, V5a, V6a, V7a, V8a, V9a, V10a, V11a. Furthermore, there are six additional additional gears in the present case. The six additional additional gears are designed as further forward gears.

Furthermore, the multi-stage transmission 17a is structurally designed to switch exactly one reverse gear Ra.

A number of the forward gears actually used and the reverse gears actually used may be limited depending on an operating strategy, for example, electronically by a correspondingly programmed control and regulating unit.

The multi-speed transmission 17a is provided to connect the drive unit 16a with at least one axle drive not shown for driving drive wheels 15a of the motor vehicle 12a. By means of the multi-stage transmission 17a, a gear ratio between the drive unit 16a and the final drive can be adjusted and / or changed.

The multistage transmission 17a has a transmission input element 10a. The transmission input element 10a is arranged on a transmission input side of the multistage transmission 17a. The transmission input element 10a is designed as a transmission input shaft. The transmission input element 10a is provided to initiate a drive torque output by the drive unit 16a into the multistage transmission 17a. The transmission input element 10a enters the multistage transmission 17a at the transmission input side. The transmission input element 10a is provided to be non-rotatably connected in the mounted state with a crankshaft of the drive unit 16a. In principle, further components, such as, for example, a vibration damper, a starting clutch, a separating clutch or a torque converter, may be arranged between the transmission input element 10a and the drive unit 16a.

Next, the multi-speed transmission 17a on a transmission output member 11a. The transmission output member 11a is disposed on the transmission output side. The transmission output member 11a is formed as a transmission output shaft. The transmission output member 11a is provided to discharge a drive torque from the multi-stage transmission 17a. 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 12a. The transmission output member 11a different modules can be followed, by means of which the out of the multi-stage transmission 17a torque can be distributed to the drive wheels 15a, such as a differential gear, which is provided for a speed compensation between the drive wheels 15a, or an all-wheel drive module, the drive torque on distributed two different drive axles.

The transmission input member 10a and the transmission output member 11a are arranged coaxially with the main rotation axis. In the present case, the transmission input element 10a defines a side facing the drive unit 16a, in particular the transmission input side. In the present case, the transmission output element 11a defines a side facing away from the drive unit 16a, in particular a transmission output side.

For the transmission input element 10a and / or the transmission output element 11a fundamentally different arrangements are conceivable in the axial direction. The illustrated Multi-stage transmission 17a is provided in particular for a front-longitudinal installation, in which the planetary gear P1a, P2a, P3a, P4a between the transmission input member 10a and the transmission output member 11a are arranged. In principle, however, it is also possible to rearrange the transmission input element 10a, the transmission output element 11a and / or the planetary gear sets P1a, P2a, P3a, P4a, for example the transmission output element 11a between two of the planetary gear sets P1a, P2a, P3a, P4a and / or on one side of the transmission input member 10a is arranged, for example, for a front Quereininbau.

The planetary gear P1a, P2a, P3a, P4a are arranged one behind the other in the axial direction. The multi-stage transmission 17a has four levels, in which the planetary gear P1a, 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 drive unit 16a than the second plane, the third plane and / or the fourth plane. In addition, the second level has a smaller distance to the drive unit 16a than the third level and / or fourth level. In addition, the third level has a smaller distance to the drive unit 16a than the fourth level. However, to redesign the multi-stage transmission 17a, it is also possible to change an order of the planetary gear stages P1a, P2a, P3a, P4a along the main rotation axis.

The first planetary gear P1a is arranged along the main rotation axis in the first plane. The first planetary gear P1a has a Einfachplanetenradsatz. The first planetary gear P1a includes a sun gear P11a, a ring gear P13a, and a planet carrier P12a. The planet carrier P12a leads planetary gears P14a on a circular path. The planet 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 first planetary gear P1a is viewed from the transmission input side in front of the second planetary gear P2a, the third planetary gear P3a and the fourth planetary gear P4a arranged.

The second planetary gear P2a is disposed along the main rotation axis in the second plane. The second planetary gear P2a is arranged along the main axis of rotation on a side facing away from the transmission input side of the first planetary gear P1a. The second planetary gear P2a has a Einfachplanetenradsatz. The second planetary gear P2a includes a sun gear P21a, a ring gear P23a and a planet carrier P22a. The planet P22a leads planetary gears P24a on a circular path. The planet 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 second planetary gear P2a is viewed from the transmission input side behind the first planetary gear P1a and before the third planetary gear P3a and the fourth planetary gear P4a arranged.

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 side of the second planetary gear P2a. The third planetary gear P3a has a Einfachplanetenradsatz. The third planetary gear P3a includes a sun gear P31a, a ring gear P33a, and a 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 third planetary gear P3a is viewed from the transmission input side behind the first planetary gear P1a and the second planetary gear P2a and before the fourth planetary gear P4a arranged.

The fourth planetary gear P4a is arranged along the main rotation axis in the fourth plane. The fourth planetary gear P4a is arranged along the main axis of rotation on a side remote from the transmission input side of the third planetary gear P3a. The fourth planetary gear P4a has a Einfachplanetenradsatz. The fourth planetary gear P4a includes a sun gear P41a, a ring gear P43a, and a planet carrier 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. The fourth planetary gear P4a is viewed from the transmission input side behind the first planetary gear P1a, the second planetary gear P2a and the third planetary gear P3a arranged.

In principle, however, an alternative arrangement of the planetary gear P1a, P2a, P3a, P4a would be conceivable. For example, it would be conceivable that the first planetary gear P1a and the third planetary gear P3a are arranged in the first plane, wherein the second planetary gear P2a is arranged in the second plane and wherein the fourth planetary gear P4a is arranged in the third plane. It would be particularly conceivable that the first planetary gear P1a and the third planetary gear P3a are stacked, the first planetary gear P1a is disposed radially within the third planetary gear P3a. Alternatively, it would also be conceivable to exchange at least two of the planetary gear stages P1a, P2a, P3a, P4a in their arrangement and / or to otherwise rearrange them. For example, the first planetary gear P1a in the first plane, the second planetary gear P2a in the second plane, the fourth planetary gear P4a in the third plane and the third planetary gear P3a in the fourth plane could be arranged.

Four switching units S1a, S2a, S3a, S7a of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a are designed as clutches. In the present case, the first switching unit S1a, the second switching unit S2a, the third switching unit S3a and the seventh switching unit S7a are formed as clutches. The switching units S1a, S2a, S3a, S7a designed as clutches each have a first rotatably mounted coupling element S11a, S21a, S31a, S71a and a second rotatably mounted coupling element S12a, S22a, S32a, S72a. The switching units S1a, S2a, S3a, S7a designed as clutches are each provided for non-rotatably interconnecting their two coupling elements S11a, S21a, S31a, S71a, S12a, S22a, S32a, S72a. The switching units S1a, S2a, S3a, S7a designed as clutches each have an open state in which their two coupling elements S11a, S21a, S31a, S71a, S12a, S22a, S32a, S72a are rotatably supported relative to one another, and a closed state, in which its two coupling elements S11a, S21a, S31a, S71a, S12a, S22a, S32a, S72a are non-rotatably connected to each other. Each of the coupling elements S11a, S21a, S31a, S71a, S12a, S22a, S32a, S72a of the clutch-formed shifting units S1a, S2a, S3a, S7a is connected to at least one of the sun gears P11a, P21a, P31a, P41a, one of the planetary gear carriers P12a, P22a , P32a, P42a and / or one of the ring gears P13a, P23a, P33a, P43a permanently non-rotatably connected.

Three switching units S4a, S5a, S6a of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a are designed as brakes. In the present case, the fourth switching unit S4a, the fifth switching unit S5a and the sixth switching unit S6a are designed as brakes. The switching units S4a, S5a, S6a designed as brakes each have a rotatably mounted coupling element S41a, S51a, S61a and a coupling element S42a, S52a, S62a arranged fixed to the housing. The switching units S4a, S5a, S6a designed as brakes are each provided for non-rotatably connecting their rotatably mounted coupling element S41a, S51a, S61a to the transmission housing 18a. The switching units S4a, S5a, S6a designed as brakes each have an open state in which their rotatably mounted coupling element S41a, S51a, S61a is rotatably mounted relative to the transmission housing 18a, and a closed state in which its rotatably mounted coupling element S41a, S51a, S61a rotationally fixed to the transmission housing 18a is connected. Each of the rotatably mounted coupling elements S41a, S51a, S61a of the brake units S4a, S5a, S6a is connected to at least one of the sun gears P11a, P21a, P31a, P41a, one of the planetary carriers P12a, P22a, P32a, P42a and / or one of the ring gears P13a, P23a, P33a, P43a permanently rotatably connected. The housing-fixedly arranged coupling elements S42a, S52a, S62a of the switching units S4a, S5a, S6a designed as brakes are permanently connected in a rotationally fixed manner to the transmission housing 18a. The fifth switching unit S5a can be implemented as a claw switching unit. The fifth switching unit S5a is designed as a claw switching unit. As a result, a particularly low power loss can be achieved. In principle, however, the fifth switching unit S5a could also be designed as a lamellae switching unit.

For connecting the planetary gear stages P1a, P2a, P3a, P4a with each other and with the coupling elements S11a, S21a, S31a, S41a, S51a, S61a, S71a, S12a, S22a, S32a, S42a, S52a, S62a, S72a, the multi-stage transmission 17a comprises a plurality of Transmission elements 19a, 20a, 21a, 22a, 23a, 24a, 25a, in particular a first transmission element 19a, a second transmission element 20a, a third transmission element 21a, a fourth transmission element 22a, a fifth transmission element 23a, a sixth transmission element 24a and a seventh transmission element 25a , The gear elements 19a, 20a, 21a, 22a, 23a, 24a, 25a are provided to support and / or transmit torques and / or rotational movements within the gear set formed by the planetary gear sets P1a, P2a, P3a, P4a. Each of the transmission elements 19a, 20a, 21a, 22a, 23a, 24a, 25a 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 S11a, S21a, S31a, S41a, S51a, S61a, S71a, S12a, S22a, S32a, S42a, S52a, S62a, S72a are permanently rotatable with each other or support at least one of the sun gears P11a, P21a, P31a, P41a, planetary carrier P12a, P22a, P32a , P42a and / or ring gears P13a, P23a, P33a, P43a permanently against the gear housing 18a from.

The transmission input element 10a is permanently connected in a rotationally fixed manner to the sun gear P11a of the first planetary gear P1a. Further, the ring gear P13a of the first planetary gear P1a with the sun P31a of the third planetary gear P3a permanently connected non-rotatably. The ring gear P13a of the first planetary gear P1a is permanently rotationally fixed to the sun gear P31a of the third planetary gear via the first transmission element 19a P3a connected. The first transmission element 19a is non-rotatably connected to the ring gear P13a of the first planetary gear P1a and to the sun P31a of the third planetary gear P3a. The first transmission element 19a forms an intermediate shaft. The first transmission element 19a in particular forms a hollow shaft. The first transmission element 19a encloses the second planetary gear P2a in a radial direction. The sun P21a of the second planetary gear P2a is permanently connected to the sun P41a of the fourth planetary gear P4a rotationally fixed. The sun P21a of the second planetary gear P2a is permanently rotatably connected via the fifth gear element 23a with the sun P41a of the fourth planetary gear P4a. The fifth gear element 23a is non-rotatably connected to the sun gear P21a of the second planetary gear P2a and to the sun gear P41a of the fourth planetary gear P4a. The fifth gear element 23a forms an intermediate shaft. The fifth gear element 23a in particular forms a solid shaft. The fifth gear member 23a extends in an axial direction through the second planetary gear P2a, the third planetary gear P3a and the fourth planetary gear P4a. In addition, the planet P22a of the second planetary gear P2a is permanently rotatably with the Planet carrier P32a the third planetary gear P3a connected. The planet carrier P22a of the second planetary gear P2a is permanently connected in a rotationally fixed manner to the planet carrier P32a of the third planetary gear P3a via the fourth transmission element 22a. The fourth gear element 22a is non-rotatably connected to the planet carrier P22a of the second planetary gear P2a and to the planet carrier P32a of the third planetary gear P3a. The fourth transmission element 22a forms an intermediate shaft. The fourth gear element 22a in particular forms a hollow shaft. The ring gear P33a of the third planetary gear P3a is permanently connected in a rotationally fixed manner to the ring gear P43a of the fourth planetary gear P4a. The ring gear P33a of the third planetary gear P3a is connected via the sixth gear element 24a permanently non-rotatably connected to the ring gear P43a of the fourth planetary gear P4a. The sixth gear element 24a is rotatably connected to the ring gear P33a of the third planetary gear P3a and the ring gear P43a of the fourth planetary gear P4a. The sixth gear element 24a forms an intermediate shaft. The sixth gear element 24a forms a hollow shaft. Furthermore, the planet carrier P42a of the fourth planetary gear P4a is permanently connected in a rotationally fixed manner to the transmission output element 11a.

The first switching unit S1a of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is provided for non-rotatably connecting the transmission input element 10a with the sun gear P41a of the fourth planetary gear P4a. For this purpose, the sun gear P41a of the fourth planetary gear stage P4a is permanently connected to the first rotatably mounted coupling element S11a of the first switching unit S1a via the fifth gear element 23a. Furthermore, the transmission input element 10a is permanently non-rotatably connected to the second rotatably mounted coupling element S12a of the first switching unit S1a. The fifth gear element 23a forms a connection. The first switching unit S1a is provided for non-rotatably connecting the transmission input element 10a with the sun gear P21a of the second planetary gear P2a. The first switching unit S1a is provided to rotatably connect the sun gear P11a of the first planetary gear P1a to the sun gear P41a of the fourth planetary gear P4a. The first switching unit S1a is provided to rotatably connect the sun gear P11a of the first planetary gear P1a to the planet carrier P22a of the second planetary gear P2a. The second switching unit S2a of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is intended to rotatably connect the transmission input member 10a with the planet P22a of the second planetary gear P2a. For this purpose, the transmission input element 10a is permanently non-rotatably connected to the first rotatably mounted coupling element S21a of the second switching unit S2a. Furthermore, the planet carrier P22a of the second planetary gear P2a is permanently non-rotatably connected to the second rotatably mounted coupling element S22a of the second switching unit S2a. The second switching unit S2a is provided to rotatably connect the sun gear P11a of the first planetary gear P1a with the planet carrier P22a of the second planetary gear P2a. The third switching unit S3a of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is provided for non-rotatably connecting the planet carrier P12a of the first planetary gear P1a with the ring gear P23a of the second planetary gear P2a. To this end, the planetary gear carrier P12a of the first planetary gear P1a is permanently connected to the first rotatably mounted coupling element S31a of the third switching unit S3a via the third gear element 21a. Furthermore, the ring gear P23a of the second planetary gear P2a is permanently connected non-rotatably to the second rotatably mounted coupling element S32a of the third shift unit S3a. The third gear element 21a forms a connection. The fourth switching unit S4a of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is provided to arrange the planet carrier P12a of the first planetary gear P1a fixed to the housing. For this purpose, the planet carrier P12a of the first planetary gear P1a is permanently connected in a rotationally fixed manner via the second transmission element 20a to the first rotatably mounted coupling element S41a of the fourth switching unit S4a. The second transmission element 20a forms a connection. The fifth switching unit S5a of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is intended to arrange the planet carrier P32a of the third planetary gear P3a fixed to the housing. For this purpose, the planet carrier P32a of the third planetary gear stage P3a is permanently connected in a rotationally fixed manner via the seventh transmission element 25a to the first rotatably mounted coupling element S51a of the fifth switching unit S5a. The seventh gear element 25a forms a connection.

The sixth switching unit S6a of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is provided to arrange the ring gear P13a of the first planetary gear P1a fixed to the housing. The ring gear P13a of the first planetary gear P1a is permanently connected to the first rotatably mounted coupling element S61a of the sixth switching unit S6a. The sixth switching unit S6a is provided to arrange the sun gear P31a of the third planetary gear P3a fixed to the housing. The sun gear P31a of the third planetary gear stage P3a is permanently connected to the first rotatably mounted coupling element S61a of the sixth shift unit S6a via the first transmission element 19a.

The seventh switching unit S7a is formed as a blocking switching unit. The seventh switching unit S7a is provided to lock the fourth planetary gear P4a. The seventh switching unit S7a of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is provided for non-rotatably connecting the sun gear P41a of the fourth planetary gear stage P4a with the planet carrier P42a of the fourth planetary gear stage P4a. The sun P41a of the fourth planetary gear P4a is permanently rotatably connected to the first rotatably mounted coupling element S71a the seventh switching unit S7a. The seventh switching unit S7a is provided to non-rotatably connect the sun gear P21a of the second planetary gear P2a to the planet carrier P42a of the fourth planetary gear P4a. Alternatively, the seventh shift unit S7a could be provided to non-rotatably connect the sun gear P41a of the fourth planetary gear P4a with the ring gear P43a of the fourth planetary gear P4a or the planet P42a of the fourth planetary gear P4a with the ring gear P43a of the fourth planetary gear P4a.

It is also conceivable to dispense with the seventh switching unit S7a. Due to the high number of additional gears while still constructively at least eleven forward gears can be realized. It would have to be adapted to adapt a translation series stand translations. As a result, advantageously a saving of components and / or an increased switching flexibility can be achieved.

The first switching unit S1a is arranged axially between the first planetary gear P1a and the second planetary gear P2a. The first switching unit S1a is designed on the inside. The second switching unit S2a is arranged axially between the first planetary gear P1a and the second planetary gear P2a. The second switching unit S2a is designed on the inside. The third switching unit S3a is arranged axially between the first planetary gear P1a and the second planetary gear P2a. The third switching unit S3a is designed inside. The fourth switching unit S4a is arranged axially between the drive unit 16a and the first planetary gear P1a. The fourth switching unit S4a is outboard. The fifth switching unit S5a is arranged axially between the second planetary gear P2a and the third planetary gear P3a. The fifth switching unit S5a is outboard. The sixth switching unit S6a is arranged axially in a plane of the first planetary gear P1a. The sixth switching unit S6a is outboard. The seventh switching unit S7a is disposed between the fourth planetary gear P4a and the first planetary gear P1a. The seventh switching unit S7a is designed inside. In principle, however, an external embodiment of the seventh switching unit S7a would also be conceivable. Furthermore, the switching units S1a, S2a, S3a, S4a, S6a, S7a can in principle be designed to be frictional or positive-locking. In the present case, at least a part of the switching units S1a, S2a, S3a, S4a, S6a, S7a form-fitting manner. The switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a can be designed, for example, as claw switching units or as lamella switching units.

This in 3 The circuit diagram shown shows how, by closing the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a, the forward gears V1a, V2a, V3a, V4a, V5a, V6a, V7a, V8a, V9a, V10a, V11a and the reverse gear Ra are switched become. The forward gears V1a, V2a, V3a, V4a, V5a, V6a, V7a, V8a, V9a, V10a, V11a and the reverse gear Ra are respectively closed by closing three of the total seven shift units S1a, S2a, S3a, S4a, S5a, S6a, S7a connected. In the 4 shown load switching results directly from the in 3 illustrated circuit diagram. A load circuit between two of the forward gears V1a, V2a, V3a, V4a, V5a, V6a, V7a, V8a, V9a, V10a, V11a is in this case always possible if at most one of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is closed and / or at most one of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is opened, ie if a power flow from one of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a to another one of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is transferred or when a switching state of only one of the switching units S1a, S2a, S3a, S4a, S5a, S6a, S7a is changed. In the present case, a load shiftability between a second forward gear V2a of the forward gears V1a, V2a, V3a, V4a, V5a, V6a, V7a, V8a, V9a, V10a, V11a and the reverse gear Ra is possible.

In the 5 . 6 and 7 Further embodiments of the invention are shown. The following descriptions and the drawings are essentially limited to the differences between the embodiments, wherein with respect to the same named components, in particular with respect to components with the same reference numerals, in principle to the drawings and / or the description of the first embodiment, in particular 1 to 4 , can be referenced. To distinguish the embodiments of the letter a is the reference numerals of the embodiment in the 1 to 4 readjusted. In the embodiments of the 5 . 6 and 7 the letter a is replaced by the letters b, c and d.

5 shows as a second embodiment, a transmission diagram of a multi-speed transmission 17b for a motor vehicle. The multistage transmission 17b is provided at least structurally for shifting at least eleven forward gears and at least one reverse gear.

The multistage transmission 17b comprises a transmission input element 10b for the non-rotatable connection of a drive unit and a transmission output element 11b for the rotationally fixed connection of an axle drive. In addition, the multi-stage transmission 17b includes a gear set having a first planetary gear P1b, a second planetary P2b, a third planetary P3b and a fourth planet P4b, each a sun P11b, P21b, P31b, P41b, 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 P11b, P21b, P31b, P41b leads. Further, the multi-stage transmission 17b includes seven switching units S1b, S2b, S3b, S4b, S5b, S6b, S7b, each having two coupling elements S11b, S21b, S31b, S41b, S51b, S61b, S71b, S12b, S22b, S32b, S42b, S52b, S62b , S72b. For transmitting power flows between the planetary gear stages P1b, P2b, P3b, P4b and / or for supporting against a transmission housing 18b, the multistage transmission 17b comprises a plurality of transmission elements 19b, 20b, 21b, 22b, 23b, 24b, 25b.

The transmission diagram of the second embodiment in 5 structurally corresponds to the transmission scheme of the embodiment in 2 , The transmission diagram of the second embodiment in 5 differs from the transmission scheme of the embodiment in 2 in that the multi-stage transmission 17b has an electric machine 13b. The electric machine 13b is coupled to the first transmission element 19b. The electric machine 13b has a rotor 14b. The rotor 14b is permanently connected in a rotationally fixed manner to the first transmission element 19b. The rotor 14b is permanently connected in a rotationally fixed manner to the ring gear P13b of the first planetary gear P1b. The rotor 14b is permanently connected to the sun P31b of the third planetary gear P3b rotationally fixed. In principle, the electric machine 13b can be coupled to any gear element that appears appropriate to the person skilled in the art.

The multi-stage transmission 17b includes the electric machine 13b to provide a hybrid drive module. However, it is also conceivable in this connection that the multi-stage transmission 17b comprises two or more electrical machines. The electric machine 13b is operable in particular as a drive machine and / or as a generator. In addition, the electric machine 13b may be provided as a starter for an internal combustion engine connected to the multi-speed transmission 17b. Also, the multi-speed transmission 17b may be provided by means of the electric machine 13b for switching EVT driving ranges, which serve in particular for a starting process. This makes it possible to dispense with an additional starting element and / or an embodiment of one of the switching units S1b, S2b, S3b, S4b, S5b, S6b, S7b as a starting element, whereby the multi-speed transmission 17b can be structurally particularly simple and inexpensive. Further, this is the sixth switching unit S6a implemented as a claw. The sixth switching unit S6a is designed as a claw switching element. The multi-stage transmission 17b can be connected to provide a hybrid functionality with a hybrid drive module, by means of which a drive torque can be changed. Further, an EVT can be realized by means of the hybrid drive module and the multi-speed transmission 17b, whereby a multi-speed transmission 17b can be realized, the transmission ratio can be adjusted continuously, at least in some areas.

6 shows a transmission diagram of a third embodiment of a multi-speed transmission 17c for a motor vehicle. The multistage transmission 17c is at least designed to provide at least eleven forward gears and at least one reverse gear.

The multistage transmission 17c comprises a transmission input element 10c for the non-rotatable connection of a drive unit and a Transmission output element 11c for non-rotatable connection of a final drive. In addition, the multi-stage transmission 17c includes a gear set including a first planetary gear P1c, a second planetary P2c, a third planetary P3c and a fourth planetary P4c, each of a sun P11c, P21c, P31c, P41c, a ring gear P13c, P23c, P33c, P43c and a planet carrier P12c, P22c, P32c, P42c which guides planetary gears P14c, P24c, P34c, P44c in a circular orbit around the corresponding sun gear P11c, P21c, P31c, P41c. Further, the multi-stage transmission 17c includes six switching units S1c, S2c, S3c, S4c, S5c, S6c each having two coupling elements S11c-S62c. For transmitting power flows between the planetary gear stages P1c, P2c, P3c, P4c and / or for supporting against a transmission housing 18c, the multi-stage transmission 17c comprises a plurality of transmission elements 19c, 20c, 21c, 22c, 23c, 24c, 25c. Furthermore, the multi-stage transmission 17c has an electric machine 13c. The electric machine 13c is coupled to the first transmission element 19c. The electric machine 13c has a rotor 14c.

The transmission diagram of the third embodiment in 6 structurally corresponds to the transmission scheme of the second embodiment in 5 , The transmission diagram of the third embodiment in 6 differs from the transmission scheme of the second embodiment in 5 in that the multi-stage transmission 17c is free of a seventh shifting unit, which is provided in particular for non-rotatably connecting the sun gear P41c of the fourth planetary gear P4c with the planet carrier P42c of the fourth planetary gear P4c.

7 shows a transmission diagram of a fourth embodiment of a multi-speed transmission 17 d for a motor vehicle. The multistage transmission 17d is provided at least structurally for shifting at least eleven forward gears and at least one reverse gear.

The multistage transmission 17d comprises a transmission input element 10d for the non-rotatable connection of a drive unit and a transmission output element 11d for the rotationally fixed connection of an axle drive. In addition, the multi-stage transmission 17d includes a gear set having a first planetary gear P1d, a second planetary gear P2d, a third planetary gear P3d and a fourth planetary gear P4d, each of 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 P11d, P21d, P31d, P41d leads. Furthermore, the multi-stage transmission 17d comprises five switching units S1d, S2d, S3d, S4d, S5d, each having two coupling elements S11d-S52d. For transmitting power flows between the planetary gear stages P1d, P2d, P3d, P4d and / or for supporting against a transmission housing 18d, the multistage transmission 17d comprises a plurality of transmission elements 19d, 20d, 21d, 22d, 23d, 24d, 25d. Furthermore, the multistage transmission 17d has an electric machine 13d. The electric machine 13d is coupled to the first transmission element 19d. The electric machine 13d has a rotor 14d.

The transmission diagram of the fourth embodiment in 7 structurally corresponds to the transmission scheme of the third embodiment in 6 , The transmission diagram of the fourth embodiment in 7 differs from the transmission scheme of the third embodiment in 6 in that the multistage transmission 17d is free of a sixth shifting unit, which is in particular provided to arrange the ring gear P13d of the first planetary gear P1d fixed to the housing. The sixth switching unit can be replaced in particular by the electric machine 13d, which can be operated to provide a braking function as a generator.

LIST OF REFERENCE NUMBERS

10

Transmission input member

11

Transmission output member

12

motor vehicle

13

electric machine

14

rotor

15

drive wheel

16

drive unit

17

Multi-speed transmission

18

gearbox

19

gear element

20

gear element

21

gear element

22

gear element

23

gear element

24

gear element

25

gear element

P1

planetary gear

P11

sun

P12

planet

P13

ring gear

P14

planet

P2

planetary gear

P21

sun

P22

planet

P23

ring gear

P24

planet

P3

planetary gear

P31

sun

P32

planet

P33

ring gear

P34

planet

P4

planetary gear

P41

sun

P42

planet

P43

ring gear

P44

planet

S1

switching unit

S11

coupling element

S12

coupling element

S2

switching unit

S21

coupling element

S22

coupling element

S3

switching unit

S31

coupling element

S32

coupling element

S4

switching unit

S41

coupling element

S42

coupling element

S5

switching unit

S51

coupling element

S52

coupling element

S6

switching unit

S61

coupling element

S62

coupling element

S7

switching unit

S71

coupling element

S72

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

V11

Forward gear

R

Reverse gear

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102005010210 A1 [0002]
• DE 102015203194 A1 [0003]

Claims (11)

Multi-stage transmission (17a), in particular for a motor vehicle (12a), having four planetary gear stages (P1a-d, P2a-d, P3a-d, P4a-d) operatively interconnected, each having a sun gear (P11a-d, P21a-d, P31a-d, P41a-d), a ring gear (P13a-d, P23a-d, P33a-d, P43a-d) and a planet carrier (P12a-d, P22a-d, P32a-d, P42a-d), with a plurality of switching units (S1a-d, S2a-d, S3a-d, S4a-d, S5a-d, S6a-c, S7a-b), with a transmission input element (10a-d) and with a transmission output element (11a-d) in which a first switching unit (S1a-d) of the switching units (S1a-d, S2a-d, S3a-d, S4a-d, S5a-d, S6a-c, S7a-b) is provided to connect the transmission input element (2a) d) with the sun gear (P41a-d) of the fourth planetary gear (P4a-d) rotatably connect, wherein the sun gear (P21a-d) of the second planetary gear (P2a-d) with the sun gear (P41a-d) of the fourth planetary gear stage ( P4a-d) is permanently connected rotationally fixed and wherein the planet carrier (P42a-d) of the fourth planetary gear stage (P4a-d) with the transmission output member (11a-d) is permanently connected non-rotatably, characterized in that the transmission input member (10a-d) permanently rotatably connected to the sun gear (P11a-d) of the first planetary gear (P1a-d) is connected and a second switching unit (S2a-d) of the switching units (S1a-d, S2a-d, S3a-d, S4a-d, S5a-d, S6a-c, S7a-b) is provided, the transmission input element (10a-d) with the planet carrier (P22a-d) of the second planetary gear (P2a-d) rotatably connect. Multi-speed transmission (17a) after Claim 1 , characterized in that the ring gear (P33a-d) of the third planetary gear (P3a-d) permanently non-rotatably connected to the ring gear (P43a-d) of the fourth planetary gear stage (P4a-d) is connected. Multi-speed transmission (17a) after Claim 1 or 2 , characterized in that the planet carrier (P22a-d) of the second planetary gear (P2a-d) permanently non-rotatably connected to the planet carrier (P32a-d) of the third planetary gear (P3a-d) is connected. Multi-stage transmission (17a) according to one of the preceding claims, characterized in that the ring gear (P13a-d) of the first planetary gear (P1a-d) with the sun gear (P31a-d) of the third planetary gear (P3a-d) is permanently connected rotationally fixed. Multi-stage transmission (17a) according to one of the preceding claims, characterized in that a third switching unit (S3a-d) of the switching units (S1a-d, S2a-d, S3a-d, S4a-d, S5a-d, S6a-c, S7a b) is provided to rotatably connect the planet carrier (P12a-d) of the first planetary gear (P1a-d) with the ring gear (P23a-d) of the second planetary gear (P2a-d). Multi-stage transmission (17a) according to one of the preceding claims, characterized in that a fourth switching unit (S4a-d) of the switching units (S1a-d, S2a-d, S3a-d, S4a-d, S5a-d, S6a-c, S7a -b) is provided to the planet carrier (P12a-d) of the first planetary gear (P1a-d) fixed to the housing. Multi-stage transmission (17a) according to one of the preceding claims, characterized in that a fifth switching unit (S5a-d) of the switching units (S1a-d, S2a-d, S3a-d, S4a-d, S5a-d, S6a-c, S7a -b) is provided to the planet carrier (P32a-d) of the third planetary gear (P3a-d) fixed to the housing. Multi-stage transmission (17a) according to one of the preceding claims, characterized in that a sixth switching unit (S6a-c) of the switching units (S1a-d, S2a-d, S3a-d, S4a-d, S5a-d, S6a-c, S7a b) is provided to arrange the ring gear (P13a-c) of the first planetary gear (P1a-c) fixed to the housing. Multi-stage transmission (17a) according to one of the preceding claims, characterized in that a seventh switching unit (S7a-b) of the switching units (S1a-d, S2a-d, S3a-d, S4a-d, S5a-d, S6a-c, S7a -b) is provided to lock the fourth planetary gear (P4a-b). Multi-stage transmission (17a) according to one of the preceding claims, characterized by at least one electric machine (13b-d) which is coupled to at least one transmission element (19b-d). Multi-speed transmission (17a) after Claim 7 characterized in that the electric machine (13b-d) comprises at least one rotor (14b-d) connected to the ring gear (P13b-d) of the first planetary gear (P1b-d) and to the sun gear (P31b-d) of third planetary gear (P3b-d) is permanently connected rotationally fixed.

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