DE102018007154A1 - Multi-speed transmission - Google Patents

Abstract

The invention relates to a multi-speed transmission, with at least three planetary gear, each having a sun gear, a ring gear and a planet carrier, and at least one further gear stage, which are operatively connected to each other, with at least six switching units, with a transmission input member and with a transmission output member, said Transmission input permanently non-rotatably coupled to the ring gear of the first planetary gear, the planet carrier of the first planetary gear is permanently rotatably connected to the planet carrier of the second planetary gear, the sun gear of the second planetary gear is permanently rotatably connected to the sun gear of the third planetary gear, wherein a fifth switching unit is provided to fix the sun gear of the first planetary gear fixed to the housing, wherein a second switching unit is provided to the ring gear of the second planetary gear with the planet carrier de The third planetary gear rotatably connect, wherein a sixth switching unit is provided to arrange the ring gear of the third planetary gear fixed to the housing, wherein the ring gear of the third planetary gear rotatably connected to the further gear stage, wherein a first switching unit is provided to the sun gear of the first planetary gear rotatably connected to the ring gear of the second planetary gear and a third switching unit is provided to rotatably connect the planet carrier of the second planetary gear with the planet carrier of the third planetary gear.

Description

The invention relates to a multi-step transmission.

There is already known a multi-speed transmission, in particular for a motor vehicle, with at least three planetary gear, each having a sun gear, a ring gear and a planet carrier, and at least one further gear stage, in particular a planetary gear or a spur gear, which are operatively connected to each other, with at least six switching units, with a transmission input element and with a transmission output element, wherein the transmission input element permanently rotatably coupled to the ring gear of the first planetary gear, the planet carrier of the first planetary gear is permanently connected rotationally fixed to the planet carrier of the second planetary gear, the sun gear of the second planetary gear permanently rotatably is connected to the sun gear of the third planetary gear, wherein a fifth switching unit is provided to arrange the sun gear of the first planetary gear fixed to the housing, wherein a second scarf Unit is provided to rotatably connect the ring gear of the second planetary gear with the planet carrier of the third planetary gear, a sixth switching unit is provided to fix the ring gear of the third planetary gear fixed to the housing, wherein the ring gear of the third planetary gear rotatably connected to the other gear stage.

The invention is in particular the object of providing an improved multi-step transmission, in particular with regard to a spread variation and / or a switching flexibility. 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 at least three planetary gear, each having a sun gear, a ring gear and a planet carrier, and at least one further gear stage, which are operatively connected to each other, with at least six switching units, with a transmission input element and with a transmission output element, wherein the transmission input element permanently rotatably coupled to the ring gear of the first planetary gear, the planet carrier of the first planetary gear is permanently connected rotationally fixed to the planet carrier of the second planetary gear, the sun gear of the second planetary gear permanently rotatably connected to the sun gear of the third planetary gear is connected, wherein a fifth switching unit is provided to arrange the sun gear of the first planetary gear fixed to the housing, wherein a second switching unit is provided to the ring gear of the second Pl Anetenradstufe with the planet carrier of the third planetary gear rotatably connect, wherein a sixth switching unit is provided to arrange the ring gear of the third planetary gear fixed to the housing, wherein the ring gear of the third planetary gear rotatably connected to the further gear stage. Under a gear stage to be understood in the context of the present invention caused by intermeshing gears of different diameters speed and torque change.

It is proposed that a first switching unit is provided to non-rotatably connect the sun gear of the first planetary gear with the ring gear of the second planetary gear and a third switching unit is provided to rotatably connect the planet carrier of the second planetary gear with the planet carrier of the third planetary gear. Preferably, the three planetary gear stages are formed by single planetary gear stages.

By means of an embodiment of the multistage transmission according to the invention, an embodiment with a high degree of flexibility and / or high efficiency can be made possible. In addition, advantageous translations can be displayed. An advantageously large spread can be achieved. Preferably, various gear and spread concepts can be implemented due to the number of gears. Furthermore, it is possible to present hybrid and all-wheel functionality. Preferably, a skilful integration of an e-machine and various stepless transmission ranges can be set. Furthermore, the multi-speed transmission can be advantageously represented only with single planetary gear stages, which allows an improvement of the gear efficiency. Furthermore, advantageously an electric machine can be integrated easily. Furthermore, component loads, in particular rotational speed and / or torque loads, may at least partially lie in advantageous areas, which enables topics such as lightweight construction and low-loss designs. Furthermore, the efficiencies of the individual gears / areas in cycle-relevant operating points may in some cases be higher than the state of the art. The switching flexibility for switching between the gears / areas is advantageously high or important circuits can be designed as a load circuit. By a more skilful choice of the circuit combination, instead of loss-causing lamellar switching elements, new claw switching elements can be used. Thus, the transmission losses can be kept low.

Preferably, the multi-speed transmission is at least structurally provided for the circuit of at least eleven forward gears. In particular, the eleven forward gears are differently stocked. Preferably, the multi-speed transmission is at least constructively provided for the circuit of exactly eleven forward gears. Preferably, there are further redundant and additional gears. In total there are fourteen independent forward gears. Furthermore, the multistage transmission is provided, in particular at least structurally, for shifting at least one reverse gear. Preferably, the multi-speed transmission is at least constructively provided for the circuit of exactly one reverse gear. An advantageously large spread can be achieved. As a result, various gear and / or spreading concepts can be implemented particularly advantageously. In particular, advantageously high switching flexibility can be achieved by the redundant gears.

The three planetary gear stages are hereinafter referred to as "first planetary gear stage", "second planetary gear stage" and "third planetary gear stage". The terms "first", "second" and "third" Planetenradstufe are provided in particular for determining an axial arrangement, wherein an axial order of the planetary gear stages and the further gear stage may differ from the order of the numbering. In principle, a modified arrangement of the planetary gear stages and the further gear stage and / or a stacked arrangement in which the planetary gear stages and the further gear stage 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 planets can be replaced kinematic equivalent by double planets, in particular, if at the same time the Hohlradanbindung 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 embodiment which is provided for permanent non-rotatable connection between the sun gears, planetary carriers, ring gears and / or coupling elements. 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. By "provided" is intended to be understood in particular specially programmed, designed and / or equipped. 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.

Preferably, at least four, preferably exactly four, of the switching units are designed as clutches. In addition, preferably at least two, advantageously at least three and particularly preferably exactly three of the switching units are designed as brakes. Under a switching unit, which is designed as a "clutch", should in particular a switching unit be understood, which is arranged in a power flow between two of the planetary gear or between a planetary gear and the other gear stage and which is intended to rotate their two rotatably arranged coupling elements which are independently rotatable in an open state, in a closed state against rotation with each other connect. Under a switching unit, which is designed as a "brake" should be understood in particular a switching unit, which is operatively arranged between one of the planetary gear or the other gear stage and a transmission housing and which is provided, their rotatable coupling element, the independent in an open state is rotatable by the transmission housing 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 and the further gear stage. 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. At least one switching unit can be designed as a dog clutch with or without synchronization unit for further loss reduction.

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, preferably two, particularly preferably exactly two, 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 further gear stage is designed as a planetary gear, wherein the ring gear of the third planetary gear is permanently connected rotationally fixed to the sun gear of the fourth planetary gear. Preferably, a fourth switching unit is provided for rotatably to the sun gear of the third planetary gear and the planet carrier of the fourth planetary gear connect. It is also proposed that a seventh switching unit is provided to arrange the ring gear of the fourth planetary gear fixed to the housing. As a result, in particular an advantageous multi-stage transmission can be provided. In particular, a multi-stage transmission can be provided, which consists of four planetary gear stages.

Furthermore, it is proposed that the further gear stage is designed as a spur gear. As a result, an advantageous transverse structure can be achieved. In this context, a "spur gear stage" is to be understood as meaning, in particular, a pairing of at least two mutually meshing spur gears, which are preferably arranged in a gear wheel plane. Advantageously, the Stirnradpaarung exactly one stand translation ratio. It is further proposed that a seventh shift unit is provided for non-rotatably connecting the ring gear of the third planetary gear stage and a first spur gear of a first gear level of the spur gear stage. Preferably, a fourth switching unit of the switching units is further provided to rotatably connect the sun gear of the third planetary gear and a third spur gear of a second gear level of the spur gear. Alternatively, it is proposed that a fourth switching unit is integrated within the spur gear. Preferably, the fourth switching unit has three switching positions, wherein a third switching position corresponds in particular to a closed switching position of the seventh switching unit. When the further gear stage is realized as a spur gear stage, the gear units assigned to the gear stage can in particular be integrated both within the spur gear stage and outside.

It is also proposed that the multistage transmission has at least one electric machine with at least one rotor, which is permanently connected in a rotationally fixed manner to the sun gear of the first planetary gear stage. By such a configuration, an advantageously hybridized multi-stage transmission can be provided with a basic structure, which allows a configuration with a high flexibility and / or a high efficiency. By clever arrangement of the wheelsets and the switching units results in a good integration option for the electric motor. As a result, EVT areas or e-gears can be advantageously displayed. The loads of the electric motor can be reduced by a better ratio formation. This leads to smaller, lighter and torque-reduced electric machines, which has a very positive effect on the additional costs compared to a "normal" automatic transmission. Furthermore, the lighter and reduced-torque electric machines also have a positive effect on fuel consumption.

The terms "axial" and "radial" are referred to below in particular to a main axis of rotation of the multi-speed transmission, so that the expression "axially" in particular denotes a direction which is parallel or coaxial with the main axis of rotation. Further, the term "radial" refers particularly to a direction which is perpendicular to the main axis of rotation. 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.

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 für das Mehrstufengetriebe,
• 4 eine Lastschaltbarkeit des Mehrstufengetriebes,
• 5 ein weiteres Ausführungsbeispiel eines Getriebeschemas des erfindungsgemäßen Mehrstufengetriebes mit einer E-Maschine,
• 6 ein weiteres Ausführungsbeispiel eines Getriebeschemas des erfindungsgemäßen Mehrstufengetriebes mit einer Stirnradstufe und
• 7 ein weiteres Ausführungsbeispiel eines Getriebeschemas des erfindungsgemäßen Mehrstufengetriebes mit der Stirnradstufe und integrierten Schalteinheiten.

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 for the multistage transmission,
• 4 a load shiftability of the multi-speed transmission,
• 5 a further embodiment of a transmission diagram of the multi-speed transmission according to the invention with an electric motor,
• 6 a further embodiment of a transmission scheme of the multi-speed transmission according to the invention with a spur gear and
• 7 a further embodiment of a transmission scheme of the multi-speed transmission according to the invention with the spur gear and integrated switching units.

The 1 schematically shows a motor vehicle 12a , The car 12a includes a drive train, beyond which not visible drive wheels 15a of the motor vehicle 12a driven become. 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 a multi-step transmission 17a on. The drive unit 16a has a driven crankshaft, which with a transmission input element 10a of the multi-speed transmission 17a connected is. The multistage transmission 17a is formed by a motor vehicle transmission. The multistage transmission 17a forms part of the drive train of the motor vehicle 12a , The multistage transmission 17a is along the drive train, in particular along a power flow of the drive train, behind the drive unit 16a arranged. The multistage transmission 17a is in at least one operating state via the drive unit 16a driven. Basically, the drive unit could 16a also be designed as an electric machine.

The 2 shows a transmission diagram of the multi-speed transmission 17a , The multistage transmission 17a is designed as a motor vehicle transmission. The multistage transmission 17a has exactly three interactively connected planetary gear stages P1a . P2a . P3a and another gear stage Z4a on. The further gear stage Z4a is as a fourth planetary gear P4a educated. The multistage transmission 17a has a main axis of rotation to which the first planetary gear P1a , the second planetary gear P2a , the third planetary gear P3a and the fourth planetary gear P4a are arranged coaxially. The first planetary gear P1a , the second planetary gear P2a , the third planetary gear P3a and the fourth planetary gear P4a are arranged one behind the other along the main axis of rotation in the illustrated embodiment. The four planetary gear stages P1a . P2a . P3a . P4a each have a sun gear P11a . P21a . P31a . P41A on. The four planetary gear stages P1a . P2a . P3a . P4a each have a ring gear P13a . P23A . P33a . P43a on. The four planetary gear stages P1a . P2a . P3a . P4a each have a planet carrier P12a . P22a . P32a . P42a on.

The multistage transmission 17a includes several switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 , The multistage transmission 17a has exactly seven switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 on, 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 S 7 , The switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 are for switching and / or interconnection of the planetary gear P1a . P2a . P3a . P4a intended.

The multistage transmission 17a further includes a transmission housing 18a on. The gearbox 18a takes the planetary gear stages P1a . P2a . P3a . P4a and the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 on.

The switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 are effective within one of the planetary gear stages P1a . P2a . P3a . P4a trained gear set arranged. The switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 are thus intended to different active connections between the planetary gear P1a . P2a . P3a . P4a with each other and / or the transmission housing 18a manufacture.

The multistage transmission 17a is designed to at least eleven different translated forward gears V1a . v2a . v3a . v4a . V5a . V6a . V7a . V8a . V9a . V10a . V11a to switch. In the present case, the multi-step transmission 17a constructively provided, exactly eleven different translated forward gears V1a - V11a to switch. Furthermore, there are further redundant and additional gears. In total there are fourteen independent forward gears V1a - V11a ,

Furthermore, the multi-step transmission 17a designed to provide at least one reverse gear 1a to switch. In the present case, the multi-step transmission 17a constructively provided, exactly one reverse gear 1a to switch.

A number of the forward gears actually used V1a - V11a , as well as the actually used reverse gears 1a may be limited depending on an operating strategy, for example, electronically by a correspondingly programmed control unit.

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

The multistage transmission 17a has a transmission input element 10a on. The transmission input element 10a is arranged on the input side. The transmission input element 10a is designed as a transmission input shaft. The transmission input element 10a is intended to be one of the drive unit 16a delivered drive torque in the multi-speed transmission 17a initiate. The transmission input element 10a is intended, in the assembled state against rotation with a Crankshaft of the drive unit 16a to be connected. Basically, between the transmission input element 10a and the drive unit 16a other components, such as a vibration damper, a starting clutch, a clutch or a torque converter, be arranged.

Next has the multi-speed transmission 17a a transmission output element 11a on. The transmission output element 11a is arranged gear output side. The transmission output element 11a is designed as a transmission output shaft. The transmission output element 11a is intended to drive torque from the multi-speed transmission 17a auszuleiten. The transmission output element 11a is intended to permanently rotatably in the assembled state with the final drive of the motor vehicle 12a to be connected. The transmission output element 11a Different modules can be connected downstream, by means of which from the multi-stage transmission 17a discharged moment on the drive wheels 15a can be distributed, such as a differential gear, for a speed compensation between the drive wheels 15a is provided, or an all-wheel drive module that distributes the drive torque to two different drive axles.

The transmission input element 10a and the transmission output member 11a are arranged coaxially with the main axis of rotation. The transmission input element 10a defines in the present case one of the drive unit 16a facing side. The transmission output element 11a defines in the present case one of the drive unit 16a opposite side.

The planetary gear stages P1a . P2a . P3a . P4a are arranged one behind the other in the axial direction. The multistage transmission 17a has four levels in which the planetary gear stages P1a . P2a . P3a . P4a are arranged. A numbering of the level corresponds to an order of the levels, which in the following apply to the transmission input element 10a is related. The first level has a smaller distance to the drive unit 16a on as the second level, the third level and / or the fourth level. In addition, the second level has a smaller distance to the drive unit 16a on as the third level and / or fourth level. In addition, the third level has a smaller distance to the drive unit 16a on as the fourth level. To redesign the multi-speed gearbox 17a However, it is also possible, an order of the planetary gear stages P1a . P2a . P3a . P4a to change along the main axis of rotation.

The first planetary gear P1a is arranged along the main axis of rotation in the first plane. The first planetary gear P1a has a simple planetary gear set. The first planetary gear P1a includes a sun wheel P11a , a ring gear P13a and a planet carrier P12a , The planet carrier P12a leads planetary gears P14a on a circular path. The planet wheels P14a comb with the sun wheel P11a and with the ring gear P13a , The planet wheels P14a are rotatable on the planet carrier P12a stored.

The second planetary gear P2a is arranged along the main axis of rotation in the second plane. The second planetary gear P2a is along the main axis of rotation on a transmission input member 10a opposite side of the first planetary gear P1a arranged. The second planetary gear P2a has a simple planetary gear set. The second planetary gear P2a includes a sun wheel P21a , a ring gear P23A and a planet carrier P22a , The planet carrier P22a leads planetary gears P24a on a circular path. The planet wheels P24a comb with the sun wheel P21a and with the ring gear P23A , The planet wheels P24a are rotatable on the planet carrier P22a stored.

The third planetary gear P3a is arranged along the main axis of rotation in the third plane. The third planetary gear P3a is along the main axis of rotation on a transmission input member 10a opposite side of the second planetary gear P2a arranged. The third planetary gear P3a has a simple planetary gear set. The third planetary gear P3a includes a sun wheel P31a , a ring gear P33a and a planet carrier P32a , The planet carrier P32a leads planetary gears P34a on a circular path. The planet wheels P34a comb with the sun wheel P31a and with the ring gear P33a , The planet wheels P34a are rotatable on the planet carrier P32a stored.

The fourth planetary gear P4a is arranged along the main rotation axis in the fourth plane. The fourth planetary gear P4a is along the main axis of rotation on a transmission input member 10a opposite side of the third planetary gear P3a arranged. The fourth planetary gear P4a has a simple planetary gear set. The fourth planetary gear P4a includes a sun wheel P41A , a ring gear P43a and a planet carrier P42a , The planet carrier P42a leads planetary gears P44a on a circular path. The planet wheels P44a comb with the sun wheel P41A and with the ring gear P43a , The planet wheels P44a are rotatable on the planet carrier P42a stored.

Four switching units S1a . S2a . S3a . S4a the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 are designed as couplings. In the present case, the first switching unit S1a , the second switching unit S2a , the third switching unit S3a and the fourth switching unit S4a designed as couplings. The switching units designed as clutches S1a . S2a . S3a . S4a each have a first rotatably mounted coupling element S11a . S21a . S31a . S41a and a second rotatably mounted coupling element S12a . S22a . S32a . S42a on. The switching units designed as clutches S1a . S2a . S3a . S4a are each intended to their two coupling elements S11a . S21a . S31a . S41a . S12a . S22a . S32a . S42a rotatably connect with each other. Each of the coupling elements S11a . S21a . S31a . S41a . S12a . S22a . S32a . S42a designed as clutches switching units S1a . S2a . S3a . S4a is with at least one of the sun gears P11a . P21a . P31a . P41A , one of the planet carrier P12a . P22a . P32a . P42a and / or one of the ring gears P13a . P23A . P33a . P43a permanently connected non-rotatably. The fourth switching unit S4a is feasible as a claw. The fourth switching unit S4a is designed as a claw switching unit. In principle, however, it would also be conceivable that the fourth switching unit S4a is replaced by a fixed connection, in which case in particular a first gear and a reverse gear would be omitted.

Three switching units S5a . S6a . S 7 the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 are designed as brakes. In the present case, the fifth switching unit S5a , the sixth switching unit S6a and the seventh switching unit S 7 designed as brakes. The switching units designed as brakes S5a . S6a . S 7 each have a rotatably mounted coupling element S51a . S61a . S71a and a housing fixedly arranged coupling element S72a on. The switching units designed as brakes S5a . S6a . S 7 are each provided to her rotatably mounted coupling element S51a . S61a . S71a rotatably with the gear housing 18a connect to. Each of the rotatably mounted coupling elements S51a . S61a . S71a the switching units designed as brakes S5a . S6a . S 7 is with at least one of the sun gears P11a . P21a . P31a . P41A , one of the planet carrier P12a . P22a . P32a . P42a and / or one of the ring gears P13a . P23A . P33a . P43a permanently connected non-rotatably. The housing fixedly arranged coupling element S72a the switching units designed as brakes S5a . S6a . S 7 is permanently rotatable with the gearbox 18a connected. The fifth switching unit S5a and / or the seventh switching unit S 7 are feasible as a claw. The seventh switching unit S 7 is designed as a claw element.

For connecting the planetary gear stages P1a . P2a . P3a . P4a with each other and with the coupling elements S11a - S72a includes the multi-step transmission 17a a plurality of transmission elements 19a . 20a . 21a . 22a . 23a in particular a first transmission element 19a , a second transmission element 20a , a third gear element 21a , a fourth gear element 22a and a fifth gear element 23a , The transmission elements 19a . 20a . 21a . 22a . 23a are intended torques and / or rotational movements within the by the planetary gear stages P1a . P2a . P3a . P4a support and / or transfer trained gear set. Each of the transmission elements 19a . 20a . 21a . 22a . 23a connects at least two of the sun gears P11a . P21a . P31a . P41A , Planet carrier P12a . P22a . P32a . P42a , Ring gears P13a . P23A . P33a . P43a and / or coupling elements S11a - S72a permanently rotatable with each other or supports at least one of the sun gears P11a . P21a . P31a . P41A , Planet carrier P12a . P22a . P32a . P42a and / or ring gears P13a . P23A . P33a . P43a permanently against the gearbox 18a from.

The transmission input element 10a is non-rotatable with the ring gear P13a the first planetary gear P1a coupled. Further, the planet carrier P12a the first planetary gear P1a permanently rotationally fixed about the first transmission element 19a with the planet carrier P22a the second planetary gear P2a connected. The first transmission element 19a is permanently rotatable with the planet carrier P12a the first planetary gear P1a and the planet carrier P22a the second planetary gear P2a connected. Furthermore, the sun gear P21a the second planetary gear P2a permanently rotationally fixed via the second transmission element 20a with the sun wheel P31a the third planetary gear P3a connected. The second transmission element 20a is permanently rotatable with the sun gear P21a the second planetary gear P2a and the sun wheel P31a the third planetary gear P3a connected. Further, the ring gear P33a the third planetary gear P3a permanently rotationally fixed about the third gear element 21a with the sun wheel P41A the fourth planetary gear P4a connected. This is the third transmission element 21a permanently rotationally fixed with the ring gear P33a the third planetary gear P3a and the sun wheel P41A the fourth planetary gear P4a connected. Furthermore, the planet carrier P42 the fourth planetary gear P4a permanently non-rotatable with the transmission output element 11a connected.

Furthermore, the first switching unit S1a provided the sun gear P11a the first planetary gear P1a over the fourth gear element 22a with the ring gear P23A the second planetary gear P2a connect to. The sun wheel P11a the first planetary gear P1a is permanently non-rotatable about the fourth gear element 22a with a first rotatably mounted coupling element S11a the first switching unit S1a connected. The ring gear P23A the second planetary gear P2a is permanently with a second rotatably mounted coupling element S12a connected. The second switching unit S2a is intended to the ring gear P23A the second planetary gear P2a rotatably with the planet carrier P32a the third planetary gear P3a connect to. The ring gear P23A the second planetary gear P2a is permanently non-rotatably with the second rotatably mounted coupling element S22a the second switching unit S2a connected. The planet carrier P32a the third planetary gear P3a is about a fifth gear element 23a permanently rotatably with the first rotatably mounted coupling element S21a connected. The third switching unit S3a the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 is intended to be the planet carrier P22a the second planetary gear P2a rotatably with the planet carrier P32a the third planetary gear P3a connect to. The planet carrier P22a the second planetary gear P2a is permanently non-rotatably with the second rotatably mounted coupling element S32a connected. The planet carrier P32a the third planetary gear P3a is about the fifth gear element 23a permanently rotatably with the first rotatably mounted coupling element P31a connected. Furthermore, the fourth switching unit S4a the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 provided the sun gear P21a the second planetary gear P2a and the sun wheel P31a the third planetary gear P3a with the planet carrier P42a the fourth planetary gear P4a rotatably connect. Besides, the sun wheel P21a the second planetary gear P2a and the sun wheel P31a the third planetary gear P3a over the fourth switching unit S4a non-rotatably with the transmission output element 11a connected.

Furthermore, the fifth switching unit S5a the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 provided the sun gear P11a the first planetary stage P1a over the fourth gear element 22a to be arranged fixed to the housing. The sun wheel P11a the first planetary stage P1a is permanently non-rotatable with the rotatably mounted coupling element S51a the fifth switching unit S5a connected. The sixth switching unit S6a of the S1a . S2a . S3a . S4a . S5a . S6a . S 7 is intended to the ring gear P33a the third planetary gear P3a to be arranged fixed to the housing. The ring gear P33a the third planetary gear P3a is permanently non-rotatable with the rotatably mounted coupling element S61a the sixth switching unit S6a connected. Further, the seventh switching unit S 7 the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 provided the ring gear P43a the fourth planetary stage P4a to be arranged fixed to the housing.

The first switching unit S1a is axially between the first planetary gear P1a and the second planetary gear P2a arranged. The first switching unit S1a is outboard. The second switching unit S2a is axially between the second planetary gear P2a and the third planetary gear P3a arranged. The second switching unit S2a is outboard. The third switching unit S3a is axially between the second planetary gear P2a and the third planetary gear P3a arranged. The third switching unit S3a is executed inside. The fourth switching unit S4a is axially in between the third planetary gear P3a and the fourth planetary gear P4a arranged. The fourth switching unit S4a is executed inside. The fifth switching unit S5a is axially between the first planetary gear P1a and the second planetary gear P2a arranged. The fifth switching unit S5a is outboard. The sixth switching unit S6a is in a plane of the third planetary gear P3a arranged. The sixth switching unit S6a is outboard. The seventh switching unit S 7 is in a plane of the fourth planetary gear P4a arranged. The seventh switching unit S 7 is outboard. Furthermore, the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 be formed in principle frictionally engaged or positively. In the present case, at least part of the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 formed positively.

This in 3 shown circuit diagram shows how by closing the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 the forward gears V1a - V11a and the reverse gear 1a be switched. The forward gears V1a - V11a and the reverse gear 1a each by closing four of the seven switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 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 - V11a In this case, it is always possible in particular when, in a switching operation, at most one of the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 is closed and / or at most one of the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 is opened, ie when a power flow from one of the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 to another of the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 is passed or if a switching state of only one of the switching units S1a . S2a . S3a . S4a . S5a . S6a . S 7 is changed.

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 exemplary embodiments, with reference in principle to the same reference components, in particular with respect to components with the same reference numerals, to the drawings and / or the description of the other embodiments, in particular 1 to 4 , can be referenced. To distinguish the Embodiments, 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 is the letter a through the letters b . c and d replaced.

5 shows as a second embodiment, a transmission diagram of a multi-speed transmission 17b for a motor vehicle, which is provided at least structurally for the switching of at least eleven forward gears and at least one reverse gear. The gearbox design corresponds structurally to the transmission scheme of 2 ,

The multistage transmission 17b includes a transmission input member 10b for the rotationally fixed connection of a drive unit and a transmission output element 11b for non-rotatable connection of a final drive. In addition, the multi-step transmission includes 17b a gear set with a first planetary gear P1b , a second planetary gear P2b , a third planetary gear P3b and another gear stage Z4B , in particular a fourth planetary gear p4b , each a sun gear 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 around the corresponding sun gear P11b . P21b . P31b . P41b leads have. Further includes the multi-speed transmission 17b seven switching units S1b . S2b . s3b . S 4 b . S5b . s6b . S7b , each two coupling elements S11b - S72b exhibit. For transmission of power flows between the planetary gear stages P1b . P2b . P3b . p4b and / or for support against a transmission housing 18b includes the multi-step transmission 17b a plurality of transmission elements 19b . 20b . 21b . 22b . 23b ,

The transmission scheme differs in particular in that the multi-speed transmission 17b an electric machine 13b includes. The electric machine 13b has a rotor 14b on. The rotor 14b is permanently rotatable with the sun gear P11b the first planetary gear P1b connected. Further, the rotor 14b over the first switching element S1b rotatably with the ring gear P23b the second planetary gear P2b connected. The rotor 14b is permanently non-rotatable with the fourth gear element 22b connected. Basically, this makes it possible to use the fifth switching unit S5b implement as a claw, or the fifth switching unit S5b omit. Basically, an electric machine 13b be coupled to each gear shaft, which can be various features allow. Furthermore, the fourth switching unit S 4 b be omitted. In principle, it would be conceivable that the fourth switching unit S 4 b is replaced by a fixed connection, whereby in particular a first gear and a reverse gear would be omitted. The functionality could then be over the shown connection of the E-machine 13b or compensated as a separate eATS. At the shown connection of the E-machine 13b can be the fifth switching unit S5b also be replaced by a claw or even completely eliminated.

6 shows as a third embodiment, a transmission diagram of a multi-speed transmission 17c for a motor vehicle, which is provided at least structurally for the switching of at least eleven forward gears and at least one reverse gear. The gearbox design corresponds structurally to the transmission scheme of 2 ,

The multistage transmission 17c includes a transmission input member 10c for the rotationally fixed connection of a drive unit and a transmission output element 11c for non-rotatable connection of a final drive. In addition, the multi-step transmission includes 17c a gear set with a first planetary gear P1c , a second planetary gear P2c , a third planetary gear P3c , each a sun gear P11c . P21C . P31c , a ring gear P13c . P23c . P33c and a planet carrier P12c . P22c . P32c , which planetary gears P14c . P24c . P34c in a circular orbit around the corresponding sun gear P11c . P21C . P31c leads, exhibit and with another gear stage Z4C , The additional gear stage is as a spur gear Q4c educated. Further includes the multi-speed transmission 17c seven switching units s1c . S 2 c . s3c . S4c . S5c . S6c . S7c , each two coupling elements S11c - S72C exhibit. The switching unit S5c is feasible as a claw. For transmission of power flows between the planetary gear stages P1c . P2c . P3c and the further gear stage Z4C , and / or for supporting against a transmission housing 18c includes the multi-step transmission 17c a plurality of transmission elements 19c . 20c . 21c . 22c . 23c ,

The transmission scheme differs in particular in the design of the gear stage Z4C , which as a spur gear Q4c is trained. The spur gear stage Q4c has four gears Q41c . Q42c . Q43c . Q44C , which are designed as spur gears, on. The spur gear stage Q4c has an output shaft 24c on. The output shaft 24c the spur gear stage Q4c is permanently non-rotatable with the transmission output element 11c connected. The transmission output element 11c is designed as a driven gear. The first spur gear Q41c the spur gear stage Q4c is over the transmission element 21c permanently rotationally fixed with the ring gear P33c the third planetary gear P3c connected. The first spur gear Q41c meshes with the second spur gear Q42c , The first spur gear Q41c and the second spur gear Q42c the spur gear stage Q4c form a first Stirnradpaarung. The first spur gear Q41c and the second spur gear Q42c the spur gear stage Q4c are arranged in a gear level. The second spur gear Q42c the spur gear stage Q4c is fixed to the output shaft 24c connected. The second spur gear Q42c the spur gear stage Q4c is formed by a festrad. The third spur gear Q43c the spur gear stage Q4c is over the transmission element 20c with the sun wheel P21C the second planetary gear P2c and the sun wheel P31c the third planetary gear P3c rotatably connected. The third spur gear Q43c meshes with the fourth spur gear Q44C , The third spur gear Q43c and the fourth spur gear Q44C the spur gear stage Q4c form a second Stirnradpaarung. The third spur gear Q43c and the fourth spur gear Q44C the spur gear stage Q4c are arranged in a gear level. The fourth spur gear Q44C the spur gear stage Q4d is fixed to the output shaft 24c connected. The fourth spur gear Q44C the spur gear stage Q4c is formed by a festrad.

The fourth switching unit S4c is designed as a claw. The seventh switching unit S7c is designed as a claw. The seventh switching unit S7c is permanently rotatable with the ring gear P33c the third planetary gear P3c and with the first spur gear Q41c the spur gear stage Q4c connected. The seventh switching unit S7c is intended, in particular in a closed position, the ring gear P33c the third planetary gear P3c and the first spur gear Q41c a first gear level of the spur gear Q4c rotatably connect. The fourth switching unit S4c is with the gear element 20c and with the third spur gear Q43c the spur gear stage Q4c permanently connected non-rotatably. The fourth switching unit S4c is intended to the sun gear P31c the third planetary gear P3c and the third spur gear Q43c a second gear level of the spur gear Q4c rotatably connect.

7 shows a fourth embodiment of a transmission diagram of a multi-speed transmission 17d for a motor vehicle, which is provided at least structurally for the switching of at least eleven forward gears and at least one reverse gear. The gearbox design corresponds structurally to the transmission scheme of 2 ,

The multistage transmission 17d includes a transmission input member 10d for non-rotatable connection of a drive unit 16d and a transmission output member 11d for non-rotatable connection of a final drive. In addition, the multi-step transmission includes 17d a gear set with a first planetary gear P1d , a second planetary gear P2d , a third planetary gear p3d , each a sun gear P11d . P21d . P31d , a ring gear P13d . P23d . P33D and a planet carrier P12d . P22d . P32d , which planetary gears P14d . P24d . P34d in a circular orbit around the corresponding sun gear P11d . P21d . P31d leads, exhibit and with another gear stage Z4D , The additional gear stage is as a spur gear Q4d educated. Further includes the multi-speed transmission 17d six switching units S 1 d . s2d . s3d . s4d . s5d . S6d , each two coupling elements S11d - S62D exhibit. For transmission of power flows between the planetary gear stages P1d . P2d . p3d and the further gear stage Z4D , and / or for supporting against a transmission housing 18d includes the multi-step transmission 17d a plurality of transmission elements 19d . 20d . 21d . 22d . 23d ,

The spur gear stage Q4d has four gears Q41d . Q42d . Q43d . Q44d , which are designed as spur gears, on. The spur gear stage Q4d has an output shaft 24d on. The output shaft 24d the spur gear stage Q4d is permanently non-rotatable with the transmission output element 11d connected. The transmission output element 11d is designed as a driven gear. The first spur gear Q41d the spur gear stage Q4d is over the transmission element 21d permanently rotationally fixed with the ring gear P33D the third planetary gear p3d connected. The first spur gear Q41d meshes with the second spur gear Q42d , The first spur gear Q41d and the second spur gear Q42d the spur gear stage Q4d form a first Stirnradpaarung. The first spur gear Q41d and the second spur gear Q42d the spur gear stage Q4d are arranged in a gear level. The second spur gear Q42d the spur gear stage Q4d is rotatable on the output shaft 24d arranged. The second spur gear Q42d the spur gear stage Q4d is formed by a loose wheel. The third spur gear Q43d the spur gear stage Q4d is over the transmission element 20d with the sun wheel P21d the second planetary gear P2d and the sun wheel P31d the third planetary gear p3d rotatably connected. The third spur gear Q43d meshes with the fourth spur gear Q44d , The third spur gear Q43d and the fourth spur gear Q44d the spur gear stage Q4d form a second Stirnradpaarung. The third spur gear Q43d and the fourth spur gear Q44d the spur gear stage Q4d are arranged in a gear level. The fourth spur gear Q44d the spur gear stage Q4d is rotatable on the output shaft 24d arranged. The fourth spur gear Q44d the spur gear stage Q4d is formed by a loose wheel.

The transmission scheme differs in particular by the integration of the fourth switching unit s4d the switching units S 1 d . s2d . s3d . s4d . s5d . S6d within the spur gear stage Q4d , The fourth switching unit s4d is between the gears, especially spur gears Q42d . Q44d arranged. The fourth switching unit s4d has a switching element SE4d. The switching element SE4d of the fourth switching unit s4d is formed axially displaceable over a not further visible actuator. The fourth switching unit s4d has three coupling elements S41d . S42d . S43d on. A first coupling element S41d the fourth switching unit s4d is permanently non-rotatable with the second spur gear Q42d the spur gear stage Q4d connected. A second coupling element S42d the fourth switching unit s4d is permanent rotatably with the output shaft 24d connected. A third coupling element S43d the fourth switching unit s4d is permanently non-rotatable with the fourth spur gear Q44d the spur gear stage Q4d connected.

The fourth switching unit s4d has three switch positions. The fourth switching unit s4d is intended, in the first switching position, the first coupling element S41d with the second coupling element S42d to pair. The fourth switching unit s4d has a second switching position. The fourth switching unit s4d is intended, in the second switching position, the third coupling element S42d with the second coupling element S42d to pair. The fourth switching unit s4d has a neutral switching position.

The seventh switching unit is eliminated. This creates a permanent non-rotatable connection between the ring gear P33D and the first spur gear Q41d , In principle, however, the seventh switching unit would be conceivable in the third transmission element 21d to integrate. Basically, the fourth switching unit s4d and the seventh switching unit also arbitrarily on the spur gear Q4d arranged. The fifth switching unit s5d is executable as a claw switching element. The fifth switching unit s5d is designed as a claw element.

LIST OF REFERENCE NUMBERS

10

Transmission input member

11

Transmission output member

12

motor vehicle

13

E-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

output shaft

P1

planetary gear

P11

sun

P12

planet

P13

ring gear

P14

planetary gears

P2

planetary gear

P21

sun

P22

Planetenradtäger

P23

ring gear

P24

planetary gears

P3

planetary gear

P31

sun

P32

planet

P33

ring gear

P34

planetary gears

P4

planetary gear

P41

sun

P42

planet

P43

ring gear

P44

planetary gears

Z4

gear stage

Q4

spur gear

Q41

gear

Q42

gear

Q43

gear

Q44

gear

R1

Reverse gear

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

S43

coupling element

SE4

switching element

S5

switching unit

S51

coupling element

S6

switching unit

S61

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

Claims (9)

Multi-speed transmission, in particular for a motor vehicle (12a), having at least three planetary gear stages (P1a-d, P2a-d, P3a-d), each having a sun gear (P11a-d, P21a-d, P31a-d), a ring gear (P13a -d, P23a-d, P33a-d) and a planet carrier (P12a-d, P22a-d, P32a-d), and at least one further gear stage (Z4a-d), which are operatively connected to each other, with at least six switching units (S1a-d, S2a-d, S3a-d, S4a-d, S5a-d, S6a-d, S7a-c), with a transmission input member (10a-d) and with a transmission output member (11a-d), said Transmission input element (10a-d) permanently rotatably coupled to the ring gear (P13a-d) of the first planetary gear (P1a-d), wherein the planet carrier (P12a-d) of the first planetary gear (P1a-d) permanent rotation with the planet (P22a -d) is connected to the second planetary gear (P2a-d), wherein the sun gear (P21a-d) of the second planetary gear (P2a-d) permanently rotatably with the sun gear (P31a-d) of the third Pla netenradstufe (P3a-d) is connected, wherein a fifth switching unit (S5a-d) is provided to the sun gear (P11a-d) of the first planetary gear (P1a-d) fixed to the housing, wherein a second switching unit (S2a-d) to is provided, the ring gear (P23a-d) of the second planetary gear (P2a-d) to the planet carrier (P32a-d) of the third planetary gear (P3a-d) rotatably connect, wherein a sixth switching unit (S6a-d) is provided in that the ring gear (P33a-d) of the third planetary gear stage (P3a-d) is fixed to the housing, wherein the ring gear (P33a-d) of the third planetary gear stage (P3a-d) is non-rotatably connected to the further gear stage (Z4a-d), characterized in that a first switching unit (S1a-d) is provided for non-rotatably connecting the sun gear (P11a-d) of the first planetary gear stage (P1a-d) with the ring gear (P23a-d) of the second planetary gear stage (P2a-d) and one third switching unit (S3a-d) is provided to the planet carrier (P22a-d) of the second P Lanetenradstufe (P2a-d) rotatably connected to the planet carrier (P32a-d) of the third planetary gear (P3a-d) to connect. Multi-step transmission after Claim 1 , characterized in that the further gear stage (Z4a-b) as a planetary gear (P4a-b) is formed, wherein the ring gear (P33a-b) of the third planetary gear (P3a-b) permanently rotatably connected to the sun gear (P41a-b) of fourth planetary gear (P4a-b) is connected. Multi-step transmission after Claim 2 , characterized in that a fourth switching unit (S4a) is provided for rotatably connecting the sun gear (P31a) of the third planetary gear (P3a) and the planet carrier (P42a) of the fourth planetary gear (P4a). Multi-step transmission after Claim 2 or 3 , characterized in that a seventh switching unit (S7a) is provided to arrange the ring gear (P43a) of the fourth planetary gear stage (P4a) fixed to the housing. Multi-step transmission after Claim 1 , characterized in that the further gear stage (Z4c-d) as a spur gear (Q4c-d) is formed. Multi-step transmission after Claim 5 , characterized in that a seventh switching unit (S7c) is provided for non-rotatably connecting the ring gear (P33c) of the third planetary gear stage (P3c) and a first spur gear (Q41c) of a first gear level of the spur gear stage (Q4c). Multi-step transmission after Claim 5 or 6 , characterized in that a fourth switching unit (S4c) is provided for non-rotatably connecting the sun gear (P31c) of the third planetary gear stage (P3c) and a third spur gear (Q43c) of a second gear level of the spur gear stage (Q4c). Multi-step transmission after Claim 5 , characterized in that a fourth switching unit (S4d) is integrated within the spur gear Q4d. Multi-step transmission after Claim 1 characterized by at least one electrical machine (13b-d) having at least one rotor (14b-d) which is permanently non-rotatably connected to the sun gear (P11a-d) of the first planetary gear (P1a-d).

Images