DE102013223427A1 - Powershift transmission for a hybrid powertrain - Google Patents

Abstract

A gearbox with a gearbox input shaft (4) and a gearbox output shaft (5) and three performance paths (L1, L2, L3) between the gearbox input shaft (4) and a main wheel set (HRS) consisting of two single planetary gear sets (P3, P4) with four in speed order as First, second, third and fourth shaft designated shafts (W1, W2, W3, W4), wherein at least one electric machine (EM1) is connected to the first shaft (W1) of the main gear set (HRS), the first shaft (W1) via first switching element (C) can be fixed and can be connected to the second power path (L2) via a second switching element (B), the second shaft (W2) being connected to the second power path (L2) via a third switching element (D) and via a fourth Switching element (E) can be connected to the third power path (L3), the third shaft (W3) being permanently connected to the transmission output shaft (5), the fourth shaft (W4) being connected to the third power path (A) via a fifth switching element (A) L3) and over he a sixth switching element (F) can be connected to the first power path (L1) and the second shaft (W2) or the fourth shaft (W4) can be fixed via a seventh switching element (G).

Description

The invention relates to a transmission with a transmission input shaft and a transmission output shaft and at least three power paths between the transmission input shaft and a consisting of two Einzelplanetenradsätzen main gear with four in speed order as the first, second, third and fourth wave called waves, between the transmission input shaft and the main gear three power paths wherein a first one of the power paths has a first fixed gear ratio, a second one of the power paths has a second fixed gear ratio and a third one of the power paths has a third fixed gear ratio, the third gear ratio being smaller than the second gear ratio and the second gear ratio being smaller than that first gear ratio.

Moreover, the invention relates to a hybrid powertrain for a motor vehicle comprising at least one internal combustion engine and at least one electric machine.

A transmission of the type mentioned is for example from the EP 0 434 525 A1 known. In the known transmission, which has five switching elements whose selective pairwise engagement causes different ratios between the transmission input shaft and the transmission output shaft, six forward gears and one reverse gear are realized.

Moreover, a hybrid powertrain for a vehicle having a transmission with nine forward gears and one reverse gear has become known from the prior art. Here comes a non-coaxial Lepelletier gearbox, which has been extended by an additional third power path. The speed provided by the additional third power path is above the speeds of the other two power paths of the Lepelletier transmission and allows three more overdrive gears. The speeds of the three power paths are realized via face gear. The known transmission is constructed parallel to the axis and power switchable by an electric machine, however, has the disadvantage that only nine forward gears are realized with a high construction cost with multiple spur gears. In addition, a standard standard or coaxial design in the known transmission can only be implemented with a further spur drive.

It is therefore an object of the invention to provide a transmission for a hybrid powertrain, with which more than nine forward gears and allows a simple structure for a standard drive common Koaxialbauweise.

This object is achieved with a transmission of the aforementioned type according to the invention that at least one electric machine is connected to the first shaft of the main gearset, wherein the first shaft is fixable via a first switching element and is connectable via a second switching element to the second power path, wherein the second shaft is connectable to the second power path via a third switching element and to the third power path via a fourth switching element, the third shaft being permanently connected to the transmission output shaft, the fourth shaft being connected to the third power path via a fifth switching element and a sixth power path Switching element with the first power path is connectable, wherein the second shaft or the fourth shaft via a seventh switching element can be fixed.

The solution according to the invention is characterized above all by a substantially reduced and simplified design, which also allows an optimization with regard to the total weight and the required installation space to be achieved. Each two switching elements can be actuated alternately by means of a double-acting actuator. In this case, a closing of a first switching element can result in an opening of a second switching element. All switching elements mentioned in this document may preferably be designed as form-locking switching elements, for example as claw switching elements, in particular jaw clutches or claw brakes. Another advantage of the transmission according to the invention is that it can achieve a degressive transition jump course. A degressive gear jump course means that the gear jumps become smaller with higher gears. In addition, the switching elements used need no synchronizer, since a synchronization of the switching elements via the electric machine and an internal combustion engine can be carried out in a no-load condition. In addition, the electric machine can serve as a speed sensor (resolver). In this case, undefined rotational speed states at the planetary gearsets inside and outside the shifting gears can be avoided by always defined rotational speeds on the electric machine at the drive and at the output. In addition, a load circuit in internal combustion engine driving can be done via the electric machine. Another advantage of the invention is that starting, starting, reversing, boosting and recuperation can take place via the electric machine.

The planetary gears used are preferably designed as negative planetary gear sets. A simple minus planetary gear set includes a sun gear, a ring gear, and a land on which planet gears are rotatably mounted, each meshing with the sun gear and the ring gear. This shows the ring gear at a fixed web on a direction opposite to the sun gear direction of rotation. In contrast, a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, all inner planetary gears mesh with the sun gear and all outer planetary gears with the ring gear, each inner planetary gear, each with an outer Planet wheel meshes. As a result, the ring gear has the same direction of rotation when holding the web as the sun gear. According to the invention, however, a minus planetary gear set can also be replaced by a positive planetary gear set, if at the same time the web and Hohlradanbindung exchanged and the amount of stationary translation of the planetary gear is increased by 1 compared to the design as a minus planetary gear.

An embodiment of the invention, which manages with a small number of required switching elements and avoids double circuits in sequential switching manner, envisages that fourteen forward gears can be realized by selective pairwise engagement of the seven switching elements, wherein twelve of the fourteen forward gears are shiftable and group circuit-free switchable the first forward speed by closing the sixth shift element and the first shift element, the second forward speed by closing the sixth shift element and the second shift element, the third forward speed by closing the sixth shift element and the third shift element, the fourth forward speed by closing the third shift element and the second Shift element, the fifth forward speed by closing the third switching element and the first switching element, the sixth forward speed by closing the third switching element and the fifth The seventh forward speed by closing the first shift element and the fifth shift element, the eighth forward speed by closing the second shift element and the fifth shift element, the ninth forward speed by closing the fourth shift element and the fifth shift element, the tenth forward speed by closing the second shift element and of the fourth shift element, the eleventh forward speed by closing the first shift element and the fourth shift element, and another speed by closing the sixth shift element and the fourth shift element, and in the event that the second shaft can be fixed via the seventh shift element, a creeper is generated by closing the seventh and sixth switching elements and a reverse gear is generated by closing the second and seventh switching element, and another gear by closing the seventh and the fifth switching element erze will be.

In an advantageous embodiment of the invention, it is provided that the second shaft via the seventh switching element can be fixed and by closing the seventh switching element and the sixth switching element creep is generated, and by closing the seventh and second switching element is a reverse gear is generated, and another gear is generated by closing the seventh and fifth switching elements.

According to a further advantageous variant of the invention, it is provided that the third power path is formed by the transmission input shaft, wherein the second power path comprises a first planetary gear set designed as an underdrive planetary gear set for outputting a rotational speed less than the rotational speed of the transmission input shaft, wherein the first power path second formed as an underdrive planetary gear set for outputting a speed less than the speed of the second power path, whose input is connected to a speed-reduced element of the Underdrive Planentenradsatzes the second power path.

A further favorable embodiment of the invention is that the web of the first Einzelplanetenradsatzes the main gearset is connected to a ring gear of the second Einzelplanetenradsatzes the main gearset, wherein the ring gear of the first Einzelplanetenradsatzes is connected to the sun gear of the second Einzelplanetenradsatzes, the web of the second Einzelplanetenradsatzes fixed is connected to the transmission output shaft.

The above object can also be achieved with a hybrid drive train of the type mentioned in the present invention that it has a transmission according to one of claims 1 to 5.

According to a further embodiment of the invention, at least one second to the internal combustion engine via at least one eighth switching element releasably connectable electric machine, preferably in the form of a starter or starter generator, may be provided, which is connected to the transmission input. In this variant of the invention there is the advantage that by opening the seventh switching element a purely electric, power-shiftable driving operation in all gears is possible. Further advantages associated with this embodiment are that a system independent of battery size results since internal combustion engine-electric driving becomes possible. Also, a regenerative operation for braking the internal combustion engine, in particular during the upshift from the first to the second or from the second to the third gear, possible.

A further advantageous variant of the invention, which allows a purely electric (not power-shiftable) driving without actuation of the brake element designed as the first switching element, provides that the second electric machine via a ninth switching element to the transmission input is detachably connectable.

A particularly simple and space-saving construction results from the fact that the first switching element and the second switching element and / or the third switching element and the fourth switching element and / or the fifth switching element and the sixth switching element and / or the eighth switching element and the ninth switching element respectively a double-acting actuator can be actuated.

The invention together with further advantages will be explained below with reference to some non-limiting embodiments, which are illustrated in the drawings. In these show schematically:

1 a speed diagram of a transmission according to the invention;

2 a schematic diagram for the in 3 and 4 illustrated transmission;

3 a transmission diagram of a first embodiment of a hybrid powertrain according to the invention with a transmission according to the invention and

4 a transmission diagram of a second embodiment of a hybrid powertrain according to the invention with a transmission according to the invention.

By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. The description of the figures is cross-figurative.

According to 1 has an inventive transmission between a in 3 with the reference number 4 characterized transmission input shaft and consisting of two Einzelplanetenradsätzen P3, P4 main gearset HRS three power paths L1, L2 and L3. The three power paths L1, L2 and L3 represent three different transmission paths for those of the transmission input shaft 4 The first power path L1 has a first fixed gear ratio i1, the second power paths L2 a second fixed gear ratio i2 and the third of the power path L3 a third fixed gear ratio i3. The third gear ratio i3 is smaller than the second gear ratio i2 and the second gear ratio is smaller than the first gear ratio i1.

The main gearset HSR has four rotatable shafts W1, W2, W3, W4 designated in order of speed, that is to say according to their order in a speed diagram, as first, second, third and fourth shafts. The first shaft W1 can be fixed via a first switching element C and can be connected via a second switching element B to the second power path L2. The second wave W2 can be connected via a third switching element D to the second power path L2 and via a fourth switching element E to the third power path L3 and fixed via a seventh switching element G. The third wave W3 is constantly with the transmission output shaft 5 connected. It should be mentioned at this point that in the present text the terms "constant" and "fixed" or "rotationally fixed" are used interchangeably. The fourth wave W4 can be connected via a fifth switching element A to the third power path L3 and via a sixth switching element F to the first power path L1.

By selective pairwise engagement of the seven switching elements A, B, C, D, E, F, G of the transmission are fourteen forward gears and a reverse gear, hereinafter also referred to as R-gear realized, wherein twelve of the fourteen forward gears are shiftable and switchable group circuit. The term "group-circuit-free switchable" is understood in the present context that when switching to a next higher or next lower gear only one switching element is opened and another switching element is closed.

From the in 1 The speed diagram and speed diagram shown, the relationships between the gears obtained by selectively engaging switching elements A, B, C, D, E, F, G and the gear ratio of each shaft W1, W2, W3, W4. The speed ratios are plotted on the individual shafts W1, W2, W3, W4 in the vertical direction. The horizontal distance between the waves results from the translations, so that can be connected to a specific operating point speed ratios by a straight line. At a certain input speed, the thirteen operating lines of the main gearset HRS characterize the speed ratios in twelve forward gears and one R-gear.

2 is an exemplary schematic for the in 1 to take shown multi-speed transmission. In 2 the internal combustion engine is provided with the reference symbol VM. For every gear two switching elements are closed. The shift pattern, the respective ratios of the individual gear ratios and the transition to be determined therefrom gearshift to the next higher gear are exemplified, the transmission has a spread of 10.0. Out 2 It can be seen that with sequential switching, double switching or group switching can be avoided, since two adjacent gear stages share a switching element. Exemplary values for the stationary ratios of the planetary gearsets for P1, P2, P3 and P4, which in the present case are designed as negative planetary gear sets, are -1.5 for P1, -1.57 for P2, -1.8 for P3 and -1.5 for P4.

A first forward speed is obtained by closing the sixth shift element F and the first shift element C, the second forward speed by closing the sixth shift element F and the second shift element B, the third forward speed by closing the sixth shift element F and the third shift element D, the fourth forward speed by closing the third shift element D and the second shift element B, the fifth forward speed by closing the third shift element D and the first shift element C, the sixth forward speed by closing the third shift element D and the fifth shift element A, the seventh forward speed by closing the first shift element C and the fifth shift element A, the eighth forward speed by closing the second shift element B and the fifth shift element A, the ninth forward speed by closing the fourth shift element E and the fifth shift element A, the tenth forward speed by Schli eßen the second switching element B and the fourth switching element E, the eleventh forward gear by closing the first switching element C and the fourth switching element E. Another gear is obtained by closing the sixth switching element F and the fourth switching element E.

A Kriechgang results by closing the sixth switching element F and the seventh switching element G. An R-gear is obtained by closing the second switching element B and the seventh switching element G.

According to 3 For example, an inventive hybrid powertrain for a motor vehicle has an internal combustion engine 1 and at least one electric machine EM1. In addition, a controller 2 for the electric machine EM1 and an electrical energy storage 3 be provided. Furthermore, the hybrid drive train has an inventive transmission with a transmission input shaft 4 and a transmission output shaft 5 on. For vibration damping between the internal combustion engine 1 and the transmission may be a torsional vibration damper 6 be provided. In addition, a second electric motor EM2 may be provided, for example in the form of a starter or starter generator. On the drive or on the output side and an axle differential and / or distribution differential can be arranged.

The electric machine EM1 can be permanently connected to the first shaft W1 of the main gearset HRS. As an alternative to a permanent connection, however, the electric machine EM1 can also be connected to and disconnected from, directly or via a gear, in particular a belt, chain, spur gear or planetary gear, to the first shaft W1.

The transmission output shaft 5 is preferably coaxial with the transmission input shaft 4 arranged. The main selector gearset HRS is preceded by a pair of planetary gears P1, P2 of the transfer gearset VRS having four shafts W1VS, W2VS, W3VS, W4VS designated as speed, first, second, third and fourth shafts.

The third power path L3 is through the transmission input shaft 4 formed, wherein the second power path L2 a first formed as an underdrive Planentenradsatz planetary gear set P1 for outputting a speed less than the rotational speed of the transmission input shaft 4 includes. The first power path L1 has a second planetary gear set P2 embodied as an underdrive planetary gearset for outputting a rotational speed less than the rotational speed of the second power path L2, whose input, here a sun gear SO2, to a speed-reduced element, here the web ST1, of the underdrive planetary gearset P1 of the second power path L2 is connected.

How out 3 and 4 can be seen, the sun gear SO1 of the planetary gear set P1 with the transmission input shaft 4 be connected, wherein the web ST1 coupled to the sun gear SO2 of the planetary gear P2 and a ring gear HO1 is fixed. The web ST2 of the planetary gear P2 can be connected via the sixth switching element F with the fourth wave W4 of the main gearset HRS. While a ring gear HO2 is fixed. The underdrive planetary gearset P2 of the first power path L1 includes at least one long planetary gear and a shared sun SO2 meshing therewith for performing the rotational speed of the land ST2 for the sixth shifting element F.

A web ST3 of the first single planetary gearset P3 of the main gearset HRS can be connected to a ring gear HO4 of the second single planetary gearset P4 of the main gearset HRS (shaft W2). The ring gear HO3 of the first Einzelplanetenradsatzes P3 is in this case with the sun gear SO4 of the second simple planetary gear set P4 connected (wave W4), wherein the web ST4 (shaft W3) of the second simple planetary gear set P4 fixed to the transmission output shaft 5 connected is. The sun gear SO3 (shaft W1) of the first single planetary gear set P3 can be connected via the second switching element B to the second power path L2 and fixed via the first switching element C.

The Einzelplanetenradsatz P4 whose sun gear SO4 is connected to the ring gear HO3 of the Einzelplanetenradsatzes P3, at least one long planetary and a combing with this split ring gear HO4 for carrying out the speed of the web ST4 for the output in the case of standard gearbox construction included.

How out 4 can be seen, the second electric machine EM2, preferably in the form of a starter or starter-generator, with the internal combustion engine 1 be connected via an eighth switching element K0. Alternatively, the second electric machine EM2 constantly with the internal combustion engine 1 be connected. The second electric machine EM2 can be disconnected or connected from the transmission input via a ninth switching element K1. When switching element K0 is open, a purely electrical power-shift operation in all gears is possible. In this case, the switching element K1 is closed or not provided, so that the electric machine EM2 with the transmission input shaft 4 connected is.

If the switching element K1 provided, it can be realized by opening the switching element, a purely electric (not power-shiftable) driving operation. Each of the switching elements K0 or K1 be provided on its own without the implementation of the other switching element K0 or K1. Also it is possible, as well as in 4 shown to install both switching elements K0 and K1.

It should also be noted that in all described embodiments of the invention, the switching elements A, B, D, E, F, G and the switching elements K0, K1 are preferably designed as jaw clutches, while the switching elements C and G are designed as brakes , Also, in all embodiments of the invention, the first switching element C and the second switching element B and / or the third switching element D and the fourth switching element E and / or the fifth switching element A and the sixth switching element F and / or the eighth switching element K0 and the ninth Switching element K1 each be actuated by a double-acting actuator. Thus, each pair of switching elements can be actuated by a single actuator. This simplifies the construction as well as the required installation space and the manufacturing costs can be reduced.

Like the one in 2 can be seen, the load circuit in internal combustion engine driving via the electric machine EM1.

An addition of the internal combustion engine 1 is also possible during purely electric driving - with closed switching element G - without interruption of traction. The internal combustion engine 1 can, after previous synchronization in the creeper and in the gear, which results from closing the seventh switching element G and the fifth switching element A, zugkraftunterbrechungsfrei be added.

To start the internal combustion engine 1 during the purely electric driving operation, the switching element G can be designed and preferably, in order to take advantage of the translation of the transfer gearset VSR, the switching element B are closed after prior synchronization. This can be done via the electric machine of the internal combustion engine 1 to be started. Subsequently, after prior synchronization, the switching element F can be closed and in the second gear (B and F closed) continue to be driven by internal combustion engine. Of course, in all other gears, including in the not listed in the switching logic gears (E and F, or G and A closed) after appropriate synchronization with the internal combustion engine combustion engine driven on.

A purely electric driving in a gear is also possible (forward / backward driving). Here is the translation of the purely electric gear 11,25. Depending on the overall ratio and speed limit of the electric machine, speeds over 30 km / h can be achieved.

LIST OF REFERENCE NUMBERS

1

internal combustion engine

2

control

3

electrical energy storage

4

Transmission input shaft

5

Transmission output shaft

6

torsion

VM

internal combustion engine

EM1

first electric machine

EM2

second electric machine

P1

first planetary gear

P2

second planetary gear

P3

third planetary gear

P4

fourth planetary gear

HRS

main gear

W1

first shaft main gearset

W2

second shaft main gearset

W3

third wave main gearset

W4

fourth wave main gearset

VRS

gearset

W1VS

first shaft transfer gearset

W2VS

second shaft gearset

W3VS

third wave gearset

W4VS

fourth wave gearset

C

first switching element

B

second switching element

D

third switching element

e

fourth switching element

A

fifth switching element

F

sixth switching element

G

seventh switching element

K0

eighth switching element

K1

ninth switching element

SO1

Sun gear of the first planetary gear

ST1

Bridge of the first planetary gear

HO1

Ring gear of the first planetary gear

SO2

Sun gear of the second planetary gear

ST2

Bridge of the second planetary gear

HO2

Ring gear of the second planetary gear

SO3

Sun gear of the third planetary gear

ST3

Bridge of the third planetary gear

HO3

Ring gear of the third planetary gear

SO4

Sun gear of the fourth planetary gear

ST4

Bridge of the fourth planetary gear

HO4

Ring gear of the fourth planetary gear

L1

first performance path

L2

second power path

L3

third power path

i1

first gear ratio

i2

second gear ratio

i3

third gear ratio

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

• EP 0434525 A1 [0003]

Claims (10)

Transmission with a transmission input shaft ( 4 ) and a transmission output shaft ( 5 ) and at least three power paths (L1, L2, L3) between the transmission input shaft ( 4 ) and a consisting of two Einzelplanetenradsätzen (P3, P4) main gearset (HRS) with four in speed order as the first, second, third and fourth wave designated waves (W1, W2, W3, W4), wherein between a transmission input and the main gear (HRS ) three power paths (L1, L2, L3) are provided, wherein a first of the power paths (L1) a first fixed gear ratio (i1), a second of the power paths (L2) a second fixed gear ratio (i2) and a third of the power paths (L3 ) has a third fixed gear ratio, wherein the third gear ratio (i3) is smaller than the second gear ratio (i2) and the second gear ratio is smaller than the first gear ratio (i1), characterized in that at least one electric machine (EM1) to the first Shaft of the main gearset (HRS) is connected, wherein the first shaft (W1) via a first switching element (C) can be fixed and via a second Ites switching element (B) with the second power path (L2) is connectable, wherein the second wave (W2) via a third switching element (D) with the second power path (L2) and a fourth switching element (E) with the third power path (L3 ) is connectable, wherein the third shaft (W3) constantly with the transmission output shaft ( 5 ), wherein the fourth wave (W4) is connectable to the third power path (L3) via a fifth switching element (A) and to the first power path (L1) via a sixth switching element (F), the second shaft (W2) or the fourth wave (W4) can be fixed via a seventh switching element (G). Transmission according to claim 1, characterized in that the electric machine (EM1) is constantly or on and wegschaltbar, directly or via a transmission to the first shaft (W1) of the main gearset (HRS) is connected. A transmission according to claim 1 or 2, characterized in that fourteen forward gears can be realized by selective pairwise engagement of the seven shift elements (A, B, C, D, E, F, G), wherein twelve of the fourteen forward gears are shiftable and group circuit-free switchable, wherein the first forward speed by closing the sixth shift element (F) and the first shift element (C), the second forward speed by closing the sixth shift element (F) and the second shift element (B), the third forward speed by closing the sixth shift element (F) and the third shift element (D), the fourth forward speed by closing the third shift element (D) and the second shift element (B), the fifth forward speed by closing the third shift element (D) and the first shift element (C), the sixth forward speed Closing the third shift element (D) and the fifth shift element (A), the seventh forward gear by closing the eighth forward speed by closing the second shift element (B) and the fifth shift element (A), the ninth forward speed by closing the fourth shift element (E) and the fifth shift element (FIG. A), the tenth forward speed by closing the second shift element (B) and the fourth shift element (E), the eleventh forward speed by closing the first shift element (C) and the fourth shift element (E) and another gear by closing the sixth shift element (F) and the fourth switching element (E) results. Transmission according to one of claims 1 to 3, characterized in that the second shaft (W2) via the seventh switching element (G) can be fixed and by closing the seventh switching element (G) and the sixth switching element (F) a creeper is generated, and by closing the seventh (G) and the second switching element (B), a reverse gear is generated, and another gear by closing the seventh (G) and the fifth switching element (E) is generated. Transmission according to one of claims 1 to 4, characterized in that the third power path (L3) through the transmission input shaft ( 4 ), wherein the second power path comprises a first planetary gear set (P1) designed as an underdrive planetary gearset for outputting a rotational speed less than the rotational speed of the transmission input shaft (11). 4 ), wherein the first power path (L1) has a second planetary gearset (P2) designed as an underdrive planetary gear set for outputting a rotational speed less than the rotational speed of the second power path (L2) whose input (SO2) to a speed reduced element (ST1) of Underdrive Planentenradsatzes (P1) of the second power path (L2) is connected. Transmission according to one of Claims 1 to 5, characterized in that the web (ST3) of the first single planetary gearset (P3) of the main gearset (HRS) is connected to a ring gear (HO4) of the second single planetary gearset (P4) of the main gearset (HRS), the ring gear (HO3) of the first single planetary gear set (P3) is connected to the sun gear (SO4) of the second single planetary gear set (P4), the web (ST4) of the second single planetary gear set (P4) being fixed to the transmission output shaft (P4) 5 ) connected is. Hybrid drive train for a motor vehicle comprising at least one internal combustion engine ( 1 ) and at least one electric machine (EM1), thereby characterized in that it comprises a transmission according to one of claims 1 to 5. Hybrid drive train according to claim 7, characterized in that at least one second to the internal combustion engine via at least one eighth switching element (K0) releasably connectable electric machine (EM2), preferably in the form of a starter or starter generator is provided, which is connected to the transmission input. Hybrid drive train according to claim 7 or 8, characterized in that the second electric machine (EM2) via a ninth switching element (K1) with the transmission input is detachably connectable. Hybrid drive train according to claim 9, characterized in that the first switching element (C) and the second switching element (B) and / or the third switching element (D) and the fourth switching element (E) and / or the fifth switching element (A) and the sixth Switching element (F) and / or the eighth switching element (K0) and the ninth switching element (K1) are each actuated by a double-acting actuator.

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