DE102014221600B3 - Transmission structure for a hybrid drive of a motor vehicle and hybrid drive - Google Patents

Abstract

The invention relates to a transmission structure for a hybrid drive of a motor vehicle, with a transmission input side combustion engine, from which a power input leads to a transmission structure with multiple planetary sets, each planetary gearset having a sun gear, a planet, a planet carrier and a ring gear, according to the invention in the transmission structure at the connection between two planetary gear sets an electric motor is integrated such that a rotor of the electric motor is connected to the ring gear of a planetary gear set and the planet carrier of another planetary gearset. The hybrid drive of a motor vehicle, comprising a drive train with an internal combustion engine, according to the invention includes a transmission with the above-described transmission structure with integrated electric motor and an electrical energy storage device connected to the transmission.

Description

The invention relates to a transmission structure for a hybrid drive of a motor vehicle according to the preamble of the first claim and a hybrid drive according to the preamble of the ninth patent claim.

It is known that such hybrid drives include a planetary gear systems operable in different gear ratios, these planetary sets known, a sun gear, with this combing planet, which are accommodated on a planet carrier and a ring gear which has a toothing on its inner diameter, which with the Planet is combing. It is also known that several courses are represented by actuation combination of switching or coupling elements or freewheels in transmissions.

From the publication DE 10 2013 21 35 59 A1 a drive device for a motor vehicle is known, which has a wheel drive train, a first electric motor with a first power output, a second electric motor with a second power output, and a coupling device for coupling at least the first and / or the second power output with the wheel drive train in a switchable manner. In this case, the coupling device is designed so that it comprises an adjustably positionable actuator according to the proviso of the coupling state of the coupling device can be fixed, wherein the positioning of the actuator is effected by controlled induction of relative rotation between the first and the second power output of the two electric motors. This solution is relatively complicated by the two required electric motors relative and by the relative rotation between the two power outputs of the electric motors for positioning the required actuator design. Furthermore, there is an increased space requirement through the use of two electric motors.

From the DE 10 2007 053 845 A1 already a transmission structure with several planetary gear sets and electric motors is known. Here, several gear stages are realized solely by the multiple electric motors.

From the DE 10 2007 005 438 A1 Further, a transmission structure with a double clutch, a gear-integrated electric motor and a plurality of planetary gear sets is known. The electric motor is here coupled directly to the planetary gear set, the planet carrier forms the output of the transmission.

There are also multi-speed range extender gear in planetary design with two electric motors, clutch / switching components of an actuator known, however, which have few switchable gears, causing certain operating points at unfavorably high speed, d. H. high fuel consumption must be driven. There are also high costs due to the two electric machines. Furthermore, these remain slightly below the required number of gears or spread.

The invention has for its object to provide a transmission structure for a hybrid drive of a motor vehicle and a hybrid drive for a motor vehicle, which is characterized by a simple structural design and allows a large spread of the gears of the transmission.

This object is achieved with the features of the 1st and 7th claim. Advantageous embodiments emerge from the subclaims.

The transmission structure for a hybrid drive of a motor vehicle is equipped with a transmission input side combustion engine from which a power input leads to the transmission structure, multiple planetary gear sets, multiple clutches and a brake, each planetary gear set having a sun gear, a planet, a planetary carrier and a first ring gear According to the invention in the transmission structure between two planetary gear sets an electric motor (acts as an electric motor and generator) is integrated.

For the first time, the electric motor is not gearbox input or terminal and its rotor assumes a "bridge function" as a connection between two planetary gear sets. The electric motor is potentially dry running.

The connection of the e-machine is such that it is not switched in the comfort critical gear change 1-2, and thus can be comfort-enhancing, z. As can be compensated by caused by the gear train jumps or gaps. The connection is also such that the electric motor turns faster in some gears than the combustion engine, so can bring a good efficiency and power density.

The transmission has advantageously more than 4 gears (for forward drive) and only an integrated electric motor and only a few clutches and a brake. Advantageously, the transmission structure allows depending on the choice of planetary gear ratios 5 or 6 gears, with the use of 3 planetary gear sets, 4 clutches and 1 brake (plus the one e-machine).

The rotor of the electric motor or the electric motor is in this case with the first planetary gearset, comprising a first sun gear, first planetary gear, a first planet carrier, a first ring gear and a second planetary gearset, comprising a second sun gear, second planetary gear, a second planetary gear carrier, a second ring gear can be coupled. Preferably, the rotor of the electric motor is connected to the first ring gear of the first planetary gear set and the second sun gear of the second planetary gear set, wherein the first planetary gear set is arranged on the input side of the engine side of the transmission.

On the output side, the second planetary gear set is adjoined by a third planetary gear set, comprising a third sun gear, third planets, a third planet carrier, a third ring gear, which is coupled to a brake and to which the power output (OUT) of the gear unit adjoins.

After the power input, the transmission structure at its input to a dual clutch, which can be coupled with a first coupling path with the first planet carrier of the first planetary gear set and with a second clutch path with the second ring gear of the second planetary gear set.

The dual clutch provided on the transmission input and the brake on the opposite transmission end are potentially arranged in a dry room. It is advantageous that in the dry room high friction and thus small forces can be realized and unactuated clutches / brakes have only low drag torque.

In addition to the input-side dual clutch only two more couplings (coupling or switching elements) are required. A first coupling element, which is located in the interior of the transmission structure, serves to block the second planetary gear set and is connectable, for example, between the second sun gear and the second ring gear. The coupling can be actuated electrically, hydraulically, hydrostatically or by means of a pull rod or push rod and can be supported with respect to the acting actuating force, for example by means of a partition wall. The partition also advantageously carries required bearings and seals and has hydraulic pressure on a pressure transfer means.

Another second coupling element may be disposed inside the transmission as coupling between the third sun and the third ring gear of the third planetary gearset (output side), or alternatively couple other ports of the third planetary gear set to lock this third planetary gearset so that all ports rotate synchronously. This second coupling element can then also be arranged on the right gear rim in a drying room.

The transmission structure has a particular neutral gear, in which KD and BA are open, but the first clutch path KB and the second clutch path KC of the double clutch are actuated. The internal combustion engine is then coupled to the electric motor, whereby a charging function of a battery connected to the electric motor can be realized. This occurs, for example, during vehicle standstill phases.

Likewise, in this neutral gear, the engine can be started with the powerful electric motor, z. B. in very cold aggregate when high starting torques are required.

For the forward drive, the transmission structure has 5 or 6 gears and additionally two purely electric driving gears or sail gears or recuperation gears, which are switchable depending on the state of charge of a coupled to the electric motor (the electric motor) battery (energy storage device) to represent driving functions without internal combustion engine. In both of these BEV gears, a first or a second clutch area of the transmission input double clutch is now open in comparison to a similarly translated normal gear (the 2nd or 4th gear) (the KB in 2nd gear, or the KC in 4th gear ). Gear changes can also be done similarly advantageous in or out of the 1st, 3rd or 5th gear.

Of course, the transmission structure has corresponding control devices for the existing switching elements and the electric machine or is connected to a control device which signals via receives the vehicle condition and the driver's request and which generates signals for driving the switching elements and the electric motor. The vehicle speed or the state of charge of a battery are examples of such signals indicating the vehicle condition. Exemplary signals indicating the driver's request are the pedal values of the so-called accelerator pedal or the brake pedal.

The invention also includes a transmission with an integrated electric motor having an aforementioned transmission structure.

According to the invention, a hybrid drive of a motor vehicle, having a drive train with an internal combustion engine and a previously described transmission with integrated electric motor, is thereby created, wherein an electric energy storage device (preferably in the manner of a battery) is connected to the transmission.

Due to the hybrid drive, an advantageous purely electric driving at speeds below 20 km / h and accelerator pedal operation can be done under 50%. At speeds above 50 km / h or maximum accelerator pedal operation by the driver, an internal combustion engine and / or electric driving is feasible.

With the solution according to the invention, a hybrid drive for a motor vehicle is provided which has a drive train with an internal combustion engine, a transmission structure and an electric motor, wherein the electric motor is integrated in the transmission structure.

The invention will be explained in more detail with reference to two embodiments and the accompanying drawings.

Show it:

1 a schematic diagram of the transmission structure

2 to 13 a 6-speed transmission with the representation of the force profiles in the gears 1 to 6 in two different schematic diagrams and thereby

2 and 3 Aisle 1,

4 and 5 Aisle 2,

6 and 7 Gear 3 in a first gear change variant whose gear ratio in the 5-speed version is identical to that of gear 4

8th and 9 Gear 4 as direct gear with gear ratio 1,

10 and 11 Aisle 5,

12 and 13 Aisle 6,

14 a variant of the transmission in which the clutch KD is arranged at a different position,

15 a variant of the transmission in which the components are arranged differently in the vicinity of the third planet,

16 a variant of the transmission, wherein the transmission output OUT between the second planet 2 and third planet 3 is arranged.

According to 1 For example, the transmission structure has a power input IN, via which a torque provided by an internal combustion engine can be coupled, for which purpose a dual clutch K1, which has a first clutch element KB and a second clutch element KC, is connected to the power input IN.

Instead of a double clutch and two independent, spatially separate couplings can be used (not shown).

• a) ein erster Planetensatz 1, bestehend aus einem ersten nicht drehenden Sonnenrad 1.1, einem ersten Planetenträger 1.2 mit diesem zugeordneten Planeten, die mit dem ersten Sonnenrad 1.1 kämmen und einem ersten Hohlrad 1.3, welches die Planeten umringt und mit diesen kämmt,
• b) ein zweiter Planetensatz 1, bestehend aus einem zweiten Sonnenrad 2.1, einem zweiten Planetenträger 2.2 mit diesem zugeordneten Planeten, die mit dem zweiten Sonnenrad 2.1 kämmen und einem zweiten Hohlrad 2.3, welches die Planeten umringt und mit diesen kämmt,
• c) ein dritter Planetensatz 3, bestehend aus einem dritten Sonnenrad 3.1, einem dritten Planetenträger 3.2 mit diesem zugeordneten Planeten, die mit dem dritten Sonnenrad 3.1 kämmen und einem dritten Hohlrad 3.3, welches die Planeten umringt und mit diesen kämmt,
• d) einer im Bereich des ersten und des zweiten Planetensatzes 1, 2 angeordneten E-Maschine 4, deren Rotor 4.1 eine Brückenfunktion besitzt und mit dem ersten Hohlrad 1.3 des ersten Planetensatzes 1 und dem zweiten Planetenträger 2.2 des zweiten Planetensatzes 2 verbunden ist. Die E-Maschine 4 kann wie skizziert die Planetensätze 1 und 2 vollständig oder teilweise umschließen, oder auch axial teilweise oder vollständig daneben platziert werden, wobei dann die Brückenfunktion von einem passiven Bauteil ausgefüllt würde. Die Leistungsabgabe oder -aufnahme der E-Maschine 4 kann also über beide Verbindungen mit ersten Planetensatz 1 und/oder zweiten Planetensatz 2 je nach geschaltetem Gang erfolgen und erlaubt eine Nutzung der E-Maschine 4 in vielen Schaltzuständen des Getriebes.
• e) einer nahe dem zweiten Planetensatz 2 angeordneten ersten Kupplung KE, die sich im inneren des Getriebes befindet und hydraulisch, hydrostatisch oder mittels einer Zug- oder Druckstange (nicht dargestellt) aktiviert wird,
• f) eine zweite Kupplung KD, durch welche der dritten Planetensatz 3 verblockbar ist, indem hier das Hohlrad 3.3 mit dem Planetenträger 3.2 verkoppelt wird,
• g) eine Bremse BA, welche das Hohlrad 3.3 des dritten Planetensatzes 3 festbremst.

In the transmission structure act (here from left to right)

• a) a first planetary gear set 1 consisting of a first non-rotating sun gear 1.1 , a first planetary carrier 1.2 with this planet associated with the first sun gear 1.1 combing and a first ring gear 1.3 that surrounds and meshes with the planets,
• b) a second planetary gear set 1 consisting of a second sun gear 2.1 , a second planetary carrier 2.2 with this planet associated with the second sun gear 2.1 comb and a second ring gear 2.3 that surrounds and meshes with the planets,
• c) a third planetary set 3 consisting of a third sun gear 3.1 , a third planet carrier 3.2 with this planet associated with the third sun 3.1 comb and a third ring gear 3.3 that surrounds and meshes with the planets,
• d) one in the region of the first and second planetary gear sets 1 . 2 arranged electric machine 4 whose rotor 4.1 has a bridge function and with the first ring gear 1.3 of the first planetary gear set 1 and the second planetary carrier 2.2 of the second planetary gear set 2 connected is. The electric machine 4 can sketched as the planetary gear sets 1 and 2 completely or partially enclose, or even axially partially or completely placed next to it, in which case the bridge function would be filled by a passive component. The power output or recording of the electric motor 4 So can both connections with first planetary gear set 1 and / or second planetary gear set 2 depending on the gear engaged and allows use of the electric motor 4 in many switching states of the transmission.
• e) one near the second planetary set 2 arranged first clutch KE, which is located inside the transmission and is hydraulically, hydrostatically or by means of a pull or push rod (not shown) is activated,
• f) a second clutch KD, through which the third planetary gear set 3 is blockable, here by the ring gear 3.3 with the planet carrier 3.2 is coupled
• g) a brake BA, which the ring gear 3.3 of the third planetary gear set 3 fixed braking.

The power output OUT is connected to the third planetary gearset 3 at. In this case, the planet carrier of the third planetary gear set forms 3 also the transmission output and is connected for example via a differential, not shown, on the front and / or rear axle.

Thus, the transmission structure comprises only three planetary gear sets 1 . 2 . 3 , four couplings KB, KC, KE, KD and a brake BA and an electric motor 4 ,

Below, transmission diagrams of a multi-speed transmission with the power flow in the gears 1 to 6 are shown. Only the switched switching elements and power flows were highlighted here. The respective combination of planetary gear ratios i0 of the three planetary gear sets are listed under the respective planetary gearset.

In a first transmission variant, the stand translations can approximate -1.5 in the first planetary gear set 1 . -2 in the second planetary set 2 and -2 in the third planetary set. be. These translations are given below the planetary gear sets.

This can be a very big spread 9 and large, but numerically similar increments in increments of 5 different translations are realized.

In a further variant, the stand translations can approximate -2.4 in the first planetary gear set 1 . -2 in the second planetary set 2 and -1.6 in the third planetary set be.

This second variant is the bold and italic written translations below the planetary gear sets 1 to 3 clarified.

This will cause a smaller spread 6.3 realized in smaller and numerically similar increments between 6 different translations.

In a 6-speed transmission, the first gear is according to 2 and 3 realized by the following circuits: The brake BA, the second coupling element KC of the double clutch K1 and the first clutch KE are closed. The planetary set 1 is without function, the planetary gear set 2 is blocked and the planetary set P3 converts. The electric machine 4 In this case it rotates at the same speed as the transmission input (internal combustion engine) IN and, depending on the driving situation, can supply or record additional drive power (charge or recuperate the battery).

Also in the case of a z. B. targeted slipping operated friction clutch KC, the electric motor 4 drive power in this gear or record their performance does not have to be transmitted through the clutch and does not contribute to their friction losses.

Two different transmission diagrams documenting the 2nd gear are in the 4 and 5 shown. In this switching stage, the brake BA, the first coupling element and the first clutch path KB of the dual clutch K1 and the first clutch KE are closed. The first planetary gear set 1 turns into the fast, the second planetary gear set 2 is without function and the third planetary set 3 translated.

As a result, the electric machine rotates 4 with higher speed as the transmission input (internal combustion engine) IN and can, depending on the driving situation, additional drive power of an electric motor (electric motor 4 ) or in the manner of a generator (charge or recuperate battery). The higher speed is advantageous in terms of higher performance and efficiency of the electric motor 4 and / or the lower speed of the transmission input is advantageous in terms of higher efficiency of the internal combustion engine. Again, in the case of z. B. for acoustic reasons purposefully slipping operated friction clutch in the form of a first coupling element KB the electric motor 4 Drive power or record, with their power does not have to be transmitted through the clutch and does not contribute to their friction losses.

In third gear (see 6 and 7 ) are the brake BA, and both coupling elements (coupling paths) KB and KC of the dual clutch K1 closed, whereby a power split or power backflow arises in the transmission. In addition to the drive by means of the internal combustion engine (input via IN), a charging of a battery, not shown, by means of the electric motor 4 be realized, which then acts as a generator. Likewise, the combustion engine can be supported by the electric motor ("boost").

To fourth gear (see 8th and 9 ) is a double switch, since the second and the third planetary gear set 2 . 3 are blocked, which is realized by the first and second clutches KE and KD closed here. Here, the internal combustion engine drives via IN, and the input-side second clutch path KC of the dual clutch K1 is closed. There may be an additional drive power or charging function via the electric motor 4 to be provided. The gear ratio is one and the transmission efficiency is very high, as no load-bearing toothing rolls.

The transmission diagrams with the power flow in the 5th gear are in the 10 and 11 shown. The first clutch path KB and the first clutches KE and the second clutch KD are closed. Here translated the first planetary gear set 1 fast, while the second and third planetary gear set 2 and 3 both are blocked. Overall, this results in an overdive.

The gear 6 is based on two transmission diagrams in the 12 and 13 shown, in 13 as everywhere the power flow is indicated by the strongly emphasized lines. Both the combustion engine and the electric motor 4 if this acts as an electric motor, provide a drive power. Furthermore, by the electric motor (if it acts as a generator) and the battery (not shown) to be loaded. The first and second coupling element KB and KC of the dual clutch K1 and the second clutch KD are closed.

The possible functions of the transmission and specific characteristics of gears 4, 5 and 6 are similar to gears 1, 2 and 3 except for the contribution of the third planet 3 which is either blocked (gears 4, 5 and 6) or translated (gears 1, 2 and 3).

The second coupling element KD is in the above-described figures at the transmission output as a coupling between the third planet carrier 3.2 and third ring gear 3.3 right, here third planetary set 3 arranged. The first clutch KE and the second clutch KD can also be rearranged, as these only for blocking the second planetary gear set 2 and / or the third planetary gear set 3 be used.

For example, this may be the second clutch KD according to 14 also on the inside of the transmission (here on the left) of the third planetary gearset 3 be arranged.

Also alternatively, the actuatable second clutch KD the ring gear 3.3 and the sun wheel 3.1 couple together.

Also alternatively, the transmission as in 15 represented between the second planet 2 and the third planet 3 divided into two halves each with its own housing and a connecting shaft (eg cardan shaft between the gearbox and rear axle gearbox). In this case, the environment of the second clutch KD can in turn form a drying space.

Also alternative and functionally identical, the transmission as in 16 shown configured such that the transmission output OUT between the second planet 2 and third planet 3 is arranged. This arrangement is particularly suitable for font-transverse drive trains or front-longitudinal drive trains. It allows the second clutch KD and the brake BA to be arranged in a drying space at the right end of the transmission in the figure.

An overview of the gear spectrum and the operating options of a first variant of the transmission with large spread 9 and large increments and the corresponding circuits are shown below. iVM is the translation of the internal combustion engine and iEM the translation of the electric motor (acting as an electric motor and / or as a starter and / or as a generator): actuated corridor Clutch / brake i _VM i _EM Remarks 1 BA _ KC _ KE 3 3 1 without function, 2 blocked, 3 converts 2 BA KB _ _ KE 1.8 3 1 into the fast, 2 without function, 3 translated 3 BA KB KC _ _ 1 1.67 4 _ KC KD KE 1 1 Double switching 3-4 5 _ KB _ KD KE 0.6 1 6 _ KB KC KD _ 12:33 12:55

Another overview of the gear spectrum and the operating options of a second variant of the transmission with a smaller spread 6.3 and smaller increments is shown in the table below. iVM is also the translation of the internal combustion engine and iEM the translation of the e-machine against the output: actuated corridor Clutch / brake i _VM i _EM Remarks 1 BA _ KC _ KE 3 3 1 without function, 2 blocked, 3 converts 2 BA KB KE 2.12 3 1 fast, 2 no function, 3 over puts 3 BA KB KC _ _ 1:44 2 4 _ KC KD KE 1 1 Double switching 3-4 5 KB _ KD KE 0.71 1 6 KB KC KD _ 12:48 0.68

The combinations or the like listed in the two aforementioned tables are characteristic of well-graded and well-spread gears.

If the first clutch element / first clutch path KB of the dual clutch K1 is open in both transmission variants in the second gear or the second clutch element / second clutch path KC of the double clutch K1 is opened in fourth gear, then a BEV gear is realized, ie a purely electric drive via the E Engine, wherein the internal combustion engine can be stopped to reduce exhaust and noise emissions.

If the first clutch KE is opened in both transmission variants in first gear or in fourth gear, a CVT-like range is provided, ie a stepless transmission. In this mode are control technology, the moment of the internal combustion engine and the moment of the electric motor in a by the state translation of the second planet 2 set fixed torque ratio, which mix or share the performance of these two drives in the transmission.

If neither the second clutch KD nor the brake BA is actuated (that is, for example, only the first clutch element KB of the dual clutch K1), then a neutral gear is realized, in which, however, the internal combustion engine is operatively connected to the electric motor. The e-machine can work as a generator and the battery is charged. Similarly, the electric motor can work as a starter, and start the engine. These functions are possible at standstill of the vehicle as well as when the vehicle is rolling. Since there is no connection to the output, this charging function or starting function have no influence on the vehicle acceleration and can be executed smoothly.

Thus, the transmission further operating modes, which can be used as a purely electric driving gears or CVT areas or leagues or Rekuperationsgänge or starting gears or charging gears depending on the vehicle speed and state of charge of the battery. In the two BEV gears, a clutch element / clutch path is now open in each case compared to a similarly translated normal gear (the 2nd or 4th gear) (the KB in 2nd gear, or the KC in 4th gear). Gear changes can also be done similarly advantageous in or out of the 1st, 3rd or 5th gear.

With the solution according to the invention, a transmission is provided, which has more than 4 gears (only forward) and only one integrated in an advantageous place e-machine, and thereby has only a few clutches and brakes.

This can be achieved by a planetary gear structure, which allows 5 or 6 gears depending on the choice of planetary gear ratios, using three planetary gear sets, four clutches and a brake, and an electric motor.

The transmission structures shown can be used for standard drives (longitudinal motor and gearbox), but also for front-transverse drives or front-mounted drives or other configurations.

LIST OF REFERENCE NUMBERS

1

first planetary gear set

1.1

first sun gear

1.2

first planet carrier

1.3

first ring gear

2

second planetary set

2.1

second sun wheel

2.2

second planet carrier

2.3

second ring gear

3

third planetary set

3.1

third sun wheel

3.2

third planet carrier

3.3

third ring gear

4

E-machine

4.1

rotor

BA

brake

IN

power Entry

i0

Planet-ratios

K1

Double coupling

KB

first coupling element / coupling path of the double clutch K1

KC

second coupling element / coupling path of the double clutch K1

KD

second clutch

KE

first clutch

OUT

power output

Claims (8)

A transmission structure for a hybrid drive of a motor vehicle, comprising a transmission input side internal combustion engine, from which a power input (In) leads to a gear train having a plurality of planetary gear sets, each planetary gear set having a sun gear, planets, a planet carrier and a ring gear, wherein in the transmission structure at the connection between two planetary gear sets an electric motor ( 4 ) is integrated such that a rotor ( 4.1 ) of the electric machine ( 4 ) is connected to the ring gear of a planetary gear set and the planet carrier of a further planetary gear set, and wherein after the power input (In) of the gear stage, a double clutch (K1) is arranged with a first clutch path (KB) with the first planet carrier ( 1.2 ) of the first planetary gear set ( 1 ) and with a second coupling path (KC) with the second ring gear ( 2.3 ) of the second planetary gear set ( 2 ), characterized in that the rotor ( 4.1 ) of the electric machine ( 4 ) with a first ring gear ( 1.3 ) of a first planetary gear set ( 1 ) and a second planet carrier ( 2.2 ) of a second planetary gear set ( 2 ) and that the first planetary gear set ( 1 ) is arranged on the input side, that to the second planetary gear set ( 2 ) on the output side, a third planetary gear set ( 3 ), having a third sun gear ( 3.1 ), third planet, a third planet carrier ( 3.2 ), a third ring gear ( 3.3 ), whose third planet carrier ( 3.2 ) forms the power output (OUT) of the transmission structure, wherein a second sun gear ( 2.1 ) of the second planetary gear set ( 2 ) with the third sun wheel ( 3.1 ) of the third planetary set ( 3 ) is coupled. Transmission structure according to claim 1, characterized in that the transmission structure has a first coupling element (KE), with which the second planetary gear set ( 2 ) is blockable and this second planetary set ( 2 ) has a stand ratio of approximately 2 and / or that the transmission structure has a second coupling element (KD), with which the third planetary gear set ( 3 ) is blockable. Transmission structure according to claim 2, characterized in that the first coupling element (KE) on the one hand between the second sun gear ( 2.1 ) of the second planetary gear set ( 2 ) and the second ring gear ( 2.3 ) of the second planetary gear set ( 2 ) is connectable and / or that the second coupling element (KD) between the third sun ( 3.1 ) and the third ring gear ( 3.3 ) of the third planetary set ( 3 ) is arranged. Gear structure according to claim 3, characterized in that the first coupling element (KE) can be actuated electrically, hydraulically, hydrostatically or by means of a pull rod or push rod and that an acting Aktuierkraft can be supported by means of a partition wall. Transmission structure according to one of claims 1 to 4, characterized in that it has a neutral gear in which at least one of the coupling paths KB or KC of the double clutch (K1) is actuated and the internal combustion engine with the electric motor ( 4 ) is coupled and a charging function is feasible and that this has a used as a purely electrical drive or sail or recuperation gear operation mode, depending on the state of charge one with the electric motor ( 4 ) coupled battery is switchable, in which the first coupling path (KB) and the second coupling path (KC) are opened. Transmission structure according to one of claims 1 to 5, characterized in that this in a transmission with integrated electric motor ( 4 ) is integrated, wherein the transmission or the transmission structure is connected to a control device which receives signals about the vehicle condition and the driver's request and which signals for driving the switching elements and the electric motor ( 4 ) generated. Hybrid drive of a motor vehicle, comprising a drive train with an internal combustion engine, characterized in that the hybrid drive, a transmission comprising a transmission structure according to one of the preceding claims with integrated electric motor ( 4 ) and an electrical energy storage device connected to the transmission. Hybrid drive according to claim 7, characterized in that by the hybrid drive at speeds below 20 km / h and accelerator pedal operation under 50% by the driver a purely electric Driving occurs, and at speeds above 50 km / h or maximum accelerator pedal operation by the driver, an electric and combustion engine driving is feasible.

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