DE102013225208B4 - Transmission for a motor vehicle - Google Patents

Abstract

Transmission (G) for a motor vehicle with a transmission input shaft (GW1) and a transmission output shaft (GW2), a main gearset (HRS), a Zusatzradsatz (ZRS), and an electric machine (EM) with a rotor (R) and a stator (S), wherein the main gearset (HRS) has a first and a second planetary gear set (P1, P2) with a total of four designated in speed order as the first, second, third and fourth waves (W1, W2, W3, W4), the transmission (G) having first, second, third and fourth shifting elements (A, C, D, E), the third shaft (W3) of the main gearset (HRS) being connected to the transmission output shaft (GW2), the supplementary gear set (ZRS) comprises a planetary gear set (P4) having first, second and third shafts (W1P4, W2P4, W3P4), the first shaft (W1P4) of the supplementary gear set (ZRS) being permanently connected to the rotor (R), the second shaft (W2P4) of the additional gear set (ZRS) with the first shaft (W1) of the main gearset (HRS) s is continuously connected, wherein the third shaft (W3P4) of Zusatzradsatzes (ZRS) with the second, third or fourth shaft (W2, W3, W4) of the main gearset (HRS) is constantly connected, characterized in that by closing the second switching element (E ), the transmission input shaft with the second shaft (W2) of the main gearset (HRS) is connectable, by closing the third switching element (C), the first shaft (W1) of the main gearset (HRS) is rotatably fixable, wherein closing the fourth switching element (D) the second shaft (W2) or the fourth shaft (W4) of the main gearset is rotationally fixed festsetzbar, whereby- in the case that the fourth switching element (D) of the second shaft (W2) of the main gearset (HRS) is assigned by closing of the first shift element (A), the fourth shaft (W4) of the main gearset (HRS) with the transmission input shaft (GW1) is connectable, and- in the case that the fourth switching element (D) of the fourth shaft (W4) of the main gearset (HRS ) assigned , By closing the first switching element (A), the first shaft (W1) of the main gearset (HRS) with the transmission input shaft (GW1) is connectable.

Description

The invention relates to a transmission with a transmission input shaft and a transmission output shaft, a main gearset, a Zusatzradsatz, and an electric machine having a rotor and a stator, wherein the main gearset first and a second planetary gear set with four in speed order as the first, second, third and fourth shaft has designated waves, wherein the transmission input shaft via at least one switching element with at least one of the four shafts of the main gear is connectable, wherein the third shaft of the main gearset is connected to the transmission output shaft, wherein the Zusatzradsatz a planetary gear set with a first, second and third shaft, and wherein the first shaft of the Zusatzradsatzes is connected to the rotor. The invention also relates to a drive train for a motor vehicle with a transmission.

A transmission referred to here in particular a multi-speed transmission in which a predefined number of gears, ie fixed gear ratios between a transmission input shaft and a transmission output shaft, is automatically switched by switching elements. The switching elements are, for example, clutches or brakes here. Such transmissions are mainly used in motor vehicles to adjust the speed and torque output capability of the drive unit to the driving resistance of the vehicle in a suitable manner.

From the patent application DE 10 2012 201 377 A1 The applicant is a transmission with a transmission input shaft and a transmission output shaft and two power paths between the transmission input shaft and a main gearset with two Einzelplanetenradsätzen with four in speed order as first, second, third and fourth wave known waves, wherein the third of the four shafts connected to the transmission output shaft is. An electric machine is connected via a planetary gear to the first shaft of the main gearset.

The patent application US 2007/0 129 196 A1 describes several electrically variable vehicle transmissions with three planetary gear sets and two electric machines. The gearboxes are characterized by stepless operation and four fixed gears.

The object of the invention is to improve the load switching behavior of the transmission known in the prior art.

Another object of the invention is to improve the range of use of the transmission so that the electric machine in each gear is capable of receiving or delivering mechanical power from the transmission output shaft.

The objects are achieved by the features of claim 1, wherein advantageous embodiments of the dependent claims, the description and from the figures.

The transmission comprises at least a transmission input shaft and a transmission output shaft, a main gearset, a Zusatzradsatz, and an electric machine with a rotor and a stator.

The main gearset has a first and a second planetary gear set with a total of four designated in speed order as the first, second, third and fourth wave waves. The main gearset is thus designed as a two-bar four-shaft gearbox. The Zusatzradsatz has a planetary gear set with a total of three designated as first, second, and third wave waves. The first shaft of Zusatzradsatzes is permanently connected to the rotor.

Under a two-bridge four-shaft transmission is a planetary gear to understand that is formed of two over exactly two coupling shafts kinematically coupled to each other single planetary gear sets and in which four of its elements ("waves") are freely accessible to other transmission elements. A coupling shaft is defined as a permanent mechanical connection between an element - ie sun gear or web or ring gear - the first single planetary gear set with an element - ie sun nenrad or web or ring gear - the second single planetary gear set. The number of individual planetary gear sets and the number of free waves are not defined by the visual appearance of the transmission, but by its kinematics. In each gear of a two-land four-shaft transmission, two of the transmission shifting elements connected to elements of the two-land four-shaft transmission must be closed. For the graphical representation of the kinematics of the transmission usually a speed plan of the transmission is used, for example, the well-known from the Gauge Kutzbach plan. Known embodiments of such a two-bridge four-shaft transmission are the so-called Ravigneaux wheelset and the so-called Simpson wheelset.

A reduced two-bridge four-shaft transmission is a design of a two-bridge four-shaft transmission, in which an element - ie a sun gear, a bridge or a ring gear - of the transmission is saved, as another element of the Getriebes whose task is done without the kinematics thereby to change. The element which takes over the function of the saved element is thus at the same time one of the coupling shafts of the transmission. A known embodiment of this is the Ravigneaux wheelset, which has either two sun gears and only one ring gear or two ring gears and only one sun gear.

The transmission input shaft is connectable via at least one switching element with at least one of the four shafts of the main gearset. In a preferred embodiment, the transmission input shaft via two switching elements with two of the four shafts of the main gear is connectable. By closing one of the switching elements thus a rotationally fixed connection between the transmission input shaft and one of the four shafts of the main gear is made, whereby torque from the transmission input shaft to the main gear is feasible. The third wave of the main gearset is connected to the transmission output shaft.

According to the second shaft of the Zusatzradsatzes with the first wave of the main gearset is constantly connected. The third wave of Zusatzradsatzes is constantly connected to the second, third or fourth shaft of the main gearset.

When used in a motor vehicle, the transmission input shaft is connected to a shaft of a drive unit or connectable via a coupling, so that mechanical power of the drive unit of the transmission input shaft can be fed. The drive unit can be designed both as an internal combustion engine and as an electrical machine. The transmission output shaft serves as an interface for transmitting mechanical power to the drive wheels of the motor vehicle.

A shaft is not to be understood below exclusively as an example cylindrical, rotatably mounted machine element for transmitting torque, but these are also general fasteners to understand that connect individual components or elements together, in particular connecting elements that connect a plurality of elements rotatably together.

A planetary gear set includes a sun gear, a land and a ring gear. Rotatably mounted on the web are planet gears, which mesh with the toothing of the sun gear and / or with the toothing of the ring gear. In the following, a negative gearset describes a planetary gear set with a web on which the planetary gears are rotatably mounted, with a sun gear and with a ring gear, wherein the toothing meshes with at least one of the planet gears both with the toothing of the sun gear and with the toothing of the ring gear whereby the ring gear and the sun gear rotate in opposite directions of rotation when the sun gear rotates at a stationary web.

Both sun gear and ring gear of a planetary gear set can also be divided into several segments. For example, it is conceivable that the planet gears mesh with two sun gears, which are not connected to each other. The speed ratios are of course identical on both segments of the sun gear, as if they were connected together.

A plus gear set differs from the negative planetary gear set just described in that the plus gear set has inner and outer planet gears rotatably supported on the land. The toothing of the inner planet gears meshes on the one hand with the teeth of the sun gear and on the other hand with the teeth of the outer planetary gears. The toothing of the outer planetary gears also meshes with the teeth of the ring gear.

This has the consequence that rotate at a fixed land, the ring gear and the sun gear in the same direction.

The stationary gear ratio defines the speed ratio between the sun gear and ring gear of a planetary gear set with non-rotatable web. Since the direction of rotation between the sun gear and the ring gear is reversed in the case of a negative gearset with a non-rotatable web, the stationary gear ratio always assumes a negative value for a negative gearset.

The speed diagram shows the speed ratios of the individual shafts in the vertical direction. The horizontal distances between the waves result from the ratios between the waves, so that can be connected to a specific operating point speed ratios and torque ratios of the waves by a straight line. The transmission ratios between the shafts result from the stationary gear ratios of the planetary gear sets involved. The speed plan can be displayed, for example, in the form of a Kutzbach plan.

Four waves referred to as the first, second, third and fourth wave in the order of rotation are characterized in that the rotational speeds of these waves increase, decrease or become linear in the stated order. In other words, the rotational speed of the first shaft is less than or equal to the rotational speed of the second shaft. The speed of the second shaft is again less than or equal to the speed of the third shaft. The speed of the third shaft is less than or equal to the speed of the fourth shaft. These Order is also reversible, so that the fourth shaft has the highest speed, while the first shaft assumes a speed which is less than or equal to the speed of the fourth shaft. There is always a linear relationship between the speeds of all four shafts.

The speed of one or more waves can also assume negative values, or even the value zero. The speed order is therefore always to refer to the signed value of the speeds, and not on the amount.

The speeds of the four shafts are then the same if two of these elements are connected to each other by the elements ring gear, web and sun of one of the planetary gear sets.

An electric machine consists at least of a non-rotatable stator and a rotatably mounted rotor and is configured in a motor operation to convert electrical energy into mechanical energy in the form of speed and torque, and in a regenerative operation mechanical energy into electrical energy in the form of To transform electricity and voltage.

By switching elements, depending on the operating state, a relative movement between two components allowed or made a connection for transmitting a torque between the two components. Under a relative movement, for example, to understand a rotation of two components, wherein the rotational speed of the first component and the rotational speed of the second component differ from each other. In addition, the rotation of only one of the two components is conceivable while the other component is stationary or rotating in the opposite direction. The switching elements are preferably designed in the present invention as claw-switching elements, which produce the connection by positive locking.

Two elements are referred to as being connected to one another, in particular, if a solid, in particular non-rotatable connection exists between the elements. Such connected elements rotate at the same speed. The various components and elements of said invention can be connected to one another via a shaft or via a closed switching element or a connecting element, but also directly, for example by means of a welding, pressing or other connection.

Two elements are hereinafter referred to as connectable if there is a releasable rotationally fixed connection between these elements. If the connection is made, such elements rotate at the same speed.

A switching operation is effected by closing a previously not lying in the power flow of the transmission switching element of the transmission and opening a previously lying in the power flow of the transmission switching element of the transmission. The shift operation can also be performed under load, that is to say without complete withdrawal of the torque at the transmission input shaft and the transmission output shaft. Such a switching operation is referred to below as a load circuit. A prerequisite for the load circuit in the use of jaw switching elements is that the switching element to be dissolved is guided before releasing in an at least almost no-load condition. The leadership in the virtually no-load condition is achieved in that the switching element is provided largely free of torque, so that no or only a small torque is transmitted via the switching element. For this purpose, a torque is applied by the electric machine to that shaft, with which the switching element to be released establishes a connection.

The inventive connection of the rotor to the main gear is achieved that the translation is increased from the rotor to the waves of the main gear. In other words, the first wave of the main gearset is always due to the connection according to the invention in the speed plan between the first shaft of Zusatzradsatzes and the second shaft of the main gearset. This enlarged ratio reduces the torque to be applied by the rotor during the switching operation, as a result of which the electric machine can be made smaller and lighter. In this way, the reduced electric machine can apply the required torque to the transmission input shaft even at a high torque at a load circuit, without resulting in an undesirably high torque reduction at the transmission output shaft. The enlarged ratio is also useful when the torque of the electric machine to be transmitted to the transmission output shaft, for example, when using the transmission in a motor vehicle, whereby an electric driving operation of the motor vehicle is made possible. By so magnified translation starting up of the motor vehicle in a slope even with miniaturized electrical machine is possible. The increased ratio is additionally useful when transmitting torque from the electric machine to the transmission input shaft, for example when used to start an internal combustion engine connected to the transmission input shaft. Again, the enlarged translation causes the electrical machine can be smaller and thus easier to build.

Due to the inventive assignment of the waves of the main gearset to the second and third shaft of the Zusatzradsatzes is also achieved that the rotor is even at rotationally fixed fixing the first shaft of the main gearset to be able to assume a speed. This is a prerequisite for receiving and delivering mechanical power by the electric machine. This makes it possible for the electric machine to be able to absorb or dispense mechanical power even in those gears in which the first shaft of the main gearset is fixed in a rotationally fixed manner or has no appreciable rotational speed. This is particularly advantageous when using the transmission in a motor vehicle, since kinetic energy of the motor vehicle can be recuperated by the regenerative operation of the electric machine in each gear of the transmission. If an internal combustion engine is connected to the transmission input shaft, then the load point of the internal combustion engine can also be shifted by regenerative or motorized operation of the electric machine in each gear. The transmission thus enables an increase in efficiency of the motor vehicle.

Preferably, a sun gear of the planetary gear set of Zusatzradsatzes is a part of the first wave of the Zusatzradsatzes. In the case that the planetary gearset of Zusatzradsatzes is designed as minus wheelset, a bridge of the planetary gear set of Zusatzradsatzes is a part of the second shaft of the Zusatzradsatzes, and a ring gear of the planetary gear set of Zusatzradsatzes a part of the third wave of the Zusatzradsatzes. If the planetary gear set of Zusatzradsatzes designed as a plus-wheel, the assignment of ring gear and land is reversed, so that the ring gear of the planetary gearset Zusatzradsatzes is a part of the second shaft of the Zusatzradsatzes and the bridge of the planetary gear set of Zusatzradsatzes a part of the third wave of Zusatzradsatzes is.

The assignment of the Planetenradsatzes Zusatzradsatzes to Hauptradsatz but can also be mirrored by the sun gear of the planetary gear set of Zusatzradsatzes is a part of the third wave of the Zusatzradsatzes. If the planetary gear set of the additional gear set is designed as a minus wheel set, the web of the planetary gear set of the additional gear set is part of the second shaft of the Zusatzradsatzes, and the ring gear of the planetary gear set of Zusatzradsatzes is part of the first wave of the Zusatzradsatzes. If the planetary gearset of Zusatzradsatzes designed as a plus-wheel, the assignment of ring gear and land is reversed, so that the ring gear of the planetary gearset Zusatzradsatzes is a part of the second shaft of the Zusatzradsatzes and the bridge of the planetary gear set of Zusatzradsatzes a part of the first wave of the Zusatzradsatzes is.

Due to the large number of offered possibilities of connection between rotor, additional gear and main gear, the invention is particularly easy to adapt to different transmission variants and available space conditions.

The order of the four shafts of the main gearset in the speed diagram is dependent on the manner which waves are assigned to which elements of the first and second planetary gearset of the main gearset, and which of the four shafts are interconnected. Examples are known in the prior art, but certain variants have been found to be particularly advantageous for the implementation in a transmission. These are particularly advantageous because of a geometrically favorable arrangement, because of a reduced component load and because of improved accessibility to switching elements.

According to a first embodiment of the transmission, the transmission input shaft via a first switching element with the fourth shaft of the main gearset and a second switching element with the second shaft of the main gearset is connectable. The first shaft of the main gearset is rotatably fixed via a third switching element. The second shaft of the main gearset is rotatably fixed via a fourth switching element. By the third and fourth switching element therefore a firm connection with a transmission housing of the transmission or with another rotatably fixed component of the transmission can be produced.

By the first embodiment, a total of four powershift gears between the transmission input shaft and the transmission output shaft are formed. A first forward speed between the transmission input shaft and the transmission output shaft is obtained by closing the first shift element and the fourth shift element, a second forward speed by closing the first shift element and the third shift element, a third forward speed by closing the first shift element and the second shift element , and a fourth forward speed by closing the third switching element and the second switching element.

By assigning the switching elements according to the first embodiment is achieved in conjunction with the assignment of the rotor to the first shaft of Zusatzradsatzes and the assignment of the second and third shaft of the Zusatzradsatzes to the shafts of the main gear that the rotor always has a speed less than zero, provided the transmission output shaft has a speed greater than zero having. In a gear change between the forward gears, therefore, there is no dynamic speed zero crossing of the rotor. Since electrical machines are usually controlled or regulated by the rotor speed, a zero crossing of the speed at a dynamic change of direction represents a significant overhead in its control, or regulation. This extra effort can thus be easily avoided.

The second and fourth switching element is preferably actuated by a double-acting actuator according to the first embodiment, while the first and third switching element is preferably actuated by two single-acting actuators.

According to a second embodiment of the transmission, the transmission input shaft via the first switching element with the first shaft of the main gearset and via the second switching element with the second shaft of the main gearset is connectable. The first wave of the main gearset can be fixed in terms of rotation via the third switching element. The fourth wave can be fixed in terms of rotation via the fourth switching element.

The second embodiment also forms a total of four powershift gears between the transmission input shaft and the transmission output shaft. A first forward speed between the transmission input shaft and the transmission output shaft is obtained by closing the fourth shift element and the first shift element, a second forward speed by closing the fourth shift element and the second shift element, a third forward speed by closing the second shift element and the first shift element , and a fourth forward speed by closing the second switching element and the third switching element.

By assigning the switching elements according to the second embodiment is achieved in conjunction with the assignment of the rotor to the first shaft of Zusatzradsatzes and the assignment of the second and third shaft of the Zusatzradsatzes to the waves of the main gear that the rotor in the forward gears outside the circuits a speed which is clearly outside the zero speed. This ensures that the electric machine can pick up or output power from the transmission output shaft in each forward gear.

The transmission may preferably be part of a hybrid drive train of a motor vehicle. The hybrid powertrain also has an internal combustion engine in addition to the transmission. The internal combustion engine is either directly or via a clutch connected to the transmission input shaft of the transmission, or connectable. The motor vehicle can be driven both by the internal combustion engine and by the electric machine of the transmission. Optionally, the transmission to an additional electric machine, which is adapted to deliver on its rotor torque on the transmission input shaft and to start the internal combustion engine. This has the advantage that the internal combustion engine can be started by means of the additional electric machine, without having to influence a simultaneous electric driving operation, in which the motor vehicle is driven solely by the electric machine of the transmission.

The electric machine is connected to a converter, via which the electric machine is connected to an energy store. For this purpose, any form of energy storage is suitable, in particular electrochemical, electrostatic, hydraulic and mechanical energy storage.

In a further embodiment, the transmission may also be part of a drive train of an electric vehicle. An electric vehicle is driven solely by one or more electric machines, and accordingly has no internal combustion engine. At the transmission input shaft in this case, a traction electric machine is connected. Due to the different gear ratios of the transmission, the traction electric machine can always be operated in an operating range with high efficiency, whereby the energy efficiency of the entire electric vehicle is improved.

• 1 zeigt schematisch ein Getriebe entsprechend einer ersten Ausführungsform der Erfindung.
• 2 zeigt einen Drehzahlplan des Getriebes entsprechend der ersten Ausführungsform.
• 3 zeigt ein Schaltschema des Getriebes entsprechend der ersten Ausführungsform.
• 4 zeigt schematisch ein Getriebe entsprechend einer ersten Variante der ersten Ausführungsform der Erfindung.
• 5 zeigt schematisch ein Getriebe entsprechend einer zweiten Variante der ersten Ausführungsform der Erfindung.
• 6 zeigt schematisch ein Getriebe entsprechend einer dritten Variante der ersten Ausführungsform der Erfindung.
• 7 zeigt schematisch ein Getriebe entsprechend einer zweiten Ausführungsform der Erfindung.
• 8 zeigt einen Drehzahlplan des Getriebes entsprechend der zweiten Ausführungsform.
• 9 zeigt ein Schaltschema des Getriebes entsprechend der zweiten Ausführungsform.
• 10 zeigt schematisch ein Getriebe entsprechend einer ersten Variante der zweiten Ausführungsform der Erfindung.
• 11 zeigt schematisch ein Getriebe entsprechend einer zweiten Variante der zweiten Ausführungsform der Erfindung.
• 12 zeigt schematisch ein Getriebe entsprechend einer dritten Variante der zweiten Ausführungsform der Erfindung.
• 13 zeigt einen Hybridantriebstrang eines Kraftfahrzeugs.

Embodiments of the invention are described in detail below with reference to the accompanying figures.

• 1 schematically shows a transmission according to a first embodiment of the invention.
• 2 shows a speed diagram of the transmission according to the first embodiment.
• 3 shows a circuit diagram of the transmission according to the first embodiment.
• 4 schematically shows a transmission according to a first variant of the first embodiment of the invention.
• 5 schematically shows a transmission according to a second variant of the first embodiment of the invention.
• 6 schematically shows a transmission according to a third variant of the first embodiment of the invention.
• 7 schematically shows a transmission according to a second embodiment of the invention.
• 8th shows a speed diagram of the transmission according to the second embodiment.
• 9 shows a circuit diagram of the transmission according to the second embodiment.
• 10 schematically shows a transmission according to a first variant of the second embodiment of the invention.
• 11 schematically shows a transmission according to a second variant of the second embodiment of the invention.
• 12 schematically shows a transmission according to a third variant of the second embodiment of the invention.
• 13 shows a hybrid powertrain of a motor vehicle.

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.

1 schematically shows a transmission G according to a first embodiment of the invention. The gear G has a Zusatzradsatz ZRS and a main gearset HRS on. The additional wheel set ZRS has a planetary gear set P4 on while the main gearset HRS a first planetary gear set P1 and a second planetary gear set P2 having. All planetary gear sets P1 . P2 . P4 are designed as minus wheelsets.

The representation of the transmission G essentially shows the connectable and connected elements of the transmission G , By in the representation of the transmission G selected distances can not be deduced on the gear ratios.

A first wave W1 of the main gearset HRS is with a sun wheel So-P1 of the first planetary gear set P1 of the main gearset HRS connected. A second wave W2 of the main gearset HRS is with a jetty St-P1 of the first planetary gear set P1 and with a ring gear Ho-P2 of the second planetary gear set P2 of the main gearset HRS connected. A third wave W3 of the main gearset HRS is with a ring gear Ho-P1 of the first planetary gear set P1 and with a jetty St-P2 of the second planetary gear set P2 of the main gearset HRS connected. A fourth wave W4 of the main gearset HRS is with a sun wheel So-P2 of the second planetary gear set P2 of the main gearset HRS connected. By this arrangement and connection between the individual components of the first and second planetary gear set P1 . P2 of the main gearset HRS becomes the arrangement of the first, second, third and fourth wave W1 . W2 . W3 . W4 of the main gearset HRS determined in the speed plan, the order of first, second, third, fourth wave W1 . W2 . W3 . W4 whose sequence corresponds to the speed plan. The third wave W3 of the main gearset HRS is with the transmission output shaft GW2 connected. Alternatively, the third wave W3 of the main gearset HRS also via an additional transmission gearbox with the transmission output shaft GW2 be connected.

The transmission input shaft LV1 is via a first switching element A with the fourth wave W4 of the main gearset HRS and a second switching element e with the second wave W2 of the main gearset HRS connectable. The first wave W1 of the main gearset HRS is via a third switching element C fixable rotatably. The second wave W2 of the main gearset HRS is over a fourth switching element D fixable rotatably. By the third and fourth switching element C . D is therefore a firm connection with a transmission housing GG of the transmission G or with another rotatably fixed component of the transmission G produced.

The gear G has an electric machine EM on, being a stator S rotatably with the gear housing GG of the transmission G or with another non-rotatable component of the transmission G connected so that the stator S can not accept any speed. A rotatably mounted rotor R is with a sun wheel So-P4 of the planetary gear set P4 of additional wheel set ZRS connected. The sun wheel So-P4 of the planetary gear set P4 of additional wheel set ZRS is part of a first wave W1P4 of additional wheel set ZRS , A jetty St-P4 of the planetary gear set P4 of additional wheel set ZRS is part of a second wave W2P4 of additional wheel set ZRS and is with the first wave W1 of the main gearset HRS connected. A ring gear Ho-P4 of the planetary gear set P4 of additional wheel set ZRS is part of a third wave W3P4 of additional wheel set ZRS and is with the second wave W2 of the main gearset HRS connected.

2 shows a speed diagram of the first embodiment of the transmission G while in 3 a circuit diagram of the first embodiment of the transmission G is shown. In 2 are the vertical speeds of the four waves W1 . W2 . W3 . W4 of the main gearset HRS and the rotor R in proportion to the speed of the transmission input shaft LV1 applied. The maximum occurring speed of the transmission input shaft LV1 is normalized to the value one. The distances between the four waves W1 . W2 . W3 . W4 of the main gearset HRS and the rotor R result from the stationary gear ratios of the first and second planetary gear sets P1 . P2 of the main gearset HRS and the stationary gear ratio of the planetary gear set P4 of additional wheel set ZRS , Speed ratios associated with a particular operating point can be connected by a straight line.

If two of these elements are connected to each other by ring gear, land and sun of a planetary gear set, the ring gear, land and sun of this planetary gear set rotate at the same speed. In this state, the translation between the named elements assumes the value one. For the sake of clarity, the horizontal arrangement of the waves connected to these elements is not shifted in the speed plan. As a result, this condition can be recognized in the speed diagram by a horizontal straight line connecting the shafts involved.

3 shows a circuit diagram of the transmission G according to the first embodiment. Through the wiring diagram in 3 and the speed plan in 2 will the operation of the first embodiment of the transmission G clear. The closed switching elements A . C . D . e are in 3 indicated by circles. The shift pattern, the respective translations of the individual gear ratios and the gear ratios to be determined from the next higher gear can be exemplified, the transmission G such a spread of 9 6 having. The translations result from the stationary gear ratios of the planetary gear sets P1 . P2 . P4 , With sequential switching mode, double circuits or group circuits can be avoided since two adjacent gear stages share a switching element. The gears of the transmission G are shown in the different lines of the wiring diagram. In a column of the wiring diagram is further specified whether the electric machine EM in the gear in question is capable of mechanical power to the transmission output shaft GW2 to give or receive from this.

By the first embodiment, a total of four powershift gears between the transmission input shaft LV1 and the transmission output shaft GW2 educated. A first forward speed 1VM between the transmission input shaft LV1 and the transmission output shaft GW2 results from closing the first switching element A and the fourth switching element D , a second forward gear 2VM by closing the first switching element A and the third switching element C , a third forward speed 3VM by closing the first switching element A and the second switching element e , and a fourth forward gear 4VM by closing the third switching element C and the second switching element e ,

In an electric gear 1EM will torque alone from the electric machine EM to the transmission output shaft GW2 transferred, with all switching elements except for the fourth switching element D are open, and thus no torque-conducting connection between the transmission input shaft LV1 and the transmission output shaft GW2 consists. The electric gear 1EM also serves as a reverse gear in which the electric machine EM is controlled so that the rotor R a negative speed, so a reverse rotation assumes. On a separate reverse gear can thus be dispensed with.

In the first and second start mode 1S . 2S becomes the transmission input shaft LV1 Torque supplied. In the first startup mode 1S is the first switching element A and the fourth switching element D closed, causing the second wave W2 of the main gearset HRS is fixed rotationally fixed. Is in the first startup mode 1S Torque at the transmission output shaft GW2 on, so is power from the transmission output shaft GW2 to the transmission input shaft LV1 transferable. The electric machine EM can also give performance. When using the gearbox G in a vehicle with internal combustion engine VKM can be the first startup mode 1S Towing the internal combustion engine VKM to be used. In the second start mode 2S are all switching elements except for the first switching element A open. Is a parking brake engaged, which with the transmission output shaft GW2 connected, so is the third wave W3 of the main gearset HRS thus fixed rotationally fixed. By the electric machine EM can thus power from the first wave W1P4 of additional wheel set ZRS on the transmission input shaft LV1 be transferred to such a at the transmission input shaft LV1 Tailored internal combustion engine VKM to start.

By closing the third switching element C and the fourth switching element D becomes the first and the second wave W1 . W2 of the main gearset HRS fixed rotationally fixed. The gear G is blocked. When using the gearbox G In the drive train of a motor vehicle such a parking brake can be realized.

4 schematically shows a transmission G according to a first variant of the first embodiment of the invention. Unlike the in 1 illustrated gear G is the third wave W3P4 of additional wheel set ZRS instead of the second wave W2 of the main gearset HRS now with the third wave W3 of the main gearset HRS connected.

5 schematically shows a transmission G according to a second variant of the first embodiment of the invention. This is the first planetary gear set P1 of the main gearset HRS as a minus wheel set and the second planetary gear set P2 of the main gearset HRS designed as Plus wheelset. The first wave W1 of the main gearset HRS is with the sun wheel So-P1 of the first planetary gear set P1 of the main gearset HRS connected. The second wave W2 of the main gearset HRS is with the jetty St-P1 of the first planetary gear set P1 and with the jetty St-P2 of the second planetary gear set P2 of the main gearset HRS connected. The third wave W3 of the main gearset HRS is with the ring gear Ho-P1 of the first planetary gear set P1 and with the ring gear Ho-P2 of the second planetary gear set P2 of the main gearset HRS connected. The fourth wave W4 of the main gearset HRS is with the sun wheel So-P2 of the second planetary gear set P2 of the main gearset HRS connected. The third wave W3 is with the transmission output shaft GW2 connected. The ring gear Ho-P4 of the planetary gear set P4 the Zusatzradsatzes is part of the first wave W1P4 of additional wheel set ZRS , and is so with the rotor R the electric machine EM connected. The jetty St-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the second wave W2P4 of additional wheel set ZRS and is with the first wave W1 of the main gearset HRS connected. The sun wheel So-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the third wave W3P4 of additional wheel set ZRS and is with the fourth wave W4 of the main gearset HRS connected. This in 5 illustrated variant of the transmission G is particularly suitable for use in a motor vehicle with transverse to the direction arranged drive train.

6 schematically shows a transmission G according to a third variant of the first embodiment of the invention. Therein are the first and second planetary gear set P1 . P2 of the main gearset HRS designed as a minus wheel set. The first wave W1 of the main gearset HRS is with the sun wheel So-P1 of the first planetary gear set P1 of the main gearset HRS and with the sun wheel So-P2 of the second planetary gear set P2 of the main gearset HRS connected. The second wave W2 of the main gearset HRS is with the jetty St-P2 of the second planetary gear set P2 of the main gearset HRS connected. The third wave W3 of the main gearset HRS is with the jetty St-P1 of the first planetary gear set P1 of the main gearset HRS and with the ring gear Ho-P2 of the second planetary gear set P2 of the main gearset HRS connected. The fourth wave W4 of the main gearset HRS is with the ring gear Ho-P1 of the first planetary gear set P1 of the main gearset HRS connected. The sun wheel So-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the first wave W1P4 of additional wheel set ZRS and is with the rotor R connected. The jetty St-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the second wave W2P4 of additional wheel set ZRS and is with the first wave W1 of the main gearset HRS connected. The ring gear Ho-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the third wave W3P4 of additional wheel set ZRS and is with the second wave W2 of the main gearset HRS connected.

The speed plan in 2 and the schematic in 3 apply equally to all variants of the first embodiment of the invention. The stationary gear ratios of the planetary gear sets involved must be adjusted accordingly.

7 schematically shows a transmission G according to a second embodiment of the invention. Unlike the first embodiment, in the second embodiment, the transmission input shaft LV1 over the first switching element A with the first wave W1 of the main gearset HRS connectable. About the second switching element e is the transmission input shaft LV1 as well as in the first embodiment with the second shaft W2 of the main gearset HRS connectable. The first wave W1 of the main gearset HRS is as in the first embodiment via the third switching element C fixable rotatably. About the fourth switching element D is the fourth wave in the second embodiment W4 of the main gearset HRS fixable rotatably.

The sun wheel So-P1 of the first planetary gear set P1 of the main gearset HRS is part of the fourth wave W4 of the main gearset HRS , The jetty St-P1 of the first planetary gear set P1 of the main gearset HRS and the ring gear Ho-P2 of the second planetary gear set P2 of the main gearset HRS are components of the third wave W3 of the main gearset HRS , The third wave W3 of the main gearset HRS is with the transmission output shaft GW2 connected. The ring gear Ho-P1 of the first planetary gear set P1 of the main gearset HRS and the jetty St-P2 of the second planetary gear set P2 of the main gearset HRS are components of the second wave W2 of the main gearset HRS , The sun wheel So-P2 of the second planetary gear set P2 of the main gearset HRS is part of the first wave W1 of the main gearset HRS , The ring gear Ho-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the first wave W1 P4 of additional wheel set ZRS and is with the rotor R connected. The jetty St-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the second wave W2P4 of additional wheel set ZRS and is with the first wave W1 of the main gearset HRS connected. The sun wheel So-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the third wave W3P4 of additional wheel set ZRS and is with the second wave W2 of the main gearset HRS connected.

8th shows a speed plan of the transmission G according to the second embodiment, while in 9 a circuit diagram of the second embodiment of the transmission G is shown. The manner of representation is identical to the representation of the first embodiment in FIG 2 and 3 ,

Through the wiring diagram in 9 and the speed plan in 8th will the operation of the second embodiment of the transmission G clear. The closed switching elements A . C . D . e are in 9 indicated by circles. The shift pattern, the respective translations of the individual gear ratios and the gear ratios to be determined from the next higher gear can be exemplified, the transmission G so has a spread of 5.8. The translations result from the stationary gear ratios of the planetary gear sets P1 . P2 . P4 , With sequential switching mode, double circuits or group circuits can be avoided since two adjacent gear stages share a switching element. The gears of the transmission G are shown in the different lines of the wiring diagram. In a column of the wiring diagram is further specified whether the electric machine EM in the gear in question is capable of mechanical power to the transmission output shaft GW2 to give or receive from this.

Also in the second embodiment of the transmission a total of four powershift gears between the transmission input shaft LV1 and the transmission output shaft GW2 educated. The first forward gear 1VM between the transmission input shaft LV1 and the transmission output shaft GW2 results from closing the fourth switching element D and the first switching element A , the second forward gear 2VM by closing the fourth switching element D and the second switching element e , the third forward gear 3VM by closing the second switching element e and the first switching element A , and the fourth forward gear 4VM by closing the third switching element C and the second switching element e ,

In the electric gear 1 EM will torque alone from the electric machine EM to the transmission output shaft GW2 transferred, with all switching elements except for the fourth switching element D are open and thus no torque-conducting connection between the transmission input shaft LV1 and the transmission output shaft GW2 consists. The electric gear 1 EM also serves as a reverse gear in which the electric machine EM is controlled so that the rotor R a negative speed, so a reverse rotation assumes. On a separate reverse gear can thus be dispensed with.

In the first and second start mode 1S . 2S becomes the transmission input shaft LV1 Torque supplied. In the first startup mode 1S is the fourth switching element D and the first switching element A closed, causing the fourth wave W4 of the main gearset HRS is fixed rotationally fixed. Is in the first startup mode 1S Torque at the transmission output shaft GW2 on, so is power from the transmission output shaft GW2 to the transmission input shaft LV1 transferable. The electric machine EM can also give performance. When using the gearbox G in a vehicle with internal combustion engine VKM can be the first startup mode 1S Towing the internal combustion engine VKM to be used. In the second start mode 2S are all switching elements except for the first switching element A open. Is a parking brake engaged, which with the transmission output shaft GW2 connected, so is the third wave W3 of the main gearset HRS thus fixed rotationally fixed. By the electric machine EM can thus power from the first wave W1P4 of additional wheel set ZRS on the transmission input shaft LV1 be transferred to such a at the transmission input shaft LV1 Tailored internal combustion engine VKM to start.

By closing the third switching element C and the fourth switching element D becomes the first and the fourth wave W1 . W4 of the main gearset HRS fixed rotationally fixed. The gear G is blocked. When using the gearbox G In the drive train of a motor vehicle such a parking brake can be realized.

10 schematically shows a transmission G according to a first variant of the second embodiment of the invention. Unlike the in 8th illustrated gear G is the third wave W3P4 of additional wheel set ZRS instead of the second wave W2 of the main gearset HRS now with the third wave W3 of the main gearset HRS connected.

11 schematically shows a transmission G according to a second variant of the second embodiment of the invention. This is the first planetary gear set P1 of the main gearset HRS as plus wheelset and the second planetary gear set P2 of the main gearset HRS designed as a minus wheel set. The sun wheel So-P1 of the first planetary gear set P1 of the main gearset HRS is part of the fourth wave W4 of the main gearset HRS , The jetty St-P1 of the first planetary gear set P1 of gearset HRS and the jetty St-P2 of the second planetary gear set P2 of the main gearset HRS are components of the second wave W2 of the main gearset HRS , The ring gear Ho-P1 of the first planetary gear set P1 of the main gearset HRS and the ring gear Ho-P2 of the second planetary gear set P2 of the main gearset HRS are components of the third wave W3 of the main gearset HRS , The sun wheel So-P2 of the second planetary gear set P2 of the main gearset HRS is part of the first wave W1 of the main gearset HRS , The ring gear Ho-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the first wave W1P4 of additional wheel set ZRS and is with the rotor R connected. The jetty St-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the second wave W2P4 of additional wheel set ZRS and is with the first wave W1 of the main gearset HRS connected. The sun wheel So-P4 of the planetary gear set P4 of additional wheel set ZRS is part of the third wave W3P4 of additional wheel set ZRS and is with the fourth wave W4 of the main gearset HRS connected.

12 schematically shows a transmission G according to a third variant of the second embodiment of the invention, wherein the structure of the main gearset HRS and the Zusatzradsatzes ZRS the embodiment in 6 correspond.

The speed plan in 8th and the schematic in 9 apply equally to all variants of the second embodiment of the invention. The stationary gear ratios of the planetary gear sets involved must be adjusted accordingly.

13 schematically shows a hybrid powertrain of a motor vehicle. The transmission contained therein G corresponds to the first embodiment of the transmission G although this is to be considered as an example only. A rotatable rotor R2 an additional electric machine SG is with the transmission input shaft LV1 connected while the stator S2 the auxiliary electric machine SG non-rotatably on the gearbox GG of the gearbox G or at another non-rotatable component of the transmission G is connected. About a rotational vibration damper RD is an internal combustion engine VKM with the transmission input shaft LV1 connected. The transmission output shaft GW2 is with a axle drive AG connected. From the axle drive AG starting from the torque that is applied to the transmission output shaft GW2 rests on wheels W of the motor vehicle distributed. In motor operation of the electric machine EM becomes the stator S via an inverter INV electrical power supplied. In generator operation of the electric machine EM leads the stator S the inverter INV electric power too. The inverter INV converts the DC voltage of a battery BAT in one for the electric machine EM suitable alternating voltage, and vice versa. The additional electric machine SG can also do this via the inverter INV be supplied with electrical power. Alternatively, the additional electric machine SG be connected to another power supply, for example, to a low-voltage electrical system of the motor vehicle.

LIST OF REFERENCE NUMBERS

G

transmission

LV1

Transmission input shaft

GW2

Transmission output shaft

HRS

main gear

ZRS

Zusatzradsatz

EM

Electric machine

R

Rotor of the electric machine

S

Stator of the electric machine

SG

Additional electric machine

R2

Rotor of auxiliary electric machine

S2

Stator of auxiliary electric machine

RD

rotational vibration

VKM

Internal combustion engine

INV

inverter

BAT

battery

P1

First planetary gear set of the main gearset

P2

Second planetary gear set of the main gearset

P4

Planetary wheel set of additional wheelset

W1

First wave of the main gearset

W2

Second wave of the main gearset

W3

Third wave of the main gearset

W4

Fourth wave of the main gearset

W1P4

First wave of additional wheel set

W2P4

Second wave of Zusatzradsatzes

W3P4

Third wave of Zusatzradsatzes

A

First switching element

e

Second switching element

C

Third switching element

D

Fourth switching element

So-P1

Sun gear of the first planetary gear set of the main gearset

St-P1

Bridge of the first planetary gear set of the main gearset

Ho-P1

Ring gear of the first planetary gear set of the main gearset

So-P2

Sun gear of the second planetary gear set of the main gearset

St-P2

Bridge of the second planetary gear set of the main gearset

Ho-P2

Ring gear of the second planetary gear set of the main gearset

So-P4

Sun gear of the planetary gear set of additional wheelset

St-P4

Bridge of the planetary gear set of Zusatzradsatzes

Ho-P4

Ring gear of the planetary gear set of Zusatzradsatzes

1VM-4VM

First to fourth forward

1 EM

Electric gear

1S

First startup mode

2S

Second start mode

AG

transaxles

W

wheel

Claims (14)

Transmission (G) for a motor vehicle with a transmission input shaft (GW1) and a transmission output shaft (GW2), a main gearset (HRS), a Zusatzradsatz (ZRS), and an electric machine (EM) with a rotor (R) and a stator (S), wherein the main gearset (HRS) has a first and a second planetary gear set (P1, P2) with a total of four designated in speed order as the first, second, third and fourth waves (W1, W2, W3, W4), the transmission (G) having first, second, third and fourth shifting elements (A, C, D, E), the third shaft (W3) of the main gearset (HRS) being connected to the transmission output shaft (GW2), the supplementary gear set (ZRS) comprises a planetary gear set (P4) having first, second and third shafts (W1P4, W2P4, W3P4), the first shaft (W1P4) of the supplementary gear set (ZRS) being permanently connected to the rotor (R), the second shaft (W2P4) of the additional gear set (ZRS) with the first shaft (W1) of the main gearset (HRS) s is continuously connected, wherein the third wave (W3P4) of Zusatzradsatzes (ZRS) with the second, third or fourth shaft (W2, W3, W4) of the main gearset (HRS) is constantly connected, characterized in that by closing the second switching element ( E) the transmission input shaft with the second shaft (W2) of the main gearset (HRS) is connectable, wherein by closing the third switching element (C) the first shaft (W1) of the main gearset (HRS) is rotatably fixable, closing the fourth Switching element (D) the second shaft (W2) or the fourth shaft (W4) of the main gearset is rotatably fixable, wherein - in the case that the fourth switching element (D) of the second shaft (W2) of the main gearset (HRS) is assigned by Closing the first shift element (A), the fourth shaft (W4) of the main gearset (HRS) is connectable to the transmission input shaft (GW1), and - in the event that the fourth shift element (D) of the fourth shaft (W4) of the main gearset ( HRS) is net, by closing the first switching element (A), the first shaft (W1) of the main gearset (HRS) with the transmission input shaft (GW1) is connectable. Transmission (G) to Claim 1 , characterized in that a sun gear (So - P4) of the planetary gear set (P4) of Zusatzradsatzes (ZRS) is a component of the first shaft (W1P4) of Zusatzradsatzes (ZRS) is, and - in the case that the planetary gear set (P4) of Zusatzradsatzes (ZRS) is designed as minus wheelset, a web (St-P4) of the Planetenradsatzes (P4) of the Zusatzradsatzes (ZRS) is a component of the second shaft (W2P4) of Zusatzradsatzes (ZRS) and a ring gear (Ho-P4) of the planetary gearset (P4) Zusatzradsatzes (ZRS) is a part of the third wave (W3P4) of the Zusatzradsatzes (ZRS) is, and - in the case that the planetary gear set (P4) of Zusatzradsatzes (ZRS) is designed as a Plus-wheelset, the ring gear (Ho-P4) of the planetary gear set (P4) of Zusatzradsatzes (ZRS) is a part of the second Shaft (W2P4) of Zusatzradsatzes (ZRS) is and the web (St-P4) of the planetary gear set (P4) of Zusatzradsatzes (ZRS) is a component of the third wave (W3P4) of Zusatzradsatzes (ZRS). Transmission (G) to Claim 1 , characterized in that the sun gear (So-P4) of the planetary gear set (P4) of Zusatzradsatzes (ZRS) is a component of the third wave (W3P4) of the Zusatzradsatzes (ZRS), - in the case that the planetary gear set (P4) of the Zusatzradsatzes ( ZRS) is designed as a minus wheel set, the web (St-P4) of the planetary gear set (P4) of Zusatzradsatzes (ZRS) is a component of the second wave (W2P4) of Zusatzradsatzes (ZRS) and the ring gear (Ho-P4) of the planetary gear set (P4) of Zusatzradsatzes (ZRS) is a part of the first shaft (W1P4) of the Zusatzradsatzes (ZRS), and - in the case that the planetary gear set (P4) of the Zusatzradsatzes (ZRS) is designed as a plus gear set, the ring gear (Ho -P4) of the planetary gear set (P4) of Zusatzradsatzes (ZRS) is a component of the second shaft (W2P4) of Zusatzradsatzes (ZRS) and the web (St-P4) of the planetary gear set (P4) of Zusatzradsatzes (ZRS) is a part of the first wave (W1P4) of the Zusatzradsatzes (ZRS) is. Transmission (G) according to one of the preceding claims, characterized in that the first switching element (A) of the fourth wave (W4) of the main gearset (HRS) is assigned, wherein the first and second planetary gear set (P1, P2) of the main gearset (HRS) as Minus wheelsets are formed, wherein a sun gear (So-P1) of the first planetary gear set (P1) of the main gearset (HRS) is part of the first wave (W1) of the main gearset (HRS) and with the second shaft (W2P4) of Zusatzradsatzes (ZRS ), wherein a web (St-P1) of the first planetary gear set (P1) of the main gearset (HRS) and a ring gear (Ho-P2) of the second planetary gear set (P2) of the main gearset (HRS) components of the second wave (W2) of the HRS are and are connected to the third shaft (W3P4) of Zusatzradsatzes (ZRS), wherein a ring gear (Ho-P1) of the first planetary gear set (P1) of the main gearset (HRS) and a web (St-P2) of the second Planetary gear set (P2) of the main gearset (HRS) Components d it is the third wave (W3) of the main gearset (HRS), and wherein a sun gear (So-P2) of the second planetary gear set (P2) of the main gearset (HRS) is part of the fourth wave (W4) of the main gearset (HRS). Transmission (G) according to one of Claims 1 to 3 , characterized in that the first switching element (A) of the fourth wave (W4) of the main gearset (HRS) is assigned, wherein the first and second planetary gear set (P1, P2) of the main gearset (HRS) are designed as minus wheelsets, wherein the sun gear (So-P1) of the first planetary gear set (P1) of the main gearset (HRS) is constituents of the first shaft (W1) of the main gearset (HRS) and is connected to the second shaft (W2P4) of the additional gearset (ZRS), the web (St -P1) of the first planetary gear set (P1) of the main gearset (HRS) and the ring gear (Ho-P2) of the second planetary gear set (P2) of the main gearset (HRS) are components of the second shaft (W2) of the main gearset (HRS), wherein the ring gear (Ho-P1) of the first planetary gear set (P1) of the main gearset (HRS) and the web (St-P2) of the second planetary gear set (P2) of the main gearset (HRS) are components of the third shaft (W3) of the main gearset (HRS) and with the third wave (W3P4) of the Zusatzradsatzes (ZRS) are, and wobe i the sun gear (So-P2) of the second planetary gear set (P2) of the main gearset (HRS) is part of the fourth wave (W4) of the main gearset (HRS). Transmission (G) according to one of Claims 1 to 3 , characterized in that the first switching element (A) of the fourth wave (W4) of the main gearset (HRS) is assigned, wherein the first planetary gear set (P1) of the main gearset (HRS) is designed as minus wheelset and the second planetary gear set (P2) the sun gear (So-P1) of the first planetary gear set (P1) of the main gearset (HRS) is part of the first shaft (W1) of the main gearset (HRS) and with the second shaft (HRS) W2P4) of the Zusatzradsatzes (ZRS) is connected, wherein the web (St-P1) of the first planetary gear set (P1) of the main gearset (HRS) and the web (St-P2) of the second planetary gear set (P2) of the main gearset (HRS) components of second ring (W2) of the main gearset (HRS), the ring gear (Ho-P1) of the first planetary gearset (P1) of the main gearset (HRS) and the ring gear (Ho-P2) of the second planetary gearset (P2) of the main gearset (HRS) Components of the third shaft (W3) of the main gearset (HRS) s ind, and wherein the sun gear (So-P2) of the second planetary gear set (P2) of the main gearset (HRS) is part of the fourth wave (W4) of the main gearset (HRS) and is connected to the third shaft (W3P4) of the Zusatzradsatzes (ZRS) , Transmission (G) according to one of Claims 1 to 3 , characterized in that the first switching element (A) of the fourth wave (W4) of the main gearset (HRS) is assigned, wherein the first and second planetary gear set (P1, P2) of the main gearset (HRS) are designed as minus wheelsets, wherein the sun gear (So-P1) of the first planetary gear set (P1) of the main gearset (HRS) and the sun gear (So-P2) of the second planetary gear set (P2) of the main gearset (HRS) components of the first shaft (W1) of the main gearset (HRS) and with the second shaft (W2P4) of the Zusatzradsatzes (ZRS) are connected, wherein the web (St-P2) of the second planetary gear set (P2) of the main gearset (HRS) is part of the second shaft (W2) of the main gearset (HRS) and with the third shaft (W3P4) of the Zusatzradsatzes (ZRS) is connected, wherein the web (St-P1) of the first planetary gear set (P1) of the main gearset (HRS) and the ring gear (Ho-P2) of the second planetary gear set (P2) of the main gearset (HRS) components the third wave (W3) of the main gearset (HRS) are u nd wherein the ring gear (Ho-P1) of the first planetary gear set (P1) of the main gearset (HRS) is part of the fourth wave (W4) of the main gearset (HRS). Transmission (G) according to one of Claims 1 to 3 , characterized in that the first switching element (A) of the first shaft (W1) of the main gearset (HRS) is assigned, wherein the first and second planetary gear set (P1, P2) of the main gearset (HRS) are designed as minus wheelsets, wherein the sun gear (So-P2) of the second planetary gear set (P2) of the main gearset (HRS) is part of the first shaft (W1) of the main gearset (HRS) and is connected to the second shaft (W2P4) of the Zusatzradsatzes (ZRS), wherein the ring gear (Ho -P1) of the first Planetary gear set (P1) of the main gearset (HRS) and the bridge (St - P2) of the second planetary gearset (P2) of the main gearset (HRS) are components of the second shaft (W2) of the main gearset (HRS) and are connected to the third shaft (W3P4) of the main gearset (HRS) Zusatzradsatzes (ZRS) are connected, wherein the web (St-P1) of the first planetary gear set (P1) of the main gearset (HRS) and the ring gear (Ho-P2) of the second planetary gear set (P2) of the main gearset (HRS) components of the third wave ( W3) of the main gearset (HRS), and wherein the sun gear (So-P1) of the first planetary gear set (P1) of the main gearset (HRS) is part of the fourth wave (W4) of the main gearset (HRS). Transmission (G) according to one of Claims 1 to 3 , characterized in that the first switching element (A) of the first shaft (W1) of the main gearset (HRS) is assigned, wherein the first and second planetary gear set (P1, P2) of the main gearset (HRS) are designed as minus wheelsets, wherein the sun gear (So-P2) of the second planetary gear set (P2) of the main gearset (HRS) is part of the first shaft (W1) of the main gearset (HRS) and is connected to the second shaft (W2P4) of the Zusatzradsatzes (ZRS), wherein the ring gear (Ho -P1) of the first planetary gear set (P1) of the main gearset (HRS) and the web (St-P2) of the second planetary gearset (P2) of the main gearset (HRS) are components of the second shaft (W2) of the main gearset (HRS), wherein the web (St-P1) of the first planetary gear set (P1) of the main gearset (HRS) and the ring gear (Ho-P2) of the second planetary gear set (P2) of the main gearset (HRS) are components of the third wave (W3) of the main gearset (HRS) and with the third shaft (W3P4) of the Zusatzradsatzes (ZRS) are connected, and wherein the sun gear (So-P1) of the first planetary gear set (P1) of the main gearset (HRS) is part of the fourth wave (W4) of the main gearset (HRS). Transmission (G) according to one of Claims 1 to 3 , characterized in that the first switching element (A) of the first shaft (W1) of the main gearset (HRS) is assigned, wherein the first planetary gear set (P1) of the main gearset (HRS) is designed as a plus gear and the second planetary gear set (P2) the sun gear (So-P2) of the second planetary gear set (P2) of the main gearset (HRS) is part of the first shaft (W1) of the main gearset (HRS) and with the second shaft (HRS) W2P4) of the Zusatzradsatzes (ZRS) is connected, wherein the web (St-P1) of the first planetary gear set (P1) of the main gearset (HRS) and the web (St-P2) of the second planetary gear set (P2) of the main gearset (HRS) components of second ring (W2) of the main gearset (HRS), wherein the ring gear (Ho-P1) of the first planetary gearset of the main gearset (HRS) and the ring gear (Ho-P2) of the second planetary gearset (P2) of the main gearset (HRS) components of the third Wave (W3) of the main gearset (HRS) are, and wherein the sun gear (So-P1) of the first planetary gear set (P1) of the main gearset (HRS) is part of the fourth shaft (W4) of the main gearset (HRS) and is connected to the third shaft (W3P4) of the Zusatzradsatzes (ZRS). Transmission (G) according to one of Claims 1 to 3 , characterized in that the first switching element (A) of the first shaft (W1) of the main gearset (HRS) is assigned, the planetary gearset of Zusatzradsatzes (ZRS) and first and second planetary gear set (P1, P2) of the main gearset (HRS) as minus Are constructed, wherein the sun gear (So-P1) of the first planetary gear set (P1) of the main gearset (HRS) and the sun gear (So-P2) of the second planetary gear set (P2) of the main gearset (HRS) components of the first wave (W1) of the main gearset (HRS) and are connected to the second shaft (W2P4) of Zusatzradsatzes (ZRS), wherein the web (St-P2) of the second planetary gear set (P2) of the main gearset (HRS) part of the second shaft (W2) of the main gearset (HRS) and is connected to the third shaft (W3P4) of the Zusatzradsatzes (ZRS), wherein the web (St-P1) of the first planetary gear set (P1) of the main gearset (HRS) and the ring gear (Ho-P2) of the second planetary gear set (P2) of the main gearset (HRS) Components d it is the third wave (W3) of the main gearset (HRS), and wherein the ring gear (Ho-P1) of the first planetary gearset (P1) of the main gearset (HRS) is part of the fourth wave (W4) of the main gearset (HRS). Hybrid powertrain for a motor vehicle, wherein the hybrid powertrain at least one internal combustion engine (VKM), characterized in that the hybrid powertrain a transmission (G) according to one of Claims 1 to 11 having. Hybrid powertrain after Claim 12 , characterized in that the hybrid powertrain comprises at least one additional electric machine (SG) connected to the internal combustion engine (VKM) directly or via a transmission, which is set up to start the internal combustion engine (VKM), wherein a rotor (R2) of the auxiliary engine Electric machine (SG) is connected to the transmission input shaft (GW1) of the transmission (G). Drive train for an electric vehicle, characterized in that the drive train is a transmission (G) according to one of Claims 1 to 11 having.

Images