DE102020203790A1 - Hybrid transmission with pre-transmission for internal combustion engine - Google Patents

Abstract

The present invention relates to a hybrid transmission (18) for a motor vehicle drive train (12) of a motor vehicle (10), having: a transmission input shaft (32) for operative connection of the hybrid transmission to an internal combustion engine (16) of the motor vehicle; a transmission drive shaft (34) which can be connected to the transmission input shaft by means of an input connection in order to establish an internal combustion engine power path in the hybrid transmission; a countershaft (36); idler gears and fixed gears arranged in several gear set levels to form gear stages; a plurality of gear shifting devices with shifting elements (A, B, C, D, E, F) for engaging the gear steps; an output (26) for transmitting drive power from the hybrid transmission, a first gear-forming gear pair and a second gear-forming gear pair being operatively connectable to a first electric drive machine (14) of the motor vehicle in order to set up an electromotive force path in the hybrid transmission; and the input connection comprises a pre-transmission (24) for setting up at least two switchable pre-transmission stages in the internal combustion engine power path. The present invention also relates to a motor vehicle drive train with such a hybrid transmission and a motor vehicle (10) with such a motor vehicle drive train.

Description

The present invention relates to a hybrid transmission, a motor vehicle drive train with such a hybrid transmission and a motor vehicle with such a motor vehicle drive train.

Vehicles are increasingly being equipped with hybrid drives, ie with at least two different drive sources. Hybrid drives can help reduce fuel consumption and pollutant emissions. Drivetrains with an internal combustion engine and one or more electric motors as parallel hybrids or mixed hybrids have largely prevailed. Such hybrid drives have an essentially parallel arrangement of the internal combustion engine and the electric drive in the power flow. Both a superposition of the drive torques and a control with a purely internal combustion engine drive or a purely electric motor drive can be made possible here. Since the drive torques of the electric drive and the internal combustion engine can add up depending on the control, a comparatively smaller design of the internal combustion engine and / or its temporary shutdown is possible. In this way, a significant reduction in CO ₂ emissions can be achieved without any significant loss of performance or comfort. The possibilities and advantages of an electric drive can thus be combined with the range, performance and cost advantages of internal combustion engines.

A disadvantage of the above-mentioned hybrid drives is their generally more complex structure, since both drive sources preferably transmit drive power to a drive shaft with only one gear. As a result, such transmissions are usually complex and costly to produce. A reduction in the complexity in the structure of a hybrid transmission is usually associated with a loss of variability.

This disadvantage can at least partially be overcome by means of dedicated hybrid transmissions or “Dedicated Hybrid Transmissions” (DHT), in which an electric machine is integrated into the transmission in order to display the full range of functions. For example, the mechanical transmission part in particular can be simplified in the transmission, for example by eliminating the reverse gear, with at least one electrical machine being used instead.

Dedicated hybrid transmissions can emerge from known transmission concepts, i.e. from double clutch transmissions, converter planetary transmissions, continuously variable transmissions (CVT) or automated manual transmissions. The electric machine becomes part of the transmission.

The pamphlet DE 10 2012 205 319 A1 discloses a hybrid drive of a motor vehicle which has an internal combustion engine with a drive shaft, an electric machine that can be operated as a motor and generator with a rotor and a multi-stage main transmission with two input shafts and a common output shaft arranged axially parallel to the input shafts. The first input shaft can be connected to the drive shaft of the internal combustion engine via a two-stage series group. The second input shaft is in drive connection with the rotor of the electric machine. Both input shafts are arranged coaxially and axially adjacent to one another and can be connected to one another in a rotationally fixed manner by means of an engaging and disengaging coupling switching element and can be brought into drive connection with the output shaft via at least one switchable spur gear stage. The hybrid drive also has a single spur gear stage with medium gear ratio for the switchable connection of the first input shaft to the output shaft with an arrangement of the idler gear concerned and the associated gear shifting element on the first input shaft. The gear shift element of the spur gear stage of the first input shaft and the coupling shift element are combined in a first double shift element.

Against this background, a person skilled in the art is faced with the task of creating an axially compact, highly efficient and variable hybrid transmission which, in particular, allows the combustion gear steps and electric gear steps to be combined as desired.

• einer Getriebeeingangswelle zum Wirkverbinden des Hybridgetriebes mit einer Verbrennungsmaschine des Kraftfahrzeugs;
• einer Getriebeantriebswelle, die mittels einer Eingangsverbindung mit der Getriebeeingangswelle antriebswirksam verbindbar ist, um einen verbrennungsmotorischen Kraftpfad im Hybridgetriebe einzurichten;
• einer Vorgelegewelle;
• in mehreren Radsatzebenen angeordneten Losrädern und Festrädern zum Bilden von Gangstufen;
• mehreren Gangschaltvorrichtungen mit Schaltelementen zum Einlegen der Gangstufen; und
• einem Abtrieb zum Übertragen von Antriebsleistung aus dem Hybridgetriebe, wobei
• ein erstes gangbildendes Zahnradpaar und ein zweites gangbildendes Zahnradpaar mit einer ersten elektrischen Antriebsmaschine des Kraftfahrzeugs antriebswirksam verbindbar ist, um einen elektromotorischen Kraftpfad im Hybridgetriebe einzurichten; und
• die Eingangsverbindung ein Vorgetriebe umfasst, zum Einrichten von mindestens zwei schaltbaren Vorübersetzungsstufen im verbrennungsmotorischen Kraftpfad.

The above object is achieved by a hybrid transmission for a motor vehicle drive train of a motor vehicle, with:

• a transmission input shaft for operative connection of the hybrid transmission with an internal combustion engine of the motor vehicle;
• a transmission drive shaft, which can be effectively connected to the transmission input shaft by means of an input connection, in order to set up an internal combustion engine power path in the hybrid transmission;
• a countershaft;
• idler gears and fixed gears arranged in several gear set levels to form gear stages;
• a plurality of gear shifting devices with shifting elements for engaging the gear steps; and
• an output for transmitting drive power from the hybrid transmission, wherein
• a first gear-forming gear pair and a second gear-forming gear pair can be connected to a first electric drive machine of the motor vehicle in a driving manner in order to set up an electromotive force path in the hybrid transmission; and
• the input connection comprises a pre-transmission for setting up at least two switchable pre-transmission stages in the internal combustion engine power path.

• einem Hybridgetriebe wie zuvor beschrieben;
• einer Verbrennungsmaschine, die mit der Getriebeantriebswelle verbindbar ist; und
• einer ersten elektrischen Antriebsmaschine, die mit dem ersten gangbildenden Zahnradpaar antriebswirksam verbindbar ist und die mit dem zweiten gangbildenden Zahnradpaar antriebswirksam verbindbar ist.

The above object is also achieved by a motor vehicle drive train for a motor vehicle, with:

• a hybrid transmission as previously described;
• an internal combustion engine which can be connected to the transmission input shaft; and
• a first electric drive machine, which can be connected in a driving manner to the first gear-forming gear pair and which can be connected in a drivingly effective manner to the second gear-forming gear pair.

• einem Kraftfahrzeug-Antriebsstrang wie zuvor beschrieben; und
• einem Energiespeicher zum Speichern von Energie zum Versorgen der ersten elektrischen Antriebsmaschine und vorzugsweise der zweiten elektrischen Antriebsmaschine.

The above task is finally achieved by a motor vehicle with:

• an automotive powertrain as previously described; and
• an energy store for storing energy for supplying the first electric drive machine and preferably the second electric drive machine.

Preferred embodiments of the invention are described in the dependent claims. It goes without saying that the features mentioned above and those yet to be explained below can be used not only in the respectively specified combination, but also in other combinations or on their own, without departing from the scope of the present invention. In particular, the motor vehicle drive train and the motor vehicle can be designed in accordance with the configurations described for the hybrid transmission in the dependent claims.

A group transmission for the internal combustion engine can be created by means of an input connection which includes a pre-transmission for setting up at least two switchable pre-transmissions in the internal combustion engine power path. By setting up an electromotive force path through a first gear-forming gear pair and a second gear-forming gear pair, each of which can be effectively connected to a first electric drive machine of the motor vehicle, a compact hybrid transmission can be created in which, in particular, all electric gear steps with all combustion gear steps can be combined. Preferably, the second gear-forming gear pair can be integrated both in the electric motor and in the internal combustion engine power path and can transmit both drive power from the first electric drive machine and the internal combustion machine. Because the hybrid transmission is constructed with only a single countershaft, a compact hybrid transmission can be created which, in particular, is constructed with few components.

In an advantageous embodiment, a pre-transmission of the pre-transmission includes a direct transmission. In addition or as an alternative, the internal combustion engine power path in the hybrid transmission includes four gear stages. Additionally or alternatively, the electromotive force path in the hybrid transmission includes two gear stages. As a result, a compact and lightweight hybrid transmission can be created that has a sufficient spread for the internal combustion engine. A pre-translation can be set up with the pre-transmission in a technically simple manner, for example by bridging the pre-transmission. Thus, a translation can be set up by switching a single switching element. The hybrid transmission is therefore technically simple to build.

In a further advantageous embodiment, the pre-transmission comprises a planetary gear set with planetary gear set elements comprising a ring gear, a planet gear with a planetary gear carrier and a sun gear. In this way, a technically simple and, in particular, axially compact front gear can be created. In addition, it is advantageous to set up a direct transmission with a planetary gear set, since there are two ways of setting up a direct transmission. The planetary gear set can be blocked, for example. It is also conceivable to bridge the pre-transmission so the planetary gear set.

In a further advantageous embodiment, the second gear-forming gear pair is designed to be connected to the internal combustion engine and / or the first electric drive machine in a driving manner. In addition, all gear steps for the internal combustion engine can be shifted independently of the gear steps for the first electric drive machine. In this way, a highly variable and yet compact hybrid transmission can be created. In particular, the dual use of the second gear-forming gear pair makes it possible to create a transmission with fewer components and less space requirement.

In a further advantageous embodiment, a sixth switching element is designed for blocking or bridging the planetary gear set. In addition, a fifth shift element is designed to set up a translation by means of the planetary gear set. This enables the planetary gear set to be switched in a technically simple manner. The planetary gear set can preferably be shifted with a double shifting element, a shifting element of the double shifting element bridging the planetary gear set and a shifting element of the double shifting element causing a gear ratio to be set up by means of the planetary gear set.

In a further advantageous embodiment, the planetary gear set comprises three couplings. The first coupling is assigned to a first planetary gear set element and the transmission input shaft. The second coupling is assigned to a second planetary gear set element and the transmission input shaft. The third coupling is assigned to a third planetary gear set element and a component fixed to the housing. In addition, one of these couplings can be switched by means of a fifth switching element and the other two couplings are designed as a permanently fixed connection. With such a connection, the planetary gear set of the pre-transmission can be technically easily integrated into the internal combustion engine power path, since at least two of the connections are designed as permanently fixed connections, i.e. do not require any switchable connections.

In a further advantageous embodiment, the transmission drive shaft is designed as a hollow shaft and surrounds the transmission input shaft at least in sections. As a result, the compactness of the hybrid transmission can be further improved. A hybrid transmission can be created that is particularly short axially.

In a further advantageous embodiment, the switching elements are designed as form-fitting switching elements. Additionally or alternatively, two of the switching elements are designed as double switching elements and can be actuated by a double-acting actuator. A double shift element makes it possible to build the hybrid transmission with a few components, since only one actuator has to be used to actuate a double shift element, for example to engage two gear stages. Furthermore, the control of the hybrid transmission is simplified. In addition, the hybrid transmission is compact, meaning that it requires less installation space. By using positive shifting elements, the hybrid transmission can be designed with less loss, that is, more efficiently. In particular, positive shifting elements lead to a more cost-efficient hybrid transmission.

In a further advantageous embodiment, the transmission input shaft is designed to be connected to a second electric drive machine in a driving manner. This allows the functionality of the hybrid transmission to be expanded. In particular, the hybrid transmission enables the internal combustion engine to be started from a purely electric drive. Furthermore, the second electric drive machine can be operated as a generator by the internal combustion engine and thus enable functions such as on-board power supply or serial crawling and / or driving both forwards and backwards. Furthermore, the second electric drive machine can support the internal combustion machine in speed regulation, for example for coupling or for gear changes. In addition, it is possible for the tractive force support to take place by means of the second electric drive machine when the first electric drive machine changes gear. In this way, in particular, efficient, purely electric motor driving operation can be set up.

In a further advantageous embodiment, the first electric drive machine is designed as a coaxial machine. In addition, the planetary gear set and preferably two switching elements are arranged axially and / or radially inside the first electric drive machine. In this way, a highly efficient and, in particular, compact drive train can be created. The available installation space can be used to advantage. In particular, a large electric drive machine can be used.

In a further advantageous embodiment, the idler gears and fixed gears, which are arranged in several gear set levels, are arranged axially between the internal combustion engine and the first electric drive machine to form gear stages. In addition, the motor vehicle drive train preferably has a second electric drive machine, which is connected to the transmission drive shaft in a driving manner. As a result, the available installation space can be used in an improved manner. The compactness of the motor vehicle drive train can be increased. In particular, an on-board power supply, a start of the internal combustion engine from a purely electric drive and / or serial crawling or driving forwards and / or backwards can be made possible by a second electric drive machine. The variability of the motor vehicle drive train is increased.

In a further advantageous embodiment, the second electric drive machine can be controlled as a starter generator for starting the internal combustion engine. Additionally or alternatively, the second electric drive machine can be controlled as a charging generator for charging an energy store. This allows the motor vehicle drive train to be operated efficiently. The fuel consumption can be reduced. In particular, there is no need for an additional starter for the internal combustion engine. Furthermore, it is possible to dimension both the second electric drive machine and the internal combustion machine smaller, since both can provide combined drive power.

In a further advantageous embodiment, the first electric drive machine can be activated as a supporting force means when changing gears of the internal combustion engine and preferably of the second electric drive machine. Additionally or alternatively, the internal combustion engine and preferably the second electric drive machine can be controlled as a supporting force means when changing gears in the first electric drive machine. Additionally or alternatively, all gear steps of the first electric drive machine can be shifted independently of the gear steps of the internal combustion engine. Additionally or alternatively, all gear stages of the internal combustion engine can be switched independently of the gear stages of the first electric drive machine. This can increase driving comfort. A highly variable motor vehicle drive train can be created which allows both drive machines, i.e. the electric drive machine and the internal combustion engine, to be operated in an optimal operating range, in particular independently of the gear selected for the drive machine. In addition, the available drive power of the motor vehicle drive train can be increased.

Fixing an element of a planetary gear set is to be understood in particular as blocking a rotation of the element about its axis of rotation. The element is preferably connected non-rotatably to a static component such as a frame and / or a transmission housing by means of a switching element. It is also conceivable to brake the element to a standstill.

Blocking a planetary gear set includes drivingly connecting two gears and / or the planetary gear carrier and a gear of the planetary gear set so that they rotate together with the same number of revolutions around the same point, preferably the center of the planetary gear set. When two gears and / or a planetary gear carrier and a gear of the planetary gear set are interlocked, the planetary gear set preferably acts like a shaft; in particular, there is no translation in the planetary gear set.

Stationary charging or charging in neutral is to be understood in particular as the operation of the electric drive machine as a generator, preferably at a standstill with the internal combustion engine running, in order to fill an energy store and / or to feed an on-board electronics.

In the present case, an actuator is in particular a component that converts an electrical signal into a mechanical movement. Actuators that are used with double switching elements preferably perform movements in two opposite directions in order to switch one switching element of the double switching element in the first direction and to switch the other switching element in the second direction.

A gear step change takes place in particular by switching off a switching element and / or a clutch and simultaneously switching on the switching element and / or the clutch for the next higher or lower gear step. The second shift element and / or the second clutch thus takes over the torque from the first shift element and / or the first clutch piece by piece until the entire torque is taken over by the second shift element and / or the second clutch at the end of the gear step change. With prior synchronization, a gear change can take place more quickly; form-fitting shifting elements can preferably be used.

A combustion machine can in particular be any machine that can generate a rotary movement by burning a drive medium such as gasoline, diesel, kerosene, ethanol, liquefied petroleum gas, LPG, etc. An internal combustion engine can be, for example, a gasoline engine, a diesel engine, a Wankel engine or a two-stroke engine.

When driving in series or crawling, an electric drive machine of a motor vehicle is operated as a generator by an internal combustion engine of the motor vehicle. The energy generated in this way is then made available to a further electric drive machine of the motor vehicle in order to provide drive power.

• 1 eine schematische Draufsicht auf ein Kraftfahrzeug mit einem erfindungsgemäßen Kraftfahrzeug-Antriebsstrang;
• 2 eine schematische vereinfachte Darstellung eines erfindungsgemäßen Hybridgetriebes;
• 3a, 3b schematisch die Schaltzustände des Hybridgetriebes gemäß der 2;
• 4 eine erste Variante einer Anordnung der Schaltelemente eines Vorgetriebes des Hybridgetriebes;
• 5 eine weitere Variante einer Anordnung der Schaltelemente eines Vorgetriebes des Hybridgetriebes;
• 6 eine weitere Variante der Anordnung von Schaltelementen eines Vorgetriebes;
• 7 eine erste Variante einer möglichen Anbindung eines Vorgetriebes im Hybridgetriebe;
• 8 eine weitere Variante einer möglichen Anbindung eines Vorgetriebes im Hybridgetriebe;
• 9 eine weitere Variante eines erfindungsgemäßen Hybridgetriebes;
• 10 eine vereinfachte schematische Darstellung des Hybridgetriebes gemäß der 9;
• 11 eine weitere Variante eines erfindungsgemäßen Hybridgetriebes;
• 12 eine vereinfachte schematische Darstellung des Hybridgetriebes gemäß der 11;
• 13 eine weitere Variante eines erfindungsgemäßen Hybridgetriebes;
• 14 eine vereinfachte schematische Darstellung des Hybridgetriebes gemäß der 13;
• 15 eine weitere Variante eines erfindungsgemäßen Hybridgetriebes;
• 16 eine vereinfachte schematische Darstellung des Hybridgetriebes gemäß der 15;
• 17 eine weitere Variante eines erfindungsgemäßen Hybridgetriebes; und
• 18 eine weitere Variante eines erfindungsgemäßen Hybridgetriebes.

The invention is described and explained in more detail below with the aid of a few selected exemplary embodiments in connection with the accompanying drawings. Show it:

• 1 a schematic plan view of a motor vehicle with a motor vehicle drive train according to the invention;
• 2 a schematic simplified representation of a hybrid transmission according to the invention;
• 3a , 3b schematically the switching states of the hybrid transmission according to FIG 2 ;
• 4th a first variant of an arrangement of the switching elements of a pre-transmission of the hybrid transmission;
• 5 a further variant of an arrangement of the switching elements of a pre-transmission of the hybrid transmission;
• 6th another variant of the arrangement of switching elements of a pre-transmission;
• 7th a first variant of a possible connection of a pre-transmission in the hybrid transmission;
• 8th another variant of a possible connection of a pre-transmission in the hybrid transmission;
• 9 another variant of a hybrid transmission according to the invention;
• 10 a simplified schematic representation of the hybrid transmission according to FIG 9 ;
• 11 another variant of a hybrid transmission according to the invention;
• 12th a simplified schematic representation of the hybrid transmission according to FIG 11 ;
• 13th another variant of a hybrid transmission according to the invention;
• 14th a simplified schematic representation of the hybrid transmission according to FIG 13th ;
• 15th another variant of a hybrid transmission according to the invention;
• 16 a simplified schematic representation of the hybrid transmission according to FIG 15th ;
• 17th another variant of a hybrid transmission according to the invention; and
• 18th another variant of a hybrid transmission according to the invention.

In 1 is schematically a motor vehicle 10 with a motor vehicle drive train 12th shown. The motor vehicle powertrain 12th has a first electric drive machine 14th and an internal combustion engine 16 on that by means of a hybrid transmission 18th with a rear axle of the motor vehicle 10 are connected. There is also an optional second electric drive machine 20th shown in dashed lines. The second electric prime mover 20th is also by means of the hybrid transmission 18th with a rear axle of the motor vehicle 10 connectable. It goes without saying that there is also a connection to a front axle of the motor vehicle 10 is possible. By means of the motor vehicle drive train 12th becomes drive power of the first electric drive machine 14th , the internal combustion engine 16 and the optional second electric prime mover 20th the wheels of the motor vehicle 10 fed. The car 10 also has an energy store 22nd in order to store energy for supplying the first and / or second electric drive machine 14th , 20th serves.

In 2 is a schematic overview of a hybrid transmission according to the invention 18th shown in the form of a kind of circuit diagram. The individual in the hybrid transmission 18th Existing shafts are numbered consecutively with “w” and the corresponding index in order to enable easier identification of the shafts later in subsequent representations. There are also a total of three main translations with i ₁ until i ₃ designated. These translations are preferably set up by gear pairs. In addition, are in the hybrid transmission 18th Switching elements A. until F. shown in the manner of a switch. An output transmission, which is preferably set up via a meshing pair of gears, is with i _from designated.

The hybrid transmission 18th also has a pre-transmission 24 on, by means of a fifth switching element E. and a sixth switching element F. is switchable. The pre-transmission 24 is with the internal combustion engine 16 connected and can a pre-translation of the drive power of the internal combustion engine 16 set up. The pre-transmission is preferably 24 designed as a two-speed transmission. The pre-translated drive power of the internal combustion engine 16 can then by closing a first switching element A. about the main translation i ₃ and the output ratio i _from with one output 26th get connected. By closing a second switching element B. can be the pre-translated drive power of the internal combustion engine 16 by means of the main translation i ₂ and the output ratio i _from with the downforce 26th get connected. The two-speed gearbox and the main gear ratios i ₂ and i ₃ as well as the output ratio can consequently be referred to as the internal combustion engine power path.

The first electric drive machine 14th can by closing a third switching element C. effective drive with the output 26th be connected, with this being the main translation i ₁ and the output ratio i _from the drive power of the first electric drive machine 14th translate. Furthermore, the first electric drive machine 14th by closing a fourth switching element D. effective drive via the second main transmission i ₂ and the output ratio i _from with the downforce 26th get connected. The main translations i ₁ and i ₂ and the output ratio consequently form an electromotive force path.

The main translation i ₂ is therefore just like the output ratio i _from assignable to both power paths. The hybrid transmission 18th essentially has two power paths, an internal combustion engine and an electromotive path. The internal combustion engine path has a total of four gear ratios, which result from the pre-transmission, the preferably as a two-speed pre-transmission 24 can be designed and which can be designed in particular in a planetary design, and two downstream spur gear stages with the translations i ₂ and i ₃ result. In particular, the two spur gear stages can be switched from a common transmission shaft to a countershaft that meshes with a differential gear, for example. The electromotive force path has two gear ratios, which are made up of two switchable spur gear stages with the gear ratios i ₂ and i ₃ result.

An optional second electric drive machine can be connected to the internal combustion engine power path 20th be connected, which is shown in dashed lines in the drawing. Preferably, the second electric drive machine 20th in the direction of power flow after the pre-transmission 24 connected to the internal combustion engine power path.

In the 3a and 3b are the schematic switching states of the hybrid transmission 18th according to the 2 shown. In a switching matrix 28 are the switching states with regard to the combustion gear steps V1 until V4 shown. In a switching matrix 30th are the switching states with regard to the two electric gear steps E1 and E2 shown. It goes without saying that the combustion gear steps can be operated in combination with the electric gear steps in order to set up a hybrid mode.

In the first column of the switching matrix 28 are the combustion gears V1 until V4 the internal combustion engine 16 shown. The switching states of the switching elements are in the second to seventh columns A. until F. shown, where “X” means that the respective shift element is closed, that is, connects the transmission components assigned to it with one another in a driving manner. As long as there is no entry, it can be assumed that the corresponding switching element is open, i.e. that it is not transmitting any drive power. The switching matrices 28 and 30th also apply to the following embodiments of hybrid transmissions according to the invention 18th .

For setting up the first combustion gear stage V1 are the third switching element C. and the fifth switching element E. close. Closing the fourth switching element D. and the fifth switching element E. sets up the second combustion gear V2 a. The third combustion gear V3 can by inserting the third switching element C. and the sixth switching element F. to be set up. Insertion of the fourth switching element D. and the sixth switching element F. sets up the fourth combustion gear V4 a.

By inserting the first switching element A. can use the first electric gear E1 to be set up. Insertion of the second switching element B. causes the second electric gear to be set up E2 .

The pre-transmission 24 is preferably designed as a planetary gear set. A planetary gear set always has three couplings, with a first coupling connecting a first planetary gear set element to a drive shaft, which is designated in the diagram with W _An , in the examples shown. _{A second coupling connects a second planetary gear set element} with the shaft, which is designated in the scheme with W An1, and the drive power in the main gear, that is, the gear with the gear ratios i ₁ until i ₃ , directs. A third coupling connects a third planetary gear set element to the housing. One of these couplings is always via the fifth switching element E. switchable, whereby the other two couplings are designed as permanent fixed connections. The fifth switching element E. can for example be arranged on the housing side, as in the following 4th until 6th shown.

In 4th a variant is shown in which a sun gear of the planetary gear set is connected to a ring gear by closing the sixth switching element F. is connectable. This is the planetary gear set of the pre-transmission 24 blocks and sets up a translation of 1.

In 5 a variant is shown in which the sixth switching element F. the sun gear and a planet carrier of the planetary gear set connects effectively and thus ensures that the planetary gear set is locked. In the embodiments according to 4th and 5 can use the fifth switching element E. and the sixth switching element F. can be combined to form a double switching element.

In 6th a further variant is shown in which a double switching element is not possible. Here the fifth switching element connects E. a planetary gear set element with a driving effect with a component fixed to the housing, the sixth shifting element F. is designed to connect the shaft driving the planetary gear set with a shaft that transmits drive power from the planetary gear set. Closing the sixth switching element F. consequently bridges the planetary gear set.

In the 7th and 8th are different arrangements of the fifth switching element E. and the sixth switching element F. shown. In 7th is a so-called drive-side arrangement of the fifth switching element E. and the sixth switching element F. shown in which the fifth switching element E. and the sixth switching element F. in the direction of force flow between the internal combustion engine 16 and the planetary gear set of the preliminary transmission 24 are arranged.

In 8th is a so-called output-side arrangement of the fifth shift element E. and the sixth switching element F. shown in which the fifth switching element E. and the sixth switching element F. in the direction of force flow after the internal combustion engine 16 and are arranged after the planetary gear set.

In 9 is a first detailed variant of a hybrid transmission according to the invention 18th shown. The combustion engine 16 is by means of a transmission input shaft 32 effective drive with a pre-transmission in the form of a planetary gear set RS tied together. The planetary gear set RS has a sun gear, a planetary gear carrier and a ring gear, the ring gear having a driving effect with the transmission input shaft 32 is connected and the planetary gear carrier is effective for driving with a transmission drive shaft 34 connected is. The sun gear of the planetary gear set RS can by closing the fifth switching element E. be effectively connected to a component fixed to the housing and by closing the sixth switching element F. be effectively connected to the ring gear. In other words, the switching element closes E. setting up a translation by means of the planetary gear set RS and closing the switching element F. a blocking of the planetary gear set RS . The fifth switching element E. and the sixth switching element F. are combined to form a double switching element and at least partially radially and axially within the first electrical drive machine, which is designed as a coaxial machine 14th arranged.

Furthermore, the planetary gear set RS axially and radially within the first electric drive machine 14th arranged. On the gearbox drive shaft 34 there are two idler gears arranged on a countershaft 36 arranged fixed gears mesh and the translation stages i ₂ and i ₃ set up. The first switching element A. and the second switching element B. are combined to form a double switching element, with a closing of the first switching element A. the translation level i ₃ sets up, so the corresponding idler gear effective for driving with the transmission drive shaft 34 connects. Closing the second switching element B. sets the gear ratio i ₂ a, so it connects the corresponding idler gear with the transmission drive shaft 34 . By closing the fourth switching element D. can be the first electric prime mover 14th effective drive with the idler gear of the transmission gear stage i ₂ get connected. By closing the third switching element C. can be the first electric prime mover 14th be effectively connected to an idler gear, which is the transmission gear stage i ₁ sets up and with one on the countershaft 36 arranged fixed gear meshes.

On the countershaft 36 an optional parking lock wheel is also shown in dashed lines and designated by P. Furthermore, there is a meshing pair of gears, consisting of fixed gears, which are attached to the countershaft 36 and on a differential of the output 26th are arranged, an output translation i _from set up. The optional second electric drive machine 20th can be effective as a drive with the gear drive shaft 34 be connected, for example via a meshing pair of gears, a traction mechanism or another connection variant generally known in the prior art.

The transmission input shaft 32 is designed as a solid shaft. The transmission drive shaft 34 is designed as a hollow shaft and surrounds the transmission input shaft 32 at least in sections. The idler gear of the transmission gear stage i ₂ is also arranged on a hollow shaft, which is the transmission drive shaft 34 surrounds at least in sections. The idler gear of the transmission gear stage i ₁ is arranged on a hollow shaft, which is the idler gear of the transmission gear stage i ₂ associated hollow shaft surrounds at least in sections.

The shafts described above are arranged on a first transmission axis A1. The countershaft 36 is arranged on a gear axis A2. The downforce 26th and in particular a differential of the output 26th are arranged on a gear axis A3. The second electric prime mover 20th is arranged on a gear axis A4. The idler gear of the second gear ratio i ₂ associated hollow shaft is denoted _{by W 2.} Corresponding to the idler gear of the first gear stage i ₁ associated shaft designated as w ₁ and the idler gear of the transmission gear stage i ₃ Associated wave _{is designated w 3} in order to enable easier identification of the individual waves with the simplified schematic representations. The transmission input shaft 32 is alternatively designated in the scheme with W _an and the transmission drive shaft 34 is alternatively designated by W _an1 .

The pre-transmission 24 in the form of a planetary gear set RS realizes in the variant shown preferably a translation into slow speed.

In 10 is a simplified schematic representation of the hybrid transmission 18th according to the 9 shown. As already described above is a sun gear So of the planetary gear set RS by closing the fifth switching element E. Can be effectively connected to a component fixed to the housing. Closing the sixth switching element F. causes a connection of the sun gear So of the planetary gear set RS with a ring gear Ho of the planetary gear set RS . The planetary gear set RS is blocked. In the internal combustion engine power path can through Closing the first switching element A. the translation i ₃ are set up and by closing the second switching element B. the translation i2. Closing the fourth switching element D. causes the translation i2 to be set up in the electromotive force path. Closing the third switching element C. causes a translation i ₁ in the electromotive force path. All of these translations are then made via the output transmission i _from the downforce 26th fed.

In 11 is a further variant of a hybrid transmission according to the invention 18th shown. In contrast to the in 9 The variant shown is the double switching element comprising the fifth switching element E. and the sixth switching element F. on the output side on the planetary gear set RS arranged. The connection of the planetary gear set elements of the planetary gear set RS to the individual transmission components is analogous to that in 9 , the sixth switching element F. a connection of the sun gear So of the planetary gear set RS with a planet carrier or web St. of the planetary gear set RS causes.

In 12th is a simplified schematic representation of the hybrid transmission according to the invention 18th according to the 11 shown in the form of a circuit diagram. The representation of the 12th essentially corresponds to the representation in 10 . As already described above, the double switching element comprises the fifth switching element E. and the sixth switching element F. regarding the planetary gear set RS Arranged on the output side. The connection on the drive side is permanently fixed and the connection on the output side is switchable.

In 13th is a further variant of a hybrid transmission according to the invention 18th shown. The double switching element comprising the fifth switching element E. and the sixth switching element F. is in this embodiment on the drive side with respect to the planetary gear set RS arranged, the transmission input shaft 32 effective drive with a ring gear of the planetary gear set RS is connectable. The sun gear of the planetary gear set is connected to a component fixed to the housing. The transmission drive shaft 34 is effective as a drive with the planetary gear carrier or web of the planetary gear set RS tied together. Due to the fixed connection of the sun gear of the planetary gear set RS is a blocking of the planetary gear set RS not possible. Hence the sixth switching element F. designed for this purpose, the transmission input shaft 32 effective drive with the gear drive shaft 34 connect to. In other words, by closing the sixth switching element F. the planetary gear set RS bridged.

In 14th is a simplified schematic representation of the hybrid transmission according to the invention 18th according to the 13th shown. As already described above, the double switching element is the fifth switching element E. and the sixth switching element F. on the drive side with respect to the planetary gear set RS arranged, with a ring gear Ho of the planetary gear set RS by closing the fifth switching element E. effective drive with the internal combustion engine 16 is connectable. The sun gear So of the planetary gear set RS is effectively connected to a component fixed to the housing. A planet carrier or web St. of the planetary gear set RS is effective as a drive with an input of the main transmission comprising the transmission gear stages i ₁ , i ₂ and i ₃ connected and can by closing the sixth switching element F. effective drive with the internal combustion engine 16 get connected. As already described above, the sixth switching element closes F. to a bridging of the planetary gear set RS .

In 15th is a further variant of a hybrid transmission according to the invention 18th shown. The double switching element comprising the fifth switching element E. and the sixth switching element F. is arranged on the output side. The transmission input shaft 32 is effective as a drive with a ring gear of the planetary gear set RS tied together. The transmission drive shaft 34 is by closing the fifth switching element E. effective drive with a planetary gear carrier or web of the planetary gear set RS connectable. The sun gear of the planetary gear set RS is connected to a component fixed to the housing. Closing the sixth switching element F. causes the planetary gear set to be bridged RS , i.e. an effective drive connection of the transmission input shaft 32 with the transmission drive shaft 34 .

In 16 is a simplified schematic representation of the hybrid transmission according to the invention 18th according to the 15th shown in the form of a circuit diagram. As already described above, is a ring gear Ho of the planetary gear set RS effective drive with the internal combustion engine 16 tied together. A planet carrier or web St. of the planetary gear set RS can by closing the fifth switching element E. be effectively connected to the main gearbox. Closing the sixth switching element F. causes the planetary gear set to be bridged RS . The sun gear So of the planetary gear set is connected to a component fixed to the housing.

In 17th is a further variant of a hybrid transmission according to the invention 18th shown. In contrast to the hybrid transmission variants shown above 18th is the planetary gear set RS designed as a so-called plus wheel set. Basically a minus planetary gear set, so like in the previous ones Embodiments shown, advantageous over the plus wheel set, since this is more cost-effective and generally has a better efficiency. It is well known that some translations can be better and / or exclusively with a plus planetary gear set. In general, a minus planetary gear set can be converted into a plus planetary gear set by exchanging the web connection and the ring gear connection and increasing the amount of the stationary gear ratio by 1.

In the variant shown is the transmission input shaft 32 effective drive with a planet carrier of the planetary gear set RS tied together. The transmission drive shaft 34 is effective as a drive with a ring gear of the planetary gear set RS tied together. The arrangement of the double switching element comprising the fifth switching element E. and the sixth switching element F. is on the output side with respect to the planetary gear set. A sun gear of the planetary gear set RS is by closing the fifth switching element E. Can be effectively connected to a component fixed to the housing. Closing the sixth switching element F. causes a drive-effective connection of the sun gear of the planetary gear set RS with the ring gear of the planetary gear set RS . In other words, by closing the switching element F. the planetary gear set RS blocked.

In 18th is a further variant of a hybrid transmission according to the invention 18th shown. In contrast to the in 11 shown variant of a hybrid transmission 18th is the downforce 26th no longer between the translation levels i ₂ and i ₃ forming gear set planes but at one axial end of the countershaft 36 . In particular, they are an output transmission i _from forming gears in a gear plane together with the connection gears of the second electric drive machine 20th arranged.

It goes without saying that such an alternative connection of the output for each of the previously shown embodiments of hybrid transmissions 18th Can apply.

Advantages of the arrangement of the output 26th In particular, there may be further geometric restrictions in the drive train and / or in the engine compartment of a motor vehicle.

With the embodiments of hybrid transmissions shown 18th the following functions in particular are possible. The combustion gears V1 until V4 and the electric gear steps E1 and E2 can be switched independently of each other. Consequently, each of the electric gear steps E1 and E2 with each combustion gear V1 until V4 be combined.

When shifting between the combustion gears V1 until V4 can be the first electric prime mover 14th the tractive force via the electric gear steps E1 or E2 support. While between the electric gears E1 and E2 is switched, the internal combustion engine 16 the tractive effort over one of the combustion gears V1 until V4 support.

The pre-transmission, which is preferably designed as a two-speed transmission, serves as a splitter group for the spur gear stages, which the transmission stages i ₂ and i ₃ form.

When shifting from combustion gear V1 in the combustion gear V2 is a shift element change in the pre-transmission 24 required from the fifth switching element E. on the sixth switching element F. . Synchronization can be achieved here, for example, by regulating the speed of the internal combustion engine 16 take place.

The shift from the combustion gear step V2 in the combustion gear V3 is a so-called group connection. This involves changing the switching elements of the pre-transmission 24 , from the sixth switching element F. on the fifth switching element E. , as well as a change in the main group from the gear stage i ₂ to the gear ratio i ₃ what a change from the second switching element B. on the first switching element A. is carried out. Switching can take place as follows. First, there is a load reduction on the internal combustion engine 16 . Then the second switching element B. and the sixth switching element F. opened and the fifth switching element E. synchronized and closed. The first switching element is then synchronized A. which is then closed. Is a second electric prime mover 20th available, this can support the synchronization. Is not a second electric prime mover 20th present, conventional synchronizations are required on at least one of the switching elements to be switched in group switching.

When shifting from combustion gear V3 in the combustion gear V4 is a switching element change of the pre-transmission 24 required, from the fifth switching element E. on the sixth switching element F. . The synchronization also takes place here, for example, by regulating the speed of the internal combustion engine 16 .

With a second electric drive machine 20th the following functions in particular can be covered. A start of the internal combustion engine 16 from a purely electric drive is possible. The fifth is preferably Switching element E. or the sixth switching element F. closed. Advantageously, that shift element is to be closed which has to be closed for a subsequent combustion gear stage provided. Consequently is the fifth switching element E. for the combustion gear V1 and the combustion gear V3 and the sixth switching element F. for the combustion gear V2 respectively. V4 close. Furthermore, a second electric drive machine operated as a generator can be used 20th an on-board power supply and power generation for serial crawling or driving forwards and backwards take place. As already described above, the second electric drive machine 20th a speed control of the internal combustion engine 16 assist with coupling and / or switching. In addition, the second electric drive machine 20th Traction support via the gear ratios i ₂ or i ₃ afford when the first electric prime mover 14th changes gear. Furthermore, there is a purely electric drive via the gear ratios i ₂ or i ₃ possible with the first electric prime mover 14th also optionally via the electric gear steps E1 or E2 can drive.

The invention has been comprehensively described and explained with reference to the drawings and the description. The description and explanation are to be understood as an example and not restrictive. The invention is not limited to the disclosed embodiments. Other embodiments or variations will become apparent to those skilled in the art using the present invention and a careful analysis of the drawings, the disclosure, and the following claims.

In the claims, the words “comprising” and “having” do not exclude the presence of further elements or steps. The undefined article “a” or “an” does not exclude the presence of a plural. A single element or a single unit can perform the functions of several of the units mentioned in the patent claims. The mere mention of some measures in several different dependent patent claims should not be understood to mean that a combination of these measures cannot also be used advantageously. Reference signs in the patent claims are not to be understood as restrictive.

List of reference symbols

10

Motor vehicle

12th

Automotive powertrain

14th

first electric drive machine

16

Internal combustion engine

18th

Hybrid transmission

20th

second electric prime mover

22nd

Energy storage

24

Pre-transmission

26th

Downforce

28

Switching matrix

30th

Switching matrix

32

Transmission input shaft

34

Transmission drive shaft

36

Countershaft

RS

Planetary gear set

St.

web

So

Sun gear

Ho

Ring gear

w *

Gear shafts

i1-i3

Main translations

iab

Output ratio

A-F

Switching elements

V1-V4

Combustion gears

E1, E2

Electric gear steps

QUOTES INCLUDED IN THE DESCRIPTION

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

Patent literature cited

• DE 102012205319 A1 [0006]

Claims (15)

Hybrid transmission (18) for a motor vehicle drive train (12) of a motor vehicle (10), with: a transmission input shaft (32) for operative connection of the hybrid transmission with an internal combustion engine (16) of the motor vehicle; a transmission drive shaft (34) which can be connected to the transmission input shaft by means of an input connection in order to establish an internal combustion engine power path in the hybrid transmission; a countershaft (36); idler gears and fixed gears arranged in several gear set levels to form gear stages; a plurality of gear shifting devices with shifting elements (A, B, C, D, E, F) for engaging the gear steps; an output (26) for transmitting drive power from the hybrid transmission, wherein a first gear-forming gear pair and a second gear-forming gear pair can be effectively connected to a first electric drive machine (14) of the motor vehicle in order to set up an electromotive force path in the hybrid transmission; and the input connection comprises a pre-transmission (24) for setting up at least two switchable pre-transmission stages in the internal combustion engine power path. Hybrid transmission (18) according to Claim 1 , wherein a pre-transmission of the pre-transmission (24) comprises a direct transmission; the internal combustion engine power path in the hybrid transmission comprises four gear stages (V1, V2, V3, V4); and / or the electromotive force path in the hybrid transmission comprises two gear stages (E1, E2). Hybrid transmission (18) according to one of the preceding claims, wherein the pre-transmission (24) comprises a planetary gear set (RS) with planetary gear set elements, comprising a ring gear (Ho), a planet gear with a planetary gear carrier and a sun gear (So). Hybrid transmission (18) according to one of the preceding claims, wherein the second gear-forming gear pair is designed to be connected to the internal combustion engine (16) and / or to the first electric drive machine (14) in a driving manner; and all gear steps for the internal combustion engine can be switched independently of the gear steps for the first electric drive machine. Hybrid transmission (18) according to one of the preceding claims, wherein a sixth switching element (F) is designed for blocking or bridging the planetary gear set (RS); and a fifth shift element (E) is designed to set up a translation by means of the planetary gear set. Hybrid transmission (18) according to one of the preceding claims, wherein the planetary gear set (RS) comprises three couplings; the first coupling is assigned to a first planetary gear set element and the transmission input shaft (32); the second coupling is associated with a second planetary gear set element and the transmission input shaft (34); the third coupling is assigned to a third planetary gear set element and a component fixed to the housing; and one of these couplings can be switched by means of a fifth switching element (E) and the other two couplings are designed as permanently fixed connections. Hybrid transmission (18) according to one of the preceding claims, wherein the transmission drive shaft (34) is designed as a hollow shaft and surrounds the transmission input shaft (32) at least in sections. Hybrid transmission (18) according to one of the preceding claims, wherein the switching elements (A, B, C, D, E, F) are designed as form-fitting switching elements; and or two of the switching elements are designed as double switching elements and can be actuated by a double-acting actuator. Hybrid transmission (18) according to one of the preceding claims, wherein the transmission input shaft (32) is designed to be operatively connected to a second electric drive machine (20) in a driving manner. Motor vehicle drive train (12) for a motor vehicle (10), with: a hybrid transmission (18) according to any one of the preceding claims; an internal combustion engine (16) which can be connected to the transmission input shaft (34); and a first electric drive machine (14) which can be connected to drive the first gear-forming gear pair and which can be connected to the second gear-forming gear pair in a drive-effective manner. Motor vehicle drive train (12) according to Claim 10 , wherein the first electric drive machine (14) is designed as a coaxial machine; and the planetary gear set (RS) and preferably two switching elements (F, E) are arranged axially and / or radially inside the first electric drive machine. Motor vehicle drive train (12) according to Claim 10 or 11 wherein the idler gears and fixed gears arranged in several gear set planes are arranged axially between the internal combustion engine (16) and the first electric drive machine (14) for forming gear stages; and the motor vehicle drive train preferably has a second electric drive machine (20) which is connected to the transmission drive shaft (34) in a driving manner. Motor vehicle drive train (12) according to Claim 12 wherein the second electric drive machine (20) can be controlled as a starter generator for starting the internal combustion engine (16); and / or can be controlled as a charging generator for charging an energy store (22). Motor vehicle drive train (12) according to one of the preceding claims, wherein the first electric drive machine (14) can be controlled as a supporting force when changing gears of the internal combustion engine (16) and preferably the second electric drive machine (20); the internal combustion engine (16) and preferably the second electric drive machine can be controlled as a supporting force means when changing gears of the first electric drive machine; all gear steps (E1, E2) of the first electric drive machine can be switched independently of the gear steps (V1, V2, V3, V4) of the internal combustion engine; and or all gear steps of the internal combustion engine can be switched independently of the gear steps of the first electric drive machine. Motor vehicle (10) having: a motor vehicle drive train (12) according to one of the Claims 11 until 14th ; and an energy store (22) for storing energy for supplying the first electric drive machine (14) and preferably the second electric drive machine (20).

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