Planetary coupling gear

Abstract

Multi-gear planetary coupling gear (1, 2, 8, 9, 10, 11) with an input (AN) connectable to an internal combustion engine, with an output (AB), with several planetary gear sets (P1, P2, P3, P4, P5), with several shifting elements (S1, S2, S3, S4, S5), with at least one electric machine (EM1, EM2, EM3, EM4), wherein different gear ratios (A, B, C, D, E, F, G, H, I) can be represented depending on an actuation of the shifting elements (S1, S2, S3, S4, S5), wherein the at least one electric machine (EM1, EM2, EM3, EM4) is drive-connected to one of the planetary gear sets (P1, P2, P3, P4, P5), wherein the planetary coupling gear (2, 9, 11) has a first electric machine (EM1, EM3) which is assigned to a first planetary gear set (P1, P4) and a second electric machine (EM2, EM4) which is assigned to a second planetary gear set (P2, P5) and which supplies mechanical power from the first electric machine (EM1, EM3) to the first planetary gear set (P1,P4) and / or from the second electric machine (EM2, EM4) into the second planetary gear set (P2, P5), wherein the first electric machine (EM1, EM3) and / or the second electric machine (EM2, EM4) is connectable to the output (AB), so that an electric motor drive operation with at least a first gear ratio and / or with at least a second gear ratio can be realized, wherein a mechanical power can be introduced into the associated planetary gear set (P1, P2, P3, P4, P5) from the at least one electric machine (EM1, EM2, EM3, EM4) by means of a shaft of the planetary gear set (P1, P2, P3, P4, P5) assigned to it, so that gear ratios can be changed with at least reduced interruption of tractive force, characterized in that an electric motor drive operation with a shorter gear ratio or with a longer gear ratio can be realized,the drive (AN) can be connected to the output (AB) with shorter gear ratios or with longer gear ratios and, in the case of electric motor operation with a shorter gear ratio, the drive (AN) can be connected to the output (AB) with a shorter gear ratio or, in the case of electric motor operation with a longer gear ratio, the drive (AN) can be connected to the output (AB) with a longer gear ratio.

Description

The invention relates to a multi-speed planetary coupling transmission having a drive which can be connected to an internal combustion engine, having an output, having a plurality of planetary gear sets, having a plurality of shift elements, having at least one electric machine, it being possible to produce different transmission ratios as a function of an actuation of the shift elements, it being possible for the at least one electric machine to be connected in a drive manner to one of the planetary gear sets.DE 10 2007 005 438 A1 discloses a multi-speed planetary coupling transmission having a plurality of planetary gear sets and a plurality of shift elements, wherein different transmission ratios can be produced as a function of an actuation of the shift elements, in which at least one electric machine is provided, which is operatively connected to one of the planetary gear sets, and a torque can be introduced by the electric machine into the associated planetary gear set via a shaft of the planetary gear set assigned to it, in order to support a torque present at the associated planetary gear set for producing a transmission ratio via the electric machine, in order to provide a multi-speed planetary coupling transmission which can be operated with good efficiency.DE 11 2006 002 301 B4 discloses an electrically variable transmission comprising an input element for receiving power from an engine, an output element, a first and second motor / generator and a first, second and third planetary gear set, each of which has a sun gear, a ring gear and a carrier. The input member is continuously connected to the carrier of the first planetary gear set and the output member is continuously connected to the carrier of the second planetary gear set. The transmission further includes a first interconnecting member continuously interconnecting the sun gear of the first planetary gear set with the sun gear of the second planetary gear set, a second interconnecting member continuously interconnecting the carrier of the second planetary gear set with the ring gear of the third planetary gear set, and a third interconnecting member continuously grounded the ring gear of the second planetary gear set. The first motor / generator is continuously connected to the ring gear of the first planetary gear set. The second motor / generator is continuously connected to the sun gears of the first and second planetary gear sets. The transmission also includes a first torque-transmitting device that selectively connects the carrier of the first planetary gear set to the sun gear of the third planetary gear set, a second torque-transmitting device that selectively connects the sun gear of the third planetary gear set to the sun gears of the first and second planetary gear sets, a third torque-transmitting device that selectively ground the ring gear of the third planetary gear set and the carrier of the second planetary gear set, a fourth torque-transmitting device that is connected in parallel with the first motor / generator to selectively prevent rotation thereof, and a fifth torque-transmitting device that is connected in parallel with the second motor / generator to selectively prevent rotation thereof. The torque transmitting devices are engageable alone or in combinations of two to provide an electrically variable transmission having a continuously variable range of speed ratios and four fixed forward speed ratios. Further, the torque transmitting devices and the first and second motor / generators are operable to provide five operating modes in the electrically variable transmission, including a battery reverse mode, an EVT reverse mode, reverse and forward launch modes, a continuously variable transmission range mode, and a fixed ratio mode.Further transmissions of the generic type are known from DE 11 2006 003 030 T5 and DE 11 2006 002 557 B4.The object of the invention is to further improve a planetary coupling transmission mentioned at the beginning in terms of construction and / or function.The object is achieved by a multi-speed planetary coupling transmission having a drive which can be connected to an internal combustion engine, having an output, having a plurality of planetary gear sets, having a plurality of shift elements, having at least one electric machine, it being possible to produce different transmission ratios as a function of an actuation of the shift elements, it being possible for the at least one electric machine to be drive-connected to one of the planetary gear sets, in which transmission ratio a mechanical power can be introduced into the associated planetary gear set by the at least one electric machine by means of a shaft of the planetary gear set assigned to it, with the result that transmission ratios can be changed with at least reduced interruption of the tractive force.The planetary coupling transmission can have a housing. The planetary gear sets may be disposed in the housing. The drive can have a drive shaft. The drive shaft can be a solid shaft or a hollow shaft. The output can have an output shaft. The output shaft can be a solid shaft or a hollow shaft. The drive shaft may have an axis of rotation. The output shaft can have an axis of rotation. The input shaft and the output shaft may be arranged coaxially. The drive shaft can be guided into the housing. The output shaft can be led out of the housing. The output shaft can be connectable to at least one drivable vehicle wheel.A planetary gear set may include planetary gears. The planet gears can be connected to one another by means of a planet carrier. A planetary gear set may include a ring gear. A planetary gear set may include a sun gear. A planetary gear set may include a first shaft fixedly connected to the planet carrier. A planetary gear set may include a second shaft fixedly connected to the ring gear. A planetary gear set may include a third shaft fixedly connected to the sun gear. The first shaft, the second shaft and the third shaft may each have an axis of rotation. The first shaft, the second shaft, and the third shaft may be arranged coaxially. A shaft of the planetary gear set may be a solid shaft. A shaft of the planetary gear set may be a hollow shaft. A planetary gear set may include an input shaft. A planetary gear set may have an output shaft. The shafts of the planetary gear set may be arranged coaxially with the input shaft and the output shaft.A planetary gear set may be a positive planetary gear set. A planetary gear set may have a positive stationary transmission ratio. The input shaft and the output shaft of a planetary gear set can rotate in the same direction. A planetary gear set may be a minus planetary gear set. A planetary gear set may have a negative stationary ratio. The input shaft and the output shaft of a planetary gear set can rotate in opposite directions. A stationary transmission ratio can result when the planet carrier is blocked. All shafts can be fixed in space. If it allows binding, individual or several minus planetary gear sets can be converted into plus planetary gear sets, provided that simultaneously planet carrier and ring gear connections are exchanged and the amount of the stationary transmission ratio is increased by 1.The planetary coupling transmission may have two coupled planetary gear sets. The planetary coupling transmission may include a first planetary gear set and a second planetary gear set. The planetary coupling transmission can have at least one spur gear stage. The planetary coupling transmission can have a first spur gear stage, a second spur gear stage and a third spur gear stage. The planetary coupling transmission may have three coupled planetary gear sets. The planetary coupling transmission may include a first planetary gear set, a second planetary gear set, and a third planetary gear set. The planet carrier of the first planetary gear set may be connected to the ring gear of the second planetary gear set. The ring gear of the first planetary gear set may be connected to the sun gear of the third planetary gear set.A shift element may be a clutch. A shift element may be a brake. The planetary coupling transmission can have five shift elements. The planetary clutch transmission may include four clutches and one brake. Up to three switching elements can be simultaneously switchable. A fixed housing coupling can be omitted. An electric machine may be operable as a motor. An electric machine can be operable as a generator. The planetary coupling transmission can have a single electric machine. The planetary coupling transmission can have a plurality of electric machines. The planetary coupling transmission can have two electric machines. By means of the planetary coupling transmission, six different transmission ratios can be produced for forward travel in the internal combustion engine. By means of the planetary coupling transmission, two different transmission ratios for electromotive forward travel can be produced. An electric machine can be arranged on at least one shaft of the planetary coupling transmission. A freewheel device can be arranged on at least one shaft of the planetary coupling transmission. A free wheel device may be operative between the at least one shaft and the housing. A freewheel device can be effective between the at least one shaft and a further shaft. A drive connection can be a fixed connection. A drive connection can be a rotationally fixed connection. Transmission ratios can be changed with reduced traction force interruption. Transmission ratios can be changed without interruption of the tractive force.The planetary coupling transmission according to the invention enables a power-split hybrid operation. The planetary coupling transmission according to the invention has a high number of transmission ratios for driving in an internal combustion engine. The planetary coupling transmission according to the invention has a compact design. The planetary coupling transmission according to the invention has a short design in the direction of extension of the shaft axes of rotation. The planetary coupling transmission according to the invention is well suited for a front-transverse construction. Construction costs are reduced. The various ratios have good gradation. Absolute rotational speeds are reduced. Relative rotational speeds are reduced. Planetary gear set torques are reduced. Shift element torques are reduced. Gear efficiency is improved. Drag torques are reduced. Frictional shift elements can be omitted.According to the invention, the planetary coupling transmission has a first electric machine which is assigned to a first planetary gear set and a second electric machine which is assigned to a second planetary gear set, and a mechanical power can be introduced from the first electric machine into the first planetary gear set and / or from the second electric machine into the second planetary gear set. The first electric machine may be associated with a third planetary gear set and mechanical power may be input from the first electric machine to the third planetary gear set. An electromotive driving mode is thus made possible by means of the first electric machine and / or by means of the second electric machine. According to the invention, the first electric machine and / or the second electric machine can be connected to the output drive, so that an electromotive driving operation can be produced with at least one first transmission ratio and / or with at least one second transmission ratio.A mechanical power can be conducted from the first electric machine or from the second electric machine to the output and at the same time the respective other electric machine can be connected to the input. A mechanical power can be conducted from the respective other electric machine to the drive. An electromotive driving operation can thus take place and at the same time an internal combustion engine can be started by means of the respective other electric machine. A mechanical power can be conducted from the drive to the respective other electric machine. An electromotive driving operation can thus take place and at the same time an internal combustion engine can drive the respective other electric machine in a generator operation.Starting from an operating state in which a mechanical power is conducted from the first electric machine or from the second electric machine to the output and the respective other electric machine is connected to the drive, the drive can be connectable to the output via a suitable transmission ratio. Thus, starting from a serial driving operation, a change without interruption of the tractive force into a driving operation by the internal combustion engine is made possible.According to the invention, an electromotive driving operation can be produced with a shorter transmission ratio or with a longer transmission ratio, the drive can be connected to the output drive with shorter transmission ratios or with longer transmission ratios, and in an electromotive driving operation with a shorter transmission ratio, the drive can be connected to the output drive with a shorter transmission ratio, or in an electromotive driving operation with a longer transmission ratio, the drive can be connected to the output drive with a longer transmission ratio. Starting from an electromotive driving operation with a shorter transmission ratio, starting an internal combustion engine into correspondingly short transmission ratios and starting from an electromotive driving operation with a longer transmission ratio, starting an internal combustion engine into correspondingly long transmission ratios is thus made possible.A transmission ratio of the first electric machine can be exchangeable and at the same time a mechanical power can be conducted from the other electric machine to the output. Thus, when a transmission ratio is changed in an electromotive driving operation, at least partial retention of the tensile force is made possible. While a transmission ratio of the planetary gear set assigned to the first electric machine or the planetary gear set assigned to the second electric machine is changed, the respective other electric machine can support the output drive.The shift elements may be positive clutches and / or positive brakes. The shift elements may be switchable dog clutches and / or switchable dog brakes. The shift elements can each have a sliding sleeve. Drag torques are thus reduced. A switching element can be synchronizable by means of the at least one electric machine.The planetary gear set assigned to the at least one electric machine can have a ring gear and a planetary carrier, the at least one electric machine can be drivingly connected to the ring gear and the planetary carrier can be drivingly connected to the drive. The planetary coupling transmission may include a first electric machine having a rotor that is associated with a first planetary gear set having a ring gear, the rotor of the first electric machine being drivingly connected to the ring gear of the first planetary gear set, and a second electric machine having a rotor that is associated with a second planetary gear set having a planet carrier, the rotor of the second electric machine being drivingly connected to the planet carrier of the second planetary gear set. The planetary gear set assigned to the at least one electric machine can have a sun gear and the at least one electric machine can be drivingly connected to the sun gear of this planetary gear set and the planetary coupling transmission can have a further planetary gear set with a ring gear and the ring gear of this planetary gear set can be drivingly connected to the drive. The planetary coupling transmission may include a first electric machine having a rotor associated with a first planetary gear set having a sun gear, the rotor of the first electric machine drivingly connected to the sun gear of the first planetary gear set, and a second electric machine having a rotor associated with a second planetary gear set having a planet carrier, the rotor of the second electric machine drivingly connected to the planet carrier of the second planetary gear set.Optional features of the invention are designated in particular by "can". Accordingly, there is in each case one exemplary embodiment of the invention which has the respective feature or features.Exemplary embodiments of the invention are described in more detail below with reference to figures. Further features and advantages result from this description. Specific features of these exemplary embodiments may represent general features of the invention. Features of these exemplary embodiments that are associated with other features can also represent individual features of the invention.They show schematically and by way of example: FIG. 1 shows a planetary coupling transmission not according to the invention with three planetary gear sets and an electric machine, FIG. 2 shows a planetary coupling transmission with three planetary gear sets and two electric machines, FIG. 3 shows a planetary coupling transmission not according to the invention with three planetary gear sets and an electric machine, FIG. 4 shows a planetary coupling transmission with three planetary gear sets and two electric machines, FIG. 5 shows a shift matrix of a planetary coupling transmission having three planetary gear sets and at least one electric machine, FIG. 6 shows a planetary coupling transmission not according to the invention with two planetary gear sets and an electric machine, FIG. 7 shows a planetary coupling transmission with two planetary gear sets and two electric machines, and FIG. 8 shows a shift matrix of a planetary coupling transmission having two planetary gear sets and at least one electric machine.In the figures, identical components or assemblies are denoted by identical reference numerals. FIG. 1 shows a planetary coupling transmission 1 having a first planetary gear set P 1, a second planetary gear set P 2, a third planetary gear set P 3 and an electric machine EM 1. FIG. 2 shows a planetary coupling transmission 2 having a first planetary gear set P 1, a second planetary gear set P 2, a third planetary gear set P 3, a first electric machine EM 1 and a second electric machine EM 2.The first planetary gear set P 1 has planetary gears. The planetary gears of the first planetary gear set P 1 are connected to one another by means of a planetary carrier P 1A. The first planetary gear set P 1 includes a ring gear P 1B. The first planetary gear set P 1 includes a sun gear P 1C. The second planetary gear set P 2 has planetary gears. The planet gears of the second planetary gear set P 2 are connected to one another by means of a planet carrier P 2A. The second planetary gear set P 2 includes a ring gear P 2B. The second planetary gear set P 2 includes a sun gear P 2C. The third planetary gear set P 3 has planetary gears. The planet gears of the third planetary gear set P 3 are connected to one another by means of a planet carrier P 3A. The third planetary gear set P 3 includes a ring gear P 3B. The third planetary gear set P 3 has a sun gear P 3C.The planetary coupling transmission 1, 2 has an input AN and an output AB. The first planetary gear set P 1 is arranged on the drive side. The third planetary gear set P 3 is arranged on the output side. The second planetary gear set P 2 is disposed between the first planetary gear set P 1 and the third planetary gear set P 3. The planet carrier P1A is connected to the ring gear P2B. The ring gear P 1B is connected to the sun gear P 3C. The drive AN is connected to the ring gear P 2B. The output AB is connected to the planet carrier P 3A.The planetary coupling transmission 1, 2 has a housing 3. Between the case 3 and the sun gear P 1C, a switching element S 1 is disposed. The shift element S 1 is a brake. Between the housing 3 and the ring gear P 3B, a switching element S 2 is arranged. The shift element S 2 is a brake. Between the planet carrier P 2A and the planet carrier P 3A, a shifting element S 3 is arranged. The shift element S 3 is a clutch. Between the sun gear P 2C and the ring gear P 3B, a switching element S 4 is arranged. The shift element S 4 is a clutch. Between the ring gear P 1B and the planet carrier P 2A, a shifting element S 5 is arranged. The shift element S 5 is a clutch. The shift elements S 1, S 2, S 3, S 4, S 5 are each designed as a form-fitting shift element, such as a claw clutch or claw brake. The switching elements S 1, S 2, S 3, S 4, S 5 can each be switched between an open switching position and a closed switching position.The electric machine EM 1 has a stator 4 and a rotor 5. The stator 4 is fixedly arranged with respect to the housing 3. The rotor 5 is connected to the ring gear P 1B. The rotor 5 is connected to the sun gear P 3C. The electric machine EM 2 has a stator 6 and a rotor 7. The stator 6 is fixedly arranged with respect to the housing 3. The rotor 7 is connected to the planet carrier P2A. The electric machines EM 1, EM 2 can each be operated as a motor or as a generator.The height of a stationary transmission ratio of the planetary coupling transmission 1, 2, and thus the height of the transmission ratios and spreads, can in principle be freely selected. For example, the first planetary gear set P 1 has a stationary transmission ratio i 0P1 of i 0P1= -3,495, the second planetary gear set P 2 has a stationary transmission ratio i 0P2 of i 0P2= -2,664 and the third planetary gear set P 3 has a stationary transmission ratio i 0P3 of i 0P3= -1,870.FIG. 3 shows a planetary coupling transmission 8 having a first planetary gear set P 1, a second planetary gear set P 2, a third planetary gear set P 3 and an electric machine EM 1. FIG. 4 shows a planetary coupling transmission 9 having a first planetary gear set P 1, a second planetary gear set P 2, a third planetary gear set P 3, a first electric machine EM 1 and a second electric machine EM 2. The second planetary gear set P 2 is arranged on the drive side. The third planetary gear set P 3 is arranged on the output side. The first planetary gear set P 1 is disposed between the second planetary gear set P 2 and the third planetary gear set P 3. Compared to the planetary coupling transmission 1 according to FIG. 1 and the planetary coupling transmission 2 according to FIG. 2, the first planetary gear set P 1 and the second planetary gear set P 2 are interchanged in the planetary coupling transmission 8 and the planetary coupling transmission 9. For the rest, reference is additionally made in particular to FIGS. 1 and 2 and the associated description.FIG. 5 shows a shift matrix of a planetary coupling transmission, such as planetary coupling transmission 1 according to FIG. 1, planetary coupling transmission 2 according to FIG. 2, planetary coupling transmission 8 according to FIG. 3 or planetary coupling transmission 9 according to FIG. 4, having three planetary gear sets, at least one electric machine and five shift elements S 1, S 2, S 3, S 4, S 5 for nine transmission stages A, B, C, D, E, F, G, H, I. The transmission stages A, B, C, D, E, F, G, H, I serve for forward travel. The transmission stages A, B, C, D, E, F are regular transmission stages. The transmission stages A, B, C, D, E, F are continuously stepped successively. The transmission stage G is an additional transmission stage. The transmission stages H, I enable an alternative representation of the transmission stage B. The transmission stages B, H, I have the same transmission. The shift matrix shows rows for the transmission stages A, B, C, D, E, F, G, H, I and columns for the shift elements S 1, S 2, S 3, S 4, S 5. In the switching matrix, closed switching elements are each marked with "x". A closed switching element enables power transmission.In the transmission ratio A, the shift elements S 2, S 4, S 5 are closed, while the other shift elements are open. In the transmission ratio B, the shift elements S 1, S 2, S 4 are closed, while the other shift elements are open. In the transmission stage C, the shift elements S 2, S 3, S 4 are closed, while the remaining shift elements are open. In the transmission ratio D, the shift elements S 3, S 4, S 5 are closed, while the remaining shift elements are open. In the transmission stage E, the shift elements S 1, S 3, S 5 are closed, while the remaining shift elements are open. In the transmission stage F, the shift elements S 1, S 4, S 5 are closed, while the remaining shift elements are open. In the transmission ratio G, the shift elements S 1, S 3, S 4 are closed, while the other shift elements are open. In the transmission stage H, the shift elements S 1, S 2, S 3 are closed, while the other shift elements are open. In the transmission stage I, the shift elements S 1, S 2, S 5 are closed, while the other shift elements are open.The transmission ratio step A has, for example, a transmission ratio i A of i A= 3,949. The transmission ratio step B has, for example, a transmission ratio i B of i B= 2,232. The transmission ratio step C has, for example, a transmission ratio i C of i C= 1,375. The transmission ratio step D has, for example, a transmission ratio i D of i D= 1,000. The transmission ratio step E has, for example, a transmission ratio i E of i E= 0,778. The transmission ratio step F has, for example, a transmission ratio i F of i F= 0,561. The transmission ratio step G has, for example, a transmission ratio i G of i G= 1,077. The transmission ratio step H has, for example, a transmission ratio i H of i H= 2,232. The transmission ratio stage I has, for example, a transmission ratio i I of i I= 2,232.Reference is also made to FIGS. 1, 2, 3 and 4 below. In an operating state in which the shift element S 2 is closed, the first electric machine EM 1 is connected to the output drive, for example, via a transmission ratio of i=1-i 0P3= 2,87. It can thus be driven by electric motor.In an operating state in which the shift elements S 2, S 4 are closed, the first electric machine EM 1 is connected to the output drive, for example, via a transmission ratio of i=1-i 0P3=2,87. It can thus be driven by electric motor. If the shift element combination S 2, S 4 occurs during the A-B or B-C shift during internal combustion engine operation, the first electric machine EM 1 supports the tractive force by means of its fixed transmission ratio to the output AB, and the shift can take place without interruption of tractive force with sufficient power of the first electric machine EM 1.In an operating state in which the shift elements S 2, S 4 are closed and a transition is made to an operating state in which the shift element S 4 is open, the shift element S 3 is closed and the shift element S 5 is closed, the first electric machine EM 1 is connected in 0P3=2,87 to the output AB via a transmission ratio of i=1-i. The opening of the switching element S 4 does not change anything thereon, but allows the closing of the switching element S 3. As a result, the second electric machine EM 2 can also support the output AB. If the driving power is supplied completely by the second electric machine EM 2 via the shift element S 3, the shift element S 2 can likewise be opened and the first electric machine EM 1 synchronizes the shift element S 5, which is then closed. The result is therefore a transition from an electromotive driving operation with a short transmission ratio (i=2.97) using the first electric machine EM 1 to a driving operation with a long transmission ratio (i=1) with at least partial retention of the tensile force. This means a load shift in the purely electromotive driving mode.In an operating state in which the shift elements S 3 and S 5 are closed, a fixed transmission ratio from the second electric machine EM 2, where i=1 to the output, arises as a result of the shift element S 3. The first electric machine EM 1 is likewise connected directly to the output AB by the shift element S 5. This allows the electric motor to be driven and the circuit D-E of the internal combustion engine transmission stages can be supported.In an operating state in which the shifting elements S 1 or S 1 and S 3 are closed, the first electric machine EM 1 is coupled to the drive AN by the shifting element S 1 with a fixed transmission ratio. The engine may start the internal combustion engine and operate as a generator. This enables, for example, a series operation together with the second electric machine EM 2 when the second electric machine EM 2 is coupled to the output AB via the shift element S 3 and the second electric machine EM 2 provides a driving power. This series operation can also take place at higher travel speeds and can also transition into the transmission stage E of the internal combustion engine operation, since the shift elements S 1 and S 3 are already closed in the transmission stage E. In order to start the internal combustion engine, additional measures can be provided.In an operating state occurring at a shift C-D in which the shift elements S 3 and S 4 are closed, the second electric machine EM 2 may support the output AB through a direct connection with the output AB. The first electric machine EM 1 carries out a so-called EDA circuit, a circuit with an electrodynamic starting element, and in the process synchronizes the internal combustion engine in such a way that the shift element S 5 can be closed. The first electric machine EM 1 is generator-type and can thus provide a portion of the electrical power required by the second electric machine EM 2. In such an EDA circuit, the first electric machine EM 1, the internal combustion engine (drive AN) and the output AB are operatively connected via one or more planetary sets.In an operating state in which the switching elements S 2 and S 4 are closed, the second electric machine EM 2 is fixedly coupled to the internal combustion engine at the drive AB. It can therefore start the internal combustion engine and then be used as a generator in order either to charge an electrical energy store or to supply an electrical power for a driving operation by means of the first electrical machine EM 1.In an operating state in which the shift element S 3 is closed, the second electric machine EM 2 is fixedly coupled to the output AB. It can be used for electric motor driving or also to support the shifts C-D and D-E of the internal combustion engine transmission ratios.In an operating state in which the shift elements S 3 and S 5 are closed, both the first electric machine EM 1 and the second electric machine EM 2 act on the output AB with a transmission ratio of i=1. Electromotive driving is possible jointly with both electric machines EM 1, EM 2, and thus with increased power. The internal combustion engine can be started from this operation. One possibility for this is to open the switching element S 5 and to synchronize and close the shaft element S 1 with the first electric machine EM 1. As a result, the first electric machine EM 1 is connected to the internal combustion engine and can start the internal combustion engine. The traction force can be maintained via the second electric machine EM 2 during the entire process via the shifting element S 3. Another possibility is a start of the internal combustion engine with traction force interruption or a further element which enables the start, such as a friction clutch between the internal combustion engine and the drive AB or an additional starter.FIG. 6 shows a planetary coupling transmission 10 having a first planetary gear set P 4, a second planetary gear set P 5 and a first electric machine EM 3. FIG. 7 shows a planetary coupling transmission 11 having a first planetary gear set P 4, a second planetary gear set P 5, a first electric machine EM 3 and a second electric machine EM 4.The first planetary gear set P 4 has planetary gears. The planetary gears of the first planetary gear set P 4 are connected to one another by means of a planetary carrier P 4A. The first planetary gear set P 4 includes a ring gear P 4B. The first planetary gear set P 4 includes a sun gear P 4C. The second planetary gear set P 5 has planetary gears. The planet gears of the second planetary gear set P 5 are connected to one another by means of a planet carrier P 5A. The second planetary gear set P 5 includes a ring gear P 5B. The second planetary gear set P 5 includes a sun gear P 5C.The planetary coupling transmission 10, 11 has an input AN and an output AB. The first planetary gear set P 4 is arranged on the output side. The second planetary gear set P 5 is arranged on the drive side. The drive AN is connected to the ring gear P 5B. The output AB is connected to the planet carrier P 4A. The planetary coupling transmission 10, 11 has a first spur gear stage R 1, a second spur gear stage R 2 and a third spur gear stage R 3. The first planetary gear set P 4 and the second planetary gear set P 5 are connected to one another by means of the spur gear stages R 1, R 2, R 3. The spur gear stages R 1, R 2, R 3 each have two gearwheels. The spur gear stage R 3 has two gearwheels Z 1, Z 2. The spur gear stages R 1, R 2, R 3 each have two fixed wheels. The first spur gear stage R 1 connects the ring gear P 4B and the sun gear P 5C. The second spur gear stage R 2 connects the planetary carrier P 4A and the planetary carrier P 5A. The third spur gear stage R 3 connects the sun gear P 4C and the ring gear P 5B. The gear Z1 is connected to the sun gear P4C. The first spur gear stage R 1 has, for example, a transmission ratio i R1 of i R1= 1,000, the second spur gear stage R 2 has a transmission ratio i R2 of i R2= 1,000 and the third spur gear stage R 3 has a transmission ratio i R3 of i R3= 0,777.The planetary coupling transmission 10, 11 has a housing 3. Between the housing 3 and the ring gear P 4B, a switching element S 1 is arranged. The shift element S 1 is a brake. Between the gear Z 2 and the ring gear P 5B, a shift element S 2 is disposed. The shift element S 2 is a clutch. A shifting element S 3 is arranged between the planetary carrier P 4A and the second spur gear stage R 2. The shift element S 3 is a clutch. A shifting element S 4 is arranged between the ring gear P 4B and the first spur gear stage R 1. The shift element S 4 is a clutch. A shifting element S 5 is arranged between the second spur gear stage R 2 and the gearwheel Z 1. The shift element S 5 is a clutch.The electric machine EM 1 has a stator 4 and a rotor 5. The stator 4 is fixedly arranged with respect to the housing 3. The rotor 5 is connected to the sun gear P 4C. The rotor 5 is connected to the gear Z 1. The electric machine EM 2 has a stator 6 and a rotor 7. The stator 6 is fixedly arranged with respect to the housing 3. The rotor 7 is connected to the planet carrier P5A.The height of a stationary transmission ratio of the planetary coupling transmission 10, 11, and thus the height of the transmission ratios and spreads, can in principle be freely selected. For example, the first planetary gear set P 4 has a stationary transmission ratio i 0P4 of i 0P4= -3,495 and the second planetary gear set P 5 has a stationary transmission ratio i 0P5 of i 0P5= -1,870. The stationary transmission ratios i 0P4, i 0P5 of the planetary gear sets P 4, P 5 can each be varied by up to approximately ±30%.Compared to the planetary coupling transmission 1 according to FIG. 1 and the planetary coupling transmission 2 according to FIG. 2, in the planetary coupling transmission 10 and the planetary coupling transmission 11, the first planetary gear set P 1 is replaced by a spur gear stage. In addition, the wheelset is distributed on the main shaft and the auxiliary shaft. The brake S 1 becomes the clutch S 2. For the rest, reference is additionally made in particular to FIGS. 1 and 2 and the associated description.FIG. 8 shows a shift matrix of a planetary coupling transmission, such as planetary coupling transmission 10 according to FIG. 6 or planetary coupling transmission 11 according to FIG. 7, having two planetary gear sets, at least one electric machine and five shift elements S 1, S 2, S 3, S 4, S 5 for nine transmission stages A, B, C, D, E, F, G, H, I. In transmission stage A, the shift elements S 1, S 4, S 5 are closed, while the remaining shift elements are open. In the transmission ratio B, the shift elements S 1, S 2, S 4 are closed, while the other shift elements are open. In the transmission stage C, the shift elements S 1, S 3, S 4 are closed, while the remaining shift elements are open. In the transmission ratio D, the shift elements S 3, S 4, S 5 are closed, while the remaining shift elements are open. In the transmission stage E, the shift elements S 2, S 3, S 5 are closed, while the remaining shift elements are open. In the transmission stage F, the shift elements S 2, S 4, S 5 are closed, while the remaining shift elements are open. In the transmission ratio G, the shift elements S 2, S 3, S 4 are closed, while the other shift elements are open. In the transmission stage H, the shift elements S 1, S 2, S 3 are closed, while the other shift elements are open. In the transmission stage I, the shift elements S 1, S 2, S 5 are closed, while the other shift elements are open. For the rest, reference is additionally made in particular to FIG. 5 and the associated description.Reference numerals denote reference numerals1 Planetary coupling transmission 2 Planetary coupling transmission 3 Housing 4 Stator 5 Rotor 6 Stator 7 Rotor 8 Planetary coupling transmission 9 Planetary coupling transmission 10 Planetary coupling transmission 11 Planetary coupling transmission AN Drive AB Output P 1 First planetary gear set P 1A Planetary carrier P 1B Ring gear P 1C Sun gear P 2 Second planetary gear set P 2A Planetary carrier P 2B Ring gear P 2C Sun gear P 3 Third planetary gear set P 3A Planetary carrier P 3B Ring gear P 3C Sun gear P 4A Planetary carrier P 4B Ring gear P 4C Sun gear P 5 Second planetary gear set P 5A Planetary carrier P 5B Ring gear P 5C Sun gear R 1 First spur gear stage R 2 second spur gear stage R 3 third spur gear stage Z 1 gear Z 2 gear S 1 shifting element S 2 shifting element S 3 shifting element S 4 shifting element S 5 shifting element EM 1 first electric machine EM 2 second electric machine EM 3 first electric machine EM 4 second electric machine

Claims

Multi-speed planetary coupling transmission (1, 2, 8, 9, 10, 11) having an input (AN) which can be connected to an internal combustion engine, having an output (AB), having a plurality of planetary gear sets (P1, P2, P3, P4, P5), having a plurality of shift elements (S1, S2, S3, S4, S5), having at least one electric machine (EM1, EM2, EM3, EM4), it being possible to produce different transmission ratios (A, B, C, D, E, F, G, H, I) as a function of an actuation of the shift elements (S1, S2, S3, S4, S5), it being possible to produce the at least one electric machine (EM1, EM2, EM3, EM4) having one of the planetary gear sets (P1, P2, P3, P4, P5), wherein the planetary coupling transmission (2, 9, 11) has a first electric machine (EM1, EM3) which is assigned to a first planetary gear set (P1, P4) and a second electric machine (EM2, EM4) which is assigned to a second planetary gear set (P2, P5), and a mechanical power can be introduced from the first electric machine (EM1, EM3) into the first planetary gear set (P1, P4) and / or from the second electric machine (EM2, EM4) into the second planetary gear set (P2, P5), wherein the first electric machine (EM1, EM3) and / or the second electric machine (EM2, EM4) can be connected to the output (AB), such that an electromotive driving mode can be implemented with at least one first transmission ratio and / or with at least one second transmission ratio, wherein a mechanical power can be introduced into the assigned planetary gear set (P1, P2, P3, P4, P5) by the at least one electric machine (EM1, EM2, EM3, EM4) by means of a shaft of the planetary gear set (P1, P2, P3, P4, P5) assigned to it, such that transmission ratios with at least reduced interruption of the tractive force can be changed, characterized in that an electromotive driving mode can be implemented with a shorter transmission ratio or with a longer transmission ratio, the drive (AN) with shorter transmission ratios or with longer transmission ratios can be connected to the output (AB) and, in the case of an electromotive driving operation with a shorter transmission ratio, the drive (AN) with a shorter transmission ratio can be connected to the output (AB) or, in the case of an electromotive driving operation with a longer transmission ratio, the drive (AN) with a longer transmission ratio can be connected to the output (AB).Planetary coupling transmission (2, 9) according to Claim 1, characterized in that the first electric machine (EM1) is assigned to a third planetary gear set (P3), and a mechanical power can be introduced from the first electric machine (EM1) into the third planetary gear set (P3).Planetary coupling transmission (2, 9, 11) according to Claim 1 or Claim 2, characterized in that a mechanical power can be conducted from the first electric machine (EM1, EM3) or from the second electric machine (EM2, EM4) to the output (AB) and at the same time the respective other electric machine can be connected to the drive (AN).Planetary coupling transmission (2, 9, 11) according to Claim 3, characterized in that a mechanical power can be conducted from the respective other electric machine to the drive (AN).Planetary coupling transmission (2, 9, 11) according to Claim 3, characterized in that a mechanical power can be conducted from the drive (AN) to the respective other electric machine.Planetary coupling transmission (2, 9, 11) according to one of Claims 3 to 5, characterized in that, starting from an operating state in which a mechanical power is conducted from the first electric machine (EM1, EM3) or from the second electric machine (EM2, EM4) to the output (AB) and the respective other electric machine is connected to the drive (AN), the drive (AN) can be connected to the output (AB) via a suitable transmission ratio.Planetary coupling transmission (2, 9, 11) according to one of the preceding claims, characterized in that the transmission ratio of the first electric machine (EM1, EM3) can be changed and at the same time a mechanical power can be conducted from the other electric machine to the output (AB).Planetary coupling transmission (1, 2, 8, 9, 10, 11) according to one of the preceding claims, characterized in that the shift elements (S1, S2, S3, S4, S5) are form-fitting clutches and / or form-fitting brakes.Planetary coupling transmission (1, 2, 8, 9) according to one of the preceding claims, characterized in that the planetary gear set (P1, P2, P3, P4, P5) assigned to the at least one electric machine (EM1) has a ring gear (P1B) and a planetary carrier (P1A), the at least one electric machine (EM1) is drive-connected to the ring gear (P1B) and the planetary carrier (P1A) is drive-connected to the drive (AN).Planetary coupling transmission (2, 9) according to one of the preceding claims, characterized in that the planetary coupling transmission (2, 9) has a first electric machine (EM1) with a rotor (5) which is assigned to a first planetary gear set (P1) with a ring gear (P1B), wherein the rotor (5) of the first electric machine (EM1) is drivingly connected to the ring gear (P1B) of the first planetary gear set (P1), and a second electric machine (EM2) with a rotor (7) which is assigned to a second planetary gear set (P2) with a planetary carrier (P2A), wherein the rotor (7) of the second electric machine (EM2) is drivingly connected to the planetary carrier (P2A) of the second planetary gear set (P2).Planetary coupling transmission (10, 11) according to Claim 1 or one of Claims 3 to 8, characterized in that the planetary gear set (P4) assigned to the at least one electric machine (EM3) has a sun wheel (P4C) and the at least one electric machine (EM3) is drive-connected to the sun wheel (P4C) of this planetary gear set (P4), and the planetary coupling transmission (10, 11) has a further planetary gear set (P5) with a ring wheel (P5B), and the ring wheel (P5B) of this planetary gear set (P5) is drive-connected to the drive (AN).Planetary coupling transmission (11) according to Claim 1 or one of Claims 3 to 8 or Claim 11, characterized in that the planetary coupling transmission (11) has a first electric machine (EM3) with a rotor (5) which is assigned to a first planetary gear set (P4) with a sun wheel (P4C), the rotor (5) of the first electric machine (EM3) being drivingly connected to the sun wheel (P4C) of the first planetary gear set (P4), and a second electric machine (EM4) with a rotor (7) which is assigned to a second planetary gear set (P5) with a planetary carrier (P5A), the rotor (7) of the second electric machine (EM4) being drivingly connected to the planetary carrier (P5A) of the second planetary gear set (P5), has.

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