DE102017003194A1 - Hybrid powertrain for a motor vehicle, in particular for a motor vehicle - Google Patents

Abstract

The invention relates to a hybrid drive train (10) for a motor vehicle, having at least one planetary gear (12), a first planetary gear set (14), a second planetary gear set (16), a first input shaft (18), a second input shaft (20), a third input shaft (22), a first output shaft (24) and a second output shaft (26), with at least one internal combustion engine (28), the output shaft (32) rotatably connected to the first input shaft (18), with an electric drive unit ( 34), by means of which the second input shaft (20) and the third input shaft (22) are drivable, with a first partial transmission (44) which is drivable by the first output shaft (24), and with a second partial transmission (46), which from the second output shaft (26) is drivable, wherein at least one coupling element (76) for blocking the first planetary gear set (14) is provided.

Description

The invention relates to a hybrid drive train for a motor vehicle, in particular for a motor vehicle, according to the preamble of patent claim 1.

Such a hybrid powertrain for a motor vehicle, in particular for a motor vehicle such as a passenger car, for example, is already the DE 10 2007 043 173 A1 to be known as known. The hybrid powertrain includes at least one planetary gear having a first planetary gear set, a second planetary gear set, a first input shaft, a second input shaft, a third input shaft, a first output shaft, and a second output shaft. In addition, the hybrid powertrain comprises at least one internal combustion engine, by means of which the motor vehicle is drivable. The internal combustion engine in this case has an output shaft designed, for example, as a crankshaft, via which the internal combustion engine can, for example, provide torques for driving the motor vehicle or at least one wheel of the motor vehicle. In this case, the output shaft, in particular permanently or constantly, rotatably connected to the first input shaft, so that, for example, torques between the first input shaft and the output shaft can be transmitted.

In addition, an electric drive unit is provided, by means of which the second input shaft and the third input shaft are drivable. In other words, torques can be transmitted between the electric drive unit and the second input shaft and between the electric drive unit and the third input shaft.

In addition, a first partial transmission is provided, which is drivable by the first output shaft. Furthermore, a second partial transmission is provided which can be driven by the second output shaft.

Object of the present invention is to develop a hybrid powertrain of the type mentioned in such a way that a particularly advantageous operation of the hybrid powertrain in a particularly simple manner can be realized.

This object is achieved by a hybrid drive train having the features of patent claim 1. Advantageous embodiments with expedient developments of the invention are specified in the remaining claims.

In order to develop a hybrid powertrain specified in the preamble of claim 1 type such that a particularly advantageous operation of the hybrid powertrain is realized in a particularly simple manner, at least one coupling element for blocking the first planetary gear set is provided according to the invention. The particular planetary gearset has at least one sun gear as the first transmission element, at least one ring gear as the second transmission element, at least one planet carrier as the third transmission element and at least one planetary gear, which rotatably on the planet carrier is mounted and meshes with the ring gear and with the sun gear. For blocking the planetary gear set two of the three gear elements are rotatably connected to each other, that is blocked, so that rotatably interconnected or interlocked gear elements rotate as a block about a common axis of rotation.

By blocking the planetary gear set, this is in a locked state in which the interconnected transmission elements rotate around said axis of rotation as a block, that is, together. If the planetary gear set is not locked, then the planetary gear set is in an unblocked state in which, for example, the gear elements locked together in the blocked state can rotate about the axis of rotation relative to one another. By using the coupling element and the ability to lock the first planetary gear by means of the coupling element, additional operating states of the hybrid powertrain can be generated in a simple manner, so that a particularly advantageous and, for example, particularly efficient operation of the hybrid powertrain is represented. In particular, it is possible to switch the first planetary gear set in a simple and effective manner between the blocked state and the unblocked state. For this purpose, for example, the coupling element is switched or moved between a blocking state and a release state. In the locked state, the first planetary gear set is locked by means of the coupling element. In the release state of the coupling element of the unblocked state of the first planetary gear set is set.

In order to realize a particularly advantageous operation of the hybrid drive train, at least one second coupling element for blocking the second planetary gear set is provided in a further embodiment. The previous and following statements on the first planetary gear and in particular the first coupling element can readily on the second coupling element and the second planetary gear set and vice versa. Thus, it is for example possible to easily switch the second planetary gear set by means of the second coupling element between the blocked state and the unblocked state. By using the second coupling element can be realized on simple, space, weight and cost further additional operating states of the hybrid powertrain, so that a particularly advantageous and in particular efficient operation can be displayed.

In addition, a particularly simple and cost-effective hybridization of a conventional dual-clutch transmission (DCT) can be realized by means of the hybrid powertrain according to the invention, so that starting from such a conventional dual-clutch transmission Dedicated Hybrid Transmission (DHT - dedicated hybrid transmission) can be created in a particularly cost-effective manner. Starting from a conventional dual-clutch transmission, in which two clutches are used in a well-known manner, the clutches are replaced by the two planetary gear sets and the electric drive unit, the planetary gear sets are also referred to simply as planetary gear sets. This means, for example, that the planetary gear sets and the electric drive unit can fulfill the function of two couplings used in a conventional dual-clutch transmission. In addition, a modular approach can be made possible by the hybrid powertrain according to the invention, so that for example the same wheelset and the same Schaltaktorik for a conventional dual-clutch transmission and a derived DHT can be used. In addition, the hybrid powertrain according to the invention enables the realization of at least two different driving modes. In a first of the driving modes can be driven in fixed gears, as it is known from conventional dual clutch transmissions. Thus, it is possible to realize or simulate fixed gears or gear ratios by means of the partial transmission, the planetary gear sets and the electric drive unit. The second driving mode, for example, a CVT mode (CVT - continuously variable transmission - continuously variable transmission), so that for example by means of the planetary gear sets and the electric drive unit, the hybrid powertrain in the manner of a CVT transmission can be operated without fixed gear or gear stages.

In order to realize a particularly efficient and thus efficient operation, the respective coupling element is preferably designed as a positive coupling element, so that the respective planetary gear set can be positively locked by means of the coupling element. For this purpose, the respective coupling element is preferably designed as a claw, dog clutch or claw switching element.

In a further embodiment of the invention, the electric drive unit has a first electric machine and an additionally provided second electric machine. In this case, the second input shaft can be driven by means of the first electric machine, wherein the third input shaft can be driven by means of the second electrical machine. As a result, a particularly advantageous operation of the hybrid powertrain can be realized. In addition, the number of parts and thus the cost, weight and space requirements can be kept low because, for example, by using the two electrical machines on clutches such as jaw clutches for coupling the electric drive unit can be dispensed with the input shafts. In this case, it is provided, for example, that a first rotor of the first electric machine, in particular directly, is non-rotatably connected to the second input shaft, for example, a second rotor of the second electric machine, in particular directly, is rotatably connected to the third input shaft. In particular, for example, the respective rotor is permanently or permanently rotatably connected to the respective input shaft.

Alternatively or additionally, it is preferably provided that the output shaft of the internal combustion engine designed, for example, as a crankshaft, is permanently or permanently connected to the first input shaft so as to be non-rotatable. Under the permanent or permanent non-rotatable connection is to be understood that, for example, based on the first input shaft and the output shaft between the first input shaft and the first output shaft no clutch or no starting element and thus no means is arranged, which between a closed position for non-rotatable connection of the first Input shaft with the output shaft and an open position is adjustable, in which the output shaft is decoupled from the first input shaft and thus not rotatably connected to the first input shaft.

In order to keep the particular axial space requirement of the hybrid powertrain particularly low, it is provided in a further embodiment of the invention that the first coupling element facing away on a first side of the electric drive unit and the second coupling element on one of the first side in the axial direction of the electric drive unit second side of the electric drive unit is arranged. This can also be particularly advantageous Force or torque flows are realized, so that a particularly efficient and effective operation can be realized.

It has been found to be particularly advantageous if at least one rotor element of the electric drive unit is arranged in the axial direction between the coupling elements. As a result, a particularly advantageous power flow can be realized. The electric drive unit comprises at least one stator and at least one rotor, which is rotatable about an axis of rotation relative to the stator. In this case, the rotor element is, for example, the rotor or component of the rotor of the electric machine.

Another embodiment is characterized in that a first coupling element and a second coupling element are provided, wherein by means of the first coupling element, the electric drive unit can be coupled to the second input shaft. By means of the second coupling element, the electric drive unit can be coupled to the third input shaft.

In order to be able to realize a particularly efficient operation, the respective coupling element is designed, for example, as a claw, claw switching element or dog clutch, so that the electrical drive unit, in particular a rotor of the electric drive unit, can be positively coupled to the respective input shaft via the respective coupling element.

In order to be able to keep the axial space requirement of the hybrid drive train particularly low, for example, the first coupling element on the first side of the electric drive unit and the second coupling element of the first side facing away in the axial direction of the electric drive unit second side of the electric drive unit is arranged. In this case, for example, the aforementioned rotor element is arranged in the axial direction of the electric drive unit between the coupling elements.

In addition, it has been found that a particularly advantageous operation can be realized in that the coupling elements are arranged in the axial direction of the electric drive unit on the same side of the electric drive unit. The coupling elements are arranged, for example, in the axial direction between the electric drive unit and the Planetenradsätzen.

In a further embodiment of the invention, the respective planetary gear set is designed as a so-called plus planetary gear. This means that the first planetary gearset has first planetary gears and second planetary gears that mesh with the first planetary gears. The first planetary gears are, for example, externally toothed, wherein the second planetary gears are externally toothed. For example, the first planetary gears are rotatable about respective first axes of rotation, the second planetary gears being rotatable about respective second axes of rotation, and the second axes of rotation being parallel to the first axes of rotation and spaced from the first axes of rotation.

In addition, the second planetary gear on third planet gears and meshing with the planetary gears fourth planet gears. For example, the third planetary gears are externally toothed, wherein preferably the fourth planetary gears are externally toothed. The third planet gears are rotatable, for example, about respective third axes of rotation, wherein the fourth planetary gears are rotatable about respective fourth axes of rotation. In this case, for example, run the fourth axes of rotation parallel to the third axes of rotation, wherein the fourth axes of rotation are spaced from the third axes of rotation. For example, the first axes of rotation preferably coincide with the third axes of rotation, the second axes of rotation coinciding with the fourth axes of rotation. This embodiment of the hybrid powertrain makes it possible to present a particularly advantageous and, in particular, efficient operation. Finally, it has proven to be advantageous for the realization of a particularly efficient operation when the first planetary gear has a first ring gear rotatably connected to the first output shaft, a first sun gear and planetary gears rotatably connected to the second input shaft. In this case, the second planetary gearset has a second ring gear rotatably connected to the second output shaft, a second sun gear and planetary gears connected in a rotationally fixed manner to the third input shaft. In addition, a Planetenradsätzen common and rotatably connected to the first input shaft connected planet carrier is provided on which the planetary gears of the first planetary gear and the planetary gears of the second planetary gear are rotatably mounted. Furthermore, for blocking the first planetary gear set of the planet carrier by means of the first coupling element with the first sun gear rotatably connected.

Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing. The features and feature combinations mentioned above in the description as well as the features and feature combinations mentioned below in the description of the figures and / or shown alone in the figures are not only in the respectively indicated combination but also in other combinations or in Used alone, without departing from the scope of the invention.

• 1 eine schematische Darstellung einer ersten Ausführungsform eines erfindungsgemäßen Hybridantriebsstrangs für ein Kraftfahrzeug, mit wenigstens einem Planetengetriebe, welches wenigstens zwei Planetenradsätze aufweist, und mit wenigstens einem Koppelelement zum Verblocken eines der Planetenradsätze;
• 2 ein Kutzbachplan des Planetengetriebes in einem ersten Betriebszustand;
• 3 ein Kutzbachplan des Planetengetriebes in einem zweiten Betriebszustand;
• 4 ausschnittsweise eine schematische Darstellung einer zweiten Ausführungsform des Hybridantriebsstrangs;
• 5 ausschnittsweise eine schematische Darstellung einer dritten Ausführungsform des Hybridantriebsstrangs; und
• 6 ausschnittsweise eine schematische Darstellung einer vierten Ausführungsform des Hybridantriebsstrangs.

The drawing shows in:

• 1 a schematic representation of a first embodiment of a hybrid powertrain according to the invention for a motor vehicle, with at least one planetary gear, which has at least two planetary gear sets, and with at least one coupling element for blocking one of the planetary gear sets;
• 2 a Kutzbach plan of the planetary gear in a first operating state;
• 3 a Kutzbach plan of the planetary gear in a second operating state;
• 4 a detail of a schematic representation of a second embodiment of the hybrid powertrain;
• 5 a schematic representation of a third embodiment of the hybrid powertrain; and
• 6 a schematic representation of a fourth embodiment of the hybrid powertrain.

In the figures, the same or functionally identical elements are provided with the same reference numerals.

1 shows a schematic representation of a first embodiment of a generally designated 10 hybrid powertrain for a motor vehicle, in particular for a trained example as a passenger car motor vehicles. The hybrid powertrain 10 includes a planetary gear 12 comprising a first planetary gear set 14, a second planetary gear set 16 , a first input shaft 18 , a second input shaft 20 , a third input shaft 22 , a first output shaft 24 and a second output shaft 26 having.

Furthermore, the hybrid powertrain 10 an internal combustion engine 28 which is designed as a reciprocating piston engine and consequently a plurality of combustion chambers in the form of cylinders 30 having. In the respective cylinder 30 a piston, not visible in the figures, is received in a translationally movable manner. The internal combustion engine 28 has a crankshaft 32 trained output shaft, wherein the piston via respective connecting rods hinged to the crankshaft 32 are coupled. The crankshaft 32 is rotatably mounted on a crankcase of the internal combustion engine 28 and thus can rotate about an axis of rotation relative to the crankcase. By the articulated coupling of the piston, the translational movements of the piston in a rotational movement of the crankshaft 32 converted to its axis of rotation. In this case, at least one wheel of the motor vehicle by means of the internal combustion engine 28 over the crankshaft 32 drivable so that, for example, the motor vehicle as a whole by means of the internal combustion engine 28 is drivable. For this purpose, the internal combustion engine 28 over her crankshaft 32 Provide torques for driving the motor vehicle or the wheel.

Out 1 is recognizable that the crankshaft 32 permanently or permanently against rotation with the first input shaft 18 connected is. Thus, torques between the crankshaft 32 and the first input shaft 18 be transferred, so for example, the input shaft 18 from the crankshaft 32 or can be driven in reverse. The hybrid powertrain 10 further comprises an electric drive unit 34 , which at the in 1 illustrated in the first embodiment exactly one electric machine 36 having. The electric machine 36 has a stator 38 and a rotor 40 which is rotatable about the aforementioned rotation axis relative to the stator 38. The rotor 40 includes, for example, a laminated core and an output shaft 42 on which the laminated core is arranged. The laminated core is non-rotatable with the output shaft 42 connected.

The electric drive unit 34 or the electric machine 36 is for example in a motor operation and thus operable as an electric motor. In engine operation, the electric drive unit provides 34 or the electric machine 36, in particular via the output shaft 42 or over the rotor 40 , Torques ready, by means of which, for example, at least the aforementioned wheel or the motor vehicle is driven in total. Furthermore, it is conceivable that the electric drive unit 34 or the electric machine 36 in a generator mode and thus can be operated as a generator. In the generator mode, for example, the rotor 40 driven by the aforementioned wheel or by the moving motor vehicle, so that by means of the generator kinetic energy of the motor vehicle is converted into electrical energy, which is provided by the generator.

As will be explained in more detail below, the input shafts are 20 and 22 from the electric drive unit 34 drivable. These are the input shafts 20 and 22 each rotatably with the electric drive unit 34 , in particular the rotor 40 , connectable or connected. This allows the electric drive unit 34 , in particular the electric machine 36 , the input shafts 20 and 22 drive.

The hybrid powertrain 10 also has a first partial transmission 44 on which of the first output shaft 24 is drivable. Furthermore, the hybrid powertrain has 10 a second partial transmission 46 on which of the second output shaft 26 is drivable. At the in 1 shown first embodiment, the first partial transmission 44 permanently non-rotatable with the first output shaft 24 connected. For this purpose, the first partial transmission 44 Gear wheels designed as gears 48a-c on, which constantly or permanently against rotation with the output shaft 24 are connected. In addition, the partial transmission 44 includes a first countershaft 50 , on which designed as gears loose wheels 52a-c are arranged. Besides, are on the countershaft 50 clutches 54 and 56 of the partial transmission 44 arranged. The loose wheels 52a-c per se are rotatable relative to the countershaft 50 and can via the couplings 54 and 56 rotatably connected to the countershaft 50 are connected. Furthermore, the partial transmission 44 a permanent rotation with the countershaft 50 connected and designed as a gear driven wheel 58 on, which meshes with a gear designed as a driven gear 60. The driven wheel 60 is permanently non-rotatable with an output shaft 62 connected via which the hybrid powertrain 10 Can provide torques for driving the wheel or the motor vehicle. For example, the wheel, in particular wheels, of the motor vehicle of the hybrid powertrain 10 over the output shaft 62 , And in particular via a differential gear to be driven.

The partial transmission 46 is permanently non-rotatable with the second output shaft 26 connected. For this purpose, the partial transmission 46 Gear wheels designed as gears 64a-c on which on the output shaft 26 arranged and permanently against rotation with the output shaft 6 are connected. For example, the gear wheels 64a-c formed integrally with the output shaft 26. Alternatively or additionally, the gear wheels 48a-c integral with the output shaft 24 connected.

In addition, the partial transmission has 46 formed as gears loose wheels 66a-c on, which with the corresponding gear wheels 64a-c combing and, in particular, loose, on a countershaft 68 of the partial transmission 46 are arranged. In addition, the partial transmission has 46 clutches 70 and 72 on. The loose wheels 66a-c are loosely arranged on the countershaft 68 and thus relative to the countershaft 68 rotatable, but can via the couplings 70 and 72 rotatably with the countershaft 68 get connected. The respective coupling 54 . 56 . 70 respectively 72 is designed for example as a dog clutch, so that a positive rotational connection between the respective countershaft 50 respectively 68 and the respective idler gear 52a-c respectively 66a-c is feasible. In addition, the partial transmission has 46 a trained as a gear driven wheel 74 on, which is permanently connected rotationally fixed to the countershaft 68. The driven wheels 58 and 64 mesh with the output gear 60. Thus, for example, depending on the operating state of the hybrid powertrain 10, the output shaft 62 over the output gear 60 and via the driven gear 58 from the countershaft 50 or via the output gear 60 and via the driven gear 74 from the countershaft 68 are driven.

Now to a particularly advantageous operation of the hybrid powertrain 10 To realize in a simple, weight and cost-effective manner, at least one coupling element 76 for blocking the first planetary gear set 14 intended. In other words, the planetary gear set 14 by means of the coupling element 76 into blocks. Preferably, the coupling element 76 designed as a positive coupling element, so that the first planetary gear 14 can be positively locked. In this case, the coupling element 76, for example, as a claw, that is designed as a claw switching element, which is formed for example as a dog clutch.

At the in 1 shown first embodiment, it is provided that the first planetary gear 14 rotatably connected to the first output shaft 24 connected first ring gear 78, a rotationally fixed to the second input shaft 20 connected first sun gear 80 and planet gears 82 which, with the sun gear 80 and the ring gear 78. The second planetary gear set 16 has a second ring gear rotatably connected to the second output shaft 26 84 a second sun gear rotatably connected to the third input shaft 22 86 and planet gears 88 on, which with the ring gear 84 and the sun wheel 86 comb.

This includes the planetary gear 12 one the planetary gear sets 14 and 16 common planet carrier 90 , which is permanently connected in a rotationally fixed manner to the first input shaft 18. At the planet carrier 90 Both are the planet gears 82 of the planetary gear 14 as well as the planet wheels 88 the planetary gear set 16 rotatably mounted. The respective planet wheels 82 For example, they are separate from the planetary gears 88 designed so that the planetary gears 82 and the planet wheels 88 respective, separately formed components are. Here are the planetary gears 82 coaxial with the planet wheels 88 arranged or their respective axes of rotation about which the planet gears 82 and 88 relative to the planet carrier 90 are rotatable, parallel to each other or even fall together.

For blocking the first planetary gear set 14 is the planet carrier 90 , in particular via the input shaft 18 , with the first sun wheel 80 , in particular via the second input shaft 20 , rotatably connected. For this purpose, the coupling element 76 comprises a first positive coupling part 92 , a second positive coupling part 94 and a third positive coupling part in the form of a sliding sleeve 96 , which in the axial direction of the input shaft 18 and thus the planet carrier 90 relative to the planet carrier 90 and relative to the input shaft 20 , in particular translational, is movable or displaceable. Here is the sliding sleeve 96 , for example by means of an in 1 Actuator, not shown, between a in 1 Entkoppelzustand shown and a coupling state, not shown movable. The coupling part 92 is, in particular permanently or constantly, rotatably connected to the input shaft 18, wherein the coupling part 94 , in particular permanent, non-rotatable with the input shaft 20 connected is. The Entkoppelzustand is also referred to as Entkoppelstellung, the coupling state is also referred to as a coupling position. In the decoupling state, for example, the sliding sleeve engages 96 in the coupling part 94 but not in the coupling part 92 one, so the planet carrier 90 not with the sun wheel 80 is blocked.

In the coupling state, however, engages the sliding sleeve 96 both in the coupling part 94 as well as in the coupling part 92 and thus acts with the coupling parts 92 and 94 form-fitting together, so that the coupling parts 92 and 94 over the sliding sleeve 96 interact positively. This is the planet carrier 90 with the sun wheel 80 rotatably connected, that is blocked, causing the planetary gear set 14 is blocked. The decoupling position of the sliding sleeve 96 thus corresponds to a release state or with a release position in which or the planetary gear 14 is in an unblocked state. In the unblocked state is the planet carrier 90 not with the sun wheel 80 splinted. The coupling position of the sliding sleeve 96 corresponds to a Verblockungszustand or with a Verblockungsstellung, in which or the planet carrier 90 via the coupling element 76 positively with the sun gear 80 is blocked. Then there is the planetary gear set 14 in his locked state. In the locked state, the planet carrier run 90 and the sun wheel 80 around the common axis of rotation around the crankshaft 32 and the input shaft 18 , in particular are rotatable relative to the crankcase, as a block and thus together around.

Furthermore, the hybrid powertrain 10 at least one second coupling element 98 on, by means of which the second planetary gear set 16 can be blocked. For blocking the second planetary gear set 16 is the planet carrier 90 , in particular via the input shaft 22 , rotatable with the sun gear 86 connectable. The coupling element 98 has a fourth coupling part 100 , a fifth coupling part 102 and a sixth coupling part in the form of a second sliding sleeve 104 on, with the previous and following comments on the coupling element 76 can be easily transferred to the coupling element 98 and vice versa. Thus, the sliding sleeve 104 is in the axial direction relative to the planet carrier 90 and relative to the sun gear 86 translationally movable and thus displaceable, so that the sliding sleeve 104 between a coupling position or a coupling state and a Entkoppelstellung or a Entkoppelzustand can be moved. The coupling part 100 is, in particular permanent, rotationally fixed to the input shaft 22 and thus with the sun wheel 86 connected, wherein the coupling part 102 , in particular permanent, rotationally fixed to the planet carrier 90 , which is also referred to as a web connected. In its Entkoppelstellung the sliding sleeve acts 104 although, for example, with the coupling part 100 , but not with the coupling part 102 together, so that in the decoupling of the sliding sleeve 104 the planetary gear set is not locked and thus assumes its unblocked state. In the coupling position, however, the sliding sleeve 104 engages both in the coupling part 100 as well as in the coupling part 102 a, so that the sliding sleeve 104 positive fit with the coupling parts 100 and 102 interacts. As a result, the coupling parts act 100 and 102 over the sliding sleeve 104 form-fitting together, causing the planetary gear set 16 is locked and is in its locked state. Then the input shaft is running 22 or the sun wheel 86 and the planet carrier 90 together as a block around the aforementioned axis of rotation. Thus, the Entkoppelstellung the sliding sleeve corresponds 104 with a release position or with a release state, in which or the planetary gear 16 not blocked, that is unblocked. Furthermore, the coupling position of the sliding sleeve corresponds 104 with a blocking state or a blocking position in which or the planetary gear 16 is locked and thus is in its locked state.

In particular, the axial space requirement of the hybrid powertrain 10 To be able to keep particularly low, is the first coupling element 76 on a first page 106 the electric drive unit 34 . in particular the electric machine 36 , arranged, wherein the second coupling element 98 on one of the first page 106 in the axial direction of the electric drive unit 34 , in particular the electric machine 36 , second side facing away 108 the electric drive unit 34 , in particular the electric machine 36 , is arranged. In this case, the axial direction of the electric drive unit 34, in particular the electric machine 36 , with the axial direction of the input shaft 18 and thus of the planetary gear 12 or the hybrid powertrain 10 altogether. The axial direction of the hybrid drive train 10 coincides with the axis of rotation, around which the crankshaft 32 is rotatable relative to the crankcase.

In particular, it is provided in the first embodiment that at least one rotor element such as the laminated core of the rotor 40 the electric machine 36 or the electric drive unit 34 in the axial direction between the coupling elements 76 and 98 is arranged.

The hybrid powertrain 10 In the first embodiment, moreover, it comprises a first coupling element 110 , by means of which the electric drive unit 34 , in particular the rotor 40 , with the second input shaft 20 rotatably connected or can be coupled. In addition, the hybrid powertrain includes 10 a second coupling element 112 , by means of which the electric drive unit 34 , in particular the rotor 40 , with the third input shaft 22 rotatably coupled or connectable. In this case, the electric drive unit 34 over the respective coupling element 110 respectively 112 are positively connected to the respective input shaft 20 and 22, respectively. For this purpose, the respective coupling element 110 comprises a coupling part 114 respectively 116 , a coupling part 118 respectively 120 and a coupling part 122 respectively 124 , The coupling part 114 is permanently non-rotatable with the input shaft 20 connected, wherein the coupling member 118 permanently rotatably connected to the rotor 40 , in particular with the output shaft 42 of the rotor 40 , connected is. The coupling part 116 is permanently rotatable with the input shaft 22 connected, wherein the coupling part 120 permanently non-rotatable with the output shaft 42 or the rotor 40 connected is. The respective coupling part 122 respectively 124 is designed as a sliding sleeve, which in the axial direction relative to the coupling parts 114 and 118 respectively 116 and 120 can be moved. In particular, the respective coupling part 122 respectively 124 be moved between a closed position and an open position in the axial direction. In the closed position are the coupling parts 114 and 118 over the coupling part 122 or the coupling parts 116 and 120 over the coupling part 124 positively connected rotationally fixed to each other, whereby the electric drive unit 34 over the coupling element 110 with the input shaft 20 or the electric drive unit 34 over the coupling element 112 with the input shaft 22 positively connected rotationally fixed.

In the release position of the coupling part 122 is the electric drive unit 34 from the input shaft 20 decoupled because there are no torques between the electric drive unit 34 and the input shaft 20 over the coupling part 122 or via the coupling element 110 can be transmitted. In the release position of the coupling part 124 is the electric drive unit 34 decoupled from the input shaft 22, since in the release position of the coupling part 124 no torques between the electric drive unit 34 and the input shaft 22 over the coupling part 124 or via the coupling element 112 can be transmitted.

A ride on the partial transmission 44 can be realized, for example, by moving the sliding sleeve 96 in the coupling position of the first planetary gear set 14 is blocked while the planetary gear set 16 is unblocked or is in its unblocked state, which is realized in that the sliding sleeve 104 is in its Entkoppelstellung. Furthermore, while the coupling part is located 124 in his release position. To drive over the partial transmission 44 To realize a boost operation, in particular as a parallel hybrid, for example, the coupling element 110 switched on by the coupling part 122 is moved from its release position to its closed position. When driving over the partial transmission 44 For example, a boost operation via the partial transmission 46 be realized by the coupling element 112 is switched on. For this purpose, the coupling part 124 is moved from its release position into its closed position, that is shifted.

A speed adjustment by means of the planetary gear set 14 is possible by the coupling element 110 is activated or is. For this purpose, the coupling part 122 is in its closed position, in particular while the coupling part 124 in its release position, the sliding sleeve 96 in its Entkoppelstellung and the sliding sleeve 104 is in its Entkoppelstellung.

A ride on the partial transmission 46 can be realized that the coupling element 98 is activated or is. For this purpose, or the sliding sleeve 104 is moved into its coupling position. In order to realize a boost as a parallel hybrid, the coupling element 112 activated by the coupling part 124 is moved from the release position to the closed position. When driving over the partial transmission 46 can thereby Boost or a boost operation via the partial transmission 44 can be realized, in particular, while the sliding sleeve 104 is in its coupling position, the coupling element 110 activated, that is, the coupling member 122 is moved from its release position to its closed position.

A speed adjustment by means of the planetary gear set 16 can be realized by the coupling element 112 activated, that is, the coupling part 124 is moved in the closed position, in particular while the sliding sleeve 96 in its Entkoppelstellung, the coupling part 122 in its release position and the sliding sleeve 104 is in its Entkoppelstellung.

In the following example, the speed of the respective sun gear 80 respectively 86 denoted by n _S. The speed n _S results in: $$n_S=n_{St}+i_0\left(n_H-n_{St}\right)$$

Where: n _{St is} the speed of the planetary carrier 90 (Bridge), i ₀ the respective stand ratio and n _H the speed of the respective ring gear 78 respectively 84 ,

Furthermore, this results from the respective sun gear 80 respectively 86 deployable torque M _S to: $$M_S=-\frac{M_H}{i_0}$$

M _H denotes that of the respective ring gear 78 respectively 84 provided torque.

Finally, the respective power P _{S of} the respective sun gear results 80 respectively 86 to: $$P_S~-M_H\left(n_{St}\left(\frac{1}{i_0}-1\right)+n_H\right)mit{i}_0<0$$

2 shows a Kutzbach plan of the planetary gear 12 in a first operating state, wherein 3 a Kutzbach plan of the planetary gear 12 in a different from the first operating state second operating state shows. In the respective Kutzbach plan illustrates a straight line 126 the electric drive unit 34 , a straight 128 the internal combustion engine 28 and a respective straight line 130 the respective ring gear 78 respectively 84 , Thus, the respective straight line illustrates 126 the respective sun wheel 80 respectively 86 , where the respective straight line 128 the planet carrier 90 illustrated. The respective ring gear 78 respectively 84 thus provides a respective output of the planetary gear 12 represents.

Overall is off 1 recognizable that, for example, starting from a conventional dual-clutch transmission with two clutches designed in particular as friction clutches clutches by the planetary gear sets 14 and 16 and the electric drive unit 34 can be substituted. As a result, the conventional dual-clutch transmission can be designed as DHT. As a result, in particular a module strategy can be realized, since both the conventional dual-clutch transmission and the DHT can be realized with the same wheelset. In particular, in the hybrid powertrain 10 a CVT operation can be realized, so that a transmission can be represented with stepless transmission. In addition, can be dispensed with the realization of an explicit reverse gear, as for example, a reverse drive by the electric drive unit 34 and in particular by a corresponding direction of rotation of the rotor 40 can be realized. Furthermore, a power transmission over two gears is possible, one of the planetary gear sets 14 and 16 is locked and a torque on the other planetary gear 16 or 14 via the electric drive unit 34 is transmitted. As a result, higher input torques can be realized with a given wheelset than with conventional transmissions.

A pure electric drive could be realized, for example, by reference to a torque flow from the output shaft (crankshaft 32 ) On the input shaft 18 and vice versa a starting element such as a clutch between the crankshaft 32 and the input shaft 18 is arranged.

4 shows a second embodiment in which compared to the first embodiment, an actuation of the coupling elements 110 and 112 preferably designed as a jaw clutches can be simplified. In the first embodiment, both the coupling element 76 as well as the coupling element 110 on the website 106 arranged while both the coupling element 98 as well as the coupling element 112 on the side 108 are arranged. At the in 4 illustrated second embodiment is the coupling element 76 on the website 106 arranged while the coupling element 98 on the website 108 is arranged. In the second embodiment, the coupling part takes over 120 also the function of the coupling part 118, wherein the coupling part 124 also the function of the coupling part 122 takes over. The coupling part 124 is thus displaceable between two different closed positions.

In a first of the closed positions are the coupling parts 116 and 120 via the coupling part 124 positively connected rotationally fixed to each other, so that the electric drive unit 34, in particular the rotor 40 , about the coupling parts 116 . 120 and 124 positive locking against rotation with the input shaft 22 connected is. In this case, the electric drive unit 34 of the input shaft 20 decoupled. In the second closed position, however, are the coupling parts 120 and 114 over the coupling part 124 positively connected rotationally fixed to each other, so then the electric drive unit 34 over the coupling parts 114, 124 and 120 form-fitting rotationally fixed to the input shaft 20 is connected while the input shaft 22 from the electric drive unit 34 is decoupled. Thus, in the second embodiment, the coupling part 114 arranged on the side 108, while in the first embodiment, the coupling part 114 on the website 106 is arranged. In other words, the coupling parts used in the first embodiment are 122 and 124 in the second embodiment, to the coupling part 124 united so that the coupling part 124 associated with both coupling elements 110 and 112. As a result, the number of parts and the weight and the cost can be kept low.

By means of the hybrid powertrain 10 can be easily electrified a conventional dual-clutch transmission modular, so that, for example, an electric double clutch can be displayed. Here, a conventional double clutch by the electric drive unit 34 , the planetary gear sets 14 and 16 and the coupling elements 110 and 112 are replaced. The electrical double clutch created in this way enables the "start-up" and "speed adaptation during switching" functions to be taken over. The hybrid powertrain 10 allows a ride with fixed gears or in the manner of a continuously variable transmission. While driving in fixed gears, the functionality of a parallel hybrid can be displayed, with the complete installed power of the electric drive unit 34 is available for boosting.

5 shows a third embodiment, in which compared to the first and second embodiment, different speed and torque ratios can be displayed. In the third embodiment, the respective planetary gear set 14 respectively 16 designed as a plus planetary gear set. In this case, the first planetary gear 14, the planetary gears 82 as the first planet gears, which mesh with the ring gear 78. Furthermore, the planetary gearset 14 second planet wheels 132 on, which with the planet wheels 82 and the sun wheel 80 comb. The planetary gear set 16 assigns the planet wheels 88 as a third planet gears and other planetary gears 134 as fourth planet gears on. The planetary gears mesh 88 with the ring gear 84 and with the planet wheels 134 , which with the planet wheels 88 and the sun wheel 86 comb. Here are both the planet gears 82 as well as the planet wheels 88 . 132 and 134 at the planet carrier 90 (Bridge) rotatably mounted.

Finally shows 6 a fourth embodiment in which the electric drive unit 34, the electric machine 36 and a second electric machine provided in addition to the electric machine 36 136 includes. The previous and following versions of the electric machine 36 can easily on the electric machine 136 be transferred and vice versa. By using the two respective electrical machines 36 and 136 can on the designed as jaw couplings coupling elements 110 and 112 be waived. In this case, for example, the rotor 40 the electric machine 36 arranged directly on the input shaft 20 and in particular permanently or permanently against rotation with the input shaft 20 connected. The electric machine 136 has a stator 138 and a rotor 140 which is about the aforementioned axis of rotation relative to the stator 138 is rotatable. In this case, for example, the rotor 140 arranged directly on the input shaft 22 and in particular permanently or permanently against rotation with the input shaft 22 connected. By using the two electric machines 36 and 136, for example, a battery-neutral energy balance can be realized.

QUOTES INCLUDE IN THE DESCRIPTION

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Cited patent literature

• DE 102007043173 A1 [0002]

Claims (10)

Hybrid powertrain (10) for a motor vehicle, comprising at least one planetary gear (12), a first planetary gear set (14), a second planetary gear set (16), a first input shaft (18), a second input shaft (20), a third input shaft (22 ), a first output shaft (24) and a second output shaft (26), with at least one internal combustion engine (28), the output shaft (32) rotatably connected to the first input shaft (18) is connected to an electric drive unit (34) by means of which the second input shaft (20) and the third input shaft (22) are drivable, with a first partial transmission (44) which is drivable by the first output shaft (24), and with a second partial transmission (46), which from the second output shaft (26) is drivable, characterized in that at least one coupling element (76) for blocking the first planetary gear set (14) is provided. Hybrid powertrain (10) after Claim 1 , characterized in that at least one second coupling element (98) for blocking the second planetary gear set (16) is provided. Hybrid powertrain (10) after Claim 2 , characterized in that the first coupling element (76) on a first side (106) of the electric drive unit (34) and the second coupling element (98) on one of the first side (106) in the axial direction of the electric drive unit (34) facing away from the second Side (108) of the electric drive unit (34) is arranged. Hybrid powertrain (10) after Claim 2 or 3 , characterized in that at least one rotor element (40) of the electric drive unit (34) in the axial direction between the coupling elements (76, 98) is arranged. Hybrid drive train according to one of the preceding claims, characterized in that the electric drive unit (34) comprises a first electric machine (36) by means of which the second input shaft (20) is drivable, and a second electric machine (136), by means of which the third Input shaft (22) is driven. Hybrid drive train (10) according to any one of the preceding claims, characterized in that a first coupling element (110) by means of which the electric drive unit (34) with the second input shaft (20) is coupled, and a second coupling element (112) is provided by means of in which the electric drive unit (34) can be coupled to the third input shaft (22), Hybrid powertrain (10) after Claim 6 , characterized in that the first coupling element (110) on a first side (106) of the electric drive unit (34) and the second coupling element (112) on one of the first side (106) in the axial direction of the electric drive unit (34) facing away from the second Side (108) of the electric drive unit (34) is arranged. Hybrid powertrain (10) after Claim 6 , characterized in that the coupling elements (110, 112) in the axial direction of the electric drive unit (34) on the same side (108) of the electric drive unit (34) are arranged. Hybrid drive train (10) according to one of the preceding claims, characterized in that the first planetary gear (14) first planetary gears (82) and with the first planetary gears (82) meshing second planet gears (132) and the second planetary gear set (16) third planetary gears (88 ) and with the third planet gears (88) meshing fourth planet gears (134). Hybrid drive train (10) according to any one of the preceding claims, characterized in that - the first planetary gear set (14) rotatably connected to the first output shaft (24) first ring gear (78), a non-rotatably connected to the second input shaft (20) first sun gear ( 80) and planet wheels (82); - The second planetary gear set (16) a rotatably connected to the second output shaft (26) second ring gear (84), a non-rotatably connected to the third input shaft (22) second sun gear (86) and planet gears (88); a planet carrier (90) which is connected to the planetary gearsets (82) of the first planetary gear set (14) and the planet wheels (88) of the second planetary gear set (14) is provided in common with the first input shaft (18). 16) are rotatably mounted; and - for blocking the first planetary gear set (14) of the planet carrier (90) by means of the coupling element (76) with the first sun gear (80) rotatably connected.

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