Hybrid transmission layout and hybrid powertrain

Abstract

Hybrid transmission arrangement (10) for a motor vehicle (30), with - a transmission (11) having a first input (14) connectable to an internal combustion engine (VM), a second output (22), a third output (23) and at least one planetary gear set (PS1, PS2), - a third planetary gear set (PS3) having a first member (S3;H3'), a second member (H3;S3') and a third member (P3;P3'), which can be locked by means of a first switching element (E) and which is arranged coaxially to a first axis (A1), and - a first electric machine (EM1), - wherein the first element (S3; H3') is connected to the first electric machine (EM1), - wherein the second member (H3; S3') is connected to the second output (22) of the transmission (11), - wherein the third output (23) of the transmission (11) is connected to the first member (S3; H3'), and - wherein the third member (P3; P3') is connected to an output (Ab) of the hybrid transmission arrangement (10), characterized in that the first electric machine (EM1) is arranged offset axially parallel to the first axis (A1) and is connected to the first member (S3; H3') of the third planetary gear set (PS3) via a spur gear set (26) or via a traction means.

Description

[0001] The present invention relates to a hybrid transmission arrangement for a motor vehicle, which has a transmission with a plurality of planetary gear sets and a first electric machine.

[0002] Furthermore, the present invention relates to a hybrid drive train for a motor vehicle having a hybrid transmission arrangement.

[0003] Hybrid powertrains for motor vehicles generally comprise an internal combustion engine that can provide drive power to drive the motor vehicle, as well as an electric motor that, depending on the operating mode, can provide drive power for the motor vehicle alternatively or in addition to the internal combustion engine.

[0004] In hybrid powertrains, a distinction is made between a variety of different concepts, each of which provides a different connection of the electric motor to a transmission arrangement of the hybrid powertrain.

[0005] For example, it is known to arrange an electric machine concentrically to an input shaft, wherein a rotor of the electric machine is connected to a hollow shaft arranged around an input shaft.

[0006] In some cases, the electric motor is connected to a gear arrangement of the hybrid transmission via a pre-transmission gear. The pre-transmission gear arrangement may include a planetary gear set.

[0007] Document DE 10 2013 215 114 A1 discloses a hybrid drive for a motor vehicle in which an electric motor can be connected to an output shaft of a hybrid transmission via a spur gear set. Furthermore, this document discloses arranging an electric motor coaxially with a transmission output shaft, axially offset from a planetary gear set designed as a superposition gear for electric motor drive power and combustion engine drive power.

[0008] Furthermore, US 2007 / 0 298 924 A1 discloses a transmission with a first, second and third planetary gear set, a battery, two electric machines that can be operated as a motor or generator, and at least five torque transmission devices.

[0009] Hybrid transmissions are preferably designed as powershift transmissions. When installed in a motor vehicle transversely to the drive direction (front transverse or rear transverse), the axial length of the hybrid transmission is of great importance. Furthermore, when installed transversely to the direction of travel, the installation environment often has to be considered. Constricted points may include a side shaft joint, a transmission mount, and / or a lower vehicle longitudinal member.

[0010] Against this background, it is an object of the present invention to provide an improved hybrid transmission arrangement and an improved hybrid drive train for a motor vehicle, wherein the hybrid transmission arrangement is compact and / or has a wide range of functions and can preferably be easily installed transversely in a motor vehicle.

[0011] The above object is achieved by a hybrid transmission arrangement for a motor vehicle, comprising a transmission having a first input which can be connected to an internal combustion engine, a second output, a third output and at least one planetary gear set, comprising a third planetary gear set which has a first member, a second member and a third member which can be blocked by means of a first switching element and which is arranged coaxially to a first axis, and comprising a first electric machine, wherein the first member is connected to the first electric machine, and wherein the second member is connected to the second output of the transmission, wherein the third output of the transmission is connected to the first member and wherein the third member is connected to an output of the hybrid transmission arrangement.

[0012] In more general form, the object is achieved by a hybrid transmission arrangement for a motor vehicle with a transmission which has a first input, two outputs and at least one first planetary gear set, preferably two planetary gear sets, and which can preferably set up 3 to 5, in particular 4 gear stages.

[0013] Furthermore, the above object is achieved by a hybrid drive train for a motor vehicle having a first axle and a second axle, with a hybrid transmission arrangement of the type according to the invention for driving the first axle and preferably with an electric axle drive for driving the second axle.

[0014] The hybrid transmission arrangement enables a radially compact design. The transmission is preferably implemented using planetary gear sets. The hybrid transmission arrangement can preferably be implemented without spur gear stages.

[0015] The hybrid transmission arrangement enables the superposition of combustion engine power and electric motor power provided by the first electric motor. Furthermore, purely electric motor operation is possible, preferably in at least one electric gear.

[0016] The hybrid transmission arrangement allows at least two, preferably exactly four, combustion engine gear stages to be set up, as well as at least one, preferably exactly two electric gear stages.

[0017] In the third planetary gear set, the combustion engine and electric motor power can be superimposed. The third planetary gear set can be used as an electrodynamic starting element (EDA). This involves a superposition of the combustion engine speed, the speed of the first electric motor, and the speed of the output. The first electric motor can then support a torque. Consequently, starting from a standstill with the combustion engine running is possible.

[0018] The hybrid transmission arrangement enables traction assistance in hybrid mode via the first electric motor. In particular, it is possible to perform so-called "output-assisted" gear shifts, in which the first electric motor is connected to the output with a fixed gear ratio and supports the traction solely with the electric motor. Meanwhile, the combustion engine can perform load-free gear shifts in the background, similar to an automated manual transmission.

[0019] The hybrid transmission arrangement can be implemented without conventional powershift elements (brakes and friction clutches). Instead, all shifting elements can be implemented, preferably as claw clutches, i.e., as purely positive-locking shifting elements.

[0020] In addition, the hybrid transmission arrangement enables a number of other hybrid functions, such as combustion engine start (particularly using a high-voltage starter generator), load point shifting and recuperation.

[0021] In a preferred embodiment, the internal combustion engine and the first electric motor can be connected to each other without blocking the third planetary gear set. Charging in neutral can be realized, with the internal combustion engine driving the first electric motor as a generator.

[0022] Furthermore, good overall gear efficiency can be achieved, both in combustion engine and electric mode. Furthermore, transmission losses are low because claw shift elements can be used. A good gear ratio range can also be achieved. The hybrid transmission arrangement can also be designed so that the shift elements are easily accessible from the actuators.

[0023] The hybrid transmission arrangement is preferably implemented as a group transmission with two transmission groups connected in series and a downstream EDA planetary gear set, which can be blocked via the first switching element.

[0024] Despite a radially compact design, the hybrid transmission arrangement can be realized with few radial planes, so that an axially comparatively compact design is also possible.

[0025] Preferably, the hybrid transmission arrangement further includes at least one second electric machine, which is preferably designed in the manner of a high-voltage starter generator (HVSG) and is connected to the input of the first transmission group.

[0026] The number of actuating devices for actuating shift elements of the hybrid transmission arrangement is preferably exactly three or four, in addition to an actuating device for a separating clutch, if one is provided.

[0027] The hybrid transmission arrangement is preferably installed transversely in a motor vehicle, preferably transversely at the front.

[0028] A hybrid drivetrain for a motor vehicle having a first and a second axle is preferably equipped with such a hybrid transmission arrangement for driving the first axle. It is particularly preferred if an electric axle drive is provided on the second axle for driving the second axle. In this case, the drivetrain preferably has at least two electric motors for driving the vehicle. It is particularly preferred if the at least two electric motors of the drivetrain are powered by a common battery of the motor vehicle. Preferably, at least one of the electric motors is also configured to charge the battery in generator mode.

[0029] Reversing is preferably carried out exclusively by electric motor. A mechanical reverse gear is therefore preferably not provided.

[0030] The following terms can be understood in the context of this disclosure in particular as follows: A gear pair comprises exactly two gears that mesh with each other, in particular, mesh with each other. The gears of a gear pair preferably each have spur gearing, are preferably arranged in a radial plane, and are preferably each assigned to a different shaft. The gears of the gear pair can be two fixed gears (a so-called constant gear set). In a shiftable gear pair, the two gears can be a fixed gear and an idler gear (see below), which preferably together define a gear stage (see below).

[0031] A gear set (spur gear set) comprises at least two meshing (especially intermeshing) gears and can include one or more gear pairs, preferably located in a common radial gear set plane. If a gear set has a fixed gear that meshes with two different gears, this is also referred to as dual-use. In general, a gear set can also be a planetary gear set.

[0032] An idler gear is a gear mounted on a shaft for rotation. It can be connected to or disconnected from the shaft by means of a switching element. A fixed gear is a gear fixed to a shaft for rotational stability.

[0033] A shifting element (or clutch) serves to connect or release elements, such as an idler gear and a shaft, or a shaft and a housing, and is particularly formed by a shifting clutch, in particular a positive-locking shifting clutch such as a dog clutch. However, the shifting element can also be a friction clutch or a positive-locking synchronous shifting clutch. The term "shifting element" is synonymous with the term "clutch."

[0034] A double switching element includes two switching elements, which are preferably assigned to different members and which can be switched alternatively by means of a single actuating device. Furthermore, the double switching element preferably includes a neutral position in which neither of the two switching elements is switched.

[0035] Two relatively rotatable elements are connected if they necessarily rotate at a proportional speed. The term "connected" is synonymous with "operably connected." A "rotationally fixed connection" means that the two elements rotate at the same speed. Two elements are connectable if they can either be connected to each other or decoupled from each other. Preferably, the two elements can be connected to each other by means of a switching element (e.g., a clutch or a brake).

[0036] Two elements are axially aligned if they at least partially overlap in the axial direction and / or if they lie in a common radial plane. The term "radial plane" should preferably be understood functionally rather than geometrically. Consequently, two switching elements of a double switching element can also lie in a common radial plane.

[0037] A planetary gear set is interlockable if two of its members can be connected by means of a shifting element, but in this case, this also includes if one of the members can be fixed relative to a housing by means of a shifting element. Interlocking thus establishes a fixed gear ratio for the planetary gear set.

[0038] A combustion engine gear enables purely combustion engine operation, but also always allows for electric motor power to be superimposed on the combustion engine drive power. For "boost" operation, positive electric motor power is superimposed. For recuperation operation, negative electric motor power is superimposed. Combustion engine gears can therefore also be referred to as hybrid gears, and vice versa.

[0039] An electric gear enables purely electric motor operation.

[0040] The problem is thus completely solved.

[0041] In general, the transmission, which can preferably provide three to five, in particular exactly four gear stages, can be implemented as a spur gear transmission or by means of planetary gear sets coupled to one another.

[0042] Preferably, however, the transmission is designed with a first transmission group having the first input, a first output and a first planetary gear set, with a second transmission group having a second input, the second output, the third output and a second planetary gear set, wherein the second input of the second transmission group is connected to the first output of the first transmission group.

[0043] The first transmission group and / or the second transmission group each include at least one planetary gear set, preferably exactly one planetary gear set. The first transmission group and / or the second transmission group preferably do not include a spur gear set. The first transmission group and the second transmission group are each arranged on a single axis. However, the axes of the two transmission groups can be different. The first transmission group is preferably arranged coaxially with a drive shaft of an internal combustion engine. The second transmission group is preferably arranged coaxially with a differential of the output, preferably around one of the output shafts of the differential. Accordingly, the hybrid transmission arrangement can be arranged on essentially two axes, thus enabling a radially compact design.

[0044] According to a preferred embodiment, the first transmission group has two shifting elements coupled to the first planetary gear set and the first input and the first output in such a way that two different gear ratios can be set between the first input and the first output. Alternatively or additionally, the second transmission group has two shifting elements coupled to the second planetary gear set and the second input and the second output and to the third output in such a way that two different gear ratios can be set between the second input and the second output, on the one hand, and between the second input and the third output, on the other hand.

[0045] The coupling of the shifting elements can be implemented, for example, such that both shifting elements of a transmission group are connected to the respective input. Furthermore, one of the shifting elements can be connected to a member of the planetary gear set of the transmission group that is connected to the second or third output. The other shifting element can preferably be connected to the other output of the respective transmission group.

[0046] Consequently, it is possible to set up two different gear ratios in each transmission group using two shift elements and a planetary gear set.

[0047] Each gear group can therefore be designed both radially and compactly.

[0048] It is particularly preferred if the two shifting elements of the first transmission group are connected to the first planetary gear set and the first input and the first output in such a way that one of the two gear ratios between the first input and the first output is a direct gear ratio and the other gear ratio is greater than 1 or less than 1.

[0049] In a corresponding manner, alternatively or additionally, it is preferred if the two shifting elements of the second transmission group are connected to the second planetary gear set and the second input and the second output and the third output in such a way that one of the two gear ratios between the second input and the second output or the third output is a direct gear ratio and the other gear ratio is greater than 1 or less than 1.

[0050] In both cases, one of the shift elements is designed to directly connect the respective input and output of the transmission group. This establishes the respective direct ratio (i = 1), essentially bypassing the associated planetary gear set.

[0051] The other shift element preferably connects the input of the respective transmission group to a member of the respective planetary gear set. By selecting which member of the associated planetary gear set the shift element is connected to, either a gear ratio greater than 1 or a gear ratio less than 1 can be set.

[0052] In a preferred variant for establishing a gear ratio greater than 1 (corresponding to a short gear), the respective shifting element of the transmission group can be connected on the input side to the respective input of the transmission group and on the output side to a ring gear of the respective planetary gear set. In this case, for example, the planet carrier of the respective planetary gear set can be connected to an output of the respective transmission group. In this case, a sun gear of the respective planetary gear set can also be connected to a housing.

[0053] If, on the other hand, a gear ratio less than 1 (corresponding to a longer gear) is to be realized in addition to the direct transmission, the output element of the associated shifting element can be connected, for example, to the planet carrier of the planetary gear set of the transmission group, in which case the ring gear of this planetary gear set is connected to an output of the transmission group. In this case, too, it is preferred if the sun gear is connected to a housing.

[0054] In a first variant, it is possible to set up a ratio greater than 1 in both transmission groups in addition to the direct ratio. It is also possible to set up a ratio less than 1 in each of the two transmission groups in addition to the direct ratio. It is also possible to set up a ratio greater than 1 in one transmission group in addition to the direct ratio and a ratio less than 1 in the other transmission group.

[0055] Furthermore, it is advantageous if the two shifting elements of the first transmission group are formed by a first double shifting element which is arranged coaxially to the first planetary gear set, and / or if the two shifting elements of the second transmission group are formed by a second double shifting element which is arranged coaxially to the second planetary gear set.

[0056] The first transmission group can therefore implement two different gear ratios using a single actuating device. Similarly, the second transmission group can implement two different gear ratios using a single actuating device. In conjunction with an actuating device for actuating the first shifting element, by means of which the third planetary gear set can be locked, the hybrid transmission arrangement can thus be implemented with three actuating devices.

[0057] In particular, if at least the double shift element of the second transmission group also allows a neutral position, a purely electric motor driving operation can be set up with the transmission groups completely decoupled.

[0058] Preferably, a neutral position can also be established in the double shift element in the first transmission group. In this case, it is possible, for example, to start an internal combustion engine using a high-voltage starter generator connected to the input of the first transmission group, without having to drag elements of the transmission groups along.

[0059] According to a further overall preferred embodiment, the second gear group is arranged coaxially with the first axis, i.e., coaxially with the third planetary gear set. The second gear group is preferably arranged coaxially with a second axis, which is offset axially parallel to the first axis.

[0060] The second axis is preferably coaxial with an axis of an internal combustion engine when the hybrid transmission assembly is installed in a motor vehicle.

[0061] Consequently, the hybrid transmission arrangement can be realized with only two axles, with additional axles being provided for the first electric machine (in the case of an axis-parallel arrangement) and / or for the second electric machine (high-voltage starter generator) if necessary.

[0062] Overall, it is particularly advantageous if the output has a differential gear that is arranged coaxially to the first axle.

[0063] In this embodiment, the third planetary gear set and the second gear group are preferably arranged coaxially with the differential and are preferably arranged around one of the output shafts of the differential. In other words, an output shaft for transmitting drive power from the differential to one of the driven wheels of the motor vehicle extends axially through the third planetary gear set and through the second gear group.

[0064] This enables a particularly compact design.

[0065] According to a further preferred embodiment, the output between the third member of the third planetary gear set and a differential gear has a gear set with a constant gear ratio.

[0066] The gear set can generally be a spur gear set. It is particularly preferred if the gear set is a planetary gear set, which has a member that is fixed to a housing and thus establishes a constant gear ratio.

[0067] The gear set is functionally arranged between the third planetary gear set and the differential. It is particularly preferred if the gear set is also structurally arranged axially between the third planetary gear set and the differential. This results in a particularly advantageous arrangement coaxial with the first axis.

[0068] In general, the first electric machine can be arranged coaxially to the first axis.

[0069] According to the invention, the first electric machine is arranged offset axially parallel to the first axis and is connected to the first member of the third planetary gear set via a spur gear set or via a traction means.

[0070] The spur gear set can, for example, include a gear connected to a shaft of the first electric machine, a fixed gear connected in a rotationally fixed manner to the first member of the third planetary gear set, and optionally an intermediate gear arranged between these gears in order to establish a gear ratio adjustment.

[0071] In this embodiment, the first electric machine preferably overlaps with the second gear group in the axial direction.

[0072] Purely electric drive is possible by closing the first shift element, as this locks the third planetary gear set and allows a purely electric drive via the first electric motor. This allows exactly one electric gear to be set up.

[0073] Preferably, a member of the third planetary gear set can be connected to a housing via a second switching element.

[0074] This measure makes it possible to set up an additional electric gear stage, in particular a shorter electric gear stage, which is suitable, for example, for electric motor reversing.

[0075] It is particularly preferred if the second shifting element is designed to connect the second output of the second transmission group and consequently the second member of the third planetary gear set to the housing.

[0076] According to a further preferred embodiment, a second electric machine is connected to the first input of the first transmission group.

[0077] The second electric machine, as mentioned above, is preferably a high-voltage starter generator and serves, for example, to start a connected combustion engine. However, the second electric machine can also be used for recuperative purposes, for example, to shift a load point. Charging in neutral using the second electric machine is generally also possible. However, the rated power of the second electric machine is preferably significantly lower than the rated power of the first electric machine, preferably less than half the rated power of the first electric machine.

[0078] The first input of the transmission can be connected in a rotationally fixed manner to a drive shaft of the combustion engine.

[0079] In a particular embodiment, however, the first input of the transmission is connected to an output member of a separating clutch, the input member of which can be connected to a drive shaft of the internal combustion engine.

[0080] The separating clutch is preferably also designed as a dog clutch. The separating clutch enables the internal combustion engine to be decoupled from the hybrid transmission assembly.

[0081] It is understood that in all cases, an element for decoupling torsional vibrations can be arranged between the first input of the transmission and the drive shaft of the combustion engine, for example a torsional damper, a dual-mass flywheel, etc.

[0082] The inputs and outputs of the first and second transmission groups are preferably realized by shafts, wherein it is preferred if the first input is a first input shaft of the first transmission group, and / or if the first output is a first output shaft of the first transmission group and / or if the second input is a second input shaft of the second transmission group and / or if the second output is a second output shaft of the second transmission group.

[0083] The first input shaft and the first output shaft are preferably arranged coaxially with the second axis. The second input shaft and the second output shaft are preferably arranged coaxially with the first axis.

[0084] As mentioned at the beginning, the first and second gear groups can be arranged coaxially to each other.

[0085] However, it is particularly preferred if the first output shaft and the second input shaft are arranged offset parallel to the axis and are connected to one another via a spur gear set or a traction means.

[0086] This makes it possible to arrange the first gear group coaxially to the first axis and the second gear group coaxially to the second axis.

[0087] Furthermore, it is advantageous if the first planetary gear set and / or the second planetary gear set establishes a fixed gear ratio.

[0088] Alternatively or additionally, it is advantageous if the first planetary gear set and the second planetary gear set axially overlap with each other.

[0089] In particular, the first planetary gear set and the second planetary gear set can be arranged in a common radial plane.

[0090] The spur gear set (or traction means) connecting the first output shaft and the second input shaft can be arranged in a further radial plane axially adjacent to this radial plane.

[0091] The internal combustion engine is preferably arranged on one axial side of these radial planes. The third planetary gear set is preferably arranged on an opposite axial side of these radial planes.

[0092] It is understood that the features mentioned above and those to be explained below can be used not only in the combination specified in each case, but also in other combinations or on their own, without departing from the scope of the present invention.

[0093] Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description. They show: Fig. 1 is a schematic representation of an embodiment of a hybrid transmission arrangement; Fig. 2 a shift table for the hybrid transmission arrangement of the Fig. 1; Fig. 3 is a schematic diagram of a vehicle with a hybrid powertrain; Fig. 4 is a schematic representation of another embodiment of a hybrid transmission arrangement; Fig. 5 is a schematic representation of another embodiment of a hybrid transmission arrangement; Fig. 6 a modification of the gear arrangement of the Fig. 1 for setting up a second electric gear stage; Fig. 7 a modification of the hybrid transmission arrangement of the Fig. 6; Fig. 8 shows a further embodiment of a hybrid transmission arrangement; Fig. 9 shows another embodiment of a hybrid transmission arrangement; Fig. 10 shows another embodiment of a hybrid transmission arrangement; Fig. 11 is a schematic representation of a transmission group for a hybrid transmission arrangement; and Fig. 12 is a schematic representation of an alternative transmission group for a hybrid transmission arrangement.

[0094] In Fig. 1 shows a first embodiment of a hybrid transmission arrangement for a motor vehicle in schematic form and is generally designated 10.

[0095] The hybrid transmission arrangement 10 comprises a transmission 11 with a first transmission group 12 and a second transmission group 18. The transmission 11 or the first transmission group 12 comprises a first input shaft 14 which is connected to a drive shaft An of an internal combustion engine (in Fig. 1 not shown). Furthermore, the first transmission group 12 has a first output shaft 16.

[0096] The second transmission group 18 has a second input shaft 20 connected to the first output shaft 16. Furthermore, the transmission 11 or the second transmission group 14 has a second output shaft 22 and a third output shaft 23.

[0097] The first transmission group 10 includes at least one first planetary gear set PS1 and at least one, preferably two, shifting elements A, B, which are coupled to the first planetary gear set PS1, the first input shaft 14 and the first output shaft 16 in order to establish at least two different gear ratios by means of the first transmission group 12.

[0098] Correspondingly, the second transmission group 18 includes a second planetary gear set PS2 and one or two shifting elements C, D. The shifting element(s) is / are connected to the second planetary gear set PS2 and to the second input shaft 20, the second output shaft 22, and the third output shaft 23 in such a way that two different gear ratios can be set up by means of the second transmission group 18. In particular, the second transmission group 18 is designed such that when one of the shifting elements C, D is shifted (e.g., C), drive power is supplied to one of the second output shaft 22 and the third output shaft 23 (e.g., 22). When the other of the shifting elements C, D is shifted (e.g., D), in this embodiment, drive power is supplied to the other of the second output shaft 22 and the third output shaft 23 (e.g., 23).

[0099] By providing the second and third output shafts 22, 23, it is therefore possible, on the one hand, to use one of the shifting elements (e.g., C) of the second transmission group 18 to feed engine power and electromotive power into different members of the third planetary gear set PS3 in order to establish an EDA mode, which is described below. On the other hand, it is also possible to use the other shifting element (e.g., D) of the second transmission group 18 to feed engine power and electromotive power into the same member of the third planetary gear set PS3 in order to establish a LiN mode, which is described below.

[0100] The transmission 11, with the first gear group 12 and the second gear group 18, is thus designed to provide four different gear ratios. In this case, the transmission 11 is formed by the two gear groups 12, 18 with respective planetary gear sets PS1, PS2, but can also be formed by a spur gear or a type of transmission with four different gear ratios.

[0101] The hybrid transmission assembly 10 further includes a third planetary gear set PS3, which includes a sun gear S3, a ring gear H3, and a planet carrier P3. The ring gear H3 is connected, preferably non-rotatably, to the second output shaft 22. The planet carrier P3 is connected to an output Ab of the hybrid transmission assembly 10.

[0102] The hybrid transmission assembly 10 further includes a third input shaft 24, which is preferably arranged as a hollow shaft section around the second output shaft 22. The third input shaft 24 is connected, in particular rotationally fixed, to the third output shaft 23. The third input shaft 24 is connected via a spur gear set 26 to a first electric machine EM1, which is arranged axially parallel to the third input shaft 24 and offset from the second transmission group 18, preferably overlapping in the axial direction.

[0103] The third input shaft 24, and consequently also the third output shaft 23, is connected to the sun gear S3, in particular connected in a rotationally fixed manner.

[0104] The third input shaft 24 can also be connected to the third planetary carrier P3 via a first switching element E in order to block the third planetary gear set PS3.

[0105] Fig. 2 shows a shift table for the hybrid transmission arrangement 10 of the Fig. 1. In Fig. 2, closed switching elements are marked with an "x." Open switching elements are marked with empty table entries.

[0106] As it turns out Fig. 2, the hybrid transmission arrangement allows for four hybrid gear stages H1-H4. In these hybrid gear stages, purely combustion engine operation is possible, but superimposing electric motor power using the first electric motor EM1 is also possible.

[0107] In all four hybrid gears H1-H4, the first shift element E is closed, so that the third planetary gear set PS3 is locked. The first electric motor EM1 is thus directly connected to the output Ab.

[0108] In the first hybrid gear stage H1, a shift element A is engaged in the first transmission group 12 and a shift element C is engaged in the second transmission group 18. In the second hybrid gear stage H2, the shift element A is engaged in the first transmission group 12 and a shift element D is engaged in the second transmission group 18.

[0109] In the third hybrid gear stage, a shift element B and the shift element C are closed in the first transmission group 12. In the fourth hybrid gear stage, the shift element B is closed in the first transmission group 12 and the shift element D is closed in the second transmission group 18.

[0110] Furthermore, a single electric gear stage E2 can be set up with the hybrid transmission arrangement 10, namely by closing the switching element E and by opening all switching elements AD.

[0111] In addition, two different EDA modes can be set up using the hybrid transmission arrangement, namely EDA1 and EDA2.

[0112] In all of these EDA modes, the first shift element E remains open. Consequently, combustion engine drive power is fed via transmission groups 12 and 18 into the ring gear H3 of the third planetary gear set PS3 (in the EDA Classic mode) or into the sun gear S3' of the third planetary gear set PS3'. Torque can be "electrically" supported via the sun gear S3 or the ring gear H3', enabling an "EDA" start. From the first EDA mode EDA1, the first shift element E can then be engaged to shift into the hybrid gear H1, since shift elements A and C remain engaged and shift elements B and D remain engaged.

[0113] Accordingly, a change from the EDA mode EDA2 to the hybrid gear H3 is possible by closing the first switching element E. The switching elements B, C remain closed, and the switching elements A, D remain open.

[0114] As mentioned above, purely electric driving can be achieved by closing the first shift element E and opening the other shift elements. Starting from this, any hybrid gear ratio can be set by closing two shift elements in each of the two transmission groups, in which additional combustion engine power is transferred to the output.

[0115] Gear shifts with traction assistance are possible between the hybrid gear ratios. In all cases, traction assistance is preferably provided by supporting the downforce with the first electric motor EM1.

[0116] For example, a load shift from H1 to H2 in hybrid mode, starting from closed switching elements A, C, and E, occurs as follows. First, a load reduction occurs at switching element C and a simultaneous load buildup at the first electric machine EM1. Subsequently, switching element C can be opened. The speed of the combustion engine is reduced so that switching element D becomes synchronous. For this purpose, a second electric machine in the form of a high-voltage starter generator, which is connected to the first input shaft 14, can operate as a generator, for example. This is the preferred variant. Alternatively, if such a second electric machine is not available, the combustion engine can go into overrun mode.

[0117] Switching element B can then be inserted. Switching elements A and E remain closed during switching.

[0118] After the switching element C is opened, the electric motor EM1 supports the pulling force completely on its own until the switching element D is closed.

[0119] Gear shifts to the other gears occur in a similar manner. When shifting from H2 to H3, after the load builds up on the electric motor EM1, the two shift elements A and E are opened, and after shift elements B and C are synchronized, they are closed.

[0120] With the hybrid transmission arrangement 10, according to Fig. 2 Furthermore, two different modes for charging in neutral (LiN1, LiN2) can be set up. In both cases, the first switching element E remains open, and the switching element D is closed in both cases.

[0121] In LiN1, switching elements A, D are closed, and switching elements B, C are open. Therefore, both an internal combustion engine VM (via A and D) and the first electric machine EM1 are connected to the third output shaft 23, and the third planetary gear set PS3 is not blocked. Consequently, the first electric machine EM1 can be driven by the internal combustion engine VM when stationary in order to operate the first electric machine EM1 as a generator and to charge a connected electrical energy storage device (e.g., battery) or to supply electrical consumers. Such a consumer can also be another electric machine, e.g., an electric axle drive on another vehicle axle, as described below.

[0122] In LiN2, switching elements B and D are closed, and switching elements A and C are open. Consequently, the same situation exists as in LiN1, except that the internal combustion engine VM is connected to the third output shaft 23 with a different gear ratio (via B and D instead of A and D).

[0123] From LiN1 mode, you can switch directly to the hybrid gear H2, since the shift elements A and D are closed in both modes. From LiN2 mode, you can switch directly to the hybrid gear H4, since the shift elements B and D are closed in both modes.

[0124] The hybrid transmission assembly 10 thus includes a transmission with two series-connected transmission groups, each configured as a 2-speed transmission. Furthermore, the hybrid transmission assembly includes the downstream EDA planetary gear set PS3, which can be locked via the shift element E.

[0125] Each transmission group is preferably implemented by exactly one planetary gear set and two shifting elements. In each transmission group, one shifting element implements a shorter gear, and one shifting element implements a longer gear. One of the two gears preferably corresponds to a respective direct drive (ratio i = 1.0). The other of the two gears in each transmission group corresponds to either a ratio i > 1.0 or a ratio i < 1.0. The two shifting elements are preferably designed as double shifting elements.

[0126] A fixed gear ratio in the form of a planetary gear set or a spur gear stage can be connected downstream of the third planetary gear set PS3 if necessary. Furthermore, a differential is connected downstream either directly to the third planetary gear set PS3 or to the additional fixed gear ratio, allowing the drive power to be distributed to the vehicle's driven wheels.

[0127] A separating clutch K0 can be connected between the first input shaft 14 and the combustion engine (see e.g. Fig. 5) in order to decouple the internal combustion engine VM from the hybrid transmission arrangement. In all cases, it is preferred if an element for torsional vibration decoupling is provided between the first input shaft 14 and the internal combustion engine VM.

[0128] The hybrid transmission arrangement 10 of the Fig. 1 is preferably installed transversely in a motor vehicle, and preferably transversely at the front. The hybrid transmission arrangement can therefore be used, for example, to implement front-wheel drive or rear-wheel drive of a motor vehicle.

[0129] In Fig. 3 shows an example of a motor vehicle 30 having a first axle 32 and a second axle 34.

[0130] A hybrid transmission arrangement 10 as shown in Fig. 1, is arranged in the region of the first axle 32, specifically in a front / transverse arrangement. Furthermore, an internal combustion engine VM, which is connected to the hybrid transmission arrangement 10, is arranged in the region of the first axle 32. In addition to the transmission groups 12, 18, the hybrid transmission arrangement 10 also includes a differential 40, by means of which drive power can be distributed to the driven wheels of the first axle 32. The differential 40 is preferably arranged coaxially with at least one axle of the transmission 11.

[0131] In the area of ​​the second axle 34, an electric axle drive 36 is optionally arranged, which can include a further electric motor and a mechanical differential or two further electric motors for the driven wheels of the second axle 34.

[0132] The combustion engine VM, the hybrid transmission arrangement 10 and the optional axle drive 36 form a hybrid drive train 38 for the motor vehicle.

[0133] With the Fig. An all-wheel drive system can be implemented using the hybrid drive train 38 shown in Figure 3. For example, a pure front-wheel drive system can be implemented using the combustion engine, the first electric motor EM1, and the hybrid transmission assembly 10. Additional rear-axle drive is possible using the electric axle drive 36.

[0134] Furthermore, a power-split E-CVT driving range is possible for the combustion engine, which also allows battery-neutral operation.

[0135] Furthermore, the electric axle drive 36 can be used to assist the traction force when shifts are necessary in the hybrid transmission arrangement 10, during which the output is unloaded. Such shifts include, for example, initially driving purely electrically using the electric motor EM1 (and possibly EM2) and then starting the combustion engine in neutral using the first electric motor EM1.

[0136] Further hybrid transmission arrangements are described below, which in terms of structure and function are generally similar to the hybrid transmission arrangement of the Fig. 1 and Fig. 2. Identical elements are therefore identified by the same reference numerals. The differences are essentially explained below.

[0137] In Fig. 4 shows a hybrid transmission arrangement 10' which replaces the planetary gear set PS3 of the Fig. 1 has a planetary gear set PS3', which includes a sun gear S3', a ring gear H3' and a planet carrier P3'. The planet carrier P3' is connected to the output Ab. In contrast to the embodiment of the Fig. 1, the ring gear H3' is connected to the third input shaft 24 and consequently to the first electric machine EM1. The sun gear S3' is connected to the second output shaft 22.

[0138] While the connection of the planetary gear set PS3 according to Fig. 1 is called “EDA Classic”, the connection of the planetary gear set PS3' in Fig. 4 can also be called “EDA inverse”.

[0139] The switching table of the Fig. 2 can be applied in the same way to the hybrid transmission arrangement 10' of the Fig. 4. The same applies to the other hybrid transmission arrangements explained below.

[0140] In Fig. 5 shows a hybrid transmission assembly 10" based on the hybrid transmission assembly 10 of the Fig. 1 and Fig. 2 based.

[0141] The hybrid transmission arrangement 10" of the Fig. 5 has a first axis A1 and a second axis A2. The first transmission group 12 is arranged coaxially with the second axis A2. The second axis A2 is also arranged coaxially with a drive shaft An of the internal combustion engine. The drive shaft An is connected to an input member of a separating clutch K0 via a vibration damper ST. The output member of the separating clutch K0 is connected to the first input shaft 14, which is arranged as a hollow shaft section around the drive shaft An. However, the drive shaft An can also be connected directly to the first input shaft 14 via the vibration damper ST. The first transmission group 12 has a radial plane R1a.

[0142] The second gear group 18 is arranged coaxially with the first axis A1. The second gear group 12 has a radial plane R1b.

[0143] The first electric machine EM1 is arranged offset axially parallel to the first axis A1 and connected to the third input shaft 24 via the connection 26. However, the first electric machine EM1 can also be arranged coaxially thereto. The first electric machine EM1 is arranged on a third axis A3.

[0144] The output of the 10" hybrid transmission arrangement includes a fourth planetary gear set PS4, which establishes a constant gear ratio between the planet carrier P3 of the third planetary gear set PS3 and a differential 40. The fourth planetary gear set PS4 has an unspecified ring gear connected to a housing. A sun gear of the fourth planetary gear set PS4 is rotationally fixedly connected to the planet carrier P3. An unspecified planet carrier of the fourth planetary gear set PS4 is connected to an input member of the differential 40.

[0145] The differential gear 40, like the fourth planetary gear set PS4 and the third planetary gear set PS3, is arranged coaxially to the first axis A1.

[0146] The differential 40 has a first output shaft 42 and a second output shaft 44, which are rotationally fixedly connected to the driven wheels of the motor vehicle. Arranged axially around the second output shaft 44, extending from the differential 40 are the fourth planetary gear set PS4, the third planetary gear set PS3, the spur gear set 26 for connecting the first electric motor EM1, the first shifting element E, the double shifting element D, C, and the second planetary gear set PS2.

[0147] A connection between the first output shaft 16 and the second input shaft 20 is in Fig. 5 with 46. This connection can be realized by a spur gear set or by a traction device such as a chain. The connection 46 lies in a radial plane R2, which can be arranged axially between the radial planes R1a, R1b, as shown in Fig. 5, or adjacent thereto, as shown in Fig. 6 is shown.

[0148] A second electric machine EM2, which can be configured as a high-voltage starter generator, is connected to the first input shaft 14 via a connection 48, but can also be arranged coaxially therewith. The second electric machine EM2 is arranged on a fourth axle A4. The additional connection 48 can be implemented by a spur gear set or a traction mechanism.

[0149] The first switching element E can be actuated by means of a first actuating device B1. Fig. 6 shows a further embodiment of a hybrid transmission arrangement which, in terms of structure and operation of the hybrid transmission arrangement, is Fig. 5 corresponds.

[0150] In addition, an optional second switching element F is provided, by means of which the second output shaft 22 can be connected to the housing G.

[0151] This allows a second electric gear stage E1 to be set up, which has a shorter gear ratio than the electric gear stage E2 of the Fig. 2, which is switched by means of the first switching element E.

[0152] Fig. 6 also shows details of the gear groups 12, 18, as they are also shown in the embodiments of the Fig. 1, Fig. 4 and Fig. 5 can be used.

[0153] The first transmission group 12 has the first planetary gear set PS1, which is arranged in a first radial plane R1. The first planetary gear set PS1 includes a sun gear S1, which is fixed to a housing G. Furthermore, the first planetary gear set PS1 has a planet carrier P1, which is connected to the first output shaft 16. The first output shaft 16 is arranged as a hollow shaft section around the drive shaft An. The first input shaft 14 and the first output shaft 16 are arranged axially adjacent to one another.

[0154] The shifting element A is designed to connect the first input shaft 14 to the ring gear H1 of the first planetary gear set PS1. The shifting element B is designed to connect the first input shaft 14 directly to the first output shaft 16.

[0155] The gear ratio that can be set using shift element A is greater than 1.0, so that a shorter (lower) gear stage is set using shift element A than using shift element B.

[0156] The second transmission group 18 includes the second planetary gear set PS2, which is also arranged in the first radial plane R1. The second planetary gear set PS2 includes a sun gear S2, which is fixed to the housing G. Furthermore, the second planetary gear set PS2 includes a planet carrier P2 and a ring gear H2.

[0157] The second input shaft 20 is arranged as a hollow shaft section around a shaft connected to the ring gear H2 and around the second output shaft 22 and is connected to the shifting elements C, D. The shifting element C is further connected to the ring gear H2 of the second planetary gear set PS2. The shifting element D is further connected to the third output shaft and consequently also to the third input shaft 24. The planet carrier P2 of the second planetary gear set PS2 is connected to the second output shaft 22. By means of a shifting element D, the second input shaft 20 is connectable directly to the third output shaft 23. By means of the shifting element C, the second input shaft 20 is connectable to the second output shaft 22 via the second planetary gear set PS2.

[0158] In the second transmission group 18, a direct gear ratio i = 1 is established by means of the shifting element D. A gear ratio greater than 1 is established by means of the shifting element C, corresponding to a shorter gear step than via the shifting element D.

[0159] The second planetary gear set PS2 is preferably arranged in the same radial plane R1 as the first planetary gear set PS1. The connection 46 is arranged axially adjacent thereto, specifically between the planetary gear sets PS1, PS2 and the double shift element D, C.

[0160] The second shifting element F is arranged axially adjacent to the planetary gear set PS2, on an axial side opposite the connection 46. Since the shifting elements E, F are located axially in different positions in the present case, it is preferred if the second shifting element F can be actuated by means of a further actuating device B5, specifically independently of the first shifting element E. This independent actuation can, in contrast to the implementation as a double shifting element, also have advantages when changing gears from E1 to E2 and vice versa.

[0161] On the second axis A2, the double switching element A, B is arranged in the axial direction between the first planetary gear set PS1 and the first shaft 14.

[0162] In other words, the double switching elements A, B and D, C are located on axially opposite sides of the radial plane R1 formed by the planetary gear sets PS1, PS2.

[0163] In the hybrid transmission arrangements 10, 10', 10'' and 10''', a direct gear corresponding to the highest hybrid slope level H4 is established by closing the switching elements B, D.

[0164] The shift elements A, B, which are implemented by means of a double shift element, are actuated by a second actuating device B2. The shift elements C, D, which are implemented by means of a double shift element, are actuated by means of a third actuating device B3. The separating clutch K0, if present, is actuated by means of a fourth actuating device B4.

[0165] Fig. 7 shows a section of another hybrid transmission arrangement 10 IV , in which the transmission groups 12, 18 and the first electric machine EM1 are not shown. In comparison to the hybrid transmission arrangement 10''' of the Fig. 6, the hybrid transmission arrangement 10 IVthe alternative third planetary gear set PS3' (EDA-Invers).

[0166] The hybrid transmission arrangements of the Fig. 6 and Fig. 7 the same table can be used that is in Fig. 2 is shown.

[0167] In Fig. 8 is another embodiment of a hybrid transmission arrangement 10 V shown, which in terms of structure and function generally correspond to the hybrid transmission arrangement 10''' of the Fig. 6, without the second switching element F, which, however, can also be provided here. Identical elements are therefore identified by the same reference numerals.

[0168] In the hybrid transmission arrangement 10 V is in the first gear group 12 V a first planetary gear set PS1 V which has a sun gear S1 connected to the housing V and a ring gear H1 connected to the first output shaft 16 V The planet carrier P1 Vis connected to a switching element B, by means of which the first input shaft 14 is connected to the planet carrier P1 V can be connected. The shifting element A is designed to directly connect the first input shaft 14 and the first output shaft 16 to one another, thus establishing a direct transmission i = 1.

[0169] With the alternative first planetary gear set PS1 V By switching a switching element B, a gear ratio is set up that is smaller than 1, so that a longer gear ratio is set up by means of the switching element B than by means of the switching element A.

[0170] In this case, the assignment of the shift elements to the designations AD is selected in such a way that in each hybrid transmission arrangement the highest gear ratio is set by shift element A and the lowest gear ratio (longest gear step) by shift element D.

[0171] In the hybrid transmission arrangement 10 Va direct gear is established by closing the switching elements A, D, corresponding to the hybrid gear stage H2.

[0172] In Fig. 9 is another hybrid transmission arrangement 10 VI shown, which is based on the hybrid transmission arrangement 1''' of the Fig. 6, without the second switching element F, which can, however, also be provided here.

[0173] In the second gear group 18 VI a second planetary gear set PS2 VI which has a sun gear S2 connected to the housing VI , one via the switching element D with the second input shaft 20 VI connectable planet carrier P2 VI and a ring gear H2 VI which is connected to the second output shaft 22. By means of the switching element C, the second input shaft 20 VI connectable to the third output shaft 23. By means of the switching element D, the second planetary gear set PS2 VIa ratio of less than 1.0 is set, corresponding to a longer gear step.

[0174] A direct gear stage is therefore established by closing the switching elements B and C, corresponding to the hybrid gear stage H3.

[0175] In Fig. 10 is another hybrid transmission arrangement 10 VII shown, which are based on the hybrid transmission arrangements of the Fig. 8 and Fig. 9. In the first gear group 12 V the first planetary gear set PS1 V included, as in the embodiment of the Fig. 8. In the second gear group 18 VI is the second planetary gear set PS2 VI included, as in the embodiment of the Fig. 9.

[0176] A direct gear stage is therefore established by closing the switching elements A and C, corresponding to the hybrid gear stage H1.

[0177] The Fig. 11 and Fig. 12 each show exemplary representations of a planetary gear set together with a double shift element, as can be realized in the transmission groups described above.

[0178] One of the shift elements is intended to bridge the planetary gear set PS1 by connecting an input shaft (An) and an output shaft (Ab). The other shift element is intended to activate the planetary gear set so that the ratio i between An and Ab is not equal to 1.0.

[0179] There are several arrangement variants for these switching elements. One is a drive-side arrangement of the double switching element between the drive and the planetary gear set, as in Fig. 11. Here, the switching element B sets the ratio i = 1. The arrangement essentially corresponds to the double switching element A, B, which is shown in Fig. 5 is shown.

[0180] In Fig.Figure 12 shows an output-side arrangement of the shifting element A', B' between the planetary gear set PS1' and the output Ab. Here, the shifting element B' is also designed to establish the ratio i = 1. Reference symbol 10 Hybrid transmission arrangement 11 gearboxes 12 first gear group 14 first input shaft 16 first output shaft 18 second gear group 20 second input shaft 22 second output shaft 23 third output shaft 24 third input shaft 26 Connection EM1 / 24 30 motor vehicles 32 first axis 34 second axis 36 electric axle drive 38 Hybrid powertrain 40 differential gears 42 first output shaft 44 second output shaft 46 Connection 16 / 20 48 Connection EM2 / 14 PS1 first planetary gear set S1 sun gear PS1 H1 ring gear PS1 P1 planet carrier / web PS1 PS2 second planetary gear set S2 sun gear PS2 H2 ring gear PS2 P2 planet carrier / web PS2 PS3 third planetary gear set S3 Sun Gear PS3 H3 ring gear PS3 P3 planet carrier / web PS3 PS4 fourth planetary gear set E first switching element F second switching element A, B first double switching element 14 C, D second double switching element 18 B1-B5 Actuating devices A1-A4 axes R1,R2 radial planes EM1 first electric machine EM2 second electric machine VM combustion engine From output On drive shaft ST vibration absorber

Claims

[1] Hybrid transmission arrangement (10) for a motor vehicle (30), with - a transmission (11) having a first input (14) connectable to an internal combustion engine (VM), a second output (22), a third output (23) and at least one planetary gear set (PS1, PS2), - a third planetary gear set (PS3) having a first member (S3;H3'), a second member (H3;S3') and a third member (P3;P3'), which can be locked by means of a first switching element (E) and which is arranged coaxially to a first axis (A1), and - a first electric machine (EM1), - wherein the first element (S3; H3') is connected to the first electric machine (EM1), - wherein the second member (H3; S3') is connected to the second output (22) of the transmission (11), - wherein the third output (23) of the transmission (11) is connected to the first member (S3; H3'), and - wherein the third member (P3; P3') is connected to an output (Ab) of the hybrid transmission arrangement (10), characterized by that the first electric machine (EM1) is arranged offset axially parallel to the first axis (A1) and is connected to the first member (S3; H3') of the third planetary gear set (PS3) via a spur gear set (26) or via a traction means. [2] Hybrid transmission arrangement (10) according to claim 1, wherein the transmission (11) comprises: - a first transmission group (12) having the first input (14), a first output (16) and a first planetary gear set (PS1), and - a second transmission group (18) having a second input (20), the second output (22), the third output (23) and a second planetary gear set (PS2), wherein the second input (20) of the second transmission group (18) is connected to the first output (16) of the first transmission group (12). [3] Hybrid transmission arrangement (10) according to claim 2, wherein - the first transmission group (12) has two shift elements (A, B) which are coupled to the first planetary gear set (PS1) and the first input (14) and the first output (16) in such a way that two different gear ratios can be set between the first input (14) and the first output (16), and / or - the second transmission group (18) has two shift elements (C, D) which are coupled to the second planetary gear set (PS2) and the second input (20) and the second output (22) and the third output in such a way that two different transmission ratios can be set between the second input (20) and the second output (22) on the one hand and between the second input (20) and the third output (22) on the other hand. [4] Hybrid transmission arrangement (10) according to claim 3, wherein - the two shift elements (A, B) of the first transmission group (12) are connected to the first planetary gear set (PS1) and the first input (14) and the first output (16) in such a way that one of the two ratios between the first input (14) and the first output (16) is a direct ratio and the other ratio is greater than 1.0 or less than 1.0, and / or - the two shift elements (C, D) of the second transmission group (18) are connected to the second planetary gear set (PS2) and the second input (20) and the second output (22) and the third output in such a way that one of the two gear ratios between the second input (20) and the second output (22) or the third output (23) is a direct gear ratio and the other gear ratio is greater than 1.0 or less than 1.

0. [5] Hybrid transmission arrangement (10) according to claim 3 or 4, wherein - the two shifting elements (A, B) of the first transmission group (12) are formed by a first double shifting element which is arranged coaxially to the first planetary gear set (PS1), and / or - the two shifting elements (C, D) of the second transmission group (18) are formed by a second double shifting element which is arranged coaxially to the second planetary gear set (PS2). [6] Hybrid transmission arrangement (10) according to one of claims 2-5, - wherein the second gear group (18) is arranged coaxially with the first axis (A1) and / or - wherein the first gear group (12) is arranged coaxially to a second axis (A2) which is arranged axially parallel and offset to the first axis (A1). [7] Hybrid transmission arrangement (10) according to one of claims 1-6, wherein - the output (Ab) has a differential gear (40) which is arranged coaxially to the first axis (A1), and / or wherein - the output (Ab) between the third member (P3;P3') of the third planetary gear set (PS3) and a differential gear (40) has a gear set (PS4) with a constant gear ratio. [8] Hybrid transmission arrangement (10) according to one of claims 1-7, wherein a member (H3; S3') of the third planetary gear set (PS3) is connectable to a housing (G) via a second shift element (F). [9] Hybrid transmission arrangement (10) according to one of claims 1-8, wherein a second electric machine (EM2) is connected to the first input (14) of the transmission (11). [10] Hybrid transmission arrangement (10) according to one of claims 1-9, wherein the first input (14) of the transmission (11) is connected to an output member of a separating clutch (K0), the input member of which is connectable to a drive shaft (An) of an internal combustion engine (VM). [11] Hybrid transmission arrangement (10) according to one of claims 2-10, wherein the first input is a first input shaft (14) of the first transmission group (12) and / or wherein the first output is a first output shaft (16) of the first transmission group (12) and / or wherein the second input is a second input shaft (20) of the second transmission group (18) and / or wherein the second output is a second output shaft (22) of the second transmission group (18). [12] Hybrid transmission arrangement (10) according to claim 11, wherein the first output shaft (16) and the second input shaft (20) are arranged offset parallel to the axis and are connected to one another via a spur gear set or a traction means (46). [13] Hybrid transmission arrangement (10) according to one of claims 1-12, wherein - the first planetary gear set (PS1) and / or the second planetary gear set (PS2) sets up a fixed gear ratio, and / or - the first planetary gear set (PS1) and the second planetary gear set (PS2) overlap axially. [14] Hybrid drive train (38) for a motor vehicle (30) having a first axle (32) and a second axle (34), with a hybrid transmission arrangement (10) according to one of claims 1 to 13 for driving the first axle (32).

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