Transmission and drivetrain and vehicle

Abstract

Gearbox (G) comprising an input shaft (10), a first output shaft (11), a second output shaft (12), a first planetary gear set (P1) and a second planetary gear set (P2) connected to the first planetary gear set, wherein the planetary gear sets (P1, P2) each comprise several elements (E11, E21, E31, E12, E22, E32), wherein - the first output shaft (11) is non-rotatably connected to a second element (E21) of the first planetary gear set (P1), - the second output shaft (12) is non-rotatably connected to a third element (E32) of the second planetary gear set (P2), - a third element (E31) of the first planetary gear set (P1) is connected to a first element (E12) of the second planetary gear set (P2) via a shaft (3) in a rotationally fixed manner and - a second element (E22) of the second planetary gear set (P2) is fixed to a rotationally fixed component (GG), the transmission further comprising a third planetary gear set (P3) comprising three elements (E13, E23, E33) and two switching elements (K1, B1), wherein - a first switching element (K1) is formed to lock the third planetary gear set (P3) by connecting two of its elements in a rotationally fixed manner, - a second switching element (B1) is formed, to fix a first element (E13) of the third planetary gear set (P3) to the rotationally fixed component (GG), - a second element (E23) of the third planetary gear set (P3) is non-rotatably connected to the first element (E11) of the first planetary gear set (P1) via an intermediate shaft (14). - a third element (E33) of the third planetary gear set (P3) is connected to the input shaft (10) in a rotationally fixed manner.

Description

[0001] The invention relates to a transmission comprising an input shaft, a first output shaft, a second output shaft, a first planetary gear set, and a second planetary gear set connected to the first planetary gear set, wherein the planetary gear sets each comprise several elements, and wherein a 2-speed transmission is arranged upstream of the transmission. The invention further relates to a drive train and a vehicle with such a transmission.

[0002] Such transmissions are known from the prior art, e.g., from DE 10 2011 079 975 A1. Such a transmission enables torque conversion as the ratio of an output torque to an input torque, as well as a gear ratio as the ratio of an input speed to an output speed. It is also known to connect a two-speed transmission upstream of the aforementioned transmission.

[0003] An integrated differential is known from DE 10 2018 112 880 A1.

[0004] The object of the present invention is to improve the known integrated differential, in particular to add a 2-speed gearbox to the known integrated differential in order to enable a more compact and cost-effective drive machine and to improve the efficiency of a drive train.

[0005] The problem is solved by a transmission with the features of claim 1, by a drive train according to claim 24, and by a vehicle with the features of claim 25.

[0006] Based on the known transmission, this transmission is characterized by the fact that the input shaft, the two output shafts, the planetary gear sets, and their components are arranged and designed in such a way that a torque introduced via the input shaft is converted and distributed between the two output shafts in a defined ratio, thus preventing the generation of a total torque. At least one component of the first planetary gear set is connected to another component of the second planetary gear set, and another component of the second planetary gear set is fixed to a rotationally rigid component.

[0007] For the purposes of this invention, a "shaft" is understood to be a rotatable component of the transmission, via which the respective components of the transmission are connected to one another in a rotationally fixed manner, or via which such a connection is established when a corresponding switching element is actuated. The shaft can connect the components axially or radially, or both axially and radially. The shaft can also serve as an intermediate piece, via which a component is connected, for example, radially.

[0008] The elements are primarily in the form of a sun gear, planet carrier, and ring gear.

[0009] In the context of the invention, "axial" refers to an orientation along a longitudinal center axis, along which the planetary gear sets are arranged coaxially to one another. "Radial" refers to an orientation in the diameter direction of a shaft that lies on this longitudinal center axis.

[0010] If an element is fixed, it is prevented from rotating. The rotationally fixed component of the gearbox can preferably be a permanently stationary component, preferably a gearbox housing, a part of such a housing, or a component rigidly connected to it.

[0011] Unlike in the prior art, no total torque is generated, e.g., at a differential housing. Preventing the generation of a total torque means that the sum of the individual torques applied to the two output shafts is not present at any rotating component (input shaft, output shafts, elements of the planetary gear sets), as is the case with differentials known from the prior art.

[0012] The gearbox can, for example, be designed in such a way that the input shaft is connected to a first element of the first planetary gear set in a rotationally fixed manner; the first output shaft is connected to a second element of the first planetary gear set in a rotationally fixed manner; wherein a third element of the first planetary gear set is rotationally fixed to a first element of the second planetary gear set; wherein a second element of the second planetary gear set is fixed to a rotationally fixed component of the transmission; the second output shaft is connected to a third element of the second planetary gear set in a rotationally fixed manner.

[0013] The torque conversion specification should be understood as follows: The transmission has two output shafts whose sum of torques, relative to the input torque, describes the transmission's conversion. The gear ratio of each output shaft is initially undefined. Only the coupling of the two output shafts, for example via the vehicle's wheels on a road, generates defined rotational speeds. If both output shafts rotate at the same speed, as for example... When driving straight ahead, the gear ratio can be defined, as in the prior art, as the ratio between the input speed and one of the two identical output speeds. In all other cases, it is not possible to define the gear ratio using the common definition of gear ratio.

[0014] The transmission is further characterized by a third planetary gear set comprising three elements and two shift elements for forming the two-speed stage. A first shift element is configured to lock the third planetary gear set by connecting two of its elements in a rotationally fixed manner. A second shift element is configured to fix one of the three elements, in particular a first element of the third planetary gear set, to the rotationally fixed component. A second element of the third planetary gear set is rotationally fixed to the first element of the first planetary gear set via an intermediate shaft. A third element of the third planetary gear set is rotationally fixed to the first input shaft.

[0015] This gearbox allows for both torque conversion using a housing support and torque distribution to the output shafts.

[0016] This multi-stage transmission, or gearbox, is part of the gearbox and serves to provide an additional gear ratio by increasing the speed of the drive motor and driving the input shaft at this increased speed. The multi-stage transmission, or gearbox, is in the form of a planetary gear set.

[0017] This provides a transmission, in particular a differential, that can perform the two functions of torque conversion and torque distribution, previously achieved by two separate assemblies, through a single integrated assembly, and also features a selectable and deselectable input shaft gear ratio. In other words, the invention is a combined transmission and differential unit additionally equipped with an upstream 2-speed gearbox. The inclusion of a 2-speed gearbox according to the invention allows for better utilization of, for example, an electric motor's characteristic map and thereby increases the efficiency of the drive system.

[0018] The first and second planetary gear sets can be arranged axially adjacent to each other. However, the first planetary gear set can also be arranged radially inside the second planetary gear set. In the latter configuration, the planetary gear sets are also referred to as nested arrangements.

[0019] It is preferred if the gear teeth of the two interconnected elements of the first and second planetary gear set, i.e., the third element of the first planetary set and the first element of the second planetary set, are formed on the same component.

[0020] It is preferred if the pitch of the gear teeth on the third element of the first planetary gear set and on the first element of the second planetary gear set is identical. The identical pitch enables axial force-free operation of the connecting component or coupling shaft, thus eliminating the need for a complex axial bearing.

[0021] The pitch or lead of a helical gear refers to the axial displacement measured along a corresponding axis of rotation. This displacement, if one tooth were to extend beyond the actual width of the gear, would be required to complete a 360° turn around the axis. Similarly, the term thread pitch is used for threads. A helical gear with multiple teeth is thus comparable to a multi-start thread. For spindles, the term lead height is also used for the corresponding measurement.

[0022] It is preferred if the input shaft, and thus the third element of the third planetary gear set for introducing torque into the transmission, is connected to a drive motor, in particular an electric motor or an internal combustion engine. In the case of an electric motor, it is preferred if the rotor of the electric motor is rotationally fixed to the input shaft. It is preferred if the rotor is connected to the input shaft via at least one transmission stage.

[0023] The electric motor can be arranged either coaxially to the planetary gear sets or parallel to them. In the former case, the rotor of the electric motor can either be directly and rotationally fixed to the third planetary gear set or coupled to it via one or more intermediate transmission stages, the latter allowing for a more efficient design of the electric motor with higher speeds and lower torque. The at least one transmission stage can be a spur gear stage and / or a planetary gear stage.

[0024] If, however, the electric motor is positioned offset from the planetary gear sets, coupling is achieved via one or more intermediate transmission stages and / or a traction drive. The one or more transmission stages can also be implemented individually as either spur gear stages or planetary gear stages. A traction drive can be either a belt or a chain drive.

[0025] In a coaxial arrangement of the electric motor, it is preferred if the first output shaft passes through the rotor of the electric motor. This makes the gearbox with the electric motor particularly compact.

[0026] It is preferred if the stationary gear ratio of the second planetary gear set is calculated at least approximately as the reciprocal of the stationary gear ratio of the first planetary gear set minus 1, i.e.: i02=1i01−1.

[0027] In the event that the two planetary sets are implemented as negative planetary sets (e.g. according to...) Fig. 2 or Fig. 3) This calculation method, neglecting transmission losses, results in an equal distribution of the output torque between the two output shafts. This is particularly advantageous when the invention is used to distribute the torque between two wheels on the same axle.

[0028] If a different torque distribution is desired or the planetary gear sets are designed differently (e.g., Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8 to Fig. 9), a calculation rule can be defined in a meaningful way ( Fig. 19) Since, under real-world operating conditions, asymmetrical transmission losses towards the two output shafts can make a slight deviation from the calculation advantageous in order to obtain equal output torques on both shafts, the wording "at least approximately" is used. Furthermore, this wording is used because exact adherence to the calculation, while maintaining integer tooth counts and favorable tooth combinations, e.g., with regard to acoustic requirements, is sometimes not possible.

[0029] In Fig. For the gear set combinations according to claims 15 to 20, the calculation rules for the respective dependence of the stationary gear ratio of the second planetary gear set on the stationary gear ratio of the first planetary gear set are specified analogously. These result, neglecting transmission losses, in an output torque of the same magnitude and sign at both output shafts.

[0030] It is preferred if the number of planets in the second planetary gear set is greater than the number of planets in the first planetary gear set. Using this configuration, a high gear ratio can be achieved despite applying the aforementioned calculation method, which in turn enables a particularly compact and cost-effective electric machine. It is preferred if the second planetary gear set has six planets and the first planetary gear set has four planets. Of course, the number of planets in the second planetary gear set can also be greater than in the first planetary gear set without applying the calculation method.

[0031] It is preferred if the drive motor is installed transversely to the direction of travel. It is preferred if the two output shafts are rotationally fixed to the wheels of a vehicle.

[0032] It is preferred if the two output shafts distribute the applied torque to different axles of a vehicle. This allows for the implementation of a longitudinal transfer case (also called a longitudinal distributor), i.e., a transmission that distributes the applied torque, for example, to several axles, in particular to a front axle and a rear axle of a vehicle.

[0033] The torque distribution of the transmission does not have to be even across the output shafts. Particularly in the longitudinal transfer case configuration, the distribution between the two axles can be uneven. For example, the torque supplied by the input shaft can be distributed such that 60% is sent to the rear axle and 40% to the front axle.

[0034] The first and second planetary gear sets can be configured as either a negative or a positive planetary gear set. A combination of negative and positive planetary gear sets is also possible.

[0035] A negative planetary gear set is composed in a manner known in principle to those skilled in the art from the elements sun gear, planet carrier and ring gear, wherein the planet carrier carries at least one, but preferably several planet gears rotatably mounted, each of which meshes with both the sun gear and the surrounding ring gear.

[0036] In a plus planetary gear set, the elements sun gear, ring gear and planet carrier are also present, the latter carrying at least one pair of planet gears, in which one planet gear is in tooth mesh with the inner sun gear and the other planet gear is in tooth mesh with the surrounding ring gear, and the planet gears mesh with each other.

[0037] Where the connection of the individual elements allows, a negative planetary gear set can be converted into a positive planetary gear set. In this case, compared to the negative planetary gear set, the ring gear and planet carrier connections must be exchanged, and the gear ratio must be increased by one. Conversely, a positive planetary gear set could also be replaced by a negative planetary gear set, provided the connection of the gear elements allows this. In this case, compared to the positive planetary gear set, the ring gear and planet carrier connections would also need to be exchanged, the gear ratio reduced by one, and the sign reversed. However, within the scope of the invention, the two planetary gear sets are preferably each configured as negative planetary gear sets.

[0038] It is preferred if the first and second planetary gear sets are designed as negative planetary gear sets. These have good efficiency and can be arranged axially side by side and radially nested.

[0039] When combining negative and positive planetary gear sets in a nested arrangement, it is preferred that the radially inner planetary gear set is a negative planetary gear set and the radially outer planetary gear set is a positive planetary gear set. This maintains the ease of nesting. Furthermore, the fixed ring gear offers the advantage that the (usually) lower efficiency caused by the positive planetary gear set only affects a single output shaft.

[0040] The elements of the transmission can preferably be designed as follows: a) Gearbox with two negative planetary gear sets, wherein it is - the first element of the first planetary gear set around a sun gear, - in the second element of the first planetary gear set around a planet carrier and - the third element of the first planetary gear set is a ring gear and where - the first element of the second planetary gear set around a sun gear, - in the second element of the second planetary gear set around a planet carrier and - the third element of the second planetary gear set is a ring gear.

[0041] This gearbox could be described as a first concept with two negative planetary gear sets. b) Gearbox with two negative planetary gear sets, wherein it is - the first element of the first planetary gear set around a sun gear, - the second element of the first planetary gear set is a ring gear and - the third element of the first planetary gear set is a planet carrier and where - the first element of the second planetary gear set around a ring gear, - in the second element of the second planetary gear set, around a planet carrier and - the third element of the second planetary gear set is a sun gear.

[0042] This gearbox could be described as a second concept with two negative planetary gear sets. c) Gearbox with two negative planetary gear sets, wherein it is - the first element of the first planetary gear set around a ring gear, - in the second element of the first planetary gear set around a planet carrier and - the third element of the first planetary gear set is a sun gear and where - the first element of the second planetary gear set around a sun gear, - in the second element of the second planetary gear set around a planet carrier and - the third element of the second planetary gear set is a ring gear.

[0043] This gearbox could be described as a fifth concept with two negative planetary gear sets. d) Gearbox with a positive and a negative planetary gear set, wherein the second planetary gear set is the negative planetary gear set, wherein it is - the first element of the first planetary gear set around a sun gear, - in the second element of the first planetary gear set, around a ring gear and - the third element of the first planetary gear set is a planet carrier and where - the first element of the second planetary gear set around a sun gear, - in the second element of the second planetary gear set around a planet carrier and - the third element of the second planetary gear set is a ring gear.

[0044] This gearbox is essentially the first concept with a plus planetary gear set. e) Gearbox with a positive and a negative planetary gear set, wherein the first planetary gear set is the negative planetary gear set, wherein it is - the first element of the first planetary gear set around a sun gear, - in the second element of the first planetary gear set around a planet carrier and - the third element of the first planetary gear set is a ring gear and where - the first element of the second planetary gear set around a sun gear, - in the second element of the second planetary gear set (P2) around a ring gear and - the third element of the second planetary gear set is a planet carrier.

[0045] This gearbox is essentially the first concept with a plus planetary gear set. f) Transmission with two plus planetary gear sets, wherein it is - the first element of the first planetary gear set around a sun gear, - in the second element of the first planetary gear set, around a ring gear and - the third element of the first planetary gear set is a planet carrier and where - the first element of the second planetary gear set around a sun gear, - in the second element of the second planetary gear set around a ring gear and - the third element of the second planetary gear set is a planet carrier.

[0046] This gearbox is essentially the first concept with two plus planetary gear sets.

[0047] The third planetary gear set can be arranged axially adjacent to one of the first two planetary gear sets. However, it can also be arranged axially adjacent to both first two planetary gear sets.

[0048] The first switching element can be in particular a clutch, which, when actuated, may align the rotational movements of the components of the transmission directly connected to it and then connect them together in a rotationally fixed manner.

[0049] The second switching element can, in particular, function as a brake, which, when actuated, locks the first element of the third planetary gear set and consequently prevents it from rotating.

[0050] If a planetary gear set is locked in place, the gear ratio is always one, regardless of the number of teeth. In other words, the planetary gear set rotates as a single unit. The engagement of the third planetary gear set can be achieved by the first switching element - connects the first element with the second element of the third planetary gear set, - connects the first element with the third element of the third planetary gear set, or - connects the second element with the third element of the third planetary gear set.

[0051] It is preferred if the third planetary gear set is a minus planetary gear set, wherein the first element is a sun gear, the second element is a planet carrier, and the third element is a ring gear.

[0052] Alternatively, it is preferred if the planetary gear set is a plus planetary gear set, wherein the first element is a sun gear, the second element is a ring gear and the third element is a planet carrier.

[0053] It is preferred if at least one of the switching elements is designed as a load switching element.

[0054] It is preferred if at least one of the switching elements is designed as a positive locking element, preferably a claw switching element or synchronization.

[0055] Positive locking switching elements have the advantage over friction-locking switching elements that lower drag losses occur in the open state, thus enabling a better efficiency of the gearbox.

[0056] It is preferred if one of the two switching elements is designed as a load switching element and the other of the two switching elements is designed as a positive locking element.

[0057] In this preferred embodiment, the faster gear can be assigned to the power-shifting element to enable power-shifting capability during traction operation. The slower gear, on the other hand, can be assigned to the positive-locking element. The positive-locking element can be designed to be particularly compact, since power shifting during traction is often unnecessary.

[0058] It is preferred if the two switching elements are designed as a double switching element, which saves one switching element.

[0059] Preferably, the first output shaft passes through the third planetary gear set. Preferably, the switching elements are arranged radially above one another. The two aforementioned features, either individually or in combination, result in a compact transmission design.

[0060] It is preferred that the intermediate shaft passes through the third planetary gear set, in particular through the first element of the third planetary gear set. It is preferred that the intermediate shaft is guided at least partially radially between the third planetary gear set and the first output shaft. It is preferred that a connecting element linking the first element of the third planetary gear set and the second switching element is arranged at least partially axially between the first planetary gear set and the third planetary gear set. The connecting element can be a shaft.

[0061] The three aforementioned features regarding the intermediate shaft and the connecting element, either individually or in combination, result in a gearbox in which the rotor shaft can be supported on a small diameter. This enables the use of small rolling bearings, which allow for high electric motor speeds.

[0062] It is preferred that the magnitude of the stationary gear ratio of the third planetary gear set is smaller than the magnitude of the stationary gear ratio of the first planetary gear set. It is also preferred that the tooth diameter of the first element of the third planetary gear set is larger than the tooth diameter of the first element of the first planetary gear set. These two features, either individually or in combination, enable a balanced gear ratio series for the transmission. This allows the electric machine to be designed compactly. Furthermore, when using one or two power-shift elements, the load on the power-shift element(s) can be kept relatively low.

[0063] The transmission is, in particular, part of a motor vehicle powertrain for a hybrid or electric vehicle and is then arranged between a drive motor of the motor vehicle, designed as an internal combustion engine or an electric motor, and further components of the powertrain that follow the direction of power flow to the drive wheels of the motor vehicle. Here, the input shaft of the transmission is preferably coupled to a crankshaft of the internal combustion engine or the rotor shaft of the electric motor. The transmission can also be part of a powertrain for a conventional motor vehicle, i.e., a vehicle that is powered solely by an internal combustion engine.

[0064] The fact that two components of the transmission are rotationally fixed, "connected," or "coupled" means, within the meaning of the invention, a permanent coupling of these components so that they cannot rotate independently of each other. Therefore, no switching element is provided between these components, which may be elements of the planetary gear sets and / or shafts and / or a rotationally fixed component of the transmission; rather, the corresponding components are rigidly coupled to one another. A torsionally flexible connection between two components is also understood as rotationally fixed. In particular, a rotationally fixed connection can also include joints, for example, to enable steering movement or suspension travel of a wheel.

[0065] Overall, the invention enables the provision of a transmission and a vehicle with such a transmission, featuring an integral design, i.e., torque conversion and torque distribution, as well as a compact and axially short design (especially in nested arrangements). Furthermore, the transmission is characterized by high efficiency and low costs due to its low complexity. Significantly lower gear forces occur. In addition, the problem of scuffing is reduced. Furthermore, an extremely low locking value is achievable.

[0066] The invention is not limited to the specified combination of features of the main claim or the dependent claims. Furthermore, it is possible to combine individual features, including those that arise from the claims, the subsequent description of preferred embodiments of the invention, or directly from the drawings. References in the claims to the drawings by means of reference numerals are not intended to limit the scope of protection of the claims.

[0067] Advantageous embodiments of the invention, which are explained below, are illustrated in the drawings. They show: Fig. 1 a schematic view of a motor vehicle powertrain; Fig. 2 - 5 a schematic view of each gearbox as used in the motor vehicle drivetrain made of Fig. 1 can be used, in one preferred embodiment each; Fig. 6 A schematic view of a gearbox as used in the motor vehicle drivetrain made of Fig. 1 can be used, in a preferred embodiment; Fig. Figures 7-9 show a schematic view of a gearbox as used in the motor vehicle drivetrain. Fig. 1 can be used, in one preferred embodiment each; Fig. Figures 10-11 show a schematic view of one gearbox as used in the motor vehicle drivetrain made of Fig. 1 can be used, in one preferred embodiment each; Fig. 12 the execution according to Fig. 3 in a sectional view; Fig. 13-16 a schematic representation of the operating principle of the invention; Fig. 17 an overview of the stationary gear ratios of the individual embodiments; and Fig. 18, Fig. 19, Fig. 20, Fig. 21, Fig. 22, Fig. 23, Fig. 24, Fig. 25, Fig. 26, Fig. 27, Fig. 28 to Fig. 29 preferred embodiments relating to the 2-speed transmission using the example of the transmission from Fig. 3.

[0068] Fig. Figures 1a to 1e each show a schematic view of a gearbox G of a motor vehicle drive train 100 of a vehicle 1000 in the form of a passenger car.

[0069] The powertrain 100 according to Fig. Figure 1a shows an electric drive that powers the rear axle A of vehicle 1000. The drive train includes a gearbox G, which distributes the drive torque of the electric motor EM to two output shafts 11 and 12. The gearbox G and the electric motor are arranged in a common housing. The forward direction of travel is indicated by arrow 99. As also shown in Fig. As can be seen in Figure 1a, the gearbox G and the electric machine EM are aligned transversely to the direction of travel of the vehicle.

[0070] The powertrain 100 according to Fig. Figure 1b shows an internal combustion engine drive that powers the rear axle A of vehicle 1000. The drivetrain includes a transmission G, which distributes the drive torque of the internal combustion engine VM to two output shafts 11 and 12, with another transmission, e.g., an automatic transmission of the vehicle, being arranged between transmission G and the internal combustion engine VM. The forward direction of travel is indicated by arrow 99. As also shown in Fig. As can be seen in Figure 1b, the gearbox G and the internal combustion engine VM are aligned longitudinally to the direction of travel of the vehicle.

[0071] The powertrain 100 according to Fig. Figure 1c shows an internal combustion engine drive that powers the rear axle A and the front axle B of vehicle 1000. The drivetrain includes a transmission G, which distributes the drive torque of the internal combustion engine VM to axles A and B. Another transmission, e.g., an automatic transmission, is located between transmission G and the internal combustion engine VM. Transmission G can then be connected via an output shaft 11 to an axle differential of the rear axle A and via an output shaft 12 to an axle differential of the front axle B. The forward direction of travel is indicated by arrow 99. As further shown in Fig. As can be seen in Figure 1c, the gearbox G and the internal combustion engine VM are aligned longitudinally to the direction of travel of the vehicle.

[0072] The powertrain 100 according to Fig. Figure 1d shows an electric drive that powers the front axle B of vehicle 1000, i.e., an electric front-transverse drive. The drive train includes a gearbox G, which distributes the drive torque of the electric motor EM to two output shafts 11 and 12. The gearbox G and the electric motor are arranged in a common housing. The forward direction of travel is indicated by arrow 99. As also shown in Fig. As can be seen in Figure 1d, the gearbox G and the electric machine EM are aligned transversely to the direction of travel of the vehicle.

[0073] The powertrain 100 according to Fig. Figure 1e shows an electric all-wheel drive system that drives the rear axle A and the front axle B of vehicle 1000. This system is a transmission designed as a longitudinal distributor. The drivetrain includes a gearbox G, which distributes the drive torque of the electric motor EM to two output shafts 11 and 12. Output shaft 11 transmits the torque to the front axle B, while output shaft 12 transmits the torque to the rear axle A. The respective torques are then directed to the respective axle differentials. The gearbox G and the electric motor are arranged in a common housing. The forward direction of travel is indicated by arrow 99. As also shown in Fig. As can be seen in Figure 1e, the gearbox G and the electric machine EM are aligned transversely to the direction of travel of the vehicle.

[0074] The Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8 to Fig. Figure 9 shows gearboxes that can be equipped with a third planetary gear set and two shift elements for the input shaft reduction. Examples of such gearboxes follow from [date]. Fig. 18 Fig.

[0075] Fig. Figure 2 shows a transmission G in a first preferred embodiment. The transmission G comprises an input shaft 10, a first output shaft 11, a second output shaft 12, a first planetary gear set P1, and a second planetary gear set P2 connected to the first planetary gear set P1. The planetary gear sets P1 and P2 are each configured as a negative planetary gear set. The planetary gear sets P1 and P2 each comprise several elements E11, E21, E31, E12, E22, and E32, wherein the first element E11 is a sun gear SO1, the second element E21 is a planet carrier PT1, and the third element E31 of the first planetary gear set P1 is a ring gear HO1. In the second planetary gear set P2, the first element E12 is a sun gear SO2, the second element E22 is a planet carrier PT2, and the third element E32 is a ring gear HO2.The planet carriers PT1 and PT2 each support several planet gears, which are shown but not labeled. The planet gears mesh with both the respective radially inner sun gear and the respective surrounding ring gear. The input shaft 10, the first output shaft 11, and the second output shaft 12 are arranged coaxially. Likewise, the two planet gear sets P1 and P2 are arranged coaxially.

[0076] The input shaft 10 is non-rotatably connected to the first element E11. The first output shaft 11 is non-rotatably connected to the second element E21 of the first planetary gear set. The second output shaft 12 is non-rotatably connected to the third element E32 of the second planetary gear set. The third element E31 of the first planetary gear set P1 is non-rotatably connected to the first element E12 of the second planetary gear set P2, while the second element E22 of the second planetary gear set P2 is fixed to a non-rotatable component GG. The non-rotatable component GG is a gearbox housing of gearbox G.

[0077] The third element E31, i.e. the ring gear HO1 of the first planet gear set P1 and the first element E12, i.e. the sun gear SO2 of the second planet gear set, form a common component, which in this case is a shaft 3.

[0078] As in Fig. As can be seen in Figure 2, the input shaft 10, the first output shaft 11, and the second output shaft 12 are arranged coaxially. Likewise, the two planetary gear sets P1 and P2 are arranged coaxially. According to this embodiment, the two planetary gear sets P1 and P2 are arranged axially spaced apart from each other.

[0079] The input shaft 10 can be connected to a drive motor and thus introduce an input torque into the gearbox G. This means that the input and output shafts rotate in the same direction. By connecting the two planetary gear sets P1 and P2 to each other and supporting the second element E22 on the housing GG, the introduced input torque can be distributed to the two output shafts 11 and 12. In this configuration, the gearbox not only functions as a transmission but also as a differential. That is, the introduced torque is not only translated but also distributed to different output shafts. In this embodiment, there is no reversal of the direction of rotation.

[0080] Fig. Figure 3 shows another preferred embodiment of the gearbox G. In contrast to the embodiment according to Fig. 2 shows the execution according to Fig. 3 a radially nested arrangement of the two planetary gear sets P1, P2. While the design according to Fig. 2 proposes an extremely radially compact solution, enabling the embodiment according to Fig. 3. An extremely axially compact gearbox G. The first planetary gear set P1 forms the radially inner planetary gear set. The second planetary gear set P2 forms the radially outer planetary gear set. The first planetary gear set P1 is therefore located radially inside the second planetary gear set P2. In this embodiment as well, the connection between the first ring gear HO1 of the first planetary gear set P1 and the sun gear SO2 of the second planetary gear set is designed as a single component, which in this case is also a shaft 3. In this embodiment, there is also no reversal of the direction of rotation.

[0081] Fig. Figure 4 shows a transmission G in a further preferred embodiment. In contrast to Fig. In section 2, the first planetary gear set P1 is now configured as a plus planetary gear set. This means that the third element E31 of the first planetary gear set is configured as a planet carrier, which is rotationally fixed to the first element E12 of the second planetary gear set, i.e., the sun gear SO2. The second element E21 is now configured as a ring gear HO1 and is rotationally fixed to the first output shaft 11. The third element E31 of the first planetary gear set and the first element E12 of the second planetary gear set are again configured on the same component, which in this case is a shaft 3. For further details, please refer to the explanations regarding... Fig. 2 referred.

[0082] Fig. Figure 5 shows another preferred embodiment of the gearbox G. In contrast to the embodiment according to Fig. In this case, both planetary gear sets P1 and P2 are now configured as plus planetary gear sets. The second element, E21, is configured as a ring gear HO1 and is non-rotatably connected to the first output shaft 11. The third element, E31, is now configured as a planet carrier PT1 and is non-rotatably connected to the first element, E12, i.e., the sun gear SO2 of the second planetary gear set P2. The second element, E22, of the second planetary gear set P2 is now configured as the ring gear HO2 and is fixed to the non-rotatable component GG. The third element, E32, of the second planetary gear set P2, however, is configured as a planet carrier PT2 and is non-rotatably connected to the second output shaft 12.

[0083] Therefore, the planet carrier and ring gear connections were swapped in both planetary gear sets P1 and P2. For further details, please refer to the explanations regarding... Fig. 2 referred.

[0084] Fig. Figure 6 shows a gearbox in a further preferred embodiment. In contrast to the embodiment according to Fig. In section 2, the second planetary gear set P2 is now configured as a plus planetary gear set, while the first planetary gear set P1 remains unchanged. Thus, the ring gear HO2 of the second planetary gear set P2 is fixed to the housing GG. Furthermore, the planet carrier PT2 is rotationally fixed to the second output shaft 12. The planet carrier and ring gear connections of the second planetary gear set have therefore been reversed. For further details, please refer to the explanations regarding... Fig. 2 referred.

[0085] Fig. Figure 7 shows another preferred embodiment of the gearbox G. In contrast to the embodiment according to Fig. 6 provides the embodiment according to Fig. Seven radially nested planetary gear sets P1, P2 are present. The radially inner planetary gear set is the first planetary gear set P1. The radially outer planetary gear set is the second planetary gear set P2. For further details, please refer to the explanations regarding... Fig. 6 or 2 referred.

[0086] Fig. Figure 8 shows the gearbox G in a further preferred embodiment. This embodiment differs from the embodiment shown in Figure 8 in that it has a further preferred embodiment. Fig. The following two differences are apparent. Firstly, a drive machine in the form of an electric machine EM is provided. The electric machine EM comprises a housing-mounted stator S and a rotor R. The rotor R of the electric machine EM is non-rotatably connected to the first element E11, i.e., the sun gear SO1 of the first planetary gear set. Another difference lies in the fact that the second element E21 of the first planetary gear set is designed as a ring gear HO1 and is non-rotatably connected to the first output shaft 11. Furthermore, the third element E31 of the first planetary gear set P1 is designed as a planet carrier PT1 and is non-rotatably connected to the first element E12 of the second planetary gear set P2, which in this case is designed as a ring gear HO2. The second element E22 of the second planetary gear set is also designed as a planet carrier PT2 and is fixed to the housing GG.Accordingly, the third element E32 is designed as a sun gear SO2 and is rotationally fixed to the second output shaft. In this preferred embodiment, the direction of rotation of the input speed is reversed. Nesting of the planetary gear sets P1 and P2 is not possible in this embodiment.

[0087] In other words, the torque is still introduced via the sun gear SO1 of the first planetary gear set P1, while the output is ensured via the ring gear HO1. Unlike in Fig. 2. The planet carrier of the first planet gear set P1 is now rotationally fixed to the ring gear HO2 of the second planet gear set. In contrast to the design according to Fig. 2. The output of the second planetary gear set is therefore via the sun gear SO2.

[0088] Fig. Figure 9 shows another preferred embodiment of the gearbox G. This embodiment differs from the embodiment according to the following: Fig. 2. Firstly, a drive machine in the form of an electric machine EM is provided, which has a housing-mounted stator S and a rotor R. The rotor R is non-rotatably connected to the input shaft 10, which in turn is connected to the first element E11, which is configured here as a ring gear HO1, of the first planetary gear set P1. The first output shaft 11 is configured here as a second element E21, which is configured here as a planet carrier PT2, of the first planetary gear set P1. The third element E31 of the first planetary gear set P1, which is configured here as a sun gear SO1, is configured non-rotatably connected to the first element E12, i.e., the sun gear SO2, of the second planetary gear set P2. The remaining elements of the second planetary gear set remain unchanged.

[0089] Unlike the embodiment according to Fig. 2 is carried out in the embodiment according to Fig. 9. The introduction of torque via the ring gear HO1 of the first planetary gear set P1, while the output of the first planetary gear set P1 continues to be via the planet carrier PT1. In contrast to the Fig. 2 The connection of the two planetary gear sets P1, P2 is achieved via a common sun gear, which in this case is represented as a shaft 3.

[0090] Fig. Figure 10 shows a drive train of a vehicle with a transmission according to the invention in a further preferred embodiment. The transmission G is the preferred embodiment according to Fig. 2, to which reference is made. The drive machine is designed as an electric machine EM. The electric machine EM has a housing-mounted stator S and a rotor R. The rotor R is non-rotatably connected to the input shaft 10. As can be clearly seen, the electric machine EM is arranged coaxially with the input shaft 10 and with the output shafts 11, 12. It is also thus arranged coaxially with the planetary gear sets P1, P2. The input shaft 10 is designed as a hollow shaft through which the first output shaft 11 passes. For further details, reference is made to the descriptions in section 2. Fig. 10 referred.

[0091] Fig. Figure 11 shows a further drive train 100 with a transmission G in a preferred embodiment. In contrast to the embodiment according to Fig. In 10, the planetary gear sets P1 and P2 are not arranged axially next to each other, but radially one above the other, i.e., nested. Gear unit G is therefore the preferred embodiment of Fig. 3. Furthermore, reference is made to the explanations according to Fig. 10 and Fig. 3 referred.

[0092] Fig. Figure 12 shows the preferred embodiment of the gearbox G according to Fig. Figure 3 shows a sectional view. The shaft in the center is the output shaft 11. The input shaft 10 coincides with the sun gear of P1 in this drawing; that is, the input shaft 10 is connected to a sun gear of the first planetary gear set P1. The sun gear of the first planetary gear set P1, in turn, meshes with planet gears of the first planetary gear set P1. The planet gears of the first planetary gear set P1 mesh with the surrounding ring gear of the first planetary gear set P1, which also forms the sun gear of the second planetary gear set P2. The sun gear of the second planetary gear set P2, in turn, meshes with planet gears of the second planetary gear set P2. The planet gears of the second planetary gear set P2, in turn, mesh with the ring gear of the second planetary gear set P2 that surrounds the planet gears.

[0093] As can be clearly seen, the number of planets in the second planetary gear set is greater than the number of planets in the first planetary gear set. According to this diagram, the second planetary gear set has six planets, while the first planetary gear set has four.

[0094] This configuration allows for a large gear ratio, which in turn enables a particularly compact and cost-effective electric machine.

[0095] However, a large gear ratio leads to the following according to the calculation rule. i02=1i01−1 This results in a smaller gear ratio at the second planetary gear set P2. A smaller gear ratio, in turn, leads to a smaller planetary diameter. A smaller planetary diameter, in turn, worsens the tooth engagement and reduces the installation space for the planetary bearings.

[0096] It has been found that a higher number of planets in the second planetary gear set compared to the first planetary gear set counteracts this effect.

[0097] The following Fig. 13, Fig. 14 to Fig. Figure 15 shows the force introduction and force support of the invention in comparison to the prior art, such as DE 10 2011 079 975 A1. The preferred embodiment with two negative planetary gears, as described inter alia in DE 10 2011 079 975 A1, is compared to the prior art. Fig. 2 and Fig. 3. However, this consideration also applies analogously to the other embodiments.

[0098] For the Fig. 13, Fig. 14 to Fig. 15 applies generally: At the first planetary gear set P1, the torque of the input shaft 10 is converted into the output torque for the first output 11. The third element E31 of the first planetary gear set P1 (which is also the first element E12 of the second planetary gear set P2) is driven backward by its reaction torque. The backward movement of the third element E31 is permitted so that a portion of the mechanical drive power (preferably 50% in the case of the transverse differential and straight-line driving) is transmitted through the first planetary gear set P1 into the second planetary gear set.

[0099] Furthermore, by turning backwards the gear ratio to the first output (11) is increased (stationary gear ratio i0 = -3 would only allow a gear ratio of i = 4 with a fixed ring gear).

[0100] In the second planetary gear set P2, the direction of rotation applied to the first element (E12) (reverse) is reversed into the output motion of the second output (12) with the aid of a housing support (E22) (forward). Here, the torque introduced into the second planetary gear set P2 and the torque transmitted to the second output (12) combine to form the housing support torque. The second planetary gear set P2 transmits only the portion of the mechanical power that is directed to the second output (12) (typically 50%). The second planetary gear set P2 is only subjected to a portion of the power, thus positively impacting the overall efficiency.

[0101] In the current state of the art, torque conversion is usually achieved with the aid of a housing support. The reaction torque of the transmission is transmitted directly into the housing and does not contribute to generating the second output torque. As a result, a transmission must first be designed for the combined torque of both output shafts (generally twice the torque). Subsequently, a separate differential is required to divide this combined torque, which is not needed in this form anywhere, back into two output torques.

[0102] The individual Fig. 13, Fig. 14 to Fig. 15 show specifically: Fig. Figure 13 schematically shows the first planetary gear set P1 of the transmission G (right) and a first stage of the spur gear differential from the prior art (left). The force is transmitted from the planetary gears to the sun gear in parallel via three fixed gear engagements. The output to the first output shaft is via the sun gear.

[0103] In contrast, the force transmission according to the preferred embodiment occurs in parallel via eight moving, i.e., rotating, gear engagements. Four gear engagements exist between the sun gear SO1 and four planet gears. Four further gear engagements act between each planet gear and the ring gear HO1 (not shown). The output to the first output shaft 11 is via the planet carrier PT1. The technical advantage lies in the significantly lower gear forces acting on the first planet gear set.

[0104] Fig. Figure 14 schematically shows the second planetary gear set P2 of the transmission G (right) and a second stage of the stepped planetary gear from the prior art (left). The force is transmitted from the planetary gears to the sun gear in parallel via three fixed, i.e., stationary, tooth engagements. The output to the second output shaft is via the sun gear.

[0105] In contrast, the force is introduced into the second planetary gear set P2 according to the preferred embodiment via six moving, i.e., rotating, tooth engagements. Each of the six tooth engagements acts between one of the six planet gears and the ring gear HO2. The fixed planet carrier PT2, which supports the six planet gears, and the sun gear SO2 are not shown. The output to the second output shaft 12 is via the ring gear HO2. The technical advantage lies in the significantly lower tooth forces acting on the second planetary gear set due to the larger effective diameter and the greater number of possible planets.

[0106] Fig. Figure 15 schematically shows the introduction of the supporting torque into the housing. In the state-of-the-art stepped planetary gear (left), the force is introduced via three parallel tooth engagements in a fixed ring gear.

[0107] According to the preferred embodiment, the force is introduced via 12 parallel tooth engagements in the fixed planet carrier PT2. Six tooth engagements act between the sun gear SO2 and the six planet gears of the second planetary gear set. The other six tooth engagements act between each planet gear of the second planetary gear set and the ring gear HO2. The technical benefit lies in the significantly lower tooth forces acting on the second planet carrier PT2.

[0108] Fig. 16 shows that in the Fig. 13, Fig. 14 to Fig. 15 principles are shown in more detail in a further view.

[0109] The maximum torque in the wheelset according to the invention (right) corresponds to the output torque of a single wheel. Only the housing support has a high torque factor, following the laws of physics.

[0110] The state-of-the-art stepped planetary gear set (left) generates from an input torque M an The full output torque, i.e., the sum of the torque of both wheels. The differential divides this high torque into two equal wheel torques M. an1 and M an2 .

[0111] The diagram symbolically represents the magnitude of the torques as they pass through the gearbox. The direction of rotation is not indicated.

[0112] Fig. Figure 17 provides an overview of the calculation procedure for the stationary gear ratio of the individual embodiments. Neglecting gear losses, these result in an output torque of the same magnitude and sign at both output shafts (11, 12). 01 denotes the stationary gear ratio of the first planetary gear set P1. i 02This refers to the stationary gear ratio of the second planetary gear set P2. Depending on the use of the gearbox, one of the planetary gear set configurations with the corresponding stationary gear ratio can be selected.

[0113] The following figures describe the implementation of a 2-speed transmission in the form of a third planetary gear set P3 in the transmissions shown above.

[0114] Fig. 18, Fig. 19, Fig. 20, Fig. 21, Fig. 22, Fig. 23, Fig. 24, Fig. 25, Fig. 26, Fig. 27, Fig. 28 to Fig. Figure 29 shows various configurations of the two-speed transmission with regard to the design of the third planetary gear set P3 as a negative or positive gear set. The different locking variants are also shown. Thus, 12 variations are possible for each transmission, concerning the planetary gear set or the locking variant.

[0115] Fig. Figure 18 shows the preferred embodiment of the gearbox according to Fig. 3 or the drive train according to Fig. 11 with a third planetary gear set and two switching elements for implementing a gear ratio of the input shaft. Based on the description of Fig. 3 and Fig. 11, to which explicit reference is made, a third planetary gear P3 and two switching elements are provided for the translation of the drive speed of the electric machine EM.

[0116] The third planetary gear set P3 is designed as a negative planetary gear set and has three elements: a first element E13, a second element E23, and a third element E33. The first element E13 is a sun gear SO3, the second element a planet carrier PT3, and the third element E33 a ring gear HO3.

[0117] The third element E33, in this case the ring gear HO3, of the third planetary gear set P3 is connected to the input shaft 10. The second element E23, in this case the planet carrier PT3, is always connected via an intermediate shaft 14 to the first element E11, in this case the sun gear SO1, of the first planetary gear set P1. The rotor R of the electric machine EM is connected to the input shaft 10.

[0118] It should be noted at this point that the input shaft 10 of the embodiments according to Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8, Fig. 9, Fig. 10 to Fig. 11 and the input shaft 10 of the embodiment according to Fig. 18 are identical. They all have in common that they are connected to the drive motor. Between the input shaft 10 and the first element E11 of the first planetary gear set P1, only the third planetary gear set P3 is now arranged, so that, unlike before, it is not the sun gear SO1 but the ring gear HO3 that can be driven.

[0119] The third planetary gear set P3 can be locked by connecting the sun gear SO3 to the ring gear HO3. For this purpose, a first switching element is provided which, when actuated, connects the sun gear SO3 to the ring gear HO3. A second switching element, when actuated, connects the sun gear SO3 to the housing GG, thereby locking the sun gear SO3 in place. The first switching element is designed as a clutch K1, while the second element is designed as a brake B1.

[0120] The output shaft 11 is guided through the hollow input shaft 10, the hollow sun gear SO3 and the rotor R, thus providing an extremely compact gearbox.

[0121] As can also be seen, clutch K1 and brake B1 are arranged radially one above the other, with brake B1 being located radially outside clutch K1. Both switching elements K1 and B1 are arranged radially outside the third planetary gear set P3. The third planetary gear set and the two switching elements are positioned axially between the first and second planetary gear sets on the one hand and the electric motor on the other.

[0122] A connecting element 16 connects the sun gear SO3 to the coupling K1 via a connecting element 16. This is partially arranged axially between the first and third planetary gear sets.

[0123] The first gear of the 2-speed transmission is engaged by closing, i.e., applying brake B1. In first gear, the clutch is disengaged. The second gear of the 2-speed transmission is engaged by applying clutch K1. In second gear, the brake is disengaged.

[0124] Fig. 19 shows a modification of the execution according to. Fig. 18. In contrast, the locking of the third planetary gear set P3 is achieved by connecting the sun gear SO3 to the planet carrier PT3, so that this is a locking variant. Otherwise, this embodiment corresponds to the embodiment according to [reference]. Fig. 18.

[0125] Fig. Figure 20 shows a modification of the execution according to. Fig. 18. In contrast, the locking of the third planetary gear set P3 is achieved by connecting the ring gear HO3 to the planet carrier PT3, thus constituting a locking variant. Otherwise, this embodiment corresponds to the embodiment according to [reference to relevant document]. Fig. 18.

[0126] Fig. Figure 21 shows a further embodiment of the invention. Kinematically, this embodiment corresponds to the Fig. 21 of that embodiment according to Fig. 18. In contrast, the third planetary gear set P3 is designed as a plus planetary gear set. In addition, the connecting element 16 is arranged partially axially between the third planetary gear set P3 and the electric machine.

[0127] The input shaft 10 is still connected to the second element E23, which is now a ring gear HO3. The rotor R is still connected to the third element E33 of the third planetary gear set P3, which is now a planet carrier PT3.

[0128] Brake B1 can lock sun gear SO3 to housing GG. Clutch K1 can lock the third planetary gear set P3 by connecting sun gear SO3 and planet carrier PT3. Otherwise, this embodiment corresponds to the embodiment according to [reference to relevant document]. Fig. 18.

[0129] Fig. Figure 22 shows a modification of the execution according to. Fig. 21. In contrast, the locking of the third planetary gear set P3 is achieved by connecting the ring gear HO3 to the sun gear. Otherwise, this embodiment corresponds to the embodiment according to [reference to relevant document]. Fig. 21.

[0130] Fig. Figure 23 shows a modification of the execution according to. Fig. 21. In contrast, the locking of the third planetary gear set P3 is achieved by connecting the planet carrier PT3 to the sun gear SO3. Otherwise, this embodiment corresponds to the embodiment according to [reference to relevant section]. Fig. 21.

[0131] Fig. Figure 24 shows a further embodiment of the invention. In contrast to the embodiment according to Figure 24, the embodiment shown in Figure 24 is further illustrated in Figure 24. Fig. In Figure 18, the rotor is not connected to the ring gear HO3 but to the first element E13, in this case, the sun gear SO3. Furthermore, the planet carrier PT3 is connected to the sun gear SO1. By actuating the brake B1, the ring gear HO3 can be locked to the housing GG. By actuating the clutch K1, the sun gear SO3 and the ring gear HO3 are connected, thereby locking the third planet gear set P3. Otherwise, this embodiment corresponds to the embodiment according to [reference to relevant figure]. Fig. 18.

[0132] Fig. Figure 25 shows a modification of the execution according to. Fig. 24. In contrast, the locking of the third planetary gear set P3 is achieved by connecting the sun gear SO3 to the planet carrier PT3, thus constituting a locking variant. Otherwise, this embodiment corresponds to the embodiment according to [reference to relevant document]. Fig. 24.

[0133] Fig. Figure 26 shows a modification of the execution according to. Fig. 24. In contrast, the locking of the third planetary gear set P3 is achieved by connecting the ring gear HO3 to the planet carrier PT3, thus constituting a locking variant. Otherwise, this embodiment corresponds to the embodiment according to [reference to relevant section]. Fig. 24.

[0134] Fig. 27 shows a further embodiment of the invention. In contrast to the embodiment according to . Fig. 24 is the third planetary gear set P3 designed as a plus planetary gear set.

[0135] The input shaft 10 is therefore still connected to the second element E23, which in this case is a ring gear. The rotor is still connected to the sun gear SO3.

[0136] The brake B1 can lock the third element E33, in this case the planet carrier PT3, to the housing GG. The clutch K1 can lock the third planet gear set P3 by connecting the first element, i.e., the sun gear SO3, and the third element E33, i.e., the planet carrier PT3. Otherwise, this embodiment corresponds to the embodiment according to... Fig. 24.

[0137] Fig. Figure 28 shows a modification of the execution according to. Fig. 27. In contrast, the locking of the third planetary gear set P3 is achieved by connecting the sun gear SO3 to the ring gear HO3, thus constituting a locking variant. Otherwise, this embodiment corresponds to the embodiment according to [reference to relevant section]. Fig. 27.

[0138] Fig. Figure 29 shows a modification of the execution according to. Fig. 27. In contrast, the locking of the third planetary gear set P3 is achieved by connecting the ring gear HO3 to the planet carrier PT3, thus constituting a locking variant. Otherwise, this embodiment corresponds to the embodiment according to [reference to relevant document]. Fig. 27.

[0139] It should be noted again at this point that the third planetary gear set and the two switching elements are compatible with all transmissions as described in the Fig. 2 and 4 to 9 are revealed, and can be combined: In the gearbox according to Fig. 2. The connection of the 2-speed gearbox is identical to that of the gearbox according to Fig. 3, since the only difference concerns the arrangement of the first and second planetary gear sets. The axially spaced arrangement of the first planetary gear set relative to the second planetary gear set does not affect the connection of the third planetary gear set and the two switching elements.

[0140] In the gearbox according to Fig. 4. The connection of the 2-speed gearbox is identical to that of the gearbox according to Fig. 3, since the only difference concerns the conversion of the first planetary gear set into a positive planetary gear set. This involves simply swapping the connections of the ring and pinion gears, which has no effect on the connection of the third planetary gear set. The third planetary gear set is connected via the input shaft 10 to the sun gear SO1. The axially spaced arrangement of the first planetary gear set relative to the second planetary gear set does not affect the connection of the third planetary gear set or the two switching elements.

[0141] In the gearbox according to Fig. 5. The connection of the 2-speed gearbox is identical to that of the gearbox according to Fig. 3, since the only difference concerns the conversion of the first and second planet gear sets into a positive planet gear set. Only the link and ring gear connections are swapped, which has no effect on the connection of the third planet gear set. The third planet gear set is connected via the input shaft 10 to the sun gear SO1. The axially spaced arrangement of the first planet gear set relative to the second planet gear set does not affect the connection of the third planet gear set or the two switching elements.

[0142] In the gearbox according to Fig. 6. The connection of the 2-speed gearbox is identical to that of the gearbox according to Fig. 3, since the only difference concerns the conversion of the second planetary gear set into a positive planetary gear set. This involves simply swapping the connections of the ring and pinion gears, which has no effect on the connection of the third planetary gear set. The third planetary gear set is connected via the input shaft 10 to the sun gear SO1. The axially spaced arrangement of the first planetary gear set relative to the second planetary gear set does not affect the connection of the third planetary gear set or the two switching elements.

[0143] In the gearbox according to Fig. 7. The connection of the 2-speed gearbox is identical to that of the gearbox according to Fig. 3, since the only difference concerns the conversion of the second planetary gear set into a positive planetary gear set. Only the connecting links of the ring and pinion gears are swapped, which has no effect on the connection of the third planetary gear set. The connection of the third planetary gear set is made via the input shaft 10 with the sun gear SO1.

[0144] The Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6 to Fig. 7 correspond to the first concept. All variations regarding the conversion of the third planetary gear set into a plus planetary gear set or blocking variants are possible with these transmissions, as exemplified in the Fig. 18, Fig. 19, Fig. 20, Fig. 21, Fig. 22, Fig. 23, Fig. 24, Fig. 25, Fig. 26, Fig. 27, Fig. 28 to Fig. 29 based on the gearbox Fig. 3 shown.

[0145] The gearbox according to Fig. 8 corresponds to the second concept. Regarding the transmission according to Fig. 8. The connection of the 2-speed gearbox is identical to that of the gearbox according to Fig. 3. Although, unlike in Fig. 3. The first output shaft 11 is connected to the ring gear HO1, and the planet carrier PT1 is connected to the ring gear HO2. However, this change only affects the connection of the first and second planet gear sets P1 and P2 to each other and their connection to the housing. The input shaft 10, which continues to connect the rotor R to the sun gear SO1, is not affected. The axially spaced arrangement of the first planet gear set relative to the second planet gear set does not affect the connection of the third planet gear set or the two switching elements.

[0146] The gearbox according to Fig. 9 corresponds to the third concept. Regarding the transmission according to Fig. 9. The connection of the 2-speed gearbox is carried out with a modification. According to Fig. 9. The drive is via the ring gear HO1. For connection, the third element E33 (the ring gear HO3 in the case of a negative planetary gear set) of the third planetary gear set P3 can be connected to the rotor. The second element E23 (the planet carrier PT3 in the case of a negative planetary gear set) of the third planetary gear set P3 can be connected to the input shaft 10, which in turn is non-rotatably connected to the ring gear HO1 of the first planetary gear set P1. By means of the coupling K1, the sun gear SO3 can be connected to the planet carrier PT3, thereby locking the third planetary gear set P3. The sun gear can be locked in place by means of the brake B1.

[0147] The invention has been comprehensively described and explained with reference to the drawings and the description. The description and explanation are to be understood as examples and not as limiting. The invention is not limited to the disclosed embodiments. Other embodiments or variations will become apparent to a person skilled in the art when using the present invention and upon a detailed analysis of the drawings, the disclosure, and the subsequent claims.

[0148] In the patent claims, the words "comprise" and "with" do not preclude the presence of further elements or steps. The undefined article "a" or "an" does not preclude the presence of multiple elements. A single element or unit can perform the functions of several of the units mentioned in the patent claims. The mere mention of some measures in several different dependent patent claims is not to be understood as precluding the advantageous use of a combination of these measures. Reference sign G gearbox GG rotationally fixed component, housing E11 first element first planetary gear set E21 second element first planetary gear set E31 third element first planetary gear set E12 first element second planetary gear set E22 second element second planetary gear set E32 third element second planetary gear set E13 first element third planetary gear set E23 second element third planetary gear set E33 third element third planetary gear set P1 first planetary gear set P2 second planetary gear set P3 third planetary gear set SO sun wheel PT Planetary Carrier HO hollow gear EM electric machine S Stator R Rotor EW input shaft electric machine SRS spur gear stage SR1 first spur gear SR2 second spur gear B1 Switching element, brake K1 switching element, clutch N neutral position VM internal combustion engine A axle of the vehicle, rear B axle of the vehicle, front 3rd wave 10 Input wave 11 first output wave 12 second output wave 14 Intermediate shaft 15 joint 16 Connecting element 20 wheels 99 Direction of travel, forward 100 Powertrain 1000 vehicles i 01 Stationary gear ratio of the first planetary gear set i 02 Stationary gear ratio of the second planetary gear set

Claims

[1] Gearbox (G) comprising an input shaft (10), a first output shaft (11), a second output shaft (12), a first planetary gear set (P1) and a second planetary gear set (P2) connected to the first planetary gear set, wherein the planetary gear sets (P1, P2) each comprise several elements (E11, E21, E31, E12, E22, E32), wherein - the first output shaft (11) is non-rotatably connected to a second element (E21) of the first planetary gear set (P1), - the second output shaft (12) is non-rotatably connected to a third element (E32) of the second planetary gear set (P2), - a third element (E31) of the first planetary gear set (P1) is connected to a first element (E12) of the second planetary gear set (P2) via a shaft (3) in a rotationally fixed manner and - a second element (E22) of the second planetary gear set (P2) is fixed to a rotationally fixed component (GG), the transmission further comprising a third planetary gear set (P3) comprising three elements (E13, E23, E33) and two switching elements (K1, B1), wherein - a first switching element (K1) is formed to lock the third planetary gear set (P3) by connecting two of its elements in a rotationally fixed manner, - a second switching element (B1) is formed, to fix a first element (E13) of the third planetary gear set (P3) to the rotationally fixed component (GG), - a second element (E23) of the third planetary gear set (P3) is non-rotatably connected to the first element (E11) of the first planetary gear set (P1) via an intermediate shaft (14). - a third element (E33) of the third planetary gear set (P3) is connected to the input shaft (10) in a rotationally fixed manner. [2] Transmission according to claim 1, wherein the first switching element is a clutch. [3] Transmission according to claim 1 or 2, wherein the second switching element is a brake. [4] Transmission according to one of the preceding claims, wherein the first switching element is configured to connect the first element (E13) to the third element (E33) of the third planetary gear set. [5] Transmission according to any one of the preceding claims 1 to 3, wherein the first switching element is configured to connect the first element (E13) with the second element (E23) of the third planetary gear set. [6] Transmission according to any one of the preceding claims 1 to 3, wherein the first switching element is configured to connect the second element (E23) to the third element (E33) of the third planetary gear set. [7] Gearbox according to one of the preceding claims, wherein the third planetary gear set is a minus planetary gear set, wherein the first element is a sun gear (SO3), the second element is a planet carrier (PT3), the third element is a ring gear (HO3). [8] Gearbox according to any one of the preceding claims 1 to 6, wherein the third planetary gear set (P3) is a plus planetary gear set, wherein the first element is a sun gear (SO3), the second element is a ring gear (HO3) and the third element is a planet carrier (PT3). [9] Transmission according to one of the preceding claims, wherein at least one of the switching elements is designed as a load-shifting element. [10] Transmission according to any one of the preceding claims 1 to 8, wherein at least one of the switching elements is designed as a positive locking element, preferably a claw switching element or synchronizer. [11] Transmission according to claim 9 or 10, wherein one of the two switching elements is designed as a load switching element and the other of the two switching elements is designed as a positive locking element. [12] Transmission according to one of the preceding claims, wherein the two switching elements are designed as a double switching element. [13] Transmission according to one of the preceding claims wherein the first output shaft is guided through the third planetary gear set. [14] Transmission according to one of the preceding claims, wherein the switching elements are arranged radially above one another. [15] Gearbox according to one of the preceding claims, wherein the number of planets of the second planetary gear set is greater than the number of planets of the first planetary gear set. [16] Gearbox according to one of the preceding claims, wherein the gear teeth of the two interconnected elements (E31, E12) of the first (P1) and second planetary gear set (P2) are formed on the same component. [17] Gearbox according to one of the preceding claims, wherein the pitch of the gearing on the third element (E31) of the first planetary set (P1) and on the first element (E21) of the second planetary set (P2) is identical. [18] Transmission according to one of the preceding claims, wherein the stationary gear ratio of the second planetary set (P2) is calculated at least approximately from the reciprocal of the stationary gear ratio of the first planetary set (P1) minus 1, i.e. i02=1i01−1. [19] Transmission according to one of the preceding claims, wherein the intermediate shaft (14) is guided through the third planetary gear set (P3), in particular through the first element (E13) of the third planetary gear set (P3). [20] Transmission according to one of the preceding claims, wherein the intermediate shaft (14) is guided at least partially radially between the third planetary gear set (P3) and the first output shaft (11). [21] Transmission according to one of the preceding claims, wherein a connecting element (16) connecting the first element (E13) of the third planetary gear set (P3) and the second switching element (B1) is arranged at least partially axially between the first planetary gear set (P1) and the third planetary gear set (P3). [22] Transmission according to one of the preceding claims, wherein the magnitude of the stationary gear ratio of the third planetary gear set (P3) is less than the magnitude of the stationary gear ratio of the first planetary gear set (P1). [23] Gearbox according to one of the preceding claims, wherein the tooth diameter of the first element (E13) of the third planetary gear set (P3) is larger than the tooth diameter of the first element (E11) of the first planetary gear set (P1). [24] Drive train with a transmission according to any one of claims 1 to 23. [25] Vehicle with a drive train according to claim 24 or a transmission according to any one of claims 1 to 23.

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