WO2021062458A1

WO2021062458A1 - Transmission arrangement

Info

Publication number: WO2021062458A1
Application number: PCT/AT2020/060352
Authority: WO
Inventors: Ivan ANDRASEC
Original assignee: Avl List Gmbh
Priority date: 2019-10-04
Filing date: 2020-10-05
Publication date: 2021-04-08
Also published as: AT523003B1; DE112020000949A5; AT523003A1

Abstract

The invention relates to a transmission arrangement (1) with a primary drive shaft (12) for rotational connection to a primary drive (7) and with an extended Ravigneaux transmission (2) and with a further transmission (3) connected upstream of the extended Ravigneaux transmission (2), wherein the extended Ravigneaux transmission (2) comprises a double planetary transmission which has two sun gear shafts (6, 11), one planet carrier shaft (17) and two ring gear shafts (4, 5), characterized in that a first ring gear shaft (5) of the extended Ravigneaux transmission (2) is rotationally connectable to the primary drive shaft (12) by means of a first clutch device (C1).

Description

Gear arrangement

The invention relates to a gear arrangement with a primary drive shaft for rotary connection with a primary drive and with an extended Ravigneaux gear and an advanced Ravigneaux gear upstream of the white direct gear, the extended Ravigneaux gear having a first gear set and first planetary gears in this first gear set with the plane tträgerwelle connected planet carrier with a first sun gear of a first sun gear shaft and with a first ring gear of the first ring gear shaft, the extended Ravigneaux gear has a second gear set and in this second gear set second planet gears of the planet carrier with a second sun gear of a second sun gear shaft , mesh with a second ring gear of a second ring gear shaft, each first planet gear also meshes with a second planet gear each, the first ring gear shaft of the extended Ravig- neaux gearbox with the primary drive shaft by means of a first clutch ngsein direction is rotatably connected, an output shaft is rotatably connected or rotatably connected to the second ring gear shaft, an output shaft of the further transmission with at least one first element of the extended Ravigneaux transmission, preferably in front of the first sun gear, is rotatable by means of a second clutch device, a second element of the extended Ravigneaux transmission, preferably the planet carrier shaft, can be rotatably connected to the primary drive shaft by means of a third clutch device, a third element of the extended Ravigneaux transmission, preferably the second sun gear shaft, can be blocked with at least one second braking device.

It also relates to a drive system, the drive system having at least one primary drive, preferably an internal combustion engine, and at least one gear arrangement, and the primary drive being rotatably or rotatably connected to the gear arrangement via a primary drive shaft.

In addition, it relates to a motor vehicle, in particular a hybrid vehicle, with a drive system with a transmission arrangement.

Depending on the arrangement and operative connection of shifting elements in the Getriebean order, including clutch device and braking devices, zueinan as well as in operative connection with the individual transmission elements result in different properties of the transmission.

In DE 11 2013 001 057 T5, an alternative Ravigneaux gear is be written in which the step pinion meshes with both ring gears and directly or Comb with the sun gears via short pinions. Such embodiments are complex in construction and therefore costly.

DE 10 2017 207 191 A1 and DE 10 2017 207 200 A1 disclose extended Ravigneaux gears in which the input shaft is rotatably connected to a first ring gear by means of a first shaft. This leads to a limited number of switching variants.

DE 10 2014 223 340 A1 shows an embodiment in which the primary drive shaft can be rotatably connected to two different elements of the Ravigneaux transmission without translation via a clutch device and translated via a further transmission. Although this enables a few switching steps, the number of options is still insufficient. The primary drive shaft can be rotatably connected to the white direct transmission via a coupling device, which can lead to space problems in the transmission.

DE 10 2015 222 596 A1 describes a gear arrangement in which the output shaft of the further gear can be connected to two elements of the Ravigneaux gear. This can lead to disadvantageous gear ratios.

In WO 2018/115227 A1 an embodiment is described which has a Ravig neaux gear with only one ring gear and a secondary drive which is rotatably connected to a first sun gear shaft. This means that different gear ratios and shift modes can be achieved via the different shifting of the shifting elements, with a compact design of the transmission still being made possible. However, the number of different switching modes is insufficient.

AT 513 538 B1 describes a transmission of the type mentioned, in which two hollow wheel shafts are provided, which enables different switching modes for different control of the drives when a secondary drive is provided. However, the number of switching modes to be achieved can still be insufficient. In particular when a secondary drive is connected to the transmission, more switching modes are important in order to achieve optimal operating combinations of the drives. Due to the limited number of gears or switching modes and thus low functionality, the primary drive and any secondary drive that may be provided cannot always be operated optimally. This leads to only limited operational options and, in certain load situations, to inadequate provision of the torque. DE 10 2014 223 339 A1 describes a gear arrangement in which both the planet carrier of the Ravigneaux gear and the further gear can be connected to the primary drive shaft via a coupling device. This enables a number of switching stages, but the number is still insufficient, which leads to the problems described above.

The object of the invention is thus to provide a transmission arrangement with improved functionality, a corresponding drive system, and a corresponding motor vehicle. It is essential not only to provide a sufficient number of switching stages, but also that the individual switching stages can be designed by suitable selection of the number of teeth of the individual gears so that the gear ratios of the switching stages are reasonably even and free of too large Show jumps. This must be possible while observing structural constraints, such as the minimum number of teeth on gears or maximum speeds of transmission elements.

According to the invention, this object is achieved in that the primary drive shaft is rotatably connected to an input shaft of the further transmission.

The rotary connection of the primary drive shaft with the first ring gear shaft enables additional gears and shift modes and thus more possible uses of the primary drive. Due to the arrangement according to the invention, the output shaft of the further transmission can be connected to the Ravigneaux transmission regardless of the position of the third clutch device with the Ravigneaux transmission. This enables an additional expansion of the switching modes. Due to this increased range of variation in switching modes, in particular those are possible that are advantageous when a secondary drive is provided.

A particularly favorable variant of the invention provides that when the first clutch device is closed, the gear ratio between the primary drive shaft and the first ring gear shaft of the extended Ravigneaux gear differs from the gear ratio when the second clutch device is closed between the primary drive shaft and the first element of the extended Ravigneaux gear is. In this way, the transmission ratios of the individual gear stages can be better adapted to the requirements, ie a more even gradation of the transmission ratios can be represented. In particular, compared to the prior art, it can be avoided that different gear stages have the same gear ratio, in which case only one gear stage could effectively be used. It is advantageous if the first coupling device is connected directly to the primary drive shaft. In other words, there is no translation and / or other coupling device between the primary drive shaft and the first coupling device and the primary drive shaft is rotatably connected to a coupling part of the coupling device. Accordingly, it is also advantageous if the third coupling device is connected directly to the primary drive shaft. Thus, the power split from the primary drive shaft to the further transmission is upstream of the first clutch device and / or the third clutch device. This is particularly advantageous because the coupling devices can be switched independently of one another and cannot block one another.

The extended Ravigneaux gear includes a double planetary gear, so it preferably has two planetary gear sets, the plane ten wheels mesh with one another.

In the context of the invention, rotatably connected or rotatably connected is understood to mean a rotatably fixed connection of two elements or components. A rotary movement and torque are thus transmitted between the elements. In the context of the invention, however, a rotationally connectable connection is understood to mean a connection between two components that can be both rotationally fixed and detachable, for example a connection by means of a coupling device such as a separating clutch, with a rotationally fixed connection being present when the coupling device is closed and a released one when the coupling device is open Rotary connection, that is, when the coupling device is open, the components connected to the coupling device are rotatable relative to one another, but can be rotatably connected to one another by closing the coupling device and are therefore rotatable with one another.

An input side of a transmission, in particular the input side of the further transmission, is understood to mean an area and / or at least one component of the associated transmission via which a power, in particular a drive power, can be applied to the respectively associated transmission.

In the context of the invention, an output side of a transmission, in particular the output side of the further transmission, is to be understood as an area and / or at least one component via which a power applied to the respective associated transmission can be dissipated. The terms entry side and exit side are not to be understood in a spatially restrictive manner, ie the entry side and the exit side do not necessarily have to be one another are located on different sides of a transmission, but can definitely be arranged close to one another on one side.

Under certain circumstances, it can also be provided that, in certain operating states, a power, in particular a drive power, is applied to the respective associated transmission via an output shaft and is accordingly dissipated via an input shaft. In particular, if an electrical machine's drive is provided, this can be advantageous in order to draw electrical energy from a deceleration process.

The further transmission of a transmission arrangement according to the invention has an input side and an output side, the input side of the further transmission being rotatably connected to the first input shaft and the output side of the further gear set being rotatably connected to an output shaft. Elements of the extended Ravigneaux transmission can be rotatably connected or rotatably connected to the output shaft. The first planetary gear set and the second planetary gear set form an extended Ravigneaux planetary gear set, which is preceded by the further gear set in the power flow direction. Here, the power flow runs from the primary drive via the primary drive shaft to the input shaft of the further transmission. The input shaft of the white direct transmission is preferably rotatably connected or rotatably connected to the primary drive shaft.

A planetary gear set within the meaning of the invention is understood to mean a gear which is used to convert an input torque into an output torque and has one or more gear elements for this purpose, a planetary gear in the sense of the invention preferably having at least two gear elements, in particular at least one on a planet carrier rotatably movably supported planet gear and a sun gear and / or a ring gear, wherein the at least one planet gear meshes with the sun gear and / or the ring gear. In principle, the input torque can be applied to each transmission element and the output torque can be tapped at each of the further transmission elements that are not subjected to the input torque.

It is advantageous if the third clutch device is arranged in such a way that when the third clutch device is disengaged, the primary drive shaft is rotatably connected to the input shaft of the further transmission. This ensures an independent supply of torque to the further transmission.

According to the invention it is provided that the extended Ravigneaux transmission has a first gear set and first planetary gears one in this first gear set with the planet carrier shaft connected planet carrier with a first sun gear of a first sun gear shaft and with a first ring gear of the first ring gear shaft mesh, and that the extended Ravigneaux gear has a second gear set and in this second gear set second planet gears of the planet carrier with a second sun gear one second sun gear shaft, mesh with a second ring gear of a second ring gear shaft and that each first planet gear also meshes with a second planet gear each. In other words, a transmission according to the invention has a first gear set or planetary gear set, which has a first sun gear, at least one first planet gear that meshes with the first sun gear, and a planet carrier connected to the planet carrier shaft for rotatably supporting the at least one first planet gear . The at least one first planet gear also meshes with a first ring gear, which is rotatably connected to a first ring gear shaft. The second gear set or planetary gear set of a transmission according to the invention has as second gear elements a second sun gear, a second ring gear and at least one second planet gear, the at least one, second planet gear meshing with the second sun gear, the second ring gear and with one of the first planet gears and is rotatably supported on the planet carrier, in particular on the same planet carrier as the at least one, first planet wheel.

It is advantageous that an output shaft is or can be rotatably connected to a second ring gear shaft. An output shaft in the sense of the invention is an output shaft or a transmission element via which a mechanical power, in particular an output power, can be dissipated from the transmission. In a transmission according to the invention, the output shaft is preferably designed as a shaft and at least partially supported by a transmission housing and / or mounted in the transmission housing and / or in particular at least partially guided out of the transmission housing. If the output shaft can be rotatably connected to the second ring gear shaft, they can preferably be rotatably connected via a coupling device.

Furthermore, it can be advantageous if the further transmission is a simple planetary set, with a further sun gear shaft preferably being fixed to the housing, an output shaft preferably being rotatably connected to another planet carrier shaft and a further ring gear shaft being rotatably connected to the primary drive shaft. A compact construction of the further transmission and a better degree of efficiency can thus be achieved.

Alternatively it can be provided that the further gear is a spur gear with preferably two stages. Two stages mean two translation stages. In a preferred embodiment it is provided that at least one element of the extended Ravigneaux transmission is rotatably or rotatably connected to a secondary drive - particularly preferably having an electrical machine. With the help of several switching elements in the form of coupling devices and / or braking devices, different gears can be shifted, whereby in addition to the primary drive, a secondary drive can be coupled to the transmission, in particular the type that can be driven in addition to pure gear steps that can be driven by the primary drive Further, additional gear steps result in which a pure drive by means of the secondary drive is possible and / or a drive superimposed by means of the secondary drive, ie a so-called boost mode and / or a so-called ECVT mode (Electronic Continuously Variable Transmission ) can be realized in which torque and speed can be set continuously variably.

In order to achieve an easily switchable introduction of the torque from the secondary drive into the transmission, it can be provided that the secondary drive is or can be rotatably connected to a first ring gear shaft of the extended Ravigneaux transmission.

Alternatively, it can also be provided that the secondary drive is rotatably or rotatably connected to a first sun gear shaft of the extended Ravigneaux transmission. This is particularly advantageous because it enables a higher torque to be achieved. In addition, such embodiments are also particularly advantageous for secondary drives that have at least one electrical machine that is operated in the low-voltage range, for example with 48V.

It can also be advantageous if the secondary drive is rotatably connected to the extended Ravigneaux gear via a secondary gear or can be rotated, the amount of the gear ratio of the secondary gear preferably being greater than 1. The secondary gear is preferably a non-shiftable gear. The transmission ratio is the quotient of the speed of the input side and the speed of the output side, the output side being or rotatably connected to the extended Ravigneaux gear and the input side being rotatably or rotatably connected to the secondary drive. In other words, the secondary gear can be designed as a reduction gear.

Furthermore, it can also be provided that the secondary gear and / or the further gear is designed as a reduction gear and / or as a minus gear. Minus gears are planetary gears in which - when one shaft is held - the other two shafts rotate in different directions of rotation. It is particularly advantageous that an output shaft of the further transmission can be rotatably connected to at least one first element of the extended Ravigneaux transmission, preferably a first sun gear shaft, by means of a second coupling device. Several elements of the extended Ravigneaux transmission can therefore be connected to the output shaft, preferably at least one, namely the first element, is connected to it. Alternatively, the first element can also be a second sun gear shaft. This expands the number of different switching modes. If several coupling devices are provided, these can preferably be switched independently of one another.

A clutch device in the sense of the invention is a torque transmission device which can be operated in at least two switching states, preferably in a closed switching state in which a torque can be transmitted via the clutch device, and in an open state in which a power flow between two each with the coupling device, in particular mechanically connected components, is separated and thus no torque can be transmitted via the coupling device. For this purpose, a coupling device preferably has at least two coupling parts, the two coupling parts being mechanically, preferably rotatably connected to one another in a closed state of the coupling device, in particular frictionally or positively, and in an open state being independent of one another in particular rotatable against one another.

It is also advantageous that at least one second element of the expanded Ravig neaux transmission, preferably the planet carrier shaft, can be rotatably connected to the primary drive shaft by means of a third coupling device. So it can be connected to the primary drive shaft several elements of the extended Ravigneaux transmission. At least one, namely the second element, is preferably connected to it. If several coupling devices are provided, these can preferably be switched independently of one another.

It is also advantageous if the second element of the extended Ravigneaux gearbox, preferably the planet carrier shaft, can be blocked with a first braking device.

A braking device within the meaning of the invention is used to detachably set at least one component non-rotatably connected to the braking device, in particular for detachably fixing at least one gear element, in particular for detachably fixing the associated gear element on a gear housing surrounding the gear. When the braking device is activated, ie when the braking device is closed, the fixed gear element is immovable and can therefore preferably not rotate and is thus in particular in its Rotation blocked. When the brake device is open, however, the gear element is preferably movable in at least one of its intended degrees of freedom.

Furthermore, it is provided according to the invention that at least a third element of the extended Ravigneaux transmission, preferably a second sun gear shaft, can be blocked with at least one second braking device. So it can verbun several elements of the extended Ravigneaux transmission with braking devices to be the. At least one element, namely the third element, is preferably connected to it and can be braked. If several braking elements are provided, these can preferably be switched independently of one another.

It can also be advantageous if the third element of the extended Ravigneaux transmission can be rotatably connected to an output shaft of the further transmission by means of a fourth coupling device.

In the case of a vehicle, it is also particularly advantageous if an output shaft of the transmission arrangement can be rotatably connected or rotatably connected to at least one drivable axle of the vehicle.

The invention is explained in more detail below with reference to the non-restrictive figures. They show schematically:

1a shows a drive system according to the invention of a motor vehicle according to the invention with a transmission arrangement according to the invention in a first variant;

FIG. 1b shows a switching matrix of this first embodiment variant;

2a shows a drive system according to the invention in a second embodiment variant;

2b shows a switching matrix of the second embodiment variant;

3 shows a drive system according to the invention in a third embodiment variant;

Fig. 4a a drive system according to the invention in a fourth Ausfüh approximately variant;

4b shows a switching matrix of the fourth embodiment variant;

5 shows a drive system according to the invention in a fifth embodiment; 6a shows a drive system according to the invention in a sixth embodiment;

6b shows a switching matrix of the sixth embodiment variant;

7 shows a drive system according to the invention in a seventh embodiment variant;

8a shows a drive system according to the invention in an eighth embodiment variant;

8b shows a switching matrix of the eighth embodiment variant;

9 shows a drive system according to the invention in a ninth embodiment variant;

10a a drive system according to the invention in a tenth embodiment variant;

10b shows a switching matrix of the tenth embodiment variant;

11a a drive system according to the invention in an eleventh embodiment variant;

11b shows a switching matrix of the eleventh embodiment variant;

Functionally equivalent parts are seen in the designs with the same reference numerals ver.

The drive systems 21 shown in the figures with gear assemblies 1 of a motor vehicle each have an expanded Ravigneaux planetary gear set 2 with an upstream further gear 3, with the further gear 3 being designed as a reducing planetary gear set formed by a minus gear or as a two-stage spur gear is. In addition, a primary drive 7 designed as an internal combustion engine is connected to the transmission arrangement 1 via a primary drive shaft 12.

The substantially formed by a double planetary gear set expanded Ravigneaux planetary set 2 has a first sun gear 11a and a second Son nenrad 6a, which with a corresponding first sun gear shaft 11 and a second sun gear shaft 6 are connected, and at least one connected to a second ring gear shaft 4 second ring gear 4a. A set of first planet gears 9a meshes with a first ring gear 5a, which is angeord net on a ring gear shaft 5, and the first sun gear 11a. A set of second planet gears 10a mesh with the second sun gear 6a and mesh with the first planet gears 9a and the second ring gear 4a. The planet gears 9a, 10a are arranged to rotate freely on a common planet carrier 16 which is connected to a plane carrier shaft 17.

The primary drive 7, which is designed as an internal combustion engine, has a primary drive shaft 12 on which the primary drive provides its drive power.

An output shaft 15 is rotatably connected to the differential (final drive) FD of a driven axle, in particular to the front wheels, of the vehicle.

Fig. 1 shows a first embodiment according to the invention. The further transmission 3 is a spur gear, the input shaft 13 of which is rotatably connected to the primary drive shaft 12. A translation into the slow speed is achieved over two stages and the translated power of the primary drive 7 is provided on an output shaft 14 of the further transmission 3.

The primary drive shaft 12 can be rotatably connected to the first ring gear shaft 5 via a first coupling device CI. The primary drive shaft 12 is also connected to the planet carrier shaft 17 via a third coupling device C3. The first and third coupling devices CI, C3, like the input shaft 13, are directly connected to the primary drive shaft 12. For this purpose, a branch point 22 is provided for branching the power of the primary drive shaft 12 to the first and third clutch device CI, C3 and the input shaft 13 and all three parts CI, C3, 13 with the primary drive shaft 12 a related party in parallel. Thus, each of the parts CI, C3, 13 is supplied with torque from the primary drive shaft 12 independently of the others. The output shaft 14 can be rotatably connected to the first sun gear shaft 11 via a second coupling device C2. A second braking device B2 is connected to the second sun gear shaft 6, so that this can be fixed to the housing by activating the brake.

Fig. Lb shows a switching matrix of the clutch devices CI, C2, C3 and the braking device B2 for the transmission arrangement shown in Fig. La, wherein an "X" represents the activated, ie closed state of the corresponding clutch devices CI, C2, C3 or braking device B2 . By activating two of the clutch devices CI, C2, C3 or the braking device B2, a total of six forward gears gl-g6 can be shifted. In the with "i" marked column, the transmission ratio i is entered for a constructively solved embodiment that fulfills all the required boundary conditions. It can be seen that the gear ratios i vary between 2.548 and 0.477 and are different in pairs. In the column next to it, the relations F of the transmission ratios of the individual gear stages to the immediately preceding gear stage are entered. A favorable gradation is achieved with a maximum value of 1.746. The overall spread of the transmission is within the desired range at 5.34.

Fig. 2a shows a second embodiment of the invention, with a secondary drive 18 in the form of an electrical machine. The secondary drive 18 is translated into a slower speed via a non-shiftable secondary gear 19 before it is rotatably connected to the extended Ravigneaux gear 2.

The secondary drive 18 is rotationally connected to the first ring gear shaft 5 via the secondary gear 19 in the first embodiment.

FIG. 2b shows the corresponding switching matrix for FIG. 2a. The operating modes (gear ranges) are gl to g6 for the drive only by the drive machine 21 forward gears, El is a gear in which it is only driven by the secondary drive. This is achieved when only the second braking device B2 is activated. Due to the large number of switching modes, charging gears LI to L3 can also be achieved by activating only one clutch device C1-C3, in which the primary drive 7 supplies the secondary drive 18 with power when the vehicle is stationary and the vehicle's batteries are charged via the electric machine. At L2 (P) and L3 (P), however, the output shaft 4 must be braked - by a braking device such as a handbrake, for example. It is therefore clear that the invention enables several forward gears gl-g6, a purely electric gear El and, in addition, stationary charging modes.

The transmission ratios of the mechanical operating modes are the same as those of the variant of FIG. 1 a and FIG. 1 b.

If only clutch device C2 or only clutch device C3 is activated and the output shaft is not braked, the drive train can be operated in a steplessly power-split operating range E-CVT1, E-CTV2, in that the primary drive is advantageously operated stationary and the secondary drive 21 is either operated as a generator or in a first operating range is operated by a motor in a second operating area. This enables stepless electrodynamic start-up, which means that a separate start-up element, such as a hydrodynamic torque converter or a start-up clutch, is not required can. Switching from stepless power split operation to one of the five shiftable gears gl-g5 can be done while driving.

Reversing is possible by driving the secondary drive in the opposite direction in switching mode E1, which is easily possible with electrical machines.

During operation in one of the shiftable gears gl to g6, the secondary operation 18 can be operated either as a generator or as a motor to enable hybrid functions such as "boosting", recuperation "," shifting load point "or" sailing ".

Fig. 3 shows a third embodiment, which is very similar to the first, the further gear 3 is designed as a simple planetary gear. Another sun gear is fixed to the housing, the input shaft 13 is connected to a wide Ren planet carrier shaft and the output shaft 14 is connected to a further ring gear shaft. The switching matrix from Fig. 2b also corresponds to the possible Schaltfor men of this variant.

In FIG. 4 a, a fourth variant is shown which, compared to the second, has a fourth coupling device C4, which makes the output shaft 14 rotatable with the second sun gear shaft 6. Further switching modes are thus possible, as can be seen in FIG. 4b.

Eight forward gears gl -g8, yet another charging mode L4 (P) (in which the output shaft 4 must also be braked) and a continuously variable power split operation as reverse gear R-E-CVT can thus be engaged.

Fig. 5 shows a fifth embodiment which, like the fourth embodiment, provides a fourth clutch device C4, but a further gear 3 as a planetary gear as in FIG. Accordingly, the switching matrix from FIG. 4b also applies to this embodiment.

In FIG. 6 a, a sixth variant is shown which, in comparison to the fourth, has a first braking device B1 which can fix the second sun gear shaft 6. This means that further switching modes are possible, which are visible in FIG. 6b.

This means that nine forward gears gl -g9 and one reverse gear ER, in which only the secondary drive drives, can be engaged.

FIG. 7 shows a seventh embodiment which, like the sixth embodiment, provides a first braking device B1 and a further gear 3 as a planetary gear as in FIG. 5. Accordingly, the switching matrix from FIG. 6b also applies to this embodiment. FIG. 8a shows an eighth embodiment similar to that from FIG. 6a, but no secondary drive is provided. Accordingly, as in Fig. 8b, there are obviously a total of nine forward gears gl-g9 and one reverse gear R.

FIG. 9 shows a ninth embodiment like that from FIG. 7, but likewise without a secondary drive. Accordingly, the circuit diagram from FIG. 8b also applies here.

A tenth embodiment can be seen in FIG. 10a, which is very similar to the second embodiment. In this case, however, the secondary drive can be rotatably connected to the first sun gear shaft 11 via a secondary coupling device 20. The secondary clutch device 20 is preferably arranged between the secondary transmission and the first sun gear shaft 11, as shown. The switching modes can be seen from the switching matrix in FIG. 10b.

11a and 12a show eleventh and twelfth embodiments in which, as in the tenth embodiment, the secondary drive with the first sun gear shaft 11 can be rotated. They also have a fourth clutch device C4 between the output shaft 14 and the second sun gear shaft 6 and the twelfth embodiment also has the first braking device B1 for the planet carrier shaft 17. The respective switching matrices are ersicht Lich in Fig. 11b and Fig. 12b.

The embodiments from Fig. 10a, Fig. 11a, and Fig. 12a all have spur gears as further gears 3, these embodiments being of course also conceivable with planetary gears as further gears 3. For example, a planetary gear like the further gear 3 can be used in the embodiment from FIG. 3.

Claims

PATENT CLAIMS

1. Gear arrangement (1) with a primary drive shaft (12) for Drehverbin manure with a primary drive (7) and with an extended Ravigneaux gear (2) and the extended Ravigneaux gear (2) upstream of further gear (3), wherein the extended Ravigneaux transmission (2) has a first gear set and in this first gear set first Plane tenräder (9a) of a planet carrier (16) connected to the planet carrier shaft (17) with a first sun gear (11a) a first sun gear shaft (11) and men with a first ring gear (5a) of the first ring gear shaft (5), the extended Ravigneaux gear (2) having a second gear set and in this second gear set second planet gears (10a) of the planet carrier (16) with a second sun gear ( 6a) a second sun gear shaft (6), mesh with a second ring gear (4a) of a second ring gear shaft (4), each first planet gear (9a) also meshes with a second planet gear (10a), the first ring gear shaft (5) of the e extended Ravigneaux gearbox (2) can be rotatably connected to the primary drive shaft (12) by means of a first coupling device (CI), an output shaft (15) is rotatably connected or rotatably connected to the second ring gear shaft (4), an output shaft (14) of the further transmission (3) with at least one first element of the extended Ravigneaux transmission (2), preferably the first sun gear shaft (11), can be rotatably connected by means of a second clutch device (C2), a second element of the extended Ravigneaux transmission (2), preferably as the planet carrier shaft (17), with the primary drive shaft (12) can be rotatably connected by means of a third clutch device (C3), a third element of the extended Ravigneaux gear (2), preferably the second sun gear shaft (6), with at least one second braking device (B2 ) can be blocked, characterized in that the primary drive shaft (12) is rotatably connected to an input shaft (13) of the further transmission (3).

2. Transmission arrangement (1) according to claim 1, characterized in that the third clutch device (C3) is arranged so that when the third clutch device (C3) is open, the primary drive shaft (12) with the input shaft (13) of the further transmission (3) is rotationally connected.

3. Gear arrangement (1) according to one of claims 1 or 2, characterized in that when the first clutch device (CI) is closed, the transmission ratio between the primary drive shaft (12) and the first ring gear shaft (5) of the extended Ravigneaux gear (2) of the About transmission ratio with the second clutch device (C2) engaged between tween the primary drive shaft (12) and the first element of the extended Ravigneaux transmission (2) is different.

4. Gear arrangement (1) according to one of claims 1 to 3, characterized in that both the first ring gear shaft (5) of the expanded Ravig- neaux gear (2) and the second element of the expanded Ravig- neaux gear (2) untranslated with the primary drive shaft (12) are rotatable bindable.

5. Gear arrangement (1) according to one of claims 1 to 4, characterized in that the further gear (3) is a simple planetary gear set, preferably a further sun gear shaft is fixed to the housing, an output shaft is preferably rotatably connected to another planet carrier shaft and another The ring gear shaft is rotatably connected to the primary drive shaft (17).

6. Gear arrangement (1) according to one of claims 1 to 4, characterized in that the further gear (3) is a spur gear with preferably two stages.

7. Transmission arrangement (1) according to one of claims 1 to 6, characterized in that at least one element of the extended Ravigneaux transmission (2) with a secondary drive (18) is rotatably connected or rotatable - particularly preferably send an electrical machine aufwei.

8. Gear arrangement (1) according to claim 7, characterized in that the secondary drive (18) is rotatably connected or rotatably connected to a first ring gear shaft (5) of the extended Ravigneaux gear (3).

9. Gear arrangement (1) according to claim 7, characterized in that the secondary drive (18) with a first sun gear shaft (11) of the extended Ravigneaux gear (3) is rotatably connected or rotatably connected.

10. Gear arrangement (1) according to one of claims 7 to 9, characterized in that the secondary drive (18) via a secondary gear (19) with the extended Ravigneaux gear (3) is rotatably connected or rotatably connected bar, the amount of the gear ratio of the Secondary gearbox bes (19) is preferably greater than 1.

11. Transmission arrangement (1) according to one of claims 1 to 10, characterized in that the second element of the extended Ravigneaux gearbox (2), preferably the planet carrier shaft (17), can be blocked with a first braking device (B1).

12. Transmission arrangement (1) according to claim 11, characterized in that the third element of the extended Ravigneaux transmission (2) can be rotatably connected to an output shaft (14) of the further transmission (3) by means of a fourth coupling device (C4).

13. Drive system (21), wherein the drive system (21) has at least one primary drive (7), preferably an internal combustion engine, and at least one gear arrangement (1) and wherein the primary drive (7) via a primary drive shaft (12) with the gear arrangement ( 1) is rotatable or rotatably connected, characterized in that the Getriebeanord voltage (1) is designed according to one of claims 1 to 12.

14. Motor vehicle, in particular hybrid vehicle, with a drive system (21) with a gear arrangement (1), characterized in that the gear arrangement (1) is designed according to one of claims 1 to 12 and preferably the drive system (21) is designed according to claim 13 is.

15. Motor vehicle according to claim 14, characterized in that a drive shaft (15) from the transmission arrangement (1) is rotatably or rotatably connected to at least one drivable axle of the vehicle.