AT523003A1 - GEAR ARRANGEMENT - Google Patents

Abstract

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

Description

The invention relates to a transmission arrangement with a primary drive shaft for rotary connection with a primary drive and with an extended Ravigneaux transmission and a further transmission upstream of the extended Ravigneaux transmission, the extended Ravigneaux transmission having two sun gear shafts, a planet carrier shaft and two ring gear shafts

includes double planetary gear.

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

a drive system with a gear arrangement.

Depending on the arrangement and operative connection of shifting elements in the transmission arrangement, including the clutch device and braking device, result in relation to one another and in operative connection with the individual transmission elements

different properties of the transmission.

In WO 2018/115227 A1 an embodiment is described which has a Ravigneaux 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 ring gear 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. Especially if a secondary drive with the gearbox

connected, so more switching modes are important to optimal

Torque.

The object of the invention is therefore to provide a transmission arrangement with improved functionality, a corresponding drive system, and a corresponding motor vehicle.

According to the invention, this object is achieved in that a first ring gear shaft of the extended Ravigneaux transmission is connected to the primary drive shaft by means of a

first coupling device is rotatable.

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. As a result of this increased range of variation in switching modes, in particular those can also be possible which, with the provision of a

Secondary drive are advantageous.

The extended Ravigneaux gear includes a double planetary gear, so it preferably has two planetary gear sets, their planet gears

comb each other.

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 releasable, 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 rotational connection when the coupling device is disengaged , that is, when the coupling device is open, the components connected by means of 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.

a drive power can be applied to the respective 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 input side and output side are not to be understood in a spatially restrictive manner, i.e. the input side and the output side do not necessarily have to be on different sides of a gearbox, but rather

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 when an electrical machine is provided as the drive, this can be advantageous in order to be electrical

To draw energy from a deceleration process.

The further gear of a gear arrangement according to the invention has an input side and an output side, the input side of the further gear 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 further transmission is preferably connected to the

Primary drive shaft rotatably connected or rotatable.

A planetary gear set in the sense of the invention is a gear

understand what the conversion of an input torque into a

Output torque is used and has one or more gear elements, wherein a planetary gear in the sense of the invention preferably has at least two gear elements, in particular at least one planet gear rotatably supported on a planet carrier and a sun gear and / or a ring gear, the at least one planet gear each with the sun gear and / or meshes with the ring gear. In principle, the input torque can be applied to each transmission element and the output torque can be tapped off at each of the further transmission elements that are not subjected to the input torque.

It is preferably provided that the extended Ravigneaux gear has a first gear set and in this first gear set first planet gears of a planet carrier connected to the planet carrier shaft mesh with a first sun gear of a first sun gear shaft and with a first ring gear of the first ring gear shaft, and that the extended Ravigneaux gear Transmission has a second gear set and in this second gear set second planet gears of the planet carrier mesh with a second sun gear of a second sun gear shaft, 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 being rotatable is supported on the planet carrier, in particular on the same planet carrier as that

at least one, first planetary gear.

It is advantageous if 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 removed from the transmission. In a transmission according to the invention, the output shaft is preferably designed as a shaft and is 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, then they can preferably be rotatably connected via a coupling device.

It can also be advantageous if the further transmission is a simple planetary gear 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. This allows a more compact design of the further transmission and a better one

Efficiency can be achieved.

Alternatively it can be provided that the further gear is a spur gear with preferably two stages. There are two translation stages with two stages

meant.

In a preferred embodiment it is provided that at least one element of the extended Ravigneaux gear 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 clutch devices and / or braking devices, different gear steps can be shifted, whereby in addition to the primary drive, a secondary drive can be coupled to the transmission, in particular in such a way that, in addition to pure gear steps that can be driven via the primary drive, further, additional Gears 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 implemented 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 rotationally connected or connected to a first ring gear shaft of the extended Ravigneaux transmission

is rotatable.

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 particularly advantageous for secondary drives that have at least one electrical machine that is operated in the low-voltage range, for example with 48V.

Furthermore, it can be advantageous if the secondary drive is rotatably or rotatably connected to the extended Ravigneaux gear via a secondary gear, the magnitude of the transmission 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 transmission can be used as a

Be designed 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 if 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 are preferably independent

switchable from each other.

A coupling device within the meaning of the invention is a

Torque transmission device which is in at least two switching states

7734

can be operated, 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 components, each mechanically connected to the clutch device, is separated and thus no torque via the Coupling device can be transmitted. For this purpose, a coupling device preferably has at least two coupling parts, the two coupling parts being mechanically, preferably rotationally connected to one another in a closed state of the coupling device, in particular frictionally or positively, and independently in an open state

from each other, in particular, are rotatable relative to each other.

Furthermore, it can be advantageous if at least one 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 coupling device. Several elements of the extended Ravigneaux transmission can therefore be connected to the primary drive shaft. At least one, namely the second element, is preferably connected to it. Are several coupling devices

provided, these are preferably switchable independently of one another.

It is also advantageous if the second element of the extended Ravigneaux transmission, preferably the planet carrier shaft, has a first braking device

can be blocked.

A braking device in the sense of the invention is used to releasably secure at least one component non-rotatably connected to the braking device, in particular to releasably secure at least one gear element, in particular to releasably secure the associated gear element to a gear housing surrounding the gear. When the braking device is activated, i.e. when the braking device is closed, the fixed gear element cannot be moved and thus preferably cannot rotate and is therefore blocked in particular in its rotational movement. When the brake device is open, however, the gear element is preferably provided in at least one of its

Degrees of freedom movable.

Furthermore, it can be provided that at least a third element of the expanded

Ravigneaux gear, preferably a second sun gear shaft, with at least

a second braking device can be blocked. Several elements of the extended Ravigneaux transmission can therefore be connected to braking devices. At least one element, namely the third element, is preferably connected to it and can be braked. If several braking elements are provided, these are

preferably switchable independently of one another.

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

Coupling device is rotatable.

In the case of a vehicle, it is also particularly advantageous if an output shaft of the transmission arrangement with at least one drivable axis of the

Vehicle is rotatably or rotatably connected.

The invention is explained in more detail below with reference to the non-restrictive figures

explained. 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

Design variant;

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

2a shows a drive system according to the invention in a second

Design 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;

4a shows a drive system according to the invention in a fourth

Design variant;

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

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

Design variant;

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 an eighth drive system according to the invention

Design variant;

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

9 shows a drive system according to the invention in a ninth

Design variant;

10a shows a drive system according to the invention in a tenth

Design variant;

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

11a shows a drive system according to the invention in an eleventh

Design variant;

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

11a shows a drive system according to the invention in an eleventh

Design variant;

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

Functionally identical parts are given the same reference numerals in the designs

Mistake.

The drive systems 21 shown in the figures with gear arrangements 1 of a motor vehicle each have an extended Ravigneaux planetary set 2 with an upstream further gear 3,

wherein the further transmission 3 as one formed by a minus gear

Reducing planetary set or designed as a two-stage spur gear. In addition, a primary drive 7 designed as an internal combustion engine is over

a primary drive shaft 12 is connected to the transmission arrangement 1.

The extended Ravigneaux planetary gear set 2, essentially formed by a double planetary gear, has a first sun gear 11a and a second sun gear 6a, which are connected to a corresponding first sun gear shaft 11 and a second sun gear shaft 6, and at least one second ring gear connected to a second ring gear shaft 4 4a on. A set of first planet gears 9a mesh with a first ring gear 5a, which is arranged 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 planet 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

provides.

An output shaft 15 is driven with the differential (final drive) FD

Axis, in particular with the front wheels, of the vehicle rotatably connected.

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

Output shaft 14 of the further transmission 3 is provided.

The primary drive shaft 12 can be rotatably connected to the first ring gear shaft 5 via a first coupling device C1. The primary drive shaft 12 is also connected to the planet carrier shaft 17 via a third coupling device C3. 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, thereby activating the brake

can be fixed to the housing.

Fig. 1b shows a switching matrix of the clutch devices C1, C2, C3 and the braking device B2 for the transmission arrangement shown in Fig. 1a, an "X" representing the activated, i.e. closed state of the corresponding clutch devices C1, C2, C3 or braking device B2. By activating two of the clutch devices C1, C2, C3 or the braking device B2, a total of six forward gears g1-g6 can be shifted

become.

2a shows a second embodiment according to the invention, with a secondary drive 18 in the form of an electrical machine. The secondary drive 18 is slowed down via a non-shiftable secondary gear 19

translated before it is rotatably connected to the extended Ravigneaux gear 2.

The secondary drive 18 is via the secondary gear 19 in the first

Embodiment with the first ring gear shaft 5 rotatably connected.

FIG. 2b shows the corresponding switching matrix for FIG. 2a. The operating modes (gear step ranges) g1 to g6 are forward gears for the drive only by the prime mover 21, and E1 is a gear in which the secondary drive is only driven. This is achieved when only the second braking device B2 is activated. Due to the large number of switching modes, charging gears L1 to L3 can also be achieved by activating only one clutch device C1C3 each, in which the primary drive 7 supplies the secondary drive 18 with power when the vehicle is stationary and the vehicle's batteries are thus 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 g1-g6, a purely electric gear E1 and, in addition, also stationary ones

Loading modes are made possible.

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 by advantageously operating the primary drive stationary and the secondary drive 21 either as a generator or in a first operating range is operated by a motor in a second operating range. This is a stepless

Electrodynamic start-up possible, which creates a separate start-up element such as

Example, a hydrodynamic torque converter or a starting clutch can be omitted. Switching from stepless power split operation to

one of the five shiftable gears g1-g5 can be done while driving.

Reversing is possible by driving the secondary drive in the opposite direction in shift mode E1, which is the case with electrical machines

is easily possible.

During operation in one of the shiftable gears g1 to g6, the secondary operation 18 can optionally be operated as a generator or as a motor in order to provide hybrid functions such as "boosting", recuperation ",

Enable "load point shift" or "sailing".

3 shows a third embodiment which is very similar to the first, the further gear 3 being designed as a simple planetary gear. Another sun gear is fixed to the housing, the input shaft 13 is connected to a further 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 switching forms of this embodiment 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. This means that there are more switching modes

possible, as can be seen in Fig. 4b.

Eight forward gears g1-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. 3. 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.

Thus, nine forward gears g1-g9 and one reverse gear ER, in which

only the secondary drive can be switched.

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. Correspondingly, this also applies to this embodiment

Switching matrix from Fig. 6b.

FIG. 8a shows an eighth embodiment similar to that from FIG. 6a, but no secondary drive is provided. Accordingly, as can be seen in FIG. 8b, a total of nine forward gears g1-g9 and one reverse gear R result.

FIG. 9 shows a ninth embodiment like that from FIG. 7, but also without

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. As shown, the secondary clutch device 20 is preferably arranged between the secondary gear and the first sun gear shaft 11. From the

Switching matrix in Fig. 10b, the switching modes can be seen.

11a and 12a show eleventh and twelfth embodiments in which, as in the tenth embodiment, the secondary drive can be rotatably connected to the first sun gear shaft 11. 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 can be seen in FIGS. 11b and 12b.

The embodiments from FIGS. 10a, 11a, and 12a all have spur gears as further gears 3, these embodiments naturally also being conceivable with planetary gears as further gears 3. For example, a planetary gear like the further gear 3 in the embodiment from FIG. 3

be used.

Claims (1)

PATENT CLAIMS Gear arrangement (1) with a primary drive shaft (12) for rotary connection with a primary drive (7) and with an expanded Ravigneaux gear (2) and a further gear (3) connected upstream of the expanded Ravigneaux gear (2), the expanded Ravigneaux gear Gear (2) comprises a double planetary gear with two sun gear shafts (6,11), a planet carrier shaft (17) and two ring gear shafts (4,5), characterized in that a first ring gear shaft (5) of the extended Ravigneaux gear (2) with the primary drive shaft (12) by means of a first coupling device (C1) is rotatable. Gear arrangement (1) according to claim 1, characterized in that the extended Ravigneaux gear (2) has a first gear set and in this first gear set first planet gears (9a) of a planet carrier (16) connected to the planet carrier shaft (17) with a first sun gear (11a) mesh with a first sun gear shaft (11) and with a first ring gear (5a) of the first ring gear shaft (5), and that the extended Ravigneaux gear (2) has a second gear set and in this second gear set second planet gears (10a) of the Planet carrier (16) mesh with a second sun gear (6a) of a second sun gear shaft (6), with a second ring gear (4a) of a second ring gear shaft (4) and that each first planet gear (9a) also meshes with a second planet gear (10a) . Gear arrangement (1) according to Claim 1 or 2, characterized in that an output shaft (15) with a second ring gear shaft (4) is rotatably connected or rotatable. Gear arrangement (1) according to one of claims 1 to 3, characterized in that the further gear (3) is a simple planetary set, wherein preferably a further sun gear shaft is fixed to the housing, an output shaft is preferably rotatably connected to a further planet carrier shaft and a further ring gear shaft with the Primary drive shaft (17) is rotatably connected. 11. 12th 15th Gear arrangement (1) according to one of claims 1 to 3, characterized in that the further gear (3) has a spur gear is preferably two stages. Gear arrangement (1) according to one of Claims 1 to 5, characterized in that at least one element of the extended Ravigneaux gear (2) is or can be rotatably connected to a secondary drive (18) which is particularly preferably an electrical machine. Gear arrangement (1) according to claim 6, characterized in that the secondary drive (18) with a first ring gear shaft (5) of the extended Ravigneaux gear (3) is rotatably connected or rotatably connected. Gear arrangement (1) according to claim 6, 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. Gear arrangement (1) according to one of claims 6 to 8, characterized in that the secondary drive (18) is rotatably or rotatably connected to the extended Ravigneaux gear (3) via a secondary gear (19), the magnitude of the gear ratio of the secondary gear (19 ) is preferably greater than 1. Gear arrangement (1) according to one of claims 1 to 9, characterized in that an output shaft (14) of the further gear (3) with at least one first element of the extended Ravigneaux gear (2), preferably a first sun gear shaft (11), by means of a second Coupling device (C2) is rotatable. Gear arrangement (1) according to one of Claims 1 to 10, characterized in that at least one second element of the extended Ravigneaux gear (2), preferably the planet carrier shaft (17), is connected to the primary drive shaft (12) by means of a third clutch device (C3) is rotationally connected. Gear arrangement (1) according to claim 11, characterized in that the second element of the extended Ravigneaux gear (2), preferably the planet carrier shaft (17), with a first braking device (B1) can be blocked. 13. Gear arrangement (1) according to one of claims 1 to 10, characterized in that at least a third element of the extended Ravigneaux gear (2), preferably a second sun gear shaft (6), with at least one second braking device (B2) can be blocked. 14. Transmission arrangement (1) according to claim 13, characterized in that the third element of the extended Ravigneaux transmission (2) with an output shaft (14) of the further transmission (3) by means of a fourth Coupling device (C4) is rotatable. 15. 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) is connected to the gear arrangement (1) via a primary drive shaft (12) ) is rotatable or rotatably connected, characterized in that the gear arrangement (1) is designed according to one of claims 1 to 14. 16. Motor vehicle, in particular hybrid vehicle, with a drive system (21) with a transmission arrangement (1), characterized in that the transmission arrangement (1) is designed according to one of claims 1 to 14 and preferably the drive system (21) according to claim 15 is formed. 17. Motor vehicle according to claim 15, characterized in that an output shaft (15) of the transmission arrangement (1) is rotatably or rotatably connected to at least one drivable axle of the vehicle. 04.10.2019 MT