DE102020123172A1 - Transmission arrangement and electrically operable drive train of a motor vehicle - Google Patents

Abstract

The invention relates to a transmission arrangement (1), comprising a first interface (4) for coupling a motor (5), in particular one that can be driven electrically, and a second interface (6), the transmission arrangement (1) for at least two-speed, switchable transmission of the drive torque of the motor (5) is formed between the first interface (4) and the second interface (6) of the gear arrangement (1), the gear arrangement (1) having a housing (14) for receiving a planetary gear (8), with a sun wheel (9 ) and a first group of planet gears (10) rotating between a first ring gear (11) and the sun gear (9), and a second group of planet gears (12) rotating between a second ring gear (13) and the sun gear (9 ) Rotate, and wherein the first group of planetary gears (10) and the second group of planetary gears (12) are axially offset from one another on common planetary gear axes (21) rotatably mounted, which in one The planetary carrier (15) arranged coaxially to the sun gear (9) is arranged concentrically to the sun gear (9), the first ring gear (11) being coupled to a first switching device (16) which blocks the rotation of the first ring gear (11) and / or brakes and / or releases and the second ring gear (13) is coupled to a second switching device (17) which blocks and / or brakes and / or releases the rotation of the second ring gear (13).

Description

The present invention relates to a transmission arrangement, in particular for use in an electrically operable drive train of a motor vehicle, comprising a first interface for coupling an in particular electrically drivable motor and a second interface, in particular for coupling a functional module, such as a differential device, decoupling unit, parking lock unit, torque -Vectoring module or the like, wherein the gear arrangement is designed for at least two-speed, switchable transmission of the drive torque of the motor between the first interface and the second interface of the gear arrangement, the gear arrangement having a housing for accommodating a planetary gear, with a sun gear and a first group of planetary gears rotating between a first ring gear and the sun gear, and a second group of planetary gears rotating between a second ring gear and the sun gear rotate, and wherein the first group of planetary gears and the second group of planetary gears are rotatably mounted axially offset to one another on common planetary gear axes of rotation, which are arranged concentrically to the sun gear in a planetary carrier arranged coaxially to the sun gear, the first ring gear being coupled to a first switching device which blocks and/or brakes and/or releases the rotation of the first ring gear and the second ring gear is coupled to a second switching device which blocks and/or brakes and/or releases the rotation of the second ring gear, the first group of planetary gears has a first pitch diameter, and the second set of planetary gears has a second pitch diameter, the first pitch diameter being greater than the second pitch diameter. The invention also relates to an electrically operable drive train of a motor vehicle.

Electric motors are increasingly being used to drive motor vehicles in order to create alternatives to internal combustion engines that require fossil fuels.

An article in the ATZ magazine, volume 113, 05/2011, pages 360-365 by Erik Schneider, Frank Fickl, Bernd Cebulski and Jens Liebold shows an electric drive with the title: Highly integrative and flexible electric drive unit for electric vehicles.

the DE 10 2011 007 260 A1 describes a drive device with an electrical machine, a manual transmission, with a differential that can be driven by the electrical machine via the manual transmission, with a torque-resistant first operative connection between a first drive shaft of the electrical machine and the manual transmission.

the DE 10 2009 059 903 A1 describes a system for variable torque distribution within a motor vehicle axle with a main drive and a torque vectoring motor.

The invention is based on the object of proposing a transmission arrangement, in particular for use in an electrically operable drive train of a motor vehicle, which has a particularly compact design and is very easy to assemble. The invention is also based on the object of realizing an electrically operable drive train of a motor vehicle that is particularly compact.

This object is achieved on the one hand by a transmission arrangement, in particular for use in an electrically operable drive train of a motor vehicle, comprising a first interface for coupling an in particular electrically drivable motor and a second interface, in particular for coupling a functional module, such as a differential device, decoupling unit, Parking lock unit, torque vectoring module, or the like, wherein the transmission arrangement is designed for at least two-speed, switchable translation of the drive torque of the engine between the first interface and the second interface of the transmission arrangement, the transmission arrangement having a housing for accommodating a planetary gear, with a Sun gear and a first group of planetary gears rotating between a first ring gear and the sun gear, and a second group of planetary gears which rotate between a second ring gear and the son inner wheel rotate, and wherein the first group of planetary gears and the second group of planetary gears are rotatably mounted axially offset to one another on common planetary gear axes of rotation, which are arranged concentrically to the sun gear in a planetary carrier arranged coaxially to the sun gear, the first ring gear having a first switching device is coupled, which blocks and/or brakes and/or releases the rotation of the first ring gear and the second ring gear is coupled to a second switching device which blocks and/or brakes and/or releases the rotation of the second ring gear, the first group of Planet gears has a first pitch circle diameter, and the second group of planet gears has a second pitch circle diameter, the first pitch circle diameter being larger than the second pitch circle diameter, the first group of planet gears facing the motor side in the axial direction and the second group of planet enwheel faces the function module side in the axial direction, and the first switching device and the second switching device are positioned at least in sections radially above the second ring gear, the first ring gear being positioned via a first ring gear carrier by means of a first group of at least two roller bearings for absorbing at least one axial force relative to the housing and is rotatably mounted on the planet carrier, and the second ring gear is rotatably mounted via a second ring gear carrier by means of a second group of at least two roller bearings for absorbing at least one axial force relative to the planet carrier and a functional module that can be coupled to the second interface.

This achieves the advantage that the transmission arrangement can be made particularly compact. A further advantage of the transmission arrangement according to the invention is that it can be combined in a very simple manner with other functional units, such as a differential device, decoupling unit, parking lock unit, torque vectoring module or the like.

For the purposes of this application, motor vehicles are land vehicles that are moved by machine power without being tied to railroad tracks. A motor vehicle can be selected, for example, from the group of passenger cars (cars), trucks (lorries), mopeds, light motor vehicles, motorcycles, buses (COM) or tractors.

The transmission arrangement can be coupled in particular to an electric motor which is designed to generate a drive torque for the motor vehicle. The drive torque is particularly preferably a main drive torque, so that the motor vehicle is driven exclusively by the drive torque. In particular, the electric motor is dimensioned in such a way that vehicle speeds of more than 50 km/h, preferably more than 80 km/h and in particular more than 100 km/h can be achieved. The electric motor particularly preferably has an output of more than 30 kW, preferably more than 50 kW and in particular more than 70 kW.

According to an advantageous embodiment of the invention, it can be provided that the second interface of the transmission arrangement is formed by an annular, axially extending coupling section of the planetary carrier, which is arranged in the radial direction below the second group of planetary gears and is configured for torque-transmitting coupling with the functional module. The advantage of this configuration is that the transmission arrangement can be designed to be particularly compact axially.

According to a further preferred development of the invention, it can also be provided that the first group of planet wheels and the second group and, if present, further groups of planet wheels are operatively connected to one another in a torque-transmitting manner, in particular are designed as double planets. As a result, the ease of assembly of the transmission arrangement can be further optimized since only one component has to be handled during assembly. Furthermore, tolerance chains can be reduced since, for example, splines for coupling the planet gears that are subject to tolerances can be dispensed with.

Furthermore, according to a likewise advantageous embodiment of the invention, it can be provided that the planetary carrier is designed in two parts. The advantageous effect of this configuration is based on the fact that the planetary carrier can be designed to be particularly easy to assemble.

According to a further particularly preferred embodiment of the invention, it can be provided that the coupling section of the planetary carrier is designed as an internal spline, as a result of which the compact design of the transmission arrangement can be further optimized.

Furthermore, the invention can also be further developed such that the first group of at least two roller bearings and/or the second group of at least two roller bearings is/are designed as axial roller bearings, in particular as axial needle roller bearings. The advantage of this configuration is that axial forces can be absorbed by particularly low-friction and compact bearing elements.

In a likewise preferred embodiment variant of the invention, it can also be provided that the first shifting device and/or the second shifting device is/are designed as a brake. In this way it can be achieved that the gear arrangement can be shifted between at least two gear stages in a particularly reliable and efficient manner.

It can also be advantageous to further develop the invention such that the housing is shaped like a pot, with a cylindrical ring-shaped housing shell extending in the axial direction and a housing base extending in the radial direction. Due to the pot-like design, a particularly easy-to-install embodiment is made possible, in which the individual components of the transmission arrangement can be inserted axially into the housing one after the other and are held there.

According to a further preferred embodiment of the subject matter of the invention, it can be provided that the non-rotating part of the first brake and/or the second brake is/are arranged non-rotatably on the housing casing, which further optimizes the compact structure of the gear arrangement.

The object of the invention is also achieved by an electrically operable drive train of a motor vehicle, comprising a transmission arrangement according to one of Claims 1-9.

The invention will be explained in more detail below with reference to figures without restricting the general inventive idea.

• 1 eine erfindungsgemäße Getriebeanordnung in einer schematischen Axialschnittansicht,
• 2 einen Detailausschnitt des Planetengetriebes der aus der 1 bekannten Getriebeanordnung in einer Axialschnittansicht, und
• 3 ein Kraftfahrzeug mit einer erfindungsgemäßen Getriebeanordnung in einer schematischen Blockschaltansicht.

Show it:

• 1 a transmission arrangement according to the invention in a schematic axial sectional view,
• 2 a detail of the planetary gear from the 1 known gear assembly in an axial section, and
• 3 a motor vehicle with a transmission arrangement according to the invention in a schematic block circuit view.

the 1 shows an embodiment of a transmission arrangement 1 according to the invention, in particular for use in an electrically operable drive train 2 of a motor vehicle 3, as is the case, for example, in FIG 2 is shown.

The transmission arrangement includes a first interface 4 for coupling an electrically drivable motor 5 and a second interface 6 for coupling a functional module 7, such as a differential device, decoupling unit, parking lock unit, torque vectoring module, or the like. Of course, the function module 7 can also be a housing cover in its simplest embodiment. It is also conceivable that the functional module 7 is designed as an adapter for connection to an output shaft and/or cardan shaft.

The transmission arrangement 1 is designed for at least two-speed, switchable transmission of the drive torque of the motor 5 between the first interface 4 and the second interface 6 of the transmission arrangement 1, which will be discussed in more detail below.

The gear arrangement 1 has a housing 14 for accommodating a planetary gear 8. The planetary gear 8 comprises a sun gear 9 and a first group of planetary gears 10 which rotate between a first ring gear 11 and the sun gear 9. Furthermore, the planetary gear 8 has a second group of planet gears 12 which rotate between a second ring gear 13 and the sun gear 9 . The first group of planetary gears 10 and the second group of planetary gears 12 are rotatably mounted axially offset to one another on common planetary gear axes of rotation 21 , which are arranged concentrically to the sun gear 9 in a planetary carrier 15 arranged coaxially to the sun gear 9 .

The first ring gear 11 is coupled to a first switching device 16 which blocks and/or brakes and/or releases the rotation of the first ring gear 11 . Analogous to this, the second ring gear 13 is coupled to a second switching device 17 which blocks and/or brakes and/or releases the rotation of the second ring gear 13 . The rotation control of the first ring gear 11 and the second ring gear 13 that can be implemented herewith allows the planetary gear 8 to be switched to different transmission or reduction stages. The first switching device 16 and the second switching device 17 are designed as a brake in the embodiment shown.

The first group of planetary gears 10 have a first pitch circle diameter and the second group of planetary gears 12 has a second pitch circle diameter, the first pitch circle diameter being greater than the second pitch circle diameter, which is good from the 1 is removable. the 1 It is also easy to see that the first group of planetary gears 10 and the second group of planetary gears are designed as double planets.

The first group of planet wheels 10 faces the motor side 24 in the axial direction and the second group of planet wheels 12 faces the functional module side 25 in the axial direction. The first switching device 16 and the second switching device 17 are positioned radially above the second ring gear 13, as a result of which a particularly compact design of the transmission arrangement 1 can be implemented.

The axial bearing of the planetary gear 8 is explained in more detail below and is particularly good from the synopsis of 1 with the detail view of 2 removable. The first ring gear 11 is rotatably mounted on a first ring gear carrier 19 by means of a first group of at least two roller bearings 20 for absorbing at least one axial force relative to the housing 14 and the planetary carrier 15 . The first group of roller bearings 20 is in the radial direction on the Height of the planetary gear axes 21 arranged. The first group of roller bearings 20 comprises a first thrust roller bearing 28 and a second thrust roller bearing 29 which are spaced apart axially, the ring gear carrier 19 being accommodated in the axial space between the thrust roller bearings 28,29. A first race of the first axial roller bearing 28 is supported in the axial direction on the radially running housing bottom 27 of the housing 14 . The second race of the first axial roller bearing 28 rests against the ring gear carrier 19 and is supported on this in the axial direction. The first race of the second axial roller bearing 29 is also in contact with the ring gear carrier 19, while the second race is supported on the planet carrier 15 in the axial direction.

The second ring gear 13 is rotatably mounted via a second ring gear carrier 22 by means of a second group of at least two roller bearings 23 for absorbing at least one axial force relative to the planet carrier 15 and a function module 7 that can be coupled to the second interface 6 . The second group of roller bearings 23 comprises a third thrust roller bearing 30 and a fourth thrust roller bearing 31 which are spaced apart axially, the second ring gear carrier 22 being accommodated in the axial space between the thrust roller bearings 30,31. A first race of the third axial roller bearing 30 is supported in the axial direction on the radially running section 32 of the functional module 7 . The second race of the third axial roller bearing 30 rests against the second ring gear carrier 22 and is supported on this in the axial direction. The first race of the fourth axial roller bearing 31 is also in contact with the second ring gear carrier 22, while the second race is supported on the planetary carrier 15 in the axial direction.

In the embodiment shown, the first group of at least two roller bearings 20 and the second group of at least two roller bearings 23 are designed as axial needle bearings. The first group of roller bearings 20 includes identical axial needle bearings, and the second group of rolling elements 23 includes identical axial needle bearings. The first group of rolling bearings 20 and the second group of rolling bearings 23 are coaxially aligned with each other.

From the 1 It can also be seen that the second interface 6 of the transmission arrangement 1 is formed by an annular, axially running coupling section 18 of the planetary carrier 15, which is arranged in the radial direction below the second group of planetary gears 12 and is configured for torque-transmitting coupling with the functional module 7. The coupling section 18 of the planet carrier 15 is designed here as an internal spline. This makes it possible during assembly of the transmission arrangement 1 to center the functional module 7 by inserting an axially extending section 33 of the functional module 7 and provided with a corresponding spline, to center the functional module 7 in the transmission arrangement 1 and to transmit torque to the coupling section 16 of the planetary carrier 15 connect to. At the same time, the radially running section 32 of the functional module 7 forms a bearing for the second group of rolling elements 23.

The assembly of the gear assembly 1 can be done from the open side of the pot-shaped housing 14 . The housing 14 has a cylindrical housing shell 26 extending in the axial direction and a housing base 27 extending in the radial direction.

Finally shows the 3 a motor vehicle 3 with an electrically operable drive train 2, comprising a transmission arrangement 1, as from 1-2 is known. the 3 shows in particular the connection of the transmission arrangement 1 to an electric motor 5 to form an electrically operable drive train 2. Such an electrically operable drive train 2 is also referred to as an e-axle. In principle, it is possible to drive the two wheels of a vehicle axle via a common drive train 2 (left embodiment) and/or to equip each vehicle wheel with a separate drive train 2 (right embodiment).

The invention is not limited to the embodiments shown in the figures. The foregoing description is therefore not to be considered as limiting but as illustrative. The following patent claims are to be understood in such a way that a mentioned feature is present in at least one embodiment of the invention. This does not exclude the presence of other features. If the patent claims and the above description define 'first' and 'second' feature, this designation serves to distinguish between two similar features without establishing a ranking.

Reference List

1

gear arrangement

2

powertrain

3

motor vehicle

4

interface

5

engine

6

interface

7

function module

8th

planetary gear

9

sun gear

10

planet gears

11

ring gear

12

planet gears

13

ring gear

14

housing

15

planet carrier

16

switching device

17

switching device

18

coupling section

19

ring gear carrier

20

roller bearings

21

planetary gear axes

22

ring gear carrier

23

roller bearings

24

engine side

25

function module page

26

housing jacket

27

caseback

28

thrust roller bearing

29

thrust roller bearing

30

thrust roller bearing

31

thrust roller bearing

32

section

33

section

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 102011007260 A1 [0004]
• DE 102009059903 A1 [0005]

Claims (10)

Transmission arrangement (1), in particular for use in an electrically operable drive train (2) of a motor vehicle (3), comprising a first interface (4) for coupling an electrically drivable motor (5) and a second interface (6), the transmission arrangement ( 1) is designed for at least two-speed, switchable transmission of the drive torque of the engine (5) between the first interface (4) and the second interface (6) of the gear arrangement (1), the gear arrangement (1) having a housing (14) for receiving a planetary gear (8) having a sun gear (9) and a first group of planet gears (10) rotating between a first ring gear (11) and the sun gear (9), and a second group of planet gears (12) which rotate between a second ring gear (13) and the sun gear (9), and wherein the first group of planetary gears (10) and the second group of planetary gears (12) are axially offset from one another on common Planetary wheel axes of rotation (21) are rotatably mounted, which are arranged concentrically to the sun wheel (9) in a planetary carrier (15) arranged coaxially to the sun wheel (9), the first ring gear (11) being coupled to a first switching device (16), which blocks and/or brakes and/or releases the rotation of the first ring gear (11) and the second ring gear (13) is coupled to a second switching device (17) which blocks and/or brakes the rotation of the second ring gear (13) and /or releases, the first group of planetary gears (10) having a first pitch circle diameter, and the second group of planetary gears (12) having a second pitch circle diameter, the first pitch circle diameter being greater than the second pitch circle diameter, characterized in that the first group of planet wheels (10) faces the motor side (24) in the axial direction and the second group of planet wheels (12) faces the functional modules in the axial direction te (25), and the first shifting device (16) and the second shifting device (17) are positioned at least in sections radially above the second ring gear (13), the first ring gear (11) being positioned via a first ring gear carrier (19) by means of a first group of at least two roller bearings (20) for absorbing at least one axial force relative to the housing (14) and the planetary carrier (15), and the second ring gear (13) via a second ring gear carrier (22) by means of a second group of at least two roller bearings (23) for absorbing at least one axial force relative to the planetary carrier (15) and a functional module (7) that can be coupled to the second interface (6). Transmission arrangement (1) according to claim 1 , characterized in that the second interface (6) of the transmission arrangement (1) is formed by an annular, axially extending coupling section (18) of the planetary carrier (15), which is arranged in the radial direction below the second group of planetary gears (12) and for torque-transmitting Coupling with the function module (7) is configured. Transmission arrangement (1) according to one of the preceding claims, characterized in that the first group of planet wheels (10) and the second group and, if present, further groups of planet wheels (12) are operatively connected to one another in a torque-transmitting manner, in particular are designed as double planets. Transmission arrangement (1) according to one of the preceding claims, characterized in that the planet carrier (15) is designed in two parts. Transmission arrangement (1) according to one of the preceding claims, characterized in that the coupling section (18) of the planet carrier (15) is designed as an internal spline. Transmission arrangement (1) according to one of the preceding claims, characterized in that the first group of at least two roller bearings (20) and/or the second group of at least two roller bearings (23) is/are designed as axial roller bearings, in particular as axial needle bearings. Transmission arrangement (1) according to one of the preceding claims, characterized in that the first switching device (16) and/or the second switching device (17) is/are designed as a brake. Transmission arrangement (1) according to one of the preceding claims, characterized in that the housing (14) is pot-shaped, with a cylindrical ring-shaped housing jacket (26) extending in the axial direction and a housing base (27) extending in the radial direction. Transmission arrangement (1) according to one of Claims 7 or8, characterized in that the non-rotating part of the first brake (16) and/or the second brake (17) is/are arranged on the housing shell (26) in a rotationally fixed manner. Electrically operable drive train (2) of a motor vehicle (3), comprising a transmission arrangement (1) according to one of the preceding claims.

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