DE102018131492A1 - Gear device for a motor vehicle - Google Patents

Abstract

The invention relates to a gear device (1) for a motor vehicle, comprising a drive shaft (2), a switching device (3) with a first and second clutch (4a, 4b), a first, second and third planetary gear (5a, 5b, 5c) , a differential gear (6) and a spur gear stage (7), wherein the first and second planetary gear (5a, 5b) are coaxial, and wherein the third planetary gear (5c) is axially parallel to the first and second planetary gear (5a, 5b), wherein the spur gear stage (7) is effectively arranged between the second and the third planetary gear (5b, 5c), the first planetary gear (5a) also having a first sun gear (8a), a first ring gear (9a) and a first planetary gear set with a plurality of first planet gears (10a), which are rotatably mounted on a first planet carrier (11a) and mesh with the first sun gear (8a) and the first ring gear (9a), the second planetary gear (5b) having a second sun gear (8b), egg n has a second ring gear (9b) and a second planetary gear set with a plurality of second planet gears (10b) which are rotatably mounted on a second planet carrier (11b) and which mesh with the second sun gear (8b) and the second ring gear (9b), and wherein the third planetary gear (5c) has a third sun gear (8c), a third ring gear (9c) and a third planetary gear set with a plurality of third planet gears (10c) which are rotatably mounted on a third planet carrier (11c) and with the third sun gear ( 8c) and the third ring gear (9c) are in meshing engagement.

Description

The invention relates to a transmission device for a motor vehicle and a drive device with such a transmission device. In particular, the motor vehicle is electrically driven.

From the DE 10 2011 088 668 A1 is a drive device with at least one electric drive machine, with at least a first planetary gear with a clutch and with a differential. A rotor shaft of the drive machine is coupled in a rotationally fixed manner to a first connection shaft of the planetary drive formed from at least three connection shafts. A second connecting shaft of the first planetary drive can be fixed against rotation against a component of the drive device by means of a shift sleeve of the clutch. A third connection shaft of the first planetary drive is operatively connected to a sum wave of the differential. The shift sleeve can be moved in positive engagement either with the second connecting shaft of the first planetary gear or in a torque-transmitting operative connection with the sum shaft of the differential.

The object of the present invention is to provide an alternative transmission device. The object is achieved by the subject matter of patent claim 1. Preferred embodiments can be found in the dependent claims.

A transmission device according to the invention for a motor vehicle comprises a drive shaft, a switching device with a first and second clutch, a first, second and third planetary gear, a differential gear and a spur gear stage, the first and second planetary gear being coaxial, and the third planetary gear being axially parallel to that is first and second planetary gear, wherein the spur gear is effectively arranged between the second and the third planetary gear, wherein the first planetary gear further comprises a first sun gear, a first ring gear and a first planetary gear set with a plurality of first planet gears, which are rotatably mounted on a first planet carrier and are in meshing engagement with the first sun gear and the first ring gear, the second planetary gear having a second sun gear, a second ring gear and a second planetary gear set with a plurality of second planet gears which are rotatable on a second planet carrier g are supported and mesh with the second sun gear and the second ring gear, and wherein the third planetary gear has a third sun gear, a third ring gear and a third planetary gear set with a plurality of third planet gears rotatably supported on a third planet carrier and with the third Sun gear and the third ring gear are in mesh.

In other words, the spur gear stage serves to bridge an axial distance between the second planetary gear and the third planetary gear. The first and the second planetary gears rotate in particular together with the drive shaft about a drive axis, the third planetary gears rotate together with the differential gear about an output axis, and the drive axis and the output axis are formed parallel to one another.

The differential gear is designed as a spur gear differential or a bevel gear differential and is intended to distribute a drive power or a drive torque of an electrical machine that can be operatively connected to the drive shaft to a first and a second output shaft. The respective output shaft is connected in particular to a respective wheel of the motor vehicle, the two output shafts forming a drive axle of the motor vehicle.

The spur gear stage is formed from two toothings or gearwheels that mesh with one another. Two gearwheels that mesh with one another are provided for transmitting a torque and a speed from one gearwheel to the other gearwheel. A gearwheel is to be understood, for example, as a toothing, a sun gear, a ring gear and a planet gear of a planetary gear set and a spur gear.

The switching device is preferably designed as a double clutch or synchronization unit. A shifting device with two clutches is to be understood as a device which realizes at least a first and a second gear stage via the shifting of the respective clutch. The respective clutch has at least one open and one closed state and can be switched between the at least two states. In the open state, the respective clutch does not transmit any torque. Thus, the respective clutch transmits a torque between two shafts operatively connected to this respective clutch only in an at least partially closed state, the two shafts being connected to one another in a rotationally fixed manner in the closed state of this respective clutch. The respective coupling can be designed to be frictional or positive. The two couplings are preferably arranged coaxially to one another. In particular, the respective clutch can be actuated by a respective actuator in order to initiate opening or closing of the respective clutch. The actuator can be hydraulic, be electromechanically, electromagnetically or, for example, also pneumatically operable.

The invention includes the technical teaching that closing the first clutch and opening the second clutch realizes a first gear ratio, closing the second clutch and opening the first clutch realizing a second gear ratio, and opening both clutches results in a power cutoff realized. The first gear ratio is preferably not the same as the second gear ratio. For example, the first gear ratio is larger than the second gear ratio. Alternatively, the first gear ratio is smaller than the second gear ratio. For example, the first gear ratio is between 14 and 16, the second gear ratio between 7 and 8.

The first clutch is preferably designed for the rotationally fixed coupling of the drive shaft to the first sun gear. Thus, in the closed state of the first clutch, the drive shaft and the first sun gear are connected to one another in a rotationally fixed manner.

According to a preferred embodiment of the invention, the second clutch is set up for the rotationally fixed coupling of the drive shaft to the first planet carrier and the second sun gear. Thus, in the closed state of the second clutch, the drive shaft, the first planet carrier and the second sun gear are connected to one another in a rotationally fixed manner.

The first ring gear is preferably connected in a rotationally fixed manner to the second planet carrier, the second ring gear being designed to be fixed to the housing. In particular, the second ring gear is rotatably connected to a housing of the transmission device.

Furthermore, the first ring gear and the third ring gear preferably each have an external toothing, the external toothing on the first ring gear being in meshing engagement with the external toothing on the third ring gear, the third planet carrier being connected in a rotationally fixed manner to a differential carrier of the differential gear, and the third Sun gear is fixed to the housing. In other words, the first and the second ring gear are not only designed with internal teeth, but the first and the second ring gear each also have teeth on their outer circumferential surface, the two external teeth being in mesh with one another and forming the spur gear stage. The third sun gear is in particular stationary on the housing of the transmission device. The drive torque, which was translated via the three planetary gears, is fed into the differential gear via the third planet carrier.

According to a further preferred embodiment of the invention, the second clutch is designed for the rotationally fixed coupling of the drive shaft to the second ring gear. Thus, in the closed state of the second clutch, the drive shaft and the second ring gear are connected to one another in a rotationally fixed manner.

The first ring gear is preferably designed to be fixed to the housing and connected in a rotationally fixed manner to the second sun gear, the first planet carrier being connected in a rotationally fixed manner to the second planet carrier and to a first spur gear. In particular, the first ring gear and the second sun gear are rotatably connected to the housing of the transmission device.

Further preferably, the first spur gear meshes with a second spur gear, the second spur gear being connected to the third sun gear in a rotationally fixed manner, and the third ring gear being fixed to the housing, the third planet carrier being connected in a rotationally fixed manner to a differential carrier of the differential gear. In other words, the first and second spur gears meshing with one another form the spur gear stage. The third ring gear is in particular stationary on the housing of the transmission device and the drive torque, which has been translated via the three planetary gears, is fed into the differential gear via the third planet carrier.

According to a preferred embodiment of the invention, the differential gear is designed as a bevel gear differential. Two differential gears are rotatably mounted on a differential cage of the differential gear, which mesh with two bevel gears. The first bevel gear is rotatably connected to the first output shaft. Furthermore, the second bevel gear is rotatably connected to the second output shaft. The differential carrier is non-rotatably connected to the third planet carrier.

According to a further preferred embodiment of the invention, the differential gear is designed as a spur gear differential and has two planetary gear sets, each with a plurality of first and second planetary gears. The respective planet gears of the differential gear are rotatably mounted on a differential cage of the differential gear, the differential cage being designed as a planet carrier. The first planet gears of the differential gear mesh with a first spur gear, which is non-rotatably connected to the first output shaft, the second planet gears of the differential gear mesh with a second spur gear, which is non-rotatably connected to the second output shaft. Furthermore, the first are Planet gears of the differential gear in pairs with the second planet gears of the differential gear in meshing engagement. The differential carrier is non-rotatably connected to the third planet carrier.

A drive device according to the invention for a motor vehicle comprises a drive machine which is operatively connected to a transmission device according to the invention via a drive shaft. The drive machine is preferably electrical and comprises a stator and a rotor, the rotor being connected in a rotationally fixed manner to the drive shaft. The drive shaft is therefore designed as a rotor shaft.

The term “operatively connected” is to be understood to mean that two gear elements can be connected directly to one another, or that there are further gear elements between two gear elements, for example one or more shafts or gear wheels.

• 1 eine vereinfachte schematische Darstellung zur Veranschaulichung des Aufbaus einer erfindungsgemäßen Antriebsvorrichtung gemäß einem ersten Ausführungsbeispiel,
• 2 eine vereinfachte schematische Darstellung zur Veranschaulichung des Aufbaus einer erfindungsgemäßen Antriebsvorrichtung gemäß einem zweiten Ausführungsbeispiel,
• 3 eine vereinfachte schematische Darstellung zur Veranschaulichung des Aufbaus einer erfindungsgemäßen Antriebsvorrichtung gemäß einem dritten Ausführungsbeispiel, und
• 4 eine vereinfachte schematische Darstellung zur Veranschaulichung des Aufbaus einer erfindungsgemäßen Antriebsvorrichtung gemäß einem vierten Ausführungsbeispiel.

Further measures improving the invention are shown below together with the description of four preferred exemplary embodiments of the invention with reference to the figures. It shows

• 1 1 shows a simplified schematic illustration to illustrate the structure of a drive device according to the invention in accordance with a first exemplary embodiment,
• 2nd 1 shows a simplified schematic illustration to illustrate the structure of a drive device according to the invention in accordance with a second exemplary embodiment,
• 3rd a simplified schematic representation to illustrate the structure of a drive device according to the invention according to a third embodiment, and
• 4th a simplified schematic representation to illustrate the structure of a drive device according to the invention according to a fourth embodiment.

According to the 1 , 2nd , 3rd and 4th has a respective drive device according to the invention for a motor vehicle - not shown here - a drive machine 12 on that via a drive shaft 2nd with a gear device 1 is connected. The prime mover 12 is designed as an electrical machine and comprises a stator and a rotor. A drive power or a drive torque of the drive machine 12 is about the drive shaft 2nd in the gear device 1 initiated.

The gear device 1 includes the drive shaft 2nd , a switching device 3rd with a first and second clutch 4a , 4b , a first planetary gear designed as an input stage and a second planetary gear designed as a load stage 5a , 5b , a third planetary gear 5c , the axially parallel to the first and second planetary gear 5a , 5b is a differential gear 6 and a spur gear 7 . The spur gear stage 7 is effective between the second and third planetary gears 5b , 5c arranged. The first and the second planetary gear 5a , 5b are coaxial.

The first planetary gear 5a includes a first sun gear 8a , a first ring gear 9a and a first planetary gear set with a plurality of first planetary gears 10a . The first planet gears 10a are on a first planet carrier 11a rotatably and stand with the first sun gear 8a and the first ring gear 9a in meshing. The second planetary gear 5b includes a second sun gear 8b , a second ring gear 9b and a second planetary gear set with a plurality of second planet gears 10b . The second planet gears 10b are on a second planet carrier 11b rotatably mounted and stand with the second sun gear 8b and the second ring gear 9b in meshing. The third planetary gear 5c includes a third sun gear 8c , a third ring gear 9c and a third planetary gear set with a plurality of third planet gears 10c . The third planet gears 10c are on a third planet carrier 11c rotatably and stand with the third sun gear 8c and the third ring gear 9c in meshing. Because of the sectional view, there is only a single first, second and third planet gear 10a , 10b . 10c of the respective planetary gear set.

The differential gear 6 is provided to drive the drive machine 12 on a first and second output shaft 16a , 16b the transmission device 1 to distribute. There is also a differential cage 15 of the differential gear 6 rotationally fixed with the third planet carrier 11c connected. Every output shaft 16a , 16b is operatively connected to a respective wheel of the motor vehicle, not shown here. The drive shaft 2nd and the two planetary gears 5a , 5b are axially parallel to the differential gear 6 arranged. In the present are the prime mover 12 , the drive shaft 2nd and the first and second planetary gears 5a , 5b on a common drive axle 13 the transmission device 1 arranged, the differential gear 6 , the two output shafts 16a , 16b and the third planetary gear 5c on a common output axis 14 the transmission device 1 are arranged.

The switching device 3rd is designed as a double clutch in the present case. Closing the first clutch 4a and opening the second clutch 4b realizes a first gear ratio. In contrast, the second clutch is closed 4b and opening the first clutch 4a a second gear ratio. The first gear ratio is not the same as the second gear ratio. Furthermore, both clutches are opened 4a , 4b a power cut-off. Hence the drive shaft 2nd when the power is switched off from the two output shafts 16a , 16b Cut.

According to the 1 and 2nd is the first clutch 4a for the rotationally fixed coupling of the drive shaft 2nd with the first sun gear 8a set up. The second clutch 4b is for the rotationally fixed coupling of the drive shaft 2nd with the first planet carrier 11a and the second sun gear 8b set up. The first ring gear 9a is non-rotatable with the second planet carrier 11b connected, the second ring gear 9b is formed fixed to the housing. The first ring gear 9a and the third ring gear 9c each have an external toothing 7b , 7c on. The external toothing 7b on the first ring gear 9a stands with the external toothing 7c on the third ring gear 9c in meshing, the two external gears 7b , 7c the spur gear stage 7 form. The third planet carrier 11c is with a differential cage 15 of the differential gear 6 non-rotatably connected and the third sun gear 8c is designed to be fixed to the housing.

In 1 is the first planetary gear 5a axially between the switching device 3rd and the second planetary gear 5b arranged, the spur gear 7 nested radially between the first and third planetary gears 5a , 5c is trained.

In 2nd is the second planetary gear 5b axially between the switching device 3rd and the first planetary gear 5a arranged, the spur gear 7 nested radially between the first and third planetary gears 5a , 5c is trained.

According to the 3rd and 4th is the first clutch 4a for the rotationally fixed coupling of the drive shaft 2nd with the first sun gear 8a set up. The second clutch 4b is for the rotationally fixed coupling of the drive shaft 2nd with the second ring gear 9b set up. The first ring gear 9a is designed to be fixed to the housing and non-rotatable with the second sun gear 8b connected. Furthermore, the first planet carrier 11a rotatable with the second planet carrier 11b and with a first spur gear 7c connected. The first spur gear 7c stands with a second spur gear 7d in meshing, the second spur gear 7d rotatable with the third sun gear 8c connected is. The first and the second spur gear 7c , 7d form the spur gear stage 7 out. The third ring gear 9c is fixed to the housing, the third planet carrier 11c with the differential cage 15 of the differential gear 6 is rotatably connected.

In 3rd is the second planetary gear 5b axially between the switching device 3rd and the first planetary gear 5a arranged. Furthermore, the first planetary gear 5a axially between the second planetary gear 5b and the first spur gear 7c arranged. The spur gear stage 7 is thus axially adjacent to the first planetary gear 5a educated. Furthermore, the second spur gear 7d and thus also the spur gear stage 7 axially adjacent to the third planetary gear 5c educated.

In 4th is the second planetary gear 5b axially between the switching device 3rd and the first planetary gear 5a arranged. Furthermore, the first spur gear 7c axially between the first planetary gear 5a and the second planetary gear 5b arranged. The spur gear stage 7 is thus axially adjacent to the first and second planetary gears 5a , 5b educated. Furthermore, the second spur gear 7d and thus also the spur gear stage 7 axially adjacent to the third planetary gear 5c educated.

Reference symbol list

1

Gear device

2nd

drive shaft

3rd

Switching device

4a, 4b

clutch

5a, 5b, 5c

Planetary gear

6

Differential gear

7

Spur gear

7a

External teeth on the first ring gear

7b

External teeth on the third ring gear

7c

first spur gear

7d

second spur gear

8a, 8b, 8c

Sun gear

9a, 9b, 9c

Ring gear

10a, 10b, 10c

Planet gear

11a, 11b, 11c

Planet carrier

12

Prime mover

13

Drive axle

14

Output axis

15

Differential cage

16a, 16b

Output shaft

QUOTES INCLUDE IN THE DESCRIPTION

This list of documents listed by the applicant has been generated automatically and is only included 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 102011088668 A1 [0002]

Claims (10)

Gear device (1) for a motor vehicle, comprising a drive shaft (2), a switching device (3) with a first and second clutch (4a, 4b), a first, second and third planetary gear (5a, 5b, 5c), a differential gear ( 6) and a spur gear stage (7), the first and second planetary gear (5a, 5b) being coaxial, and the third planetary gear (5c) being axially parallel to the first and second planetary gear (5a, 5b), the spur gear stage (7 ) is effectively arranged between the second and the third planetary gear (5b, 5c), the first planetary gear (5a) also having a first sun gear (8a), a first ring gear (9a) and a first planetary gear set with a plurality of first planet gears (10a), which are rotatably mounted on a first planet carrier (11a) and mesh with the first sun gear (8a) and the first ring gear (9a), the second planetary gear (5b) having a second sun gear (8b), a second ring gear ( 9b) and e a second planetary gear set with a plurality of second planet gears (10b), which are rotatably mounted on a second planet carrier (11b) and are in mesh with the second sun gear (8b) and the second ring gear (9b), and wherein the third planetary gear (5c ) a third sun gear (8c), a third ring gear (9c) and a third planetary gear set with several third planet gears (10c) which are rotatably mounted on a third planet carrier (11c) and with the third sun gear (8c) and the third ring gear ( 9c) are in mesh. Gear device (1) after Claim 1 , characterized in that closing the first clutch (4a) and opening the second clutch (4b) realizes a first gear ratio, closing the second clutch (4b) and opening the first clutch (4a) realizing a second gear ratio, wherein the first gear ratio is not the same as the second gear ratio, and wherein opening both clutches (4a, 4b) realizes a power cut-off. Gear device (1) according to one of the preceding claims, characterized in that the first clutch (4a) is set up for the rotationally fixed coupling of the drive shaft (2) to the first sun gear (8a). Transmission device (1) according to one of the preceding claims, characterized in that the second clutch (4b) is set up for the rotationally fixed coupling of the drive shaft (2) to the first planet carrier (11a) and the second sun gear (8b). Gear device (1) after Claim 4 , characterized in that the first ring gear (9a) is rotatably connected to the second planet carrier (11b), the second ring gear (9b) being fixed to the housing. Gear device (1) after Claim 5 , characterized in that the first ring gear (9a) and the third ring gear (9c) also each have external teeth (7b, 7c), the external teeth (7b) on the first ring gear (9a) with the external teeth (7c) on the third The ring gear (9c) is in meshing engagement, the third planet carrier (11c) being operatively connected to a differential carrier (15) of the differential gear (6), and the third sun gear (8c) is designed to be fixed to the housing. Gear device (1) according to one of the Claims 1 to 3rd , characterized in that the second clutch (4b) is set up for the rotationally fixed coupling of the drive shaft (2) to the second ring gear (9b). Gear device (1) after Claim 7 , characterized in that the first ring gear (9a) is fixed to the housing and is non-rotatably connected to the second sun gear (8b), the first planet carrier (11a) being non-rotatably connected to the second planet carrier (11b) and to a first spur gear (7c) is. Gear device (1) after Claim 8 , characterized in that the first spur gear (7c) meshes with a second spur gear (7d), the second spur gear (7d) being non-rotatably connected to the third sun gear (8c), and the third ring gear (9c) being fixed to the housing The third planet carrier (11c) is operatively connected to a differential carrier (15) of the differential gear (6). Drive device for a motor vehicle, comprising an electric drive machine (12) connected via a drive shaft (2) with a gear device (1) according to one of the Claims 1 to 9 is connected.

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