Drive device for a motor vehicle

Abstract

A transmission comprises a first planetary stage that has a first planetary gear train with a first set of planet gears configured to rotate on a first planet carrier and mesh with a first sun gear and a first ring gear, a second planetary stage wherein the second planetary stage has a second planetary gear train with a second set of planet gears, wherein the second set of planet gears are configured to rotate on a second planet carrier and mesh with a second sun gear and a second ring gear, wherein the first planet carrier is connected to the second sun gear, wherein the first sun gear is operatively connected to a drive shaft, a differential stage operatively connected to the second planet carrier and configured to distribute power, and a double-clutch device that includes a first and second clutch and is located between the planetary stages.

Claims

1. A drive device for a motor vehicle, comprising: an electric drive machine connected to a transmission via a drive shaft, wherein the transmission has at least first and second planetary stages and a differential stage, wherein the first planetary stage has a first planetary gear train with numerous planet gears, wherein the planet gears of the first planetary gear train can rotate on a first planet carrier and mesh with a first sun gear and a first ring gear, wherein the second planetary stage has a second planetary gear train with numerous planet gears, wherein the planet gears of the second planetary gear train can rotate on a second planet carrier and mesh with a second sun gear and a second ring gear, wherein the first planet carrier is connected to the second sun gear for conjoint rotation therewith, wherein the drive shaft is operatively connected to first sun gear, wherein the second ring gear is also secured in a stationary manner to a housing, wherein the first planet carrier is fixed to the second sun gear, and wherein the second planet carrier is directly connected to the differential stage, wherein a double-clutch device with a first and second power-shiftable clutches is located axially between the first and second planetary stages, wherein the first and second power-shiftable clutches are radially-nested frictions clutches, wherein the first ring gear is connected to the second sun gear via the first clutch such that the first ring gear and the second sun gear rotate in unison when the first clutch is engaged, and wherein the first ring gear is rotationally fixed to the second planet carrier via the second clutch such that the first ring gear and the second planet carrier rotate in unison when the second clutch is engaged.

2. The drive device according to claim 1, wherein when the first and second power-shiftable clutch are disengaged, power transfer is shut off.

3. The drive device of claim 2, wherein when the first clutch is engaged, and the second clutch is disengaged, a first transmission ratio is obtained, wherein when the second clutch is engaged and the first clutch is disengaged, a second transmission ratio is obtained.

4. The drive device of claim 3, wherein the first transmission ratio differs from the second transmission ratio.

5. The drive device of claim 1, wherein the electric drive machine has a stator and a rotor, wherein the rotor is connected to the drive shaft for conjoint rotation therewith.

6. The drive device of claim 1, wherein the differential stage is a spur gear differential, wherein the differential stage distributes a drive power of the drive machine to a first and second output shafts.

7. The drive device of claim 1, wherein the drive machine is coaxial to the differential stage.

8. A drive device for a motor vehicle, comprising: an electric drive machine; a transmission connected to the electric drive machine via a drive shaft, wherein the transmission includes: a first planetary stage, wherein the first planetary stage has a first planetary gear train with a first set of planet gears configured to rotate on a first planet carrier and mesh with a first sun gear and a first ring gear; a second planetary stage wherein the second planetary stage has a second planetary gear train with a second set of planet gears, wherein the second set of planet gears are configured to rotate on a second planet carrier and mesh with a second sun gear and a second ring gear, wherein the first planet carrier is connected to the second sun gear for conjoint rotation therewith, wherein the drive shaft is operatively connected to the first sun gear, wherein the second ring gear is also secured to a housing, wherein the first planet carrier is fixed to the second sun gear; a differential stage directly connected to the second planet carrier; and a double-clutch device including a first and second clutches located axially between the first and second planetary stages, wherein the first and second clutches are radially-nested frictions clutches, wherein the first ring gear is rotationally fixed to the second sun gear via the first clutch such that the first ring gear and the second sun gear rotate in unison when the first clutch is engaged, and wherein the first ring gear is rotationally fixed to the second planet carrier via the second clutch such that the first ring gear and the second planet carrier rotate in unison when the second clutch is engaged.

9. The drive device of claim 8, wherein the first and second clutches are configured to shut off power transfer when disengaged.

10. The drive device of claim 8, wherein the double-clutch device is configured to: have a first transmission ratio when the first clutch is engaged and the second clutch is disengaged; and have a second transmission ratio when the first clutch is disengaged and the second clutch is engaged.

11. The drive device of claim 10, wherein the first transmission ratio is different than the second transmission ratio.

12. The drive device of claim 10, wherein the first transmission ratio is greater than the second transmission ratio.

13. The drive device of claim 8, wherein the electric drive machine includes a stator and a rotor, wherein the rotor is connected to the drive shaft for conjoint rotation therewith.

14. The drive device of claim 8, wherein the differential stage forms a spur gear differential and is configured to distribute a drive power from the drive machine to a first and second output shaft.

15. The drive device of claim 14, wherein the first and second output shafts are located on a common drive axis.

16. The drive device of claim 14, wherein the drive machine is coaxial to the differential stage.

17. A transmission connected to an electric drive machine, the transmission comprising: a first planetary stage, wherein the first planetary stage has a first planetary gear train with a first set of planet gears configured to rotate on a first planet carrier and mesh with a first sun gear and a first ring gear; a second planetary stage wherein the second planetary stage has a second planetary gear train with a second set of planet gears, wherein the second set of planet gears are configured to rotate on a second planet carrier and mesh with a second sun gear and a second ring gear, wherein the first planet carrier is connected to the second sun gear for conjoint rotation therewith, wherein the first sun gear is operatively connected to a drive shaft, wherein the first planet carrier is fixed to the second sun gear; a differential stage operatively connected to the second planet carrier, wherein the differential stage is configured to distribute drive power of the drive machine to a first and second output shaft; and a double-clutch device located axially between the first and second planetary stages, wherein the double-clutch device includes a first and second clutch, wherein the first and second clutch are radially-nested frictions clutches, wherein the first ring gear is rotationally fixed to the second sun gear via the first clutch such that the first ring gear and the second sun gear rotate in unison when the first clutch is engaged.

18. The transmission of claim 17, wherein the double-clutch device is configured to obtain a first transmission ratio when the first clutch is engaged and the second clutch is disengaged, and the double-clutch device is further configured to obtain a second transmission ratio when the second clutch is engaged and the first clutch is disengaged.

19. The transmission of claim 17, wherein the double-clutch device is configured to shut off power transfer and decouple the first and second output shafts from the electric drive machine when the first and second clutch are disengaged.

20. The transmission of claim 17, wherein the first ring gear is rotationally fixed to the second planet carrier via the second clutch such that the first ring gear and the second planet carrier rotate in unison when the second clutch is engaged.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) According to the FIG. 1, the drive device according to the disclosure for a motor vehicle (not shown), has an electric drive machine 1 and a transmission 3. The drive machine 1 has a stator 13 and a rotor 14. A drive power of the drive machine is supplied to the transmission 3 via a drive shaft 2, located between the drive machine 1 and the transmission 3, forming a rotor shaft.

DETAILED DESCRIPTION

(2) The transmission 3 comprises first and second planetary stages 4, 5, and a differential stage 6. The differential stage 6 is in the form of a spur gear differential, and distributes a drive power of the drive machine 1 to a first and second output shaft 15a, 15b. The drive shaft 2 is coaxial to the two output shafts 15a, 15b. Furthermore, the drive machine 1 is coaxial to the differential stage 6.

(3) The first planetary stage 4 has a first planetary gear train with numerous planet gears 7a, wherein the planet gears 7a of the first planetary gear train can rotate on a first planet carrier 8a and mesh with a first sun gear 9a and a first ring gear 10a. Furthermore, the planet gears 7a of the first planetary gear train are located radially between the first sun gear 9a and the first ring gear 10a. The drive shaft 2 is connected to the first sun gear 9a for conjoint rotation therewith.

(4) Furthermore, the second planetary stage 5 has a second planetary gear train with numerous planet gears 7b, wherein the planet gears 7b of the second planetary gear train can rotate on a planet carrier 8b and mesh with a second sun gear 9b and a second ring gear 10b. Furthermore, the planet gears 7b of the second planetary gear train are located radially between the second sun gear 9b and the second ring gear 10b. The ring gear is secured in a stationary manner to the housing 16 of the transmission 3. Furthermore, the second planet carrier 8b is operatively connected to the differential stage 6.

(5) Moreover, a double-clutch device 11 with first and second power-shiftable clutches 12a, 12b is located between the first and second planetary stages 4, 5. The first ring gear 10a can be connected via the first clutch 12a to the second sun gear 9b. Because the second sun gear 9b is connected to the first planet carrier 8a for conjoint rotation therewith, when the first clutch 12a is engaged, the first planet carrier 8a, the first ring gear 10a, and the second sun gear 9b are connected to one another for conjoint rotation. Furthermore, the first ring gear 10a can be connected to the second planet carrier 8b via the second clutch 12b. When the first clutch 12a is engaged and the second clutch 12b is disengaged, a first transmission ratio is obtained, and when the second clutch 12b is engaged, and the first clutch 12a is disengaged, a second transmission ratio is obtained. The first transmission ratio differs from the second transmission ratio. By disengaging both clutches 12a, 12b, the power transfer is shut off, wherein the drive machine 1 is decoupled from the two output shafts 15a, 15b.

REFERENCE SYMBOLS

(6) 1 drive machine 2 drive shaft 3 transmission 4 first planetary stage 5 second planetary stage 6 differential stage 7a, 7b planet gears 8a, 8b planet carriers 9a, 9b sun gears 10a, 10b ring gears 11 double-clutch device 12a, 12b clutch 13 stator 14 rotor 15a, 15b output shaft 16 housing