Transmission and drivetrain for a motor vehicle
A motor vehicle transmission comprising a drive shaft, an output shaft, a planetary gear set system, and four shift elements. The first planet gear meshes with the first sun gear, first ring gear, and with one of the second planet gears. The second planet gear meshes with the second sun gear and second ring gear. The first sun gear has a smaller diameter than the second sun gear. The first ring gear has a larger diameter than the second ring gear, and is connected to the output shaft. The second ring gear is rotationally fixable by closing the first shift element. The drive shaft is connectable to the second sun gear by closing the third shift element. The drive shaft is connectable to the planet carrier by closing the fourth shift element. The first sun gear is rotationally fixable by closing the second shift element.
1. A transmission (G) for a motor vehicle, the transmission (G) comprising:
a drive shaft (GW 1 );
an output shaft (GW 2 );
a planetary gear set system (PS) having a first sun gear (S 1 ), a second sun gear (S 2 ), a planet carrier (P), a first ring gear (H 1 ), a second ring gear (H 2 ), first planet gears (R 1 ), and second planet gears (R 2 ); and
only four shift elements, namely a first, a second, a third and a fourth shift element ( 05 , 06 , 13 , 14 );
wherein
each of the first planet gears (R 1 ) mesh with the first sun gear (S 1 ), the first ring gear (H 1 ), and a respective one of the second planet gears (R 2 ),
each of the second planet gears (R 2 ) mesh with the second sun gear (S 2 ) and the second ring gear (H 2 ),
the first and second planet gears (R 1 , R 2 ) are rotatably mounted on the planet carrier (P),
the first sun gear (S 1 ) has a smaller effective diameter than the second sun gear (S 2 ),
the first ring gear (H 1 ) has a larger effective diameter than the second ring gear (H 2 ),
the output shaft (GW 2 ) is permanently connected to the first ring gear (H 1 ),
the second ring gear (H 2 ) is rotationally fixable by closing the first shift element ( 05 ),
the drive shaft (GW 1 ) is connectable to the second sun gear (S 2 ) by closing the third shift element ( 13 ),
the drive shaft (GW 1 ) is connectable to the planet carrier (P) by closing the fourth shift element ( 14 ), and
the first sun gear (S 1 ) is rotationally fixable by closing the second shift element ( 06 ).
2. A transmission (G) for a motor vehicle, the transmission (G) comprising:
a drive shaft (GW 1 );
an output shaft (GW 2 );
a planetary gear set system (PS) having a first sun gear (S 1 ), a second sun gear (S 2 ), a planet carrier (P), a first ring gear (H 1 ), a second ring gear (H 2 ), first planet gears (R 1 ), and second planet gears (R 2 );
only four shift elements, namely a first, a second, a third and a fourth shift element ( 05 , 06 , 13 , 14 ); and
an electric motor (EM) with a rotationally fixed stator and with a rotatable rotor (R), the rotor being permanently connected to the drive shaft (GW 1 ) or to the second sun gear (S 2 ),
wherein
each of the first planet gears (R 1 ) mesh with the first sun gear (S 1 ), the first ring gear (H 1 ), and a respective one of the second planet gears (R 2 ),
each of the second planet gears (R 2 ) mesh with the second sun gear (S 2 ) and the second ring gear (H 2 ),
the first and second planet gears (R 1 , R 2 ) are rotatably mounted on the planet carrier (P),
the first sun gear (S 1 ) has a smaller effective diameter than the second sun gear (S 2 ),
the first ring gear (H 1 ) has a larger effective diameter than the second ring gear (H 2 ),
the output shaft (GW 2 ) is permanently connected to the first ring gear (H 1 ),
the second ring gear (H 2 ) is rotationally fixable by closing the first shift element ( 05 ),
the drive shaft (GW 1 ) is connectable to the second sun gear (S 2 ) by closing the third shift element ( 13 ),
the drive shaft (GW 1 ) is connectable to the planet carrier (P) by closing the fourth shift element ( 14 ), and
the first sun gear (S 1 ) is rotationally fixable by closing the second shift element ( 06 ).
3. A transmission (G) for a motor vehicle, the transmission (G) comprising:
a drive shaft (GW 1 );
an output shaft (GW 2 );
a planetary gear set system (PS) having a first sun gear (S 1 ), a second sun gear (S 2 ), a planet carrier (P), a first ring gear (H 1 ), a second ring gear (H 2 ), first planet gears (R 1 ), and second planet gears (R 2 );
a plurality of shift elements having a first, a second, a third and a fourth shift element ( 05 , 06 , 13 , 14 );
an additional shift element ( 04 ),
wherein
each of the first planet gears (R 1 ) mesh with the first sun gear (S 1 ), the first ring gear (H 1 ), and a respective one of the second planet gears (R 2 ),
each of the second planet gears (R 2 ) mesh with the second sun gear (S 2 ) and the second ring gear (H 2 ),
the first and second planet gears (R 1 , R 2 ) are rotatably mounted on the planet carrier (P),
the first sun gear (S 1 ) has a smaller effective diameter than the second sun gear (S 2 ),
the first ring gear (H 1 ) has a larger effective diameter than the second ring gear (H 2 ),
the output shaft (GW 2 ) is permanently connected to the first ring gear (H 1 ),
the second ring gear (H 2 ) is rotationally fixable by closing the first shift element ( 05 ),
the drive shaft (GW 1 ) is connectable to the second sun gear (S 2 ) by closing the third shift element ( 13 ),
the drive shaft (GW 1 ) is connectable to the planet carrier (P) by closing the fourth shift element ( 14 ),
the first sun gear (S 1 ) is rotationally fixable by closing the second shift element ( 06 ), and
the planet carrier (P) is rotationally fixable by closing the additional shift element ( 04 ).
4. The transmission (G) of claim 3 , wherein five forward gear ratios ( 1 through 5 ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) are shiftable through selective pairwise closure of the four shift elements ( 05 , 06 , 13 , 14 ),
a first forward gear ratio ( 1 ) being formed by closing the first and the third shift elements ( 05 , 13 ),
a second forward gear ratio ( 2 ) being formed by closing the second and the third shift elements ( 06 , 13 ),
a third forward gear ratio ( 3 ) being formed by closing the third and the fourth shift elements ( 13 , 14 ),
a fourth forward gear ratio ( 4 ) being formed by closing the second and the fourth shift elements ( 06 , 14 ), and
a fifth forward gear ratio ( 5 ) being formed by closing the first and the fourth shift elements ( 05 , 14 ).
5. The transmission (G) of claim 3 , wherein the planetary gear set system (PS) is arranged axially between the fourth shift element ( 14 ) and the second shift element ( 06 ).
6. The transmission (G) of claim 3 , wherein the additional shift element ( 04 ) is a positive locking shift element.
7. The transmission (G) of claim 3 , wherein the additional shift element ( 04 ) is a frictionally engaging frictional shift element, plates of the additional shift element ( 04 ) having only lining-free friction surfaces.
8. The transmission (G) of claim 3 , further comprising a second additional shift element ( 15 ), the drive shaft (GW 1 ) being connectable to the second ring gear (H 2 ) by closing the second additional shift element ( 15 ).
9. The transmission (G) of claim 8 , wherein the second additional shift element ( 15 ) is a positive locking shift element.
10. The transmission (G) of claim 8 , wherein the second additional shift element ( 15 ) is a frictionally engaging frictional shift element, plates of the second additional shift element ( 15 ) having only lining-free friction surfaces.
11. The transmission (G) of claim 3 , further comprising an electric motor (EM) with a rotationally fixed stator and with a rotatable rotor (R), the rotor being permanently connected to the drive shaft (GW 1 ) or to the second sun gear (S 2 ).
12. The transmission (G) of claim 11 , further comprising an additional transmission gearing (ST), wherein the rotor (R) is permanently connected to the drive shaft (GW 1 ) by the additional transmission gearing (ST).
13. The transmission (G) of claim 11 , further comprising an additional transmission gearing (ST), wherein the rotor (R) is permanently connected to the second sun gear (S 2 ) by the additional transmission gearing (ST).
14. The transmission (G) of claim 11 , wherein an electric gear ratio stage (E 2 ) between the rotor and the output shaft (GW 2 ) is implementable by closing the first shift element ( 05 ) when the rotor is permanently connected to the second sun gear (S 2 ).
15. The transmission (G) of claim 11 , wherein an electric gear ratio stage (E 3 ) between the rotor and the output shaft (GW 2 ) is implementable by closing the second shift element ( 06 ) when the rotor is permanently connected to the second sun gear (S 2 ).
16. The transmission (G) of claim 11 , wherein a power-split operating mode (EDA) between the drive shaft (GW 1 ), the rotor (R) and the output shaft (GW 2 ) is implementable by closing the fourth shift element ( 14 ) when the rotor is permanently connected to the second sun gear (S 2 ).
17. The transmission (G) of claim 3 , further comprising a clutch (K 0 ) between the drive shaft (GW 1 ) and a connecting shaft (AN) of the transmission (G), the connecting shaft (AN) having an interface (A) to a drive unit external to the transmission.
18. The transmission (G) of claim 17 , wherein the connecting shaft (AN) has two sections connected to each other by at least one torsional vibration damper (TS).
19. A drive train for a motor vehicle having the transmission (G) of claim 3 .