Gearing for a motor vehicle, and a drive train with same
A transmission for a motor vehicle has an input shaft, output shaft, first and second minus planetary gear sets, and first electric machine with a rotationally fixed stator and a rotatable rotor connectable to the input shaft. The first planetary gear set is stepped and has planet gears of a larger and a smaller effective diameter. In the first planetary gear set, first sun gear engages the larger planet gears and is connected or connectable to the rotor; second sun gear engages the smaller planet gears and is connected to a sun gear of the second planetary gear set and connectable to the input shaft; a carrier is connected to a ring gear of the second planetary gear set; and a ring gear is rotationally fixable. In the second planetary gear set, the carrier is connectable to the input shaft and the ring gear is connected to the output shaft.
1. A transmission (G) for a motor vehicle, comprising:
an input shaft (GW 1 );
an output shaft (GW 2 );
a first planetary gear set (P 1 ), wherein the first planetary gear set is a stepped planetary gear set and comprises planet gears (PL 1 ) having two different effective diameters;
a second planetary gear set (P 2 ); and
a first electric machine (EM 1 ) with a rotationally fixed stator (S 1 ) and a rotatable rotor (R 1 );
wherein the first and the second planetary gear sets (P 1 , P 2 ) are minus gear sets;
a first sun gear (E 111 ) of the first planetary gear set (P 1 ) engages with the larger effective diameter planet gears (PL 1 ), the first sun gear (E 111 ) of the first planetary gear set (P 1 ) is either permanently connected or connectable by an auxiliary shift element (K) to the rotor (R 1 ) of the first electric machine (EM 1 );
a second sun gear (E 112 ) of the first planetary gear set (P 1 ) engages with the smaller effective diameter planet gears (PL 1 ), the second sun gear (E 112 ) is permanently connected to a sun gear (E 12 ) of the second planetary gear set (P 2 );
a carrier (E 21 ) of the first planetary gear set (P 1 ) is permanently connected to a ring gear (E 32 ) of the second planetary gear set (P 2 );
the input shaft (GW 1 ) is connectable by a first shift element ( 18 ) to the carrier (E 22 ) of the second planetary gear set (P 2 ), the input shaft (GW 1 ) is connectable by a second shift element ( 14 ) to the second sun gear (E 112 ) of the first planetary gear set (P 1 ), and the input shaft (GW 1 ) is connectable by a third shift element ( 13 ) to the rotor (R 1 ) of the first electric machine (EM 1 );
the output shaft (GW 2 ) is connected to the ring gear (E 32 ) of the second planetary gear set (P 2 ); and
a ring gear (E 31 ) of the first planetary gear set (P 1 ) is rotationally fixable by a fourth shift element ( 06 ).
2. The transmission (G) according to claim 1 , wherein the first sun gear (E 111 ) of the first planetary gear set (P 1 ) is rotationally fixable by a fifth shift element ( 03 ).
3. The transmission (G) according to claim 2 , wherein:
the first sun gear (E 111 ) of the first planetary gear set (P 1 ) is permanently connected to the rotor (R 1 );
at least five forward gear ratios (G 1 , G 2 , G 3 , G 4 , G 5 ) between the input shaft (GW 1 ) and the output shaft (GW 2 ) are selectable by selective actuation of the first, second, third, fourth and fifth shift elements ( 18 , 14 , 13 , 06 , 03 );
the first forward gear ratio (G 1 ) realized by closing the fourth shift element ( 06 ) and the third shift element ( 13 );
the second forward gear ratio (G 2 ) realized by closing the fourth shift element ( 06 ) and the second shift element ( 14 );
the third forward gear ratio (G 3 ) realized by closing the fourth shift element ( 06 ) and the first shift element ( 18 );
the fourth forward gear ratio (G 4 ) realized by closing the first shift element ( 18 ) and optionally the third shift element ( 13 ) or the second shift element ( 14 ); and
the fifth forward gear ratio (G 5 ) realized by closing the first shift element ( 18 ) and either by closing the fifth shift element ( 03 ) or by supporting the first sun gear (E 111 ) of the first planetary gear set (P 1 ) with the first electric machine (EM 1 ).
4. The transmission (G) according to claim 2 , wherein:
the first sun gear (E 111 ) of the first planetary gear set (P 1 ) is connectable to the rotor (R 1 ) of the first electric machine (EM 1 ) by the auxiliary shift element (K);
at least five forward gear ratios (G 1 , G 2 , G 3 , G 4 , G 5 ) between the input shaft (GW 1 ) and the output shaft (GW 2 ) are shiftable by selective actuation of the first, second, third, fourth and fifth shift elements ( 18 , 14 , 13 , 06 , 03 ) and of the auxiliary shift element (K);
the first forward gear ratio (G 1 ) realized by closing the fourth shift element ( 06 ), the third shift element ( 13 ) and the auxiliary shift element (K);
the second forward gear ratio (G 2 ) realized by closing the fourth shift element ( 06 ), the second shift element ( 14 ) and the auxiliary shift element (K);
the third forward gear ratio (G 3 ) realized by closing the fourth shift element ( 06 ), the first shift element ( 18 ) and the auxiliary shift element (K);
the fourth forward gear ratio (G 4 ) realized by closing the first shift element ( 18 ), the auxiliary shift element (K) and optionally the third shift element ( 13 ) or the second shift element ( 14 ); and
the fifth forward gear ratio (G 5 ) realized by closing the first shift element ( 18 ) and the fifth shift element ( 03 ).
5. The transmission (G) according to claim 2 , wherein:
the first sun gear (E 111 ) of the first planetary gear set (P 1 ) is connectable to the rotor (R 1 ) of the first electric machine (EM 1 ) by the auxiliary shift element (K);
at least five forward gear ratios (G 1 , G 2 ′, G 3 ′, G 4 , G 5 ) between the input shaft (GW 1 ) and the output shaft (GW 2 ) are shiftable by selective actuation of the first, second, third, fourth and fifth shift elements ( 18 , 14 , 13 , 06 , 03 ) and of the auxiliary shift element (K);
the first forward gear ratio (G 1 ) realized by closing the fourth shift element ( 06 ), the third shift element ( 13 ) and the auxiliary shift element (K);
the second forward gear ratio (G 2 ) realized by closing the fourth shift element ( 06 ) and the second shift element ( 14 );
the third forward gear ratio (G 3 ′) realized by closing the fourth shift element ( 06 ) and the first shift element ( 18 );
the fourth forward gear ratio (G 4 ) realized by closing the first shift element ( 18 ), the auxiliary shift element (K) and optionally the third shift element ( 13 ) or the second shift element ( 14 ); and
the fifth forward gear ratio (G 5 ) realized by closing the first shift element ( 18 ) and the fifth shift element ( 03 ).
6. The transmission (G) according to claim 1 , wherein the first, second and fourth shift elements ( 18 , 14 , 06 ) are dog-clutches, and the third shift element ( 13 ) is a multi-plate clutch.
7. The transmission (G) according to claim 6 , wherein the first shift element ( 18 ) and the third shift element ( 13 ) are closed in the fourth forward gear ratio (G 4 ), and the first shift element ( 18 ) and the second shift element ( 14 ) are actuatable by a common actuation mechanism.
8. The transmission (G) according to claim 1 , wherein the first, second and third shift elements ( 18 , 14 , 13 ) are multi-plate clutches, and the fourth shift element ( 06 ) is a dog-clutch.
9. The transmission (G) according to claim 8 , wherein the first sun gear (E 111 ) of the first planetary gear set (P 1 ) is permanently connected to the rotor (R 1 ) of the first electric machine (EM 1 ), the transmission (G) has a sixth forward gear ratio (G 6 ) which is realized by closing the second shift element ( 14 ) and either by closing the fifth shift element ( 03 ) or by supporting the first sun gear (E 111 ) of the first planetary gear set (P 1 ) with the first electric machine (EM 1 ).
10. The transmission (G) according to claim 8 , wherein the transmission (G) has the auxiliary shift element (K) and the fifth shift element ( 03 ), and the sixth forward gear ratio (G 6 ) is realized by closing the fifth shift element ( 03 ) and the second shift element ( 14 ).
11. The transmission (G) according to claim 1 , wherein the carrier (E 22 ) of the second planetary gear set (P 2 ) is rotationally fixable by a sixth shift element ( 08 ), and a first reverse gear ratio (GR) is realized by closing the sixth shift element ( 08 ), the third shift element ( 13 ) and the auxiliary shift element (K).
12. The transmission (G) according to claim 11 , wherein, in addition to or alternatively to the first reverse gear ratio (GR), a second reverse gear ratio (GR 2 ) is realized by closing the sixth shift element ( 08 ) and the second shift element ( 14 ).
13. The transmission (G) according to claim 11 , wherein the second planetary gear set (P 2 ) has a second ring gear (E 322 ) which is connected to the output shaft (GW 2 ), the connection between the carrier (E 22 ) of the second planetary gear set (P 2 ) and the sixth shift element ( 08 ) leading through and between the two ring gears (E 32 , E 322 ) of the second planetary gear set (P 2 ).
14. The transmission (G) according to claim 11 , wherein the fourth shift element ( 06 ) and the sixth shift element ( 08 ) are actuatable by a common actuation mechanism.
15. The transmission (G) according to claim 11 , wherein the sixth shift element ( 08 ) and the auxiliary shift element (K) are closed and all further shift elements ( 18 , 14 , 13 , 06 , 03 , 07 ) are open and the torque acting at the output shaft (GW 2 ) is continuously variable through variation of the torque acting at the rotor (R 1 ) of the first electric machine (EM 1 ) in a second electric operating mode (E 2 ).
16. The transmission (G) according to claim 11 , wherein the sixth shift element ( 08 ) and the fourth shift element ( 06 ) are closable to provide a parking lock (P).
17. The transmission (G) according to claim 1 , wherein:
the ring gear (E 31 ) of the first planetary gear set (P 1 ) engages with the larger effective diameter planet gears (PL 1 ) and is rotationally fixable by the fourth shift element ( 06 ); and
a second ring gear (E 312 ) of the first planetary gear set (P 1 ) engages with the smaller effective diameter planet gears (PL 1 ), and the second ring gear (E 312 ) of the first planetary gear set (P 1 ) is rotationally fixable by a seventh shift element ( 07 ).
18. The transmission (G) according to claim 17 , wherein:
the seventh shift element ( 07 ) is open in the first through sixth forward gear ratios (G 1 -G 6 ); and
the seventh shift element ( 07 ), the third shift element ( 13 ) and the auxiliary shift element (K) are closed in a seventh forward gear ratio (G 7 ).
19. The transmission (G) according to claim 1 , wherein the transmission (G) has a second electric machine (EM 2 ) with a rotationally fixed stator (S 2 ) and a rotatable rotor (R 2 ), and the rotor (R 2 ) of the second electric machine (EM 2 ) is permanently connected to the input shaft (GW 1 ).
20. The transmission (G) according to claim 1 , wherein in a first electrodynamic operating mode (EDA 1 ), the second shift element ( 14 ) and the auxiliary shift element (K) are closed and all further shift elements ( 18 , 13 , 06 , 03 , 08 , 07 ) are open, the torque acting at the output shaft (GW 2 ) being continuously variable through variation of the torque acting at the input shaft (GW 1 ) and of the torque acting at the rotor (R 1 ) of the first electric machine (EM 1 ).
21. The transmission (G) according to claim 1 , wherein the first shift element ( 18 ) and the auxiliary shift element (K) are closed and all further shift elements ( 14 , 13 , 06 , 03 , 08 , 07 ) are open and the torque acting at the output shaft (GW 2 ) is continuously variable through variation of the torque acting at the input shaft (GW 1 ) and of the torque acting at the rotor (R 1 ) of the first electric machine (EM 1 ) in a second electrodynamic operating mode (EDA 2 ).
22. The transmission (G) according to claim 1 , wherein the fourth shift element ( 06 ) and the auxiliary shift element (K) are closed and all further shift elements ( 18 , 14 , 13 , 03 , 08 , 07 ) are open and the torque acting at the output shaft (GW 2 ) is continuously variable through variation of the torque acting at the rotor (R 1 ) of the first electric machine (EM 1 ) in a first electric operating mode (E 1 ).
23. The transmission (G) according to claim 1 , wherein all shift elements ( 18 , 14 , 13 , 06 , 03 , 08 , 07 ) are actuatable by a closed hydraulic system which comprises a pressure accumulator or by an electromechanical actuation system.
24. A drivetrain for a motor vehicle, wherein the drivetrain comprises the transmission (G) of claim 1 , an internal combustion engine (VKM), and an axle transmission (AG) connected to wheels (DW) of the motor vehicle,
wherein the input shaft (GW 1 ) of the transmission (G) is connected to the internal combustion engine (VKM) by at least one torsional vibration damper (TS);
the output shaft (GW 2 ) of the transmission (G) is operatively connected to the axle transmission (AG); and
the motor vehicle is driven by the internal combustion engine (VKM) alone in the forward gear ratios (G 1 -G 5 ; G 6 ; G 7 ), by interaction of the internal combustion engine (VKM) and the first electric machine (EM 1 ) in a first and second electrodynamic operating modes (EDA 1 , EDA 2 ), and by the first electric machine (EM 1 ) alone in the first electric operating mode (E 1 ).