Vehicle transmission and drivetrain

Patent metadata

Field	Value
Publication number	US-10495187-B2
Application number	US-201715678352-A
Country	US
Kind code	B2
Filing date	Aug 16, 2017
Priority date	Aug 19, 2016
Publication date	Dec 3, 2019
Grant date	Dec 3, 2019

Abstract

A transmission includes a drive shaft, an output shaft, three planetary gear sets, and five shift elements, the first and second planetary gear sets are negative or minus gear sets. The third planetary gear set comprises three elements. The drive shaft is connected to the first element. A ring gear of the first planetary gear set is connected to the second element. The drive shaft is connectable to a sun gear of the first planetary gear set through the first shift element. The third element is rotationally fixable through the second shift element. The sun gear of the second planetary gear set is rotationally fixable through the third shift element. The planetary carrier of the second planetary gear set is rotationally fixable through the fourth shift element. The drive shaft is connectable to the planetary carrier of the second planetary gear set through the fifth shift element.

First claim

The invention claimed is:

1. A transmission (G) for a motor vehicle, comprising:
a drive shaft (GW 1 );
an output shaft (GW 2 );
a plurality of planetary gear sets having first, second and third planetary gear sets (P 1 , P 2 , P 3 ); and
a plurality of shift elements having first, second, third, fourth and fifth shift elements (A, B, C, D, E);
wherein
the first and the second planetary gear sets (P 1 , P 2 ) are negative gear sets and are in a common gear set plane (RSE) that is perpendicular to an axis of rotation of the drive shaft (GW 1 ),
the third planetary gear set (P 3 ) comprises first, second and third elements (E 13 , E 23 , E 33 ),
the drive shaft (GW 1 ) is permanently connected to the first element (E 13 ) of the third planetary gear set (P 3 ),
the output shaft (GW 2 ) is permanently connected to a ring gear (E 32 ) of the second planetary gear set (P 2 ),
a ring gear (E 31 ) of the first planetary gear set (P 1 ) is permanently connected to a sun gear (E 12 ) of the second planetary gear set (P 2 ) and to the second element (E 23 ) of the third planetary gear set (P 3 ),
a planet gear carrier (E 21 ) of the first planetary gear set (P 1 ) is permanently connected to a planet gear carrier (E 22 ) of the second planetary gear set (P 2 ),
the drive shaft (GW 1 ) is connectable to a sun gear (E 11 ) of the first planetary gear set (P 1 ) by actuating the first shift element (A),
the third element (E 33 ) of the third planetary gear set (P 3 ) is rotationally fixable by actuating the second shift element (B),
the sun gear (E 12 ) of the second planetary gear set (P 2 ) is rotationally fixable by actuating the third shift element (C),
the planet gear carrier (E 22 ) of the second planetary gear set (P 2 ) is rotationally fixable by actuating the fourth shift element (D),
the drive shaft (GW 1 ) is connectable to the planet gear carrier (E 22 ) of the second planetary gear set (P 2 ) by actuating the fifth shift element (E),
gear teeth (GW 2 A) are formed on the output shaft (GW 2 ) to transfer power to a transmission-internal or transmission-external differential transmission (AG), where the gear teeth (GW 2 A) and the plurality of planetary gear sets (P 1 , P 2 , P 3 ) are positioned in an axial sequential order of: the gear teeth (GW 2 A); the first and second planetary gear sets (P 1 , P 2 ) in the common gear set plane (RSE); and the third planetary gear set (P 3 ), and
the first shift element (A) is axially between the gear set plane (RSE) and the third planetary gear set (P 3 ).

2. The transmission (G) of claim 1 , wherein the third planetary gear set (P 3 ) is a negative gear set, the first element (E 13 ) is a sun gear of the third planetary gear set (P 3 ), the second element (E 23 ) is a planet gear carrier of the third planetary gear set (P 3 ), and the third element (E 33 ) is a ring gear of the third planetary gear set (P 3 ).

3. The transmission (G) of claim 1 , wherein the third planetary gear set (P 3 ) is a positive gear set, the first element (E 13 ) is a sun gear of the third planetary gear set (P 3 ), the second element (E 23 ) is a ring gear of the third planetary gear set (P 3 ), and the third element (E 33 ) is a planet gear carrier of the third planetary gear set (P 3 ).

4. The transmission (G) of claim 1 , wherein the gear teeth (GW 2 A) of the output shaft (GW 2 ) are axially between the fifth shift element (E) and the gear set plane (RSE).

5. The transmission (G) of claim 1 , wherein the fifth shift element (E) is radially inside the gear teeth (GW 2 A) of the output shaft (GW 2 ).

6. The transmission (G) of claim 1 , wherein the transfer of power between the gear teeth (GW 2 A) of the output shaft (GW 2 ) and the transmission-internal or transmission-external differential transmission (AG) is by a two stage spur gear set, by a chain drive, or by a single stage spur gear set and downstream planetary gear set.

7. The transmission (G) of claim 1 , wherein the third shift element (C) is at least partially radially outside the first shift element (A).

8. The transmission (G) of claim 1 , wherein the second shift element (B) and the first, second and third elements (E 13 , E 23 , E 33 ) of the third planetary gear set (P 3 ) are in a second plane (RSE 3 ) that is perpendicular to the axis of rotation of the drive shaft (GW 1 ).

9. The transmission (G) of claim 1 , wherein the fourth shift element (D) is axially directly next to the third shift element (C).

10. The transmission (G) of claim 1 , wherein the fourth shift element (D) is radially inside a rolling bearing (GW 2 L), the rolling bearing (GW 2 L) radially supporting the output shaft (GW 2 ) with respect to a rotationally fixed component of the transmission (G).

11. The transmission (G) of claim 1 , wherein the fourth shift element (D) is a positive engaging shift element.

12. The transmission (G) of claim 1 , wherein the fourth shift element (D) is a non-positive engaging frictional shift element, friction surfaces of the non-positive engaging frictional shift element having no friction linings.

13. The transmission (G) of claim 1 , further comprising an electric motor (EM).

14. The transmission (G) of claim 13 , wherein the electric motor (EM) is arranged paraxially to the drive shaft (GW 1 ) and has a rotor that is constantly connected to the drive shaft (GW 1 ).

15. The transmission (G) of claim 13 , wherein the electric motor (EM) is arranged paraxially to the drive shaft (GW 1 ) and has a rotor that is in shiftable operative connection with the drive shaft (GW 1 ) by a fixed gear ratio.

16. A drive train for a motor vehicle, the drive train comprising the transmission (G) of claim 1 and an internal combustion engine (VKM), wherein the drive shaft (GW 1 ) of the transmission (G) is directly connected in a rotationally elastic manner to the internal combustion engine (VKM) by at least one transmission-internal or transmission-external torsional vibration damper (TS) or is connectable to the internal combustion engine (VKM) by a disconnect clutch (K 0 ) and the at least one transmission-internal or transmission-external torsional vibration damper (TS), and wherein driving wheels (DW) of the motor vehicle are connected to output shafts of the transmission-internal or transmission-external differential transmission (AG).

Assignees

• Zahnradfabrik Friedrichshafen

Inventors

• Roske Michael
• Kuberczyk Raffael
• Pawlakowitsch Juri
• Unseld Bernd
• Rosemeier Thomas
• Ziemer Peter

Classifications

• B60K6/547

  the transmission being a stepped gearing · CPC title

• B60Y2200/92

  Hybrid vehicles · CPC title

• F16H2200/2094

  using positive clutches, e.g. dog clutches · CPC title

• B60K6/365 Primary

  with the gears having orbital motion · CPC title

• F16H2200/0052

  the gear ratios comprising six forward speeds · CPC title