Transmission for a motor vehicle

Patent metadata

Field	Value
Publication number	US-10570995-B2
Application number	US-201615744424-A
Country	US
Kind code	B2
Filing date	Jun 21, 2016
Priority date	Jul 21, 2015
Publication date	Feb 25, 2020
Grant date	Feb 25, 2020

Abstract

A transmission (G) for a motor vehicle includes a drive shaft (GW 1 ), an output shaft (GW 2 ), a first and a second planetary gear set (P 1 , P 2 ), and a first, second, third, fourth and fifth shift element ( 04, 13, 14, 26, 36 ). Six forward gear ratios ( 1 - 6 ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) are engagable through selective pairwise closure of the five shift elements ( 04, 13, 14, 26, 36 ) and rotationally fixed immobilization of the sun gear (E 11 ) of the first planetary gear set (P 1 ).

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 first planetary gear set (P 1 ) and a second planetary gear set (P 2 ); and
a first shift element ( 04 ), a second shift element ( 13 ), a third shift element ( 14 ), a fourth shift element ( 26 ) and a fifth shift element ( 36 ),
wherein 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 ),
wherein the output shaft (GW 2 ) is permanently connected to a carrier (E 22 ) of the second planetary gear set (P 2 ),
wherein the carrier (E 21 ) of the first planetary gear set (P 1 ) is rotationally fixable by closing the first shift element ( 04 ),
wherein the drive shaft (GW 1 ) is connectable to a sun gear (E 12 ) of the second planetary gear set (P 2 ) by closing the second shift element ( 13 ),
wherein the drive shaft (GW 1 ) is connectable to the carrier (E 21 ) of the first planetary gear set (P 1 ) by closing the third shift element ( 14 ),
wherein a ring gear (E 31 ) of the first planetary gear set (P 1 ) is connectable to the output shaft (GW 2 ) by closing the fourth shift element ( 26 ),
wherein the ring gear (E 31 ) of the first planetary gear set (P 1 ) is connectable to the sun gear (E 12 ) of the second planetary gear set (P 2 ) by closing the fifth shift element ( 36 ), and
wherein a sun gear (E 11 ) of the first planetary gear set (P 1 ) is either permanently rotationally fixed or switchably rotationally fixable.

2. The transmission (G) of claim 1 , wherein six forward gear ratios ( 1 - 6 ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) are engagable through selective pairwise closure of the first, second, third, fourth and fifth shift elements ( 04 , 13 , 14 , 26 , 36 ) and rotationally fixed immobilization of the sun gear (E 11 ) of the first planetary gear set (P 1 ), wherein
the first forward gear ratio ( 1 ) is realized by closing the first shift element ( 04 ) and the second shift element ( 13 ),
the second forward gear ratio ( 2 ) is realized by closing the second shift element ( 13 ) and the fourth shift element ( 26 ),
the third forward gear ratio ( 3 ) is realized by closing the second shift element ( 13 ) and the fifth shift element ( 36 ),
the fourth forward gear ratio ( 4 ) is realized by closing the second shift element ( 13 ) and the third shift element ( 14 ),
the fifth forward gear ratio ( 5 ) is realized by closing the third shift element ( 14 ) and the fifth shift element ( 36 ), and
the sixth forward gear ratio ( 6 ) is realized by closing the third shift element ( 14 ) and the fourth shift element ( 26 ).

3. The transmission (G) of claim 1 , wherein the first shift element ( 04 ), the second shift element ( 13 ), or both the first and second shift elements ( 04 , 13 ) is formed as a positively locking shift element.

4. The transmission (G) of claim 1 , wherein an external interface (GW 1 -A) of the drive shaft (GW 1 ) is arranged coaxially with an external interface (GW 2 -A) of the output shaft (GW 2 ), the external interfaces (GW 1 -A, GW 2 -A) of the drive shaft (GW 1 ) and the output shaft (GW 2 ) are arranged at opposite axial ends of the transmission (G), and the second planetary gear set (P 2 ) is positioned axially further from the external interface (GW 1 -A) of the drive shaft (GW 1 ) than the first planetary gear set (P 1 ).

5. The transmission (G) of claim 1 , wherein an external interface (GW 1 -A) of the drive shaft (GW 1 ) is arranged coaxially with an external interface (GW 2 -A) of the output shaft (GW 2 ), the external interfaces (GW 1 -A, GW 2 -A) of the drive shaft (GW 1 ) and the output shaft (GW 2 ) are arranged at a common axial end of the transmission (G), and the second planetary gear set (P 2 ) is positioned axially closer to the external interface (GW 1 -A) of the drive shaft (GW 1 ) than the first planetary gear set (P 1 ).

6. The transmission (G) of claim 1 , further comprising an electric motor (EM) with a rotationally fixed stator (S) and a rotatable rotor (R), wherein the rotor (R) is permanently connected either to the drive shaft (GW 1 ) or to the sun gear (E 12 ) of the second planetary gear set (P 2 ).

7. The transmission (G) of claim 6 , wherein the rotor (R) is permanently connected to the sun gear (E 12 ) of the second planetary gear set (P 2 ), and a superposition operating mode (EDA) is realized by closing the third shift element ( 14 ) and by rotationally fixing the sun gear (E 11 ) of the first planetary gear set (P 1 ).

8. The transmission (G) of claim 1 , further comprising a sixth shift element ( 05 ) and a seventh shift element ( 15 ), wherein the sun gear (E 11 ) of the first planetary gear set (P 1 ) is rotationally fixable by closing the sixth shift element ( 05 ), and the drive shaft (GW 1 ) is connectable to the sun gear (E 11 ) of the first planetary gear set (P 1 ) by closing the seventh shift element ( 15 ).

9. The transmission (G) of claim 8 , wherein the sixth and seventh shift elements ( 05 , 15 ) are positively locking shift elements that are actuatable by a common actuating mechanism.

10. The transmission (G) of claim 8 , wherein a first reverse gear ratio (R 1 ) between drive shaft (GW 1 ) and output shaft (GW 2 ) is realizable by closing the first shift element ( 04 ), the seventh shift element ( 15 ) and the fifth shift element ( 36 ).

11. The transmission (G) of claim 10 , wherein a second reverse gear ratio (R 2 ) is realizable by closing the first shift element ( 04 ), the seventh shift element ( 15 ) and the fourth shift element ( 26 ).

12. The transmission (G) of claim 1 , wherein the first planetary gear set (P 1 ) is a stepped planetary gear set such that the first planetary gear set (P 1 ) has planet gears (PL 1 ) with a smaller effective diameter and a larger effective diameter, the sun gear (E 11 ) of the first planetary gear set (P 1 ) meshes with the smaller effective diameter of the planet pears (PL 1 ), and the ring gear (E 31 ) of the first planetary gear set (P 1 ) meshes with the larger effective diameter of the planet gears (PL 1 ).

13. The transmission (G) of claim 12 , wherein an additional sun gear (E 112 ) of the first planetary gear set (P 1 ) meshes with the larger effective diameter of the planet gears (PL 1 ), and the drive shaft (GW 1 ) is connectable to the additional sun gear (E 112 ) by closing an additional shift element ( 15 b ).

14. The transmission (G) of claim 13 , wherein a reverse gear ratio (R 1 b , R 2 b , R 3 b ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) is formable by closing the additional shift element ( 15 b ) and the second, fifth or fourth shift element ( 13 , 36 , 26 ).

15. The transmission (G) of claim 12 , wherein an additional ring gear (E 312 ) of the first planetary gear set (P 1 ) meshes with the planet gears (PL 1 ) with the smaller effective diameter, and the output shaft (GW 2 ) is connectable to the additional ring gear (E 312 ) by closing a further additional shift element ( 27 ).

16. The transmission (G) of claim 15 , wherein eight forward gear ratios ( 1 b - 8 b ) between the drive shaft (GW 1 ) and the output shaft (GW 2 ) are engageable through selective pairwise closure of the first through fifth shift elements ( 04 , 13 , 14 , 26 , 36 ) and of the further additional shift element ( 27 ), wherein
the first forward gear ratio ( 1 b ) is realized by closing the first shift element ( 04 ) and the second shift element ( 13 ),
the second forward gear ratio (

Assignees

• Zahnradfabrik Friedrichshafen

Inventors

• Beck Stefan
• Wechs Michael
• Brehmer Martin
• Kaltenbach Johannes
• Münch Eckehard
• Warth Viktor
• King Julian
• Moraw Jens
• Scharr Stephan
• Horn Matthias
• Griesmeier Uwe
• Ziemer Peter
• Pawlakowitsch Juri
• Knöpke Bernd
• Niederbrucker Gerhard
• Kuberczyk Raffael

Classifications

• F16H2200/2043

  with five engaging means · CPC title

• F16H2200/2046

  with six engaging means · CPC title

• B60K2006/4816

  Electric machine connected or connectable to gearbox internal shaft · CPC title

• F16H3/66

  composed of a number of gear trains without drive passing from one train to another · CPC title

• F16H3/663 Primary

  with conveying rotary motion between axially spaced orbital gears, e.g. a stepped orbital gear or Ravigneaux · CPC title