Transmission for a motor vehicle and hybrid drivetrain provided therewith

Patent metadata

Field	Value
Publication number	US-10406907-B2
Application number	US-201615574343-A
Country	US
Kind code	B2
Filing date	Apr 19, 2016
Priority date	May 19, 2015
Publication date	Sep 10, 2019
Grant date	Sep 10, 2019

Abstract

A transmission (G) for a motor vehicle including an input shaft (GW 1 ), an output shaft (GW 2 ), three planetary gear sets (P 1 , P 2 , P 3 ) with three elements each, and five shift elements (B 1 , K 1 , K 2 , K 3 , K 4 ). The third planetary gear set (P 3 ) has first and second couplings (V 1 , V 2 ), wherein the first coupling (V 1 ) is between the first elements (E 12 , E 13 ) of the second and third planetary gear sets (P 2 , P 3 ), the second coupling (V 2 ) is between the third element (E 33 ) of the third planetary gear set (P 3 ) and the output shaft (GW 2 ), and the second element (E 23 ) of the third planetary gear set (P 3 ) is permanently connected to the input shaft (GW 1 ). One of the first and second couplings (V 1 , V 2 ) is a permanently rotationally conjoint connection and the other one of the first and second couplings (V 1 , V 2 ) is a connection selectable by the third shift element (K 2 ).

First claim

The invention claimed is:

1. A transmission (G) for a motor vehicle, the transmission comprising:
an input shaft (GW 1 );
an output shaft (GW 2 );
a plurality of planetary gear sets with a first, a second and a third planetary gear set (P 1 , P 2 , P 3 );
a plurality of shift elements with a first, a second, a third, a fourth and a fifth shift element (B 1 , K 1 , K 2 , K 3 , K 4 ), the plurality of shift elements configured such that selective engagement of the plurality of shift elements realizes eight selectable forward gear ratios (G 1 -G 8 ) between the input shaft (GW 1 ) and the output shaft (GW 2 ),
wherein each of the first, second and third planetary gear sets (P 1 , P 2 , P 3 ) is either a minus gear set or a plus gear set,
wherein each of the first, second and third planetary gear sets (P 1 , P 2 , P 3 ) has
a first element (E 11 , E 12 , E 13 ) that is a sun gear of the respective first, second or third planetary gear set (P 1 , P 2 , P 3 ),
a second element (E 21 , E 22 , E 23 ) that is a carrier of the respective planetary gear set (P 1 , P 2 , P 3 ) in the case of the minus gear set or that is a ring gear of the respective first, second or third planetary gear set (P 1 , P 2 , P 3 ) in the case of the plus gear set, and
a third element (E 31 , E 32 , E 33 ) that is the ring gear of the respective planetary gear set in the case of the minus gear set or that is the carrier of the respective first, second or third planetary gear set (P 1 , P 2 , P 3 ) in the case of the plus gear set,

wherein the first element (E 11 ) of the first planetary gear set (P 1 ) is permanently rotationally fixedly immobilized,
wherein the second element (E 21 ) of the first planetary gear set (P 1 ) is permanently connected to the input shaft (GW 1 ),
wherein the second element (E 22 ) of the second planetary gear set (P 2 ) is permanently connected to the output shaft (GW 2 ),
wherein the third element (E 32 ) of the second planetary gear set (P 2 ) is rotationally fixedly immobilizable by closing the first shift element (B 1 ),
wherein the third element (E 31 ) of the first planetary gear set (P 1 ) is connectable to the first element (E 12 ) of the second planetary gear set (P 2 ) by closing the fourth shift element (K 3 ),
wherein the third element (E 31 ) of the first planetary gear set (P 1 ) is connectable to the third element (E 32 ) of the second planetary gear set (P 2 ) by closing the fifth shift element (K 4 ),
wherein the third planetary gear set (P 3 ) has a first coupling (V 1 ) and a second coupling (V 2 ), the first coupling (V 1 ) is between the first element (E 13 ) of the third planetary gear set (P 3 ) and the first element (E 12 ) of the second planetary gear set (P 2 ), and the second coupling (V 2 ) is between the third element (E 33 ) of the third planetary gear set (P 3 ) and the output shaft (GW 2 ),
wherein the second element (E 23 ) of the third planetary gear set (P 3 ) is permanently connected to the input shaft (GW 1 ),
wherein one of the first coupling (V 1 ) and the second coupling (V 2 ) is a permanently rotationally conjoint connection and the other one of the first coupling (V 1 ) and the second coupling (V 2 ) is a connection selectable by the third shift element (K 2 ),
wherein, when the first coupling (V 1 ) is the permanently rotationally conjoint connection, a rotationally conjoint connection between two of the first, second and third elements (E 13 , E 23 , E 33 ) of the third planetary gear set (P 3 ) is producible by closing the second shift element (K 1 ),
wherein, when the second coupling (V 2 ) is the permanently rotationally conjoint connection, the input shaft (GW 1 ) is connectable to the first element (E 12 ) of the second planetary gear set (P 2 ) by closing the second shift element (K 1 ), and
wherein the third element (E 31 ) of the first planetary gear set (P 1 ) is permanently rotationally conjointly connected to a rotor (R) of an electric motor (EM 1 ).

2. The transmission (G) according to claim 1 , wherein
a first forward gear ratio (G 1 ) of the eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the first shift element (B 1 ) and the second shift element (K 1 ),
a second forward gear ratio (G 2 ) of the eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the first shift element (B 1 ) and the fourth shift element (K 3 ),
a third forward gear ratio (G 3 ) of the eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the first shift element (B 1 ) and the third shift element (K 2 ),
a fourth forward gear ratio (G 4 ) of the eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the third shift element (K 2 ) and the fourth shift element (K 3 ),
a fifth forward gear ratio (G 5 ) of the eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the second shift element (K 1 ) and the third shift element (K 2 ),
a sixth forward gear ratio (G 6 ) of the eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the third shift element (K 2 ) and the fifth shift element (K 4 ),
a seventh forward gear ratio (G 7 ) of the eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the second shift element (K 1 ) and the fifth shift element (K 4 ), and
an eighth forward gear ratio (G 8 ) of the eight selectable forward gear ratios (G 1 -G 8 ) is realized by closing the fourth shift element (K 3 ) and the fifth shift element (K 4 ).

3. The transmission (G) according to claim 1 , wherein the first shift element (B 1 ) is a dog-clutch shift element.

4. The transmission (G) according to claim 1 , further comprising a connecting shaft (AN) connectable by a sixth shift element (K 0 ) to the input shaft (GW 1 ),
wherein the connecting shaft (AN) and the output shaft (GW 2 ) are arranged coaxially with respect to one another,
wherein the connecting shaft (AN) and the output shaft (GW 2 ) are arranged at opposite axial ends of the transmission (G),
wherein, proceeding from an axial end of the transmission (G) proximate the connecting shaft (AN), the first, second and third planetary gear sets (P 1 , P 2 , P 3 ) are arranged in the following axial sequence: first planetary gear set (P 1 ); second planetary gear set (P 2 ); and third planetary gear set (P 3 ).

5. The transmission (G) according to claim 4 , wherein the sixth shift element (K 0 ) is a positively locking shift element.

6. The transmission (G) according to claim 4 , wherein the sixth shift element (K 0 ) is a frictionally locking shift element with variable torque transfer capability.

7. The transmission (G) according to claim 1 , further comprising a connecting shaft (AN) connectable by a sixth shift element (K 0 ) to the input shaft (GW 1 ),
wherein, proceeding from an axial end of the transmission (G) proximate the connecting shaft (AN), the first, second and third planetary gear sets (P 1 , P 2 , P 3 ) are arranged in the following axial sequence: third planetary gear set (P 3 ); second planetary gear set (P 2 ); and first planetary gear set (P 1 ).

8. The transmission (G) according to claim 7 , wherein the sixth shift element (K 0 ) is a positively locking shift element.

9. The transmission (G) according to claim 7 , wherein the sixth shift element (K 0 ) is a frictionally locking shift element with variable torque transfer capability.

10. The transmission (G) according to claim 1 , wherein, when the first coupling (V 1 ) is the permanently rotationally conjoint connection, the first element (E 13 ) of the third planetary gear set (P 3 ) is connectable to the second element (E 23 ) of the third planetary gear set (P 3 ) by closing the second shift element (K 1 ), and the s

Assignees

• Zahnradfabrik Friedrichshafen

Inventors

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

Classifications

• F16H3/66 Primary

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

• F16H3/666

  with intermeshing orbital gears (F16H3/663 takes precedence) · CPC title

• Y10S903/919

  Stepped shift · CPC title

• F16H2200/2043

  with five engaging means · CPC title

• B60K6/547

  the transmission being a stepped gearing · CPC title