Multi-stage power-shift transmission

Patent metadata

Field	Value
Publication number	US-9506531-B2
Application number	US-201314396092-A
Country	US
Kind code	B2
Filing date	Mar 13, 2013
Priority date	Apr 27, 2012
Publication date	Nov 29, 2016
Grant date	Nov 29, 2016

Abstract

A power-shiftable multi-stage transmission in planetary design, between a drive shaft and an output shaft, in particular an automatic transmission for a vehicle. The multi-stage transmission has two parallel shaft sections, six shift elements, at least two spur-gear stages and three planetary gear sets, each of which has one sun gear, one ring gear, and one planet carrier having a plurality of planetary gears. The planet carrier is united in a carrier, and the two shaft sections can be connected to one another via the at least two spur-gear stages. Different transmission ratios between the drive shaft and the output shaft can be implemented by selective engagement of the six shift elements such that a plurality of forward gears, in particular nine forward gears, and at least one reverse gear, can be implemented.

First claim

The invention claimed is:

1. A power-shiftable multi-stage transmission ( 120 ) of a planetary design, for a vehicle ( 100 ), for installation between a drive shaft (AN) and an output shaft (AB), the mufti-stage transmission comprising:
first and second parallel shaft sections (WS 1 , WS 2 );
first, second, third and fourth clutches (K 1 , K 2 , K 3 , K 4 ) and first and second brakes (B 1 , B 2 );
at least first and second spur-gear stages (STS 1 , STS 2 );
first, second and third planetary gear sets (PS 1 , PS 2 , PS 3 ); and
each of the first, the second and the third planetary gear sets (PS 1 , PS 2 , PS 3 ) comprising a sun gear (SO 1 , SO 2 , SO 3 ), a ring gear (HO 1 , HO 2 , HO 3 ), and a planet carrier (ST 1 , ST 2 , ST 3 ) supporting a plurality of planetary gears;
wherein the first and the second shaft sections (WS 1 , WS 2 ) are connectable to one another via at least the first and the second spur-gear stages (STS 1 , STS 2 );
each of the first shift brake (B 1 ), the second shift clutch (K 2 ) and the third shift clutch (K 3 ) are directly connected to the planet carrier of the third planetary gear set (PS 3 ) for coupling the planet carrier of the third planetary gear set (PS 3 ) to other components of the mufti-stage transmission ( 120 );
different transmission ratios between the drive shaft (AN) and the output shaft (AB) are implemented by selective engagement of the first, the second, the third, and the fourth clutches (K 1 , K 2 , K 3 , K 4 ) and first and second brakes (B 1 , B 2 ) such that nine forward gears, and at least one reverse gear, are implementable.

2. The power-shiftable multi-stage transmission ( 120 ) according to claim 1 , wherein:
the first, the second and the third planetary gear sets (PS 1 , PS 2 , PS 3 ) and the drive shaft (AN) are disposed on the first shaft section (WS 1 );
the output shaft (AB) is disposed on the second shaft section (WS 2 );
the first and the second parallel shaft sections (WS 1 , WS 2 ) are connected to one another via the at least first and the second spur-gear stages (STS 1 , STS 2 );
the sun gear (SO 2 ) of the second planetary gear set (PS 2 ) and the drive shaft (AN) are connected to one another in a rotationally fixed manner to form a first connection element ( 1 );
the sun gear (SO 1 ) of the first planetary gear set (PS 1 ), a first spur gear (ST 2 a ) of the second spur-gear stage (STS 2 ), and the ring gear (HO 2 ) of the second planetary gear set (PS 2 ) are directly connected to one another and also form a second, a fourth, and a fourteenth connection element,
the second, the fourth, and the fourteenth connection elements ( 2 , 4 , 14 ) have a common connection point, and the second connection element ( 2 ) is connected to the sun gear (SO 1 ) of the first planetary gear set (PS 1 ), the fourth connection element ( 4 ) is connected to the ring gear (HO 2 ) of the second planetary gear set (PS 2 ), and the fourteenth connection element ( 14 ) is connected to the first spur gear (ST 2 a ) of the second spur-gear stage (STS 2 );
the ring gear (HO 3 ) of the third planetary gear set (PS 3 ) and the carrier (ST 2 ) of the second planetary gear set (PS 2 ) are connected to one another in a rotationally fixed manner to form a third connection element ( 3 );
a first spur gear (ST 1 a ) of the first spur-gear stage (STS 1 ) and a ring gear (HO 1 ) of the first planetary gear set (PS 1 ) form a fifth connection element ( 5 );
a second spur gear (ST 1 b ) of the first spur-gear stage (STS 1 ) and the output shaft (AB) are connected to one another and form a sixth connection element ( 6 );
the carrier (ST 1 ) of the first planetary gear set (PS 1 ) and the drive shaft (AN) are releasably connectable to one another and form a seventh connection element ( 7 );
a second spur gear (ST 2 b ) of the second spur-gear stage (STS 2 ) and the output shaft (AB) form an eighth connection element ( 8 );
the second shift clutch (K 2 ) is disposed in a power flow between the drive shaft (AN) and the carrier (ST 3 ) of the third planetary gear set (PS 3 );
the third shift clutch (K 3 ) is disposed in a power flow between the fourth connection element ( 4 ) and the carrier (ST 3 ) of the third planetary gear set (PS 3 );
the first shift brake (B 1 ) is disposed in the power flow between the carrier (ST 3 ) of the third planetary gear set (PS 3 ) and a transmission housing (GG); and
the second shift brake (B 2 ) is disposed in the power flow between the sun gear (SO 3 ) of the third planetary gear set (PS 3 ) and the transmission housing (GG).

3. The power-shiftable multi-stage transmission ( 120 ) according to claim 2 , wherein the seventh connection element ( 7 ) further comprises the first shift clutch (K 1 ), and the first shift clutch (K 1 ) is disposed in a power flow between the drive shaft (AN) and the carrier (ST 1 ) of the first planetary gear set (PS 1 ).

4. The power-shiftable multi-stage transmission ( 120 ) according to claim 2 , wherein the second connection element ( 2 ) comprises the first shift clutch (K 1 ), the first shift clutch (K 1 ) is disposed in the power flow between the first spur gear (ST 2 a ) of the second spur-gear stage (STS 2 ) and the sun gear (SO 1 ) of the first planetary gear set.

5. The power-shiftable multi-stage transmission ( 120 ) according to claim 2 , wherein the fifth connection element ( 5 ) comprises the first shift clutch (K 1 ), the first shift clutch (K 1 ) is disposed in the power flow between the ring gear (HO 1 ) of the first planetary gear set (PS 1 ) and the first spur gear (ST 1 a ) of the first spur-gear stage (STS 1 ).

6. The power-shiftable multi-stage transmission ( 120 ) according to claim 2 , wherein the sixth connection element ( 6 ) comprises the first shift clutch (K 1 ), the first shift clutch (K 1 ) is disposed in the power flow between the second spur gear (ST 1 b ) of the first spur-gear stage (STS 1 ) and the output shaft (AB).

7. The power-shiftable multi-stage transmission ( 120 ) according to claim 2 , wherein the eighth connection element ( 8 ) comprises the fourth shift clutch (K 4 ), and the fourth shift clutch (K 4 ) is disposed in the power flow between the second spur gear (ST 2 b ) of the second spur-gear stage (STS 2 ) and the output shaft (AB).

8. The power-shiftable multi-stage transmission ( 120 ) according to claim 2 , wherein the fourteenth connection element ( 14 ) comprises the fourth shift clutch (K 4 ), and the fourth shift clutch (K 4 ) is disposed in a power flow between either the fourth connection element ( 4 ) or the ninth connection element ( 9 ) and the first spur gear (ST 2 a ) of the second spur-gear stage (STS 2 ).

9. The power-shiftable multi-stage transmission ( 120 ) according to claim 1 , wherein
the second and the third planetary gear sets (PS 2 , PS 3 ) and the drive shaft (AN) are disposed on the first shaft section (WS 1 );
the first planetary gear set (PS 1 ) and the output shaft (AB) are disposed on the second shaft section (WS 2 );
the first and the second parallel shaft sections (WS 1 , WS 2 ) are connectable to one another via the first and the second spur-gear stages and a third spur-gear stage (STS 2 , STS 3 , STS 4 );
the sun gear (SO 2 ) of the second planetary gear set (PS 2 ) and the drive shaft (AN) are connected to one another in a rotationally fixed manner to form a first connection element ( 1 );
the ring gear (HO 3 ) of the third planetary gear set (PS 3 ) and the carrier (ST 2 ) of the second planetary gear set (PS 2 ) are connected to one another in a rotationally fixed manner to form a third connection element ( 3 );
the ring gear (HO 2 ) of the second planetary gear set (PS 2 ) and a first spur gear (ST 2 a ) of the sec

Assignees

• Zahnradfabrik Friedrichshafen

Inventors

• Beck Stefan

Classifications

• F16H2200/0065

  the gear ratios comprising nine forward speeds · CPC title

• F16H2200/0082

  characterised by the number of reverse speeds · CPC title

• F16H3/66 Primary

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

• F16H2003/445

  without permanent connection between the input and the set of orbital gears · CPC title

• F16H2200/201

  with three sets of orbital gears · CPC title