US 2015/0087472 A1 · MULTI-SPEED GEARBOX

Abstract

Transmission comprising four planetary gear sets, shafts and six shift elements. Sun of first set is connected to fifth shaft, which is connected to sun of second set and is couplable to housing by second brake. Driveshaft is connectable by first clutch to fourth shaft connected to carrier of second set and is couplable by first brake to housing. Driveshaft is connectable by second clutch to seventh shaft connected to ring gear of second set and sun of third set, and is connectable by third clutch to eighth shaft connected to carrier of third set. Eighth shaft is connectable by fourth clutch to third shaft connected to ring gear of fourth set. Sixth shaft is connected to ring gear of third set and carrier of first set. Sun of fourth set is coupled to housing. Output shaft is connected to carrier of fourth set and ring gear of first set.

Claims17

Dependent claims

1-7. (canceled)

A multi-stage transmission of a planetary design comprising:

a drive shaft (1),
an output shaft (2),
first, second, third and fourth planetary gear sets (P1, P2, P3, P4) being arranged within a housing (G),
third, fourth, fifth, six, seventh and eighth rotatable shafts (3, 4, 5, 6, 7, 8),
six shift elements (04, 05, 14, 17, 18, 38) comprising brakes (38, 04) and clutches (14, 17, 18, 38), and selective engagement of the six shift elements (04, 05, 14, 17, 18, 38) generating different transmission ratios between the drive shaft (1) and the output shaft (2) such that nine forward gears and one reverse gear are implementable,
wherein the fifth shaft (5) is connected to both the sun gear of the first planetary gear set (P1) and the sun gear of the second planetary gear set (P2), and the fifth shaft (5) is couplable to the housing (G) by engagement of a second brake (05),
the drive shaft (1) is detachably connected to the fourth shaft (4) by engagement of a first clutch (14), the fourth shaft (4) is connected to the carrier of the second planetary gear set (P2), and the fourth shaft (4) is couplable by engagement of a first brake (04) to the housing (G),
the drive shaft (1) is detachably connected by engagement of a second clutch (17) to the seventh shaft (7) which is connected to both the ring gear of the second planetary gear set (P2) and the sun gear of the third planetary gear set (P3),
the drive shaft (1) is detachably connected by engagement of a third clutch (18) to the eighth shaft (8), and the eighth shaft (8) is connected to the carrier of the third planetary gear set (P3), the eighth shaft is detachably connectable, by engagement of a fourth clutch (38), to the third shaft (3) which is connected to the ring gear of the fourth planetary gear set (P4),
the sixth shaft (6) is connected to both the ring gear of the third planetary gear set (P3) and the carrier of the first planetary gear set (P1),
the sun gear of the fourth planetary gear set (P4) is coupled to the housing (G), and
the drive shaft (2) is connected to the carrier of the fourth planetary gear set (P4) and the ring gear of the first planetary gear set (P1).

9 more elements

A multi-stage transmission of a planetary design comprising:

a drive shaft,
an output shaft,
first, second, third and fourth planetary gear sets being arranged within a housing, and each of the four planetary gear sets comprises a sun gear, a ring gear and planet gears,
third, fourth, fifth, six, seventh and eighth rotatable shafts,
six shift elements comprising brakes and clutches, and selective engagement of the six shift elements generating different transmission ratios between the drive shaft and the output shaft such that nine forward gears and one reverse gear are implementable,
wherein the fifth shaft is connected to both the sun gear of the first planetary gear set and the sun gear of the second planetary gear set, and the fifth shaft is couplable to the housing by engagement of a second brake,
the drive shaft is detachably connected to the fourth shaft by engagement of a first clutch, the fourth shaft is connected to the carrier of the second planetary gear set, and the fourth shaft is couplable by engagement of a first brake to the housing,
the drive shaft is detachably connected by engagement of a second clutch to the seventh shaft which is connected to both the ring gear of the second planetary gear set and the sun gear of the third planetary gear set,
the drive shaft is detachably connected by engagement of a third clutch to the eighth shaft, and the eighth shaft is connected to the carrier of the third planetary gear set, the eighth shaft is detachably connectable, by engagement of a fourth clutch, to the third shaft which is connected to the ring gear of the fourth planetary gear set,
the sixth shaft is connected to both the ring gear of the third planetary gear set and the carrier of the first planetary gear set,
the sun gear of the fourth planetary gear set is coupled to the housing, and
the output shaft is directly connected to both the carrier of the fourth planetary gear set and the ring gear of the first planetary gear set.

9 more elements

Dependencies are inferred from the claim text.

Facts

Application

14/396,070Filed 13 Mar 2013

Priority

DE 10 2012 206 773.625 Apr 2012

Published

26 Mar 2015

Term ends

Not estimatedThe source records don’t support an estimate.

Classification9 codes

F16H 3/66
Gearings having three or more central gears: composed of a number of gear trains without drive passing from one train to another
F16H 2003/445
Using gears having orbital motion: without permanent connection between the input and the set of orbital gears
F16H 2200/0065
Characterised by the number of forward speeds: the gear ratios comprising nine forward speeds
F16H 2200/0082
Transmissions for multiple ratios: characterised by the number of reverse speeds

Multi-speed gearbox

Life of this patent

Multi-speed gearbox

Life of this patent

Abstract

Claims17