US 8,210,982 B2Granted

Multi-step-transmission

AssigneeZF Friedrichshafen AG

InventorsGerhard Gumpoltsberger, Martin Brehmer, Peter Ziemer, Peter Tiesler, Gabor Diosi, Josef Haupt

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Abstract

A multi-step transmission including four gear sets, shafts, and shifting elements. The sun gear of gearset (P4) couples shaft (3) which communicates, via brake (03), with the housing. The carrier of gearset (P4) couples the output shaft, which couples the ring gear of gearset (P2). The ring gear of gearset (P4) couples shaft (7), which couples the carrier of gearset (P2) and, via clutch (17), communicates with the drive shaft, which communicates, via clutch (18), with the ring gear of gearset (P1) coupled to shaft (8), and, via clutch (15), communicates with shaft (5). Shaft (5) couples the sun gear of gearset (P3), and, via brake (05), communicates with the housing. The carrier of gearset (P1) couples the shaft (6), the ring gear of gearset (P3) and the sun gear of gearset (P2). The carrier of gearset (P3) couples the shaft (4), which, via brake (4), communicates with the housing.

Claims15

Dependent claims

A multi-step planetary transmission for an automobile, the transmission comprising:

an input drive shaft (1) and an output shaft (2);
first, second, third and fourth planetary gear sets (P1, P2, P3, P4) being arranged in a housing (G) of the transmission, each of the first planetary gear set (P1), the second planetary gear set (P2), the third planetary gear set (P3) and the fourth planetary gear set (P4) having a sun gear, a planet carrier and a ring gear;
at least third, fourth, fifth, sixth, seventh and eighth rotatable shafts (3, 4, 5, 6, 7, 8);
six shifting elements (03, 04, 05, 15, 17, 18) comprising first, second and third brakes (03, 05, 04) and first, second, and third clutches (17, 18, 15) and selective engagement of the six shifting elements (03, 04, 05, 15, 17, 18) achieves different gear ratios, between the drive shaft (1) and the output shaft (2), such that nine forward gears and one reverse gear can be implemented;
the sun gear of the fourth planetary gear set (P4) is coupled to the third shaft (3), and the third shaft (3) is connectable, via the first brake (03), to the housing (G) of the transmission;
the planet carrier of the fourth planetary gear set (P4) is permanently coupled to the output shaft (2), and the output shaft (2) is permanently connected to the ring gear of the second planetary gear set (P2);
the ring gear of the fourth planetary gear set (P4) is to the seventh shaft (7);
the seventh shaft (7) is connected to the planetary carrier of the second planetary gear set (P2) and is connectable, via the a first clutch (17), to the drive shaft (1);
the drive shaft (1) is connectable, via the second clutch (18), to the eighth shaft (8), and, via the third clutch (15), to the fifth shaft (5);
the eight shaft (8) is coupled to the ring gear of the first planetary gear set (P1);
the fifth shaft (5) is permanently connected to both the sun gear of the first planetary gear set (P1) and the sun gear of the third planetary gear set (P3) and is connectable, via the second brake (05), with the housing (G) of the transmission;
the planetary carrier of the first planetary gear set (P1) is coupled to the sixth shaft (6), and the sixth shaft (6) is coupled to an element which is coupled to both the ring gear of the third planetary gear set (P3) and the sun gear of the second planetary gear set (P2);
and
the planetary carrier of the third planetary gear set (P3) is coupled to the fourth shaft (4), and the fourth shaft (4) is connectable, via the third brake (04), with the housing (G) of the transmission.

11 more elements

A multi-step planetary transmission for an automobile, the transmission comprising:

an input drive shaft (1) and an output shaft (2);
first, second, third and fourth planetary gear sets (P1, P2, P3, P4) being arranged in a housing (G) of the transmission, each of the first planetary gear set (P1), the second planetary gear set (P2), the third planetary gear set (P3) and the fourth planetary gear set (P4) having a sun gear, a planet carrier and a ring gear;
at least third, fourth, fifth, sixth, seventh and eighth rotatable shafts (3, 4, 5, 6, 7, 8);
six shifting elements (03, 04, 05, 15, 17, 18) comprising first, second and third brakes (03, 05, 04) and first, second, and third clutches (17, 18, 15) and selective engagement of the six shifting elements (03, 04, 05, 15, 17, 18) for achieving different gear ratios, between the drive shaft (1) and the output shaft (2), such that nine forward gears and one reverse gear can be implemented;
the sun gear of the fourth planetary gear set (P4) being coupled brake (03), to the housing (G) of the transmission;
the planet carrier of the fourth planetary gear set (P4) being coupled to the output shaft (2), and the output shaft (2) being coupled to the ring gear of the second planetary gear set (P2);
the ring gear of the fourth planetary gear set (P4) being coupled to the seventh shaft (7);
the seventh shaft (7) being coupled to the planetary carrier of the second planetary gear set (P2) and being connectable, via the a first clutch (17), to the drive shaft (1);
the drive shaft (1) being connectable, via the second clutch (18), to the eighth shaft (8), and, via the third clutch (15), to the fifth shaft (5);
the eight shaft (8) being coupled to the ring gear of the first planetary gear set (P1);
the fifth shaft (5) being coupled to the sun gear of the first planetary gear set (P1) and the sun gear of the third planetary gear set (P3) and being connectable, via the second brake (05), with the housing (G) of the transmission;
the planetary carrier of the first planetary gear set (P1) being coupled to the sixth shaft (6), and the sixth shaft (6) being coupled to an element coupled to both the ring gear of the third planetary gear set (P3) and the sun gear of the second planetary gear set (P2);
and
the planetary carrier of the third planetary gear set (P3) being coupled to the fourth shaft (4), and the fourth shaft (4) being connectable, via the third brake (04), with the housing (G) of the transmission;
a first forward gear being implemented by engagement of the second clutch (18), the first brake (03) and the third brake (04);
a second forward gear being implemented by engagement of the first brake (03), the second brake (05) and the second clutch (18);
a third forward gear being implemented by engagement of the third clutch (15), the second clutch (18) and the first brake (03);
a fourth forward gear being implemented by engagement of the first clutch (17), the second clutch (18) and the first brake (03);
a fifth forward gear being implemented by engagement of the first clutch (17), second clutch (18) and the third clutch (15);
a sixth forward gear being implemented by engagement of the second brake (05), the first clutch (17) and the second clutch (18);
a seventh forward gear being implemented by engagement of the third brake (04), the first clutch (17) and the second clutch (18);
an eighth forward gear being implemented by engagement of the third brake (04), the second brake (05) and the first clutch (17);
a ninth forward gear being implemented by engagement of the third brake (04), the first clutch (17) and the third clutch (15);
and
the reverse gear being implemented by engagement of the first brake (03), the third brake (04) and the third clutch (15).

22 more elements

A multi-step planetary transmission for an automobile, the transmission comprising:

an input drive shaft (1) and an output shaft (2);
first, second, third and fourth planetary gear sets (P1, P2, P3, P4) being arranged in a housing (G) of the transmission, each of the first planetary gear set (P1), the second planetary gear set (P2), the third planetary gear set (P3) and the fourth planetary gear set (P4) having a sun gear, a planet carrier and a ring gear;
at least third, fourth, fifth, sixth, seventh and eighth rotatable shafts (3, 4, 5, 6, 7, 8);
six shifting elements (03, 04, 05, 15, 17, 18) comprising first, second and third brakes (03, 05, 04) and first, second, and third clutches (17, 18, 15) and selective engagement of the six shifting elements (03, 04, 05, 15, 17, 18) for achieving different gear ratios, between the drive shaft (1) and the output shaft (2), such that nine forward gears and one reverse gear can be implemented;
the sun gear of the fourth planetary gear set (P4) being connectable to the housing (G) of the transmission via the first brake (03),
the planet carrier of the fourth planetary gear set (P4) being permanently connected to the output shaft (2), and the output shaft (2) being permanently connected to the ring gear of the second planetary gear set (P2);
the ring gear of the fourth planetary gear set (P4) being permanently connected to the seventh shaft (7), the seventh shaft (7) being permanently connected to the planetary carrier of the second planetary gear set (P2), and the seventh shaft (7) being connectable, via the a first clutch (17), to the drive shaft (1);
the drive shaft (1) being connectable, via the second clutch (18), to the eighth shaft (8), and the drive shaft (1) being connectable, via the third clutch (15), to the fifth shaft (5);
the eight shaft (8) being permanently connected to the ring gear of the first planetary gear set (P1);
the fifth shaft (5) being permanently connected to both the sun gear of the first planetary gear set (P1) and the sun gear of the third planetary gear set (P3) and being releaseable connectable, via the second brake (05), with the housing (G) of the transmission;
the planetary carrier of the first planetary gear set (P1) being permanently connected to the sixth shaft (6), and the sixth shaft (6) being permanently connected to an element permanently connected to both the ring gear of the third planetary gear set (P3) and the sun gear of the second planetary gear set (P2);
and
the planetary carrier of the third planetary gear set (P3) being permanently connected to the fourth shaft (4), and the fourth shaft (4) being connectable, via the third brake (04), with the housing (G) of the transmission.

10 more elements

Dependencies are inferred from the claim text.

Facts

Application: 12/538,945Filed 11 Aug 2009
Priority: DE 10 2008 041 19513 Aug 2008
Published: US 2010/0041509 A118 Feb 2010
Granted: 3 Jul 2012
Term ends: Not estimatedThe source records don’t support an estimate.

Classification6 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 2003/442
Using gears having orbital motion: comprising two or more sets of orbital gears arranged in a single plane
F16H 2200/0065
Characterised by the number of forward speeds: the gear ratios comprising nine forward speeds
F16H 2200/2012
Characterised by the number of sets of orbital gears: with four sets of orbital gears