US 8,303,455 B2Granted

Multi-ratio transmission

AssigneeZF Friedrichshafen AG

InventorsGerhard Gumpoltsberger, Christian Sibla, Stefan Beck, Josef Haupt, Gert Bauknecht, Peter Ziemer

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Abstract

A multi speed transmission comprising planetary gearsets (P1, P2, P3, P4), shafts and shift elements. The sun gear of gearset (P1) couples shaft (4) which can couple housing (G) via brake (04) and the carrier of set (P1) couples shaft (3) which can couple housing (G), via brake (03), and drive shaft (1) via clutch (13), and shaft (6) via clutch (36). Shaft (6) couples the ring gear of gearset (P2) and the sun gears of gearsets (P3, P4). Shaft (1) couples the sun gear of gearset (P2) and is operatively connected to the carrier of gearset (P3). Shaft (7) couples the ring gear of set (P1) and the carrier of gearset (P2). The ring gear of gearset (P4) couples shaft (5) which can couple housing (G) via brake (05) and output shaft (2) operatively couples the carrier of gearset (P4) and the ring gear of gearset (P3).

Claims6

Dependent claims

A multi speed transmission, of a planetary design for an automatic transmission for a motor vehicle, comprising:

a drive shaft (1);
an output shaft (2);
first, second, third and fourth planetary gear sets (P1, P2, P3, P4) which are disposed in a transmission housing (G), each of the first, the second, the third, and the fourth planetary gear sets (P1, P2, P3, P4) comprising a sun gear, a carrier and a ring gear;
a third rotatable shaft (3), a fourth rotatable shaft (4), a fifth rotatable shaft (5), a sixth rotatable shaft (6), a seventh rotatable shaft (7), and an eighth rotatable shaft (8, 8′);
at least six shift elements (03, 04, 05, 13, 18, 28, 36) comprising a first brake (04), a second brake (03), a third brake (05), a first clutch (13), a second clutch (36) and a third clutch (18, 28) whose selected engagement produces different transmission ratios between the drive shaft (1) and the output shaft (2) such that nine forward gears and one reverse gear can be achieved;
wherein the sun gear of the first planetary gear set (P1) is connected to the fourth shaft (4) which is directly connectable to the housing (G) via the first brake (04);
the carrier of the first planetary gear set (P1) is connected to the third shaft (3) which is directly connectable to the housing (G) via the second brake (03), the third shaft (3) is directly connectable to the drive shaft (1) via the first clutch (13) and the third shaft (3) is directly connectable to the sixth shaft (6) via the second clutch (36);
the sixth shaft (6) is directly connected to each of the ring gear of the second planetary gear set (P2), the sun gear of the third planetary gear set (P3) and the sun gear of the fourth planetary gear set (P4);
the drive shaft (1) is directly connected to the sun gear of the second planetary gear set (P2) and is operatively connected to the carrier of the third planetary gear set (P3);
the seventh shaft (7) is connected to the ring gear of the first planetary gear set (P1) and the carrier of the second planetary gear set (P2);
the ring gear of the fourth planetary gear set (P4) is connected to the fifth shaft (5) which is directly connectable to the housing (G) via the third brake (05);
and
the output shaft (2) is both operatively connected to the ring gear of the third planetary gear set (P3) and is continuous connected to the carrier of the fourth planetary gear set (P4).

10 more elements

A multi speed transmission of a planetary design for an automatic transmission for a motor vehicle comprising:

a drive shaft (1);
an output shaft (2);
first, second, third and fourth planetary gear sets (P1, P2, P3, P4) which are disposed in a transmission housing (G), each of the first, the second, the third, and the fourth planetary gear sets (P1, P2, P3, P4) comprising a sun gear, a carrier and a ring gear;
a third rotatable shaft (3), a fourth rotatable shaft (4), a fifth rotatable shaft (5), a sixth rotatable shaft (6), a seventh rotatable shaft (7), and an eighth rotatable shaft (8, 8′);
at least six shift elements (03, 04, 05, 13, 18, 28, 36) comprising a first brake (04), a second brake (03), a third brake (05), a first clutch (13), a second clutch (36) and a third clutch (18, 28) whose selected engagement produces different transmission ratios between the drive shaft (1) and the output shaft (2) such that nine forward gears and one reverse gear can be achieved;
wherein the sun gear of the first planetary gear set (P1) is connected to the fourth shaft (4) which is connectable to the housing (G) via the first brake (04);
the carrier of the first planetary gear set (P1) is connected to the third shaft (3) which is connectable to the housing (G) via the second brake (03), the third shaft (3) is connectable to the drive shaft (1) via the first clutch (13) and the third shaft (3) is connectable to the sixth shaft (6) via the second clutch (36);
the sixth shaft (6) is connected to the ring gear of the second planetary gear set (P2), the sun gear of the third planetary gear set (P3), and the sun gear of the fourth planetary gear set (P4);
the drive shaft (1) is connected to the sun gear of the second planetary gear set (P2) and is operatively connected to the carrier of the third planetary gear set (P3);
the seventh shaft (7) is connected to the ring gear of the first planetary gear set (P1) and the carrier of the second planetary gear set (P2);
the ring gear of the fourth planetary gear set (P4) is connected to the fifth shaft (5) which is connectable to the housing (G) via the third brake (05);
and
the output shaft (2) is connected to the ring gear of the third planetary gear set (P3) and is operatively connected to the carrier of the fourth planetary gear set (P4);
the eighth shaft (8) is connected to the carrier of the third planetary gear set (P3) and the drive shaft (1) is operatively connectable to the eighth shaft (8) and the carrier of the third planetary gear set (P3) via the third clutch (18);
the output shaft (2) is connected to the ring gear of the third planetary gear set (P3);
a first forward gear is achieved by engagement of the first and the third brakes (04, 05) and the second clutch (36);
a second forward gear is achieved by engagement of the third brake (05) and the first and the second clutches (13, 36);
a third forward gear is achieved by engagement of the first and the third brakes (04, 05) and the first clutch (13);
a fourth forward gear is achieved by engagement of the third brake (05) and the first and the third clutches (13, 18);
a fifth forward gear is achieved by engagement of the first brake (04) and the first and the third clutches (13, 18);
a sixth forward gear is achieved by engagement of the first, the second and the third clutches (13, 36, 18);
a seventh forward gear is achieved by engagement of first brake (04) and the second and the third clutches (36, 18);
an eighth forward gear is achieved by engagement of the second brake (03) and the second and the third clutches (36, 18);
a ninth forward gear is achieved by engagement of the first and the second brakes (04, 03) and the third clutch (18);
and
the reverse gear is achieved by engagement of the first, the second and the third brakes (03, 04, 05).

23 more elements

A multi speed transmission of a planetary design for an automatic transmission for a motor vehicle comprising:

a drive shaft (1);
an output shaft (2);
first, second, third and fourth planetary gear sets (P1, P2, P3, P4) which are disposed in a transmission housing (G), each of the first, the second, the third, and the fourth planetary gear sets (P1, P2, P3, P4) comprising a sun gear, a carrier and a ring gear;
a third rotatable shaft (3), a fourth rotatable shaft (4), a fifth rotatable shaft a sixth rotatable shaft 6 a seventh rotatable shaft 7 and an eighth rotatable shaft (8, 8′);
at least six shift elements (03, 04, 05, 13, 18, 28, 36) comprising a first brake (04), a second brake (03), a third brake (05), a first clutch (13), a second clutch (36) and a third clutch (18, 28) whose selected engagement produces different transmission ratios between the drive shaft (1) and the output shaft (2) such that nine forward gears and one reverse gear can be achieved;
wherein the sun gear of the first planetary gear set (P1) is connected to the fourth shaft (4) which is connectable to the housing (G) via the first brake (04);
the carrier of the first planetary gear set (P1) is connected to the third shaft (3) which is connectable to the housing (G) via the second brake (03), the third shaft (3) is connectable to the drive shaft (1) via the first clutch (13) and the third shaft (3) is connectable to the sixth shaft (6) via the second clutch (36);
the sixth shaft (6) is connected to the ring gear of the second planetary gear set (P2), the sun gear of the third planetary gear set (P3), and the sun gear of the fourth planetary gear set (P4);
the drive shaft (1) is connected to the sun gear of the second planetary gear set (P2) and is operatively connected to the carrier of the third planetary gear set (P3);
the seventh shaft (7) is connected to the ring gear of the first planetary gear set (P1) and the carrier of the second planetary gear set (P2);
the ring gear of the fourth planetary gear set (P4) is connected to the fifth shaft (5) which is connectable to the housing (G) via the third brake (05);
and
the output shaft (2) is connected to the ring gear of the third planetary gear set (P3) and is operatively connected to the carrier of the fourth planetary gear set (P4);
the drive shaft (1) is connected to the carrier of the third planetary gear set (P3), and
the eighth shaft (8′) is connected to the ring gear of the third planetary gear set (P3) and the output shaft (2) is operatively connectable to the eighth shaft (8′) and the ring gear of the third planetary gear set (P3) via the third clutch (28);
a first forward gear is achieved by engagement of the first and the third brakes (04, 05) and the second clutch (36);
a second forward gear is achieved by engagement of the third brake (05) and the first and the second clutches (13, 36);
a third forward gear is achieved by engagement of the first and the third brakes (04, 05) and the first clutch (13);
a fourth forward gear is achieved by engagement of the third brake (05) and the first and the third clutches (13, 18);
a fifth forward gear is achieved by engagement of the first brake (04) and the first and the third clutches (13, 18);
a sixth forward gear is achieved by engagement of the first, the second and the third clutches (13, 36, 18);
a seventh forward gear is achieved by engagement of first brake (04) and the second and the third clutches (36, 18);
an eighth forward gear is achieved by engagement of the second brake (03) and the second and the third clutches (36, 18);
a ninth forward gear is achieved by engagement of the first and the second brakes (04, 03) and the third clutch (18);
and
the reverse gear is achieved by engagement of the first, the second and the third brakes (03, 04, 05).

23 more elements

Dependencies are inferred from the claim text.

Facts

Application: 13/384,625Filed 19 Aug 2010
Priority: DE 10 2009 028 67220 Aug 2009
Published: US 2012/0122626 A117 May 2012
Granted: 6 Nov 2012
Term ends: Not estimatedThe source records don’t support an estimate.

Classification5 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 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
F16H 2200/2046
Characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes: with six engaging means