Multi-ratio transmission

• US 8,444,524 B2
• Filed: 08/19/2010
• Issued: 05/21/2013
• Est. Priority Date: 08/20/2009
• Status: Active Grant

• Current Assignee: ZF Friedrichshafen AG (Zeppelin - Stiftung der Stadt Friedrichshafen)
• Original Assignee: ZF Friedrichshafen AG (Zeppelin - Stiftung der Stadt Friedrichshafen)
• Inventors: Gumpoltsberger, Gerhard, Sibla, Christian, Beck, Stefan, Haupt, Josef, Bauknecht, Gert, Ziemer, Peter
• Primary Examiner(s): Le, David D
• Assistant Examiner(s): KNIGHT, DEREK DOUGLAS
• Application Number:
  US13/384,629
• Publication Number:
  US 20120142486A1
• Time in Patent Office: 1,006 Days
• Field of Search: 475/276, 475/280, 475/290
• US Class Current: 475/276
• CPC Class Codes: F16H 2200/0065 the gear ratios comprising nine forward speeds
• CPC Class Codes: F16H 2200/2012 with four sets of orbital gears
• CPC Class Codes: F16H 2200/2046 with six engaging means
• CPC Class Codes: F16H 2200/2097 comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
• CPC Class Codes: F16H 3/66 composed of a number of gear trains without drive passing from one train to another

Abstract

A multi step transmission comprises planetary gearsets (P1, P2, P3, P4), shafts and shift elements. The sun gear of gearset (P1) couples housing (G). The carrier of gearset (P1) couples shaft (3), which couples housing (G) via brake (03), drive shaft (01) via clutch (13), and shaft (5) via clutch (35). Shaft (5) operatively couples the sun gear of gearset (P3) and couples the ring gear of gearset (P2) and the sun gear of set (P4). Shaft (1) couples, via clutch (17), shaft (7), which couples the sun gear of gearset (P2), and operatively couples the carrier of gearset (P3). Shaft (6) couples the ring gear of gearset (P1) and the carrier of gearset (P2) The ring gear of gearset (P4) couples shaft (4), which couples housing (G) via brake (04), and output shaft (2) couples the ring gear of gearset (P3) and the carrier of set (P4).

Claims

1. A multi step 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, 13, 17, 18, 35, 58) comprising a first brake (04), a second brake (03), a first clutch (13), a second clutch (35), a third clutch (18, 58) and a fourth clutch (17) 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;

the sun gear of the first planetary gear set (P1) is coupled to the housing (G);

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 carrier of the first planetary gear set (P1) is connectable to the drive shaft (1) via the first clutch (13), and the carrier of the first planetary gear set (P1) is connectable via the second clutch (35) to the fifth shaft (5) which is operatively connected to the sun gear of the third planetary gear set (P3);

the fifth shaft (5) is connected to the ring gear of the second planetary gear set (P2) and the sun gear of the fourth planetary gear set (P4);

the drive shaft (1) is connectable, via the fourth clutch (17), to the seventh shaft (7) which is connected to the sun gear of the second planetary gear set (P2), and the drive shaft (1) is operatively connected to the carrier of the third planetary gear set (P3);

the sixth shaft (6) 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 fourth shaft (4) which is connectable, via the first brake (04), to the housing (G); and

the output shaft (2) is connected to the ring gear of the third planetary gear set (P3) and the carrier of the fourth planetary gear set (P4).

2. The multi step transmission according to claim 1, wherein the eighth shaft (8) is connected to the carrier of the third planetary gear set (P3) and the drive shaft (1) is connectable to the eighth shaft (8) and the carrier of the third planetary gear set (P3) via the third clutch (18), and

the fifth shaft (5) is directly connected to the sun gear of the third planetary gear set (P3).

3. The multi step transmission according to claim 1, wherein the drive shaft (1) is connected to the carrier of the third planetary gear set (P3), and

the eight shaft (8′

) is connected to the sun gear of the third planetary gear set (P3) and the fifth shaft (5) is connectable to the eight shaft (8′

) and the sun gear of the third planetary gear set (P3) via the third clutch (58).

4. The multi step transmission according to claim 1, wherein the first, the second, the third and the fourth planetary gear sets (P1, P2, P3, P4) are minus planetary gear sets.

5. The multi step transmission according to claim 2, wherein a first forward gear is achieved by engagement of the first brake (04) and the second and the fourth clutches (35, 17);

a second forward gear is achieved by engagement of the first brake (04) and the first and the second clutches (13, 35);

a third forward gear is achieved by engagement of the first brake (04) and the first and the fourth clutches (13, 17);

a fourth forward gear is achieved by engagement of the first brake (04) and the first and the third clutches (13, 18);

a fifth forward gear is achieved by engagement of the first, the third and the fourth clutches (13, 18, 17);

a sixth forward gear is achieved by engagement of the first, the second and the third clutches (13, 35, 18);

a seventh forward gear is achieved by engagement of the second, the third and the fourth clutches (35, 18, 17);

an eighth forward gear is achieved by engagement of the second brake (03) and the second and the third clutches (35, 18);

a ninth forward gear is achieved by engagement of the second brake (03) and the third and the fourth clutches (18, 17); and

the reverse gear is achieved by engagement of the first and the second brakes (04, 03), and the fourth clutch (17).

6. The multi step transmission according to claim 3, wherein a first forward gear is achieved by engagement of the first brake (04) and the second and the fourth clutches (35, 17);

a second forward gear is achieved by engagement of the first brake (04) and the first and the second clutches (13, 35);

a third forward gear is achieved by engagement of the first brake (04) and the first and the fourth clutches (13, 17);

a fourth forward gear is achieved by engagement of the first brake (04) and the first and the third clutches (13, 18);

a fifth forward gear is achieved by engagement of the first, the third and the fourth clutches (13, 18, 17);

a sixth forward gear is achieved by engagement of the first, the second and the third clutches (13, 35, 18);

a seventh forward gear is achieved by engagement of the second, the third and the fourth clutches (35, 18, 17);

an eighth forward gear is achieved by engagement of the second brake (03) and the second and the third clutches (35, 18);

a ninth forward gear is achieved by engagement of the second brake (03) and the third and the fourth clutches (18, 17); and

the reverse gear is achieved by engagement of the first and the second brakes (04, 03), and the fourth clutch (17).