Dual-clutch transmission

Patent metadata

Field	Value
Publication number	US-9273757-B2
Application number	US-201214364753-A
Country	US
Kind code	B2
Filing date	Dec 3, 2012
Priority date	Dec 14, 2011
Publication date	Mar 1, 2016
Grant date	Mar 1, 2016

Abstract

A countershaft-type dual clutch transmission for a vehicle has two clutches having input sides connected to a driveshaft (AN) and output sides connected respectively to one of two transmission input shafts arranged coaxial to a mainshaft axis. A sub-transmission is associated in each instance with the transmission input shafts, at least two countershafts, a plurality of gear planes to which are assigned gear ratio steps, and at least one output shaft which can be connected to the sub-transmissions via an output gear plane. Only six gear planes with at least nine assigned gear ratio steps can be realized via only four double shift elements and at least one single shift element. Each countershaft can be coupled with four gear ratio steps via double shift elements, and one of the transmission input shafts can be coupled with a gear ratio step via a single shift element.

First claim

The invention claimed is:

1. A dual clutch transmission for a vehicle comprising:
first and second clutches (K 1 , K 2 ) having input sides connected to a driveshaft (AN) and output sides connected respectively to one of a first and second transmission input shaft (EW 1 , EW 2 ) arranged coaxial to a mainshaft axis;
a first and second sub-transmission each associated with a respective one of the first and second transmission input shafts (EW 1 , EW 2 );
at least a first and second countershaft (VW 1 , VW 2 ), with a plurality of gear planes comprising a first, second, third, fifth, sixth and seventh gear plane (I, II, III, V, VI, VII) to which are assigned gear ratio steps (A, B, C, D, E, F, G, H, I);
at least one output shaft (AB) connectable to the first and second sub-transmissions via an output gear plane (IV); four double shift elements comprising a first, second, third and fourth double shift element (S 1 -S 2 , S 3 -S 4 , S 5 -S 6 , S 7 -S 8 ) and at least one single shift element (S 9 , S 10 ) constructed so as to realize six gear planes (I, II, III, V, VI, VII) with at least nine assigned gear ratio steps comprising gear ratio step A, gear ratio step B, gear ratio step C, gear ratio step D, gear ratio step E, gear ratio step F, gear ratio step G, gear ratio step H and gear ratio step I, wherein each countershaft (VW 1 , VW 2 ) can be coupled with four gear ratio steps (A, B, C, D; E, F, G, H) via one of the double shift elements (S 1 -S 2 , S 3 -S 4 , S 5 -S 6 , S 7 -S 8 ), and wherein one of the transmission input shafts (EW 1 , EW 2 ) can be coupled with a gear ratio step (I) via the single shift element (S 9 ).

2. The dual clutch transmission according to claim 1 , wherein the first transmission input shaft (EW 1 ) is constructed as a solid shaft, and comprises first and second fixed gears (Z 4 , Z 5 ) arranged coaxial to the mainshaft axis and an idler gear (Z 6 ) arranged coaxial to the mainshaft axis, the fixed gears (Z 4 , Z 5 ) and the idler gear (Z 6 ) being assigned to the first transmission input shaft (EW 1 ), and wherein the idler gear (Z 6 ) can be connected to the first transmission input shaft (EW 1 ) via the single shift element (S 9 ).

3. The dual clutch transmission according to claim 2 , wherein the second transmission input shaft (EW 2 ) is constructed as a hollow shaft, and comprising first, second and third fixed gears (Z 1 , Z 2 , Z 3 ) arranged coaxial to the mainshaft axis and assigned to the second transmission input shaft (EW 2 ).

4. The dual clutch transmission according to claim 3 , wherein the first countershaft (VW 1 ) is constructed as solid shaft arranged coaxial to a first countershaft axis; the first countershaft (VW 1 ) comprising a fixed gear (Z 17 ) arranged coaxial to the first countershaft axis as output constant to the first countershaft (VW 1 ) and idler gears comprising a first, second, third and fourth idler gear (Z 7 , Z 8 , Z 9 , Z 10 ) arranged coaxial to the first countershaft axis and assigned to the first countershaft (VW 1 ); and wherein the first idler gear (Z 7 ) and the second idler gear (Z 8 ) can be connected to the first countershaft (VW 1 ) in each instance via the first double shift element (S 1 -S 2 ), and the third idler gear (Z 9 ) and fourth idler gear (Z 10 ) can be connected to the first countershaft (VW 1 ) in each instance via the third double shift element (S 5 -S 6 ).

5. The dual clutch transmission according to claim 4 , wherein the second the countershaft (VW 2 ) is constructed as a solid shaft, the second countershaft (VW 2 ) comprising first and second fixed gears (Z 18 , Z 15 ) arranged coaxial to the second countershaft axis and assigned to the second countershaft (VW 2 ) and four idler gears comprising a first, second, third and fourth idler gear (Z 11 , Z 12 , Z 13 , Z 14 ) arranged coaxial to the second countershaft axis and assigned to the second countershaft (VW 2 ); and wherein the first idler gear (Z 11 ) and the second idler gear (Z 12 ) can be connected to the second countershaft (VW 2 ) in each instance via the second double shift element (S 3 -S 4 ), and the third idler gear (Z 13 ) and fourth idler gear (Z 14 ) can be connected to the second countershaft (VW 2 ) in each instance via the fourth double shift element (S 7 -S 8 ), and wherein the first fixed gear (Z 18 ) is provided as output constant.

6. The dual clutch transmission according to claim 5 , wherein in the first gear plane (I) the first fixed gear (Z 1 ) of the second transmission input shaft (EW 2 ) engages with the first idler gear (Z 7 ) of the first countershaft (VW 1 ) and with the first idler gear (Z 11 ) of the second countershaft (VW 2 ),wherein in a second gear plane (II) the second fixed gear (Z 2 ) of the second transmission input shaft (EW 2 ) engages with the second idler gear (Z 8 ) of the first countershaft (VW 1 ), wherein in a third gear plane (III) the third fixed gear (Z 3 ) of the second transmission input shaft (EW 2 ) engages with the second idler gear (Z 12 ) of the second countershaft (VW 2 ), wherein in a fourth gear plane (IV), as output gear plane, the output shaft (AB) having a fixed gear (Z 16 ) which meshes with the fixed gear (Z 17 ) of the first countershaft (VW 1 ) and with the fixed gear (Z 18 ) of the second countershaft (VW 2 ), wherein in a fifth gear plane (V) the first fixed gear (Z 4 ) of the first transmission input shaft (EW 1 ) engages with the third idler gear (Z 9 ) of the first countershaft (VW 1 ) and with an intermediate gear (ZW) for reversing the rotating direction; wherein the intermediate gear (ZW) meshes with the third idler gear (Z 13 ) of the second countershaft, wherein in a sixth gear plane (VI) the second fixed gear (Z 5 ) of the first transmission input shaft (EW 1 ) engages with the fourth idler gear (Z 10 ) of the first countershaft (VW 1 ) and with the fourth idler gear (Z 14 ) of the second countershaft (VW 2 ), and wherein in a seventh gear plane (VII) the idler gear (Z 6 ) of the first transmission input shaft (EW 1 ) meshes with second fixed gear (Z 15 ) of the second countershaft (VW 2 ).

7. The dual clutch transmission according to claim 1 , wherein the gear ratio step A is shiftable proceeding from the second clutch (K 2 ) via the second transmission input shaft (EW 2 ), wherein the power flow is transmitted via the first gear plane (I) to the first countershaft (VW 1 ) and via the fourth gear plane (IV) to the output shaft (AB) when shift element (S 1 ) is activated; wherein the gear ratio step B is shiftable proceeding from the second clutch (K 2 ) via the second transmission input shaft (EW 2 ), wherein the power flow is transmitted via the second gear plane (II) to the first countershaft (VW 1 ) and via the fourth gear plane (IV) to the output shaft (AB) when shift element (S 2 ) is activated; wherein the gear ratio step C is shiftable proceeding from the first clutch (K 1 ) via the first transmission input shaft (EW 1 ), wherein the power flow is transmitted via the fifth gear plane (V) to the first countershaft (VW 1 ) and via the fourth gear plane (IV) to the output shaft (AB) when shift element (S 5 ) is activated; wherein the gear ratio step D is shiftable proceeding from the first clutch (K 1 ) via the first transmission input shaft (EW 1 ), wherein the power flow is transmitted via the sixth gear plane (VI) to the first countershaft (VW 1 ) and via the fourth gear plane (IV) to the output shaft (AB) when shift element (S 6 ) is activated; wherein the gear ratio step E is shiftable proceeding from the second clutch (K 2 ) via the second transmission input shaft (EW 2 ), wherein the power flow is transmitted via the first gear plane (I) to the second countershaft (VW 2 ) and via the fourth gear plane (IV) to the output shaft (AB) when shift element (S 3 ) is activated;

Assignees

• Michel Christian
• WAFZIG JüRGEN
• Wechs Michael
• Renninger Markus
• Rosemeier Thomas
• Kaltenbach Johannes
• Zahnradfabrik Friedrichshafen

Inventors

• Michel Christian
• WAFZIG JüRGEN
• Wechs Michael
• Renninger Markus
• Rosemeier Thomas
• Kaltenbach Johannes

Classifications

• F16H3/006 Primary

  power being selectively transmitted by parallel flow paths, e.g. dual clutch transmissions · CPC title

• Y10S903/902

  Prime movers comprising electrical and internal combustion motors · CPC title

• Y10T74/19014

  Plural prime movers selectively coupled to common output · CPC title

• F16H2003/0931

  each countershaft having an output gear meshing with a single common gear on the output shaft · CPC title

• B60K6/547

  the transmission being a stepped gearing · CPC title