CN101255904A

CN101255904A - Multi-speed dual clutch transmission

Info

Publication number: CN101255904A
Application number: CNA2007101968753A
Authority: CN
Inventors: P·-G·比约尔克; M·莫林; J·A·迪默; P·S·波尔特尔; H·K·索乌尔
Original assignee: GM Global Technology Operations LLC
Current assignee: GM Global Technology Operations LLC
Priority date: 2006-12-08
Filing date: 2007-12-07
Publication date: 2008-09-03

Abstract

A transmission is provided having an input member, an output member, a dual clutch assembly, a countershaft, a plurality of co-planar gear sets, a plurality of interconnecting members, and a plurality of torque transmitting devices. The torque transmitting devices include synchronizer assemblies.

Description

The double-clutch speed changer of many speed

The cross reference of relevant patent

The application requires to enjoy in the U.S. Provisional Application No.60/873 that submitted on December 8th, 2006,728 rights and interests, and the disclosure of the Invention content of this U.S. Provisional Application is incorporated by reference herein.

Technical field

The present invention openly relates to a kind of speed changer, more specifically relates to a kind of multi-speed transmission with double clutch assembly and countershaft.

Background technique

Typical how fast double-clutch speed changer uses the combination of two friction clutches and several dog-clutch/synchronizers, by between a friction clutch and another friction clutch, rotating, to realize " initial state " or dynamic shifting, wherein synchronizer be actual carry out dynamic shifting before " pre-selected " gear ratio of being used to arrive." initial state " gear shift means the torque-flow that did not need to interrupt motor before carrying out gear shift.This design is used usually and is had the gear pair of different special uses or the counter shaft gear device of gear train, to obtain various forward velocity ratios.Therefore, the twice of the forward velocity quantity of needed gear sum adds three numbers of gears that are used for reverse gear in this typical design.This needs a large amount of necessary gear pairs, especially in the speed changer with relatively large amount forward velocity ratio.

For obtain these gears than and the torque range clutch, break and the gear train that add may cause the speed changer weight and the size of inefficiency or contretemps.Therefore, exist in related domain having improved encapsulation, provide simultaneously required gear than and the demand of the speed changer of torque range.

Summary of the invention

The invention provides a kind of speed changer with input block, output block, double clutch assembly, countershaft, a plurality of co-planar gear sets, a plurality of interconnecting member and a plurality of torque transmitters.This torque transmitter comprises synchronizer assembly.

An embodiment of speed changer of the present invention comprises input block, output block, first, second, third, fourth, the the 5th, the 6th, the 7th and the octadentate wheels, each described gear train has first gear and second gear, wherein output block constantly (continuosly) link to each other with the 5th gear train, first interconnecting member be connected constantly the 7th and the octadentate wheels on, second interconnecting member links to each other with third and fourth gear train constantly, and countershaft is connected first, second constantly, on the 5th and the 7th gear train.The double clutch assembly optionally engages, thereby makes one of them interconnecting member interconnection of input block and first interconnecting member and second interconnecting member.Four synchronizer assemblies optionally with first, second, third, fourth, the 5th, the 6th, the 7th and one of them gear train and first interconnecting member of octadentate wheels, one of them parts of second interconnecting member and countershaft link up.Double clutch assembly and four synchronizer assemblies optionally are joined together at least in twos in combination, so that set up at least seven forward velocity ratios and at least one reverse speed ratio between input block and output block.

In one aspect of the invention, first countershaft is positioned at the radially outside and parallel with it orientation of input block.

In another aspect of this invention, output block is positioned at the radially outside and parallel with it orientation of input block.

In still another aspect of the invention, torque converter links to each other with input block constantly.

In still another aspect of the invention, the double clutch assembly comprises and is used for optionally first clutch that input block and first interconnecting member are coupled together.

In still another aspect of the invention, the double clutch assembly comprises and is used for optionally second clutch that input block and second interconnecting member are coupled together.

In still another aspect of the invention, first interconnecting member is positioned in second interconnecting member, and concentric with it.

In still another aspect of the invention, first, second, third, fourth, the 5th, the 6th, the 7th and each gear trains of octadentate wheels in first gear and second gear radially aim at.

In still another aspect of the invention, the 4th gear train comprises can be around the 3rd gear that rotates from the radially outwards also parallel with it axis of countershaft, and first gear and second gear of the 3rd gear and the 4th gear train are meshing with each other.

In still another aspect of the invention, the 5th gear train comprises the 3rd gear that is connected constantly on the output block.

In still another aspect of the invention, first, second of the 4th and the 5th gear train and the 3rd gear are radially aimed at.

In still another aspect of the invention, first synchronizer assembly in four synchronizer assemblies optionally is connected to one of them gear train of first gear train and second gear train on second interconnecting member.

In still another aspect of the invention, second synchronizer assembly in four synchronizer assemblies optionally is connected to one of them gear train of the 3rd gear train and the 4th gear train on the countershaft.

In still another aspect of the invention, the 3rd synchronizer assembly in four synchronizer assemblies optionally is connected to one of them gear train of the 5th gear train and the 6th gear train on first interconnecting member.

In still another aspect of the invention, the 4th synchronizer assembly in four synchronizer assemblies optionally is connected to one of them gear train of the 7th gear train and octadentate wheels on the countershaft.

In still another aspect of the invention, first gear train can link to each other with one of them interconnecting member of first interconnecting member and second interconnecting member, and wherein second gear train can link to each other with countershaft.

In still another aspect of the invention, first, second, third, fourth, the 5th, the 6th, the 7th and the octadentate wheels arrange respectively the most close double clutch assembly of first gear train wherein, and the octadentate wheels from the double clutch assembly farthest from left to right in order.

Another embodiment of speed changer comprises input block, output block, first, second, the 3rd, the 4th, the 5th, the 6th, the 7th and the octadentate wheels, each described gear train has first gear and second gear, wherein output block links to each other with the 4th gear train constantly, first interconnecting member links to each other with the 6th gear train with the 5th constantly, second interconnecting member links to each other with first and second gear trains constantly, countershaft is constantly with the 3rd, the 4th, the 7th, link to each other with the octadentate wheels, and the double clutch assembly optionally engages, thereby one of them interconnecting member of input block and first interconnecting member and second interconnecting member is interconnected.Four synchronizer assemblies optionally with first, second, third, fourth, the 5th, the 6th, the 7th and one of them gear train and first interconnecting member of octadentate wheels, one of them parts of second interconnecting member and countershaft link up.First, second, third, fourth, the the 5th, the 6th, the 7th and the octadentate wheels arrange respectively the most close double clutch assembly of first gear train wherein, and the octadentate wheels from the double clutch assembly farthest from left to right in order.Double clutch assembly and four synchronizer assemblies optionally are joined together at least in twos in combination, so that set up at least seven forward velocity ratios and at least one reverse speed ratio between input block and output block.

From below in conjunction with accompanying drawing to the detailed description that realizes optimal mode of the present invention, will be easy to clear above-mentioned feature of the present invention and advantage and further feature and advantage.

Description of drawings

Fig. 1 is an embodiment's of multi-speed transmission a sketch in accordance with the principles of the present invention; With

Fig. 2 is another embodiment's of multi-speed transmission a sketch in accordance with the principles of the present invention.

Embodiment

With reference to accompanying drawing, wherein similar label is represented similar member, has shown multiple-speed gear-box 10 among Fig. 1.Speed changer 10 comprises input block 12 and output block 14.In this embodiment, input block 12 and output block 14 are axles, and will so call.It will be appreciated by those skilled in the art that input block and

output block

12,14 can be the members that is different from axle.Input shaft 12 links to each other with torque converter 16 or other starting arrangement constantly.The motor (not shown) is connected on the torque converter 16, and provides driving torque for torque converter 16.Output shaft 14 links to each other with main reducing gear unit 18 constantly.Speed changer 10 comprises counter shaft gear device 20, and it comprises interconnecting member, countershaft, and the pitch wheel group of coplane and the synchronizer that optionally engages, as described below.For example, counter shaft gear device 20 comprises the first interconnection axle or the parts 22 and second interconnection axle or the parts 24.The second interconnection axle 24 is sleeves concentric with the first interconnection axle 22.Counter shaft gear device 20 also comprises countershaft 26.Countershaft 26 and input shaft 12, output shaft 14 and

interconnection axle

22,24 are spaced apart and parallel.Output shaft 14,

interconnection axle

22,24 and countershaft 26 comprise first case member, 27, the second case members 29 and the 3rd case member 31 by a plurality of supporting units support.

Case member

27,29,31 have equipped the bearing 33 that is used for rotatably supporting output shaft 14, the first and

second interconnection axles

22,24 and countershaft 26.In the embodiment who is provided, case member 27 is arranged on the position of the most close torque converter 16 and main reducing gear unit 18.Case member 29 is arranged between case member 27 and the case member 31.

Double clutch 30 is connected between input shaft 12 and first and second interconnection axle 22,24.Double clutch 30 comprises with input shaft 12 and linking to each other so that the clutch outer member 32 of rotation.In addition, clutch 30 has first and second clutch elements or dish hub 34 and 36.

Clutch element

34 and 36 is configured to form friction clutch double clutch well known in the art with shell 32.More particularly,

clutch element

34,36 and clutch outer member 32 have mounted thereto interaction and form the friction plate 35 of friction clutch.In addition, clutch element 34 links to each other with the first interconnection axle 22, so that common rotation, clutch element 36 links to each other with the second interconnection axle 24, so that common rotation.Thereby, clutch element 34 engages with the selectivity of clutch outer member 32 can with input shaft 12 and the first interconnection axle 22 couple together so that common rotation, and clutch element 36 engages with the selectivity of clutch outer member 32 and the input shaft 12 and the second interconnection axle 24 can be coupled together so that rotate jointly.

Counter shaft gear device 20 also comprises the

pitch wheel group

40,50,60,70,80,90,100 and 110 of coplane.In the embodiment who is provided,

gear train

40,50,60 and 70 are arranged between case member 27 and the case member 29, and gear train 80,90,100 and 110 is arranged between case member 29 and the case member 31.

Co-planar gear sets 40 comprises gear 42 and gear 44.Gear 42 optionally is connected so that rotate jointly with the second interconnection axle 24, and is meshing with each other with gear 44.Gear 44 is connected with countershaft 26 so that common rotation.

Co-planar gear sets 50 comprises gear 52 and gear 54.Gear 52 optionally is connected so that rotate jointly with the second interconnection axle 24, and is meshing with each other with gear 54.Gear 54 is connected with countershaft 26 so that common rotation.

Co-planar gear sets 60 comprises gear 62 and gear 64.Gear 62 is connected so that rotate jointly with the second interconnection axle 24, and is meshing with each other with gear 64.Gear 64 optionally is connected with countershaft 26 so that common rotation.

Co-planar gear sets 70 comprises

pitch wheel

72,74 and 76.Gear 72 is connected so that rotate jointly with the second interconnection axle 24, and is meshing with each other with idler gear 74.Idler gear 74 can be around axis I rotation.Gear 74 also is meshing with each other with gear 76.Gear 76 optionally links to each other with countershaft 26.

Co-planar gear sets 80 comprises pitch wheel 82,84 and 86.Gear 82 optionally is connected so that rotate jointly with the first interconnection axle 22, and is meshing with each other with gear 84.Gear 84 is connected with countershaft 26 so that rotate jointly, and is meshing with each other with gear 86.Gear 86 is connected with output shaft 14 so that common rotation.

Co-planar gear sets 90 comprises pitch wheel 92 and 96.Gear 92 optionally is connected so that rotate jointly with the first interconnection axle 22, and is meshing with each other with gear 94.Gear 94 is connected with countershaft 26 so that common rotation.

Co-planar gear sets 100 comprises pitch wheel 102 and 104.Gear 102 is connected so that common rotation with the first interconnection axle 22.Gear 102 is meshing with each other with gear 104.Gear 104 optionally is connected with countershaft 26 so that common rotation.

Co-planar gear sets 110 comprises pitch wheel 112 and 114.Gear 112 is connected so that common rotation with the first interconnection axle 22.Gear 112 is meshing with each other with gear 114.Gear 114 optionally is connected with countershaft 26 so that common rotation.

Speed changer 10 also comprises a plurality of alternative synchronizers 120,122,124,126,128,130,132 and 134 that engage.Synchronizer 120/122,124/126,128/130,132/134 is positioned at the left side and the right side of synchronizer assembly, shared public synchronizer dish hub and sleeve pipe (sleeve).Synchronizer 120 optionally engages, thereby the gear 42 and the second interconnection axle 24 are coupled together, so that rotation common with it.Synchronizer 122 optionally engages, thereby the gear 52 and the second interconnection axle 24 are coupled together, so that rotation common with it.Synchronizer 124 optionally engages, thereby gear 64 and countershaft 26 are coupled together, so that rotation common with it.Synchronizer 126 optionally engages, thereby gear 76 and countershaft 26 are coupled together, so that rotation common with it.Synchronizer 128 optionally engages, thereby the gear 82 and the first interconnection axle 22 are coupled together, so that rotation common with it.Synchronizer 130 optionally engages, thereby the gear 92 and the first interconnection axle 22 are coupled together, so that rotation common with it.Synchronizer 132 optionally engages, thereby gear 104 and countershaft 26 are coupled together, so that rotation common with it.Synchronizer 134 optionally engages, thereby gear 114 and countershaft 26 are coupled together, so that rotation common with it.

Speed changer 10 can be passed to output shaft 14 with moment of torsion from input shaft 12 under advancing torque ratio and a reverse gear torque ratio at least seven.The torque ratio of respectively advancing and reverse gear torque ratio realize by the joint of double clutch 30 and one of them

clutch element

34,36 and wherein one or more synchronizers 120,122,124,126,128,130,132 and 134.It will be appreciated by those skilled in the art that different velocity ratios is associated with each torque ratio.

In order to set up the reverse gear torque ratio, the clutch element 36 of double clutch 30 engages with synchronizer 126.By this joint, the clutch element 36 of double clutch 30 is passed to second interconnection axle 24 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to idler gear 74 from the second interconnection axle 24 by gear 72.Idler gear 74 transfers a torque to gear 76.When synchronizer 126 engaged, gear 76 transferred a torque to countershaft 26.Countershaft 26 transfers a torque to gear 84.Gear 84 transfers a torque to gear 86, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit (final drive unit) 18 with moment of torsion.

First torque ratio (first gear) of advancing realizes by the clutch element 34 of double clutch 30 and the joint of synchronizer 134.By this joint, the clutch element 34 of double clutch 30 is passed to first interconnection axle 22 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to gear 112 from the first interconnection axle 22.Gear 112 transfers a torque to gear 114.When synchronizer 134 engaged, gear 114 transferred a torque to countershaft 26.Countershaft 26 transfers a torque to gear 84.Gear 84 transfers a torque to gear 86, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

The follow-up torque ratio of advancing (second gear) is set up by the clutch element 36 of double clutch 30 and the joint of synchronizer 124.By this joint, the clutch element 36 of double clutch 30 is passed to second interconnection axle 24 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to gear 62 from the second interconnection axle 24.Gear 62 transfers a torque to gear 64.When synchronizer 124 engaged, gear 64 transferred a torque to countershaft 26.Countershaft 26 transfers a torque to gear 84.Gear 84 transfers a torque to gear 86, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

Follow-up torque ratio (the 3rd gear) is set up by the clutch element 34 of double clutch 30 and the joint of synchronizer 132.By this joint, the clutch element 34 of double clutch 30 is passed to first interconnection axle 22 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to gear 102 from the first interconnection axle 22.Gear 102 transfers a torque to gear 104.When synchronizer 132 engaged, gear 104 transferred a torque to countershaft 26.Countershaft 26 transfers a torque to gear 84.Gear 84 transfers a torque to gear 86, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

Next follow-up torque ratio of advancing (the 4th gear) is set up by the clutch element 36 of double clutch 30 and the joint of synchronizer 122.By this joint, the clutch element 36 of double clutch 30 is passed to second interconnection axle 24 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, when synchronizer 122 engaged, moment of torsion can be passed to gear 52 from the second interconnection axle 24.Gear 52 transfers a torque to gear 54.Gear 54 transfers a torque to countershaft 26.Countershaft 26 transfers a torque to gear 84.Gear 84 transfers a torque to gear 86, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

Follow-up torque ratio (the 5th gear) is set up by the clutch element 34 of double clutch 30 and the joint of synchronizer 128.By this joint, the clutch element 34 of double clutch 30 is passed to first interconnection axle 22 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, when synchronizer 122 engaged, moment of torsion can be passed to gear 82 from the first interconnection axle 22.Gear 82 transfers a torque to gear 84.Gear 84 transfers a torque to countershaft 26 and gear 86.Gear 86 transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

The follow-up torque ratio of advancing (the 6th gear) is set up by the clutch element 36 of double clutch 30 and the joint of synchronizer 120.By this joint, the clutch element 36 of double clutch 30 is passed to second interconnection axle 24 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to gear 42 from the second interconnection axle 24 by synchronizer 120.Gear 42 transfers a torque to gear 44.Gear 44 transfers a torque to countershaft 26.Countershaft 26 transfers a torque to gear 84.Gear 84 transfers a torque to gear 86, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

Follow-up torque ratio (the 7th gear) is set up by the clutch element 34 of double clutch 30 and the joint of synchronizer 130.By this joint, the clutch element 34 of double clutch 30 is passed to first interconnection axle 22 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to gear 92 from the first interconnection axle 22 by synchronizer 130.Gear 92 transfers a torque to gear 94.Gear 94 transfers a torque to countershaft 26.Countershaft 26 transfers a torque to gear 84.Gear 84 transfers a torque to gear 86, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

The present invention imagination, various torque ratios (being the torque ratio of 14 pairs of input blocks 12 of output block) can be by selective transmission 10 the number of teeth of gear realize.In addition, the present invention has advantageously provided the

driving gear

82,84,86 on the single plane.This design relatively provides the chance that reduces speed changer length with two-sided driving gear.In addition, by utilizing single pinion mate (small gear that separates with each gear), provide the flexibility of selecting about the gear ratio of first to the 7th gear.By using single plane idler gear 74, can realize the minimizing of extra speed changer length.In addition, the radially encapsulation requirement of single countershaft design reduction speed changer.

Referring now to Fig. 2,, it has shown an alternative of the present invention with multiple-speed gear-box 200.Speed changer 200 comprises input block 12 and output block 14.In this embodiment, input block 12 and output block 14 are axles, and will so call.It will be appreciated by those skilled in the art that input block and

output block

12,14 can be the members that is different from axle.Input shaft 12 links to each other with torque converter 16 or other starting arrangement constantly.The motor (not shown) is connected on the torque converter 16, and provides driving torque for torque converter 16.Output shaft 14 links to each other with main reducing gear unit 18 constantly.Speed changer 200 comprises counter shaft gear device 202, and it comprises the interconnection axle, countershaft, and the pitch wheel group of coplane and the synchronizer that optionally engages, as described below.For example, counter shaft gear device 202 comprises the first interconnection axle, the 22 and second interconnection axle 24, and it is the sleeve concentric with the first interconnection axle 22.Counter shaft gear device 202 also comprises countershaft 26.Countershaft 26 and input shaft 12, output shaft 14 and

interconnection axle

22,24 are spaced apart and parallel.Output shaft 14,

interconnection axle

22,24 and countershaft 26 comprise first case member 27, second case member 29 and the 3rd case member 31 by a plurality of supporting units

support.Case member

second interconnection axles

Double clutch 30 is connected between input shaft 12 and first and second interconnection axle 22,24.Double clutch 30 comprises with input shaft 12 and linking to each other so that the clutch outer member 32 of rotation.In addition, clutch 30 has first and second clutch elements or dish hub (hub) 34 and 36.

Clutch element

34 and 36 is configured to form friction clutch with shell 32, double clutch promptly well known in the art.More particularly,

clutch element

34,36 and clutch outer member 32 have mounted thereto interaction and form the friction plate of friction clutch.In addition, clutch element 34 links to each other with the first interconnection axle 22, so that common rotation, clutch element 36 links to each other with the second interconnection axle 24, so that common rotation.Thereby, clutch element 34 engages with the selectivity of clutch outer member 32 can with input shaft 12 and the first interconnection axle 22 couple together so that common rotation, and clutch element 36 engages with the selectivity of clutch outer member 32 and the input shaft 12 and the second interconnection axle 24 can be coupled together so that rotate jointly.

Counter shaft gear device 202 also comprises the pitch wheel group 210,220,230,240,250,260,270 and 280 of coplane.In the embodiment who is provided, gear train 210,220,230 and 240 are arranged between case member 27 and the case member 29, and gear train 250,260,270 and 280 is arranged between case member 29 and the case member 31.

Co-planar gear sets 210 comprises gear 212,214 and 216.Gear 212 is connected so that rotate jointly with the second interconnection axle 24, and is meshing with each other with idler gear 214.Idler gear 214 can rotate around idle running axis I, and is meshing with each other with gear 216.Gear 216 optionally is connected with countershaft 26 so that common rotation.

Co-planar gear sets 220 comprises gear 222 and gear 224.Gear 222 is connected so that rotate jointly with the second interconnection axle 24, and is meshing with each other with gear 224.Gear 224 optionally is connected with countershaft 26 so that common rotation.

Co-planar gear sets 230 comprises gear 232 and gear 234.Gear 232 optionally is connected so that rotate jointly with the second interconnection axle 24, and is meshing with each other with gear 234.Gear 234 is connected with countershaft 26 so that common rotation.

Co-planar gear sets 240 comprises pitch wheel 242,244 and 246.Gear 242 optionally is connected so that rotate jointly with the second interconnection axle 24, and is meshing with each other with gear 244.Gear 244 is connected with countershaft 26 so that common rotation.Gear 244 also is meshing with each other with gear 246.Gear 246 is connected with output shaft 14 so that common rotation.

Co-planar gear sets 250 comprises pitch wheel 252 and 254.Gear 252 is connected so that rotate jointly with the first interconnection axle 22, and is meshing with each other with gear 254.Gear 254 optionally is connected with countershaft 26 so that common rotation.

Gear train 260 comprises the

pitch wheel

262 and 264 of coplane.Gear 262 is connected so that common rotation with the first interconnection axle 22.Gear 264 optionally is connected with countershaft 26 so that common rotation.

Gear train 270 comprises the pitch wheel 272 and 274 of coplane.Gear 272 optionally is connected so that common rotation with the first interconnection axle 22.Gear 272 is meshing with each other with gear 274.Gear 274 is connected with countershaft 26 so that common rotation.

Co-planar gear sets 280 comprises pitch wheel 282 and 284.Gear 282 optionally is connected so that common rotation with the first interconnection axle 22.Gear 282 is meshing with each other with gear 284.Gear 284 is connected with countershaft 26 so that common rotation.

Speed changer 200 also comprises a plurality of alternative synchronizers 300,302,304,306,308,310,312 and 314 that engage.Synchronizer 300/302,304/306,308/310,312/314 is positioned at the left side and the right side of synchronizer assembly, shared public synchronizer dish hub and sleeve pipe.Synchronizer 300 optionally engages, thereby gear 216 and countershaft 26 are coupled together, so that rotation common with it.Synchronizer 302 optionally engages, thereby gear 224 and countershaft 26 are coupled together, so that rotation common with it.Synchronizer 304 optionally engages, thereby the gear 232 and the second interconnection axle 24 are coupled together, so that rotation common with it.Synchronizer 306 optionally engages, thereby the gear 242 and the second interconnection axle 24 are coupled together, so that rotation common with it.Synchronizer 308 optionally engages, thereby gear 254 and countershaft 26 are coupled together, so that rotation common with it.Synchronizer 310 optionally engages, thereby gear 264 and countershaft 26 are coupled together, so that rotation common with it.Synchronizer 312 optionally engages, thereby the gear 272 and the first interconnection axle 22 are coupled together, so that rotation common with it.Synchronizer 314 optionally engages, thereby gear 282 and countershaft 22 are coupled together, so that rotation common with it.

Speed changer 200 can be passed to output shaft 14 with moment of torsion from input shaft 12 under advancing torque ratio and a reverse gear torque ratio at least seven.The torque ratio of respectively advancing and reverse gear torque ratio realize by the joint of double clutch 30 and one of them

clutch element

34,36 and wherein one or more synchronizers 300,302,304,306,308,310,312 and 314.It will be appreciated by those skilled in the art that different velocity ratios is associated with each torque ratio.

In order to set up the reverse gear torque ratio, the clutch element 36 of double clutch 30 engages with synchronizer 300.By this joint, the clutch element 36 of double clutch 30 is passed to second interconnection axle 24 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to idler gear 210 from the second interconnection axle 24 by gear 212.Idler gear 210 transfers a torque to gear 216.When synchronizer 300 engaged, gear 216 transferred a torque to countershaft 26.Countershaft 26 transfers a torque to gear 244.Gear 244 transfers a torque to gear 246, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

First torque ratio (first gear) of advancing realizes by the clutch element 34 of double clutch 30 and the joint of synchronizer 308.By this joint, the clutch element 34 of double clutch 30 is passed to first interconnection axle 22 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to gear 252 from the first interconnection axle 22.Gear 252 transfers a torque to gear 254.When synchronizer 308 engaged, gear 254 transferred a torque to countershaft 26.Countershaft 26 transfers a torque to gear 244.Gear 244 transfers a torque to gear 246, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

The follow-up torque ratio of advancing (second gear) is set up by the clutch element 36 of double clutch 30 and the joint of synchronizer 302.By this joint, the clutch element 36 of double clutch 30 is passed to second interconnection axle 24 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to gear 222 from the second interconnection axle 24.Gear 222 transfers a torque to gear 224.When synchronizer 302 engaged, gear 224 transferred a torque to countershaft 26.Countershaft 26 transfers a torque to gear 244.Gear 244 transfers a torque to gear 246, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

Follow-up torque ratio (the 3rd gear) is set up by the clutch element 34 of double clutch 30 and the joint of synchronizer 310.By this joint, the clutch element 34 of double clutch 30 is passed to first interconnection axle 22 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to gear 262 from the first interconnection axle 22.Gear 262 transfers a torque to gear 264.When synchronizer 310 engaged, gear 264 transferred a torque to countershaft 26.Countershaft 26 transfers a torque to gear 244.Gear 244 transfers a torque to gear 246, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

Next follow-up torque ratio of advancing (the 4th gear) is set up by the clutch element 36 of double clutch 30 and the joint of synchronizer 306.By this joint, the clutch element 36 of double clutch 30 is passed to second interconnection axle 24 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, when synchronizer 306 engaged, moment of torsion can be passed to gear 242 from the second interconnection axle 24.Gear 242 transfers a torque to gear 244.Gear 244 transfers a torque to gear 246, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

Follow-up torque ratio (the 5th gear) is set up by the clutch element 34 of double clutch 30 and the joint of synchronizer 314.By this joint, the clutch element 34 of double clutch 30 is passed to first interconnection axle 22 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, when synchronizer 314 engaged, moment of torsion can be passed to gear 282 from the first interconnection axle 22.Gear 282 transfers a torque to gear 284.Gear 284 transfers a torque to countershaft 26.Countershaft 26 transfers a torque to gear 244.Gear 244 transfers a torque to gear 246, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

The follow-up torque ratio of advancing (the 6th gear) is set up by the clutch element 36 of double clutch 30 and the joint of synchronizer 304.By this joint, the clutch element 36 of double clutch 30 is passed to second interconnection axle 24 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, when synchronizer 304 engaged, moment of torsion can be passed to gear 232 from the second interconnection axle 24.Gear 232 transfers a torque to gear 234.Gear 234 transfers a torque to countershaft 26.Countershaft 26 transfers a torque to gear 244.Gear 244 transfers a torque to gear 246, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

Follow-up torque ratio (the 7th gear) is set up by the clutch element 34 of double clutch 30 and the joint of synchronizer 312.By this joint, the clutch element 34 of double clutch 30 is passed to first interconnection axle 22 from input shaft 12 by clutch outer member 32 with moment of torsion.In addition, moment of torsion can be passed to gear 272 from the first interconnection axle 22 by synchronizer 312.Gear 272 transfers a torque to gear 274.Gear 274 transfers a torque to countershaft 26.Countershaft 26 transfers a torque to gear 244.Gear 244 transfers a torque to gear 246, and it then transfers a torque to output shaft 14.Output shaft 14 passes to main reducing gear unit 18 with moment of torsion.

The present invention imagination, various torque ratios (being the torque ratio of 14 pairs of input blocks 12 of output block) can be by selective transmission 200 the number of teeth of gear realize.In addition, because small gear 212,222,232,242,252,262,272 and 282 is small gears of independent engagement (be each small gear only with a gear engagement), therefore just provide select about first, second, third, the 5th, the 6th and the 7th and the flexibility of the extra gear ratio of reverse gear gear ratio.Use by following has just realized the minimizing of whole speed changer length, and these comprise: the reverse gear idler gear in (1) single plane; (2) the single plane of driving gear; (3) single countershaft design, it has reduced the radially encapsulation requirement of speed changer.

In another embodiment of the present invention, provide Parking gear 320.As shown in Figure 2, Parking gear 320 is connected with output shaft 14 so that common rotation.When starting Parking actuator (not shown), 320 rotations of Parking gear are fixing, and therefore prevent output shaft 14 rotations.The present invention's imagination, Parking gear 320 can be positioned on other position of output shaft 14.

Be used to realize optimal mode of the present invention though described in detail, the technician in field related to the present invention should understand, within the scope of the appended claims, can make various alternative design and embodiment and implement the present invention.

Claims

1. speed changer comprises:

Input block;

Output block;

First, second, third, fourth, the the the 5th, the 6th, the 7th and the octadentate wheels, each described gear train has first gear and second gear, and wherein, described output block links to each other with one of them gear train constantly;

Be connected constantly the described the 7th and the octadentate wheels on first interconnecting member;

Second interconnecting member that links to each other with described third and fourth gear train constantly;

Be connected constantly described first, second, the countershaft on the 5th and the 6th gear train;

The double clutch assembly that optionally engages and one of them interconnecting member of described input block and described first interconnecting member and second interconnecting member is interconnected; With

Optionally with described first, second, third, fourth, the the 5th, the 6th, the 7th and four synchronizer assemblies linking up of one of them parts of one of them gear trains of octadentate wheels and described first interconnecting member, described second interconnecting member and described countershaft; And

Wherein, described double clutch assembly and described four synchronizer assemblies optionally are joined together at least in twos in combination, so that set up at least seven forward velocity ratios and at least one reverse speed ratio between described input block and described output block.

2. speed changer according to claim 1 is characterized in that, described countershaft is positioned at the radially outside and parallel with it orientation from described input block.

3. speed changer according to claim 2 is characterized in that, described output block is positioned at the radially outside and parallel with it orientation from described input block.

4. speed changer according to claim 3 is characterized in that, described first interconnecting member is concentric with described second interconnecting member.

5. speed changer according to claim 4 is characterized in that, also comprises the torque converter that links to each other with described input block constantly.

6. speed changer according to claim 1, it is characterized in that, described double clutch assembly comprises and is used for optionally first clutch that described input block and described first interconnecting member are coupled together, and is used for optionally second clutch that described input block and second interconnecting member are coupled together.

7. speed changer according to claim 1 is characterized in that, described output block links to each other with described the 5th gear train constantly.

8. speed changer according to claim 1 is characterized in that, described first, second, third, fourth, the the 5th, the 6th, the 7th and each gear trains of octadentate wheels in first gear and second gear radially aim at.

9. speed changer according to claim 8, it is characterized in that, described the 4th gear train comprises can be around the 3rd gear that rotates from the radially outside also parallel with it axis of described countershaft, and first gear and second gear of described the 3rd gear and described the 4th gear train are meshing with each other.

10. speed changer according to claim 9 is characterized in that, described the 5th gear train comprises the 3rd gear that is connected constantly on the described output block.

11. speed changer according to claim 10 is characterized in that, first, second of the described the 4th and the 5th gear train and the 3rd gear are radially aimed at.

12. speed changer according to claim 1 is characterized in that, first synchronizer assembly of described four synchronizer assemblies optionally couples together one of them gear train in described first gear train and second gear train and described second interconnecting member.

13. speed changer according to claim 12 is characterized in that, second synchronizer assembly of described four synchronizer assemblies optionally couples together one of them gear train in described the 3rd gear train and the 4th gear train and described countershaft.

14. speed changer according to claim 13 is characterized in that, the 3rd synchronizer assembly of described four synchronizer assemblies optionally couples together one of them gear train in described the 5th gear train and the 6th gear train and described first interconnecting member.

15. speed changer according to claim 14 is characterized in that, the 4th synchronizer assembly of described four synchronizer assemblies optionally couples together one of them gear train and described countershaft in described the 7th gear train and the octadentate wheels.

16. speed changer according to claim 1 is characterized in that, described first gear train can link to each other with one of them interconnecting member of described first interconnecting member and second interconnecting member, and wherein, described second gear train can link to each other with described countershaft.

17. speed changer according to claim 1, it is characterized in that, described first gear train is adjacent with described double clutch assembly, described second gear train is adjacent with described first gear train, described the 3rd gear train is adjacent with described second gear train, described the 4th gear train is adjacent with described the 3rd gear train, described the 5th gear train is adjacent with described the 4th gear train, described the 6th gear train is adjacent with described the 5th gear train, described the 7th gear train and described the 6th gear adjacent group, and described octadentate wheels are adjacent with described the 7th gear train.

18. a speed changer comprises:

Input block;

Output block;

First, second, third, fourth, the the the 5th, the 6th, the 7th and the octadentate wheels, each described gear train has first gear and second gear, and wherein, described output block links to each other with described the 5th gear train constantly;

Be connected constantly described first, second, the countershaft on the 5th and the 7th gear train;

The double clutch assembly, it comprises and is used for optionally first clutch that described input block and described first interconnecting member are coupled together, and is used for optionally second clutch that described input block and second interconnecting member are coupled together;

Be used for optionally one of them gear train with described first gear train and second gear train and be connected to first synchronizer assembly on described second interconnecting member;

Be used for optionally one of them gear train with described the 3rd gear train and the 4th gear train and be connected to second synchronizer assembly on the described countershaft;

Be used for optionally one of them gear train with described the 5th gear train and the 6th gear train and be connected to the 3rd synchronizer assembly on described first interconnecting member; With

Be used for optionally one of them gear train with described the 7th gear train and octadentate wheels and be connected to the 4th synchronizer assembly on the described countershaft;

19. speed changer according to claim 18 is characterized in that, described first, second, third, fourth, the the 5th, the 6th, the 7th and each gear trains of octadentate wheels in first gear and second gear radially aim at.

20. speed changer according to claim 19, it is characterized in that, described the 4th gear train comprises can be around the 3rd gear that rotates from the radially outside also parallel with it axis of described countershaft, first gear and second gear of described the 3rd gear and described the 4th gear train are meshing with each other, wherein, described the 5th gear train comprises the 3rd gear that is connected constantly on the described output block, and wherein, first, second of the described the 4th and the 5th gear train and the 3rd gear are radially aimed at.

21. speed changer according to claim 20 is characterized in that, described first gear train can link to each other with one of them interconnecting member of described first interconnecting member and second interconnecting member, and wherein, described second gear train can link to each other with described countershaft.

22. speed changer according to claim 21, it is characterized in that, described first gear train is adjacent with described double clutch assembly, described second gear train is adjacent with described first gear train, described the 3rd gear train is adjacent with described second gear train, described the 4th gear train is adjacent with described the 3rd gear train, described the 5th gear train is adjacent with described the 4th gear train, described the 6th gear train is adjacent with described the 5th gear train, described the 7th gear train and described the 6th gear adjacent group, and described octadentate wheels are adjacent with described the 7th gear train.

23. a speed changer comprises:

Input block;

Output block;

First, second, third, fourth, the the the 5th, the 6th, the 7th and the octadentate wheels, each described gear train has first gear and second gear, and wherein, described output block links to each other with described the 4th gear train constantly;

Constantly with the described the 5th first interconnecting member that links to each other with the 6th gear train;

Second interconnecting member that links to each other with described first and second gear trains constantly;

Constantly with described the 3rd, the 4th, the 7th countershaft that links to each other with the octadentate wheels;

The double clutch assembly, it optionally engages, thereby one of them interconnecting member of described input block and described first interconnecting member and second interconnecting member is interconnected; With

Optionally with described first, second, third, fourth, the the 5th, the 6th, the 7th and one of them gear train and described first interconnecting member of octadentate wheels, four synchronizer assemblies that one of them of described second interconnecting member and described countershaft links up

Wherein, described first gear train is adjacent with described double clutch assembly, described second gear train is adjacent with described first gear train, described the 3rd gear train is adjacent with described second gear train, and described the 4th gear train is adjacent with described the 3rd gear train, and described the 5th gear train is adjacent with described the 4th gear train, described the 6th gear train is adjacent with described the 5th gear train, described the 7th gear train and described the 6th gear adjacent group, and described octadentate wheels are adjacent with described the 7th gear train, and

24. speed changer according to claim 23 is characterized in that, also comprises being connected on the described output block to be used for optionally fixing described output block in order to avoid the Parking gear of rotation.

25. a speed changer comprises:

Input block;

Output block;

Be connected first interconnecting member on the described the 5th and the 6th gear train constantly;

Be connected constantly the described the the 3rd, the 4th, the 7th and the octadentate wheels on countershaft;

The double clutch assembly, it comprises and is used for optionally first clutch that described input block and described first interconnecting member are coupled together, and is used for optionally second clutch that described input block and described second interconnecting member are coupled together;

Be used for optionally one of them gear train with described first gear train and second gear train and be connected to first synchronizer assembly on the described countershaft;

Be used for optionally one of them gear train with described the 3rd gear train and the 4th gear train and be connected to second synchronizer assembly on described second interconnecting member;

Be used for optionally one of them gear train with described the 5th gear train and the 6th gear train and be connected to the 3rd synchronizer assembly on the described countershaft;

Be used for optionally one of them gear train with described the 7th gear train and octadentate wheels and be connected to the 4th synchronizer assembly on described first interconnecting member; And