CN102362098A - Dual clutch transmission for vehicles - Google Patents

Dual clutch transmission for vehicles Download PDF

Info

Publication number
CN102362098A
CN102362098A CN2009801200943A CN200980120094A CN102362098A CN 102362098 A CN102362098 A CN 102362098A CN 2009801200943 A CN2009801200943 A CN 2009801200943A CN 200980120094 A CN200980120094 A CN 200980120094A CN 102362098 A CN102362098 A CN 102362098A
Authority
CN
China
Prior art keywords
gear
idle pulley
countershaft
input shaft
grades
Prior art date
Application number
CN2009801200943A
Other languages
Chinese (zh)
Inventor
迈克尔·B·莫琳
阿克塞尔·盖伯格
马塞厄斯·雷姆勒
马库斯·罗肯巴克
Original Assignee
通用汽车环球科技运作公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to EP08006645 priority Critical
Priority to EP08006645.9 priority
Application filed by 通用汽车环球科技运作公司 filed Critical 通用汽车环球科技运作公司
Priority to PCT/EP2009/002354 priority patent/WO2009121570A1/en
Publication of CN102362098A publication Critical patent/CN102362098A/en

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft

Abstract

Double-clutch transmission (DCT) (1) comprises two input shafts (20, 22) that are connected to two clutch discs respectively. The DCT (1) further comprises gearwheels on lay-shafts (40, 50) and the input shafts (20, 22). The gearwheels comprise six gearwheel groups for providing six gears respec- tively. Each of the gearwheel groups comprises a fixed gearwheel on one of the input shafts (20, 22), meshing with an idler gearwheel on one of the layshafts (40, 50). A third fixed gearwheel (25) meshes with the third gear idler gearwheel (62) and the fifth gear idler gearwheel (64). Additionally, the DCT device (1) further comprises a seventh gearwheel group for providing a seventh gear. The seventh gearwheel group comprises a seventh fixed gearwheel, meshing with a seventh gear idler gearwheel (66). The DCT (1) further comprises a reverse gear idler shaft (38) and one reverse gearwheel on the reverse gear idler shaft (38) for providing a reverse gear.

Description

The double-clutch speed changer that is used for vehicle
Technical field
The present invention relates to be used for the double-clutch speed changer of vehicle.
Background technique
Double-clutch speed changer (DCT) comprises two input shafts, and they are separately connected to two clutches and are actuated by these two clutches.These two clutches are combined as single assembly usually, allow any actuate in each two clutches.These two clutches are connected to two input shafts of DCT individually so that driving torque is provided.
US 7,246, and 534 B2 have disclosed a kind of six speed dual clutch transmissions.In the automobile that this six speed dual clutch transmission also is not widely used for driving in the street.Hindering DCT is used for the street and drives the problem of using and be the DCT that will provide compact, reliable and fuel-efficient.Therefore, the DCT that can be afforded by the Consumer need be provided.
Summary of the invention
The application provides a kind of double-clutch speed changer, and it has interior input shaft and outer input shaft.Interior axle can be hollow or solid.The part of interior input shaft by outer input shaft radially around.The radial direction of axle is meant the direction of pointing to along the abaxial central axis of the radius of axle.
There are first clutch and second clutch, input shaft and outer input shaft in non-rotatably being connected to respectively.For example, first clutch is fixed to interior input shaft, and second clutch is fixed to outer input shaft.Alternatively, non-rotatable connection can provide through universal joint.
Speed changer also comprises first countershaft (layshaft), second countershaft, and this first countershaft and second countershaft and input shaft spaced radial are opened, and is parallel to the input shaft setting.
At least one of countershaft comprises fixing output gear, is used for driving torque is outputed to the moment of torsion output unit, such as the differential gearbox of vehicle.The example of vehicle comprises automobile or motorcycle.The small gear of DCT (pinion) is meshing with output gear respectively, thereby output gear will be delivered to output shaft from the moment of torsion of small gear, be used for powered vehicle.
Gear is arranged on first countershaft, on second countershaft, on the interior input shaft and on the outer input shaft.Gear comprises first gear train, second gear train, the 3rd gear train, the 4th gear train, the 5th gear train and the 6th gear train, is used to the gear that provides six to increase progressively.The gear that increases progressively has been described a kind of cumulative order, and the element in this order is followed each other.The gear of automobile is provided with the mode that reduces in succession from one grade to six grades than (gear ratio) usually.For example, in having the vehicle of gearbox, one grade of gear ratio with 2.97: 1; Second gear has 2.07: 1 gear ratio, and third gear has 1.43: 1 gear ratio, and fourth gear has 1.00: 1 gear ratio; Five grades of gear ratios with 0.84: 1, six grades of gear ratios with 0.56: 1.Six shelves provide the increase of the output speed of speed changer to be used for powered vehicle in proper order.
One grade of idle pulley gear engagement on the first gear train fixing gear of first on the input shaft that included, itself and one of them countershaft.Third gear idle pulley gear engagement on the 3rd gear train fixing gear of the 3rd on the input shaft that included, itself and one of them countershaft.Five grades of idle pulley gear engagement on the 5th gear train fixing gear of the 5th on the input shaft that included, itself and one of them countershaft.Second gear train is included in the fixing gear of second on the outer input shaft, the second gear idle pulley gear engagement on itself and one of them countershaft.The 4th gear train is included in the fixing gear of the 4th on the outer input shaft, the fourth gear idle pulley gear engagement on itself and one of them countershaft.The 6th gear train is included in the fixing gear of the 6th on the outer input shaft, six grades of idle pulley gear engagement on itself and one of them countershaft.Each gear train comprises coupling arrangement, and this coupling arrangement is arranged on one of them countershaft, is used for selecting of six shelves optionally to engage in the idle pulley gear one.
Gear and third gear idle pulley gear and the 5th idle pulley gear engagement that on the interior input shaft the 3rd is fixing.
Extraly, the double-clutch speed changer device comprises the 7th gear train, is used to provide seven grades, and the 7th gear train fixing gear of the 7th on the input shaft that included is with seven grades of idle pulley gear engagement on one of them countershaft.The 7th gear train also comprises coupling arrangement, and this coupling arrangement is arranged on one of them countershaft, optionally to engage one of them idle pulley gear, is used to select seven grades.The double-clutch speed changer device also comprises the reverse idler gear axle and is installed at least one reverse gear on the reverse idler gear axle (idler shaft), is used to provide reverse gear.
Double-clutch speed changer provides seven forward gearss through double clutch.Double clutch makes that the gear switch between odd number shelves and the even number shelves is rapidly with efficiently, because the gear that is used for odd gear and even number gear is assigned to different clutches respectively.Two engagements are provided by the fixing gear of the 3rd on the interior input shaft and third gear idle pulley gear and five grades of idle pulley gear engagement.Two engagements make double-clutch speed changer compactness, lightweight, low cost, because avoided a fixing gear on a countershaft therein.
In this application, different input shafts can provide first forward gears and reverse gear respectively.DCT is arranged in first forward gears and reverse gear on two different input shafts.The double clutch of DCT makes, the switching between two input shafts can promptly realize.Therefore, DCT alternately engage the driven strategy works of two input shafts can be apace powered vehicle forward and backward.This strategy is useful, so that vehicle is shifted out from the mud pit, because vehicle can drive before and after simply, to leave the mud pit.The momentum loss of countershaft that can realize gear and DCT is less.
In this application, this at least one reverse gear can comprise first reverse gear and second reverse gear, respectively with gear in two engagements.Double-clutch speed changer also provides reverse gear, makes vehicle to fall back.Reverse gear makes vehicle more can control.Two reverse gears make DCT eliminate the small gear that only is used for reverse gear.This small gear does not cause the quality of DCT and cost to reduce.
In this application, first reverse gear can with the second fixing gear engagement, and second reverse gear can mesh with reverse idler gear.First reverse gear and second reverse gear the two and the shared same spin axis of reverse idler gear, it is coaxial.In fact, gear typically is installed to its supporting axle coaxially, only if statement in addition.Gear and supporting axle thereof have same spin axis makes the adjacent gear engage a gear engagement as one man on the gear axle in parallel.
Double-clutch speed changer also can comprise the parking lock gear, and it is fixed to and is used to provide the locking of stopping on one of them countershaft.Countershaft with the locking of stopping comprises last driving pinion, is used to lock the differential mechanism of DCT.Differential mechanism comprises the output gear on the output shaft.The parking latch makes vehicle be parked in a position with the mode of safety, even on the slope.The parking latch is implemented easily and is useful for vehicle and passenger's safety.
In this application, at least two of one grade of idle pulley gear, second gear idle pulley gear, third gear idle pulley gear and fourth gear idle pulley gear can be installed on the same countershaft.Low-grade (for example, one, two, three and fourth gear) gear is supposed to be installed on the same countershaft, and is firm so that transmitting large torque because one of them countershaft 40,50 need be formed into.
In this application, at least two in five grades of idle pulley gears, six grades of idle pulley gears and the seven grades of idle pulley gears are installed on the same countershaft.High-grade being installed in than multi-gear provides on the same countershaft that more multimachine can be to be installed in low-grade gear on another axle.Another can be formed into short so that carry the gear of lesser amt thus.
In this application, five grades of idle pulley gears, six grades of idle pulley gears and seven grades of idle pulley gears can be installed in down on the countershaft.The gear of higher gears (for example, five, six and seven grades) is supposed to be used to be installed in same axle, and is thin because this can be formed into, to transmit less moment of torsion.Therefore, DCT can be formed into the lower and lightweight of cost.Three gears that are installed in the top grade on the same countershaft go far towards to reduce the quality of countershaft.DCT with this countershaft also can be formed into lighter.Need not be used to support the bearing of high-grade countershaft so.
In this application, coupling arrangement can comprise the bilateral coupling arrangement, is used for the left side or the gear engagement on the right side of coupling arrangement are arrived the axle that carries coupling arrangement.
In this application, also be provided with the bearing that is used to support countershaft, wherein at least one bearing is set near one in one grade of idle pulley gear and the second gear idle pulley gear.The bearing of back shaft more advantageously is set near low-grade gear.When gear during near low-grade gear, back shaft can be formed into thin, and has less deflection.
In this application, DCT also can comprise output gear, and the pinion on itself and the countershaft is so that provide output torque.Output gear receives driving torque from small gear, and single output is offered the outside of double-clutch speed changer.A plurality of joint outer parts that need be not related with countershaft.Connection to double-clutch speed changer is simplified thus.
In this application, a kind of powertrain device with gearbox is provided.This powertrain device can comprise at least one power source, is used to produce driving torque.Powertrain device alternatively is known as power train.
In this application, power source comprises internal-combustion engine.Vehicle with internal-combustion engine and double-clutch speed changer is made easily.Internal-combustion engine consumes less gasoline so that the protection environment.In addition, the internal-combustion engine that is used for other kind of fuel can even have disposal of pollutants still less, for example hydrogen fuel.
In this application, power source can comprise electric notor.Compare with typical case's burning of using fuel, the electric notor that in hybrid vehicle or electric vehicle, uses makes to pollute and reduces.
In this application, a kind of vehicle is provided, has comprised powertrain device.Vehicle with powertrain device is being efficiently through using double-clutch speed changer aspect the energy use.
Description of drawings
Fig. 1 shows embodiment's the front elevation of the application's double-clutch speed changer;
Fig. 2 shows the moment of torsion flow path of one grade of gear ratio;
Fig. 3 shows the moment of torsion flow path of second gear gear ratio;
Fig. 4 shows the moment of torsion flow path of three class gear shift ratio;
Fig. 5 shows the moment of torsion flow path of four-speed gear shift ratio;
Fig. 6 shows the moment of torsion flow path of five grades of gear ratio;
Fig. 7 shows the moment of torsion flow path of six grades of gear ratio;
Fig. 8 shows the moment of torsion flow path of seven grades of gear ratio;
Fig. 9 shows the moment of torsion flow path of reverse gear gear ratio;
Figure 10 show the bilateral coupling arrangement with its near the assembly of the gear that is used to engage;
Figure 11 show one-sided coupling arrangement with its near the assembly of the gear that is used to engage;
Figure 12 shows the assembly of idle gear, and this idle pulley is rotatably supported by axle on bearing;
Figure 13 shows the assembly of fixing gear, and this gear is supported on the axle;
Figure 14 shows the cross section according to the bent axle of DCT embodiment's internal-combustion engine;
Figure 15 shows the front elevation of replacement of expansion side view of the double-clutch speed changer of Fig. 2.
Embodiment
In following explanation, will be through description the application's embodiment.But it should be apparent to those skilled in the art that and not utilize these details to realize the present invention.
Fig. 1-14 provides embodiment's the detailed description of the application's double-clutch speed changer (DCT).
Fig. 1 shows embodiment's the front elevation of the application's double-clutch speed changer 1.DCT 1 comprises 20,22, two small gears 41,51 of 12, two input shafts of bigger output gear and reverse idler gear axle 38.Two input shafts the 20, the 22nd, solid input shaft 20 (that is, K1) with the input shaft 22 of hollow (that is, K2).Solid input shaft 20 and the input shaft of hollow 22 shared identical spin axiss, and non-rotatably be connected to two clutch wheel 8,10 of double clutch 6 separately.Two small gears the 41, the 51st, last small gear and following small gear 51.Two small gears 41,51 are fixed to countershaft 40 and following countershaft 50 respectively at their spin axis place.Output gear 12 is fixed to output shaft 14 at its spin axis place.These two small gears 41,51 mesh at the diverse location place and the output gear 12 of output gear 12 individually.
Output shaft 20,22, last countershaft 40, countershaft 50, reverse idler gear axle 38 and output shaft 14 are parallel with predetermined distance down.These are apart from along these radial direction settings of 20,22,40,50,38,14, and are visible better like Fig. 2.Other gear is installed on these axles 20,22,40,50,38,14 respectively according to predetermined way and is engaged with each other.The installation of these gears and engagement system are visible better in following accompanying drawing.
Fig. 1 has also shown cutting planes A-A, is used to show the expansion cross-sectional view through DCT 1, and this DCT shows in Fig. 2 to 9.Cutting planes A-A passes through following small gear 51, output gear 12, input gear shaft 20,22, goes up the spin axis of small gear 41 and reverse idler gear axle 38.One of them purpose of Fig. 2 to 9 is structure and the torque-flow that further shows DCT 1.
Fig. 2 shows the unfolded drawing of DCT 1, and it has shown the mode that gear is installed, and corresponding to Fig. 1.
According to Fig. 2, DCT 1 comprises with lower shaft, from the top to the bottom is reverse idler gear axle 38, last countershaft 40, solid input shaft 20, hollow input shaft 22, following countershaft 50 and output shaft 14.Solid input shaft 20 partly is arranged in the hollow input shaft 22, and solid input shaft 20 is projected into outside the hollow input shaft 22 at its place, two ends.Hollow input shaft 22 is installed to solid input shaft 20 through a pair of solid shaft bearing 71, and said a pair of solid shaft bearing 71 is arranged between solid input shaft 20 and the hollow input shaft 22 at the place, two ends of hollow input shaft 22.Therefore, two input shafts 20,22 be linked together, thereby solid input shaft 20 rotation freely in hollow input shaft 22.Hollow input shaft 22 is around the right part of solid input shaft 20, and the left part of solid input shaft 20 is exposed to outside the hollow input shaft 22.The assembly of input shaft 20,22 is located in the left side, in the protrusion end of solid shaft 20 to be supported by quill shaft bearing 72 on the right side by 71 supports of solid shaft bearing.
As shown in Figure 2, the part of solid input shaft 20 along the radial direction of input shaft 20,22 by outside input shaft 22 around.There are three gears 25,27,24, are installed in the left expose portion of solid input shaft 20.These gears the 25,27, the 24th, third gear fixed wheel 25, seven grades of fixed wheels 27 and one grade of fixed wheel 24.Third gear fixed wheel 25, seven grades of fixed wheels 27 and one grade of fixed wheel 24 one after the other are arranged in the expose portion of solid shaft 20 from right to left.Third gear fixed wheel 25 is also as five grades of fixed wheels 26.Hollow input shaft 22 is installed in the right part of solid input shaft 20, and second gear fixed wheel 30, six grades of fixed wheels 32 and fourth gear fixed wheels 31 are installed on this hollow input shaft from right to left.Second gear fixed wheel 30, six grades of fixed wheels 32 and fourth gear fixed wheel 31 are fixed to hollow input shaft 22 coaxially.
Following countershaft 50 is arranged under solid input shaft 20 and the hollow input shaft 22.There are a plurality of gears and coupling arrangement on the countershaft 50 down, from right to left, comprising small gear 51, second gear idle pulley 61, bilateral coupling arrangement 83, fourth gear idle pulley 63, third gear idle pulley 62, bilateral coupling arrangement 82 and one grade of idle pulley 60 down.A counter shaft bearing 73 is near small gear 51 and 61 the two setting of second gear idle pulley down.Another counter shaft bearing 73 is provided with near one grade of idle pulley 60 at the place, left part of following countershaft 50.Second gear idle pulley 61, fourth gear idle pulley 63, third gear idle pulley 62 and one grade of idle pulley 60 pass through Bearing Installation respectively on following countershaft 50, thus these gears the 61,63,62, the 60th, and idle pulley freely rotates around following countershaft 50.In other words, low-grade gear 60,61,62,63 is arranged on the same countershaft 50, and the bearing 73 of two countershafts is near lowest gear gear 60,61.Bilateral coupling arrangement 83 is arranged between second gear idle pulley 61 and the fourth gear idle pulley 63.Another bilateral coupling arrangement 82 is arranged between third gear idle pulley 62 and the one grade of idle pulley 60.Two bilateral coupling arrangements 82,83 are constructed to move along following countershaft 50, thereby they arrive countershaft 50 down with the gear engagement on left side or right side respectively.Second gear idle pulley 61 and 30 engagements of second gear fixed wheel.Fourth gear idle pulley 63 and 31 engagements of fourth gear fixed wheel.Third gear idle pulley 62 and 25 engagements of third gear fixed wheel.One grade of idle pulley 60 and one grade of fixed wheel 24 engagement.
Last countershaft 40 is set on the input shaft 20,22.On last countershaft 40, there are gear and coupling arrangement, from left to right, comprise small gear 41, reverse idler gear 37, bilateral coupling arrangement 80, six grades of idle pulleys 65, parking lock gear 39, five grades of idle pulleys 64, bilateral coupling arrangement 81 and seven grades of idle pulleys 66.Counter shaft bearing 73 near last small gear 41 and reverse idler gear 37 the two and between it, be provided with.Another counter shaft bearing 73 is provided with near seven grades of idle pulleys 66 at the place, the other end of last countershaft 40.Reverse idler gear 37, six grades of idle pulleys 65, five grades of idle pulleys 64 and seven grades of idle pulleys 66 respectively through Bearing Installation on last countershaft 40, thereby these gears the 37,65,64, the 66th, idle pulley freely rotates around last countershaft 40.In other words, high-grade gear 64,65,66 is installed on the same countershaft 40.Bilateral coupling arrangement 80 is constructed to move along last countershaft 40, thereby joins reverse idler gear 37 or six grades of idle pulleys 65 to countershaft 40 at every turn.Another bilateral coupling arrangement 81 is constructed to along last countershaft 40 move, thereby joins in five grades of idle pulleys 64 and the seven grades of idle pulleys 66 any to countershaft 40 at every turn.Six grades of idle pulleys 65 and six grades of fixed wheel 32 engagements.Five grades of idle pulleys 64 and five grades of fixed wheel 26 engagements.Seven grades of idle pulleys 66 and seven grades of fixed wheel 27 engagements.
In other words, at two countershafts 40, only have a two engagement between 50.Two engagements comprise via the five grade idle pulleys 64 of third gear fixed wheel 25 with 62 engagements of third gear idle pulley.Third gear fixed wheel 25 is also as five grades of fixed wheels 26.
Reverse idler gear axle 38 also is set at countershaft 40 tops.On reverse idler gear axle 38, there is gear, comprises from right to left, first reverse gear 35 and second reverse gear 36.Two idler shaft bearings 74 are provided with at the place, two ends of reverse idler gear axle 38 respectively.The two is fixed on reverse idler gear axle 38 coaxially first reverse gear 35 and second reverse gear 36.First reverse gear 35 is via intermediate gear and 61 engagements of second gear idle pulley, and this intermediate gear is a second gear fixed wheel 30.Second reverse gear 36 and reverse idler gear 37 engagements.
Output shaft 14 is arranged on down under the countershaft 50.Two opposed end places that a pair of output shaft bearing 75 is arranged on output shaft 14 are used for supporting.Output gear 12 is fixed on the output shaft 14 coaxially.Output gear 12 and following small gear 51 and last small gear 41 engagements.
In this manual, statement " engagement " and " meshing (comb) " is regarded as synonym with respect to the gear of engage a gear wheel or joint.Solid input shaft 20 alternatively is called interior input shaft 20, and hollow input shaft 22 alternatively is called outer input shaft 22.Solid input shaft 20 is alternatively replaced by quill shaft, and this quill shaft is arranged within the hollow input shaft 22.Term " coupling arrangement " is called " gearshift mechanism ", is used for gear engagement on axle or does not engage.Double-clutch speed changer (DCT) alternatively is called double clutch, double-clutch speed changer or dual clutch speed changer (DCT).In the input shaft 20,22 any can be kept more than two bearings, so that supported better.
One grade of fixed wheel 24 is also referred to as the first fixing gear 24.Third gear fixed wheel 25 is also referred to as the 3rd fixing gear 25.Five grades of fixed wheels 26 are also referred to as the 5th fixing gear 26.Seven grades of fixed wheels 27 are also referred to as the 7th fixing gear 27.Second gear fixed wheel 30 is also referred to as the second fixing gear 30.Fourth gear fixed wheel 31 is also referred to as the 4th fixing gear 31.Six grades of fixed wheels 32 are also referred to as the 6th fixing gear 32.One grade of idle pulley 60 is also referred to as one grade of idle pulley gear 60.Second gear idle pulley 60 also is called as second gear idle pulley gear 61.Third gear idle pulley 62 is also referred to as third gear idle pulley gear 62.Fourth gear idle pulley 63 is also referred to as fourth gear idle pulley gear 63.Five grades of idle pulleys 64 are also referred to as five grades of idle pulley gears 64.Six grades of idle pulleys 65 are also referred to as six grades of idle pulley gears 65.Seven grades of idle pulleys 66 are also referred to as seven grades of idle pulley gears 66.Coupling arrangement alternatively is called synchronizer.
The application provides a kind of DCT 1, and it allows driving torque loss the carrying out gear-change operation to reduce.This be because gear-change operation can be through optionally connecting DCT 1 a realization of two clutch wheel 8,10.Therefore, the additional main clutch that drives that is associated can be avoided.Connect in two clutch wheel 8, this selectivity between 10 and make also and realize automatic speed changing that this automatic speed changing can realize under the situation that no propeller power is interrupted.Propeller power comprises from the swing pinion of DCT 1 and the momentum of axle acquisition.The such speed change and the design class of mechanical hand gear seemingly, and it correspondingly has low-down frictional loss.Double-clutch speed changer 1 also provides parallel hand gear, and it can be used in the cross setting of f-w-d vehicle.
DCT 1 according to the application can be connected to known manual transmission similarly, such as parallel manual transmission.In known manual transmission, the live axle that is used for automobile front-axle stretches out from its DCT case, is parallel to the output shaft 14 of main DCT 1.The remaining less space that is provided with of known manual transmission is used for actuating of manual transmission and clutch, also is used for optional electric notor.Optional electric notor can be used as starting arrangement, is used for internal-combustion engine, is used for brake operating or as the additional drives structure of motor vehicle driven by mixed power as energy recycle device.Have so little space and show a lot of difficulties, and these difficulties are solved by the application or alleviated at least.The application provides a kind of double-clutch speed changer 1, and this double-clutch speed changer has two clutches, is used for being connected to electric notor and manual transmission with the mode of compactness.
The application provides a kind of compact structure of parallel speed changer.The application provides a kind of parallel speed changer that is used for vehicle, and each that comprises 20,22, two input shafts of two input shafts all can non-rotatably be attached to by driving motor via its oneself clutch the axle of power is provided.The application's DCT 1 also provides output shaft 14, and this output shaft 14 is parallel to input shaft 20,22.
Be particularly suitable for the cross setting of f-w-d vehicle according to the application's double-clutch speed changer 1, wherein, for example, preceding differential mechanism is positioned under the small gear 41,51.The power train that is used for transmitting torque can obtain short length overall.
The application provides at least two less small gears 41,51 on the countershaft 40,50 of centre setting, this small gear 51 and a bigger output gear 12 are meshing, and this gear 12 is connected with output shaft 14 again.This set provides the DCT 1 of compact and lightweight.
The application also allows a kind of design, and wherein, output gear 12 is incorporated into the speed changer differential mechanism, and the middle output shaft of DCT 1 is not provided.This allows to be used for very closely knit the sealing of DCT 1.
Also advantageously, on an output shaft, be provided for the fixed wheel of even number gear and on another output shaft, be provided for the fixed wheel of odd gear.When one after the other carrying out gear shift, this setting provides above-mentioned gear-change operation with level and smooth with mode efficiently.This is because DCT 1 alternately engages of two clutch wheel 8,10.For example, cause solid output shaft 20 alternately to engage with hollow output shaft 22 from one grade of gear-change operation to fourth gear, this is energy efficient and very quick.
Third gear idle pulley 62 and fourth gear idle pulley 64 provide the efficient gear shift between third gear and five grades via single two engagements of middle third gear idle pulley 25 (that is five grades of fixed wheels 26).Do not need input shaft or clutch to change to be used for the direct gear shift between third gear and five grades.Because third gear fixed wheel 25 is identical with five grades of fixed wheels 26, do not need extra gear to be used to provide each of third gear and five grades.Solid input shaft 20 can be saved a gear, so that reduce cost and the weight of DCT 1 thus by being made into shortlyer.
The gear 60,61,62,63 of low-grade (that is, one, two, three and fourth gear) is with once being provided with on the countershaft 50, and this is favourable.This be because, compare with last countershaft 40, following countershaft 50 has the slow-speed of revolution and large-size, is used for higher moment of torsion.This is provided with to eliminate provides the many countershafts with large-size to come to carry respectively the needs of those low-grade heavy duty gears 60,61,62,63.Therefore, DCT 1 be formed into light and cost less.
The bearing 73 of DCT 1 is installed to be near the gear 60,61 of low grade and small gear 41,51.This is set to axle 40,50 provides stronger mechanical support so that shaft flexing is less.Similarly, the bearing 74,75 that is used for reverse idler gear axle 38 and output shaft 14 is also near gear 12,35,36.Therefore, axle 14,38 reduces on weight so that cost is less.
Also advantageously through different input shafts 20,22 one grade of the driving of DCT 1 and the gear train of reverse gear.This provide powered vehicle slow forward and slow between backward change and not with same group of gear engagement or asynthetic ability.Only through engaging and each clutch 8,10 that does not engage two input shafts 20,22, DCT 1 makes that vehicle can be with less transmitted power or gear loss of momentum fast moving forward and backward.This helps wheel to be absorbed in many situation of rugged environment, such as nivation cirque or mud pit.Vehicle can freely wave through switching in two clutch wheel 8 of DCT 1, between 10.
The variant that on one or two of input shaft 20,22, has the embodiment of two shared gears has the higher flexibility of providing and less dependent advantage.The gear of advantageously, one grade, reverse gear and second gear is set near the bearing that is used to support.The high-grade gear of the force rate of the gear experience of these low grades (for example, a grade, second gear, reverse gear etc.) gear is big, because the velocity ratio of low-grade and reverse gear is bigger.Therefore, these power are sustained near the strong point of axle 38,50, therefore reduced the overbending of axle.
Fig. 2 shows the moment of torsion flow path of one grade of gear ratio.In Fig. 2, one grade input torque receives from the bent axle 2 of internal-combustion engine (not shown).According to Fig. 2, one grade input torque is received by the double clutch 6 of solid input shaft 20 from DCT 1.One grade moment of torsion is from solid input shaft 20, via one grade of fixed wheel 24, via one grade of idle pulley 60, via bilateral coupling arrangement 82, via following countershaft 50, via descending small gear 51, being delivered to output shaft 14 via output gear 12.(DCT is provided when transmitting one grade of moment of torsion
1 one grade) time, bilateral coupling arrangement 82 is engaged to one grade of idle pulley 60.Being used for the indented joint of one grade of moment of torsion transmission or the quantity of engaged gear mesh is two.
Fig. 3 shows the moment of torsion flow path of second gear gear ratio.In Fig. 3, the input torque of second gear receives from the bent axle 2 of internal-combustion engine (not shown).According to Fig. 3, the input torque of second gear is received by the double clutch 6 of hollow input shaft 22 from DCT 1.The moment of torsion of second gear is from the input shaft 22 of hollow, via second gear fixed wheel 30, second gear idle pulley 61, via bilateral coupling arrangement 83, via countershaft 50 down, via small gear 51 down, be delivered to output shaft 14 via output gear 12.When transmitting second gear moment of torsion (second gear of DCT 1 is provided), bilateral coupling arrangement 83 is engaged to second gear idle pulley 60.Being used for the indented joint of second gear moment of torsion transmission or the quantity of engaged gear mesh is two.
Fig. 4 shows the moment of torsion flow path of three class gear shift ratio.In Fig. 4, the input torque of third gear receives from the bent axle 2 of internal-combustion engine (not shown).According to Fig. 4, the input torque of third gear is received by the double clutch of solid input shaft 20 from DCT 1.The moment of torsion of third gear is from solid input shaft 20, via third gear fixed wheel 25, via third gear idle pulley 62, via bilateral coupling arrangement 82, via following countershaft 50, via descending small gear 51, being delivered to output shaft 14 via output gear 12.When transmitting third gear moment of torsion (third gear of DCT 1 is provided), bilateral coupling arrangement 82 is engaged to third gear idle pulley 62.Being used for the indented joint of third gear moment of torsion transmission or the quantity of engaged gear mesh is two.
Fig. 5 shows the moment of torsion flow path of four-speed gear shift ratio.In Fig. 5, the input torque of fourth gear receives from the bent axle 2 of internal-combustion engine (not shown).According to Fig. 5, the input torque of fourth gear is received by the double clutch 6 of hollow input shaft 22 from DCT 1.The moment of torsion of fourth gear is from hollow input shaft 22, via fourth gear fixed wheel 31, via fourth gear idle pulley 63, via bilateral coupling arrangement 83, via following countershaft 50, via descending small gear 51, being delivered to output shaft 14 via output gear 12.When transmitting fourth gear moment of torsion (fourth gear of DCT 1 is provided), bilateral coupling arrangement 83 is engaged to fourth gear idle pulley 63.Being used for the indented joint of fourth gear moment of torsion transmission or the quantity of engaged gear mesh is two.
Fig. 6 shows the moment of torsion flow path of five grades of gear ratio.In Fig. 6, five grades input torque receives from the bent axle 2 of internal-combustion engine (not shown).According to Fig. 6, five grades input torque is received by the double clutch 6 of solid input shaft 20 from DCT 1.Five grades moment of torsion is from solid input shaft 20, via five grades of fixed wheels 26, via five grades of idle pulleys 64, via bilateral coupling arrangement 81, via last countershaft 40, via last small gear 41, be delivered to output shaft 14 via output gear 12.When transmitting five grades of moments of torsion (provide DCT 1 five grades), bilateral coupling arrangement 81 is engaged to five grades of idle pulleys 64.Being used for the indented joint of five grades of moment of torsion transmission or the quantity of engaged gear mesh is two.
Fig. 7 shows the moment of torsion flow path of six grades of gear ratio.In Fig. 7, six grades input torque receives from the bent axle 2 of internal-combustion engine (not shown).According to Fig. 7, six grades input torque is received by the double clutch 6 of hollow input shaft 22 from DCT 1.Six grades moment of torsion is from hollow input shaft 22, via six grades of fixed wheels 32, via six grades of idle pulleys 65, via bilateral coupling arrangement 80, via last countershaft 40, via last small gear 41, be delivered to output shaft 14 via output gear 12.When transmitting six grades of moments of torsion (provide DCT 1 six grades), bilateral coupling arrangement 80 is engaged to six grades of idle pulleys 65.Being used for the indented joint of six grades of moment of torsion transmission or the quantity of engaged gear mesh is two.
Fig. 8 shows the moment of torsion flow path of seven grades of gear ratio.In Fig. 8, seven grades input torque receives from the bent axle 2 of internal-combustion engine (not shown).According to Fig. 8, seven grades input torque is received by the double clutch 6 of solid input shaft 20 from DCT 1.Seven grades moment of torsion is from solid input shaft 20, via seven grades of fixed wheels 27, via seven grades of idle pulleys 66, via bilateral coupling arrangement 81, via last countershaft 40, via last small gear 41, be delivered to output shaft 14 via output gear 12.When transmitting seven grades of moments of torsion (provide DCT 1 seven grades), bilateral coupling arrangement 81 is engaged to seven grades of idle pulleys 66.Being used for the indented joint of seven grades of moment of torsion transmission or the quantity of engaged gear mesh is two.
Fig. 9 shows the moment of torsion flow path of reverse gear gear ratio.In Fig. 9, the input torque of reverse gear receives from the bent axle 2 of internal-combustion engine (not shown).According to Fig. 9, the input torque of reverse gear is received by the double clutch 6 of hollow input shaft 22 from DCT 1.The moment of torsion of reverse gear is from hollow input shaft 22, via second gear fixed wheel 30, via first reverse gear 35, via reverse idler gear axle 38, via second reverse gear 36, via reverse idler gear 37, via bilateral coupling arrangement 80, via last countershaft 40, via last small gear 41, be delivered to output shaft 14 via output gear 12.When transmitting reverse gear moment of torsion (reverse gear of DCT 1 is provided), bilateral coupling arrangement 80 is engaged to reverse idler gear 37.Being used for the indented joint of reverse gear moment of torsion transmission or the quantity of engaged gear mesh is three.
The path of replacement can be provided, be used to transmit above-mentioned moment of torsion flow path.
Figure 10 shows the assembly 100 of bilateral coupling arrangement 102 and its adjacent gear that is used to engage 101,103.Assembly 100 comprises axle 104, has the coaxial mounted idle pulley 101,103 of two on two bearings respectively.Coupling arrangement 102 is arranged between the idle pulley 101 and right side idle pulley 103 in left side.Coupling arrangement 102 is constructed to 104 move along axle, optionally once to engage any of idle pulley 101,103.In other words, idle pulley 101,103 alternately engages with the non-rotation of axle 104 formation through coupling arrangement 102.The symbol that is used for display module 100 provides at the right-hand side of Figure 10.
Figure 11 shows the assembly 110 of one-sided coupling arrangement 112 and its adjacent gear that is used to engage 113.Assembly 110 comprises axle 114, has a coaxial mounted idle pulley 113 on bearing.Coupling arrangement 112 is provided with near idle pulley 113 in the left side.Coupling arrangement 112 is constructed to move along axle 114, to engage idle pulley 113.In other words, idle pulley 113 engages with the non-rotation of axle 104 formation through one-sided coupling arrangement 112.The symbol that is used for display module 110 provides at the right-hand side of Figure 11.
Figure 12 shows the assembly 120 that idle pulley gear 121 can be rotated to support on the bearing 123 by axle 122.Idle pulley gear 121 is installed on the axle 122 via bearing 123 coaxially.Bearing 123 makes idle pulley gear 121 freely rotate around axle 122.The symbol of display module 120 provides at the right-hand side of Figure 12.
Figure 13 shows the assembly 130 that is supported on gear 132 fixing on the axle 131.Fixing gear 132 is installed on the axle 131 coaxially, thereby gear 132 is fixed to axle 132.It is one that fixing gear 132 links with axle 131, thereby the moment of torsion of fixing gear 132 directly is delivered to axle 131, and vice versa.
A plurality of fixing gears are connected to input shaft 20,22 and other axles 14,38,40,50 securely.The symbol that formerly is used for so fixing gear in the accompanying drawing is arranged on the left side of Figure 13.The symbol that more generally uses that is used for so fixing gear is arranged on the right-hand side of Figure 13.
Figure 14 shows through the cross section according to the bent axle 2 of DCT 1 embodiment's internal-combustion engine.In Figure 14, non-rotatably be connected to the housing 4 of double clutch 6 at the bent axle 2 of this unshowned internal-combustion engine.Clutch wheel 8 and outer clutch wheel 10 in double clutch 6 comprises, they can be via control unit and housing 4 non-rotatable joints, and this control unit does not illustrate at this.Solid input shaft 20 non-rotatably is connected to clutch wheel 8, and extends through quill shaft 22 always.Similarly, hollow input shaft 22 non-rotatably is connected to another clutch wheel 10.
Clutch housing 4 around interior clutch wheel 8 than having bigger external diameter around outer clutch wheel 10.Therefore, interior clutch wheel 8 has the outer diameter bigger than outer clutch wheel 10 in clutch housing 4.Driving one grade than imperial palace clutch wheel 8 and cause DCT 1 firm on solid input shaft 20.
Above-mentioned eight moment of torsion flow paths not only provide eight gears that variable solutions produces DCT 1 (that is, seven forward gearss and retreat shelves), and the possibility that switches to another gear from a gear efficiently also is provided.For example, can realize that this intermediate gear is a third gear fixed wheel 25 via the two engagements of intermediate gear through five grades of idle pulleys 64 and third gear idle pulley 62 from the trip stop of third gear to five grade.Third gear fixed wheel 25 is also as five grades of fixed wheels 26.Trip stop between third gear and five grades need not make solid input shaft 20 stop.In addition, two engagements of third gear idle pulley 62 and five grades of idle pulleys 64 avoid on input shaft, being provided with the needs of two independent fixed gears.In other words, on hollow input shaft 22, need less space, because two fixing gears 25,26 are combined into one.DCT 1 can be formed into lighter cheap with more through reducing by a gear thus.
Parking lock gear 39 is the gears that are fixed on the countershaft 40, is used to provide the parking latch.The parking latch is the wheel that is provided with ratchet unit, and it has the pawl device, and this pawl device has rack elements, pawl-like member etc.The parking latch keeps going up countershaft 40 and prevents rotation with output shaft 14, and this makes that the vehicle with DCT 1 becomes by advancing and stops when vehicle parking.When using the parking latch, the parking lock gear 39 on the last countershaft 40 can be via last small gear 41, via output gear 12 with output shaft 14 is become from rotation stop and locking output shaft 14.
Figure 15 shows the replacement front elevation of expansion side view of the double-clutch speed changer of Fig. 2.Figure 15 comprises and the similar parts of the parts of Fig. 1 to 14.Similarly parts have similar or the same parts reference character.Similar or same parts be described in this through with reference to being introduced into.
Although above description comprises many details, they should not be regarded as restriction embodiment's scope, and only are regarded as having explained previous embodiment.Particularly, the above-mentioned advantage of present embodiment should not be regarded as restriction embodiment's scope, and only is used to explain if the potential advantages of said embodiment when being used to put into practice.Thus, the scope of present embodiment should be confirmed by claim, rather than confirm through the examples given.

Claims (15)

1. a double-clutch speed changer (1) comprising:
Interior input shaft (20) and outer input shaft (22), at least a portion of interior input shaft (20) by outer input shaft (22) radially around,
Be connected to the first clutch (8) of interior input shaft (20) and be connected to the second clutch (10) of outer input shaft (22),
First countershaft (40) and second countershaft (50), radially spaced apart with input shaft (20,22), and be parallel to input shaft (20,22) setting,
Be arranged on the gear on first countershaft (40), second countershaft (50), interior input shaft (20) and the outer input shaft (22); Said gear comprises that first gear train, second gear train, the 3rd gear train, the 4th gear train, the 5th gear train and the 6th gear train are used to provide six gears
The first gear train fixing gear (24) of first on the input shaft (20) that included, it meshes with one grade of idle pulley gear (60) on one of them countershaft (40,50),
The 3rd gear train fixing gear (25) of the 3rd on the input shaft (20) that included, it meshes with third gear idle pulley gear (62) on one of them countershaft (40,50),
The 5th gear train fixing gear (26) of the 5th on the input shaft (20) that included, it meshes with five grades of idle pulley gears (64) on one of them countershaft (40,50),
Second gear train is included in the fixing gear (30) of second on the outer input shaft (22), and it meshes with second gear idle pulley gear (61) on one of them countershaft (40,50),
The 4th gear train is included in the fixing gear (31) of the 4th on the outer input shaft (22), and it meshes with fourth gear idle pulley gear (63) on one of them countershaft (40,50),
The 6th gear train is included in the fixing gear (32) of the 6th on the outer input shaft (22), and it meshes with six grades of idle pulley gears (65) on one of them countershaft (40,50),
Each gear train comprises coupling arrangement, and this coupling arrangement is arranged on one of them countershaft (40,50), with optionally engage in the idle pulley gear one be used for selecting one of six gears and
The 3rd fixing gear (25) also meshes with the 5th idle pulley gear (64),
Wherein,
Double-clutch speed changer (1) also comprises the 7th gear train, is used to provide seven grades, the 7th gear train fixing gear (27) of the 7th on the input shaft (20) that included, and with seven grades of idle pulley gears (66) engagement on one of them countershaft (40,50),
The 7th gear train also comprises coupling arrangement, and this coupling arrangement is arranged on one of them countershaft (40,50), optionally to engage seven grades of idle pulley gears (66), be used to provide seven grades and
Double-clutch speed changer (1) also comprises reverse idler gear axle (38) and is installed at least one reverse gear on the reverse idler gear axle (38), is used to provide reverse gear.
2. double-clutch speed changer as claimed in claim 1 (1), wherein
First forward gears is provided by different input shaft (20,22) with reverse gear.
3. like each the described double-clutch speed changer (1) in the aforementioned claim, wherein
Said at least one reverse gear comprises first reverse gear (35) and second reverse gear (36), respectively with two gear engagement of seven gear trains.
4. double-clutch speed changer as claimed in claim 3 (1), wherein
First reverse gear (35) meshes with the second fixing gear (30), and second reverse gear (36) and reverse idler gear (37) engagement.
5. like each the described double-clutch speed changer (1) in the aforementioned claim, also comprise
Parking lock gear (39) is fixed to and is used to provide the locking of stopping on one of them countershaft (40,50).
6. like each the described double-clutch speed changer (1) in the aforementioned claim, wherein
At least two in one grade of idle pulley gear (60), second gear idle pulley gear (61), third gear idle pulley gear (62) and the fourth gear idle pulley gear (63) are installed on the same countershaft.
7. like each the described double-clutch speed changer (1) in the aforementioned claim, wherein
At least two in five grades of idle pulley gears (64), six grades of idle pulley gears (65) and the seven grades of idle pulley gears (66) are installed on the same countershaft.
8. double-clutch speed changer as claimed in claim 7 (1), wherein
Five grades of idle pulley gears (64), six grades of idle pulley gears (65) and seven grades of idle pulley gears (66) are installed in down on the countershaft (50).
9. double-clutch speed changer as claimed in claim 1 (1), wherein
Coupling arrangement comprises the bilateral coupling arrangement, is used for the left side or the gear engagement on the right side of coupling arrangement are arrived the axle that carries coupling arrangement.
10. like each the described double-clutch speed changer (1) in the aforementioned claim, also comprise
Be used to support the bearing of countershaft (40,50), wherein at least one bearing is set near one in one grade of idle pulley gear and the second gear idle pulley gear.
11. a gearbox has like each the described double-clutch speed changer (1) in the aforementioned claim, also comprises
Output gear (12), respectively with countershaft (40,50) on small gear (41,51) engagement so that output torque is provided.
12. a powertrain device has gearbox as claimed in claim 11, this powertrain device comprises
At least one power source is used to produce driving torque.
13. powertrain device as claimed in claim 12, wherein
Power source comprises internal-combustion engine.
14. powertrain device as claimed in claim 12, wherein
Power source comprises electric notor.
15. a vehicle comprises according to one powertrain device in the claim 12 to 14.
CN2009801200943A 2008-03-31 2009-03-31 Dual clutch transmission for vehicles CN102362098A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP08006645 2008-03-31
EP08006645.9 2008-03-31
PCT/EP2009/002354 WO2009121570A1 (en) 2008-03-31 2009-03-31 Double-clutch transmission for vehicles

Publications (1)

Publication Number Publication Date
CN102362098A true CN102362098A (en) 2012-02-22

Family

ID=45586799

Family Applications (1)

Application Number Title Priority Date Filing Date
CN2009801200943A CN102362098A (en) 2008-03-31 2009-03-31 Dual clutch transmission for vehicles

Country Status (1)

Country Link
CN (1) CN102362098A (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103453082A (en) * 2013-08-19 2013-12-18 吉孚动力技术(中国)有限公司 Hybrid double-clutch gearbox with dual gear
CN103453080A (en) * 2013-08-19 2013-12-18 吉孚动力技术(中国)有限公司 Hybrid double clutch transmission
CN103557282A (en) * 2013-08-19 2014-02-05 吉孚动力技术(中国)有限公司 Double-clutch transmission with dual gears and short idler shaft
CN103557275A (en) * 2013-08-19 2014-02-05 吉孚动力技术(中国)有限公司 Dual-clutch transmission with special reverse structure and duplex gear
CN103557285A (en) * 2013-08-19 2014-02-05 吉孚动力技术(中国)有限公司 Short-idler-shaft double-clutch transmission with dual gear
CN103557287A (en) * 2013-08-19 2014-02-05 吉孚动力技术(中国)有限公司 Short-wheelbase dual-clutch transmission adopting short idler shaft

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103453082A (en) * 2013-08-19 2013-12-18 吉孚动力技术(中国)有限公司 Hybrid double-clutch gearbox with dual gear
CN103453080A (en) * 2013-08-19 2013-12-18 吉孚动力技术(中国)有限公司 Hybrid double clutch transmission
CN103557282A (en) * 2013-08-19 2014-02-05 吉孚动力技术(中国)有限公司 Double-clutch transmission with dual gears and short idler shaft
CN103557275A (en) * 2013-08-19 2014-02-05 吉孚动力技术(中国)有限公司 Dual-clutch transmission with special reverse structure and duplex gear
CN103557285A (en) * 2013-08-19 2014-02-05 吉孚动力技术(中国)有限公司 Short-idler-shaft double-clutch transmission with dual gear
CN103557287A (en) * 2013-08-19 2014-02-05 吉孚动力技术(中国)有限公司 Short-wheelbase dual-clutch transmission adopting short idler shaft

Similar Documents

Publication Publication Date Title
US9528583B2 (en) Dual clutch gearbox with countershaft design
CN100529465C (en) Nine speed automatic transmission with six torque-transmitting mechanisms
KR100603492B1 (en) Twin-clutch manual transmission
DE102007058425B4 (en) More speed dual clutch transmission
CN100356092C (en) Double clutch transmission device
US9115789B2 (en) Double clutch transmission
EP1649192B1 (en) Twin clutch transmission with coaxial drive and output
CN103403392B (en) Double-clutch speed changer
JP5312242B2 (en) transmission
CN101230899B (en) Multi-speed countershaft transmission with a planetary gear set and method
CN101131198B (en) Powertrain with torque converter and axially compact seven speed dual clutch transmission
US8408085B2 (en) Seven speed dual clutch transmission
US6209407B1 (en) Toothed gear transmission having two partial transmissions disposed parallel to each other in the power flow
JP3533581B2 (en) Compound helical gear transmission
CN101858421B (en) Seven speed dual clutch transmission
CN100478583C (en) Eight-speed transmissions with four planetary gear sets
CN101251171B (en) Multi-speed transmission with countershaft gearing
JP4822891B2 (en) Gear transmission
CN101251169B (en) Multi-speed transmission with countershaft gearing
CN100380020C (en) Double clutch transmissions for motor vehicle
JP4855092B2 (en) Double clutch type transmission
CA2670248C (en) Dual clutch multi-speed transaxle
KR100957148B1 (en) Automatic transmission for vehicles
CN101251170B (en) Multi-speed transmission with a countershaft gearing
US9032823B2 (en) Dual clutch transmission designed as reduction gearing

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C02 Deemed withdrawal of patent application after publication (patent law 2001)
WD01 Invention patent application deemed withdrawn after publication

Application publication date: 20120222