CN103189668B - Dual-clutch transmission for front cross application - Google Patents

Dual-clutch transmission for front cross application Download PDF

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Publication number
CN103189668B
CN103189668B CN201180051753.XA CN201180051753A CN103189668B CN 103189668 B CN103189668 B CN 103189668B CN 201180051753 A CN201180051753 A CN 201180051753A CN 103189668 B CN103189668 B CN 103189668B
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CN
China
Prior art keywords
gear
plane
free
switching
output
Prior art date
Application number
CN201180051753.XA
Other languages
Chinese (zh)
Other versions
CN103189668A (en
Inventor
M·莱施
J·穆勒
R·雷施
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汽车交通工程有限公司
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Filing date
Publication date
Priority to DE102010050238 priority Critical
Priority to DE102010050238.3 priority
Priority to DE102010053130.8 priority
Priority to DE102010053130.8A priority patent/DE102010053130B4/en
Application filed by 汽车交通工程有限公司 filed Critical 汽车交通工程有限公司
Priority to PCT/DE2011/000168 priority patent/WO2012055382A1/en
Publication of CN103189668A publication Critical patent/CN103189668A/en
Application granted granted Critical
Publication of CN103189668B publication Critical patent/CN103189668B/en

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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
    • 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
    • F16H2003/0803Toothed 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 with countershafts coaxial with input or output shaft
    • 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
    • F16H2003/0807Toothed 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 with gear ratios in which the power is transferred by axially coupling idle gears
    • 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
    • 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
    • F16H2003/0933Toothed 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 with coaxial countershafts
    • 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
    • F16H2200/00Transmissions for multiple ratios
    • F16H2200/003Transmissions for multiple ratios characterised by the number of forward speeds
    • 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
    • F16H2200/00Transmissions for multiple ratios
    • F16H2200/003Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds

Abstract

The present invention relates to a kind of dual-clutch transmission for automobile.It is an object of the invention to provide the dual-clutch transmission can shifted gears to power failure-free successively of a kind of automobile for having the electromotor being transversely mounted, it includes at least nine forward gears, and described dual-clutch transmission is axially and radially being gone up compact conformation and had the mediation hierarchical sequence for maximal comfort and pull strength.This task is solved by a kind of special speed changer structure, and this structure is that described forward gear only uses the switching device unit (B, C, D, E, F, G, H, I) of four gear plane (ZRE1, ZRE2, ZRE3, ZRE4) and four two-sided actions and a single switching device.It addition, the diameter of eight gears (8,9,10,11,12,13,14,15) of described four gear plane based in the first and second gears remesh more minimum and the number of components based on for realize the multiple use of forward gear compared with forward gear quantity less.It addition, change by comfortable transmission ratio can be realized for the gear stage combination of nine forward gears that can shift gears to power failure-free.

Description

Dual-clutch transmission for front cross application

Technical field

The present invention relates to a kind of dual-clutch transmission for vehicle.

Background technology

Dual-clutch transmission be mainly characterized by two clutches switched with interrupting power.Main task is the rotating speed-moment of torsion conversion of driving means, such as internal combustion engine.Dual-clutch transmission is such as being transversely mounted internal combustion engine in the car.The clutch of variator and synchronizer operation such as can be carried out by electricity, mechanically and hydraulically operation device automatically.

DE102007049265A1 discloses a kind of dual-clutch transmission that can shift gears to power failure-free, and it includes a drive shaft, two transmission input shafts, two jackshafts and an output shaft.The transmission input shaft arranged coaxially to each other is respectively equipped with the gear that two nothings are arranged with the relative rotation, and these gears are otherwise known as fixed gear.Being respectively provided with the gear of four rotatable supportings on two jackshafts, these gears are otherwise known as free gear.Each fixed gear of transmission input shaft and each free gear engagement of two jackshafts.These three meshed gears constitutes a gear plane.Described fixed gear and free gear are arranged in four gear plane altogether.It addition, each output gear of two jackshafts all engages with a fixed gear of output shaft.Utilize the free gear on a jackshaft in one of four gear plane can realize for two direction of rotation reversed gear to change.By forward gear to shifting gears with can realizing total of eight energy power failure-free of eight gear stages in four gear plane and two other output gears with realize two and reverse gear.

Summary of the invention

The dual-clutch transmission shifted gears with it is an object of the invention to provide the compact energy power failure-free of a kind of internal combustion engine for being transversely mounted, this dual-clutch transmission realizes forward gear that is that at least eight can be shifted gears to power failure-free successively and that have favourable gear classification by the output stage of the single jackshaft circuit of four gear plane and two.

This task is addressed by the dual-clutch transmission that can shift gears to power failure-free, comprising: two can the clutches of power failure-free ground switching, the input side of the two clutch is connected with drive shaft and the outlet side of the two clutch is connected with one of two transmission input shafts being coaxially disposed of variator respectively;At least two jackshaft circuit, the first jackshaft circuit at least includes that the free gear of multiple rotatable supporting and first output gear and the second jackshaft circuit at least include the free gear of multiple rotatable supporting and second output gear;Without the fixed gear being relatively rotatably disposed on transmission input shaft, described fixed gear at least partly engages with free gear and therefore constitutes at least one gear plane, and at least one gear stage is formed;Multiple switching devices, for without connecting free gear, output gear and transmission input shaft with the relative rotation, output gear is all connected with a teeth portion of output shaft and constitutes output gear stage and output plane;Coaxially another transmission shaft is set in transmission input shaft, and without arranging two fixed gears with the relative rotation on another transmission shaft described, and another transmission shaft described can by the first switching device and the first transmission input shaft without connecting with the relative rotation, and at least in a jackshaft circuit free gear can by a switching device and other free gear without connect with the relative rotation and can by another switching device with another other free gear without being connected with the relative rotation.

By favourable scheme, the forward gear of at least eight energy power failure-free ground gearshift can realize as follows: another transmission shaft described is relatively rotatably disposed in a fixed gear among two fixed gears on another transmission shaft described in nothing and is in the first gear plane and is situated coaxially within the first transmission input shaft without being relatively rotatably disposed in the case of another fixed gear among two fixed gears on another transmission shaft described is in the second gear plane, and engage with the free gear of the first jackshaft circuit and the free gear of the second jackshaft circuit in the first gear plane, and engage with the free gear of the first jackshaft circuit and the free gear of the second jackshaft circuit in the second gear plane;The free gear engagement of the fixed gear on the first transmission input shaft and the second jackshaft circuit in the 3rd gear plane;The free gear engagement of the fixed gear on the second transmission input shaft and the free gear of the first jackshaft circuit and the second jackshaft circuit in the 4th gear plane;Another transmission shaft described can pass through the first switching device and the first transmission input shaft without being connected with the relative rotation together with being relatively rotatably disposed in two fixed gears on another transmission shaft described with nothing;In the first jackshaft circuit, the free gear of the first gear plane can be by the first output gear of the 3rd switching device and output plane without being connected by the free gear of the second switching device and the second gear plane with the relative rotation;In the first jackshaft circuit, the free gear of the 4th gear plane can be by the free gear of the 4th switching device and the second gear plane without connecting with the relative rotation;In the second jackshaft circuit, the free gear of the 3rd gear plane can be by the second output gear of the 6th switching device and output plane without being connected by the free gear of the 7th switching device or the 4th gear plane with the relative rotation;And in the second jackshaft circuit, the free gear of the 3rd gear plane can be by the 8th switching device and the free gear of the first gear plane and can be by the free gear of the 9th switching device and the second gear plane without connecting with the relative rotation.

By favourable scheme, at least nine can the forward gears of power failure-free ground gearshift can realize as follows: another transmission shaft described is being in the first gear plane and is being situated coaxially within the first transmission input shaft without being relatively rotatably disposed in the case of another fixed gear among two fixed gears on another transmission shaft described is in the second gear plane without being relatively rotatably disposed in a fixed gear among two fixed gears on another transmission shaft described, and engage with the free gear of the first jackshaft circuit and the free gear of the second jackshaft circuit in the first gear plane, and engage with the free gear of the first jackshaft circuit and the free gear of the second jackshaft circuit in the second gear plane;In the 3rd gear plane, the free gear engagement of the fixed gear on the first transmission input shaft and the free gear on the first jackshaft circuit and the second jackshaft circuit;In the 4th gear plane, the fixed gear on the second transmission input shaft and the free gear engagement of the free gear of the first jackshaft circuit and the second jackshaft circuit;Another transmission shaft described can pass through the first switching device and the first transmission input shaft without being connected with the relative rotation together with being relatively rotatably disposed in two fixed gears on another transmission shaft described with nothing;In the first jackshaft circuit, the free gear of the first gear plane can be by the first output gear of the 3rd switching device and output plane without being connected by the free gear of the second switching device and the second gear plane with the relative rotation;In the first jackshaft circuit, the free gear of the 4th gear plane can be by the 4th switching device and the free gear of the second gear plane and can be by the free gear of the 5th switching device and the 3rd gear plane without connecting with the relative rotation;In the second jackshaft circuit, the free gear of the 3rd gear plane can be by the second output gear of the 6th switching device and output plane without being connected by the free gear of the 7th switching device or the 4th gear plane with the relative rotation;And in the second jackshaft circuit, the free gear of the 3rd gear plane can be by the 8th switching device and the free gear of the first gear plane and can be by the free gear of the 9th switching device and the second gear plane without connecting with the relative rotation.

By favourable scheme, said two transmission input shaft at least through the 5th switching device and can be connected by least two gear stage.

By favourable scheme, the fixed gear of the free gear of the first gear plane of the first jackshaft circuit and the first gear plane of another transmission shaft described is engaged with each other and forms the first gear stage;The free gear of the fixed gear of the first gear plane of another transmission shaft described and the first gear plane of the second jackshaft circuit is engaged with each other and forms the second gear stage;The fixed gear of the free gear of the second gear plane of the first jackshaft circuit and the second gear plane of another transmission shaft described is engaged with each other and forms the 3rd gear stage;The free gear of the fixed gear of the second gear plane of another transmission shaft described and the second gear plane of the second jackshaft circuit is engaged with each other and forms the 4th gear stage;The fixed gear of the free gear of the 3rd gear plane of the first jackshaft circuit and the 3rd gear plane of the first transmission input shaft is engaged with each other and forms the 5th gear stage;The free gear of the fixed gear of the 3rd gear plane of the first transmission input shaft and the 3rd gear plane of the second jackshaft circuit is engaged with each other and forms the 6th gear stage;The fixed gear of the free gear of the 4th gear plane of the first jackshaft circuit and the 4th gear plane of the second transmission input shaft is engaged with each other and forms the 7th gear stage;The free gear of the fixed gear of the 4th gear plane of the second transmission input shaft and the 4th gear plane of the second jackshaft circuit is engaged with each other and forms the 8th gear stage;First output gear of the output plane of the first jackshaft circuit and the teeth portion of output shaft are engaged with each other and form the first output gear stage;Second output gear of the output plane of the second jackshaft circuit and the teeth portion of output shaft are engaged with each other and form the second output gear stage.

By favourable scheme, at least nine can power failure-free ground gearshift forward gears produce as follows: the first forward gear can by Guan Bi second clutch connect with the 8th switching device with the three, the 5th be respectively closed, and use second, third, the five, the 6th and the 7th gear stage and first export gear stage;Second forward gear can be connected with the 8th switching device with the 3rd be respectively closed by the first clutch of Guan Bi, and uses second, third and the 6th gear stage and first to export gear stage;3rd forward gear can be connected with the third and fourth switching device being respectively closed by the second clutch of Guan Bi, and uses the 7th gear stage and the first output gear stage;4th forward gear can be connected with the 9th switching device with the 3rd be respectively closed by the first clutch of Guan Bi, and uses the three, the 4th and the 6th gear stage and the first output gear stage;5th forward gear can be connected with the 6th switching device of Guan Bi by the second clutch of Guan Bi, and uses the 8th gear stage and the second output gear stage;6th forward gear can be connected with the first and second switching devices being respectively closed by the first clutch of Guan Bi, and uses the first gear stage and the first output gear stage;7th forward gear can be connected with the 4th switching device with second be respectively closed by the second clutch of Guan Bi, and uses the first, the 3rd and the 7th gear stage and the first output gear stage;8th forward gear can be connected with the 7th switching device of Guan Bi by the first clutch of Guan Bi, and uses the 6th gear stage and the second output gear stage;9th forward gear can be connected with first be respectively closed, the 4th and the 7th switching device by the second clutch of Guan Bi, and uses the three, the 6th and the 7th gear stage and the second output gear stage.

By favourable scheme, at least the first forward gear and the second forward gear, the second forward gear and the 3rd forward gear, the second forward gear and the 5th forward gear, the 3rd forward gear and the 4th forward gear, the 3rd forward gear and the 8th forward gear, the 4th forward gear and the 5th forward gear, the 5th forward gear and the 6th forward gear, the 6th forward gear and the 7th forward gear, the 7th forward gear and the 8th forward gear, the 8th forward gear and the 9th forward gear are to shift gears to power failure-free.

By favourable scheme, the gear ratio of the other forward gear of at least four is formed as follows by gear stage, output gear stage, clutch and switching device: the gear ratio of the first other forward gear is produced by the first clutch closed and first be respectively closed and the 3rd switching device and therefore produced by the 3rd gear stage and the first output gear stage;The gear ratio of the second other forward gear by Guan Bi first clutch and be respectively closed the four, the 6th and the 8th switching device produce and therefore by second, third, the six, the 7th and the 8th gear stage and second output gear stage produce, this other forward gear with the 5th forward gear be at least can power failure-free shift gears;The gear ratio of the 3rd other forward gear is produced by first clutch and the four, the 6th and the 9th switching device being respectively closed of Guan Bi and is therefore produced by the three, the four, the six, the 7th and the 8th gear stage and the second output gear stage, and this other forward gear is at least to shift gears to power failure-free with the 5th forward gear;The gear ratio of the 4th other forward gear is produced by second clutch and the four, the 7th and the 8th switching device being respectively closed of Guan Bi and is therefore produced by second, third and the 7th gear stage and the second output gear stage.

It is spaced by the speed ratio of the gear ratio of favourable scheme, at least the first six forward gear and successively decreases.

By favourable scheme, the first switching device is in the side other at the first gear plane of another transmission shaft described or between the second gear plane and the 3rd gear plane.

By favourable scheme, described switching device is configured to the shape latch members that can not switch to power failure-free.

By favourable scheme, two, four, six or eight switching devices are combined into the switching device unit of one, two, three or four two-sided action.

By favourable scheme, the switching device unit of one two-sided action is set in the first jackshaft circuit between the first gear plane and the second gear plane, and/or the switching device unit of a two-sided action is set in the first jackshaft circuit between the second gear plane and the 3rd gear plane, and/or the switching device unit of a two-sided action is set in the second jackshaft circuit between the first gear plane and the second gear plane, and/or the switching device unit of a two-sided action is set in the second jackshaft circuit between the 3rd gear plane and the 4th gear plane.

By favourable scheme, output plane is arranged between two clutches and the first gear plane, or is positioned at the other side of two clutches or the side on the 4th gear plane side.

The present invention provides a kind of dual-clutch transmission, and it includes a drive shaft and two transmission input shafts being coaxially disposed with this drive shaft, two jackshaft circuits be arrangeding in parallel and an output shaft be arrangeding in parallel.Drive shaft and output shaft, transmission input shaft and jackshaft circuit be arranged in parallel and fixed gear, free gear and switching device are in jackshaft circuit, transmission input shaft and the coaxially distribution on another transmission shaft that transmission input shaft is arranged, it is allowed to variator has short axial length.It addition, being disposed with of shape latch members that can not switch to power failure-free beneficially reduces installing space.Advantageously, eight in nine switching devices are combined into the switching device unit of four two-sided actions, and always one first or the second switching device can close.Switching device unit can be operated by a common executor.The described switching device that can not switch to power failure-free is such as configured to synchronizer.The free gear switch groups being primarily characterized in jackshaft circuit of the variator according to the present invention is fit, and this switching combining physical ability is realized by the layout of switching device.

Eight gear stage gear trains in other words are produced, because being respectively arranged with a gear of each gear plane on two parallel jackshaft circuits by two jackshaft circuits be arrangeding in parallel by four gear plane.The unit including the switching device unit of four free gears, output gear and two two-sided actions respectively is referred to as jackshaft circuit at this, and jackshaft circuit extends on all gear plane.By multiple use gear train to form gear ratio, at least nine forward gears can shifted gears to power failure-free successively can be realized by the dual-clutch transmission according to the present invention.Also can realize the other forward gear of at least four, they part the most to each other and with above-mentioned nine forward gear energy power failure-free shift gears.

One transmission shaft is co-axially located on a transmission input shaft.This transmission shaft arranges two fixed gears.Additionally on two jackshaft circuits, each free gear can be connected with two other free gear by switching device unit.

So select to be arranged in the space between gear plane switching device so that only one of which switching device is in coaxial space between transmission input shaft or another transmission shaft described and the jackshaft circuit that drive shaft is arranged respectively.Thus can reduce the jackshaft circuit wheelbase to drive shaft.Thus reduce gear diameter and the radial dimension of the most whole variator simultaneously.

First the first two forward gear gear ratio is realized by multiple gear stage.The most relatively compensate for the gear ratio of gear stage.Additionally wheelbase has approximately uniform value and switching device is saved and positions spatially.This is capable of the extremely compact structure with little radial and axial size.

Dual-clutch transmission according to the present invention another feature is that gear classification that is comfortable and that adapt to engine characteristics field.Based on this dual-clutch transmission, the speed ratio interval between the first six gear is on that successively decrease and remaining speed ratio interval remains at low levels, in order to realizes IC engine oil consumption characteristic field as optimally as possible and realizes comfortable little speed ratio interval.

As another feature of the dual-clutch transmission according to the present invention it is proposed that a kind of special construction, it allows nine gear dual-clutch transmissions to be become eight speed dual clutch transmission by omitting a switching device and a free gear in an advantageous manner.

Accompanying drawing explanation

Two kinds of embodiments of the dual-clutch transmission illustrate the energy power failure-free according to the present invention at this shifted gears.Relevant accompanying drawing is as follows:

Fig. 1 is the schematic diagram of the speed changer structure of nine gear dual-clutch transmissions;

Fig. 2 be nine can power failure-free the ground forward gears that shift gears and the shift logic of four additional forward gear and exemplary gear ratio and speed ratio interval;

Fig. 3 is the schematic diagram of the speed changer structure of eight speed dual clutch transmission;

Fig. 4 is eight shift logic of forward gears that can shift gears to power failure-free and exemplary gear ratio and speed ratio interval.

Detailed description of the invention

Dual-clutch transmission shown in Fig. 1 includes two clutches K1, K2 in this embodiment, and they are driven by drive shaft An and are configured to friction clutch K1 and K2 that can switch independently of one another.Each clutch is connected with transmission input shaft W1 or W2 of variator.Two transmission input shaft W1 and W2 are arranged in drive shaft An coaxially with each other and coaxially at this.First transmission input shaft W1 is configured to hollow axle.The the first transmission input shaft W1 being connected with first clutch K1 arranges fixed gear 3 and another transmission shaft W3, thus two transmission input shafts and described another transmission shaft W3 are coaxially to each other.Described another transmission shaft W3 arranges fixed gear 1 and 2.Described another transmission shaft W3 can be by switching device A without being connected with the first transmission input shaft W1 with the relative rotation at this.Second transmission input shaft W2 is connected with second clutch K2 and has fixed gear 4.

It addition, in dual-clutch transmission, two jackshaft circuit VWS1 and VWS2 are parallel to transmission input shaft W1 and W2 location.First jackshaft circuit VWS1 includes free gear 8,9,10,11 and output gear 5, and this output gear engages with the teeth portion of output shaft Ab.Second jackshaft circuit VWS2 includes free gear 12,13,14,15 and output gear 6, and this output gear also teeth portion with output shaft Ab engages.Free gear 8,9,10,11,12,13,14,15 can part to each other or be connected with output gear 5 and 6 nothing with the relative rotation by switching device B, C, D, E, F, G, H and I.In each of two jackshaft circuit VWS1 and VWS2, each four switching devices can be combined into the switching device unit of two two-sided actions.For switching device B-C and D-E of combination on the first jackshaft circuit VWS1, and at switching device G-F and H-I that the second jackshaft circuit VWS2 is combination.

Therefore forming four gear plane ZRE1, ZRE2, ZRE3 and ZRE4 for this dual-clutch transmission, they extend respectively on two jackshaft circuit VWS1 and VWS2, transmission input shaft W1 and W2 and described another transmission input shaft W3.Being additionally formed an output plane ABE, it extends on two jackshaft circuit VWS1 and VWS2 and transmission output shaft Ab.

First gear plane ZRE1 includes: a fixed gear 1, this fixed gear and described another transmission shaft W3 are without being connected with the relative rotation and another transmission shaft described can be rotatably set in again on the first transmission input shaft W1, and this another transmission shaft can be by switching device A without being connected with the first transmission input shaft W1 with the relative rotation;One free gear 8 of the first jackshaft circuit VWS1, this free gear rotatably supports and can be connected without output gear 5 with output plane ABE with the relative rotation by switching device B;And second another free gear 12 of jackshaft circuit VWS2, this free gear is rotatably supported and can be connected without free gear 15 with the 3rd gear plane ZRE3 with the relative rotation by switching device H.It is made up of the first gear stage α the free gear 8 of the first jackshaft circuit VWS1 and the fixed gear 1 of described another transmission shaft W3 and is constituted the second gear stage β by the free gear 12 of the second jackshaft circuit VWS2 and the fixed gear 1 of described another transmission shaft W3.

Second gear plane ZRE2 includes: a fixed gear 2, this fixed gear and transmission shaft W3 are without being connected with the relative rotation and this transmission shaft can be rotatably set in again on the first transmission input shaft W1, and this another transmission input shaft can be by switching device A without being connected with the first transmission input shaft W1 with the relative rotation;One free gear 10 of the first jackshaft circuit VWS1, this free gear rotatably supports and can be by switching device C without being connected with the output gear 5 of output plane ABE with the relative rotation and can be connected without free gear 9 with the 4th gear plane ZRE4 with the relative rotation by switching device D;And a free gear 14, this free gear be can be rotated to support on the second jackshaft circuit VWS2 and can be connected without free gear 15 with the 3rd gear plane ZRE3 with the relative rotation by switching device I.It is made up of the 3rd gear stage γ the free gear 10 of the first jackshaft circuit VWS1 and the fixed gear 2 of described another transmission shaft W3 and is constituted the 4th gear stage δ by the free gear 14 of the second jackshaft circuit VWS2 and the fixed gear 2 of described another transmission shaft W3.

3rd gear plane ZRE3 includes: a fixed gear 3, and this fixed gear and the first transmission input shaft W1 are without connecting with the relative rotation;One free gear 11 of the first jackshaft circuit VWS1, this free gear is rotatably supported and can be connected by the free gear 9 of switching device E and the 4th gear plane ZRE4;And second free gear 15 of jackshaft circuit VWS2, this free gear rotatably supports and can be by the free gear 12 of switching device H and the first gear plane ZRE1 without connecting with the relative rotation and can pass through the free gear 14 of switching device I and the second gear plane ZRE2 without connecting with the relative rotation.Free gear 15 can also be by switching device G without being connected with output gear 6 with the relative rotation.Constituted the 5th gear stage ε by the fixed gear 3 of the free gear 11 and the first transmission input shaft W1 of the first jackshaft circuit VWS1 and the fixed gear 3 by the free gear 15 and the first transmission input shaft W1 of the second jackshaft circuit VWS2 constitutes the 6th gear stage φ.

4th gear plane ZRE4 includes: one with the second transmission input shaft W2 without the fixed gear 4 being connected with the relative rotation;One free gear 9 of the rotatable supporting of the first jackshaft circuit VWS1, this free gear can be by the free gear 10 of switching device D and the second gear plane ZRE2 without connecting and can pass through the free gear 11 of switching device E and the 3rd gear plane ZRE3 without connecting with the relative rotation with the relative rotation;And second free gear 13 of rotatable supporting of jackshaft circuit VWS2, this free gear can by switching device F with output gear 6 without being connected with the relative rotation.Constituted the 7th gear stage η by the fixed gear 4 of the free gear 9 and the second transmission input shaft W2 of the first jackshaft circuit VWS1 and the fixed gear 4 by the free gear 13 and the second transmission input shaft W2 of the second jackshaft circuit VWS2 constitutes the 8th gear stage κ.

Two jackshaft route VWS1 and VWS2 are carried out in output plane ABE to the output of output shaft Ab, and the second output gear 6 that wherein first output gear 5 of the first jackshaft circuit VWS1 engaged and defined the 9th gear stage λ and the second jackshaft circuit VWS2 with the teeth portion of output shaft Ab engages and define the tenth gear stage μ with the teeth portion of output shaft Ab.

In the advantageous scheme according to the dual-clutch transmission of the present invention, output plane ABE may be provided between two clutches K1, K2 and the first gear plane ZRE1, or in dual-clutch transmission side other for gear plane ZRE4, or in dual-clutch transmission side other for clutch K1 and K2.On the one hand dual-clutch transmission side refers to the position of the axle head being connected with first clutch K2 of the second transmission input shaft W2, and on the other hand refers to the position of the most contrary axle head of transmission input shaft W2.In other words, dual-clutch transmission side refers to the position of the second end of the position of the first end of dual-clutch transmission and the contrary of dual-clutch transmission, at these four gear plane ZRE1, ZRE2, ZRE3 and ZRE4 and two clutch K1 and K2 between two ends of dual-clutch transmission.

As the alternative of this embodiment, synchronizer A can be positioned in the second and the 3rd space between gear plane ZRE2 and ZRE3 for connecting transmission input shaft W1 and described another transmission shaft W3 to reduce axial arrangement length.

The shift logic according to gear that figure 2 illustrates nine forward gear G1 to G9 that can shift gears to power failure-free is spaced together with exemplary transmission ratio and speed ratio.Also illustrate that other forward gear the most in fig. 2ExtremelyShift logic and transmission ratio.By defining the shift logic of forward gear with switching device A, B, C, D, E, F, G, H and I of clutch K1 or K2 closed according to gear and Guan Bi.In order to realize transmission ratio G1 to G9 and described other transmission ratioExtremelyThe multiple use drawn by shift logic of gear stage is as follows:

First gear stage α is used for the 6th and the 7th transmission ratio G6 and G7;

Second gear stage β is used for the first and second transmission ratio G1 and G2 and second and the 4th other transmission ratioWith

3rd gear stage γ is used for the first, second, the four, the 7th and the 9th transmission ratio G1, G2, G4, G7 and G9 and the other transmission ratio of first, second, third and fourthWith

4th gear stage δ is used for the 4th transmission ratio G4 and the 3rd other transmission ratio

5th gear stage ε is used for the first transmission ratio G1;

6th gear stage φ is used for the first, second, the four, the 8th and the 9th transmission ratio G1, G2, G4, G8 and G9 and second and the 3rd other transmission ratioWith

7th gear stage η is for the first, the three, the 7th and the 9th transmission ratio G1, G3, G7 and G9 and second, third and the 4th other transmission ratioWith

8th gear stage κ is used for the 5th transmission ratio G5 and second and the 3rd other transmission ratioWith

9th gear stage λ is used for the first, second, third, fourth, the 6th and the 7th transmission ratio G1, G2, G3, G4, G6 and G7 and the first other transmission ratio

Tenth gear stage μ is for the five, the 8th and the 9th transmission ratio G5, G8 and G9 and second, third and the 4th other transmission ratioWith

Therefore, in order to realize the transmission ratio of nine forward gear G1 to G9 that can shift gears to power failure-free and realize four described other forward gearsExtremelyTransmission ratio, the use of gear stage is as follows:

It is that the first forward gear G1 uses six gear stages β, γ, ε, φ, η and λ;

It is that the second forward gear G2 uses four gear stages β, γ, φ and λ;

It is that the 3rd forward gear G3 uses two gear stage η and λ;

It is that the 4th forward gear G4 uses four gear stages γ, δ, φ and λ;

It is that the 5th forward gear G5 uses two gear stage κ and μ;

It is that the 6th forward gear G6 uses two gear stage α and λ;

It is that the 7th forward gear G7 uses four gear stages α, γ, η and λ;

It is that the 8th forward gear G8 uses two gear stage φ and μ;

It is that the 9th forward gear G9 uses four gear stages γ, φ, η and μ;

For described other forward gearUse two gear stage γ and λ;

For described other forward gearUse six gear stages β, γ, φ, η, κ and μ;

For described other forward gearUse six gear stages γ, δ, φ, η, κ and μ;

For described other forward gearUse four gear stages β, γ, η and μ.

The speed ratio interval of the forward gear that nine shown in Fig. 2 can shift gears to power failure-free is shown as harmonic curve, and it is until the 6th gear ratio successively decreases and provides little speed ratio to be spaced to reach the optimum in IC engine oil consumption characteristic curve accordingly.

Dual-clutch transmission shown in Fig. 3 is the particularly advantageous flexible program of one of above-mentioned nine gear dual-clutch transmissions.Nine gear dual-clutch transmissions can be become eight speed dual clutch transmission by omitting switching device E and free gear 11.

Claims (14)

1. the dual-clutch transmission can shifted gears to power failure-free, comprising: two can the clutches (K1, K2) of power failure-free ground switching, the input side of the two clutch is connected with drive shaft (An) and the outlet side of the two clutch is connected with one of two transmission input shafts being coaxially disposed (W1, W2) of variator respectively;At least two jackshaft circuit (VWS1, VWS2), the first jackshaft circuit (VWS1) at least includes that the free gear (8,9,10,11) of multiple rotatable supporting and first output gear (5) and the second jackshaft circuit (VWS2) at least include the free gear (12,13,14,15) of multiple rotatable supporting and second output gear (6);Without the fixed gear (3,4) being relatively rotatably disposed on transmission input shaft (W1, W2), described fixed gear at least partly engages with free gear (8,9,10,11,12,13,14,15) and therefore constitutes at least one gear plane (ZRE1, ZRE2, ZRE3, ZRE4), and at least one gear stage (α, β, γ, δ, ε, φ, η, κ) is formed;Multiple switching devices (B, C, D, E, F, G, H, I), for without connecting free gear (8,9,10,11,12,13,14,15), output gear (5,6) and transmission input shaft (W1, W2) with the relative rotation, output gear (5,6) is all connected with a teeth portion of output shaft (Ab) and constitutes output gear stage (λ, μ) and output plane (ABE);
It is characterized in that, coaxial in transmission input shaft (W1, another transmission shaft (W3) W2) is set, and it is upper without arranging two fixed gears (1 with the relative rotation described another transmission shaft (W3), 2), and described another transmission shaft (W3) can be connected with the first transmission input shaft (W1) nothing with the relative rotation by the first switching device (A), and at least at a jackshaft circuit (VWS1, VWS2) free gear (9 in, 15) can be by a switching device (D, H) with an other free gear (10, 12) nothing connects with the relative rotation and can be by another switching device (E, I) free gear (11 other with another, 14) without connecting with the relative rotation.
Dual-clutch transmission the most according to claim 1, it is characterised in that the forward gear of at least eight energy power failure-free ground gearshift can realize as follows:
nullDescribed another transmission shaft (W3) is relatively rotatably disposed in a fixed gear (1) among two fixed gears on another transmission shaft described in nothing and is in the first gear plane (ZRE1) and is situated coaxially within the first transmission input shaft (W1) without being relatively rotatably disposed in the case of another fixed gear (2) among two fixed gears on another transmission shaft described is in the second gear plane (ZRE2),And engage with the free gear (8) of the first jackshaft circuit (VWS1) and the free gear (12) of the second jackshaft circuit (VWS2) in the first gear plane (ZRE1) without being relatively rotatably disposed in the one fixed gear (1) among two fixed gears on another transmission shaft described,And engage with the free gear (10) of the first jackshaft circuit (VWS1) and the free gear (14) of the second jackshaft circuit (VWS2) in the second gear plane (ZRE2) without being relatively rotatably disposed in described another fixed gear (2) among two fixed gears on another transmission shaft described;
In the 3rd gear plane (ZRE3), the fixed gear (3) on the first transmission input shaft (W1) engages with the free gear (15) of the second jackshaft circuit (VWS2);
In the 4th gear plane (ZRE4), the fixed gear (4) on the second transmission input shaft (W2) engages with the free gear (9) of the first jackshaft circuit (VWS1) and the free gear (13) of the second jackshaft circuit (VWS2);
Described another transmission shaft (W3) can be connected with the first transmission input shaft (W1) nothing by the first switching device (A) together with being relatively rotatably disposed in two fixed gears (1,2) on another transmission shaft described with nothing with the relative rotation;
In the first jackshaft circuit (VWS1), the free gear (8) of the first gear plane (ZRE1) can be connected with the first output gear (5) nothing of output plane (ABE) by the 3rd switching device (C) with the relative rotation by the free gear (10) of the second switching device (B) and the second gear plane (ZRE2);
In the first jackshaft circuit (VWS1), the free gear (9) of the 4th gear plane (ZRE4) can be connected with free gear (10) nothing of the second gear plane (ZRE2) with the relative rotation by the 4th switching device (D);
In the second jackshaft circuit (VWS2), the free gear (15) of the 3rd gear plane (ZRE3) can be connected with the second output gear (6) nothing of output plane (ABE) by the 6th switching device (F) with the relative rotation by the free gear (13) of the 7th switching device (G) or the 4th gear plane (ZRE4);
And in the second jackshaft circuit (VWS2), the free gear (15) of the 3rd gear plane (ZRE3) can be by the free gear (12) of the 8th switching device (H) and the first gear plane (ZRE1) and can be by the free gear (14) of the 9th switching device (I) and the second gear plane (ZRE2) without be connected with the relative rotation.
Dual-clutch transmission the most according to claim 1, it is characterised in that at least nine forward gears that can shift gears to power failure-free can realize as follows:
nullDescribed another transmission shaft (W3) is relatively rotatably disposed in a fixed gear (1) among two fixed gears on another transmission shaft described in nothing and is in the first gear plane (ZRE1) and is situated coaxially within the first transmission input shaft (W1) without being relatively rotatably disposed in the case of another fixed gear (2) among two fixed gears on another transmission shaft described is in the second gear plane (ZRE2),And engage with the free gear (8) of the first jackshaft circuit (VWS1) and the free gear (12) of the second jackshaft circuit (VWS2) in the first gear plane (ZRE1) without being relatively rotatably disposed in the one fixed gear (1) among two fixed gears on another transmission shaft described,And engage with the free gear (10) of the first jackshaft circuit (VWS1) and the free gear (14) of the second jackshaft circuit (VWS2) in the second gear plane (ZRE2) without being relatively rotatably disposed in described another fixed gear (2) among two fixed gears on another transmission shaft described;
In the 3rd gear plane (ZRE3), the fixed gear (3) on the first transmission input shaft (W1) engages with the free gear (15) of the free gear (11) on the first jackshaft circuit (VWS1) and the second jackshaft circuit (VWS2);
In the 4th gear plane (ZRE4), the fixed gear (4) on the second transmission input shaft (W2) engages with the free gear (9) of the first jackshaft circuit (VWS1) and the free gear (13) of the second jackshaft circuit (VWS2);
Described another transmission shaft (W3) can be connected with the first transmission input shaft (W1) nothing by the first switching device (A) together with being relatively rotatably disposed in two fixed gears (1,2) on another transmission shaft described with nothing with the relative rotation;
In the first jackshaft circuit (VWS1), the free gear (8) of the first gear plane (ZRE1) can be connected with the first output gear (5) nothing of output plane (ABE) by the 3rd switching device (C) with the relative rotation by the free gear (10) of the second switching device (B) and the second gear plane (ZRE2);
In the first jackshaft circuit (VWS1), the free gear (9) of the 4th gear plane (ZRE4) can be by the free gear (10) of the 4th switching device (D) and the second gear plane (ZRE2) and can be by the free gear (11) of the 5th switching device (E) and the 3rd gear plane (ZRE3) without be connected with the relative rotation;
In the second jackshaft circuit (VWS2), the free gear (15) of the 3rd gear plane (ZRE3) can be connected with the second output gear (6) nothing of output plane (ABE) by the 6th switching device (F) with the relative rotation by the free gear (13) of the 7th switching device (G) or the 4th gear plane (ZRE4);
And in the second jackshaft circuit (VWS2), the free gear (15) of the 3rd gear plane (ZRE3) can be by the free gear (12) of the 8th switching device (H) and the first gear plane (ZRE1) and can be by the free gear (14) of the 9th switching device (I) and the second gear plane (ZRE2) without be connected with the relative rotation.
4. according to the dual-clutch transmission of one of claims 1 to 3, it is characterized in that, said two transmission input shaft (W1, W2) can be at least through the 5th switching device (E) with by least two gear stage (ε, η) connection.
5. according to the dual-clutch transmission of one of claims 1 to 3, it is characterised in that
The fixed gear (1) of the free gear (8) of first gear plane (ZRE1) of the first jackshaft circuit (VWS1) and first gear plane (ZRE1) of another transmission shaft described (W3) is engaged with each other and forms the first gear stage (α);
The free gear (12) of the fixed gear (1) of first gear plane (ZRE1) of described another transmission shaft (W3) and first gear plane (ZRE1) of the second jackshaft circuit (VWS2) is engaged with each other and forms the second gear stage (β);
The fixed gear (2) of the free gear (10) of second gear plane (ZRE2) of the first jackshaft circuit (VWS1) and second gear plane (ZRE2) of another transmission shaft described (W3) is engaged with each other and forms the 3rd gear stage (γ);
The free gear (14) of the fixed gear (2) of second gear plane (ZRE2) of described another transmission shaft (W3) and second gear plane (ZRE2) of the second jackshaft circuit (VWS2) is engaged with each other and forms the 4th gear stage (δ);
The fixed gear (3) of the free gear (11) of the 3rd gear plane (ZRE3) of the first jackshaft circuit (VWS1) and the 3rd gear plane (ZRE3) of the first transmission input shaft (W1) is engaged with each other and forms the 5th gear stage (ε);
The free gear (15) of the fixed gear (3) of the 3rd gear plane (ZRE3) of the first transmission input shaft (W1) and the 3rd gear plane (ZRE3) of the second jackshaft circuit (VWS2) is engaged with each other and forms the 6th gear stage (φ);
The fixed gear (4) of the free gear (9) of the 4th gear plane (ZRE4) of the first jackshaft circuit (VWS1) and the 4th gear plane (ZRE4) of the second transmission input shaft (W2) is engaged with each other and forms the 7th gear stage (η);
The free gear (13) of the fixed gear (4) of the 4th gear plane (ZRE4) of the second transmission input shaft (W2) and the 4th gear plane (ZRE4) of the second jackshaft circuit (VWS2) is engaged with each other and forms the 8th gear stage (κ);
First output gear (5) of the output plane (ABE) of the first jackshaft circuit (VWS1) and the teeth portion of output shaft (Ab) are engaged with each other and form the first output gear stage (λ);
Second output gear (6) of the output plane (ABE) of the second jackshaft circuit (VWS2) and the teeth portion of output shaft (Ab) are engaged with each other and form the second output gear stage (μ).
6. according to the dual-clutch transmission of one of claims 1 to 3, it is characterised in that at least nine forward gears (G1, G2, G3, G4, G5, G6, G7, G8, G9) that can shift gears to power failure-free produce as follows:
First forward gear (G1) can by Guan Bi second clutch (K2) connect with the 8th switching device (C, E, H) with the three, the 5th be respectively closed, and use second, third, the five, the 6th and the 7th gear stage (β, γ, ε, φ, η) and first export gear stage (λ);
Second forward gear (G2) can be connected with the 8th switching device (C, H) with the 3rd be respectively closed by the first clutch (K1) of Guan Bi, and uses second, third and the 6th gear stage (β, γ, φ) and first to export gear stage (λ);
3rd forward gear (G3) can be connected with the third and fourth switching device (C, D) being respectively closed by the second clutch (K2) of Guan Bi, and uses the 7th gear stage (η) and the first output gear stage (λ);
4th forward gear (G4) can be connected with the 9th switching device (C, I) with the 3rd be respectively closed by the first clutch (K1) of Guan Bi, and uses the three, the 4th and the 6th gear stage (γ, δ, φ) and the first output gear stage (λ);
5th forward gear (G5) can be connected by the 6th switching device (F) of the second clutch (K2) of Guan Bi with Guan Bi, and uses the 8th gear stage (κ) and the second output gear stage (μ);
6th forward gear (G6) can be connected with the first and second switching devices (A, B) being respectively closed by the first clutch (K1) of Guan Bi, and uses the first gear stage (α) and the first output gear stage (λ);
7th forward gear (G7) can be connected with the 4th switching device (B, D) with second be respectively closed by the second clutch (K2) of Guan Bi, and uses the first, the 3rd and the 7th gear stage (α, γ, η) and the first output gear stage (λ);
8th forward gear (G8) can be connected by the 7th switching device (G) of the first clutch (K1) of Guan Bi with Guan Bi, and uses the 6th gear stage (φ) and the second output gear stage (μ);
9th forward gear (G9) can by the second clutch (K2) of Guan Bi and first be respectively closed, the 4th connect with the 7th switching device (A, D, G), and use the three, the 6th and the 7th gear stage (γ, φ, η) and second to export gear stage (μ).
7. according to the dual-clutch transmission of one of claims 1 to 3, it is characterized in that, at least the first forward gear (G1) and the second forward gear (G2), second forward gear (G2) and the 3rd forward gear (G3), second forward gear (G2) and the 5th forward gear (G5), 3rd forward gear (G3) and the 4th forward gear (G4), 3rd forward gear (G3) and the 8th forward gear (G8), 4th forward gear (G4) and the 5th forward gear (G5), 5th forward gear (G5) and the 6th forward gear (G6), 6th forward gear (G6) and the 7th forward gear (G7), 7th forward gear (G7) and the 8th forward gear (G8), 8th forward gear (G8) can be shifted gears to power failure-free with the 9th forward gear (G9).
Dual-clutch transmission the most according to claim 6, it is characterised in that the other forward gear of at least fourGear ratio formed as follows by gear stage (α, β, γ, δ, ε, φ, η, κ), output gear stage (λ, μ), clutch (K1, K2) and switching device (A, B, C, D, E, F, G, H, I):
First other forward gearGear ratio by Guan Bi first clutch (K1) and be respectively closed first and the 3rd switching device (A, C) produce and therefore by the 3rd gear stage (γ) and first output gear stage (λ) generation;
Second other forward gearGear ratio by Guan Bi first clutch (K1) and be respectively closed the four, the 6th and the 8th switching device (H, D, F) produce and therefore by second, third, the six, the 7th and the 8th gear stage (β, γ, φ, η, κ) and second output gear stage (μ) generation, this other forward gearAt least can shift gears to power failure-free with the 5th forward gear (G5);
3rd other forward gearGear ratio by Guan Bi first clutch (K1) and be respectively closed the four, the 6th and the 9th switching device (I, D, F) produce and therefore by the three, the four, the six, the 7th and the 8th gear stage (γ, δ, φ, η, κ) and second output gear stage (μ) generation, this other forward gearAt least can shift gears to power failure-free with the 5th forward gear (G5);
4th other forward gearGear ratio produced and therefore by second, third and the 7th gear stage (β, γ, η) and the second output gear stage (μ) generation by second clutch (K2) and the four, the 7th and the 8th switching device (D, H, G) being respectively closed of Guan Bi.
9. according to the dual-clutch transmission of one of claims 1 to 3, it is characterised in that successively decrease at least speed ratio interval of the gear ratio of the first six forward gear (G1 to G6).
10. according to the dual-clutch transmission of one of claims 1 to 3, it is characterized in that, the first switching device (A) is positioned at the side other at the first gear plane (ZRE1) of described another transmission shaft (W3) or is positioned between the second gear plane (ZRE2) and the 3rd gear plane (ZRE3).
11. according to the dual-clutch transmission of one of claims 1 to 3, it is characterised in that described switching device (A, B, C, D, E, F, G, H, I) is configured to the shape latch members that can not switch to power failure-free.
12. according to the dual-clutch transmission of one of claims 1 to 3, it is characterized in that, two, four, six or eight switching devices (A, B, C, D, E, F, G, H, I) are combined into the switching device unit (B-C, D-E, G-F, H-I) of one, two, three or four two-sided action.
13. dual-clutch transmissions according to claim 12, it is characterised in that
The switching device unit (B-C) of one two-sided action is set in the first jackshaft circuit (VWS1) between the first gear plane (ZRE1) and the second gear plane (ZRE2), and/or
The switching device unit (D-E) of one two-sided action is set in the first jackshaft circuit (VWS1) between the second gear plane (ZRE2) and the 3rd gear plane (ZRE3), and/or
The switching device unit (H-I) of one two-sided action is set in the second jackshaft circuit (VWS2) between the first gear plane (ZRE1) and the second gear plane (ZRE2), and/or
The switching device unit (G-F) of one two-sided action is set in the second jackshaft circuit (VWS2) between the 3rd gear plane (ZRE3) and the 4th gear plane (ZRE4).
14. according to the dual-clutch transmission of one of claims 1 to 3, it is characterized in that, output plane (ABE) is arranged between two clutches (K1, K2) and the first gear plane (ZRE1), or is positioned at the other side of two clutches (K1, K2) or the side on the 4th gear plane (ZRE4) side.
CN201180051753.XA 2010-10-27 2011-02-22 Dual-clutch transmission for front cross application CN103189668B (en)

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DE102010050238.3 2010-10-27
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DE102010053130.8A DE102010053130B4 (en) 2010-10-27 2010-11-29 Dual clutch transmission for front-transverse applications
PCT/DE2011/000168 WO2012055382A1 (en) 2010-10-27 2011-02-22 Dual-clutch gearbox for front-transverse applications

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DE102010053130B4 (en) 2019-12-19

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