CN103189668A - Dual-clutch gearbox for front-transverse applications - Google Patents
Dual-clutch gearbox for front-transverse applications Download PDFInfo
- Publication number
- CN103189668A CN103189668A CN201180051753XA CN201180051753A CN103189668A CN 103189668 A CN103189668 A CN 103189668A CN 201180051753X A CN201180051753X A CN 201180051753XA CN 201180051753 A CN201180051753 A CN 201180051753A CN 103189668 A CN103189668 A CN 103189668A
- Authority
- CN
- China
- Prior art keywords
- gear
- plane
- free
- switching member
- jack shaft
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 claims description 155
- 229910052739 hydrogen Inorganic materials 0.000 claims description 5
- 230000008093 supporting effect Effects 0.000 claims description 5
- 230000007423 decrease Effects 0.000 claims description 3
- 238000010276 construction Methods 0.000 abstract description 2
- 101000944259 Homo sapiens Calcium/calmodulin-dependent protein kinase type 1G Proteins 0.000 description 16
- 101001011446 Homo sapiens Interferon regulatory factor 6 Proteins 0.000 description 16
- 102100030130 Interferon regulatory factor 6 Human genes 0.000 description 16
- 238000002485 combustion reaction Methods 0.000 description 5
- 230000002349 favourable effect Effects 0.000 description 3
- 239000010705 motor oil Substances 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed 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
- F16H3/087—Toothed 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
- F16H3/093—Toothed 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed 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
- F16H2003/0803—Toothed 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed 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
- F16H2003/0807—Toothed 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed 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
- F16H3/087—Toothed 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
- F16H3/093—Toothed 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
- F16H2003/0931—Toothed 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed 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
- F16H3/087—Toothed 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
- F16H3/093—Toothed 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
- F16H2003/0933—Toothed 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention relates to a dual-clutch gearbox for motor vehicles. The problem addressed by the invention consists in providing a sequentially power-shiftable dual-clutch gearbox that comprises at least nine forward gears for motor vehicles with a transversely installed engine. Said gearbox has a compact construction, both axially and radially, and allows a harmonic ratio series to be implemented for the highest possible degree of comfort and traction. This problem is solved by means of a special gearbox structure which uses just four gear-wheel planes (ZRE1, ZRE2, ZRE3, ZRE4) for the forward gears, as well as four shifting element units (B, C, D, E, F, G, H, I) which act on both sides, and one single shifting element.; In addition, the diameters of the eight gear-wheels (8, 9, 10, 11, 12, 13, 14, 15) of the four gear-wheel planes are very small due to multiple tooth engagements in gears one and two, and, in proportion to the number of forward gears, the number of components is kept low by virtue of multiple usage for the implementation of the forward gears. Furthermore, a comfortable gear ratio progression can be achieved in the gearbox for the nine power-shiftable forward gears by using the combination of the gear ratios.
Description
Technical field
The present invention relates to a kind of dual-clutch transmission that is used for vehicle according to claim 1.
Background technique
The major character of dual-clutch transmission is two can not interrupt the clutch that power ground switches.Main task is the rotating speed-moment of torsion conversion of drive unit, for example internal-combustion engine.Dual-clutch transmission for example is used for laterally being installed in the internal-combustion engine of automobile.The clutch of speed changer and synchronizer operational example if can be carried out automatically by electricity, machinery and apply device.
DE102007049265A1 discloses a kind of dual-clutch transmission that can shift gears to power failure-free, and it comprises a live axle, two transmission input shafts, two jack shafts and an output shaft.The transmission input shaft of She Zhiing is respectively equipped with the gear that two nothings arrange with the relative rotation coaxially to each other, these gears fixed gear that is otherwise known as.The gear of four rotatable supportings is set, these gears free gear that is otherwise known as respectively on two jack shafts.Free gear engagement of each of each fixed gear of transmission input shaft and two jack shafts.These three meshed gears constitute a gear plane.Described fixed gear and free gear are arranged in four gear planes altogether.In addition, each output gear of two jack shafts all meshes with a fixed gear of output shaft.Utilize the free gear on a jack shaft in one of four gear planes can realize changing for two sense of rotation of reversing gear.By eight gear stages and two other output gears in four gear planes forward gear and two of the realizations that can realize eight energy power failure-free ground gearshifts are altogether reversed gear.
Goal of the invention
The object of the present invention is to provide a kind of dual-clutch transmission of energy power failure-free ground gearshift of the compactness for the internal-combustion engine of laterally installing, this dual-clutch transmission by the output stage of four gear planes and two independent jack shaft circuits realize at least eight successively can power failure-free ground forward gear that shift gears and that have favourable retaining classification.
Technological scheme
This task is solved by the device according to claim 1 feature.Favourable scheme is especially provided by dependent claims.
Invention description
The invention provides a kind of dual-clutch transmission, it comprises a live axle and two and the transmission input shaft of the coaxial setting of this live axle, jack shaft circuit and output shaft that be arranged in parallel that two be arranged in parallel.Live axle and output shaft, transmission input shaft and jack shaft circuit be arranged in parallel and fixed gear, free gear and switching member in jack shaft circuit, transmission input shaft and coaxial distribution on another transmission shaft that transmission input shaft arranges, allow speed changer to have short axial length.In addition, can not power failure-free being furnished with to be beneficial to and reducing installing space of the shape locking element that switches of ground.Advantageously, eight switching member unit that are combined into four two-sided actions in nine switching members, always one first or second switching member can be closed.The switching member unit can be by a common final controlling element operation.The described switching member that can not switch to power failure-free for example is configured to synchronizer.Mainly be the free gear switch groups zoarium of jack shaft circuit according to the feature of speed changer of the present invention, this switching combining physical efficiency realizes by the layout of switching member.
Produce eight gear stages gear train in other words by four gear planes by two jack shaft circuits that be arranged in parallel, because a gear on each gear plane is respectively arranged on two parallel jack shaft circuits.At this unit that comprises the switching member unit of four free gears, output gear and two two-sided actions respectively is called the jack shaft circuit, the jack shaft circuit extends on all gear planes.To form velocity ratio, can realize at least nine forward gears that successively can shift gears to power failure-free by dual-clutch transmission according to the present invention by multiple use gear train.Also can realize at least four other forward gears, their parts can be shifted gears on power failure-free ground to each other and with above-mentioned nine forward gears.
Coaxial being arranged on the transmission input shaft of transmission shaft.At this transmission shaft two fixed gears are set.Each free gear can be connected with two other free gear by the switching member unit on two jack shaft circuits in addition.
Select like this switching member is arranged in the space between the gear plane, make have only respectively a switching member coaxial in transmission input shaft or the space between described another transmission shaft and the jack shaft circuit that live axle arranges.Can reduce the jack shaft circuit thus to the wheelbase of live axle.Gear diameter and the therefore radial dimension of whole speed changer have been reduced simultaneously thus.
At first preceding two forward gear velocity ratios are realized by a plurality of gear stage.Compensated the velocity ratio of gear stage thus relatively.Wheelbase has approximately uniform value in addition and switching member is saved location spatially.This can realize the very compact structure with little radial and axial size.
Be comfortable and adapt to the retaining classification of engine characteristics field according to another feature of dual-clutch transmission of the present invention.Based on this dual-clutch transmission, the speed ratio between the first six gear is that speed ratio that successively decrease and remaining is on the lower level at interval at interval, in order to realize internal-combustion engine oil consumption characteristic field as far as possible best and realize comfortable little speed ratio at interval.
Can propose a kind of special construction as the another feature according to dual-clutch transmission of the present invention, it allows in an advantageous manner by omitting a switching member and a free gear becomes eight retaining dual-clutch transmissions with nine retaining dual-clutch transmissions.
The embodiment of nine retaining dual-clutch transmissions
Illustrate a kind of mode of execution of the dual-clutch transmission of shifting gears according to energy power failure-free of the present invention ground at this.Relevant accompanying drawing is as follows:
Fig. 1 is the schematic representation of the speed changer structure of nine retaining dual-clutch transmissions;
Fig. 2 is forward gear and the gearshift logic of other four forward gears and exemplary velocity ratio and the speed ratio interval of nine energy power failure-free ground gearshifts.
Dual-clutch transmission shown in Figure 1 comprises two clutch K1, K2 in this embodiment, friction clutch K1 and K2 that they are driven and be configured to switch independently of one another by a live axle An.Transmission input shaft W1 or the W2 of each clutch and speed changer are connected.Two transmission input shaft W1 and W2 are at this coaxially with each other and coaxially arrange in live axle An ground.The first transmission input shaft W1 is configured to hollow shaft.At the first transmission input shaft W1 that is connected with first clutch K1 fixed gear 3 and another transmission shaft W3 are set, thereby two transmission input shafts and described another transmission shaft W3 are coaxially to each other.At described another transmission shaft W3 fixed gear 1 and 2 are set.Described another transmission shaft W3 can not have with the relative rotation by switching member A at this and is connected with the first transmission input shaft W1.The second transmission input shaft W2 is connected with second clutch K2 and has a fixed gear 4.
In addition, in dual-clutch transmission, two jack shaft circuit VWS1 and VWS2 are parallel to transmission input shaft W1 and W2 location.The first jack shaft circuit VWS1 comprises free gear 8,9,10,11 and output gear 5, the tooth portion engagement of this output gear and output shaft Ab.The second jack shaft circuit VWS2 comprises free gear 12,13,14,15 and output gear 6, this output gear also with the tooth portion engagement of output shaft Ab. Free gear 8,9,10,11,12,13,14,15 can part be connected to each other or with output gear 5 and 6 nothings with the relative rotation by switching member B, C, D, E, F, G, H and I.Each four switching member can be combined into the switching member unit of two two-sided actions on each of two jack shaft circuit VWS1 and VWS2.At switching member B-C and the D-E of the first jack shaft circuit VWS1 for combination, and at switching member G-F and the H-I of the second jack shaft circuit VWS2 for combination.
Therefore be this dual-clutch transmission formation four gear plane ZRE1, ZRE2, ZRE3 and ZRE4, they extend at two jack shaft circuit VWS1 and VWS2, transmission input shaft W1 and W2 and described another transmission input shaft W3 respectively.Form an output plane ABE in addition, it extends at two jack shaft circuit VWS1 and VWS2 and transmission output shaft Ab.
The first gear plane ZRE1 comprises: a fixed gear 1, this fixed gear and described another transmission shaft W3 do not have and are connected with the relative rotation and described another transmission shaft can be rotatably set in again on the first transmission input shaft W1, and this another transmission shaft can not have with the relative rotation by switching member A and is connected with the first transmission input shaft W1; The free gear 8 of the first jack shaft circuit VWS1, this free gear is rotatably mounted and can not have with the relative rotation by switching member B and be connected with the output gear 5 of output plane ABE; And another free gear 12 of the second jack shaft circuit VWS2, this free gear is rotatably mounted and can not have with the relative rotation by switching member H and be connected with the free gear 15 of the 3rd gear plane ZRE3.Constitute the first gear stage α and constitute the second gear stage β by the free gear 12 of the second jack shaft circuit VWS2 and the fixed gear 1 of described another transmission shaft W3 by the free gear 8 of the first jack shaft circuit VWS1 and the fixed gear 1 of described another transmission shaft W3.
The second gear plane ZRE2 comprises: a fixed gear 2, this fixed gear and transmission shaft W3 do not have and are 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 not have with the relative rotation by switching member A and is connected with the first transmission input shaft W1; The free gear 10 of the first jack shaft circuit VWS1, this free gear is rotatably mounted and can not have to be connected with the output gear 5 of output plane ABE with the relative rotation and can not have with the relative rotation by switching member D by switching member C and be connected with the free gear 9 of the 4th gear plane ZRE4; And a free gear 14, this free gear can be rotated to support on the second jack shaft circuit VWS2 upward and can not have with the relative rotation by switching member I and is connected with the free gear 15 of the 3rd gear plane ZRE3.Constitute the 3rd gear stage γ and constitute the 4th gear stage δ by the free gear 14 of the second jack shaft circuit VWS2 and the fixed gear 2 of described another transmission shaft W3 by the free gear 10 of the first jack shaft circuit VWS1 and the fixed gear 2 of described another transmission shaft W3.
The 3rd gear plane ZRE3 comprises: a fixed gear 3, this fixed gear do not have with the relative rotation with the first transmission input shaft W1 and are connected; The free gear 11 of the first jack shaft circuit VWS1, this free gear is rotatably mounted and can be connected with the free gear 9 of the 4th gear plane ZRE4 by switching member E; And the free gear 15 of the second jack shaft circuit VWS2, this free gear is rotatably mounted and can not have by the free gear 12 of switching member H and the first gear plane ZRE1 be connected with the relative rotation and can pass through switching member I and be connected with the relative rotation with free gear 14 nothings of the second gear plane ZRE2.Free gear 15 can also not have with the relative rotation by switching member G and is connected with output gear 6.Constitute the 5th gear stage ε and constitute the 6th gear stage φ by the free gear 15 of the second jack shaft circuit VWS2 and the fixed gear 3 of the first transmission input shaft W1 by the free gear 11 of the first jack shaft circuit VWS1 and the fixed gear 3 of the first transmission input shaft W1.
The 4th gear plane ZRE4 comprises: one is not had the fixed gear 4 that is connected with the relative rotation with the second transmission input shaft W2; A free gear 9 of the rotatable supporting of the first jack shaft circuit VWS1, this free gear can be connected with the relative rotation with free gear 10 nothings of the second gear plane ZRE2 and can not have with the free gear 11 of the 3rd gear plane ZRE3 by switching member E and be connected with the relative rotation by switching member D; And a free gear 13 of the rotatable supporting of the second jack shaft circuit VWS2, this free gear can be connected with output gear 6 nothings with the relative rotation by switching member F.Constitute the 7th gear stage η and constitute the 8th gear stage κ by the free gear 13 of the second jack shaft circuit VWS2 and the fixed gear 4 of the second transmission input shaft W2 by the free gear 9 of the first jack shaft circuit VWS1 and the fixed gear 4 of the second transmission input shaft W2.
Two jack shaft route VWS1 and VWS2 carry out in output plane ABE to the output of output shaft Ab, wherein the tooth portion engagement of the tooth portion engagement of first output gear 5 of the first jack shaft circuit VWS1 and output shaft Ab and second output gear 6 that defines the 9th gear stage λ and the second jack shaft circuit VWS2 and output shaft Ab and define the tenth gear stage μ.
In the favourable scheme according to dual-clutch transmission of the present invention, output plane ABE can be arranged between two clutch K1, K2 and the first gear plane ZRE1, or it is distolateral at the other dual-clutch transmission of gear plane ZRE4, or distolateral at the dual-clutch transmission on clutch K1 and K2 side.The distolateral one side of dual-clutch transmission refers to the position of the axle head that is connected with first clutch K2 of the second transmission input shaft W2, and refers to the position of axle head of the respective opposite of transmission input shaft W2 on the other hand.In other words, the position of the position of the first end of the distolateral finger dual-clutch transmission of dual-clutch transmission and the opposite the second end of dual-clutch transmission is between these four gear plane ZRE1, ZRE2, ZRE3 and ZRE4 and two clutch K1 and two ends of K2 at dual-clutch transmission.
As this embodiment's alternative, synchronizer A can be positioned on and is used for connecting transmission input shaft W1 and described another transmission shaft W3 in the space between the second and the 3rd gear plane ZRE2 and the ZRE3 in order to reduce axial arrangement length.
The forward gear G1 to G9 of nine energy power failure-free shown in Figure 2 ground gearshift according to the gearshift logic of gear together with exemplary transmission ratio and speed ratio at interval.Other forward gear also is shown in Fig. 2 in addition
Extremely
Gearshift logic and transmission ratio.By with gearshift logic according to the clutch K1 of gear closure or K2 and closed switching member A, B, C, D, E, F, G, H and I definition forward gear.In order to realize transmission ratio G1 to G9 and described other transmission ratio
Extremely
, gear stage as follows by the multiple use that draws of gearshift logic:
The first gear stage α is used for the 6th and the 7th transmission ratio G6 and G7;
The second gear stage β is used for the first and second transmission ratio G1 and G2 and the second and the 4th other transmission ratio
With
The 3rd gear stage γ be used for first, second, the 4th, the 7th and the 9th transmission ratio G1, G2, G4, G7 and G9 and the first, second, third and the 4th other transmission ratio
With
The 4th gear stage δ is used for the 4th transmission ratio G4 and the 3rd other transmission ratio
The 5th gear stage ε is used for the first transmission ratio G1;
The 6th gear stage φ be used for first, second, the 4th, the 8th and the 9th transmission ratio G1, G2, G4, G8 and G9 and the second and the 3rd other transmission ratio
With
The 7th gear stage η is used for the first, the 3rd, the 7th and the 9th transmission ratio G1, G3, G7 and G9 and second, third and the 4th other transmission ratio
With
The 8th gear stage κ is used for the 5th transmission ratio G5 and the second and the 3rd other transmission ratio
With
The 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
The tenth gear stage μ is used for the 5th, the 8th and the 9th transmission ratio G5, G8 and G9 and second, third and the 4th other transmission ratio
With
Therefore, transmission ratio and four described other forward gears of realization in order to realize the forward gear G1 to G9 that shifts gears in nine energy power failure-free ground
Extremely
Transmission ratio, the use of gear stage is as follows:
Be that the first forward gear G1 uses six gear stage β, γ, ε, φ, η and λ;
Be that the second forward gear G2 uses four gear stage β, γ, φ and λ;
Be that the 3rd forward gear G3 uses two gear stage η and λ;
Be that the 4th forward gear G4 uses four gear stage γ, δ, φ and λ;
Be that the 5th forward gear G5 uses two gear stage κ and μ;
Be that the 6th forward gear G6 uses two gear stage α and λ;
Be that the 7th forward gear G7 uses four gear stage α, γ, η and λ;
Be that the 8th forward gear G8 uses two gear stage φ and μ;
Be that the 9th forward gear G9 uses four gear stage γ, φ, η and μ;
Be described other forward gear
Use two gear stage γ and λ;
Be described other forward gear
Use six gear stage β, γ, φ, η, κ and μ;
Be described other forward gear
Use six gear stage γ, δ, φ, η, κ and μ;
Be described other forward gear
Use four gear stage β, γ, η and μ.
The speed ratio of the forward gear of nine energy power failure-free shown in Figure 2 ground gearshift is shown as harmonic curve at interval, its until the 6th velocity ratio be successively decrease and provide little speed ratio at interval to reach the best point in the internal-combustion engine oil consumption characteristic curve accordingly.
The embodiment of eight retaining dual-clutch transmissions
Illustrate a kind of embodiment of the dual-clutch transmission of shifting gears according to energy power failure-free of the present invention ground at this.Relevant accompanying drawing is as follows:
Fig. 3 is the schematic representation of the speed changer structure of eight retaining dual-clutch transmissions;
Fig. 4 be the gearshift logic of forward gear of eight energy power failure-free ground gearshift and exemplary velocity ratio and speed ratio at interval.
Dual-clutch transmission shown in Fig. 3 is a kind of particularly advantageous flexible program of above-mentioned nine retaining dual-clutch transmissions.Nine retaining dual-clutch transmissions can be become eight retaining dual-clutch transmissions by omitting switching member E and free gear 11.
Claims (14)
1. can power failure-free the dual-clutch transmission of ground gearshift, it comprises: the clutches (K1, K2) that two energy power failure-free ground switches, the input side of these two clutches are connected with live axle (An) and the outlet side of these two clutches is connected with one of transmission input shaft (W1, W2) of two coaxial settings of speed changer respectively; At least two jack shaft circuits (VWS1, VWS2), the first jack shaft circuit (VWS1) comprise that at least the free gear (8,9,10,11) of a plurality of rotatable supportings and first output gear (5) and the second jack shaft circuit (VWS2) comprise free gear (12,13,14,15) and second output gear (6) of a plurality of rotatable supportings at least; There is not the fixed gear (3,4) that is arranged on the relative rotation on the transmission input shaft (W1, W2), described fixed gear is at least part of with free gear (8,9,10,11,12,13,14,15) engagement and therefore constitute 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; A plurality of switching members (B, C, D, E, F, G, H, I), be used for nothing and connect 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) all is connected with a tooth portion of output shaft (Ab) and constitutes exports gear stage (λ, μ) and output plane (ABE);
It is characterized in that, coaxial in transmission input shaft (W1, W2) another transmission shaft (W3) is set, and go up nothing at described another transmission shaft (W3) two fixed gears (1 are set with the relative rotation, 2), and described another transmission shaft (W3) can be connected with first transmission input shaft (W1) nothing with the relative rotation by first switching member (A), and at least at a jack shaft circuit (VWS1, VWS2) free gear (9 in, 15) can be by a switching member (D, H) with an other free gear (10,12) nothing connects with the relative rotation and can be by another switching member (E, I) with another other free gear (11,14) there is not connection with the relative rotation.
2. according to the dual-clutch transmission of claim 1, it is characterized in that the forward gear of at least eight energy power failure-free ground gearshifts can be realized as follows:
Described another transmission shaft (W3) is in the first gear plane (ZRE1) and fixed gear (2) is under the situation in the second gear plane (ZRE2) and is positioned at coaxially on first transmission input shaft (W1) at fixed gear (1), and in the first gear plane (ZRE1), mesh with the free gear (8) of the first jack shaft circuit (VWS1) and the free gear (12) of the second jack shaft circuit (VWS2), and in the second gear plane (ZRE2), mesh with the free gear (10) of the first jack shaft circuit (VWS1) and the free gear (14) of the second jack shaft circuit (VWS2);
Fixed gear (3) in the 3rd gear plane (ZRE3) on first transmission input shaft (W1) meshes with the free gear (15) of the second jack shaft circuit (VWS2);
Fixed gear (4) in the 4th gear plane (ZRE4) on second transmission input shaft (W2) meshes with the free gear (9) of the first jack shaft circuit (VWS1) and the free gear (13) of the second jack shaft circuit (VWS2);
Described another transmission shaft (W3) can be connected with first transmission input shaft (W1) nothing by first switching member (A) with the relative rotation with fixed gear (1,2);
In the first jack shaft circuit (VWS1), the free gear (8) on the first gear plane (ZRE1) can be connected with first output gear (5) nothing of output plane (ABE) by the 3rd switching member (C) with the relative rotation by the free gear (10) on second switching member (B) and the second gear plane (ZRE2);
In the first jack shaft circuit (VWS1), the free gear (9) on the 4th gear plane (ZRE4) can be connected with free gear (10) nothing on the second gear plane (ZRE2) with the relative rotation by the 4th switching member (D);
In the second jack shaft circuit (VWS2), the free gear (15) on the 3rd gear plane (ZRE3) can be connected with second output gear (6) nothing of output plane (ABE) by the 6th switching member (F) with the relative rotation by the free gear (13) on the 7th switching member (G) or the 4th gear plane (ZRE4);
And in the second jack shaft circuit (VWS2), the free gear (15) on the 3rd gear plane (ZRE3) can and can not have with the free gear (14) on the second gear plane (ZRE2) by the 9th switching member (I) by the free gear (12) on the 8th switching member (H) and the first gear plane (ZRE1) and be connected with the relative rotation.
3. according to the dual-clutch transmission of claim 1, it is characterized in that the forward gear of at least nine energy power failure-free ground gearshifts can be realized as follows:
Described another transmission shaft (W3) is in the first gear plane (ZRE1) and fixed gear (2) is under the situation in the second gear plane (ZRE2) and is positioned at coaxially on first transmission input shaft (W1) at fixed gear (1), and in the first gear plane (ZRE1), mesh with the free gear (8) of the first jack shaft circuit (VWS1) and the free gear (12) of the second jack shaft circuit (VWS2), and in the second gear plane (ZRE2), mesh with the free gear (10) of the first jack shaft circuit (VWS1) and the free gear (14) of the second jack shaft circuit (VWS2);
In the 3rd gear plane (ZRE3), the free gear (11) on the fixed gear (3) on first transmission input shaft (W1) and the first jack shaft circuit (VWS1) and the engagement of the free gear (15) of the second jack shaft circuit (VWS2);
In the 4th gear plane (ZRE4), the fixed gear (4) on second transmission input shaft (W2) meshes with the free gear (9) of the first jack shaft circuit (VWS1) and the free gear (13) of the second jack shaft circuit (VWS2);
Described another transmission shaft (W3) can be connected with first transmission input shaft (W1) nothing by first switching member (A) with the relative rotation with fixed gear (1,2);
In the first jack shaft circuit (VWS1), the free gear (8) on the first gear plane (ZRE1) can be connected with first output gear (5) nothing of output plane (ABE) by the 3rd switching member (C) with the relative rotation by the free gear (10) on second switching member (B) and the second gear plane (ZRE2);
In the first jack shaft circuit (VWS1), the free gear (9) on the 4th gear plane (ZRE4) can and can not have with the free gear (11) on the 3rd gear plane (ZRE3) by the 5th switching member (E) by the free gear (10) on the 4th switching member (D) and the second gear plane (ZRE2) and be connected with the relative rotation;
In the second jack shaft circuit (VWS2), the free gear (15) on the 3rd gear plane (ZRE3) can be connected with second output gear (6) nothing of output plane (ABE) by the 6th switching member (F) with the relative rotation by the free gear (13) on the 7th switching member (G) or the 4th gear plane (ZRE4);
And in the second jack shaft circuit (VWS2), the free gear (15) on the 3rd gear plane (ZRE3) can and can not have with the free gear (14) on the second gear plane (ZRE2) by the 9th switching member (I) by the free gear (12) on the 8th switching member (H) and the first gear plane (ZRE1) and be connected with the relative rotation.
4. according to the dual-clutch transmission of one of aforesaid right requirement, it is characterized in that described two transmission input shafts (W1, W2) can pass through the 5th switching member (E) at least and be connected by at least two gear stages (ε, η).
5. according to the dual-clutch transmission of one of aforesaid right requirement, it is characterized in that,
The fixed gear (1) on the free gear (8) on the first gear plane (ZRE1) of the first jack shaft circuit (VWS1) and the first gear plane (ZRE1) of described another transmission shaft (W3) is engaged with each other and forms first gear stage (α);
The free gear (12) on the fixed gear (1) on the first gear plane (ZRE1) of described another transmission shaft (W3) and the first gear plane (ZRE1) of the second jack shaft circuit (VWS2) is engaged with each other and forms second gear stage (β);
The fixed gear (2) on the free gear (10) on the second gear plane (ZRE2) of the first jack shaft circuit (VWS1) and the second gear plane (ZRE2) of described another transmission shaft (W3) is engaged with each other and forms the 3rd gear stage (γ);
The free gear (14) on the fixed gear (2) on the second gear plane (ZRE2) of described another transmission shaft (W3) and the second gear plane (ZRE2) of the second jack shaft circuit (VWS2) is engaged with each other and forms the 4th gear stage (δ);
The fixed gear (3) on the free gear (11) on the 3rd gear plane (ZRE3) of the first jack shaft circuit (VWS1) and the 3rd gear plane (ZRE3) of first transmission input shaft (W1) is engaged with each other and forms the 5th gear stage (ε);
The free gear (15) on the fixed gear (3) on the 3rd gear plane (ZRE3) of first transmission input shaft (W1) and the 3rd gear plane (ZRE3) of the second jack shaft circuit (VWS2) is engaged with each other and forms the 6th gear stage (φ);
The fixed gear (4) on the free gear (9) on the 4th gear plane (ZRE4) of the first jack shaft circuit (VWS1) and the 4th gear plane (ZRE4) of second transmission input shaft (W2) is engaged with each other and forms the 7th gear stage (η);
The free gear (13) on the fixed gear (4) on the 4th gear plane (ZRE4) of second transmission input shaft (W2) and the 4th gear plane (ZRE4) of the second jack shaft 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 jack shaft circuit (VWS1) and the tooth 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 jack shaft circuit (VWS2) and the tooth 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 aforesaid right requirement, it is characterized in that the forward gear (G1, G2, G3, G4, G5, G6, G7, G8, G9) of at least nine energy power failure-free ground gearshifts produces as follows:
First forward gear (G1) can by closed second clutch (K2) and respectively closed the 3rd, the 5th and the 8th switching member (C, E, H) connect, and use second, third, the 5th, the 6th and the 7th gear stage (β, γ, ε, φ, η) and first exports gear stage (λ);
Second forward gear (G2) can be connected by first clutch (K1) and closed the 3rd and the 8th switching member (C, H) of difference of closure, and uses second, third and the 6th gear stage (β, γ, φ) and first to export gear stage (λ);
The 3rd forward gear (G3) can be connected by closed second clutch (K2) and closed third and fourth switching member (C, D) of difference, and uses the 7th gear stage (η) and the first output gear stage (λ);
The 4th forward gear (G4) can be connected by closed first clutch (K1) and closed the 3rd and the 9th switching member (C, I) of difference, and uses the 3rd, the 4th and the 6th gear stage (γ, δ, φ) and the first output gear stage (λ);
The 5th forward gear (G5) can be connected by closed second clutch (K2) and closed the 6th switching member (F), and uses the 8th gear stage (κ) and the second output gear stage (μ);
The 6th forward gear (G6) can be connected by closed first clutch (K1) and closed first and second switching members (A, B) of difference, and uses first gear stage (α) and the first output gear stage (λ);
The 7th forward gear (G7) can be connected by closed second clutch (K2) and closed the second and the 4th switching member (B, D) of difference, and uses the first, the 3rd and the 7th gear stage (α, γ, η) and the first output gear stage (λ);
The 8th forward gear (G8) can be connected by closed first clutch (K1) and closed the 7th switching member (G), and uses the 6th gear stage (φ) and the second output gear stage (μ);
The 9th forward gear (G9) can be connected by closed second clutch (K2) and closed the first, the 4th and the 7th switching member (A, D, G) of difference, and uses the 3rd, the 6th and the 7th gear stage (γ, φ, η) and the second output gear stage (μ).
7. the dual-clutch transmission that one of requires according to aforesaid right, it is characterized in that having first forward gear (G1) and second forward gear (G2) at least, second forward gear (G2) and the 3rd forward gear (G3), second forward gear (G2) and the 5th forward gear (G5), the 3rd forward gear (G3) and the 4th forward gear (G4), the 3rd forward gear (G3) and the 8th forward gear (G8), the 4th forward gear (G4) and the 5th forward gear (G5), the 5th forward gear (G5) and the 6th forward gear (G6), the 6th forward gear (G6) and the 7th forward gear (G7), the 7th forward gear (G7) and the 8th forward gear (G8), the 8th forward gear (G8) is to shift gears on power failure-free ground with the 9th forward gear (G9).
8. according to the dual-clutch transmission of claim 6, it is characterized in that at least four other forward gears
Velocity ratio form as follows by gear stage (α, β, γ, δ, ε, φ, η, κ), output gear stage (λ, μ), clutch (K1, K2) and switching member (A, B, C, D, E, F, G, H, I):
The first other forward gear
Velocity ratio by closed first clutch (K1) and respectively closed the first and the 3rd switching member (A, C) produce and therefore by the 3rd gear stage (γ) and first output gear stage (λ) generation;
The second other forward gear
Velocity ratio by closed first clutch (K1) and respectively closed the 4th, the 6th and the 8th switching member (H, D, F) produce and therefore by second, third, the 6th, the 7th and the 8th gear stage (β, γ, φ, η, κ) and second output gear stage (μ) generation, this other forward gear
At least be to shift gears on power failure-free ground with the 5th forward gear (G5);
The 3rd other forward gear
Velocity ratio by closed first clutch (K1) and respectively closed the 4th, the 6th and the 9th switching member (I, D, F) produce and therefore by the 3rd, the 4th, the 6th, the 7th and the 8th gear stage (γ, δ, φ, η, κ) and second output gear stage (μ) generation, this other forward gear
At least be to shift gears on power failure-free ground with the 5th forward gear (G5);
The 4th other forward gear
Velocity ratio by closed second clutch (K2) and respectively closed the 4th, the 7th and the 8th switching member (D, H, G) produce and therefore by second, third and the 7th gear stage (β, γ, η) and second output gear stage (μ) generation.
9. according to the dual-clutch transmission of one of aforesaid right requirement, it is characterized in that the speed ratio of the velocity ratio of the first six forward gear (G1 to G6) successively decreases at interval at least.
10. the dual-clutch transmission that one of requires according to aforesaid right, it is characterized in that first switching member (A) is positioned at the other distolateral or be positioned between the second gear plane (ZRE2) and the 3rd gear plane (ZRE3) on the first gear plane (ZRE1) of described another transmission shaft (W3).
11. the dual-clutch transmission according to aforesaid right one of requires is characterized in that, described switching member (A, B, C, D, E, F, G, H, I) is configured to the shape locking element that can not power failure-free ground switches.
12. the dual-clutch transmission according to one of aforesaid right requirement, it is characterized in that two, four, six or eight switching members (A, B, C, D, E, F, G, H, I) are combined into the switching member unit (B-C, D-E, G-F, H-I) of one, two, three or four two-sided action.
13. the dual-clutch transmission according to one of aforesaid right requirement is characterized in that,
The switching member unit (B-C) of a two-sided action is set between the first gear plane (ZRE1) and the second gear plane (ZRE2) in the first jack shaft circuit (VWS1), and/or
The switching member unit (D-E) of a two-sided action is set between the second gear plane (ZRE2) and the 3rd gear plane (ZRE3) in the first jack shaft circuit (VWS1), and/or
The switching member unit (H-I) of a two-sided action is set between the first gear plane (ZRE1) and the second gear plane (ZRE2) in the second jack shaft circuit (VWS2), and/or
The switching member unit (G-F) of a two-sided action is set between the 3rd gear plane (ZRE3) and the 4th gear plane (ZRE4) in the second jack shaft circuit (VWS2).
14. the dual-clutch transmission according to one of aforesaid right requirement, 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 distolateral of the other side, distolateral or the 4th gear plane (ZRE4) of two clutches (K1, K2).
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010050238.3 | 2010-10-27 | ||
| DE102010050238 | 2010-10-27 | ||
| DE102010053130.8A DE102010053130B4 (en) | 2010-10-27 | 2010-11-29 | Dual clutch transmission for front-transverse applications |
| DE102010053130.8 | 2010-11-29 | ||
| PCT/DE2011/000168 WO2012055382A1 (en) | 2010-10-27 | 2011-02-22 | Dual-clutch gearbox for front-transverse applications |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103189668A true CN103189668A (en) | 2013-07-03 |
| CN103189668B CN103189668B (en) | 2016-08-03 |
Family
ID=45935680
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180051753.XA Expired - Fee Related CN103189668B (en) | 2010-10-27 | 2011-02-22 | Dual-clutch transmission for front cross application |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN103189668B (en) |
| DE (1) | DE102010053130B4 (en) |
| WO (1) | WO2012055382A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107781361A (en) * | 2016-08-25 | 2018-03-09 | 福特全球技术公司 | Dual-clutch transmission for motor vehicles |
Families Citing this family (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010055645B4 (en) | 2010-12-22 | 2022-07-14 | Volkswagen Ag | dual clutch winding transmission |
| KR101293298B1 (en) * | 2011-07-08 | 2013-08-09 | 현대 파워텍 주식회사 | Automatic manual transmission |
| DE102011088383B4 (en) * | 2011-12-13 | 2021-02-18 | Zf Friedrichshafen Ag | Automotive transmissions |
| DE102011088381B4 (en) * | 2011-12-13 | 2020-10-29 | Zf Friedrichshafen Ag | Automotive transmissions |
| DE102012022777A1 (en) * | 2012-11-22 | 2014-05-22 | Daimler Ag | Dual clutch transmission i.e. jackshaft transmission, for powertrain of motor car, has idle gear arranged coaxial to sleeve shaft, and switch unit connecting another idle gear with sleeve shaft in torque-proof manner |
| DE102012022776A1 (en) * | 2012-11-22 | 2014-05-22 | Daimler Ag | Dual clutch transmission for drive train of motor vehicle, has switching units that are arranged for operative connection to shafts, and output gear planes and switching units that are connected to circuit of forward gears |
| DE102013216387A1 (en) | 2013-08-19 | 2015-02-19 | Volkswagen Aktiengesellschaft | Double clutch |
| DE102013216384A1 (en) | 2013-08-19 | 2015-02-19 | Volkswagen Aktiengesellschaft | Double clutch |
| DE102013216388A1 (en) | 2013-08-19 | 2015-02-19 | Volkswagen Aktiengesellschaft | Double clutch |
| DE102013216385A1 (en) | 2013-08-19 | 2015-02-19 | Volkswagen Aktiengesellschaft | Double clutch transmission for a motor vehicle |
| DE102013019132A1 (en) * | 2013-11-15 | 2015-05-21 | Daimler Ag | Double clutch |
| DE102013019118B4 (en) * | 2013-11-15 | 2018-05-17 | Daimler Ag | Double clutch |
| DE102014206149A1 (en) | 2014-04-01 | 2015-10-01 | Volkswagen Aktiengesellschaft | Method for switching a motor vehicle transmission |
| DE102015213923A1 (en) | 2015-07-23 | 2017-01-26 | Volkswagen Aktiengesellschaft | Double clutch |
| DE102016202915A1 (en) | 2016-02-25 | 2017-08-31 | Ford Global Technologies, Llc | Dual-clutch transmission for motor vehicles |
| DE102016202914A1 (en) | 2016-02-25 | 2017-08-31 | Ford Global Technologies, Llc | Dual-clutch transmission for motor vehicles |
| CN107225958B (en) * | 2017-05-22 | 2019-05-24 | 安徽纽恩卡自控科技有限公司 | One kind nine keeps off mixed power automobile driving system |
| CN113685498B (en) * | 2020-05-18 | 2024-06-14 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685509B (en) * | 2020-05-18 | 2024-03-29 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN111873789B (en) * | 2020-07-28 | 2022-07-08 | 重庆长安汽车股份有限公司 | Dual-clutch transmission, fuel power system and hybrid power system |
| EP4101671A1 (en) * | 2021-06-10 | 2022-12-14 | Volvo Truck Corporation | A transmission, a powertrain, and a vehicle |
| CN114321294A (en) * | 2021-12-31 | 2022-04-12 | 中国第一汽车股份有限公司 | Multi-gear double-clutch transmission |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101251169A (en) * | 2007-02-22 | 2008-08-27 | 通用汽车环球科技运作公司 | Multi-speed transmission with countershaft gearing |
| CN101424328A (en) * | 2008-12-19 | 2009-05-06 | 重庆青山工业有限责任公司 | Double clutch automatic speed transmission |
| CN101451596A (en) * | 2007-12-04 | 2009-06-10 | 艾晓林 | Bimodule type electromechanical non-stage transmission |
| CN101571181A (en) * | 2009-06-15 | 2009-11-04 | 上海汽车集团股份有限公司 | Double clutch gearbox |
| CN101802450A (en) * | 2007-10-15 | 2010-08-11 | 腓特烈斯港齿轮工厂股份公司 | Dual clutch transmission |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005045005B4 (en) * | 2005-09-21 | 2015-02-05 | Daimler Ag | Double clutch |
| US7490526B2 (en) * | 2006-05-22 | 2009-02-17 | Magna Powertrain Usa, Inc. | Dual clutch powershift transmission with transfer shaft |
| JP5312242B2 (en) | 2008-12-16 | 2013-10-09 | 本田技研工業株式会社 | transmission |
| CA2753175C (en) | 2009-03-24 | 2013-05-14 | Honda Motor Co., Ltd. | Power transmitting device |
-
2010
- 2010-11-29 DE DE102010053130.8A patent/DE102010053130B4/en not_active Expired - Fee Related
-
2011
- 2011-02-22 CN CN201180051753.XA patent/CN103189668B/en not_active Expired - Fee Related
- 2011-02-22 WO PCT/DE2011/000168 patent/WO2012055382A1/en active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101251169A (en) * | 2007-02-22 | 2008-08-27 | 通用汽车环球科技运作公司 | Multi-speed transmission with countershaft gearing |
| CN101802450A (en) * | 2007-10-15 | 2010-08-11 | 腓特烈斯港齿轮工厂股份公司 | Dual clutch transmission |
| CN101451596A (en) * | 2007-12-04 | 2009-06-10 | 艾晓林 | Bimodule type electromechanical non-stage transmission |
| CN101424328A (en) * | 2008-12-19 | 2009-05-06 | 重庆青山工业有限责任公司 | Double clutch automatic speed transmission |
| CN101571181A (en) * | 2009-06-15 | 2009-11-04 | 上海汽车集团股份有限公司 | Double clutch gearbox |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107781361A (en) * | 2016-08-25 | 2018-03-09 | 福特全球技术公司 | Dual-clutch transmission for motor vehicles |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103189668B (en) | 2016-08-03 |
| DE102010053130B4 (en) | 2019-12-19 |
| WO2012055382A1 (en) | 2012-05-03 |
| WO2012055382A8 (en) | 2013-04-18 |
| DE102010053130A1 (en) | 2012-05-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103189668A (en) | Dual-clutch gearbox for front-transverse applications | |
| CN102498318B (en) | Multi-ratio transmission | |
| CN102089550B (en) | Multi-stage gearbox | |
| US9115789B2 (en) | Double clutch transmission | |
| CN102472371B (en) | Multi-ratio transmission | |
| CN101802450B (en) | Dual clutch transmission | |
| US8393238B2 (en) | Dual clutch transmission | |
| CN101802446B (en) | Dual clutch transmission | |
| CN101275626B (en) | Multi-speed dual clutch transmission | |
| CN102414476B (en) | Power-shift double-clutch transmission | |
| US20150292606A1 (en) | Dual clutch gearbox with countershaft design | |
| CN101865259B (en) | Double clutch transmission | |
| CN101809320B (en) | Dual clutch transmission | |
| CN101865250B (en) | Double clutch transmission | |
| CN101809321B (en) | Dual clutch transmission | |
| US20100206105A1 (en) | Dual clutch transmission | |
| US20100275707A1 (en) | Dual clutch transmission | |
| CN101865253B (en) | Double clutch transmission | |
| CN105814337A (en) | Combined anti-friction and plain bearing mounting for gearbox shaft | |
| CN101825161A (en) | The multi-speed transmission that has stacked planetary gear set | |
| CN101809324A (en) | Dual-clutch transmission | |
| CN202349120U (en) | Power transmission mechanism of automobile transmission | |
| CN102425647B (en) | Power transmission mechanism for double-clutch automatic transmission | |
| CN101865256B (en) | Double clutch transmission | |
| CN101737462B (en) | Double-clutch transmission mechanism |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160803 |