CN103758945A - Dual-clutch automatic transmission - Google Patents

Dual-clutch automatic transmission Download PDF

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Publication number
CN103758945A
CN103758945A CN201310728267.8A CN201310728267A CN103758945A CN 103758945 A CN103758945 A CN 103758945A CN 201310728267 A CN201310728267 A CN 201310728267A CN 103758945 A CN103758945 A CN 103758945A
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CN
China
Prior art keywords
gear
input shaft
driving
grades
driven
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.)
Pending
Application number
CN201310728267.8A
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Chinese (zh)
Inventor
傅灵玲
刘江海
张新桂
罗大国
陈勇
吴成明
冯擎峰
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhejiang Geely Holding Group Co Ltd
Zhejiang Geely Automobile Research Institute Co Ltd
Original Assignee
Zhejiang Geely Holding Group Co Ltd
Zhejiang Geely Automobile Research Institute Co Ltd
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Publication date
Application filed by Zhejiang Geely Holding Group Co Ltd, Zhejiang Geely Automobile Research Institute Co Ltd filed Critical Zhejiang Geely Holding Group Co Ltd
Priority to CN201310728267.8A priority Critical patent/CN103758945A/en
Publication of CN103758945A publication Critical patent/CN103758945A/en
Pending legal-status Critical Current

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    • 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
    • F16H3/12Toothed 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 means for synchronisation not incorporated in the clutches
    • 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
    • F16H57/00General details of gearing
    • F16H57/02Gearboxes; Mounting gearing therein
    • F16H57/023Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H63/00Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30Constructional features of the final output mechanisms
    • F16H63/34Locking or disabling mechanisms
    • F16H63/3416Parking lock mechanisms or brakes in the transmission
    • F16H63/3425Parking lock mechanisms or brakes in the transmission characterised by pawls or wheels
    • 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
    • F16H57/00General details of gearing
    • F16H57/02Gearboxes; Mounting gearing therein
    • F16H2057/02086Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
    • 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
    • F16H2200/0056Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds

Abstract

The invention provides a dual-clutch automatic transmission. The dual-clutch automatic transmission comprises seven forward gears and a reverse gear, wherein a driving gear of a fifth gear, a driving gear of a first gear, a driving gear of a third gear and are respectively independently and fixedly arranged on a first input shaft and a driving gear of a second gear and a driving gear of a fourth gear are respectively independently and fixedly arranged on a second input shaft. Ring gears which correspondingly are engaged with the driving gears are sleevingly arranged on the first input shaft and the second input shaft, the driving gear of the fifth gear is simultaneously used as the driving gear of a seventh gear and the driving gear of the second gear is simultaneously used as the driving gear of the reverse gear so that a reverse rod is not needed. The driving gear of the fourth gear is simultaneously used as the driving gear of a sixth gear. The dual-clutch automatic transmission has the advantages that the reverse rod is not needed; the radial direction size within the dual-clutch automatic transmission is reduced so that the assembly of the dual-clutch automatic transmission is easier to assemble; automobile lightening is easier to achieve. Simultaneously, a double-tooth structure is adopted in the rear gear upon driving, thereby being beneficial to allocation and adjustment to the speed ratio of the second gear and the reverse gear and the requirement of thermal capacity of clutch upon selecting reverse gear can be reduced.

Description

A kind of double-clutch automatic gearbox
Technical field
The present invention relates to automotive transmission field, particularly relate to a kind of double-clutch automatic gearbox.
Background technique
The development of current automotive industry, energy-saving and emission-reduction become the main direction of design, and car load is got over strictly for the designing requirement of speed changer, therefore has high efficiency, double-clutch automatic gearbox high-comfort, high ratio coverage becomes development trend gradually.Power train structure in double-clutch automatic gearbox and the layout of parking ratchet wheel are the important component parts of whole speed changer, also be the most important condition of follow-up mechanical hardware design and Software for Design, therefore double-clutch speed changer requires also more and more higher to the layout of transmission and parking ratchet wheel.
For transmission system aspect, in order to obtain better power character and Economy, wider ratio coverage, more rational Speed Ratio Distribution has been an important developing direction of speed changer.Although many double-clutch automatic gearbox shafting designs have been obtained very large progress, but yet there are some because consider the defect not causing comprehensively, make its Shortcomings aspect internal space layout rationality, structural compactness, transmission performance and working stability.
Summary of the invention
An object of the present invention is to provide a kind of compact structure and use wider double-clutch automatic gearbox.
Further object of the present invention is to make that in above-mentioned speed changer, particularly the space layout of synchronizer is more reasonable.
Another further object of the present invention is to reduce above-mentioned speed changer warp-wise length and inner body quantity, optimizes assembly process.
Another further object of the present invention is to make above-mentioned speed changer operation safer stable.
Especially, the invention provides a kind of double-clutch automatic gearbox, comprising:
The first input shaft in axial direction extending, it has the first input shaft first end and the first input shaft the second end contrary with described the first input shaft first end;
First clutch, it is connected to described the first input shaft at described the first input shaft first end place;
The second input shaft, it has the second input shaft first end and the second input shaft the second end contrary with described the second input shaft first end;
Second clutch, it is connected to described the second input shaft at described the second input shaft first end place;
Described the second input shaft is hollow shaft, and it is sleeved on described the first input shaft;
Independent five grades of driving gears that arrange, one grade of driving gear and third speed drive gear, it is fixedly attached to respectively described the first input shaft; Wherein, described five grades of driving gears are simultaneously as seven grades of driving gears;
Independent second gear driving gear and the fourth gear driving gear arranging, it is fixedly attached to respectively described the second input shaft; Wherein, described second gear driving gear is simultaneously as reverse driving gear, to omit reverse gear shaft; Described fourth gear driving gear is simultaneously as six grades of driving gears;
The first output shaft and the second output shaft that along described axial direction, extend, on it, empty set is provided with the driven gear of engagement corresponding to each driving gear respectively.
Further, described five grades of driving gears, described one grade of driving gear and described third speed drive gear on described the first input shaft along setting gradually to the direction of described the first input shaft first end from described the first input shaft the second end.
Further, described second gear driving gear and described fourth gear driving gear on described the second input shaft along setting gradually to the direction of described the second input shaft first end from described the second input shaft the second end.
Further, at described the second output shaft overhead cover, be provided with seven grades of driven gears, third gear driven gear, second gear driven gear and six grades of driven gears of engagement corresponding to described five grades of driving gears, third speed drive gear, second gear driving gear and fourth gear driving gear respectively, and be formed as the reverse idler gear of conjuncted duplicate gear between described third gear driven gear and described second gear driven gear and with described second gear driven gear;
At described the first output shaft overhead cover, be provided with respectively and five grades of driven gears, first speed driven gear, reverse gear driven gear and the fourth gear driven gear of described five grades of driving gears, one grade of corresponding engagement of driving gear, reverse idler gear and fourth gear driving gear.
Further, on described the first output shaft between described first speed driven gear and five grades of driven gears, be fixed with a Five-gear synchronizer; On described the first output shaft between described fourth gear driven gear and reverse gear driven gear, be fixed with four reversing-gear synchronizers;
On described the second output shaft between described second gear driven gear and six grades of driven gears, be fixed with two or six grades of synchronizers; On described the second output shaft between described third gear driven gear and seven grades of driven gears, be fixed with pseudo-ginseng shelves synchronizer.
Further, described four reversing-gear synchronizers and described two or six grades of synchronizers are staggeredly arranged along described axial direction.
Further, described four reversing-gear synchronizers with described second gear driving gear substantially aliging in the radial direction perpendicular to described axial direction.
Further, described pseudo-ginseng shelves synchronizer and a described Five-gear synchronizer are in axial direction staggeredly arranged.
Further, described pseudo-ginseng shelves synchronizer with described one grade of driving gear substantially aliging in the radial direction perpendicular to described axial direction.
Further, also comprise parking ratchet wheel and the differential mechanism with differential casing; Wherein, described parking ratchet wheel is fixedly installed on described differential casing.
In double-clutch automatic gearbox of the present invention, cancel the use of reverse gear shaft, effectively reduced the radial dimension in speed changer, made assembling simpler, be also conducive to the realization of automotive light weight technology.Meanwhile, reverse idler gear and second gear driven gear can adopt duplex-gear structural type, and this is more conducive to distribution and the adjustment of second gear and reverse gear ratio, the requirement to clutch starting thermal capacity while also having reduced reverse gear.
The shared relation of the different gears of double-clutch automatic gearbox of the present invention by particular design to driving gear, this two aspect of the reasonable Speed Ratio Distribution to speed changer and structural compactness is optimized.
Double-clutch automatic gearbox of the present invention is in the middle of bottom gear is arranged in, and top gear is arranged in to the both sides of bottom gear.Like this, can slow down on the one hand centrifugal force that top gear High Rotation Speed the produces adverse effect to input shaft, increase the service life; On the other hand, can also make output shaft and the stressed balance more of input shaft for carrier gear, increase integrally-built stability, thereby can offset the negative effect of the total axial length of speed changer to stability, to increase the design capacity to speed changer axial length.In addition, such layout can allow synchronizer to be staggeredly arranged, thereby can further reduce total axial length of speed changer.
In double-clutch automatic gearbox of the present invention, four reversing-gear synchronizers with can be in the basic alignment of radial direction as the second gear driving gear of bottom gear, so that four reversing-gear synchronizers and two or six grades of synchronizers are staggered mutually in radial direction, thereby the space interference problem when solving four reversing-gear synchronizers and gearwheel or being arranged together with two or six grades of synchronizers, thereby the space layout of having optimized speed changer inside, adds strong stability.Similarly, pseudo-ginseng shelves synchronizer with can be in the basic alignment of radial direction as one grade of driving gear of bottom gear, so that pseudo-ginseng shelves synchronizer and a Five-gear synchronizer are staggered mutually in radial direction, thereby the space interference problem when solving pseudo-ginseng shelves synchronizer and gearwheel or being arranged together with a Five-gear synchronizer, thereby the space layout of having optimized speed changer inside, adds strong stability.
In double-clutch automatic gearbox of the present invention, one grade and reverse gear are divided Clutch Control, be more conducive to distribution and the adjustment of one grade and reverse gear ratio, the requirement to clutch starting thermal capacity while also having reduced particularly a grade.
In double-clutch automatic gearbox of the present invention, parking ratchet wheel can be arranged on differential mechanism shell, can save the axial length of speed changer, is convenient to the layout of car load lift-launch and speed changer parking drag link mechanism; And parking ratchet wheel is arranged near the mode of differential mechanism gear ring relatively, and the present invention also can further save the axial length of differential mechanism, be equally also convenient to the layout of car load lift-launch and speed changer parking drag link mechanism.
According to the detailed description to the specific embodiment of the invention by reference to the accompanying drawings below, those skilled in the art will understand above-mentioned and other objects, advantage and feature of the present invention more.
Accompanying drawing explanation
Hereinafter in exemplary and nonrestrictive mode, describe specific embodiments more of the present invention in detail with reference to the accompanying drawings.In accompanying drawing, identical reference character has indicated same or similar parts or part.It should be appreciated by those skilled in the art that these accompanying drawings may not draw in proportion.In accompanying drawing:
Fig. 1 is that speed changer structure is arranged schematic diagram according to an embodiment of the invention.
Embodiment
Present inventor finds, in existing double-clutch automatic gearbox structure, the layout of high low gear is unreasonable, can make double-clutch automatic gearbox poor stability, and stability also can be along with double-clutch automatic gearbox increases and reduces at total axial length, thereby indirectly limited the development of double-clutch automatic gearbox at total axial length, finally also can limit the utilization of double-clutch automatic gearbox in multi-vehicle-type more.In addition, for parking ratchet wheel, in existing double-clutch automatic gearbox structure, be normally arranged in output shaft end, but can make output shaft distribution of force inequality so on the one hand, reduce stability; In addition, parking ratchet wheel is positioned at the axial distance that also can increase speed changer on output shaft, and making arrangement and car load carry degree of difficulty increases to some extent.
Fig. 1 is that speed changer structure is arranged schematic diagram according to an embodiment of the invention.As shown in Figure 1, the invention provides a kind of double-clutch automatic gearbox, speed changer can comprise housing (not shown), and housing seals the gear apparatus of speed changer at least in part.This gear apparatus can comprise various axles, intermeshing co-planar gear set, double clutch assembly and the synchronizer can selectivity engaging, as described herein.
Axle of the present invention can comprise the first input shaft 1 and the second input shaft 2 coaxial and that along the extension of axial direction A shown in Fig. 1, arrange.
The first input shaft 1 can have the first input shaft first end 1 ' and the first input shaft the second end 1 ' contrary with described the first input shaft first end 1 ' '.The second input shaft 2 can have the second input shaft first end 2 ' and the second input shaft the second end 2 ' contrary with described the second input shaft first end 2 ' '.The two ends of the first input shaft 1 and the second input shaft 2 are normally arranged on case of transmission by bearing.
The second input shaft 2 is hollow shaft, and it is sleeved on described the first input shaft 1, makes can rotate relatively freely between the first input shaft 1 and the second input shaft 2.
Double clutch assembly of the present invention can comprise first clutch K1 and the second clutch K2 of nested, concentric.First clutch K1 locates to be connected to the first input shaft 1 at the first input shaft first end 1 ', to jointly rotate with the first input shaft 1.Second clutch K2 locates to be connected to the second input shaft 2 at the second input shaft first end 2 ', can jointly rotate with the second input shaft 2 equally.Therefore, in double-clutch automatic gearbox of the present invention, one grade and reverse gear are divided Clutch Control, be equally more conducive to distribution and the adjustment of one grade and reverse gear ratio, the requirement to clutch starting thermal capacity while also having reduced particularly a grade.
Axle of the present invention can also comprise the first output shaft 3 and the second output shaft 4 parallel and that separation arranges, and same, the first output shaft 3 and the second output shaft 4 are to extend along axial direction A shown in Fig. 1.
Intermeshing co-planar gear set of the present invention can comprise seven groups of forward gears gear trains and a reverse gearset, is to be separately positioned on above-mentioned the first input shaft 1, the second input shaft 2, the first output shaft 3 and the second output shaft 4.
Particularly, on the first input shaft 1 along from the first input shaft the second end 1 ' ' to the direction of the first input shaft first end 1 ', be fixedly installed successively five grades of driving gears 15, one grade of driving gear 11 and third speed drive gear 13.And on the second input shaft 2 along from the second input shaft the second end 2 ' ' to the direction of the second input shaft first end 2 ', be fixedly installed successively second gear driving gear 22 and fourth gear driving gear 24.And in the present invention, have shared driving gear mutually, wherein, five grades of driving gears 15 are simultaneously as seven grades of driving gears, and second gear driving gear 22 is simultaneously as reverse driving gear, and fourth gear driving gear 24 is simultaneously as six grades of driving gears.
Simultaneously, at the second output shaft 4 overhead covers, be provided with seven grades of driven gears 47, third gear driven gear 43, second gear driven gear 42 and six grades of driven gears 46 of engagement corresponding to five grades of driving gears 15, third speed drive gear 13, second gear driving gear 22 and fourth gear driving gear 24 respectively, and be formed as the reverse idler gear 42a of conjuncted duplicate gear between third gear driven gear 43 and second gear driven gear 42 and with second gear driven gear 42.At the first output shaft 3 overhead covers, be provided with respectively and five grades of driven gears 35, first speed driven gear 31, reverse gear driven gear 32 and the fourth gear driven gear 34 of five grades of driving gears 15, one grade of driving gear 11, reverse idler gear 42a and the corresponding engagement of fourth gear driving gear 24.Therefore, in double-clutch automatic gearbox of the present invention, cancel the use of reverse gear shaft, also reduced the use of related components, effectively reduced the radial dimension in speed changer, made assembling simpler, be also conducive to the realization of automotive light weight technology.Meanwhile, reverse gear adopts duplex-gear, is more conducive to distribution and the adjustment of second gear and reverse gear ratio, the requirement to clutch starting thermal capacity while also having reduced reverse gear.Meanwhile, the shared relation of the different gears of double-clutch automatic gearbox of the present invention by particular design to driving gear, this two aspect of the reasonable Speed Ratio Distribution to speed changer and structural compactness is optimized.
Of the present invention each between driving gear and driven gear being normal engagement.Particularly, wherein five grades of driving gears 15, with seven grades of driven gears 47 for often to engage, form seven grades of gear trains; Five grades of driving gears 15 for often to engage, form five grades of gear trains with five grades of driven gears 35; One grade of driving gear 11 for often to engage, forms one grade of gear train with first speed driven gear 31; Third speed drive gear 13 for often to engage, forms three-range transmission group with third gear driven gear 43; Second gear driving gear 22 for often to engage, forms intermediate gear group with second gear driven gear 42; Fourth gear driving gear 24 for often to engage, forms fourth gear group with fourth gear driven gear 34; Fourth gear driving gear 24 for often to engage, forms six step tooth wheels with six grades of driven gears 46.In addition, the reverse idler gear 42a that forms conjuncted duplicate gear with second gear driven gear 42 with reverse gear driven gear 32 for often to engage, in this example, above second gear driving gear 22 is used as to reverse driving gear simultaneously, power transmits to reverse gear driven gear 32 by second gear driving gear 22, second gear driven gear 42, reverse idler gear 42a successively again, realizes reverse gear function.
No matter it should be noted that, be that the gear on the first input shaft 1 or the second input shaft 2 is not necessarily arranged according to the order of placement shown in Fig. 1 in the present invention, can be also other arrangement.But, consider in high speed gear's rotary course particularly and can produce very large centrifugal force, if now high speed gear is arranged on the inclined to one side intermediate portion of input shaft, may more easily cause the bending or phenomenon such as fracture of input shaft.So be arranged on input shaft outermost end as high speed gear's group, near bearing is installed, and can extend like this working life of input shaft, further make speed changer running safer stable.
In the present invention, be substantially will to be arranged in the neutral position of speed changer as one grade of bottom gear, second gear, third gear and reverse gear, and other top gears be arranged in to the both sides of above-mentioned bottom gear.Such set-up mode can make for the output shaft of carrier gear and the stressed balance more of input shaft, increase integrally-built stability, thereby can offset the negative effect of the total axial length of speed changer to stability, to increase the design capacity to speed changer axial length, make speed changer go for more multi-vehicle-type.In addition, such layout can allow synchronizer to be staggeredly arranged, thereby can further reduce total axial length of speed changer.
Synchronizer of the present invention can comprise four, is separately positioned between the driven gear of adjacent two gears.Particularly, on the first output shaft 3 between first speed driven gear 31 and five grades of driven gears 35, be fixed with a Five-gear synchronizer 5, optionally first grade of moment of torsion and the 5th grade of moment of torsion passed to the first output shaft 3.On the first output shaft 3 between fourth gear driven gear 34 and reverse gear driven gear 32, be fixed with four reversing-gear synchronizers 6, optionally fourth speed moment of torsion and reverse gear moment of torsion passed to the first output shaft 3.On the second output shaft 4 between second gear driven gear 42 and six grades of driven gears 46, be fixed with two or six grades of synchronizers 7, optionally second gear moment of torsion and the 6th grade of moment of torsion passed to the second output shaft 4.On the second output shaft 4 between third gear driven gear 43 and seven grades of driven gears 47, be fixed with pseudo-ginseng shelves synchronizer 8, optionally third gear moment of torsion and the 7th grade of moment of torsion passed to the second output shaft 4.
In double-clutch automatic gearbox of the present invention, be by 6 and 26 grades of synchronizers 7 of four reversing-gear synchronizers in axial direction A be staggeredly arranged; Further, can be using four reversing-gear synchronizers 6 and the basic alignment in the radial direction at direction A perpendicular to axial direction as the second gear driving gear 22 of bottom gear.The arrangement so mutually staggering between four 6 and 26 grades of reversing-gear synchronizers synchronizers 7, space interference problem when can solve four reversing-gear synchronizers 6 with gearwheel or being arranged together with two or six grades of synchronizers 7, thereby the space layout of having optimized speed changer inside, adds strong stability.
Similarly, can by pseudo-ginseng shelves synchronizer 8 and a Five-gear synchronizer 5 in axial direction A be staggeredly arranged; Further, can be using pseudo-ginseng shelves synchronizer 8 and the basic alignment in the radial direction at direction A perpendicular to axial direction as one grade of driving gear 11 of bottom gear.The arrangement so mutually staggering between pseudo-ginseng shelves synchronizer 8 and a Five-gear synchronizer 5, space interference problem when can solve pseudo-ginseng shelves synchronizer 8 with gearwheel or being arranged together with a Five-gear synchronizer 5, thereby the space layout of having optimized speed changer inside, adds strong stability.It should be noted that, from the floor map shown in Fig. 1 of the present invention, may not be to reflect very intuitively for example spatial relation between 6 and 26 grades of synchronizers 7 of reversing-gear synchronizer and between pseudo-ginseng shelves synchronizer 8 and a Five-gear synchronizer 5.But those skilled in the art are to be understood that, in practice process, particularly from cross section in the radial direction, between input shaft in clutch and output shaft, be to be substantially triangularly arranged, therefore the problem that, 6 and 26 grades of synchronizers 7 of reversing-gear synchronizer and pseudo-ginseng shelves synchronizer 8 and a Five-gear synchronizer 5 just may Existential Space in topology layout be interfered.
Should be appreciated that a Five-gear synchronizer 5 can be a bilateral synchronous device, can optionally first grade of moment of torsion is passed to the first output shaft 3 or the 5th grade of moment of torsion is passed to the first output shaft 3.Hereinafter, in order to facilitate the follow-up description to speed changer power transmission line of the present invention, as shown in fig. 1, when a Five-gear synchronizer 5 is when being passed to the first output shaft 3 by first grade of moment of torsion, be referred to as one grade of synchronizer b, and when the 5th grade of moment of torsion is passed to the first output shaft 3, be referred to as Five-gear synchronizer a.In like manner, hereinafter, four reversing-gear synchronizers 6 can be called as fourth gear synchronizer d and reversing-gear synchronizer c, and two or six grades of synchronizers 7 can be called as second gear synchronizer f and six grades of synchronizer e, and pseudo-ginseng shelves synchronizer 8 can be called as third gear synchronizer h and seven grades of synchronizer g.
The first output shaft 3 ends of the present invention can also be fixedly connected with the first output gear 38, the first output gear 38 is meshed with the deceleration driven gear 10 on differential mechanism 9, be used for exporting the moment of torsion of the first output shaft 3, wherein, differential mechanism 9 has differential casing 901 parts such as grade.Equally, in the second output shaft 4 ends, also can be fixedly connected with the second output gear 48, the second output gear 48 is meshed with deceleration driven gear 10 for exporting the moment of torsion of the second output shaft 4, and output torque mode is similar to most of double clutch construction herein, repeats no more.
On differential casing 901, can also be fixedly installed parking ratchet wheel 11, belong to a part for halting mechanism (not completely shown), play parking effect, set-up mode can be saved the axial length of speed changer like this, is convenient to the layout of car load lift-launch and speed changer parking drag link mechanism.And parking ratchet wheel 11 is arranged near the mode of differential mechanism gear ring relatively, and the present invention also can further save the axial length of differential mechanism, be equally also convenient to the layout of car load lift-launch and speed changer parking drag link mechanism.
The power transmission line of seven forward gearss of the present invention and a reverse gear is as follows:
In the time of one grade, first clutch K1 closure, the moment of torsion of motor is passed to the first input shaft 1 by first clutch K1; One grade of driving gear 11 on the first input shaft 1 is passed to first speed driven gear 31; First speed driven gear 31 engages with one grade of synchronizer b, transfers a torque to the first output shaft 3, then is passed to deceleration driven gear 10 and final transmission is gone out through the first output gear 38.
When vehicle enters one grade, second clutch K2 is in off state, not transferring power, when vehicle accelerates to the shift point of second gear, self-clanging gear-shift can change to second gear in advance by gear, is about to second gear synchronizer f and engages with second gear driven gear 42, then first clutch K1 disconnects, second clutch K2 closure, gearshift procedure finishes, and vehicle enters second gear.
During second gear, second clutch K2 closure, the moment of torsion of motor is passed to the second input shaft 2 by second clutch K2; Second gear driving gear 22 on the second input shaft 2 is passed to second gear driven gear 42; Second gear driven gear 42 engages with second gear synchronizer f, transfers a torque to the second output shaft 4, then is passed to deceleration driven gear 9 and final transmission is gone out through the second output gear 48.
When vehicle enters second gear, the electrical control unit of automatic transmission in general vehicle can judge according to relevant sensor signals the state of the current operation of vehicle, so judge vehicle be about to hang into gear, as vehicle accelerates, next gear is third gear, and as vehicle deceleration, next gear is one grade.And one grade and third gear are controlled by first clutch K1, because first clutch K1 is now in off state, not transferring power, therefore can change in advance the gear that is about to carry out work by self-clanging gear-shift.When vehicle reaches shift point, only the second clutch K2 working need to be disconnected, first clutch K1 is closed simultaneously, the transfer sequence of two clutches of working good, whole gearshift procedure completes.The handoff procedure of other forward gearss is also so, no longer repeats below.
During third gear, first clutch K1 closure, the moment of torsion of motor is passed to the first input shaft 1 by first clutch K1; Third speed drive gear 13 on the first input shaft 1 is passed to third gear driven gear 43; Third gear driven gear 43 engages with third gear synchronizer h, transfers a torque to the second output shaft 4, then is passed to deceleration driven gear 9 and final transmission is gone out through the second output gear 48.
During fourth gear, second clutch K2 closure, the moment of torsion of motor is passed to the second input shaft 2 by second clutch K2; Fourth gear driving gear 24 on the second input shaft 2 is passed to fourth gear driven gear 34; Fourth gear driven gear 34 engages with fourth gear synchronizer d, transfers a torque to the first output shaft 3, then is passed to deceleration driven gear 9 and final transmission is gone out through the first output gear 38.
In the time of five grades, first clutch K1 closure, the moment of torsion of motor is passed to the first input shaft 1 by first clutch K1; Five grades of driving gears 15 on the first input shaft 1 are passed to five grades of driven gears 35; Five grades of driven gears 35 engage with Five-gear synchronizer a, transfer a torque to the first output shaft 3, then are passed to deceleration driven gear 9 and final transmission is gone out through the first output gear 38.
In the time of six grades, second clutch K2 closure, the moment of torsion of motor is passed to the second input shaft 2 by second clutch K2; Fourth gear driving gear 24 on the second input shaft 2 is passed to six grades of driven gears 46; Six grades of driven gears 46 engage with six grades of synchronizer e, transfer a torque to the second output shaft 4, then are passed to deceleration driven gear 9 and final transmission is gone out through the second output gear 48.
In the time of seven grades, first clutch K1 closure, the moment of torsion of motor is passed to the first input shaft 1 by first clutch K1; Five grades of driving gears 15 on the first input shaft 1 are passed to seven grades of driven gears 47; Seven grades of driven gears 47 engage with seven grades of synchronizer g, transfer a torque to the second output shaft 4, then are passed to deceleration driven gear 9 and final transmission is gone out through the second output gear 48.
During reverse gear, second clutch K2 closure, the moment of torsion of motor is passed to the second input shaft 2 by second clutch K2; Then the second gear driving gear 22 on the second input shaft 2 is passed to second gear driven gear 42, second gear driven gear 42 drives the reverse idler gear 42 that therewith forms conjuncted duplicate gear to rotate simultaneously, by reverse idler gear 42, drive to reverse gear driven gear 32 again, reverse gear driven gear 32 engages with reversing-gear synchronizer c, transfer a torque to the first output shaft 3, then be passed to deceleration driven gear 9 and final transmission is gone out through the first output gear 38.
So far, those skilled in the art will recognize that, although detailed, illustrate and described multiple exemplary embodiment of the present invention herein, but, without departing from the spirit and scope of the present invention, still can directly determine or derive many other modification or the modification that meet the principle of the invention according to content disclosed by the invention.Therefore, scope of the present invention should be understood and regard as and cover all these other modification or modifications.

Claims (10)

1. a double-clutch automatic gearbox, comprising:
The first input shaft (1) that in axial direction (A) extends, it has the first input shaft first end (1 ') and the first input shaft the second end contrary with described the first input shaft first end (1 ' ');
First clutch (K1), it locates to be connected to described the first input shaft (1) at described the first input shaft first end (1 ');
The second input shaft (2), it has the second input shaft first end (2 ') and the second input shaft the second end contrary with described the second input shaft first end (2 ' ');
Second clutch (K2), it locates to be connected to described the second input shaft (2) at described the second input shaft first end (2 ');
Described the second input shaft (2) is hollow shaft, and it is sleeved on described the first input shaft (1);
Independent five grades of driving gears (15), one grade of driving gear (11) and the third speed drive gear (13) arranging, it is fixedly attached to respectively described the first input shaft (1); Wherein, described five grades of driving gears (15) are simultaneously as seven grades of driving gears;
Independent second gear driving gear (22) and the fourth gear driving gear (24) arranging, it is fixedly attached to respectively described the second input shaft (2); Wherein, described second gear driving gear (22) is simultaneously as reverse driving gear, to omit reverse gear shaft; Described fourth gear driving gear (24) is simultaneously as six grades of driving gears;
The first output shaft (3) and the second output shaft (4) that along described axial direction (A), extend, on it, empty set is provided with the driven gear of engagement corresponding to each driving gear respectively.
2. double-clutch automatic gearbox according to claim 1, it is characterized in that, described five grades of driving gears (15), described one grade of driving gear (11) and described third speed drive gear (13) are upper along setting gradually to the direction of described the first input shaft first end (1 ') from described the first input shaft the second end (1 ' ') at described the first input shaft (1).
3. double-clutch automatic gearbox according to claim 1 and 2, it is characterized in that, described second gear driving gear (22) and described fourth gear driving gear (24) are upper along setting gradually to the direction of described the second input shaft first end (2 ') from described the second input shaft the second end (2 ' ') at described the second input shaft (2).
4. according to the double-clutch automatic gearbox described in any one in claim 1-3, it is characterized in that, at described the second output shaft (4) overhead cover, be provided with respectively and described five grades of driving gears (15), third speed drive gear (13), seven grades of driven gears (47) of the corresponding engagement of second gear driving gear (22) and fourth gear driving gear (24), third gear driven gear (43), second gear driven gear (42) and six grades of driven gears (46), and be positioned between described third gear driven gear (43) and described second gear driven gear (42) and be formed as the reverse idler gear (42a) of conjuncted duplicate gear with described second gear driven gear (42),
At described the first output shaft (3) overhead cover, be provided with five grades of driven gears (35), first speed driven gear (31), reverse gear driven gear (32) and the fourth gear driven gear (34) of engagement corresponding to described five grades of driving gears (15), one grade of driving gear (11), reverse idler gear (42a) and fourth gear driving gear (24) respectively.
5. double-clutch automatic gearbox according to claim 4, is characterized in that, on described the first output shaft (3) between described first speed driven gear (31) and five grades of driven gears (35), is fixed with a Five-gear synchronizer (5); On described the first output shaft (3) between described fourth gear driven gear (34) and reverse gear driven gear (32), be fixed with four reversing-gear synchronizers (6);
On described the second output shaft (4) between described second gear driven gear (42) and six grades of driven gears (46), be fixed with two or six grades of synchronizers (7); On described the second output shaft (4) between described third gear driven gear (43) and seven grades of driven gears (47), be fixed with pseudo-ginseng shelves synchronizer (8).
6. double-clutch automatic gearbox according to claim 5, is characterized in that, described four reversing-gear synchronizers (6) are staggeredly arranged along described axial direction (A) with described two or six grades of synchronizers (7).
7. according to the double-clutch automatic gearbox described in claim 5 or 6, it is characterized in that, described four reversing-gear synchronizers (6) with described second gear driving gear (22) substantially aliging in the radial direction perpendicular to described axial direction (A).
8. according to the double-clutch automatic gearbox described in any one in claim 5-7, it is characterized in that, described pseudo-ginseng shelves synchronizer (8) is in axial direction staggeredly arranged with a described Five-gear synchronizer (5).
9. according to the double-clutch automatic gearbox described in any one in claim 5-8, it is characterized in that, described pseudo-ginseng shelves synchronizer (8) with described one grade of driving gear (11) substantially aliging in the radial direction perpendicular to described axial direction (A).
10. according to the double-clutch automatic gearbox described in any one in claim 1-9, it is characterized in that, also comprise parking ratchet wheel (11) and there is the differential mechanism (9) of differential casing (901); Wherein, described parking ratchet wheel (11) is fixedly installed on described differential casing (901).
CN201310728267.8A 2013-12-25 2013-12-25 Dual-clutch automatic transmission Pending CN103758945A (en)

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CN106090141A (en) * 2015-04-29 2016-11-09 现代自动车株式会社 Many gear speed transmissions
CN110985613A (en) * 2019-12-31 2020-04-10 中国第一汽车股份有限公司 Multi-gear double-clutch transmission
CN113915298A (en) * 2020-07-08 2022-01-11 广州汽车集团股份有限公司 Vehicle automatic gearbox and vehicle

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CN101858421A (en) * 2009-04-03 2010-10-13 通用汽车环球科技运作公司 Seven speed dual clutch transmission
CN102966706A (en) * 2011-03-30 2013-03-13 浙江万里扬变速器股份有限公司 Three-shaft double-clutch speed changer

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US6250171B1 (en) * 1998-12-24 2001-06-26 Daimlerchrysler Ag Variable-ratio gear transmission having two partial transmissions each having a powershift clutch
US20060169078A1 (en) * 2003-01-14 2006-08-03 Kyowa Metal Works Co., Ltd. Twin-clutch transmission
US20050000307A1 (en) * 2003-02-08 2005-01-06 Gerhard Gumpoltsberger Six-gear or seven-gear dual-clutch transmission
CN1690471A (en) * 2004-04-23 2005-11-02 C.R.F.阿西安尼顾问公司 Double clutch transmissions for motor vehicle
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106090141A (en) * 2015-04-29 2016-11-09 现代自动车株式会社 Many gear speed transmissions
CN106090141B (en) * 2015-04-29 2019-12-27 现代自动车株式会社 Multi-gear transmission
CN110985613A (en) * 2019-12-31 2020-04-10 中国第一汽车股份有限公司 Multi-gear double-clutch transmission
CN110985613B (en) * 2019-12-31 2021-03-30 中国第一汽车股份有限公司 Multi-gear double-clutch transmission
CN113915298A (en) * 2020-07-08 2022-01-11 广州汽车集团股份有限公司 Vehicle automatic gearbox and vehicle

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