CN110230667A - The fast double-clutch automatic gearbox of one kind nine and vehicle - Google Patents
The fast double-clutch automatic gearbox of one kind nine and vehicle Download PDFInfo
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- CN110230667A CN110230667A CN201810183115.7A CN201810183115A CN110230667A CN 110230667 A CN110230667 A CN 110230667A CN 201810183115 A CN201810183115 A CN 201810183115A CN 110230667 A CN110230667 A CN 110230667A
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- gear
- shaft
- output gear
- input
- jackshaft
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Classifications
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- 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
- F16H3/085—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 more than one output shaft
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- 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
- F16H3/12—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 means for synchronisation not incorporated in the clutches
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- 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
- F16H2003/0822—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 arrangement of at least one reverse gear
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- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
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- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02091—Measures for reducing weight of gearbox
-
- 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
Abstract
The present invention relates to the fast double-clutch automatic gearbox of one kind nine and vehicles, wherein nine fast double-clutch automatic gearboxes include: input shaft, including the first input shaft, the second input shaft and input gear axle；Output shaft, including the first jackshaft and the second jackshaft.First jackshaft is equipped with the first output gear, the first bilateral synchronous device, the first output gear shaft, the 4th output gear and the first Unilateral synchronizer, and the first output gear shaft is equipped with third output gear and the second bilateral synchronous device；Second jackshaft is equipped with the 5th output gear, third bilateral synchronous device, the second output gear shaft, the 8th output gear and the second Unilateral synchronizer, and the second output gear shaft is equipped with the 7th output gear and the 4th bilateral synchronous device.The nine fast double-clutch automatic gearbox improves on the basis of existing seven fast double-clutch speed changers, while completing nine quick changes gear, can optimize the quantity of kernel output gear and synchronizer to greatest extent, compact-sized and occupied space is smaller.
Description
Technical field
The present invention relates to automotive transmission fields, and in particular to the fast double-clutch automatic gearbox of one kind nine and vehicle.
Background technique
Double-clutch automatic gearbox currently on the market, mainly based on 6 speed and 7 speed.With the liter of national emission standard
Grade, for the fuel oil performance for improving vehicle, all big enterprises possess the gearbox of more gears in exploitation and research.
The development of current auto industry, energy-saving and emission-reduction become the Main way of design, and vehicle wants the design of speed changer
It asks and more becomes stringent, therefore there is high efficiency, high-comfort, high ratio range double-clutch automatic gearbox to be increasingly becoming development and become
Gesture.The arragement construction of powertrain arrangement and parking ratchet wheel in double-clutch automatic gearbox is the important composition portion of entire speed changer
Point and subsequent mechanical hardware design and software design the most important condition, therefore double-clutch speed changer to transmission and parking ratchet wheel
Arragement construction require it is also higher and higher.
For in terms of transmission system, in order to obtain better dynamic property and economy, broader ratio coverage, more reasonably
Speed Ratio Distribution has been an important developing direction of speed changer.Although many double-clutch automatic gearbox shafting designs are
Obtain very big progress, but also there is also it is some because it is contemplated that comprehensively caused by defect so that its in structural compactness, pass
Shortcomings in terms of dynamic performance and job stability.
Summary of the invention
The object of the present invention is to provide the fast double-clutch automatic gearbox of one kind nine and vehicles, in the existing double clutch speed-changings of seven speed
It is improved on the basis of device, while completing nine quick changes gear, the quantity of gear and synchronizer can be optimized to greatest extent,
Compact-sized and occupied space is smaller.
In order to solve the above technical problems, the present invention provides one kind nine fast double-clutch automatic gearbox comprising:
Input shaft, including couple with engine by first clutch the first input shaft, by second clutch and send out
The second input shaft and input gear axle of motivation coupling, second input shaft are coaxially socketed on the outer of first input shaft
Side, the input gear axle are coaxially socketed on the outside of second input shaft；
Output shaft, the first jackshaft and the second jackshaft including being set to the input shaft two sides in parallel, in described first
Between axis and second jackshaft be respectively equipped with the master engaged with differential gear and subtract gear；
First jackshaft is successively arranged the first output gear, the first bilateral synchronous by the side towards engine
Device, the first output gear shaft, the 4th output gear and the first Unilateral synchronizer, first output gear shaft are coaxially socketed on institute
The outside of the first jackshaft is stated, third output gear is equipped with and acts on the third output gear and the 4th output gear
The second bilateral synchronous device between wheel；
Second jackshaft is successively arranged the 5th output gear, third bilateral synchronous by the side towards engine
Device, the second output gear shaft, the 8th output gear and the second Unilateral synchronizer, second output gear shaft are coaxially socketed on institute
The outside of the second jackshaft is stated, the 7th output gear is equipped with and acts on the 7th output gear and the 8th output gear
The 4th bilateral synchronous device between wheel；
The input shaft is equipped with input gear corresponding with each output gear of the output shaft, and is formed positioned at described defeated
The first gear for entering gear shaft is secondary, second gear is secondary, the 5th gear pair and the 6th gear pair, positioned at the of first input shaft
Four gear pairs and eighth gear pair, and third gear pair and the 7th gear pair positioned at second input shaft.
It optionally, further include the idler shaft that reverses gear, the idler shaft that reverses gear is in the input gear axle and described first
Between between axis, or be set between the input gear axle and second jackshaft, idler shaft and the input tooth of reversing gear
Wheel shaft cooperatively forms the 5th gear pair.
Optionally, it is described reverse gear idler shaft be set between the input gear axle and second jackshaft, and with it is described
5th output gear cooperatively forms the 11st gear pair.
Optionally, one end stretching second input shaft of first input shaft far from the engine, described second
Input shaft stretches out the input gear axle far from one end of the engine.
Provided by the present invention nine fast double-clutch automatic gearboxes have the advantage that
(1) simple process is designed and manufactured, it can be achieved that the higher production domesticization of components；
(2) compact-sized, two gears are changed to gear shaft on the basis of existing seven fast double-clutch speed changers, are being increased
While shift-up digit, only three groups of parallel gears axle construction (the first output gear shaft, the second output gear shaft and defeated is still maintained
Enter gear shaft)；
(3) lightweight optimizes the quantity of gear and synchronizer, together while completing nine quick changes gear to greatest extent
When use hollow shaft (the first output gear shaft, the second output gear shaft and input gear axle are hollow shaft), realize lightweight
Target；
(4) oil consumption is low, and gear is more, can more fully match engine torque, and speed ratio selection is more, makes engine
Work is in more reasonable range；
(5) dynamic property is strong, and speed ratio span is bigger, and torque is bigger when making to start to walk and climb, and high tap position possesses faster speed.
In addition, the vehicle has as described above nine fast double-clutch automatic gearboxes the present invention also provides a kind of vehicle.
Technical effect possessed by vehicle with as described above nine fast double-clutch automatic gearboxes and above-mentioned nine speed are double
The technical effect of clutch automatic gearbox is similar, and to save length, details are not described herein.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of nine fast double-clutch automatic gearboxes provided by the embodiment of the present invention；
Fig. 2 is the gear position operation table of according to an embodiment of the present invention nine fast double-clutch automatic gearboxes.
In attached Fig. 1 and 2, the reference numerals are as follows:
The first input shaft of 11-, the second input shaft of 12-, 13- input gear axle；
The first jackshaft of FD1-, the second jackshaft of FD2-；
K1- first clutch, K2- second clutch；
The first output gear of G1-, the first output gear shaft of G2-, G3- third output gear, the 4th output gear of G4-, G5-
5th output gear, the second output gear shaft of G6-, the 7th output gear of G7-, the 8th output gear of G8-, the master of G9- first subtract tooth
Wheel, G10- second is main to subtract gear, G11- differential gear, and G12- reverses gear idler shaft；
Z1- first gear pair, Z2- second gear pair, Z3- third gear pair, the 4th gear pair of Z4-, the 5th gear of Z5-
Pair, the 6th gear pair of Z6-, the 7th gear pair of Z7-, Z8- eighth gear pair, the 9th gear pair of Z9-, the tenth gear pair of Z10-,
The 11st gear pair of Z11-；
S1- the first bilateral synchronous device, S2- the second bilateral synchronous device, the first Unilateral synchronizer of S3-, S4- third bilateral synchronous
Device, the 4th bilateral synchronous device of S5-, the second Unilateral synchronizer of S6-.
Specific embodiment
It is with reference to the accompanying drawing and specific real in order to make those skilled in the art more fully understand technical solution of the present invention
Applying example, the present invention is described in further detail.
Referring to FIG. 1, Fig. 1 is the structural schematic diagram of nine fast double-clutch automatic gearboxes provided by the embodiment of the present invention；
Fig. 2 is the gear position operation table of according to an embodiment of the present invention nine fast double-clutch automatic gearboxes.
The embodiment of the present invention provides the fast double-clutch automatic gearbox of one kind nine and has the nine fast double-clutch automatic gearbox
Vehicle.As shown in Figure 1, the nine fast double-clutch automatic gearbox include first clutch K1, second clutch K2, input shaft and
Output shaft.Wherein, input shaft includes the first input shaft 11, the second input shaft 12 and input gear axle 13, and the first input shaft 11 is logical
It crosses first clutch K1 to couple with engine, the second input shaft 12 is coaxially socketed on the outside of the first input shaft 11, and passes through the
Two clutch K2 are coupled with engine, and third input shaft is coaxially socketed on the outside of the second input shaft 12, and the first input shaft 11 is remote
The second input shaft 12 is protruded in one end from engine, and the second input shaft 12 protrudes input gear axle 13 far from one end of engine.
Output shaft includes the first jackshaft FD1 and the second jackshaft FD2, the first jackshaft FD1 and the second jackshaft FD2
The parallel and symmetrical two sides set on input shaft, and be respectively equipped with and subtract gear with the differential gear G11 master engaged.Wherein, first
Jackshaft FD1 subtracts gear G9 by the first master and engages with differential gear G11, to form the 9th gear pair Z9, the second jackshaft
FD2 subtracts gear G10 by the second master and engages with differential gear G11, to form the tenth gear pair Z10.
First jackshaft FD1 is by the side towards engine, it is successively arranged the first output gear G1, first bilateral same
Walk device S1, the first output gear shaft G2, the 4th output gear G4 and the first Unilateral synchronizer S3, wherein the first output gear shaft
G2 is the gear shaft for being coaxially socketed on the outside of the first jackshaft FD1, is equipped with third output gear G3 and the second bilateral synchronous
Device S2.First bilateral synchronous device S1 is acted between the first output gear G1 and the first output gear shaft G2, the second bilateral synchronous
Device S2 is acted between third output gear G3 and the 4th output gear G4.
Second jackshaft FD2 is by the side towards engine, it is bilateral same to be successively arranged the 5th output gear G5, third
Walk device S4, the second output gear shaft G6, the 8th output gear G8 and the second Unilateral synchronizer S6, wherein the second output gear shaft
G6 is the gear shaft for being coaxially socketed on the outside of the second jackshaft FD2, is equipped with the 6th output gear G6 and the 4th bilateral synchronous
Device S5.Third bilateral synchronous device S4 is acted between the 5th output gear G5 and the second output gear shaft G5, the 4th bilateral synchronous
Device S5 is acted between the 7th output gear G7 and the 8th output gear G8.
Input shaft is equipped with input gear, and each input gear is corresponding with each output gear of output shaft, and forms multiple teeth
Wheel set, wherein input gear axle 13 is equipped with first gear secondary Z1, second gear secondary Z2, the 5th gear pair Z5 and the 6th gear pair
Z6, the first input shaft 11 is equipped with the 4th gear pair Z4 and eighth gear secondary Z8, and the second input shaft 12 is equipped with third gear pair Z3
With the 7th gear pair Z7.It is real between each gear pair by selection first clutch K1 or second clutch K2, each synchronizer of adjusting
Show the transmitting of kinetic current to realize the adjusting of each gear.
The nine fast double-clutch automatic gearbox is only on the basis of original seven fast double-clutch automatic gearboxes to structure
It improves, specifically, two output gears for being set to output shaft are changed to output gear shaft, and in the second input shaft 12
Input gear axle 13 is added in outside, and it is relatively simple to design and manufacture technique.Meanwhile the first output gear shaft G2, the second output
The setting of gear shaft G6 and input gear week 13 increase kinetic current transmission path, and then increase gear number, and complete nine
While quick change is kept off, only three groups of parallel pinion shafts are kept, it is compact-sized, while gear and synchronizer are being optimized to greatest extent
Quantity, and then guarantee power train size, convenient for being installed to it.
With the nine fast double-clutch automatic gearbox relative to having for seven fast double-clutch automatic gearboxes, due to improving
Gear is more afterwards, can more fully match engine torque, and speed ratio selection is also just more, so that vehicle motor work exists
In more reasonable range, and then reduce oil consumption；And speed ratio span is bigger, and torque of the vehicle in starting and climbing is bigger, moves
Power is strong, so that high tap position possesses faster speed.
Meanwhile output gear shaft is coaxially socketed on the outside of jackshaft, input gear axle 13 is coaxially socketed on the second input
The outside of axis 12, that is to say, that input gear axle 13, the first output gear shaft G2 and the second output gear shaft G6 are hollow
Axis is, it can be achieved that the whole light-weighted target of vehicle.
In addition, the nine fast double-clutch automatic gearbox is additionally provided with the idler shaft G12 that reverses gear, in the present embodiment, by this reverse gear it is lazy
Wheel shaft G12 is set between input gear axle 13 and the second jackshaft FD2, forms the 5th gear pair Z5 with input gear axle 13,
The 11st gear pair Z11 is formed with the output gear G5 of the second jackshaft FD2, to realize the gear reversing function of vehicle.Certainly, at this
In embodiment, the idler shaft G12 that this can also be reversed gear is set on the first jackshaft FD1 or the second jackshaft FD2, but this is reversed gear
Idler shaft G12 is set between input gear axle 13 and jackshaft, is set to the first jackshaft FD1 or the second jackshaft relative to by it
For FD2 is upper, it is not necessary that its corresponding position is arranged on the first jackshaft FD1 or the second jackshaft FD2, and then can be reduced
The axial length of one jackshaft FD1 or the second jackshaft FD2 reduce overall volume, convenient for the installation of the speed changer.
In the present embodiment, certainly, since the first jackshaft FD1 and the second jackshaft FD2 is symmetrical arranged, the idler shaft that reverses gear
G12 can not also do specific requirement between input gear axle 13 and the first jackshaft FD1 herein.
As depicted in figs. 1 and 2, the provided double clutches of nine speed for vehicle according to embodiments of the present invention are now specifically described
The shift process of automatic transmission.
D grades driver requested (drive shift, i.e., one grade) when driving, kinetic current Z4-Z2-Z6-Z10.
Second bilateral synchronous device S2 moves on to right position D (the 4th output gear G4), and the 4th bilateral synchronous device S4 moves to right position H
(the second output gear shaft G2), first clutch K1 are closed, and second clutch K2 opens, and power is transferred to the via the second input shaft 12
Four gear pair Z4, then the 6th gear pair Z6 is transferred to by second gear secondary Z2 torque, finally torque is passed by the tenth gear pair Z10
It passs differential mechanism and completes power output, realize forward gear.
When TCU (Transmission Control Module) judgement needs to rise to two grades, kinetic current Z7-Z10.
Third bilateral synchronous device S4 keeps right position H, the 4th bilateral synchronous device S5 to move to left position I (the 7th output gear G7),
First clutch K1 is opened, and second clutch K2 is closed, and power is transferred to the 7th gear pair Z7 via the second input shaft 12, then by the tenth
Torque is transmitted differential mechanism and completes power output by gear pair Z10, realizes forward gear.
When TCU judgement needs to rise to third gear, kinetic current Z8-Z10.
Second Unilateral synchronizer S6 is moved to left position J (the 8th output gear G8), and first clutch K1 is closed, second clutch K2
It opens, power is transferred to eighth gear secondary Z8 by the first input shaft 11, then torque is transmitted differential mechanism and complete by the tenth gear pair Z10
At power output, forward gear is realized.
When TCU judgement need to be raised to fourth gear, kinetic current Z3-Z2-Z1-Z9.
First bilateral synchronous device S1 is moved to left position A (the first output gear G1), and the second bilateral synchronous device S2 moves to left position E
(third output gear G3), first clutch K1 is opened, and second clutch K2 is closed, and power is transferred to third tooth by the second input shaft 12
Wheel set Z3, then first gear secondary Z1 is transferred to by second gear secondary Z2 torque, it is poor finally to be transmitted torque by the 9th gear pair Z9
Fast device simultaneously completes power output, realizes forward gear.
When TCU judgement need to be raised to five grades, kinetic current Z8-Z6-Z1-Z9.
First bilateral synchronous device S1 keeps left position A, the 4th bilateral synchronous device S5 to move to right position K (the 8th output gear G8),
First clutch K1 is closed, and second clutch K2 is opened, and power is transferred to eighth gear secondary Z8 by the first input shaft 11, then by the 6th tooth
Wheel set Z6 torque is transferred to first gear secondary Z1, and torque is finally transmitted differential mechanism by the 9th gear pair Z9 and to complete power defeated
Out, forward gear is realized.
When TCU judgement need to be raised to six grades, kinetic current Z7-Z6-Z1-Z9.
First bilateral synchronous device S1 keeps left position A, the 4th bilateral synchronous device S5 to move to left position I (the 7th output gear G7),
First clutch K1 is opened, and second clutch K2 is closed, and power is transferred to the 7th gear pair Z7 by the second input shaft 12, then by the 6th tooth
Wheel set Z6 torque is transferred to first gear secondary Z1, and torque is finally transmitted differential mechanism by the 9th gear pair Z9 and to complete power defeated
Out, forward gear is realized.
When TCU judgement need to be raised to seven grades, kinetic current Z4-Z9.
First Unilateral synchronizer S3 is moved on to left position B (the 4th output gear G4), and first clutch K1 is closed, second clutch K2
It opens, power is transferred to the 4th gear pair Z4 by the first input shaft 11, then torque is transmitted differential mechanism and complete by the 9th gear pair Z9
At power output, forward gear is realized.
When TCU judgement need to be raised to eight grades, kinetic current Z3-Z9.
First bilateral synchronous device S1 is moved to right position C (the first output gear shaft G2), and the second bilateral synchronous device S2 moves to left position E
(third output gear G3), first clutch K1 is opened, and second clutch K2 is closed, and power is transferred to third tooth by the second input shaft 12
Wheel set Z3, then torque is transmitted into differential mechanism by the 9th gear pair Z9 and completes power output, realize forward gear.
When TCU judgement need to be raised to nine grades, kinetic current Z8-Z6-Z2-Z9.
First bilateral synchronous device S1 keeps right position C, the 4th bilateral synchronous device S5 to shift to right position K (the 8th output gear G8),
First clutch K1 is closed, and second clutch K2 is opened, and power is transferred to eighth gear secondary Z8 via the first input shaft 11, then by the 6th
Gear pair Z6 torque is transferred to second gear secondary Z2, and torque is finally transmitted differential mechanism by the 9th Z9 of gear pair and to complete power defeated
Out, forward gear is realized.
Other downshift processes, details are not described herein again.
And R grades driver requested (reverse gear) is when driving, kinetic current Z3-Z2-Z5-Z11-Z10.
Second bilateral synchronous device S2 is moved to left position E (third output gear G3), and third bilateral synchronous device S4 moves to left position G
(the 5th output gear G5), first clutch K1 is opened, and second clutch K2 is closed, and power is transferred to third tooth by the second input shaft 12
Wheel set Z3, then the 5th gear pair Z5 is transmitted torque to via second gear secondary Z2, then be transmitted to second through the 11st gear pair Z11
Jackshaft FD2, to realize that torque is reversed；Differential mechanism most is transmitted torque to through the tenth gear pair Z10 afterwards and completes to export, and is realized
Reverse gear.
When N grades driver requested, two clutches are separated, and (sighting target determines demand, if 1 grade of pre-hung for position in all synchronizers
With R grades).
When P grades driver requested, two clutches are separated, and (sighting target determines demand, if 1 grade of pre-hung for position in all synchronizers
With R grades), halting mechanism works at this time, and since halting mechanism design is mature, to save length, details are not described herein.
The above is only the preferred embodiment of the present invention, it is noted that those skilled in the art are come
It says, various improvements and modifications may be made without departing from the principle of the present invention, these improvements and modifications also should be regarded as
Protection scope of the present invention.
Claims (5)
1. the fast double-clutch automatic gearbox of one kind nine characterized by comprising
Input shaft, including coupled with engine by first clutch (K1) the first input shaft (11), pass through second clutch
(K2) the second input shaft (12) and input gear axle (13) coupled with engine, second input shaft (12) are coaxially socketed on
The outside of first input shaft (11), the input gear axle (13) are coaxially socketed on the outer of second input shaft (12)
Side；
Output shaft, the first jackshaft (FD1) and the second jackshaft (FD2) including being set to the input shaft two sides in parallel are described
First jackshaft (FD1) and second jackshaft (FD2) are respectively equipped with the master engaged with differential gear (G11) and subtract gear；
First jackshaft (FD1) is successively arranged the first output gear (G1), first pair by the side towards engine
Side synchronizer (S1), the first output gear shaft (G2), the 4th output gear (G4) and the first Unilateral synchronizer (S3), described first
Output gear shaft (G2) is coaxially socketed on the outside of first jackshaft (FD1), is equipped with third output gear (G3) and makees
For the second bilateral synchronous device (S2) between the third output gear (G3) and the 4th output gear (G4)；
It is double that second jackshaft (FD2) is successively arranged the 5th output gear (G5), third by the side towards engine
Side synchronizer (S4), the second output gear shaft (G6), the 8th output gear (G8) and the second Unilateral synchronizer (S6), described second
Output gear shaft (G6) is coaxially socketed on the outside of second jackshaft (FD2), is equipped with the 7th output gear (G7) and makees
For the 4th bilateral synchronous device (S5) between the 7th output gear (G7) and the 8th output gear (G8)；
The input shaft is equipped with input gear corresponding with each output gear of the output shaft, and is formed and be located at the input tooth
The first gear of wheel shaft (13) secondary (Z1), second gear secondary (Z2), the 5th gear pair (Z5) and the 6th gear pair (Z6), are located at institute
The 4th gear pair (Z4) and the eighth gear for stating the first input shaft (11) are secondary (Z8), and are located at second input shaft (12)
Third gear pair (Z3) and the 7th gear pair (Z7).
2. according to claim 1 nine fast double-clutch automatic gearboxes, which is characterized in that further include the idler shaft that reverses gear
(G12), the idler shaft that reverses gear (G12) is set between the input gear axle (13) and first jackshaft (FD1), or sets
Between the input gear axle (13) and second jackshaft (FD2), the idler shaft that reverses gear (G12) and the input tooth
Wheel shaft (13) cooperatively forms the 5th gear pair (Z5).
3. according to claim 2 nine fast double-clutch automatic gearboxes, which is characterized in that the idler shaft that reverses gear (G12)
Cooperate between the input gear axle (13) and second jackshaft (FD2), and with the 5th output gear (G5)
Form the 11st gear pair (Z11).
4. according to claim 1-3 nine fast double-clutch automatic gearboxes, which is characterized in that first input
Axis (11) stretches out second input shaft (12) far from one end of the engine, and second input shaft (12) is far from the hair
The input gear axle (13) is stretched out in one end of motivation.
5. a kind of vehicle, which is characterized in that including according to any one of claims 1-4 nine fast double-clutch automatic gearboxes.
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| CN201810183115.7A CN110230667B (en) | 2018-03-06 | 2018-03-06 | Nine-speed double-clutch automatic transmission and vehicle |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113685510A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
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| CN113685510A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685510B (en) * | 2020-05-18 | 2024-01-26 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
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|---|---|
| CN110230667B (en) | 2021-10-08 |
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