CN103671748A - Transmission device of dual-clutch transmission - Google Patents
Transmission device of dual-clutch transmission Download PDFInfo
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- CN103671748A CN103671748A CN201210366812.9A CN201210366812A CN103671748A CN 103671748 A CN103671748 A CN 103671748A CN 201210366812 A CN201210366812 A CN 201210366812A CN 103671748 A CN103671748 A CN 103671748A
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- 230000007246 mechanism Effects 0.000 claims description 4
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- 230000009977 dual effect Effects 0.000 abstract description 4
- 238000005299 abrasion Methods 0.000 abstract 1
- 230000009471 action Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000003796 beauty Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
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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
- F16H3/087—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
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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
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
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Abstract
Disclosed is a transmission device of a dual-clutch transmission. The transmission device comprises an inner input shaft, an outer input shaft, two countershafts, a dual clutch, a differential assembly, a plurality of normally-engaged gear sets and a plurality of synchronizer devices, wherein the inner input shaft and the outer input shaft are coaxially arranged, the two countershafts are parallel to the two input shafts, and the normally-engaged gear sets are arranged on the shafts respectively. Because a first-speed driven gear and a reverse driven gear are arranged on the same countershaft, the transmission device has a high reverse gear transmission ratio and higher reverse motion safety. Because the reverse motion is achieved in the manner that a fourth gear and a sixth gear share one driving gear, a fifth gear and a seventh gear share another driving gear and a second-speed driven gear and a reverse driving gear are integrated or in the manner that the fourth gear and the sixth gear share one driving gear, the fifth gear and the seventh gear share another driving gear and the second-speed driven gear drives the reverse driven gear directly, the axial dimensions of the transmission are reduced. Because low-speed gear sets are arranged at the shaft ends of a shaft system of a gearbox respectively, the shaft system has higher rigidity, smaller abrasion and longer service life. The transmission device can provide seven forward gears and one reverse gear, and has the advantages that the structure is simple, the reverse motion safety is high, the number of gears is large and the gear transmission ratio and the degree of freedom are high.
Description
Technical field
The invention belongs to vehicle (automobile) speed changer technical field, be specifically related to a kind of transmission device of double clutch transmission.
Background technique
Travelling comfort, handling and high-efficiency and economic are all very important vehicle and transmission performance indexs, in the application of traditional manual speed changer and automatic transmission, at above aspect of performance, all just attend to one thing and lose sight of another.Select high handling and high-efficiency and economic just to mean low travelling comfort; Selecting high travelling comfort to mean in handling and Economy gives way to some extent.
Yet the employing of novel dual-clutch transmission (Dual Clutch Transmission), can farthest meet the integration requirement of people to above performance.Dual-clutch transmission can provide the high efficiency of the manual transmission that matches in excellence or beauty and higher handling, can meet people to vehicle economy and drive the demand of amusement; Dual-clutch transmission also has high-comfort not second to automatic transmission simultaneously, and the power that can realize in running process does not interrupt.
But, because existing dual-clutch transmission is more and more tending towards compact structure, cause Transmission gear number less, affect the smooth gear shifting of speed changer, also just mean the driving comfort that affects vehicle; Or in order to keep gear number more, but it is too many to share shifting gear group, affect each gear velocity ratio degrees of freedom of speed changer, be difficult to mate with different vehicle lift-launch; Also have part dual-clutch transmission to be provided with reverse gear shaft, make speed changer component number more, speed changer cost is higher.
Summary of the invention
The object of this invention is to provide a kind of transmission device of double clutch transmission, to realize more gear number and the larger features such as gear velocity ratio degrees of freedom by better simply structure.
Transmission device of double clutch transmission of the present invention mainly comprises interior input shaft, outer input shaft, the first countershaft, the second countershaft, differential assembly and double clutch.This dual-clutch transmission provides seven forward gears and a reverse gear.
Interior input shaft and outer input shaft are coaxially arranged, and interior input shaft has part circumferentially to be surrounded formation empty set by outer input shaft.Outer input shaft is hollow input shaft; Interior input shaft can be solid input shaft, can be also hollow input shaft.Interior input shaft and outer input shaft, by bearings, make interior input shaft and outer input shaft coaxially and keep empty set, guarantee freely to rotate separately.
On interior input shaft, being furnished with can not
in contrastthe odd number shelves driving gear rotating, on outer input shaft, being furnished with can not
in contrastthe even number shelves driving gear rotating.
The first countershaft and the second countershaft and two input shafts are arranged in parallel.On two countershafts, be respectively provided with one and countershaft
can not relatively rotatemain deceleration driving gear, and be set with each grade of driven gear and the reverse driving gear being meshed with described each grade of driving gear, on two countershafts, be also furnished with a plurality of synchromesh gears of selecting each gear to use, each grade of driven gear and reverse driving gear are optionally connected with two countershafts by the synchromesh gear being fixedly connected with two countershafts.Wherein each shifting gear on two countershafts is with empty set arranged in form on countershaft, and two main deceleration driving gears rotate with countershaft to be fixedly connected with form with each synchromesh gear.
Differential assembly is as the moment of torsion output terminal of this dual-clutch transmission.
Described transmission device of double clutch transmission comprises two coaxially arranged clutch disks, and two clutch wheel are connected with two input shafts respectively.This double clutch can be dry dual clutch or wet-type dual-clutch.Double clutch is invented described two torque input ends that close speed changer from device for this reason, and is arranged in speed changer near motor end, is fixedly connected with motor output terminal.Can select input torque to be linked into above-mentioned which input shaft by controlling alternately the engaging of two clutch disks of double clutch.
On the whole, the gear driving gear that respectively advances is fixedly connected with and two input shafts, with input shaft, rotates; Each gear driven gear and reverse gear driven gear are placed in two countershafts, and countershaft rotates relatively freely.Synchronizer and main deceleration driving gear are fixedly connected on two countershafts, with countershaft, rotate; All gears and affiliated axle are at axial restraint, and synchronizer is axial float within limits, realize from different shifting gears and engaging, and complete gear selecting.
The moment of torsion transfer mode of this transmission device of double clutch transmission is: first clutch dish and interior input shaft are fixedly connected, and second clutch dish and outer input shaft are fixedly connected, and realizes the moment of torsion transmission of Engine torque from double clutch to driving shaft; Between two input shafts and two countershafts, optionally by each gear main driven gear and synchronizer, be connected, realize the transmission of moment of torsion from input shaft to countershaft; Two countershafts and output shaft often mesh by main deceleration driving gear and differential assembly, realize the transmission of moment of torsion from countershaft to output shaft.
This transmission device of double clutch transmission, can carry out gear according to gearshift demand preselected, realizes in Vehicle Driving Cycle fast, gearshift reposefully.By control synchro, carry out gear and select action, two countershafts are connected from different input shafts respectively.At one time, two clutches only have one in jointing state, thereby, in two input shafts, there is and only have an input shaft to join motor transmitting torque to.That is to say at any time, can have two synchronizers to complete the selection of two gears, but only have a countershaft transmitting Engine torque.When two gears on different input shafts engage simultaneously, by controlling the alternately jointing state of two clutch disks of switch dual clutch, can realize crash change of speed, power does not interrupt.
All gearshift actions of transmission device of double clutch transmission and the bonding state of double clutch are controlled by transmission control unit (Transmission Control Unit).
Described two input shafts respectively have one end by bearings on mission case, and with bearing, support mutually between two input shafts, realize independent rotation separately; Each axle head of two countershafts is furnished with respectively a bearings on mission case.
Transmission device of double clutch transmission of the present invention, has following improvement:
First speed driven gear and reverse gear driven gear are placed on same countershaft.Like this, guarantee that this double-clutch automatic gearbox has larger reverse gear ratio on the one hand, thereby guarantee that car load arrives Security at that time; Guarantee that on the other hand this double-clutch automatic gearbox has less circumferential size, thereby have more excellent cost advantage.
Meanwhile, described fourth gear driven gear and six grades of driven gears share four or six grades of driving gears, effectively to control the axial dimension of double-clutch speed changer, guarantee each gear velocity ratio degrees of freedom.
And, in the present invention, first speed driven gear, third gear driven gear, fourth gear driven gear being arranged on same countershaft, second gear driven gear, five grades of driven gears, six grades of driven gears and seven grades of driven gears are arranged on another countershaft.Make so larger gear driven gear be placed in same countershaft, and be equipped with larger base ratio, it is teeth directional size that integral body reduces axle, reduces weight, saves material, cost-saving; Can guarantee very large reverse gear ratio again, the reverse gear Security having guaranteed.
The architecture advances of above three aspects: merges mutually, jointly for transmission device of double clutch transmission of the present invention, can fine realizes goal of the invention of the present invention.
Further, from away from double clutch end near double clutch extreme direction, on interior input shaft, one gear driving gear and three gear driving gears are placed between five grades of driving gears and seven grades of driving gears, and a gear driving gear is placed in compared with the position of the more close axle end bearing of three gear driving gears, can make like this speed changer top axle is that end positions is lower, benefits the layout at engine compartment other system component and gearbox.
Preferably, the main deceleration driving gear on the countershaft of first speed driven gear place is one that in two main deceleration driving gears, has with the larger gear ratio of described main deceleration driven gear.Like this by 1 grade, the driven gear that reverses gear is arranged in same countershaft, due to one grade, back gear ratio is large compared with second gear, therefore cause 1 grade, the driven gear that reverses gear is larger, in shaft system arrangement, one grade of place axle needs more away from input shaft, cause axle pastern partial volume larger, therefore, with due regard to improve one grade of main deceleration driving gear of place axle and main deceleration driven gear gear ratio, can suitably share velocity ratio in differential mechanism transfer stages, can be by 1 grade, reverse gear and input shaft on velocity ratio between driving gear suitably turn down, thereby reduce 1 grade, reverse gear diameter, make shaft system arrangement space compacter.
Preferably, reverse gear directly or by the reverse driving gear being connected mutually with second gear driven gear drives realization indirectly by second gear driven gear, both effectively controlled the axial dimension of double-clutch speed changer, farthest meet again the degrees of freedom of each gear velocity ratio, there is larger elasticity, applicable to the coupling of all kinds of vehicles, carry.
The present invention adopts seven forward gearss and reverse gear and without reverse gear shaft structure, by reverse gear main driven gear is separately positioned on two countershafts, realizes dynamic torque reverse.And speed changer only uses four synchronizers just can meet gear and selects demand, takes full advantage of synchronizer resource.
One grade and reverse gear arrange respectively with inside and outside input shaft on, be connected from different clutch disks.For with city operating mode, the set that this setting type is better divided equally two clutch disks engages probability, has improved double clutch working life, improves double clutch starting and controls.
That visible transmission device of double clutch transmission provided by the invention has is simple in structure, Security during car load reverse gear, the larger features such as gear velocity ratio degrees of freedom, has reduced number of parts, has saved speed changer cost, has improved system reliability.
Accompanying drawing explanation
By the embodiment shown in reference to the accompanying drawings, the present invention is explained in detail below.Relevant drawings is as follows:
Fig. 1 is the structural representation of the embodiment of the present invention 1;
Fig. 2 is the structural representation of the embodiment of the present invention 2;
Fig. 3 is the axial view of Fig. 1.
In accompanying drawing figure:
Embodiment
Below in conjunction with accompanying drawing, by embodiment, the present invention is further described.
Referring to Fig. 1, Fig. 2 and Fig. 3, the transmission device of double clutch transmission that each embodiment represents all has following common structure:
Interior input shaft (10) and outer input shaft (20) are coaxially arranged, and at least a portion, input shaft (10) is surrounded by outer input shaft (20); The first countershaft (30) is arranged in parallel with the second countershaft (40) and two input shafts.Interior input shaft (10) is connected with first clutch dish (72), and outer input shaft (20) is connected with second clutch dish (74).
It is upper that each forward gears driving gear (12,14,16,18,22,24) is connected to two input shafts (10,20), and they are not rotatable with respect to input shaft separately, can adopt spline joint or other form; Each forward gears driven gear and reverse driving gear (47) are placed in respectively on two countershafts (30,40).
On two countershafts, be respectively provided with one and the not relatively turnable main deceleration driving gear (39 of countershaft, 49), main deceleration driving gear (39,49) and main deceleration driven gear (82) often mesh, main deceleration driven gear (82) is connected with differential mechanism, and differential assembly (80) is as the output terminal of this dual-clutch transmission.
Fourth gear driven gear (36) shares four or six grades of driving gears (24) with six grades of driven gears (46).
First speed driven gear (32) and reverse gear driven gear (38) are placed on the same countershaft of one of described two countershafts, and the main deceleration driving gear (39) on this countershaft is in two main deceleration driving gears, to have of the less number of teeth.
First speed driven gear (32), third gear driven gear (34), fourth gear driven gear (36) are arranged on same countershaft, and second gear driven gear (48), five grades of driven gears (42), six grades of driven gears (46) and seven grades of driven gears (44) are arranged on another countershaft.
Each shifting gear master slave relation is: one grade of driving gear (12) often meshes with first speed driven gear (32), second gear driving gear (22) often meshes with second gear driven gear (48), third speed drive gear (14) often meshes with third gear driven gear (34), four or six grades of driving gears (24) often mesh with fourth gear driven gear (36) and six grades of driven gears (46) simultaneously, seven grades of driving gears (18) often mesh with seven grades of driven gears (44), five grades of driving gears (16) often mesh with five grades of driven gears (42), reverse driving gear (47) often meshes with reverse gear driven gear (38).
The gear choice relation of synchronizer is: first speed driven gear (32) with third gear driven gear (34) by the first synchromesh gear SC1(62) be optionally connected with the first countershaft (30); Fourth gear driven gear (36) with reverse gear driven gear (38) by the second synchromesh gear SC2(64) be optionally connected with the first countershaft (30); Seven grades of driven gears (44) with five grades of driven gears (42) by the 3rd synchromesh gear SC3(66) be optionally connected with the second countershaft (40); Second gear driven gear (48) with six grades of driven gears (46) by the 4th synchromesh gear SC4(68) be optionally connected with the second countershaft (40).
Reverse gear implementation has at least following two kinds of forms optional:
Described reverse gear driven gear (38) is directly driven by second gear driven gear (48);
Described reverse gear driven gear (38) is driven indirectly by the reverse driving gear (47) being connected mutually with second gear driven gear (48).
Parking wheel P arrangement at least can be selected one of following mode (the parking wheel P that in figure, dotted line represents is optional):
At described reverse gear driven gear (38) and the main deceleration driving gear FD1(39 of the first countershaft) between parking wheel P (60a) is set;
With the differential mechanism parking wheel P(60b that is connected).
From away from double clutch assembly (70) end to double clutch assembly (70) extreme direction, each embodiment's the gear relation of arranging is as follows:
Referring to Fig. 1, in embodiment 1, on interior input shaft (10), be provided with successively five gear driving gears (16), a gear driving gear (12), seven grades of driving gears (18) and three gear driving gears (14); On described outer input shaft (20), be fixed with successively four or six grades of driving gears (24) and two gear driving gears (22).
Referring to Fig. 2, in embodiment 2, on interior input shaft (10), one gear driving gear (12) and three gear driving gears (14) are placed between five grades of driving gears (16) and seven grades of driving gears (18), and a gear driving gear (12) is placed in compared with the position of the more close axle end bearing of three gear driving gears (14); On described outer input shaft (20), be fixed with successively four or six grades of driving gears (24) and two gear driving gears (22).
Take embodiment 1 as example, and seven forward gears of this transmission device of double clutch transmission and the power transmission line of a reverse gear are as follows:
One grade of power transmission line: the first synchronizer SC1(62) engage first clutch dish (72) closure with first speed driven gear (32).Engine torque passes to interior input shaft (10) by first clutch dish (72), one grade of driving gear (12), first speed driven gear (32) and the first synchronizer SC1(62 via normal engagement) be delivered to the first countershaft (30), through the first main deceleration driving gear (39), arrive differential assembly (80) again, finally by differential assembly (80) outputting power.
Second gear power transmission line: the 3rd synchronizer SC4(68) engage second clutch dish (74) closure with second gear driven gear (48).Engine torque passes to outer input shaft (20) by second clutch dish (74), second gear driving gear (16), second gear driven gear (48) and the 4th synchronizer SC4(68 via normal engagement) be delivered to the second countershaft (40), through the second main deceleration driving gear (49), arrive differential assembly (80) again, finally by differential assembly (80) outputting power.
Third gear power transmission line: the first synchronizer SC1(62) engage first clutch dish (72) closure with third gear driven gear (34).Engine torque passes to interior input shaft (10) by first clutch dish (72), third speed drive gear (14), third gear driven gear (34) and the first synchronizer SC1(62 via normal engagement) be delivered to the first countershaft (30), through the first main deceleration driving gear (39), arrive differential assembly (80) again, finally by differential assembly (80) outputting power.
Fourth gear power transmission line: the second synchronizer SC2(64) engage second clutch dish (74) closure with fourth gear driven gear (36).Engine torque passes to outer input shaft (20) by second clutch dish (74), share four or six grades of driving gears (24), fourth gear driven gear (36) and the second synchronizer (64) via normal engagement are delivered to the first countershaft (30), through the first main deceleration driving gear (39), arrive differential assembly (80) again, finally by differential assembly (80) outputting power.
Five grades of power transmission lines: the 3rd synchronizer SC3(66) engage first clutch dish (72) closure with seven grades of driven gears (44).Engine torque passes to interior input shaft (10) by first clutch dish (72), seven grades of driving gears (18), seven grades of driven gears (44) and the 3rd synchronizer SC3(66 via normal engagement) be delivered to the second countershaft (40), through the second main deceleration driving gear (49), arrive differential assembly (80) again, finally by differential assembly (80) outputting power.
Six grades of power transmission lines: the 4th synchronizer SC4(68) engage second clutch dish (74) closure with six grades of driven gears (46).Engine torque passes to outer input shaft (20) by second clutch dish (74), via normal engagement, share four or six grades of driving gears (24), six grades of driven gears (46) and the 4th synchronizer SC4(68) be delivered to the second countershaft (40), through the second main deceleration driving gear (49), arrive differential assembly (80) again, finally by differential assembly (80) outputting power.
Seven grades of power transmission lines: the 3rd synchronizer SC3(66) engage first clutch dish (72) closure with five grades of driven gears (42).Engine torque passes to interior input shaft (10) by first clutch dish (72), five grades of driving gears (16), five grades of driven gears (42) and the 3rd synchronizer SC3(66 via normal engagement) be delivered to the second countershaft (40), through the second main deceleration driving gear (49), arrive differential assembly (80) again, finally by differential assembly (80) outputting power.
Reverse gear power transmission line: the second synchronizer SC2(64) engage second clutch dish (74) closure with fourth gear driven gear (36).Engine torque passes to outer input shaft (20) by second clutch dish (74), second gear driving gear (16) and second gear driven gear (48) via normal engagement, because of second gear driven gear (48) and reverse driving gear (47) disjunctor, often reverse driving gear (47), reverse gear driven gear (38) and second synchronizer (64) of engagement are delivered to the first countershaft (30) again, through the first main deceleration driving gear (39), arrive differential assembly (80) again, finally by differential assembly (80) outputting power.
Claims (9)
1. a transmission device of double clutch transmission, comprising: coaxially arranged interior input shaft (10) and outer input shaft (20), and at least a portion, input shaft (10) is surrounded by outer input shaft (20); Be parallel to two countershafts that inside and outside input shaft (10,20) is arranged; With inside and outside input shaft (10,20) connected double clutch (70) respectively;
On described interior input shaft (10), be furnished with the odd number shelves driving gear (12,14,16,18) that can not rotate in contrast, on outer input shaft (20), be furnished with the even number shelves driving gear (22,24) that can not rotate in contrast;
On two countershafts, respectively be provided with one and the not relatively turnable main deceleration driving gear of countershaft, and being set with each grade of driven gear and the reverse driving gear being meshed with described odd number shelves and even number shelves driving gear, each grade of driven gear and reverse driving gear are optionally connected with two countershafts by the synchromesh gear being fixedly connected with two countershafts;
Two clutch disks of described double clutch (70) are coaxially arranged, are connected respectively with inside and outside input shaft (10,20);
Main deceleration driving gear on described two countershafts and the main deceleration driven gear (82) being connected with differential mechanism are meshed, and differential assembly (80) is as the output terminal of this double-clutch speed changer;
It is characterized in that:
First speed driven gear (32) is placed on same countershaft with reverse gear driven gear (38);
Fourth gear driven gear (36) and six grades of driven gears (46) share four or six grades of driving gears (24);
First speed driven gear (32), third gear driven gear (34), fourth gear driven gear (36) are arranged on same countershaft, and second gear driven gear (48), five grades of driven gears (42), six grades of driven gears (46) and seven grades of driven gears (44) are arranged on another countershaft.
2. transmission device of double clutch transmission according to claim 1, it is characterized in that: from holding to double clutch (70) extreme direction away from double clutch (70), on interior input shaft (10), be provided with successively five gear driving gears (16), a gear driving gear (12), seven grades of driving gears (18) and three gear driving gears (14); From holding to double clutch (70) extreme direction away from double clutch (70), on described outer input shaft (20), be provided with successively four or six grades of driving gears (24) and two gear driving gears (22).
3. transmission device of double clutch transmission according to claim 1, it is characterized in that: from holding near double clutch (70) extreme direction away from double clutch (70), on interior input shaft (10), one gear driving gear (12) and three gear driving gears (14) are placed between five grades of driving gears (16) and seven grades of driving gears (18), and a gear driving gear (12) is placed in compared with the position of the more close axle end bearing of three gear driving gears (14); From holding to double clutch (70) extreme direction away from double clutch (70), on described outer input shaft (20), be provided with successively four or six grades of driving gears (24) and two gear driving gears (22).
4. according to the transmission device of double clutch transmission described in claims 1 to 3 any one, it is characterized in that: the main deceleration driving gear on the countershaft of first speed driven gear (32) place is one that in two main deceleration driving gears, has with the larger gear ratio of described main deceleration driven gear (82).
5. according to the double-clutch speed changer described in claim 2 or 3, it is characterized in that: described reverse gear driven gear (38) and second gear driven gear (48) engagement, directly driven by second gear driven gear (48); Or described reverse gear driven gear (38) and reverse driving gear (47) engagement being connected mutually with second gear driven gear (48), driven by reverse driving gear (47).
6. according to the transmission device of double clutch transmission described in claim 1,2 or 3, it is characterized in that: at described reverse gear driven gear (38) and the main deceleration driving gear FD1(39 of the first countershaft) between parking wheel P(60a is set).
7. according to the transmission device of double clutch transmission described in claim 1,2 or 3, it is characterized in that: parking wheel P(60b is set on differential assembly (80)).
8. according to the transmission device of double clutch transmission described in claim 1,2 or 3, it is characterized in that: described first speed driven gear (32) with third gear driven gear (34) by the first synchromesh gear SC1(62) be optionally connected with the first countershaft (30); Fourth gear driven gear (36) with reverse gear driven gear (38) by the second synchromesh gear SC2(64) be optionally connected with the first countershaft (30); Seven grades of driven gears (44) with five grades of driven gears (42) by the 3rd synchromesh gear SC3(66) be optionally connected with the second countershaft (40); Second gear driven gear (48) with six grades of driven gears (46) by the 4th synchromesh gear SC4(68) be optionally connected with the second countershaft (40).
9. transmission device of double clutch transmission according to claim 4, is characterized in that: described first speed driven gear (32) with third gear driven gear (34) by the first synchromesh gear SC1(62) be optionally connected with the first countershaft (30); Fourth gear driven gear (36) with reverse gear driven gear (38) by the second synchromesh gear SC2(64) be optionally connected with the first countershaft (30); Seven grades of driven gears (44) with five grades of driven gears (42) by the 3rd synchromesh gear SC3(66) be optionally connected with the second countershaft (40); Second gear driven gear (48) with six grades of driven gears (46) by the 4th synchromesh gear SC4(68) be optionally connected with the second countershaft (40).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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CN201210366812.9A CN103671748A (en) | 2012-09-26 | 2012-09-26 | Transmission device of dual-clutch transmission |
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CN201210366812.9A CN103671748A (en) | 2012-09-26 | 2012-09-26 | Transmission device of dual-clutch transmission |
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CN103671748A true CN103671748A (en) | 2014-03-26 |
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CN201210366812.9A Pending CN103671748A (en) | 2012-09-26 | 2012-09-26 | Transmission device of dual-clutch transmission |
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Cited By (6)
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CN105221683A (en) * | 2014-06-10 | 2016-01-06 | 孙振台 | Traction drive synchronous governor and multi-axle gearbox having the governor |
CN105370819A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Automatic ten-gear double-clutch transmission |
CN105465295A (en) * | 2016-01-13 | 2016-04-06 | 北京理工大学 | Nine-speed dual-clutch transmission |
CN108412976A (en) * | 2018-04-25 | 2018-08-17 | 重庆青山工业有限责任公司 | The speed changer of hybrid vehicle |
CN108779835A (en) * | 2016-04-28 | 2018-11-09 | Zf 腓德烈斯哈芬股份公司 | The double-clutch speed changer of countershaft structure type |
CN108779834A (en) * | 2016-04-28 | 2018-11-09 | Zf 腓德烈斯哈芬股份公司 | The double-clutch speed changer of countershaft form |
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WO2011148065A1 (en) * | 2010-05-26 | 2011-12-01 | Pascal Thery | Dual clutch transmission comprising a transfer link and a reverse gear |
CN102308120A (en) * | 2009-02-24 | 2012-01-04 | 爱信Ai株式会社 | Dual clutch automatic transmission |
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CN101260919A (en) * | 2007-02-20 | 2008-09-10 | 通用汽车环球科技运作公司 | Multi speed transmission having a countershaft gearing arrangement |
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Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105221683A (en) * | 2014-06-10 | 2016-01-06 | 孙振台 | Traction drive synchronous governor and multi-axle gearbox having the governor |
CN105370819A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Automatic ten-gear double-clutch transmission |
CN105370819B (en) * | 2014-08-29 | 2017-10-27 | 广州汽车集团股份有限公司 | Ten fast double-clutch automatic gearboxes |
CN105465295A (en) * | 2016-01-13 | 2016-04-06 | 北京理工大学 | Nine-speed dual-clutch transmission |
CN108779835A (en) * | 2016-04-28 | 2018-11-09 | Zf 腓德烈斯哈芬股份公司 | The double-clutch speed changer of countershaft structure type |
CN108779834A (en) * | 2016-04-28 | 2018-11-09 | Zf 腓德烈斯哈芬股份公司 | The double-clutch speed changer of countershaft form |
CN108779835B (en) * | 2016-04-28 | 2021-05-14 | Zf 腓德烈斯哈芬股份公司 | Dual clutch transmission with countershaft design |
CN108779834B (en) * | 2016-04-28 | 2021-09-07 | Zf 腓德烈斯哈芬股份公司 | Dual clutch transmission in the form of a countershaft |
CN108412976A (en) * | 2018-04-25 | 2018-08-17 | 重庆青山工业有限责任公司 | The speed changer of hybrid vehicle |
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Application publication date: 20140326 |