CN103671746A - Dual-clutch transmission - Google Patents
Dual-clutch transmission Download PDFInfo
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- CN103671746A CN103671746A CN201210364376.1A CN201210364376A CN103671746A CN 103671746 A CN103671746 A CN 103671746A CN 201210364376 A CN201210364376 A CN 201210364376A CN 103671746 A CN103671746 A CN 103671746A
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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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Disclosed is a dual-clutch transmission for automobiles. The dual-clutch transmission 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 dual-clutch transmission 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 can provide seven forward gears and one reverse gear, and has the advantages that the structure is simple, the number of gears is large, the axial dimensions are small and the reverse motion safety is high.
Description
Technical field
The invention belongs to vehicle (automobile) speed changer technical field, be specifically related to a kind of dual clutch transmission structure.
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 double-clutch speed changer (Dual Clutch Transmission), can farthest meet the integration requirement of people to above performance.Double-clutch speed changer 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; Double-clutch speed changer also has high-comfort not second to automatic transmission simultaneously, and the power that can realize in running process does not interrupt.
Existing double-clutch speed changer is more and more tending towards compact structure, causes Transmission gear number less, affects the smooth gear shifting of speed changer, also just means the driving comfort that affects vehicle; Or cause gear number more, but it is too many to share shifting gear group, affects each gear velocity ratio degrees of freedom of speed changer, be difficult to mate with different vehicle lift-launch; Also have part double-clutch speed changer to be provided with reverse gear shaft, make speed changer component number more, speed changer cost is higher.
Summary of the invention
The invention provides a kind of novel double-clutch speed changer, its objective is with simple structure and obtain good reverse gear Security, more gear number and larger gear velocity ratio degrees of freedom.
Double-clutch speed changer of the present invention mainly comprises interior input shaft, outer input shaft, the first countershaft, the second countershaft, differential assembly and double clutch.This double-clutch speed changer 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, be furnished with the odd number shelves driving gear that can not rotate in contrast, on outer input shaft, be furnished with the even number shelves driving gear that can not rotate in contrast.
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 double-clutch speed changer.
Described double clutch 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 double-clutch speed changer 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 double-clutch speed changer, 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 double-clutch speed changer 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.
The improvement of double-clutch speed changer of the present invention is:
First speed driven gear and reverse gear driven gear are placed on the same countershaft of one of described two countershafts, and the main deceleration driving gear on this countershaft is in two main deceleration driving gears, to have of the less number of teeth, guarantee that this double-clutch automatic gearbox has larger reverse gear ratio, thereby guarantee the Security of car load reverse gear.
Meanwhile, adopt fourth gear driven gear and six grades of driving gears to share four or six grades of driving gears, five grades of driven gears and seven grades of driven gears share five or seven grades of driving gears.This layout advantage is effectively to have controlled the axial dimension of double-clutch speed changer.
Preferably reverse gear drives realization indirectly by the reverse driving gear being connected mutually with second gear driven gear, and reverse gear ratio can be reached and approach one grade of velocity ratio, thus the Security while guaranteeing car load reverse gear; Reverse gear also can directly be driven by second gear driven gear, guarantees that this double-clutch automatic gearbox has less circumferential size, thereby has more excellent cost advantage, and the coupling that is particularly useful for minicar and compact type vehicle is carried.
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.
In addition, adopt one grade to be arranged in second gear driving gear the structure that transmission shaft is two ends, it is that rigidity is better that this setting type makes axle, plays and reduces the distortion of axle system, raising transmission accuracy, increase transmission reliability and the effect in working life.
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, realize dynamic torque reverse, and speed changer only uses four synchronizers just can meet gear to select demand, take 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 dual-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 first embodiment of the present invention;
Fig. 2 is the structural representation of the second embodiment of the present invention;
Fig. 3 is the structural representation of the third embodiment of the present invention;
Fig. 4 is the structural representation of the fourth embodiment of the present invention;
Fig. 5 is embodiment 1 axial arrangement schematic diagram.
In accompanying drawing figure:
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Embodiment
Below in conjunction with accompanying drawing, by embodiment, the present invention is further described.
Referring to Fig. 1, Fig. 2, Fig. 3, Fig. 4 and Fig. 5, the double-clutch speed changer 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 grade of driven gear (32,34,36,38,42,44,46,48) and reverse driving gear (47) are placed in respectively on two countershafts (30,40).
On two countershafts, be respectively provided with one and countershaft
can not relatively rotatemain deceleration driving gear (39,49), main deceleration driving gear (39,49) and main deceleration driven gear (82) often mesh, main deceleration driven gear (82) and differential mechanism are connected, differential assembly (80) is as the output terminal of this double-clutch speed changer.
First speed driven gear (32) is placed on same countershaft with reverse gear driven gear (38), and the main deceleration driving gear on this countershaft is in two main deceleration driving gears, to have of the less number of teeth, guarantee that this double-clutch automatic gearbox has larger reverse gear ratio on the one hand, thus the Security while guaranteeing car load reverse gear; Guarantee that on the other hand this double-clutch automatic gearbox has less circumferential size, reduce to be arranged in and one grade of size with gear and the phase gear of countershaft, reduce speed changer weight, thereby have more excellent cost advantage, indirectly reduce complete-vehicle oil consumption.
Described fourth gear driven gear (36) and six grades of driven gears (46) share four or six grades of driving gears (24), and described five grades of driven gears (34) and seven grades of driven gears (44) share five or seven grades of driving gears (16).This layout advantage is effectively to have controlled the axial dimension of double-clutch speed changer.
The reverse gear implementation of this double-clutch speed changer has following two kinds at least:
Described reverse gear driven gear (38) is directly driven by second gear driven gear (48), makes this speed changer axial dimension less.
Described reverse gear driven gear (38) is driven by the reverse driving gear (47) being connected mutually with second gear driven gear (48), reverse gear ratio can be reached and approach one grade of velocity ratio.
The parking wheel P arrangement of this double-clutch speed changer has following several form optional (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;
Or, with the differential mechanism parking wheel P(60b that is connected).
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 (16) 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, five or seven grades of driving gears (16) often mesh with five grades of driven gears (42) and seven grades of driven gears (44) simultaneously, reverse driving gear (47) often meshes with reverse gear driven gear (38).
From away from double clutch (70) end to close double clutch (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 a gear driving gear (12), three gear driving gear (14) and five or seven grades of driving gears (16).On described outer input shaft (20), be provided with successively four or six grades of tooth driving gear (24) and two gear driving gears (22) altogether.On the first countershaft (30), be furnished with first speed driven gear (32), five grades of driven gears (34), fourth gear driven gear (36) and reverse gear driven gear (38).On the second countershaft (40), be furnished with third gear driven gear (42), seven grades of driven gears (44), six grades of driven gears (46), second gear driven gear (48).This embodiment is that axle is stressing conditions optimal case.Because, have on the basis of the total structure characteristic of the present invention, also low speed gear is located at respectively to the axle head that axle is each axle, near the bearings point of each axle, this structure has improved rigidity shaft system, reduce to shifting gear the gear destruction rate under high pulling torque and alternating stress, improve transmission reliability and working life.This layout reduces speed changer overall height in addition, increases axis rigidity, the effect that reduces the distortion of axle system and improve the gear accuracy of mesh.
Referring to Fig. 2, in embodiment 2, on interior input shaft (10), be provided with successively three gear driving gears (14), a gear driving gear (12), five or seven grades of driving gears (16); On described outer input shaft (20), be provided with successively four or six grades of driving gears (22) and two gear driving gears (22).On the first countershaft (30), be furnished with first speed driven gear (32), five grades of driven gears (34), fourth gear driven gear (36) and reverse gear driven gear (38).On the second countershaft (40), be furnished with third gear driven gear (42), seven grades of driven gears (44), six grades of driven gears (46), second gear driven gear (48).This embodiment's scheme adopts one grade of wheel tooth wheels between other shifting gear groups, the process that utilizes well one grade of driving gear machining to need, and making transmission shaft is that axial dimension is more excellent, and axle is that stressing conditions is better.
Referring to Fig. 3, in embodiment 3, on interior input shaft (10), be provided with successively five or seven grades of driving gears (16), a gear driving gear (12), three gear driving gears (14); On described outer input shaft (20), be provided with successively four or six grades of driving gears (22) and two gear driving gears (22).On the first countershaft (30), be furnished with first speed driven gear (32), five grades of driven gears (34), fourth gear driven gear (36) and reverse gear driven gear (38).On the second countershaft (40), be furnished with seven grades of driven gears (44), third gear driven gear (42), six grades of driven gears (46), second gear driven gear (48).This embodiment's scheme is utilized one grade of driving gear process space, and reducing transmission shaft is size, and it is less to reach speed changer end circumferential size, is easy to speed changer arrangement and saves cost.
Referring to Fig. 4, in embodiment 4, on interior input shaft (10), be provided with successively three gear driving gears (14), gear driving gear (12) and five or seven grades of driving gears (16); On described outer input shaft (20), be provided with successively four or six grades of tooth driving gear (24) and two gear driving gears (22) altogether.On the first countershaft (30), be furnished with first speed driven gear (32), five grades of driven gears (34), fourth gear driven gear (36) and reverse gear driven gear (38).On the second countershaft (40), be furnished with third gear driven gear (42), seven grades of driven gears (44), six grades of driven gears (46), second gear driven gear (48).Gear is arranged with the first embodiment, but the mode that adopts reverse gear driven gear (38) directly to be driven by second gear driven gear (48) realizes reverse gear, thereby has more excellent axial dimension.
In above embodiment, every kind of corresponding and different vehicle match condition all, arranges with engine compartment space, the factor such as inner each component layouts of speed changer, each gear velocity ratio selection, power character Economy performance is relevant, depending on concrete condition selection, applies.
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).
The gear of each synchromesh gear (62,64,66,68) selects action to drive each gear shift fork to realize by hydraulic pressure or motor.
Take one grade of embodiment 1 and reverse gear is example, and seven forward gears of this double-clutch speed changer device 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.
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 double-clutch speed changer, 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);
Described fourth gear driven gear (36) and six grades of driven gears (46) share four or six grades of driving gears (24), and described five grades of driven gears (34) and seven grades of driven gears (44) share five or seven grades of driving gears (16).
2. double-clutch speed changer according to claim 1, is characterized in that: on described the first countershaft (30), be furnished with first speed driven gear (32), five grades of driven gears (34), fourth gear driven gear (36) and reverse gear driven gear (38); On described the second countershaft (40), be furnished with second gear driven gear (48), third gear driven gear (42), six grades of driven gears (46), seven grades of driven gears (44).
3. double-clutch speed changer according to claim 2, it is characterized in that: from holding near double clutch (80) extreme direction away from double clutch (70), on interior input shaft (10), be provided with successively three gear driving gears (14), a gear driving gear (12), five or seven grades of driving gears (16); From holding near double clutch (80) extreme direction away from double clutch (70), on described outer input shaft (20), be provided with successively four or six grades of tooth driving gear (24) and two gear driving gears (22) altogether.
4. double-clutch speed changer according to claim 2, it is characterized in that: from holding near double clutch (70) extreme direction away from double clutch (70), on interior input shaft (10), be provided with successively five or seven grades of driving gears (16), a gear driving gear (12) and three gear driving gears (14); From holding near double clutch (80) 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).
5. double-clutch speed changer according to claim 2, it is characterized in that: from holding near double clutch (70) extreme direction away from double clutch (70), on interior input shaft (10), be provided with successively a gear driving gear (12), three gear driving gears (14), five or seven grades of driving gears (16); From holding near double clutch (80) 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).
6. according to the double-clutch speed changer described in claim 1 to 5 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).
7. according to the double-clutch speed changer described in claim 3 to 5 any one, 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).
8. according to the double-clutch speed changer described in claim 3 to 5 any one, it is characterized in that: described first speed driven gear (32) with five grades of driven gears (42) 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); Third gear driven gear (34) with seven grades of driven gears (44) 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. double-clutch speed changer according to claim 6, is characterized in that: described first speed driven gear (32) with five grades of driven gears (42) 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); Third gear driven gear (34) with seven grades of driven gears (44) 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 |
|---|---|---|---|
| CN201210364376.1A CN103671746A (en) | 2012-09-26 | 2012-09-26 | Dual-clutch transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210364376.1A CN103671746A (en) | 2012-09-26 | 2012-09-26 | Dual-clutch transmission |
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| CN103671746A true CN103671746A (en) | 2014-03-26 |
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| CN201210364376.1A Pending CN103671746A (en) | 2012-09-26 | 2012-09-26 | Dual-clutch transmission |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104373524B (en) * | 2014-07-29 | 2017-01-04 | 宁波上中下自动变速器有限公司 | A kind of eight speed double-clutch formula automatic transmission |
| CN107532686A (en) * | 2015-04-16 | 2018-01-02 | Zf 腓德烈斯哈芬股份公司 | Divide speed changer, total speed changer and agricultural operation machinery |
| CN111853170A (en) * | 2019-04-25 | 2020-10-30 | 广州汽车集团股份有限公司 | Eight-speed double-clutch type automatic transmission and vehicle |
| CN112930452A (en) * | 2018-10-02 | 2021-06-08 | 戴姆勒股份公司 | Method for operating a dual clutch transmission to disengage respective tip tooth positions |
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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 (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104373524B (en) * | 2014-07-29 | 2017-01-04 | 宁波上中下自动变速器有限公司 | A kind of eight speed double-clutch formula automatic transmission |
| CN107532686A (en) * | 2015-04-16 | 2018-01-02 | Zf 腓德烈斯哈芬股份公司 | Divide speed changer, total speed changer and agricultural operation machinery |
| CN112930452A (en) * | 2018-10-02 | 2021-06-08 | 戴姆勒股份公司 | Method for operating a dual clutch transmission to disengage respective tip tooth positions |
| CN112930452B (en) * | 2018-10-02 | 2022-07-12 | 戴姆勒股份公司 | Method for operating a dual clutch transmission to disengage respective tip tooth positions |
| US11619301B2 (en) | 2018-10-02 | 2023-04-04 | Daimler Ag | Method for operating a dual-clutch transmission for resolving respective tooth-on-tooth positions |
| CN111853170A (en) * | 2019-04-25 | 2020-10-30 | 广州汽车集团股份有限公司 | Eight-speed double-clutch type automatic transmission and vehicle |
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Application publication date: 20140326 |