CN101614266A - Double clutch is multi-functional six speed transmissions of symmetric arrangement - Google Patents

Double clutch is multi-functional six speed transmissions of symmetric arrangement Download PDF

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Publication number
CN101614266A
CN101614266A CN200910069910A CN200910069910A CN101614266A CN 101614266 A CN101614266 A CN 101614266A CN 200910069910 A CN200910069910 A CN 200910069910A CN 200910069910 A CN200910069910 A CN 200910069910A CN 101614266 A CN101614266 A CN 101614266A
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CN
China
Prior art keywords
gear
intermediate propeller
propeller shaft
double clutch
clutch
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CN200910069910A
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Chinese (zh)
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杨军
陈杨龙
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Individual
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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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses a kind of double clutch is multi-functional six speed transmissions of symmetric arrangement, comprise four transmission shafts that are arranged in parallel and 14 driving gears, casing central position and according to axially being symmetrically distributed with the double clutch assembly, double clutch assembly output shaft is provided with four driving gears, be respectively arranged with six forward gears driven gears and a backward gear driven gear on two intermediate propeller shafts, wherein first speed driven gear and backward gear driven gear mesh all the time; The driven gear of each grade is used for changing selectively four driving gear moments of torsion; The front end of two intermediate propeller shafts or rear end are respectively arranged with one and transmit gear, and these two output gears that transmit on gear and the output shaft mesh all the time, thereby the moment of torsion after will changing is delivered to output shaft.Can improve the mechanical efficiency of gearbox, reduce the weight of gearbox, and double clutch is symmetric arrangement arranged side by side that the even numbers clutch wherein and the universal component of odd number clutch have interchangeability.

Description

Double clutch is multi-functional six speed transmissions of symmetric arrangement
Technical field
The present invention relates to a kind of double clutch gearbox, relate in particular to built-in multi-functional 6 speed transmissions arranged side by side of a kind of double clutch.It is little, in light weight that the present invention has a volume, efficient height, wide application, low cost of manufacture, characteristics such as reliability height.Affiliated technical field is an automobile, truck, engineering machinery vehicle, and other motor vehicle.
Background technique
In the automobile, clutch is the switch of motor and speed changer transmission of power between motor and speed changer, it be a kind of can transferring power, can cut off the driving mechanism of power again.Its effect mainly is to guarantee the gentle start of automobile energy, alleviates the impulsive load of speed change gear during gear shift and prevents the power train overload.Separation and the gear shift that engages the realization automobile by clutch.At present, double clutch gearbox has had on automotive industry more widely to be used, and according to the difference of double clutch work running environment dry type and two kinds of double clutches of wet type is arranged.At present, dry type and wet-type dual-clutch gearbox have all entered the production in enormous quantities stage.Wherein, wet-type dual-clutch is to move with wet type in the cooling oil groove, and the moment of torsion transmission of wet-type dual-clutch realizes by the wet clutch friction plate that is immersed in the oil.Dry dual clutch then comes transmitting torque by the friction plate on the clutch driven plate, because dry dual clutch has been saved the high efficiency of the transmitting torque that relevant hydraulic systems and dry clutch itself had, dry dual clutch has improved fuel economy on the Da Cheng very much.Though the dry dual clutch benefit is many, but on torque transfer, be restricted, the boundary dimension of dry dual clutch is bigger than wet type double clutch, this is determined by the layout of double clutch and selected friction material, therefore, in and the application that scope is wide big at torque demand, such as: high-grade passenger car and middle bus etc., the wet-type dual-clutch gearbox is proper.
Publication number is CN1621715, the Chinese invention patent application that its open day is on June 1st, 2006 discloses a kind of " double clutch gearbox ", this double clutch gearbox includes: be used to receive the primary input axle of Engine torque, first input shaft that rotates on same axis with the primary input axle; With the primary input axle on same axis and along second input shaft of first input shaft periphery rotation; Be used for transmitting selectively first and second clutches of the moment of torsion of primary input axle to first and second input shafts; Be arranged on the first and the 3rd driving gear on one of them input shaft of first and second input shafts; Be arranged on wherein the second and the 4th driving gear on another input shaft of first and second input shafts; Be used for changing selectively first output unit of the first, second, third and the 4th driving gear moment of torsion, described first output unit and second output unit also are used to export the moment of torsion after the change; Also comprise the differential gear that is connected to simultaneously on first output unit and second output unit.In a word, can find out that comprise 5 axle and 16 gears side by side in this gearbox altogether, wherein 4 driving gear G1, G2, G3, G4 are arranged in (110 and 120) on first and second input shafts by Fig. 1-1 and Fig. 1-2; The pony axle 150 that is used for reverse speed is arranged in the interior edge of gearbox, and such layout has increased the horizontal and height dimension of gearbox.The double clutch assembly is arranged in the front portion of gearbox in addition, has not only limited the space of design torque vibration damper, but also has occupied the space of arranging the mixed power electric generator/electric motor.In addition, for fear of the external leakage of oil of gearbox, the shell of this double clutch will seal with second input shaft 120, and second input shaft 120 will seal with gearbox casing, and second input shaft, 120 diameter maximums, therefore, the edge line speed of seal ring is much larger than the manual transmission of corresponding moment of torsion, thereby causes the safety coefficient of seal ring to descend.
Again it, this invention does not have and shows or propose on the Motor Vehicle that its gearbox can be used on rear wheel drive.
Notification number is US 7490526 B2, U.S.'s application for a patent for invention that its open day is on February 17th, 2009 discloses a kind of " DUAL CLUTCH POWERSHIFT TRANSMISSION WITH TRANSFER SHAFT " (the double clutch Powershift transmission with passing shaft), this double clutch gearbox includes: be used to receive the vibration damper 12 of Engine torque, first input shaft 18 behind the double clutch; Second input shaft 20 along the rotation of the first input shaft periphery; Be used for transmitting selectively first and second clutches of the moment of torsion of primary input axle to first and second input shafts; Be arranged on two driving gears 102,78 on second input shaft; Be arranged on a driving gear 72, the five fast mesomerism gears and the 6th fast driven gear on first input shaft.In a word, can be found out by Fig. 2-1 and Fig. 2-2, comprise 5 side by side axle and 17 gears in this gearbox altogether, wherein the second gear driven gear of large-size is arranged on 22 of gearbox inward flange.Such layout has increased the horizontal and height dimension of gearbox.The double clutch assembly is arranged in the front portion of gearbox in addition, has not only limited the space of design torque vibration damper, but also has occupied the space of arranging the mixed power electric generator/electric motor.In addition, for fear of the external leakage of oil of gearbox, second input shaft 20 will seal with double clutch shell and gearbox casing, and second input shaft, 20 diameter maximums, therefore, the edge line speed of seal ring is much larger than the manual transmission of corresponding moment of torsion, thereby causes the safety coefficient of seal ring to descend.
Again it, the arrangement of gears of this invention needs six gear planes, thereby has increased the axial dimension of gearbox.Also have, this invention does not have yet and shows or propose on the Motor Vehicle that its gearbox can be used on rear wheel drive.
Summary of the invention
At above-mentioned prior art, the invention provides a kind of double clutch is multi-functional six speed transmissions of symmetric arrangement, the gearbox of structure of the present invention, and its mechanical efficiency height, gearbox is in light weight, low cost of manufacture, flexibility height; The engine/motor group of using for the optimization and the installation mixed power of torque absorber provides the useful space; This gearbox front end axle sealing structure is reasonable in design, has reduced the possibility of gearbox leakage of oil; Gearbox of the present invention can provide two second gear speed ratios on the basis that does not increase cost; The output gear of this gearbox and two intermediate propeller shafts transmit gear and are in the state of engagement all the time; This gearbox can be used for front-wheel drive, also can be used on the Motor Vehicle of rear wheel drive.
In order to solve the problems of the technologies described above, double clutch of the present invention is that the technological scheme that multi-functional six speed transmissions of symmetric arrangement are achieved is: this gearbox comprises casing and is used for receiving by torque absorber the primary input axle of Engine torque, first intermediate propeller shaft, second intermediate propeller shaft and the output shaft that are arranged in parallel with described primary input axle; Described primary input axle is provided with odd number clutch and the even numbers clutch that is symmetrical distribution on it is axial, and described odd number clutch and even numbers clutch constitute the double clutch assembly, and described double clutch assembly is positioned at the central position of casing; The output shaft of described odd number clutch is provided with first driving gear and the 3rd driving gear, and the output shaft of described even numbers clutch is provided with second driving gear and the 4th driving gear; Above-mentioned two clutches are respectively applied for the moment of torsion that transmits the primary input axle selectively and arrive its corresponding output shaft; Be respectively arranged with six forward gears driven gears and a backward gear driven gear on described first intermediate propeller shaft and described second intermediate propeller shaft, include the first speed driven gear that is arranged on second intermediate propeller shaft in described six forward gears driven gears, the driven gear of described backward gear is arranged on described first intermediate propeller shaft, and the driven gear of described first speed driven gear and backward gear (H1) meshes all the time; Above-mentioned six forward gears driven gears are used for changing selectively described first driving gear, second driving gear, the 3rd driving gear or the 4th driving gear moment of torsion; The end of described first intermediate propeller shaft and second intermediate propeller shaft is respectively arranged with one and transmits gear, and these two output gears that transmit on gear and the output shaft mesh all the time, thereby the moment of torsion after will changing is delivered to output shaft.
Compared with prior art, double clutch of the present invention is that the beneficial effect of multi-functional six speed transmissions of symmetric arrangement is:
(1) compares with the double clutch gearbox of prior art, reduced a parallel axle and two gears, the double clutch among the present invention is a symmetric arrangement arranged side by side, the odd number clutch wherein and the universal component of even numbers clutch, have interchangeability, can reduce manufacture cost;
(2) double clutch of the present invention is arranged in gearbox inside, provides spatial condition for the optimal design of torque absorber and for the electric generator/electric motor group of arranging hybrid power assembly;
(3) rational deployment of double clutch can also be improved the situation of gearbox leakage of oil;
(4) the spatial arrangement scheme of double clutch gearbox gear of the present invention, that is: the space that is positioned at the 4-2 synchronizer right side on the second intermediate propeller shaft A3 is furnished with the second gear driven gear, so that the second gear speed ratio to be provided; Because the gearbox of all vehicles requires the highest to the optimization of second gear speed ratio, the second gear driven gear of a less speed ratio can be arranged in the double clutch gearbox of the present invention and be positioned on the first intermediate propeller shaft A2, and be positioned at the right side of 6-2 synchronizer, can reach the purpose that improves the second gear speed ratio.
(5) gearbox of the present invention also can be with the rear end of the transmission arrangement of gears on two intermediate propeller shafts at corresponding intermediate propeller shaft, make the transmission gear on output gear and two intermediate propeller shafts be in the state of engagement all the time, can be used on the Motor Vehicle of rear wheel drive to realize this gearbox.
Description of drawings
Fig. 1-the 1st, the axial arrangement schematic representation of a kind of double clutch gearbox (CN1621715) in the prior art;
Fig. 1-2 is that the end of gearbox shown in Fig. 1-1 is to the layout structure schematic representation;
Fig. 2-the 1st, the axial arrangement schematic representation of another double clutch gearbox in the prior art (US7490526 B2);
Fig. 2-the 2nd, the end of gearbox is to the layout structure schematic representation shown in Fig. 2-1;
Fig. 3-the 1st, double clutch of the present invention are the axial arrangement schematic representation that multi-functional six speed transmissions of symmetric arrangement are used for an embodiment of front-wheel drive;
Fig. 3-the 2nd, the end of gearbox shown in Fig. 3-1 show the spatial relationship of primary input axle A1, the first intermediate propeller shaft A2, the second intermediate propeller shaft A4 and output shaft A4 to schematic representation;
Fig. 4-the 1st, double clutch of the present invention are the axial arrangement schematic representation that multi-functional six speed transmissions of symmetric arrangement are used for an embodiment of rear wheel drive;
Fig. 4-the 2nd, the end of gearbox shown in Fig. 4-1 show the spatial relationship of primary input axle A1, the first intermediate propeller shaft A2, the second intermediate propeller shaft A4 and output shaft A4 to schematic representation;
Fig. 4-the 3rd, the another end that is gearbox shown in Fig. 4-1 show the spatial relationship of primary input axle A1, the first intermediate propeller shaft A2, the second intermediate propeller shaft A4 and output shaft A4 to schematic representation.The figure illustrates its gearbox and be used in advantage on the low chassis Motor Vehicle.Wherein output shaft A4 is well below primary input axle A1.
Main parts size and specification specified in the gearbox of the present invention:
A1---primary input axle A2---first intermediate propeller shaft
A3---second intermediate propeller shaft A4---output shaft
B---differential mechanism C---double clutch assembly
C1---odd number clutch C2---even numbers clutch
D---vibration damper E1---odd number clutch output shaft
E2---even numbers clutch output shaft F---differential gear
F1, F2---transmission gear G1---first driving gear
G2---second driving gear G3---the 3rd driving gear
G4---the 4th driving gear H1---driven gear of backward gear
H2---1 grade of driven gear Y---hydraulic-pressure pump
Embodiment
Below in conjunction with the drawings and specific embodiments the present invention is done to describe in further detail.
Double clutch of the present invention is that multi-functional six speed transmissions of symmetric arrangement are shown in Fig. 3-1 and Fig. 3-2 as an embodiment of the locomotive that is used for front-wheel drive, comprise casing and four transmission shafts that are arranged in parallel, that is: be used for receiving primary input axle A1 and the first intermediate propeller shaft A2 that is arranged in parallel with described primary input axle A1, the second intermediate propeller shaft A3 and the output shaft A4 of Engine torque by torque absorber; Described primary input axle A1 is provided with odd number clutch C1 and the even numbers clutch C2 that is symmetrical distribution on it is axial, described odd number clutch C1 and even numbers clutch C2 constitute double clutch assembly C, the structure of output shaft E1, the E2 of described two clutch C1, C2 is identical, the universal component of odd number clutch C1 and even numbers clutch C2, have interchangeability, can reduce manufacture cost; Described double clutch assembly C is positioned at the central position of casing, provide spatial condition for the optimal design of torque absorber and for the electric generator/electric motor group of arranging hybrid power assembly, in addition, double clutch assembly C is arranged on the middle position of gearbox, the Seal Design of its gearbox can adopt the Seal Design with traditional manual transmission, therefore, can reduce the possibility of gearbox leakage of oil widely.The output shaft E1 of described odd number clutch C1 is provided with the first driving gear G1 and the 3rd driving gear G3, and the output shaft E2 of described even numbers clutch C2 is provided with the second driving gear G2 and the 4th driving gear G4; Above-mentioned two clutches are respectively applied for the moment of torsion that transmits primary input axle A1 selectively and arrive its corresponding output shaft (E1 and E2); Be respectively arranged with six forward gears driven gears and a backward gear driven gear H1 on described first intermediate propeller shaft A2 and the described second intermediate propeller shaft A3, include the first speed driven gear H2 that is arranged on the second intermediate propeller shaft A3 in described six forward gears driven gears, the driven gear H1 of described backward gear is arranged on the described first intermediate propeller shaft A1, and the driven gear H1 of described first speed driven gear H2 and backward gear meshes all the time; Above-mentioned six forward gears driven gears are used for changing selectively the moment of torsion of the described first driving gear G1, the second driving gear G2, the 3rd driving gear G3 or the 4th driving gear G4; The front end of the described first intermediate propeller shaft A2 and the second intermediate propeller shaft A3 is respectively arranged with one and transmits gear, shown in Fig. 3-2, these two the output gear F that transmit on gear F1, F2 and the output shaft A4 mesh all the time, thereby the moment of torsion after will changing is delivered to output shaft A4.
Be provided with vibration damper D between motor and the primary input axle, described primary input axle A1 drives the shell of hydraulic-pressure pump Y and double clutch assembly C, Engine torque/power is by the primary input axle A1 of torque absorber D input gearbox, primary input axle A1 drives hydraulic-pressure pump Y, the hydraulic pressure that hydraulic-pressure pump Y produces can suit odd number clutch C1 or even numbers clutch C2, and drives 1-3 synchronizer, 4-2 synchronizer, R-5 synchronizer or 6-2 synchronizer respectively to reach the purpose of gear shift.
In sum, double clutch gearbox of the present invention is compared with prior art constructions and has been reduced a parallel axle and two gears, can improve the mechanical efficiency of gearbox, reduce the weight of gearbox, and double clutch is symmetric arrangement arranged side by side, the even numbers clutch wherein and the universal component of odd number clutch, has interchangeability, in like manner, the friction plate that set single double clutch is used in the described clutch assembly with also be identical by the structure of friction plate, have interchangeability.Based on These characteristics, can reduce the manufacture cost of gearbox greatly.
Fig. 4-1 also shows the 6-2 synchronizer right side that is positioned at the first intermediate propeller shaft A2 in the gearbox and also leaves certain space, can make full use of the second gear driven gear that this space is provided with different speed ratios; Because gearbox requires the highest to the optimization of second gear speed ratio, double clutch gearbox of the present invention can move on to the second gear driven gear of a less speed ratio on the first intermediate propeller shaft A2 from having now on the second intermediate propeller shaft A3, and be positioned at the right side of 6-2 synchronizer, to realize a less second gear speed ratio, select for the user.
The working procedure of double clutch gearbox of the present invention is described respectively according to engage a gear, gearshift and the reverse gear of vehicle below:
At first, behind the engine start, hydraulic-pressure pump Y produces oil pressure, and odd number clutch C1 becomes to close situation with even numbers clutch C2 control valve, that is: odd number clutch C1 and even numbers clutch all are the cut-out situation, and this moment, gearbox was a neutral gear.
The vehicle start process puts in the first speed:
The hydraulic control valve body is pushed the 1-3 synchronizer to one grade of driven gear, at this moment, and engagement odd number clutch C1.Engine torque is delivered to the output shaft A4 of gearbox by the differential gear of the first driving gear G1, one grade of driven gear, 1-3 synchronizer, the second intermediate propeller shaft A3, differential mechanism B successively.
The 1-2 gear shift:
The hydraulic control valve body is pushed the 4-2 synchronizer to the second gear driven gear and is reduced the moment of torsion that odd number clutch C1 transmits gradually, meanwhile, strengthens the moment of torsion that even numbers clutch C2 transmits gradually, thereby reaches the gear shift of power failure-free.Behind the 1-2 shift end, Engine torque is delivered to the output shaft A4 of gearbox by the differential gear of the second driving gear G2, second gear driven gear, 4-2 synchronizer, the second intermediate propeller shaft A3, differential mechanism B.
The 2-3 gear shift:
The hydraulic control valve body is pushed the 1-3 synchronizer to the third gear driven gear and is reduced the moment of torsion that even numbers clutch C2 transmits gradually, meanwhile, strengthens the moment of torsion that odd number clutch C1 transmits gradually, thereby reaches the gear shift of power failure-free.Behind the 2-3 shift end, Engine torque is delivered to the output shaft A4 of gearbox by the differential gear of the 3rd driving gear G3, third gear driven gear, 1-3 synchronizer, the second intermediate propeller shaft A3, differential mechanism B.
The 3-4 gear shift:
The hydraulic control valve body is pushed the 4-2 synchronizer to the fourth gear driven gear and is reduced the moment of torsion that odd number clutch C1 transmits gradually, meanwhile, strengthens the moment of torsion that even numbers clutch C2 transmits gradually, thereby reaches the gear shift of power failure-free.Behind the 3-4 shift end, Engine torque is delivered to the output shaft A4 of gearbox by the differential gear of the 4th driving gear G4, fourth gear driven gear, 4-2 synchronizer, the second intermediate propeller shaft A3, differential mechanism B.
The 4-5 gear shift:
The hydraulic control valve body is pushed the R-5 synchronizer to five grades of driven gears and is reduced the moment of torsion that even numbers clutch C2 transmits gradually, meanwhile, strengthens the moment of torsion that odd number clutch C1 transmits gradually, thereby reaches the gear shift of power failure-free.Behind the 4-5 shift end, Engine torque is by the 3rd driving gear G3, five grades of driven gears, R-5 synchronizer, the first intermediate propeller shaft A2, and the differential gear of differential mechanism B is delivered to the output shaft A4 of gearbox.
The 5-6 gear shift:
The hydraulic control valve body is pushed the 6-2 synchronizer to six grades of driven gears and is reduced the moment of torsion that odd number clutch C1 transmits gradually, meanwhile, strengthens the moment of torsion that even numbers clutch C2 transmits gradually, thereby reaches the gear shift of power failure-free.Behind the 5-6 shift end, Engine torque is by the 4th driving gear G4, six grades of passive driven gears, 6-2 synchronizer, the first intermediate propeller shaft A2, and the differential gear of differential mechanism B is delivered to the output shaft A4 of gearbox.
From the principle of shifting from fast to slow and roughly the same last, do not repeat them here.
Change reverse gear:
Car speed is zero, and gearbox is a neutral gear.The hydraulic control valve body is pushed R one 5 synchronizers to reverse gear, engagement odd number clutch C1.As Fig. 3-2, shown in Fig. 4-2 or Fig. 4-3, during reverse gear, the driven gear H1 engagement of R-5 synchronizer and backward gear, at this moment, first speed driven gear H2 rotation on the second intermediate propeller shaft A3, because the driven gear H1 of first speed driven gear H2 and reverse gear meshes all the time, the power of described primary input axle A1 transmission gear F1, the output gear F on the driven gear H1 by the first driving gear G1, first speed driven gear H2, backward gear, R-5 synchronizer, the first intermediate propeller shaft A2 and the differential gear of differential mechanism B successively outputs power.
Because the transmission gear F1 among the present invention on the first intermediate propeller shaft A2 and the second intermediate propeller shaft A3, F2 can be arranged in the end of described two intermediate propeller shaft A2 and A3, as transmitting gear F1, F2 is arranged in the rear end of two intermediate propeller shafts, as Fig. 3-2, shown in Fig. 4-2 and Fig. 4-3, make transmission gear F1 on output gear or differential gear F and two intermediate propeller shafts, F2 meshes all the time, thereby gearbox of the present invention also be can be used on the Motor Vehicle of rear wheel drive, structure when Fig. 4-1, Fig. 4-2 and Fig. 4-3 show double clutch gearbox of the present invention and be applied to rear wheel drive.
In addition, Fig. 4-3 also shows gearbox of the present invention and is used in advantage on the low chassis Motor Vehicle, and its structure is on the basis of gearbox shown in Fig. 4-1 and Fig. 4-2, only an output shaft A4 is wherein got final product far below primary input axle A1.
Although top invention has been described in conjunction with figure; but the present invention is not limited to above-mentioned embodiment; above-mentioned embodiment only is schematic; rather than it is restrictive; those of ordinary skill in the art is under enlightenment of the present invention; under the situation that does not break away from aim of the present invention, can also make a lot of distortion, these all belong within the protection of the present invention.

Claims (10)

1. multi-functional six speed transmissions that double clutch is a symmetric arrangement comprise casing and the primary input axle (A1) that is used to receive Engine torque, it is characterized in that:
First intermediate propeller shaft (A2) that is arranged in parallel with described primary input axle (A1), second intermediate propeller shaft (A3) and final output shaft (A4);
Described primary input axle (A1) is provided with odd number clutch (C1) and the even numbers clutch (C2) that is symmetrical distribution on it is axial, described odd number clutch (C1) and even numbers clutch (C2) constitute double clutch assembly (C), and described double clutch assembly is positioned at the central position of casing; The output shaft (E1) of described odd number clutch (C1) is provided with first driving gear (G1) and the 3rd driving gear (G3), and the output shaft (E2) of described even numbers clutch (C2) is provided with second driving gear (G2) and the 4th driving gear (G4); Above-mentioned two clutches are respectively applied for the moment of torsion that transmits primary input axle (A1) selectively and arrive its corresponding output shaft (E1 and E2);
Be respectively arranged with the driven gear of six forward gearss and the driven gear (H1) of a backward gear on described first intermediate propeller shaft (A2) and described second intermediate propeller shaft (A3), include the first speed driven gear (H2) that is arranged on second intermediate propeller shaft (A3) in described six forward gears driven gears, the driven gear of described backward gear (H1) is arranged on described first intermediate propeller shaft (A1), and described first speed driven gear (H2) meshes all the time with the driven gear (H1) of backward gear; Above-mentioned six forward gears driven gears are used for changing selectively described first driving gear (G1), second driving gear (G2), the 3rd driving gear (G3) or the 4th driving gear (G4) moment of torsion;
The end of described first intermediate propeller shaft (A2) and second intermediate propeller shaft (A3) is respectively arranged with one and transmits gear, these two output gears (F) that transmit on gear (F1, F2) and the output shaft (A4) mesh all the time, thereby the moment of torsion after will changing is delivered to output shaft (A4).
2. double clutch according to claim 1 is multi-functional six speed transmissions of symmetric arrangement, it is characterized in that: the structure of the output shaft (E1, E2) of described two clutches (C1, C2) is identical, has interchangeability.
3. double clutch according to claim 1 is multi-functional six speed transmissions of symmetric arrangement, it is characterized in that: the friction plate that set single double clutch is used in the described clutch assembly (C) has interchangeability with identical by the structure of friction plate.
4. double clutch according to claim 1 is multi-functional six speed transmissions of symmetric arrangement, it is characterized in that: be provided with vibration damper (D) between motor and the described primary input axle (A1), described primary input axle (A1) drives the shell of hydraulic-pressure pump (Y) and double clutch assembly (C).
5. double clutch according to claim 1 is multi-functional six speed transmissions of symmetric arrangement, it is characterized in that: described output shaft (A4) is delivered to power respectively on the left and right sidesing driving wheel of automobile by a differential mechanism (B).
6. double clutch according to claim 1 is multi-functional six speed transmissions of symmetric arrangement, it is characterized in that: be provided with four synchronizers that are used for gear shift or reverse gear, comprise the R-5 synchronizer and the 6-2 synchronizer that are arranged on described first intermediate propeller shaft (A2), be arranged on 1-3 synchronizer and 4-2 synchronizer on described second intermediate propeller shaft (A3).
7. double clutch according to claim 6 is multi-functional six speed transmissions of symmetric arrangement, it is characterized in that: the driven gear (H1) of described first speed driven gear (H2) and described backward gear and the R-5 synchronizer that is used for reverse gear are finished the reverse gear function.
8. be multi-functional six speed transmissions of symmetric arrangement according to claim 6 or 7 described double clutches, it is characterized in that: during reverse gear, the driven gear of R-5 synchronizer and backward gear (H1) engagement, at this moment, first speed driven gear (H2) is gone up rotation at second intermediate propeller shaft (A3), because the driven gear (H1) of first speed driven gear (H2) and reverse gear meshes all the time, the power of described primary input axle (A1) is successively by first driving gear (G1), first speed driven gear (H2), the driven gear of backward gear (H1), the R-5 synchronizer, transmission gear (F1) on first intermediate propeller shaft (A2), the differential gear of output gear (F) or differential mechanism (B) outputs power.
9. according to the described arbitrary double clutch of claim 1 to 8 multi-functional six speed transmissions of symmetric arrangement, it is characterized in that: will be separately positioned on the rear end that transmission gear (F1, F2) on described first intermediate propeller shaft (A2) and second intermediate propeller shaft (A3) is arranged in the place intermediate propeller shaft, in order in the Motor Vehicle of rear wheel drive, to use.
10. double clutch according to claim 1 is multi-functional six speed transmissions of symmetric arrangement, it is characterized in that: the second gear driven gear in described six forward gearss is arranged on second intermediate propeller shaft (A3) or first intermediate propeller shaft (A2).
CN200910069910A 2009-07-27 2009-07-27 Double clutch is multi-functional six speed transmissions of symmetric arrangement Pending CN101614266A (en)

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CN101614266A true CN101614266A (en) 2009-12-30

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102192282A (en) * 2010-03-19 2011-09-21 诺迈士科技有限公司 Dual clutch transmission
CN103277466A (en) * 2013-04-28 2013-09-04 河南科技大学 Multi-clutch speed changer
CN105090383A (en) * 2015-09-14 2015-11-25 崔博琳 Connecting rod pressing wet type mechanical automatic transmission with two clutch mechanisms being arranged inside
CN107867169A (en) * 2016-09-28 2018-04-03 比亚迪股份有限公司 Power-driven system and vehicle for vehicle

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102192282A (en) * 2010-03-19 2011-09-21 诺迈士科技有限公司 Dual clutch transmission
GB2478785A (en) * 2010-03-19 2011-09-21 Romax Technology Ltd Dual clutch mechanism
GB2478785B (en) * 2010-03-19 2013-01-30 Romax Technology Ltd Dual clutch transmission
CN103277466A (en) * 2013-04-28 2013-09-04 河南科技大学 Multi-clutch speed changer
CN103277466B (en) * 2013-04-28 2015-07-15 河南科技大学 Multi-clutch speed changer
CN105090383A (en) * 2015-09-14 2015-11-25 崔博琳 Connecting rod pressing wet type mechanical automatic transmission with two clutch mechanisms being arranged inside
CN107867169A (en) * 2016-09-28 2018-04-03 比亚迪股份有限公司 Power-driven system and vehicle for vehicle

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Application publication date: 20091230