CN204004220U - Double-clutch automatic gearbox - Google Patents
Double-clutch automatic gearbox Download PDFInfo
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- CN204004220U CN204004220U CN201420362954.2U CN201420362954U CN204004220U CN 204004220 U CN204004220 U CN 204004220U CN 201420362954 U CN201420362954 U CN 201420362954U CN 204004220 U CN204004220 U CN 204004220U
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Abstract
A kind of double-clutch automatic gearbox, comprise two input shafts, two output shafts, double clutch, a plurality of driving gear, a plurality of driven gear and a plurality of synchronizers, wherein, a plurality of synchronizers comprise be arranged on the second output shaft and for control 2 grades and 4 grades transmission 2/4 grade of synchronizer and be placed in 4 grades of driven gear synchronizers on the second output shaft, 4 grades of driven gear synchronizers and 2/4 grade of synchronizer are jointly for controlling the transmission of 1 grade; When 1 grade of output, 4 grades of driven gear synchronizers engage with 3,4 grades of driven gears respectively, and 2/4 grade of synchronizer engages with 2 grades of driven gears.The utility model double-clutch automatic gearbox has been realized the object that reduces 1 grade of independent gear pair, and 1 grade of combination by 2 grades and 3 grades is achieved, and for the layout of other component provides axial space, is conducive to the lightweight of speed changer.
Description
Technical field
The utility model relates to automobile technical field, relates in particular to a kind of double-clutch automatic gearbox.
Background technique
The development of current automotive industry, energy-saving and emission-reduction become the main direction of design, car load is got over strictly for the designing requirement of speed changer, thus there is high efficiency, high-comfort double-clutch automatic gearbox becomes development trend gradually.Power train structure in double-clutch automatic gearbox is the important component part of whole speed changer, be also the most important condition of follow-up hardware and software design, so double-clutch speed changer requires also more and more higher to the layout of transmission scheme.In order to improve power character and the Economy of car load, lightweight becomes a developing direction of speed changer, therefore the requirement of transmission scheme is needed to more and more compactness, to meet the arrangement requirement of car load.
In the transmission system of most double-clutch automatic gearbox, the gear demand of 7 advance gear and 1 reverse gear mostly could realize by the gear pair of more group of quantity, axial dimension is longer, and consider that preposition forerunner's automobile is generally all subject to the restriction that very limited axial space is arranged, this will ask the axial dimension of speed changer transmission scheme shorter.For example, 1 grade is generally carried out double-stage driving by a synchronizer, and 1 grade of gear pair must take the axial arranged space of shifting gear, is unfavorable for shortening axial dimension by reducing gear pair.
In addition, existing most of dual-clutch transmission has also adopted reverse gear shaft for realizing reverse gear, because reverse gear is three grades of transmissions, so reverse gear driven gear or reverse idler gear need be arranged in reverse gear shaft (the 3rd axle) above, increased the radial arrangement space of speed changer.
Model utility content
In view of this, embodiment of the present utility model provides a kind of double-clutch automatic gearbox, and this double-clutch automatic gearbox is by cancelling 1 grade of gear pair, and 1 grade of combination by 2 grades and 3 grades is achieved, and can shorten the axial dimension of speed changer.
Embodiment of the present utility model provides a kind of double-clutch automatic gearbox, comprising:
The first input shaft of concentric arrangement and the second input shaft;
The first output shaft of parallel configuration and the second output shaft;
Double clutch, comprises to the first clutch of described the first input shaft transferring power with to the second clutch of described the second input shaft transferring power;
A plurality of odd number shelves driving gears, are fixed on described the first input shaft;
A plurality of even number shelves driving gears, are fixed on described the second input shaft;
A plurality of driven gears, distribute and be placed on described the first output shaft and described the second output shaft, and often mesh with driving gear corresponding on described the first input shaft and described the second input shaft respectively, wherein said a plurality of driven gears comprise and are placed on described the second output shaft and corresponding to 2 grades, 3 grades and 2 grades of driven gears of 4 grades, 3 grades of driven gears and 4 grades of driven gears; And
A plurality of synchronizers, distribute and be arranged on described the first output shaft and described the second output shaft, for controlling the transmission of each gear, described a plurality of synchronizer comprise be arranged on described the second output shaft and for control 2 grades and 4 grades transmission 2/4 grade of synchronizer and be placed in 4 grades of driven gear synchronizers on described the second output shaft, described 4 grades of driven gear synchronizers and described 4 grades of driven gears are fixed together, described 4 grades of driven gear synchronizers and described 2/4 grade of synchronizer are jointly for controlling the transmission of 1 grade, described 4 grades of driven gear synchronizers engage with described 3 grades of driven gears when 1 grade of output, described 2/4 grade of synchronizer engages with described 2 grades of driven gears when 1 grade of output.
Further, described a plurality of odd number shelves driving gears comprise 3/5 grade of driving gear and 7 grades of driving gears, and wherein 3 grades and 5 grades share same driving gear; Described a plurality of even number shelves driving gear comprises 2 grades of driving gears, 4/6 grade of driving gear, and wherein 4 grades and 6 grades share same driving gear; Described a plurality of driven gear also comprises 5 grades of driven gears, 6 grades of driven gears and 7 grades of driven gears, and described 5 grades of driven gears, described 6 grades of driven gears and described 7 grades of driven gears distribute and are placed on described the first output shaft.
Further, described double-clutch automatic gearbox also comprises the reverse driving gear being fixed on described the second input shaft and is placed in the reverse gear driven gear on described the first output shaft, wherein, reverse gear and 2 grades of shared same driving gears, described reverse gear driven gear and described 2 grades of driven gears often mesh.
Further, described double-clutch automatic gearbox also comprises the reverse driving gear being fixed on described the second input shaft and is placed in the reverse gear driven gear on described the first output shaft, wherein, reverse gear and 2 grades of shared same driving gears, described double-clutch automatic gearbox also comprises reverse gear shaft and reverse idler gear, described reverse idler gear is placed on described reverse gear shaft, and described reverse idler gear often meshes with described 2/ reverse driving gear and described reverse gear driven gear respectively.
Further, described a plurality of synchronizer also comprises 3 grades of synchronizers, 5/7 grade of synchronizer and 6/ reversing-gear synchronizer, wherein, described 3 grades of synchronizers are arranged on described the second output shaft and for controlling 3 grades, described 5/7 grade of synchronizer is arranged on described the first output shaft and for controlling 5 grades and 7 grades, and described 6/ reversing-gear synchronizer is arranged on described the first output shaft and for controlling 6 grades and reverse gear.
Further, described a plurality of odd number shelves driving gears comprise 3 grades of driving gears and 5/7 grade of driving gear, and wherein 5 grades and 7 grades share same driving gear; Described a plurality of even number shelves driving gear comprises 2 grades of driving gears and 4/6 grade of driving gear, and wherein 4 grades and 6 grades share same driving gear; Described a plurality of driven gear also comprises 5 grades of driven gears, 6 grades of driven gears and 7 grades of driven gears, and it is upper that described 5 grades of driven gears are placed in described the second output, and described 6 grades of driven gears and described 7 grades of driven gears are placed on described the first output shaft.
Further, described double-clutch automatic gearbox also comprises the reverse driving gear being fixed on described the second input shaft and is placed in the reverse gear driven gear on described the first output shaft, wherein, reverse gear and 2 grades of shared same driving gears, described reverse gear driven gear and described 2 grades of driven gears often mesh.
Further, described double-clutch automatic gearbox also comprises the reverse driving gear being fixed on described the second input shaft and is placed in the reverse gear driven gear on described the first output shaft, wherein, reverse gear and 2 grades of shared same driving gears, described double-clutch automatic gearbox also comprises reverse gear shaft and reverse idler gear, described reverse idler gear is placed on described reverse gear shaft, and described reverse idler gear often meshes with described 2/ reverse driving gear and described reverse gear driven gear respectively.
Further, described a plurality of synchronizer also comprises 3/5 grade of synchronizer, 7 grades of synchronizers and 6/ reversing-gear synchronizer, wherein, described 3/5 grade of synchronizer is arranged on described the second output shaft and for controlling 3 grades and 5 grades, described 7 grades of synchronizers are arranged on described the first output shaft and for controlling 7 grades, and described 6/ reversing-gear synchronizer is arranged on described the first output shaft and for controlling 6 grades and reverse gear.
Further, described double-clutch automatic gearbox also comprises differential mechanism gear ring, the first final gear and the second final gear, described the first final gear is fixed on described the first output shaft, described the second final gear is fixed on described the second output shaft, and the second final gear on the first final gear on described the first output shaft and described the second output shaft often meshes with described differential mechanism gear ring respectively.
The beneficial effect that the technological scheme that embodiment of the present utility model provides is brought is:
(1), the utility model has been realized the object that reduces 1 grade of independent gear pair, 1 grade of combination by 2 grades and 3 grades is achieved, by omitting 1 grade of gear pair, can shorten the axial dimension of speed changer, 1 grade of speed ratio is realized jointly by 2 grades of speed ratios and 3 grades of speed ratios simultaneously, thereby 1 grade of speed ratio that the scope that can obtain is larger, simultaneously, reverse gear also can obtain reverse gear ratio in a big way by sharing 2 grades of gears, sufficient tractive force requirement while having guaranteed compared with large speed ratio, improved 1 grade and reverse gear as starting gear the enough tractive force when the starting, while having reduced vehicle starting, the heat load requirement of the clutch friction material while especially starting to walk under the bad working environments such as ramp.
(2), the utility model can be by cancelling reverse gear shaft, the radial space of saving further speed changer, makes speed changer compacter.
(3), the utility model shares driving gear by a plurality of gears, further shortened the axial space of speed changer, the utility model utilizes 5 synchronizers to realize 7 forward gears and 1 reverse gear.
(4), the utility model is by two input shafts, two forms that output shaft is arranged in parallel, are arranged in odd number shelves on the first input shaft, even number shelves are arranged on the second input shaft, can realize the pre-hung function of double-clutch speed changer.
Accompanying drawing explanation
Fig. 1 is the overall structure schematic diagram of the utility model the first embodiment's double-clutch automatic gearbox.
Fig. 2 is the overall structure schematic diagram of the utility model the second embodiment's double-clutch automatic gearbox.
Fig. 3 is the overall structure schematic diagram of the utility model the 3rd embodiment's double-clutch automatic gearbox.
Fig. 4 is the overall structure schematic diagram of the utility model the 4th embodiment's double-clutch automatic gearbox.
Embodiment
For making the purpose of this utility model, technological scheme and advantage clearer, below in conjunction with accompanying drawing, the utility model mode of execution is further described.
Although the utility model is described different elements with first, second term such as grade, these elements are not subject to the restriction of these terms, and these terms are only for an element and another element region are separated.
The first embodiment
Please refer to Fig. 1, a kind of double-clutch automatic gearbox that the utility model the first embodiment provides, comprising:
The first input shaft 1 of concentric arrangement and the second input shaft 2;
The first output shaft 3 of parallel configuration and the second output shaft 4;
Double clutch, comprises to the first clutch K1 of the first input shaft 1 transferring power with to the second clutch K2 of the second input shaft 2 transferring power;
A plurality of odd number shelves driving gears, are formed by the driving gear of odd number shelves, and are fixed on the first input shaft 1;
A plurality of even number shelves driving gears, are formed by the driving gear of even number shelves, and are fixed on the second input shaft 2;
A plurality of driven gears, distribute and be placed on the first output shaft 3 and the second output shaft 4, be that wherein a part of driven gear in the plurality of driven gear is placed on the first output shaft 3, and remaining other a part of driven gear is placed on the second output shaft 4, the plurality of driven gear often meshes with driving gear corresponding on the first input shaft 1 and the second input shaft 2 respectively, and wherein the plurality of driven gear comprises and is placed on the second output shaft 4 and corresponds respectively to 2 grades, 3 grades and 2 grades of driven gear 2b of 4 grades, 3 grades of driven gear 3b and 4 grades of driven gear 4b; And
A plurality of synchronizers, distribute and be arranged on the first output shaft 3 and the second output shaft 4, for controlling the transmission of each gear, be that wherein a part of synchronizer in the plurality of synchronizer is arranged on the first output shaft 3, and remaining other a part of synchronizer is arranged on the second output shaft 4, the plurality of synchronizer comprise be arranged on the second output shaft 4 and for control 2 grades and 4 grades transmission 2/4 grade of synchronizer 6 and be placed in 4 grades of driven gear synchronizers 10 on the second output shaft 4, 4 grades of driven gear synchronizers 10 and 4 grades of driven gear 4b are fixed together, 4 grades of driven gear synchronizers 10 and 2/4 grade of synchronizer 6 are common for controlling the transmission of 1 grade, 4 grades of driven gear synchronizers 10 engage with 3 grades of driven gear 3b when 1 grade of output, 2/4 grade of synchronizer 6 engages with 2 grades of driven gear 2b when 1 grade of output.
Further, the plurality of odd number shelves driving gear comprises 3/5 grade of driving gear 3a and 7 grades of driving gear 7a, and wherein 3 grades and 5 grades share same driving gear 3a; The plurality of even number shelves driving gear comprises 2 grades of driving gear 2a and 4/6 grade of driving gear 4a, and wherein 4 grades and 6 grades share same driving gear 4a; The plurality of driven gear also comprises 5 grades of driven gear 3c, 6 grades of driven gear 4c and 7 grades of driven gear 7b, and wherein 5 grades of driven gear 3c, 6 grades of driven gear 4c and 7 grades of driven gear 7b distribute and are placed on the first output shaft 3.
Further, the utility model the first embodiment's double-clutch automatic gearbox, also comprise the reverse driving gear 2a being fixed on the second input shaft 2 and be placed in the reverse gear driven gear 2c on the first output shaft 3, wherein reverse gear and 2 grades share same driving gear 2a, and reverse gear driven gear 2c and 2 grades of driven gear 2b often mesh.
Further, the plurality of synchronizer also comprises 7,5/7 grade of synchronizer 8 of 3 grades of synchronizers and 6/ reversing-gear synchronizer 9, wherein, 3 grades of synchronizers 7 are arranged on the second output shaft 4 and for controlling 3 grades, 5/7 grade of synchronizer 8 is arranged on the first output shaft 3 and for controlling 5 grades and 7 grades, and 6/ reversing-gear synchronizer 9 is arranged on the first output shaft 3 and for controlling 6 grades and reverse gear; Wherein, 4 grades of driven gear synchronizers 10 and 3 grades of synchronizers 7 are Unilateral synchronizer, and 6,5/7 grade of synchronizer 8 of 2/4 grade of synchronizer and 6/ reversing-gear synchronizer 9 are bilateral synchronous device.
Further, the both sides of 3 grades of driven gear 3b are respectively equipped with the first soldered tooth and the second soldered tooth, wherein the first soldered tooth is arranged on the right side of illustrated 3 grades of driven gear 3b and engages with 4 grades of driven gear synchronizers 10 when 1 grade of output, and the second soldered tooth is arranged on the left side of illustrated 3 grades of driven gear 3b and engages with 3 grades of synchronizers 7 when 3 grades of output.
Further, the double-clutch automatic gearbox that the utility model embodiment provides, also comprises differential mechanism gear ring 11 for receiving outputting power, is fixedly connected with differential mechanism gear ring 11 and for differential mechanism, the first final gear 12a and the second final gear 12b of outputting power.The first final gear 12a and the first output shaft 3 are fixed together, and can rotate along with the rotation of the first output shaft 3; The second final gear 12b and the second output shaft 4 are fixed together, and can rotate along with the rotation of the second output shaft 4.The first final gear 12a and the second final gear 12b on the second output shaft 4 on the first output shaft 3 often mesh with differential mechanism gear ring 11 respectively.
Below introduce the power transmission line that each gear of the utility model the first embodiment's double-clutch automatic gearbox is controlled.
(1), 1 grade of power transmission line: 3/5 grade of driving gear 3a often meshes with 3 grades of driven gear 3b and 5 grades of driven gear 3c respectively, when 1 grade of output of needs, 4 grades of driven gear synchronizers 10 engage with first soldered tooth on the right side of 3 grades of driven gear 3b, 2/4 grade of synchronizer 6 engages with 2 grades of driven gear 2b, because the tooth hub of 4 grades of driven gear synchronizers 10 is fixedly connected with 4 grades of driven gear 4b, make power pass to the first input shaft 1 by first clutch K1, by 3/5 grade of driving gear 3a on the first input shaft 1, pass to 3 grades of driven gear 3b, by 4 grades of driven gear synchronizers 10, pass to 4 grades of driven gear 4b again, then through 4 grades of driven gear 4b, pass to 4/6 grade of driving gear 4a, then by 4/6 grade of driving gear 4a, pass to the second input shaft 2, by 2/ reverse driving gear 2a on the second input shaft 2, pass to 2 grades of driven gear 2b again, through 2/4 grade of synchronizer 6, be passed to the second output shaft 4, by the second final gear 12b, be passed to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
(2), 2 grades of power transmission lines: 2/ reverse driving gear 2a and 2 grades of driven gear 2b often mesh, when 2 grades of output of needs, 2/4 grade of synchronizer 6 engages with 2 grades of driven gear 2b, make power pass to the second input shaft 2 by second clutch K2, by 2/ reverse driving gear 2a on the second input shaft 2, pass to 2 grades of driven gear 2b, through 2/4 grade of synchronizer 6, be passed to the second output shaft 4, by the second final gear 12b, be passed to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
(3), 3 grades and 5 grades of power transmission lines: 3/5 grade of driving gear 3a often meshes with 3 grades of driven gear 3b and 5 grades of driven gear 3c respectively, when 3 grades of output of needs, 3 grades of synchronizers 7 engage with second soldered tooth in the left side of 3 grades of driven gear 3b, make power pass to the first input shaft 1 by first clutch K1, by 3/5 grade of driving gear 3a on the first input shaft 1, pass to 3 grades of driven gear 3b, through 3 grades of synchronizers 7, be passed to the second output shaft 4, by the second final gear 12b, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, again by wheel outputting power, when 5 grades of output of needs, 5/7 grade of synchronizer 8 engages with 5 grades of driven gear 3c, make power pass to the first input shaft 1 by first clutch K1, by 3/5 grade of driving gear 3a on the first input shaft 1, pass to 5 grades of driven gear 3c, through 5/7 grade of synchronizer 8, be passed to the first output shaft 3, by the first final gear 12a, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
(4), 4 grades and 6 grades of power transmission lines: 4/6 grade of driving gear 4a often meshes with 4 grades of driven gear 4b and 6 grades of driven gear 4c respectively, when 4 grades of output of needs, 2/4 grade of synchronizer 6 engages with 4 grades of driven gear 4b, make power pass to the second input shaft 2 by second clutch K2, by 4/6 grade of driving gear 4a on the second input shaft 2, pass to 4 grades of driven gear 4b, through 2/4 grade of synchronizer 6, be passed to the second output shaft 4, by the second final gear 12b, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, again by wheel outputting power, when 6 grades of output of needs, 6/ reversing-gear synchronizer 9 engages with 6 grades of driven gear 4c, make power pass to the second input shaft 2 by second clutch K2, by 4/6 grade of driving gear 4a on the second input shaft 2, pass to 6 grades of driven gear 4c, through 6/ reversing-gear synchronizer 9, be passed to the first output shaft 3, by the first final gear 12a, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
(5), 7 grades of power transmission lines: 7 grades of driving gear 7a and 7 grades of driven gear 7b often mesh, when 7 grades of output of needs, 5/7 grade of synchronizer 8 engages with 7 grades of driven gear 7b, make power pass to the first input shaft 1 by first clutch K1, by 7 grades of driving gear 7a on the first input shaft 1, pass to 7 grades of driven gear 7b, through 5/7 grade of synchronizer 8, be passed to the first output shaft 3, by the first final gear 12a, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
(6), reverse gear power transmission line: 2/ reverse driving gear 2a and 2 grades of driven gear 2b often mesh, and 2 grades of driven gear 2b and reverse gear driven gear 2c often mesh, when needs reverse gear is exported, 6/ reversing-gear synchronizer 9 engages with reverse gear driven gear 2c, make power pass to the second input shaft 2 by second clutch K2, by 2/ reverse driving gear 2a on the second input shaft 2, pass to 2 grades of driven gear 2b, through 2 grades of driven gear 2b, pass to reverse gear driven gear 2c, through 6/ reversing-gear synchronizer 9, be passed to the first output shaft 3 again, by the first final gear 12a, pass to differential mechanism gear ring 11 again, via differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
The second embodiment
Please refer to Fig. 2, a kind of double-clutch automatic gearbox that the utility model the second embodiment provides, itself and above-mentioned the first embodiment's difference is mainly arranging of reverse gear.In a second embodiment, also comprise reverse gear shaft 5 and reverse idler gear 2d, reverse gear shaft 5 and the first output shaft 3 and the second output shaft 4 parallel configuration, reverse idler gear 2d is placed on reverse gear shaft 5, reverse idler gear 2d often meshes with 2/ reverse driving gear 2a and reverse gear driven gear 2c respectively, and reverse gear driven gear 2c does not often mesh with 2 grades of driven gear 2b.
In a second embodiment, the power transmission line of reverse gear is: reverse idler gear 2d often meshes with 2/ reverse driving gear 2a and reverse gear driven gear 2c respectively, when needs reverse gear is exported, 6/ reversing-gear synchronizer 9 engages with reverse gear driven gear 2c, make power pass to the second input shaft 2 by second clutch K2, by 2/ reverse driving gear 2a on the second input shaft 2, pass to reverse idler gear 2d, through reverse idler gear 2d, pass to reverse gear driven gear 2c, through 6/ reversing-gear synchronizer 9, be passed to the first output shaft 3 again, by the first final gear 12a, pass to differential mechanism gear ring 11 again, via differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
About all the other structures of the second embodiment and the power transmission line of all the other each gears, can, referring to the first embodiment, not repeat them here.
The 3rd embodiment
Please refer to Fig. 3, a kind of double-clutch automatic gearbox that the utility model the 3rd embodiment provides, itself and above-mentioned the first embodiment's difference is mainly in the transmission of power of the setting of 5 grades and 5 grades.In the 3rd embodiment, a plurality of odd number shelves driving gears that are fixed on the first input shaft 1 comprise 3 grades of driving gear 3a and 5/7 grade of driving gear 5a, and wherein 5 grades and 7 grades share same driving gear 5a; A plurality of even number shelves driving gears that are fixed on the second input shaft 2 comprise 2/ reverse driving gear 2a and 4/6 grade of driving gear 4a, and wherein 2 grades share same driving gear 2a with reverse gear, and 4 grades and 6 grades share same driving gear 4a; A plurality of driven gears comprise 2 grades of driven gear 2b, 3 grades of driven gear 3b, 4 grades of driven gear 4b, 5 grades of driven gear 5b, 6 grades of driven gear 4c, 7 grades of driven gear 5c and reverse gear driven gear 2c, wherein 2 grades of driven gear 2b, 3 grades of driven gear 3b, 4 grades of driven gear 4b and 5 grades of driven gear 5b are placed on the second output shaft 4, and 6 grades of driven gear 4c, 7 grades of driven gear 5c and reverse gear driven gear 2c are placed on the first output shaft 3; A plurality of synchronizers comprise 13,7 grades of synchronizers 14 of 10,3/5 grade of synchronizer of 6,4 grades of driven gear synchronizers of 2/4 grade of synchronizer and 6/ reversing-gear synchronizer 9, wherein, 2/4 grade of synchronizer 6 is arranged on the second output shaft 4 and for controlling 2 grades and 4 grades, 3/5 grade of synchronizer 13 is arranged on the second output shaft 4 and for controlling 3 grades and 5 grades, 7 grades of synchronizers 14 are arranged on the first output shaft 3 and for controlling 7 grades, and 6/ reversing-gear synchronizer 9 is arranged on the first output shaft 3 and for controlling 6 grades and reverse gear; 4 grades of driven gear synchronizers 10 are placed on the second output shaft 4 and with 4 grades of driven gear 4b and are fixed together, and 4 grades of driven gear synchronizers 10 and 2/4 grade of synchronizer 6 are common for controlling the transmission of 1 grade.4 grades of driven gear synchronizers 10 and 7 grades of synchronizers 14 are Unilateral synchronizer, and 6,3/5 grade of synchronizer 13 of 2/4 grade of synchronizer and 6/ reversing-gear synchronizer 9 are bilateral synchronous device.
All the other structures about the 3rd embodiment can, with further reference to the first embodiment, not repeat them here.
Below introduce the power transmission line that each gear of the utility model the 3rd embodiment's double-clutch automatic gearbox is controlled.
(1), 1 grade of power transmission line: 3 grades of driving gear 3a and 3 grades of driven gear 3b often mesh, when 1 grade of output of needs, 4 grades of driven gear synchronizers 10 engage with first soldered tooth on the right side of 3 grades of driven gear 3b, 2/4 grade of synchronizer 6 engages with 2 grades of driven gear 2b, because the tooth hub of 4 grades of driven gear synchronizers 10 is fixedly connected with 4 grades of driven gear 4b, make power pass to the first input shaft 1 by first clutch K1, by 3 grades of driving gear 3a on the first input shaft 1, pass to 3 grades of driven gear 3b, by 4 grades of driven gear synchronizers 10, pass to 4 grades of driven gear 4b again, then through 4 grades of driven gear 4b, pass to 4/6 grade of driving gear 4a, then by 4/6 grade of driving gear 4a, pass to the second input shaft 2, by 2/ reverse driving gear 2a on the second input shaft 2, pass to 2 grades of driven gear 2b again, through 2/4 grade of synchronizer 6, be passed to the second output shaft 4, by the second final gear 12b, be passed to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
(2), 2 grades of power transmission lines: 2/ reverse driving gear 2a and 2 grades of driven gear 2b often mesh, when 2 grades of output of needs, 2/4 grade of synchronizer 6 engages with 2 grades of driven gear 2b, make power pass to the second input shaft 2 by second clutch K2, by 2/ reverse driving gear 2a on the second input shaft 2, pass to 2 grades of driven gear 2b, through 2/4 grade of synchronizer 6, be passed to the second output shaft 4, by the second final gear 12b, be passed to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
(3), 3 grades of power transmission lines: 3 grades of driving gear 3a and 3 grades of driven gear 3b often mesh, when 3 grades of output of needs, 3/5 grade of synchronizer 13 engages with 3 grades of driven gear 3b, make power pass to the first input shaft 1 by first clutch K1, by 3 grades of driving gear 3a on the first input shaft 1, pass to 3 grades of driven gear 3b, through 3/5 grade of synchronizer 13, be passed to the second output shaft 4, by the second final gear 12b, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, then by wheel outputting power.
(4), 4 grades and 6 grades of power transmission lines: 4/6 grade of driving gear 4a often meshes with 4 grades of driven gear 4b and 6 grades of driven gear 4c respectively, when 4 grades of output of needs, 2/4 grade of synchronizer 6 engages with 4 grades of driven gear 4b, make power pass to the second input shaft 2 by second clutch K2, by 4/6 grade of driving gear 4a on the second input shaft 2, pass to 4 grades of driven gear 4b, through 2/4 grade of synchronizer 6, be passed to the second output shaft 4, by the second final gear 12b, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, again by wheel outputting power, when 6 grades of output of needs, 6/ reversing-gear synchronizer 9 engages with 6 grades of driven gear 4c, make power pass to the second input shaft 2 by second clutch K2, by 4/6 grade of driving gear 4a on the second input shaft 2, pass to 6 grades of driven gear 4c, through 6/ reversing-gear synchronizer 9, be passed to the first output shaft 3, by the first final gear 12a, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
(5), 5 grades and 7 grades of power transmission lines: 5/7 grade of driving gear 5a often meshes with 5 grades of driven gear 5b and 7 grades of driven gear 5c respectively, when 5 grades of output of needs, 3/5 grade of synchronizer 13 engages with 5 grades of driven gear 3c, make power pass to the first input shaft 1 by first clutch K1, by 5/7 grade of driving gear 5a on the first input shaft 1, pass to 5 grades of driven gear 5b, through 3/5 grade of synchronizer 13, be passed to the second output shaft 4, by the second final gear 12b, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power, when 7 grades of output of needs, 7 grades of synchronizers 14 engage with 7 grades of driven gear 5c, make power pass to the first input shaft 1 by first clutch K1, by 5/7 grade of driving gear 5a on the first input shaft 1, pass to 7 grades of driven gear 5c, through 7 grades of synchronizers 14, be passed to the first output shaft 3, by the first final gear 12a, pass to differential mechanism gear ring 11 again, finally by by differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
(6), reverse gear power transmission line: 2/ reverse driving gear 2a and 2 grades of driven gear 2b often mesh, and 2 grades of driven gear 2b and reverse gear driven gear 2c often mesh, when needs reverse gear is exported, 6/ reversing-gear synchronizer 9 engages with reverse gear driven gear 2c, make power pass to the second input shaft 2 by second clutch K2, by 2/ reverse driving gear 2a on the second input shaft 2, pass to 2 grades of driven gear 2b, through 2 grades of driven gear 2b, pass to reverse gear driven gear 2c, through 6/ reversing-gear synchronizer 9, be passed to the first output shaft 3 again, by the first final gear 12a, pass to differential mechanism gear ring 11 again, via differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
The 4th embodiment
Please refer to Fig. 4, a kind of double-clutch automatic gearbox that the utility model the 4th embodiment provides, itself and above-mentioned the 3rd embodiment's difference is mainly arranging of reverse gear.In the 4th embodiment, also comprise reverse gear shaft 5 and reverse idler gear 2d, reverse gear shaft 5 and the first output shaft 3 and the second output shaft 4 parallel configuration, reverse idler gear 2d is placed on reverse gear shaft 5, reverse idler gear 2d often meshes with 2/ reverse driving gear 2a and reverse gear driven gear 2c respectively, and reverse gear driven gear 2c does not often mesh with 2 grades of driven gear 2b.
In the 4th embodiment, the power transmission line of reverse gear is: reverse idler gear 2d often meshes with 2/ reverse driving gear 2a and reverse gear driven gear 2c respectively, when needs reverse gear is exported, 6/ reversing-gear synchronizer 9 engages with reverse gear driven gear 2c, make power pass to the second input shaft 2 by second clutch K2, by 2/ reverse driving gear 2a on the second input shaft 2, pass to reverse idler gear 2d, through reverse idler gear 2d, pass to reverse gear driven gear 2c, through 6/ reversing-gear synchronizer 9, be passed to the first output shaft 3 again, by the first final gear 12a, pass to differential mechanism gear ring 11 again, via differential mechanism gear ring 11 by transmission of power to differential mechanism, by wheel outputting power.
About all the other structures of the 4th embodiment and the power transmission line of all the other each gears, can, referring to the 3rd embodiment, not repeat them here.
The utility model is executed example and is had following beneficial effect:
(1), the utility model has been realized the object that reduces 1 grade of independent gear pair, 1 grade of combination by 2 grades and 3 grades is achieved, by omitting 1 grade of gear pair, can shorten the axial dimension of speed changer, 1 grade of speed ratio is realized jointly by 2 grades of speed ratios and 3 grades of speed ratios simultaneously, thereby 1 grade of speed ratio that the scope that can obtain is larger, simultaneously, reverse gear also can obtain reverse gear ratio in a big way by sharing 2 grades of gears, sufficient tractive force requirement while having guaranteed compared with large speed ratio, improved 1 grade and reverse gear as starting gear the enough tractive force when the starting, while having reduced vehicle starting, the heat load requirement of the clutch friction material while especially starting to walk under the bad working environments such as ramp.
(2), the utility model can be by cancelling reverse gear shaft (as the first embodiment and the 3rd embodiment), the radial space of saving further speed changer, makes speed changer compacter.
(3), the utility model shares driving gear by a plurality of gears, further shortened the axial dimension of speed changer, the utility model utilizes 5 synchronizers to realize 7 forward gears and 1 reverse gear.
(4), the utility model is by two input shafts, two forms that output shaft is arranged in parallel, are arranged in odd number shelves on the first input shaft, even number shelves are arranged on the second input shaft, can realize the pre-hung function of double-clutch speed changer.
The foregoing is only preferred embodiment of the present utility model, not in order to limit the utility model, all within spirit of the present utility model and principle, any modification of doing, be equal to replacement, improvement etc., within all should being included in protection domain of the present utility model.
Claims (10)
1. a double-clutch automatic gearbox, is characterized in that, comprising:
First input shaft (1) of concentric arrangement and the second input shaft (2);
First output shaft (3) of parallel configuration and the second output shaft (4);
Double clutch, comprises to the first clutch (K1) of described the first input shaft (1) transferring power with to the second clutch (K2) of described the second input shaft (2) transferring power;
A plurality of odd number shelves driving gears, are fixed on described the first input shaft (1);
A plurality of even number shelves driving gears, are fixed on described the second input shaft (2);
A plurality of driven gears, distribute and be placed on described the first output shaft (3) and described the second output shaft (4), and often mesh with the upper corresponding driving gear of described the first input shaft (1) and described the second input shaft (2) respectively, wherein said a plurality of driven gears comprise that to be placed in described the second output shaft (4) upper and correspond respectively to 2 grades of driven gears (2b), 3 grades of driven gears (3b) and 4 grades of driven gears (4b) of 2 grades, 3 grades and 4 grades; And
A plurality of synchronizers, distribute and be arranged on described the first output shaft (3) and described the second output shaft (4), for controlling the transmission of each gear, described a plurality of synchronizer comprise be arranged at described the second output shaft (4) upper and for control 2 grades and 4 grades transmission 2/4 grade of synchronizer (6) and be placed in the 4 grades of driven gear synchronizers (10) on described the second output shaft (4), described 4 grades of driven gear synchronizers (10) are fixed together with described 4 grades of driven gears (4b), described 4 grades of driven gear synchronizers (10) are common for controlling the transmission of 1 grade with described 2/4 grade of synchronizer (6), described 4 grades of driven gear synchronizers (10) engage with described 3 grades of driven gears (3b) when 1 grade of output, described 2/4 grade of synchronizer (6) engages with described 2 grades of driven gears (2b) when 1 grade of output.
2. double-clutch automatic gearbox as claimed in claim 1, it is characterized in that: described a plurality of odd number shelves driving gears comprise 3/5 grade of driving gear (3a) and 7 grades of driving gears (7a), wherein 3 grades and 5 grades share same driving gear (3a); Described a plurality of even number shelves driving gear comprises 2 grades of driving gears (2a) and 4/6 grade of driving gear (4a), and wherein 4 grades and 6 grades share same driving gear (4a); Described a plurality of driven gear also comprises 5 grades of driven gears (3c), 6 grades of driven gears (4c) and 7 grades of driven gears (7b), and described 5 grades of driven gears (3c), described 6 grades of driven gears (4c) and described 7 grades of driven gears (7b) distribute and are placed on described the first output shaft (3).
3. double-clutch automatic gearbox as claimed in claim 2, it is characterized in that: described double-clutch automatic gearbox also comprises the reverse driving gear (2a) being fixed on described the second input shaft (2) and is placed in the reverse gear driven gear (2c) on described the first output shaft (3), wherein, reverse gear and 2 grades of shared same driving gears (2a), described reverse gear driven gear (2c) often meshes with described 2 grades of driven gears (2b).
4. double-clutch automatic gearbox as claimed in claim 2, it is characterized in that: described double-clutch automatic gearbox also comprises the reverse driving gear (2a) being fixed on described the second input shaft (2) and is placed in the reverse gear driven gear (2c) on described the first output shaft (3), wherein, reverse gear and 2 grades of shared same driving gears (2a), described double-clutch automatic gearbox also comprises reverse gear shaft (5) and reverse idler gear (2d), described reverse idler gear (2d) is placed on described reverse gear shaft (5), described reverse idler gear (2d) often meshes with described 2/ reverse driving gear (2a) and described reverse gear driven gear (2c) respectively.
5. the double-clutch automatic gearbox as described in claim 3 or 4, it is characterized in that: described a plurality of synchronizers also comprise 3 grades of synchronizers (7), 5/7 grade of synchronizer (8) and 6/ reversing-gear synchronizer (9), wherein, described 3 grades of synchronizers (7) are arranged on described the second output shaft (4) and for controlling 3 grades, described 5/7 grade of synchronizer (8) is arranged on described the first output shaft (3) and for controlling 5 grades and 7 grades, and described 6/ reversing-gear synchronizer (9) is arranged on described the first output shaft (3) and for controlling 6 grades and reverse gear.
6. double-clutch automatic gearbox as claimed in claim 1, it is characterized in that: described a plurality of odd number shelves driving gears comprise 3 grades of driving gears (3a) and 5/7 grade of driving gear (5a), wherein 5 grades and 7 grades share same driving gear (5a); Described a plurality of even number shelves driving gear comprises 2 grades of driving gears (2a) and 4/6 grade of driving gear (4a), and wherein 4 grades and 6 grades share same driving gear (4a); Described a plurality of driven gear also comprises 5 grades of driven gears (5b), 6 grades of driven gears (4c) and 7 grades of driven gears (5c), it is upper that described 5 grades of driven gears (5b) are placed in described the second output shaft (4), and described 6 grades of driven gears (4c) and described 7 grades of driven gears (5c) are placed on described the first output shaft (3).
7. double-clutch automatic gearbox as claimed in claim 6, it is characterized in that: described double-clutch automatic gearbox also comprises the reverse driving gear (2a) being fixed on described the second input shaft (2) and is placed in the reverse gear driven gear (2c) on described the first output shaft (3), wherein, reverse gear and 2 grades of shared same driving gears (2a), described reverse gear driven gear (2c) often meshes with described 2 grades of driven gears (2b).
8. double-clutch automatic gearbox as claimed in claim 6, it is characterized in that: described double-clutch automatic gearbox also comprises the reverse driving gear (2a) being fixed on described the second input shaft (2) and is placed in the reverse gear driven gear (2c) on described the first output shaft (3), wherein, reverse gear and 2 grades of shared same driving gears (2a), described double-clutch automatic gearbox also comprises reverse gear shaft (5) and reverse idler gear (2d), described reverse idler gear (2d) is placed on described reverse gear shaft (5), described reverse idler gear (2d) often meshes with described 2/ reverse driving gear (2a) and described reverse gear driven gear (2c) respectively.
9. double-clutch automatic gearbox as claimed in claim 7 or 8, it is characterized in that: described a plurality of synchronizers also comprise 3/5 grade of synchronizer (13), 7 grades of synchronizers (14) and 6/ reversing-gear synchronizer (9), wherein, described 3/5 grade of synchronizer (13) is arranged on described the second output shaft (4) and for controlling 3 grades and 5 grades, described 7 grades of synchronizers (14) are arranged on described the first output shaft (3) and for controlling 7 grades, and described 6/ reversing-gear synchronizer (9) is arranged on described the first output shaft (3) and for controlling 6 grades and reverse gear.
10. double-clutch automatic gearbox as claimed in claim 1, it is characterized in that: described double-clutch automatic gearbox also comprises differential mechanism gear ring (11), the first final gear (12a) and the second final gear (12b), described the first final gear (12a) is fixed on described the first output shaft (3), described the second final gear (12b) is fixed on described the second output shaft (4), the first final gear (12a) and the second final gear (12b) on described the second output shaft (4) on described the first output shaft (3) often mesh with described differential mechanism gear ring (11) respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420362954.2U CN204004220U (en) | 2014-07-02 | 2014-07-02 | Double-clutch automatic gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420362954.2U CN204004220U (en) | 2014-07-02 | 2014-07-02 | Double-clutch automatic gearbox |
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| Publication Number | Publication Date |
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| CN204004220U true CN204004220U (en) | 2014-12-10 |
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| CN201420362954.2U Active CN204004220U (en) | 2014-07-02 | 2014-07-02 | Double-clutch automatic gearbox |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108036028A (en) * | 2017-11-09 | 2018-05-15 | 宁波上中下自动变速器有限公司 | The transmission device and double-clutch speed changer of a kind of double-clutch speed changer |
| CN111379832A (en) * | 2018-12-27 | 2020-07-07 | 长城汽车股份有限公司 | Single output shaft transmission |
-
2014
- 2014-07-02 CN CN201420362954.2U patent/CN204004220U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108036028A (en) * | 2017-11-09 | 2018-05-15 | 宁波上中下自动变速器有限公司 | The transmission device and double-clutch speed changer of a kind of double-clutch speed changer |
| CN111379832A (en) * | 2018-12-27 | 2020-07-07 | 长城汽车股份有限公司 | Single output shaft transmission |
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