CN102425647B - Power transmission mechanism for double-clutch automatic transmission - Google Patents
Power transmission mechanism for double-clutch automatic transmission Download PDFInfo
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- CN102425647B CN102425647B CN2011103899612A CN201110389961A CN102425647B CN 102425647 B CN102425647 B CN 102425647B CN 2011103899612 A CN2011103899612 A CN 2011103899612A CN 201110389961 A CN201110389961 A CN 201110389961A CN 102425647 B CN102425647 B CN 102425647B
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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
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Abstract
The invention relates to a power transmission mechanism for a double-clutch automatic transmission for an automobile. The power transmission mechanism comprises a power input shaft, an odd shift clutch input shaft, a first auxiliary shaft, a second auxiliary shaft, a middle shaft, a reverse gear idler shaft, an odd shift clutch, an even shift clutch, and a differential; the left end of the power input shaft is provided with a sun gear, a planetary gear, an internal gear ring, and a fixed planet carrier; an internal gear ring external gear is fixed outside the internal gear ring; the second auxiliary shaft is provided with an even shift driving gear, a reverse gear driving gear and an even shift synchronizer; the middle shaft is provided with a driven gear and first and second reverse gear driven gears; and the reverse gear idler shaft is provided with first and second reverse gear idler gears. The transmission mechanism is simple and is high in integrated level, and manufacturing cost of the double-clutch automatic transmission is reduced to certain extent.
Description
Technical field
The present invention relates to the power-transmitting unit of automotive transmission, particularly power transmission mechanism for double-clutch.
Background technique
Automatic gearbox mainly contains Four types: hydraulic mechanical type automatic transmission (AT), electric control mechanical type automatic speed variator (AMT), mechanical stepless automatic speed changer (CVT) and double-clutch automatic gearbox (DCT).Wherein double-clutch automatic gearbox (DCT) had both been inherited AMT and many advantages such as manual transmission is simple in structure, installing space is compact, lightweight, transmission efficiency is high, low cost of manufacture, having merged again AT uninterruptible power, the good characteristics of smooth shifting rapidly, is a kind of speed changer of excellent performance.
The power transmission of double-clutch automatic gearbox (DCT) has two lines, article one, be odd number shelves transfer route, another is even number shelves transfer routes, article two, power transmission line connects odd number shelves input shaft and even number shelves input shaft by strange, even clutch respectively, by the driving gear on the driven shaft corresponding with input shaft, output power again, the DCT speed changer is controlled by coordination control and the synchromesh unit of two clutches, can realize in the situation that do not cut off the power transmission ratio, thereby shorten shift time, effectively improve property of automatic shft.Yet the relative manual transmission complexity of the power transmission structure of existing double-clutch automatic gearbox (DCT), thus it is large to make double-clutch automatic gearbox obtain difficulty of processing, and cost of production is high.
Summary of the invention
The purpose of this invention is to provide a kind of power transmission mechanism for double-clutch simple in structure, to reduce the manufacture cost of double-clutch automatic gearbox.
Power transmission mechanism for double-clutch of the present invention, comprise power input shaft, odd number shelves Clutch input shaft, odd number shelves clutch, even number shelves clutch and differential mechanism, also comprise first countershaft parallel with power input shaft and odd number shelves Clutch input shaft, the second countershaft, jack shaft and reverse idler gear axle, jack shaft is positioned at the centre of the first countershaft and the second countershaft, described even number shelves clutch is arranged on power input shaft and the left end of the second countershaft, odd number shelves clutch is arranged on odd number shelves Clutch input shaft and the left end of the first countershaft, left end at power input shaft is equipped with sun gear, planetary pinion, ring gear and fixing planet carrier, the ring gear outside is fixed with the ring gear external gear coaxial with it, the ring gear external gear is meshed with odd number shelves clutch active gear,
Odd number shelves driving gear and odd number shelves synchronizer are installed on the first countershaft, even number shelves driving gear, reverse driving gear and even number shelves synchronizer are installed on the second countershaft;
Driven gear and one or two reverse gear driven gears with the engagement of even number shelves driving gear and odd number shelves driving gear are installed on jack shaft, and wherein a driven gear meshes with the differential gear of differential mechanism;
The first reverse idler gear gear and the second reverse idler gear gear are installed on described reverse idler gear axle from left to right successively, and it meshes with reverse driving gear and one or two reverse gear driven gears respectively.
Odd number shelves driving gear comprises five grades of driving gears, third speed drive gear and one grade of driving gear, it is arranged on the first countershaft from left to right successively, described odd number shelves synchronizer comprises Five-gear synchronizer and a third gear synchronizer, Five-gear synchronizer is positioned at five grades of driving gears left side, and a third gear synchronizer is between third speed drive gear and one grade of driving gear.
Described even number shelves driving gear comprises fourth gear driving gear and second gear driving gear, it is arranged on the second countershaft from left to right successively, be positioned at the reverse driving gear right side, described even number shelves synchronizer comprises reversing-gear synchronizer and two fourth gear synchronizers, reversing-gear synchronizer is positioned at the reverse driving gear left side, and two fourth gear synchronizers are between fourth gear driving gear and second gear driving gear.
Driven gear on described jack shaft comprises five grades of driven gears and three fourth gear driven gears, it is arranged on jack shaft from left to right successively, be positioned at one or two reverse gear driven gear left sides, wherein one or two reverse gear driven gears mesh with one grade of driving gear, second gear driving gear and reverse idler gear shaftgear respectively, three fourth gear driven gears mesh with third speed drive gear and fourth gear driving gear respectively, and five grades of driven gears mesh with five grades of driving gears engagements and differential gear respectively.
As another kind of technological scheme, driven gear on described jack shaft comprises five grades of driven gears and three fourth gear driven gears, it is arranged on jack shaft from left to right successively, be positioned at one or two reverse gear driven gear left sides, wherein one or two reverse gear driven gears mesh with one grade of driving gear, second gear driving gear and reverse idler gear shaftgear respectively, three fourth gear driven gears mesh with third speed drive gear and fourth gear driving gear respectively, five grades of driven gears and five grades of driving gear engagements, the differential mechanism driven gear also is installed on jack shaft, and itself and differential gear mesh.
Power transmission mechanism for double-clutch of the present invention is owing to having adopted the idle pulley of planetary pinion as the first shaftgear, effectively reduce the space of driving mechanism and arranged size, make driving mechanism simpler, level of integration is higher, thereby has to a certain degree reduced the manufacture cost of double-clutch automatic gearbox.
Below in conjunction with accompanying drawing, the present invention is described in further detail.
The accompanying drawing explanation
Fig. 1 be the present invention at power intake along the power input shaft axial view;
Fig. 2 dissects along the A-A line a kind of power transmission obtained in Fig. 1 to concern schematic diagram;
Fig. 3 dissects along the A-A line the another kind of power transmission obtained in Fig. 1 to concern schematic diagram.
Embodiment
As Fig. 1, Figure 2 shows that double clutch five gear transmission power-transmitting units, comprise layout parallel to each other and the power input shaft 1 that can rotate around self axis, odd number shelves Clutch input shaft 30, the first countershaft 10, the second countershaft 5, jack shaft 9 and reverse idler gear axle 11, and odd number shelves clutch 28, even number shelves clutch 29 and differential mechanism 36, jack shaft 9 is positioned at the centre of the first countershaft 10 and the second countershaft 5, described even number shelves clutch 29 is arranged on power input shaft 1 and the left end of the second countershaft 5, odd number shelves clutch 28 is arranged on odd number shelves Clutch input shaft 30 and the left end of the first countershaft 10, left end at power input shaft 1 is equipped with sun gear 2, planetary pinion 3, ring gear 4 and fixing planet carrier 31, ring gear 4 outsides are fixed with the ring gear external gear 37 coaxial with it, ring gear external gear 37 is meshed with odd number shelves clutch active gear 27.
Odd number shelves driving gear and odd number shelves synchronizer are installed on the first countershaft 10, odd number shelves driving gear comprises five grades of driving gears 17, third speed drive gear 16 and one grade of driving gear 8, it is arranged on the first countershaft 10 from left to right successively, odd number shelves synchronizer comprises Five-gear synchronizer 21 and a third gear synchronizer 13, Five-gear synchronizer 21 is positioned at five grades of driving gear 17 left sides, and a third gear synchronizer 13 is between third speed drive gear 16 and one grade of driving gear 8.
Even number shelves driving gear, reverse driving gear 24 and even number shelves synchronizer are installed on the second countershaft 5, even number shelves driving gear comprises fourth gear driving gear 14 and second gear driving gear 6, it is arranged on the second countershaft 5 from left to right successively, be positioned at reverse driving gear 24 right sides, even number shelves synchronizer comprises reversing-gear synchronizer 20 and two fourth gear synchronizers 12, reversing-gear synchronizer 20 is positioned at reverse driving gear 24 left sides, and two fourth gear synchronizers 12 are between fourth gear driving gear 14 and second gear driving gear 6.
Driven gear and one or two reverse gear driven gears 7 are installed on described jack shaft 9, driven gear comprises five grades of driven gears 18 and three fourth gear driven gears 15, it is arranged on jack shaft 9 from left to right successively, be positioned at one or two reverse gear driven gear 7 left sides, wherein one or two reverse gear driven gears 7 respectively with one grade of driving gear 8, second gear driving gear 6 and 34 engagements of reverse idler gear shaftgear, three fourth gear driven gears 15 mesh with third speed drive gear 16 and fourth gear driving gear 14 respectively, five grades of driven gears 18 mesh with the differential gear 26 of five grades of driving gears 17 and differential mechanism 36 respectively.
The velocity ratio that the every pair of driving gear and driven gear produce is different, such as, the velocity ratio of each gear can be chosen as:
One grade: 16.4; Second gear: 10.8; Third gear: 6.7; Fourth gear: 5; Five grades: 3.7; Reverse gear: 15.9.
The first reverse idler gear gear 25 and the second reverse idler gear gear 34 are installed on described reverse idler gear axle 11 from left to right successively, and it meshes with reverse driving gear 24 and one or two reverse gear driven gears 7 respectively.
The power transmission line of these double clutch five gear transmission power-transmitting units is as follows:
During one grade of transmission of power:
One third gear synchronizer 13 engages with one grade of driving gear 8, odd number shelves clutch 28 engages, even number shelves clutch 29 separates, be delivered to the power of input shaft 1 from motor, be delivered to (1 grade) on ring gear external gear 37 by sun gear 2, planet wheel 3, ring gear 4, ring gear external gear 37 by transmission of power to odd number shelves clutch active gear 27, now, one grade of driving gear 8, a third gear synchronizer 13, first countershaft 10 synchronously are combined together, and power is delivered to (2 grades) on odd number shelves Clutch input shaft 30 by odd number shelves clutch active gear 27; All the other gear driving gears are in idling conditions, and then power is delivered to (3 grades) on one or two reverse gear driven gears 7 by one grade of driving gear 8; Power from one or two reverse gear driven gears 7 to jack shaft 9, then by five grades of driven gears 18 by transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36(4 level).Now, transmitting progression is level Four.
During the second gear transmission of power:
Two fourth gear synchronizers 12 engage with second gear driving gear 6, even number shelves clutch 29 engages, odd number shelves clutch 28 separates, be delivered to the transmission of power of power input shaft 1 to even number shelves clutch 29 from motor, now, second gear driving gear 6, two fourth gear synchronizers 12, the second countershaft 5 synchronously are combined together, by the transmission of power of motor to the second countershaft 5; All the other gear driving gears are in idling conditions, and then power is delivered to (1 grade) on one or two reverse gear driven gears 7 by second gear driving gear 6; Power from one or two reverse gear driven gears 7 to jack shaft 9 again by five grades of driven gears 18 by transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36(2 level).Now, transmitting progression is secondary.
During the third gear transmission of power:
One third gear synchronizer 13 engages with third speed drive gear 16, odd number shelves clutch 28 engages, even number shelves clutch 29 separates, be delivered to the power of input shaft 1 from motor, by sun gear 2, planet wheel 3, ring gear 4 is delivered to (1 grade) on ring gear external gear 37, ring gear external gear 37 by transmission of power to odd number shelves clutch active gear 27, now, third speed drive gear 16, one third gear synchronizer 13, odd number shelves Clutch input shaft 30 synchronously is combined together, complete power and be delivered to (2 grades) on the first countershaft 10 by odd number shelves clutch active gear 27, all the other gear driving gears are in idling conditions, and then power is delivered to (3 grades) on three fourth gear driven gears 15 by third speed drive gear 16, power from three fourth gear driven gears 15 to jack shaft 9 again by five grades of driven gears 18 by transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36(4 level).Now, transmitting progression is level Four.
During the fourth gear transmission of power:
Two fourth gear synchronizers 12 engage with fourth gear driving gear 14, even number shelves clutch 29 engages, odd number shelves clutch 28 separates, be delivered to the transmission of power of power input shaft 1 to even number shelves clutch 29 from motor, now, fourth gear driving gear 14, two fourth gear synchronizers 12, the second countershaft 5 synchronously are combined together, and complete power and are delivered on the second countershaft 5 by even number shelves clutch 29; All the other gear driving gears are in idling conditions, and then power is delivered to (1 grade) on three fourth gear driven gears 15 by fourth gear driving gear 14; Power from three fourth gear driven gears 15 to jack shaft 9 again by five grades of driven gears 18 by transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36(2 level).Now, transmitting progression is secondary.
During five grades of transmission of power:
Five-gear synchronizer 21 engages with five grades of driving gears 17, odd number shelves clutch 28 engages, even number shelves clutch 29 separates, be delivered to the power of input shaft 1 from motor, be delivered to (1 grade) on ring gear external gear 37 by sun gear 2, planet wheel 3, ring gear 4, ring gear external gear 37 by transmission of power to odd number shelves clutch active gear 27, now, five grades of driving gears 17, Five-gear synchronizer 21, odd number shelves Clutch input shafts 30 synchronously are combined together, and complete power and are delivered to (2 grades) on the first countershaft 10 by odd number shelves clutch active gear 27; All the other gear driving gears are in idling conditions, and then power is delivered to (3 grades) on five grades of driven gears 18 by five grades of driving gears 17; Power by five grades of driven gears 18 by transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36(4 level).Now, transmitting progression is level Four.
During the reverse gear transmission of power:
Reversing-gear synchronizer 20 engages with reverse driving gear 24, even number shelves clutch 29 engages, odd number shelves clutch 28 separates, be delivered to the transmission of power of power input shaft 1 to even number shelves clutch 29 from motor, now, reverse driving gear 24, reversing-gear synchronizer 20, the second countershaft 5 synchronously are combined together, and complete power and are delivered on the second countershaft 5 by even number shelves clutch 29; All the other gear driving gears are in idling conditions, and then power is delivered on reverse idler gear 25 by reverse driving gear 24, reverse idler gear 25 by reverse idler gear axle 11 by transmission of power to reverse idler gear shaftgear 34 (1 grade); Reverse idler gear shaftgear 34 is by transmission of power to one two reverse gear driven gears 7 (2 grades); Power from one or two reverse gear driven gears 7 to jack shaft 9 again by five grades of driven gears 18 by transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36(3 level).Now, transmitting progression is three grades.
During gear shift:
When above-mentioned any one gear work, but the next gear of preliminary election (making in advance corresponding synchronizer coordinate with corresponding shifting gear) is the switching of clutch during gear shift, and gear shift is completed in the unbroken situation of transmission of power.
Double clutch five gear transmission power-transmitting units are as shown in Figure 3 installed a differential mechanism driven gear 118 on jack shaft 9, and itself and differential gear 26 mesh, and other structure is identical with above-mentioned mode of execution.Changed like this position of differential mechanism 36 relative other gear trains, the transmission be conducive under the special construction condition is arranged.
Claims (5)
1. a power transmission mechanism for double-clutch, comprise power input shaft (1), odd number shelves Clutch input shaft (30), odd number shelves clutch (28), even number shelves clutch (29) and differential mechanism (36), it is characterized in that: also comprise first countershaft (10) parallel with power input shaft and odd number shelves Clutch input shaft, the second countershaft (5), jack shaft (9) and reverse idler gear axle (11), jack shaft is positioned at the centre of the first countershaft and the second countershaft, described even number shelves clutch (29) is arranged on power input shaft (1) above and the left end of the second countershaft (5), odd number shelves clutch (28) is arranged on odd number shelves Clutch input shaft (30) above and the left end of the first countershaft (10), left end at power input shaft (1) is equipped with sun gear (2), planetary pinion (3), ring gear (4) and fixing planet carrier (31), ring gear (3) outside is fixed with the ring gear external gear (37) coaxial with it, the ring gear external gear is meshed with odd number shelves clutch active gear (27),
Odd number shelves driving gear and odd number shelves synchronizer are installed on the first countershaft (10), even number shelves driving gear, reverse driving gear (24) and even number shelves synchronizer are installed on the second countershaft (5);
Driven gear and one or two reverse gear driven gears (7) with the engagement of even number shelves driving gear and odd number shelves driving gear are installed on jack shaft (9), and wherein a driven gear meshes with the differential gear (26) of differential mechanism (36);
The first reverse idler gear gear (25) and the second reverse idler gear gear (34) are installed on described reverse idler gear axle (11) from left to right successively, and it meshes with reverse driving gear (24) and one or two reverse gear driven gears (7) respectively.
2. power transmission mechanism for double-clutch according to claim 1, it is characterized in that: described odd number shelves driving gear comprises five grades of driving gears (17), third speed drive gear (16) and one grade of driving gear (8), it is arranged on the first countershaft (10) from left to right successively, described odd number shelves synchronizer comprises Five-gear synchronizer (21) and a third gear synchronizer (13), Five-gear synchronizer (21) is positioned at five grades of driving gear left sides, and a third gear synchronizer (13) is positioned between third speed drive gear (16) and one grade of driving gear (8).
3. power transmission mechanism for double-clutch according to claim 1, it is characterized in that: described even number shelves driving gear comprises fourth gear driving gear (14) and second gear driving gear (6), it is arranged on the second countershaft (5) from left to right successively, be positioned at reverse driving gear (24) right side, described even number shelves synchronizer comprises reversing-gear synchronizer (20) and two fourth gear synchronizers (12), reversing-gear synchronizer (20) is positioned at reverse driving gear (24) left side, two fourth gear synchronizers (12) are positioned between fourth gear driving gear (14) and second gear driving gear (6).
4. power transmission mechanism for double-clutch according to claim 1, it is characterized in that: the driven gear on described jack shaft (9) comprises five grades of driven gears (18) and three fourth gear driven gears (15), it is arranged on jack shaft (9) from left to right successively, be positioned at one or two reverse gear driven gear (7) left sides, wherein one or two reverse gear driven gears respectively with one grade of driving gear (8), second gear driving gear (6) and reverse idler gear shaftgear (34) engagement, three fourth gear driven gears (15) mesh with third speed drive gear (16) and fourth gear driving gear (14) respectively, five grades of driven gears (18) mesh with five grades of driving gears (17) engagement and differential gear (26) respectively.
5. power transmission mechanism for double-clutch according to claim 1, it is characterized in that: the driven gear on described jack shaft (9) comprises five grades of driven gears (18) and three fourth gear driven gears (15), it is arranged on jack shaft (9) from left to right successively, be positioned at one or two reverse gear driven gear (7) left sides, wherein one or two reverse gear driven gears respectively with one grade of driving gear (8), second gear driving gear (6) and reverse idler gear shaftgear (34) engagement, three fourth gear driven gears (15) mesh with third speed drive gear (16) and fourth gear driving gear (14) respectively, five grades of driven gears (18) and five grades of driving gears (17) engagement, differential mechanism driven gear (118) also is installed on jack shaft (9), itself and differential gear (26) mesh.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011103899612A CN102425647B (en) | 2011-11-30 | 2011-11-30 | Power transmission mechanism for double-clutch automatic transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011103899612A CN102425647B (en) | 2011-11-30 | 2011-11-30 | Power transmission mechanism for double-clutch automatic transmission |
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| CN102425647A CN102425647A (en) | 2012-04-25 |
| CN102425647B true CN102425647B (en) | 2013-12-04 |
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| CN103821897B (en) * | 2014-03-14 | 2016-08-03 | 上海交通大学 | Electric motor car two grades of automatic speed changer for machine of single planet circular system |
| CN108162743B (en) * | 2017-12-22 | 2023-08-04 | 蓝黛科技集团股份有限公司 | Speed variator for hybrid power vehicle |
| CN108162741B (en) * | 2017-12-22 | 2023-08-04 | 蓝黛科技集团股份有限公司 | Speed change structure of hybrid power vehicle |
| CN109630566B (en) * | 2019-01-30 | 2024-04-05 | 浙江海天机械有限公司 | Wet clutch unit assembly |
| CN109723769B (en) * | 2019-03-08 | 2023-07-21 | 重庆青山工业有限责任公司 | Two-stage speed reducing mechanism of pure electric vehicle speed reducer |
| CN111219455A (en) * | 2020-03-18 | 2020-06-02 | 洛阳拖拉机研究所有限公司 | Three-clutch type segment changing mechanism of tractor |
| CN118560253A (en) * | 2024-08-05 | 2024-08-30 | 盛瑞传动股份有限公司 | Hybrid transmission |
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- 2011-11-30 CN CN2011103899612A patent/CN102425647B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2006032789A1 (en) * | 2004-09-23 | 2006-03-30 | Antonov Automotive Technologies Bv | Double-clutch gearbox, in particular for motor vehicle |
| CN101089420A (en) * | 2006-06-16 | 2007-12-19 | 比亚迪股份有限公司 | Double-clutch automatic transmission mechanism |
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Effective date of registration: 20181214 Address after: 230001 No. 966 Dabieshan Road, Hefei High-tech Zone, Anhui Province Co-patentee after: Qingshan Industry Co., Ltd., Chongqing Patentee after: Hefei Changan Automobile Co., Ltd. Address before: 402761 Qingba Town, Bishan County, Chongqing Patentee before: Qingshan Industry Co., Ltd., Chongqing |