CN102019850A - Automatic transmission for double cultch - Google Patents
Automatic transmission for double cultch Download PDFInfo
- Publication number
- CN102019850A CN102019850A CN2009101525241A CN200910152524A CN102019850A CN 102019850 A CN102019850 A CN 102019850A CN 2009101525241 A CN2009101525241 A CN 2009101525241A CN 200910152524 A CN200910152524 A CN 200910152524A CN 102019850 A CN102019850 A CN 102019850A
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- gear
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- gears
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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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- 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
Abstract
The invention relates to an automatic transmission for double cultch, wherein a double clutch device comprises a clutch C11 and a clutch C22 which share a rotating axis; an inner input shaft of the automatic transmission is connected to a crankshaft output end of an engine through the clutch C11 and the outer input shaft of the automatic transmission is connected to the crankshaft output end of an engine through the clutch C22; 1st, 3rd and 5th gears are arranged on the inner input shaft; the driving gear-wheels of the 1st and 3rd gears are integrated with the inner input shaft; the driving gear wheels of 2nd, 4th and 6th and reverse gears are arranged on the outer input shaft; and the 2nd and reverse gears share a driving gear wheel with the 4th and 6th gears, so as to realize seven variable speeds, namely seven gear positions, therefore shortening 10% of the axial length of the transmission and providing a bigger space for the matching of whole vehicle. A reverse gear idler at the reverse gear is integrated with the driven gear wheel of the 2nd gear of the output shaft, which requires no idler shaft, so the transmission is compacter. A ratchet wheel of a parking mechanism is linked with a spline of the output shaft, is not engaged with other gears, and utilizes the space of the same section of two-gear gear pair along the radial direction. Compared with the traditional manner of arranging the ratchet wheel on a differential mechanism, the arranging manner of the ratchet wheel can reduce above 30% of the load of the parking mechanism and increase the parking efficiency.
Description
Technical field the present invention relates to a kind of automatic gearbox that is used for, and refers more particularly to a kind of double-clutch automatic gearbox.
The background technology double-clutch automatic speed changer for automobile uses double-clutch to select to transmit the moment of torsion of driving engine input usually on its dual input shaft, and it uses the gear on the dual input shaft to change moment of torsion and speed, transmits output.
The common nominal torque of existing double-clutch automatic speed changer for automobile can become very greatly for bearing 6 D Drive double-clutch automatic speed changer for automobile axial lengths more than the 200Nm all more than 200Nm, and therefore shared space is restricted.
The double-clutch automatic speed changer for automobile that also has has also been arranged the reverse idler gear axle except adopting dual input shaft double output shaft structure, for the speed ratio that satisfies reverse gear requires also to have established on its idler shaft two gears, so not only increase the volume of change-speed box, also improved the manufacturing cost and the difficulty of change-speed box.
Axial space in the existing double-clutch automatic speed changer for automobile holds the Parking ratchet of halting mechanism device inadequately, and the Parking ratchet only is fixed on the differential cross pin.The load to the halting mechanism device that the Parking ratchet is fixed on the differential cross pin is very big, and particularly automobile is when steeper slope, and landslide power is big, to the very big influence of halting mechanism device generation.
Summary of the invention the objective of the invention is in order to provide a kind of axial dimension less, has the individual D Drive function of six (or seven) dual-clutch transmission device, another purpose is for the Parking ratchet being set on output shaft, saving independently idler shaft arrangement structure, to reduce the load of halting mechanism.
The invention provides a kind of double-clutch automatic speed changer for automobile, it comprises: double clutch device, two transmission input medias, the first output shaft device, the second output shaft device, halting mechanism, differential cross pin.
Described double clutch device comprises power-transfer clutch C
1, power-transfer clutch C
2, power-transfer clutch C
1With power-transfer clutch C
2Radially stacked corotation shaft axis is arranged.
Described pair of transmission input media comprises axle and the driving gear of importing outer shaft and each grade in the input.The input outer shaft is located at the excircle of axle in the input, the coaxial line rotation.Axle connects power-transfer clutch C in the input
1, the input outer shaft connects power-transfer clutch C
2, and be connected with the crankshaft output end of driving engine.Axle is provided with 1,3,5 grade of driving gear in importing, and 1,3 grade of driving gear is an integral body with the interior axle of input.The input outer shaft is provided with 2,4,6, reverse driving gear, and 2, reverse gear is with a driving gear, 4,6 grades of also shared driving gears are an integral body with importing outer shaft.
The first output shaft device comprises first output shaft, First Five-Year Plan shelves synchro, two or six grades of synchros and 1,2,5,6 grade of driven gear.1,2,5,6 grades of driven gears all are arranged on first output shaft, respectively with 1,2,5,6 grade of driving gear engagement importing on the inside and outside axle.1 grade of moment of torsion with 5 grades of driven gears of First Five-Year Plan shelves synchro transmission selectively is delivered on first output shaft, 2 grades of moments of torsion with 6 grades of driven gears of two or six grades of synchro transmission selectively are delivered on first output shaft, and main subtract driving gear it is arranged on first output shaft and subtracts the driven gear engagement with the differential cross pin master.Thereby the moment of torsion of 1,5,2,6 grade of driving gear in the input on axle, the input outer shaft is exported by the conversion of selectivity.
The second output shaft device comprises second output shaft, third gear synchro, four reverse gear synchros, Parking ratchet and 3,4 reverse gear driven gears.3,4 reverse gear driven gears all are arranged on second output shaft, respectively with 3, the 4 reverse driving gears engagement of importing on the inside and outside axle.The third gear synchro transmits on moment of torsion second output shaft of 3 grades of driven gears, the gear that also can promote change-speed box is here arranged 7 grades, be that the moment of torsion that the third gear synchro also just selectively transmits 3 grades and 7 grades is exported, 4 grades of moments of torsion with the reverse gear driven gear of four reverse gear synchro transmission selectively are delivered on second output shaft, and main subtract driving gear 2 it is arranged on second output shaft and subtracts the driven gear engagement with the differential cross pin master.Thereby the moment of torsion of 3,4 in the input on axle, the input outer shaft, reverse driving gear is exported by the conversion of selectivity.
Wherein reverse gear is to be combined as a whole by input outer shaft and 2 grades of driving gears, 2 grades of driven gears of first output shaft and reverse idler gear combine as a whole, the engagement of reverse gear driven gear band engaging tooth on second input shaft and the tooth of four reverse gear synchros cover is fallen synchro by four and is passed to the output of second output shaft.2 grades of dual gears that driven gear joins together on its reverse idler gear and first output shaft save traditional idler shaft arrangement structure, make change-speed box compact more.
Halting mechanism has the Parking ratchet, and park pawl and differential cross pin, Parking ratchet are fixed on second output shaft, and the halting mechanism ratchet is fixed on the motionless case of transmission in relative car load chassis.Parking ratchet on the halting mechanism ratchet and second output shaft lock is dynamically connected, and promptly second output shaft is fixed, and the main driving gear that subtracts subtracts the driven gear engagement with the differential cross pin master on second output shaft, reaches wheel lockup realization Parking.
Reverse gear of the present invention is arranged on second output shaft, and reverse idler gear and 2 grades of driven gears of first output shaft combine as a whole, and economizes the layout of removing idler shaft, makes structure compact more, reduces the gear revolute pair, and bank increases driving efficiency, reduces noise.The present invention has designed 4,6 grades of shared driving gears, the shared driving gear of 2 reverse gears, can realize (seven) individual gear, knot car load coupling provides bigger space, the drive ratchet of mechanism is arranged on second output shaft, ratchet is fixed on the case of transmission, changes the method that is fixed on the diff, improves Parking usefulness.
Description of drawings Fig. 1 is the diagrammatic sketch of double-clutch automatic gearbox of the present invention.
Fig. 2 is that Figure 1A is to diagrammatic sketch.
The specific embodiment is recorded and narrated the technology contents of invention hereinafter with reference to the accompanying drawings in detail:
Double-clutch automatic gearbox device of the present invention comprises: power-transfer clutch C
11, power-transfer clutch C
22, axle 3 in the input, input outer shaft 4,6,1 grades of driving gears 7 of first output shaft, 5, the second output shafts, 8,5 grades of driving gears 9,2 of 3 grades of driving gears, reverse driving gear 10,4,6 grades of driving gears 11,12, two six grades of synchros 13 of First Five-Year Plan shelves synchro, 14,2 grades of driven gears 30 of 1 grade of driven gear, reverse idler gear 15,16,6 grades of driven gears 17 of 5 grades of driven gears, the main driving gear 18 that subtracts, third gear synchro 19, four reverse gear synchros 20, Parking ratchet 21,22,4 grades of driven gears 23 of 3 grades of driven gears, reverse gear driven gear 24, the main driving gear 25 that subtracts, the main driven gear 26, differential cross pin 27, halting mechanism of subtracting.
Axle 3 is by power-transfer clutch C in the input
11, the input outer shaft is by power-transfer clutch C
22 are connected with bent axle 29 mouths of driving engine.Axle 3 was unified into an integral body in axle 3 was provided with 7,3 grades of driving gears of 9,1 grades of driving gears of 8,5 grades of driving gears of 7,3 grades of driving gears of 1 grade of driving gear 8 and imports in the input.Input outer shaft 4 is provided with 2 grades of driving gears 10, reverse driving gear 10, and promptly 2 reverse gears are same with 11, six grades of driving gears 11 of 10,4 grades of driving gears of a driving gear,, 4,6 grades of shared driving gears 11, they are an integral body with input outer shaft 4 all.
1 grade of driven gear 14.16,6 grades of driven gears 17 of 15,5 grades of driven gears of 2 grades of driven gears are arranged on first output shaft 5, respectively with 1 grade of driving gear 7 and 5 grades of driving gears 9 of importing on the interior axle 3, and 2 grades of driving gears 10 and 6 six grades of driving gears 11 engagements on the input outer shaft 4.First Five-Year Plan shelves synchro 12 is arranged between 1 grade of driven gear 14 and the 5 grades of driven gears 16, put in the first speed or 5 grades of driven gears 14 or 16 and power-transfer clutch C
11 combination, power is through power-transfer clutch C
11 is delivered to axle 3 in the input, 1 grade of driving gear 7 combines as a whole with the interior axle 3 of input, driven the rotation of 1 grade or 5 grades of driven gears 14 or 16,1 grade or 5 grades of driven gears 14 or 16 band engaging tooths mesh with the tooth cover of First Five-Year Plan shelves synchro 12, thereby drive 5 rotations of first output shaft, the main deceleration driving gear 18 that combines as a whole with first output shaft 5 has driven differential cross pin 27 main deceleration driven gear 26 outputting powers.Two or six grades of synchros 13 are arranged between 2 grades of driven gears 15 and the 6 grades of driven gears 17, throw in second gear or six grades of driven gears 30 or 17, power-transfer clutch C
22 combinations, power is through power-transfer clutch C
22 are delivered to input outer shaft 4,2,6 grades of driving gears 11 combine as a whole with input outer shaft 4, driven the rotation of 2 grades or 6 grades of driven gears 30 or 17,2 grades or 6 grades of driven gears 30 or 17 band engaging tooths mesh with the tooth cover of two or six grades of synchros 13, thereby drive 5 rotations of first output shaft, the main deceleration driving gear 18 that combines as a whole with output shaft 5 has driven differential cross pin 27 main deceleration driven gear 26 outputting powers.And subtract driving gear 18 with master that first output shaft 5 combines as a whole and subtract driven gear 26 engagements with the differential cross pin master, thereby the moment of torsion of 1,5,2,6 grade of driving gear on axle 3, the input outer shaft 4 is exported by the conversion of selectivity in the input.
22,4 grades of driven gears 23 of 3 grades of driven gears, reverse gear driven gear 24, Parking ratchet 21 is arranged on second output shaft 6, respectively with 4,6 grades of driving gears 11,10 engagements of two reverse gear driving gears imported on 3 grades of driving gears 8 of interior axle, the input outer shaft.Third gear synchro 19 is arranged in a side of third gear driven gear 22, hangs up 3 grades of driven gears 22, power-transfer clutch C
11 combination, engine power is through power-transfer clutch C
11 is delivered to axle 3 in the input, axle 3 fixedly stressed joints in 3 grades of driving gears 8 and the input, driven the rotation of 3 grades of driven gears 22,3 grades of driven gears 22 are with the tooth cover engagement of engaging tooths and third gear synchro 19, thereby drive 6 rotations of second output shaft, the main deceleration driving gear 25 that combines as a whole with second output shaft 6 has driven differential cross pin 27 main deceleration driven gear 26 outputting powers.Four reverse gear synchros 20 are arranged between fourth gear driven gear 23 and the six grades of driven gears 24, put into fourth gear driven gear 23, power-transfer clutch C
11 motionless (normally open), power-transfer clutch C22 combination, engine power is through power-transfer clutch C
22 are delivered to input outer shaft 4, fourth gear driving gear 11 combines as a whole with input outer shaft 4 and has driven the rotation of fourth gear driven gear 23,4 grades of driven gears 23 are with the tooth cover engagement of engaging tooths and four reverse gear synchros 20, thereby drive output shaft 26 rotations, the main deceleration driving gear 25 that combines as a whole with output shaft 26 has driven differential cross pin 27 main deceleration driven gear 26 outputting powers.
Hang up the reverse gear driven gear 24 that is arranged on second output shaft 6, power-transfer clutch C
22 combinations, power is through power-transfer clutch C
22 are delivered to input outer shaft 4,2 grades of driving gears 10 combine as a whole with input outer shaft 4 and have driven the rotation of 2 grades of driven gears 30,2 grades of driven gears 30 are one with reverse idler gear 15, be socketed in first output shaft 5, drive is arranged in the reverse gear driven gear 24 on second output shaft 6, the tooth cover engagement of reverse gear driven gear 24 band engaging tooths and four reverse gear synchros 20, thereby drive 6 rotations of second output shaft, the main deceleration driving gear 25 that combines as a whole with second output shaft 6 has driven differential cross pin 27 main deceleration driven gear 26 outputting powers.
Five driving gears, wherein 2 grades with 11,6 grades of 4 grades of shared driving gears and the shared driving gear x of reverse gear, can realize seven kinds of speed changes, reach seven gears (six D Drives and a reverse gear), axial length to change-speed box shortens 10% at least like this, bigger space is provided for the coupling of car load.
Fig. 2 is that Figure 1A is to view.The spatial relationship of axle, input outer shaft, output shaft 1 device, output shaft 2 devices in the reverse idler gear of double-clutch automatic gearbox, differential cross pin, Parking ratchet, the input.
The input outer shaft is located at the excircle of axle in the input, the coaxial line rotation.Form triangle distribution with first output shaft 5, second output shaft 6, its task is to allow 1,3,5 grade of driving gear importing interior axle 3,2,4,6 reverse driving gears of input outer shaft 4, can with 1,5,2,6 grade of driven gear on first output shaft 5, mesh jointly with 3,4 driven gears on second output shaft 6.
The diff master subtracts driven gear 26 and first output shaft 5, second output shaft 6 form triangle distribution, and task is exactly to allow the diff master subtract master on the driven gear and first output shaft 5 subtract master on driving gear 2, second output shaft 2 and subtract driving gear 2 and mesh jointly.
Claims (6)
1. a double-clutch automatic gearbox includes double clutch device, two transmission input media, the first output shaft device, the second output shaft device, and halting mechanism and differential cross pin, double clutch device have power-transfer clutch C
11 and power-transfer clutch C
22, their radially stacked corotation rotating shafts are arranged; Two transmission input medias have axle and input outer shaft in the input, and the input outer shaft is located at axle excircle in the input, the coaxial line rotation, and axle connects power-transfer clutch C in the input
11, the input outer shaft connects power-transfer clutch C
22, and be connected with engine crankshaft; Axle is provided with 1,3,5 grade of driving gear in the input, and the input outer shaft is provided with 2,4,6, reverse driving gear; First output unit has first output shaft, First Five-Year Plan shelves synchro, and two or six grades of synchros and 1,2,5,6 grade of driven gear are arranged on first output shaft, respectively with the interior axle of input and 1,2,5,6 grade of driving gear engagement importing outer shaft; The second output shaft device has output shaft, the third gear synchro, four reverse gear synchros, Parking ratchet and 3,4, reverse gear driven gear, 3,4, the reverse gear driven gear is arranged on second output shaft, respectively with input in 3,4 on axle and the input outer shaft, reverse driving gear engagement; It is characterized in that: input outer shaft (4) combines as a whole with 2 grades of driving gears (10), 2 grades of driven gears (30) connection and one on reverse idler gear (15) and first output shaft (5), reverse gear driven gear (24) band is nibbled the tooth cover engagement with four reverse gear synchros (20), affixed second output shaft of Parking ratchet (21) (6), on the affixed case of transmission of park pawl, Parking ratchet (21) lock on park pawl and the output shaft (6) is dynamically connected.
2. a kind of double-clutch automatic gearbox as claimed in claim 1, it is characterized in that: 1,3 grades of driving gears (7), (8) are an integral body with the interior axle of input (4), 2, the shared driving gear of reverse gear (10), 4,6 grades of shared driving gears (11), and with the input outer shaft (4) be an integral body.
3. a kind of double-clutch automatic gearbox as claimed in claim 1 is characterized in that: 2 grades of driven gears (30) are connected as a single entity with reverse idler gear (15), are socketed in first output shaft (5).
4. a kind of double-clutch automatic gearbox as claimed in claim 1 is characterized in that: the main driving gear (25) that subtracts is arranged on second output shaft (6) and goes up and subtract driven gear (26) with the differential cross pin master and mesh.
5. a kind of double-clutch automatic gearbox as claimed in claim 1 is characterized in that: input outer shaft (4) is located at the excircle of axle (3) in the input, and with first output shaft (5), second output shaft (6) becomes triangle distribution.
6. a kind of double-clutch automatic gearbox as claimed in claim 1 is characterized in that: main driven gear (26) and first output shaft (5) of subtracting of differential cross pin (27), second output shaft (6) becomes triangle distribution.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009101525241A CN102019850A (en) | 2009-09-17 | 2009-09-17 | Automatic transmission for double cultch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009101525241A CN102019850A (en) | 2009-09-17 | 2009-09-17 | Automatic transmission for double cultch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102019850A true CN102019850A (en) | 2011-04-20 |
Family
ID=43861772
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009101525241A Pending CN102019850A (en) | 2009-09-17 | 2009-09-17 | Automatic transmission for double cultch |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102019850A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105822733A (en) * | 2016-05-30 | 2016-08-03 | 重庆青山工业有限责任公司 | Dual-clutch type two-gear pure electric transmission |
| CN113212149A (en) * | 2020-02-06 | 2021-08-06 | 德尔福科技工业生产有限公司 | Hybrid power transmission system |
| CN113580921A (en) * | 2021-09-03 | 2021-11-02 | 哈尔滨东安汽车发动机制造有限公司 | Hybrid vehicle transmission device |
-
2009
- 2009-09-17 CN CN2009101525241A patent/CN102019850A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105822733A (en) * | 2016-05-30 | 2016-08-03 | 重庆青山工业有限责任公司 | Dual-clutch type two-gear pure electric transmission |
| CN113212149A (en) * | 2020-02-06 | 2021-08-06 | 德尔福科技工业生产有限公司 | Hybrid power transmission system |
| CN113580921A (en) * | 2021-09-03 | 2021-11-02 | 哈尔滨东安汽车发动机制造有限公司 | Hybrid vehicle transmission device |
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| PB01 | Publication | ||
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| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20110420 |