CN101446337A - Double-clutch automatic gearbox - Google Patents
Double-clutch automatic gearbox Download PDFInfo
- Publication number
- CN101446337A CN101446337A CNA200810233387XA CN200810233387A CN101446337A CN 101446337 A CN101446337 A CN 101446337A CN A200810233387X A CNA200810233387X A CN A200810233387XA CN 200810233387 A CN200810233387 A CN 200810233387A CN 101446337 A CN101446337 A CN 101446337A
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- China
- Prior art keywords
- gear
- clutch
- countershaft
- reverse
- double
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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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
Abstract
The invention relates to a double-clutch automatic gearbox comprising an input shaft (29), an input shaft gear (1), a first counter shaft (6), a second counter shaft (8), an intermediate (7), a power take-off device, at least an odd number gear pair, at least an even number gear pair, a first clutch (2) fixed on the first counter shaft (6), and a second clutch (3) fixed on the second counter shaft (8). The gearbox is characterized in that the power take-off device comprises a compensating gear (24), and a planetary mechanism fixedly connected with the compensating gear (24). The gearbox has the advantages of a small quantity of gears, small axial length and light weight, and is easier to be arranged and used in small fore-driving sedans.
Description
Technical field
The present invention relates to a kind of transmission for vehicles, particularly relate to a kind of double-clutch automatic gearbox.
Background technique
Existing double-clutch automatic transmission comprises two clutches, synchromesh unit, shift control, automatical control system TCU and six gear speed changers, these two wet clutches are separately fixed on two countershafts, the driving gear of strange, the even gear of speed changer drives with two wet clutches respectively and is connected, and two clutches alternately transmit operation power and realize switching between the gear.But, there is following shortcoming in this kind gear: because two wet clutches are separately fixed on two input shafts, one of them input shaft be tubulose and be enclosed within another input shaft, this another input shaft with its gear cloth outside the end of tubular shafts, this layout has increased volume, weight and the price of gear, and is difficult for being installed on the compact car.
Summary of the invention
The object of the present invention is to provide the double-clutch automatic gearbox that gear quantity is few, axial length is short.
The objective of the invention is to be achieved through the following technical solutions: a kind of double-clutch automatic gearbox, comprise input shaft, input shaft gear, first countershaft, second countershaft, jack shaft, power take-off, at least one odd gear gear pair, at least one even number shifting gear pair, be fixed on the first clutch on described first countershaft, be fixed on the second clutch on described second countershaft, it is characterized in that: described power take-off comprises differential mechanism, the planetary mechanism of fixedlying connected with described differential mechanism.
Described planetary mechanism comprises sun gear, planet wheel, planet input gear, gear ring, planet carrier; Driven gear on described input gear and the described jack shaft meshes and fixes with described sun gear, and described gear ring and described differential mechanism are fixed, and the housing of described planet carrier and speed changer is fixed.
For further reducing the axial length of double-clutch automatic gearbox, described input shaft, first countershaft, second countershaft are arranged at interval.
Above-mentioned spaced apart concrete mode can be that described input shaft and described jack shaft are set to parallel type, and described first countershaft and described second countershaft are arranged on described jack shaft both sides.
The concrete structure of above-mentioned double-clutch automatic gearbox can be to be disposed with first clutch, first clutch gear, five grades of driving gears, five reverse gear synchronizers, reverse driving gear, third speed drive gear, a third gear synchronizer and one grade of driving gear on described first countershaft; Be disposed with second clutch, second clutch gear, fourth gear driving gear, two fourth gear synchronizers and second gear driving gear on described second countershaft; Be disposed with four or five grades of driven gears, two or three reverse gear driven gear and first speed driven gears on the described jack shaft; Described reverse driving gear arrives described reverse gear driven gear by the reverse idler gear that is arranged on the reverse gear shaft with transmission of power.
Described input shaft and described input shaft gear can be integral type, and promptly input shaft is the axle tooth.
The invention has the beneficial effects as follows:
(1) because described power take-off comprises differential mechanism, the planetary mechanism of fixedlying connected with described differential mechanism, therefore easier the layout in small-sized forerunner's formula car of the present invention used, abandon on countershaft and to add the axial length that structure that idle pulley exports can effectively shorten speed changer, in transmission design, if can reduce by 10% length, volume or weight is very significant;
(2) because described planetary mechanism can be designed as in the case of transmission of packing into,, can save arrangement space so can make whole speed changer volume very small and exquisite;
(3) because described planetary mechanism comprises sun gear, planet wheel, planet input gear, gear ring, planet carrier, driven gear on described input gear and the described jack shaft meshes and fixes with described sun gear, described gear ring and described differential mechanism are fixed, the housing of described planet carrier and speed changer is fixed, realization power forerunner output that therefore can be stable;
(4) since described input shaft, first countershaft, second countershaft arrange at interval, therefore for further reducing the axial length of double-clutch automatic gearbox, and avoided with automobile on the miscellaneous part occurrence positions interfere, make total small and exquisite;
Above-mentioned spaced apart concrete mode can be that described input shaft and described jack shaft are set to parallel type, and described first countershaft and described second countershaft are arranged on described jack shaft both sides;
(5) because the concrete structure of double-clutch automatic gearbox is to be disposed with first clutch on described first countershaft, first clutch gear, five grades of driving gears, five reverse gear synchronizers, reverse driving gear, third speed drive gear, one third gear synchronizer and one grade of driving gear, be disposed with second clutch on described second countershaft, the second clutch gear, the fourth gear driving gear, two fourth gear synchronizers and second gear driving gear, be disposed with four or five grades of driven gears on the described jack shaft, two or three reverse gear driven gear and first speed driven gears, described reverse driving gear arrives described reverse gear driven gear by the reverse idler gear that is arranged on the reverse gear shaft with transmission of power, therefore of the present invention rational in infrastructure, and four or five grades of driven gears are set to a gear, two or three reverse gear driven gears are set to a gear, therefore reduce the quantity of gear, also reduced the axial length of speed changer simultaneously;
In a word, since above structure, the gear negligible amounts that speed changer of the present invention adopts, axial length is short, and volume is small and exquisite, can be suitable for using on small-sized forerunner's formula car.
Description of drawings
Fig. 1 is a structural representation of the present invention;
Fig. 2 is the diagrammatic side views of Fig. 1.
Be labeled as among the figure: 1, input gear; 2, first clutch; 3, second clutch; 4, second clutch gear; 5, first clutch gear; 6, first countershaft; 7, jack shaft; 8, second countershaft; 9, one grade of driving gear; 10, second gear driving gear; 11, third speed drive gear; 12, fourth gear driving gear; 13, five grades of driving gears; 14, reverse driving gear; 15, reverse idler gear; 16, first speed driven gear; 17, two or three reverse gear driven gears; 18, four or five grades of driven gears; 19, planetary mechanism sun gear; 20, planetary mechanism planet wheel; 21, planetary mechanism input gear; 22, a third gear synchronizer; 23, planetary mechanism gear ring; 24, differential mechanism; 25, bearing; 26, planet carrier; 27, five reverse gear synchronizers; 28, two fourth gear synchronizers; 29, input shaft.
Embodiment
Embodiment 1: as depicted in figs. 1 and 2, a kind of double-clutch automatic gearbox, comprise input shaft 29, input shaft gear 1, first countershaft 6, second countershaft 8, jack shaft 7, power take-off, be fixed on the first clutch 2 on described first countershaft 6, be fixed on the second clutch 3 on described second countershaft 8, described power take-off comprises differential mechanism 24, the planetary mechanism of fixedlying connected with described differential mechanism 24, described planetary mechanism comprises sun gear 19, planet wheel 20, planet input gear 21, gear ring 23, planet carrier 26; Driven gear on described planet input gear 21 and the described jack shaft 7 meshes and fixes with described sun gear 19, and described gear ring 23 and described differential mechanism 24 are fixing, and the housing of described planet carrier 26 and speed changer is fixed; Described input shaft 29 is set to parallel type with described jack shaft 7, and described first countershaft 6 and described second countershaft 8 are arranged on described jack shaft 7 both sides; Be disposed with first clutch 2, first clutch gear 5, five grades of driving gears 13, five reverse gear synchronizers 27, reverse driving gear 14, third speed drive gear 11, a third gear synchronizer 22 and one grade of driving gear 9 on described first countershaft 6; Be disposed with second clutch 3, second clutch gear 4, fourth gear driving gear 12, two fourth gear synchronizers 28 and second gear driving gear 10 on described second countershaft 8; Be disposed with four or five grades of driven gears, 18,23 reverse gear driven gears 17 and first speed driven gear 16 on the described jack shaft 7; Described reverse driving gear 14 arrives described reverse gear driven gear 17 by the reverse idler gear 15 that is arranged on the reverse gear shaft with transmission of power; Described input shaft 29 and described input shaft gear 1 are integral type.
Therefore when vehicle remained static, first clutch 2 and second clutch 3 were in separated state, transfer motion power not.
When needing to obtain one grade, the gearshift mechanism (not shown) is stirred a third gear synchronizer 22 in advance and is put into first gear driving gear 9, engine power is through being passed to input gear 1 behind the torsional vibration damper, 1 engagement of input gear is passed to first clutch gear 5, this moment first clutch 2 closures, transmission of power is given first countershaft 6; One grade of driving gear 9 engagement first speed driven gear 16 rotates; Jack shaft 7 rotates; Planetary mechanism input gear 21 is accepted the power input of four or five grades of driven gears 18 on the jack shaft, drives 19 rotations of planetary mechanism sun gear, 20 rotations of planetary mechanism planet wheel, 23 rotations of planetary mechanism gear ring, differential mechanism 24 rotations, power output.
When needing to obtain second gear, the gearshift mechanism (not shown) is stirred two fourth gear synchronizers 28 in advance and is put into second gear driving gear 10, engine power is through being passed to input gear 1 behind the torsional vibration damper, input gear 1 is passed to second clutch gear 4 with the engine power engagement, second clutch 3 closures, transmission of power is given second countershaft 8; Second gear driving gear 10 engagement second gear driven gears 17 rotate; Jack shaft 7 rotates; Planetary mechanism input gear 21 is accepted the power input of four or five grades of driven gears 18 on the jack shaft, drives 19 rotations of planetary mechanism sun gear, 20 rotations of planetary mechanism planet wheel, 23 rotations of planetary mechanism gear ring, differential mechanism 24 rotations, power output.
When needing to obtain third gear, the gearshift mechanism (not shown) is stirred a third gear synchronizer 22 in advance and is put into third gear driving gear 11, and engine power is through being passed to input gear 1 behind the torsional vibration damper, and 1 engagement of input gear is passed to first clutch gear 5; First clutch 2 closures, transmission of power is given first countershaft 6; Third speed drive gear 11 engagement third gear driven gears 17 rotate; Jack shaft 7 rotates; Planetary mechanism input gear 21 is accepted the power input of four or five grades of driven gears 18 on the jack shaft, drives 19 rotations of planetary mechanism sun gear, 20 rotations of planetary mechanism planet wheel, 23 rotations of planetary mechanism gear ring, differential mechanism 24 rotations, power output.
When needing to obtain fourth gear, the gearshift mechanism (not shown) is stirred two fourth gear synchronizers 28 in advance and is put into fourth gear driving gear 12, and engine power is through being passed to input gear 1 behind the torsional vibration damper; Input gear 1 is passed to second clutch gear 4 with the engine power engagement; Second clutch 3 closures, transmission of power is given second countershaft 8; Fourth gear driving gear 12 engagement fourth gear driven gears 18 rotate; Jack shaft 7 rotates; Planetary mechanism input gear 21 is accepted the power input of four or five grades of driven gears 18 on the jack shaft, drives 19 rotations of planetary mechanism sun gear, 20 rotations of planetary mechanism planet wheel, 23 rotations of planetary mechanism gear ring, differential mechanism 24 rotations, power output.
When needing to obtain five grades, the gearshift mechanism (not shown) is stirred five reverse gear synchronizers 27 in advance and is put into fifth gear driving gear 13, and engine power is through being passed to input gear 1 behind the torsional vibration damper; 1 engagement of input gear is passed to first clutch gear 5; First clutch 2 closures, transmission of power is given first countershaft 6; Five grades of driven gears of five grades of driving gear 13 engagements 18 rotate; Jack shaft 7 rotates; Planetary mechanism input gear 21 is accepted the power input of four or five grades of driven gears 18 on the jack shaft, drives 19 rotations of planetary mechanism sun gear, 20 rotations of planetary mechanism planet wheel, 23 rotations of planetary mechanism gear ring, differential mechanism 24 rotations, power output.
When needing reverse gear, the gearshift (not shown) is stirred five reverse gear synchronizers 27 in advance and is hung up reverse driving gear 14, and engine power is through being passed to input gear 1 behind the torsional vibration damper, and 1 engagement of input gear is passed to first clutch gear 5; First clutch 2 closures, transmission of power is given first countershaft 6; Reverse driving gear 14 engagement reverse idler gears 15 rotate; Reverse idler gear 15 engagement reverse gear driven gears 17 rotate, and jack shaft 7 rotates; Planetary mechanism input gear 21 is accepted the power input of four or five grades of driven gears 18 on the jack shaft, drives 19 rotations of planetary mechanism sun gear, 20 rotations of planetary mechanism planet wheel, 23 rotations of planetary mechanism gear ring, differential mechanism 24 rotations, power output.
The present invention includes but be not limited to above embodiment; as long as the power take-off of double-clutch automatic gearbox comprises differential mechanism, be fixed on differential mechanism sprocket wheel on the described differential mechanism, be fixed on output drive sprocket and the discharging chain that is connected described differential mechanism sprocket wheel and described output drive sprocket on the described jack shaft, all drop in protection scope of the present invention.
The present invention includes but be not limited to above embodiment,, all drop in protection scope of the present invention as long as the power take-off of speed changer comprises differential mechanism and the planetary mechanism of fixedlying connected with described differential mechanism.
Claims (6)
1, a kind of double-clutch automatic gearbox, comprise input shaft (29), input shaft gear (1), first countershaft (6), second countershaft (8), jack shaft (7), power take-off, at least one odd gear gear pair, at least one even number shifting gear pair, be fixed on the first clutch (2) on described first countershaft (6), be fixed on the second clutch (3) on described second countershaft (8), it is characterized in that: described power take-off comprises differential mechanism (24), the planetary mechanism of fixedlying connected with described differential mechanism (24).
2, double-clutch automatic gearbox as claimed in claim 1 is characterized in that: described planetary mechanism comprises sun gear (19), planet wheel (20), planet input gear (21), gear ring (23), planet carrier (26); Driven gear engagement on described input gear (21) and the described jack shaft (7) and fixing with described sun gear (19), described gear ring (23) is fixing with described differential mechanism (24), and the housing of described planet carrier (26) and speed changer is fixed.
3, double-clutch automatic gearbox as claimed in claim 1 or 2 is characterized in that: described input shaft (29), first countershaft (6), second countershaft (8) are arranged at interval.
4, double-clutch automatic gearbox as claimed in claim 3 is characterized in that: described input shaft (29) is set to parallel type with described jack shaft (7), and described first countershaft (6) and described second countershaft (8) are arranged on described jack shaft (7) both sides.
5, double-clutch automatic gearbox as claimed in claim 4 is characterized in that: be disposed with first clutch (2), first clutch gear (5), five grades of driving gears (13), five reverse gear synchronizers (27), reverse driving gear (14), third speed drive gear (11), a third gear synchronizer (22) and one grade of driving gear (9) on described first countershaft (6); Be disposed with second clutch (3), second clutch gear (4), fourth gear driving gear (12), two fourth gear synchronizers (28) and second gear driving gear (10) on described second countershaft (8); Be disposed with four or five grades of driven gears (18), two or three reverse gear driven gears (17) and first speed driven gear (16) on the described jack shaft (7); Described reverse driving gear (14) arrives described reverse gear driven gear (17) by the reverse idler gear (15) that is arranged on the reverse gear shaft with transmission of power.
6, double-clutch automatic gearbox as claimed in claim 5 is characterized in that: described input shaft (29) and described input shaft gear (1) are integral type.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA200810233387XA CN101446337A (en) | 2008-12-17 | 2008-12-17 | Double-clutch automatic gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA200810233387XA CN101446337A (en) | 2008-12-17 | 2008-12-17 | Double-clutch automatic gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101446337A true CN101446337A (en) | 2009-06-03 |
Family
ID=40742147
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200810233387XA Pending CN101446337A (en) | 2008-12-17 | 2008-12-17 | Double-clutch automatic gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101446337A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102425647A (en) * | 2011-11-30 | 2012-04-25 | 重庆青山工业有限责任公司 | Power transmission mechanism for double-clutch automatic transmission |
| CN101737462B (en) * | 2009-12-17 | 2012-05-16 | 重庆青山工业有限责任公司 | Double-clutch transmission mechanism |
| CN101985980B (en) * | 2009-07-28 | 2015-04-15 | 现代自动车株式会社 | Shifting mechanism for double clutch transmission |
| WO2017185901A1 (en) * | 2016-04-28 | 2017-11-02 | 舍弗勒技术股份两合公司 | Transaxle and two-speed drive module thereof |
| CN108278336A (en) * | 2018-03-29 | 2018-07-13 | 徐州徐工矿山机械有限公司 | Articulated truck fourth gear dead axle and the hybrid gearbox of planetary gear and implementation method |
| CN109723769A (en) * | 2019-03-08 | 2019-05-07 | 重庆青山工业有限责任公司 | The two reduction gear of pure electric vehicle retarder |
| WO2021087946A1 (en) * | 2019-11-08 | 2021-05-14 | 舍弗勒技术股份两合公司 | Two-gear variable-speed bridge drive system having dual clutch |
-
2008
- 2008-12-17 CN CNA200810233387XA patent/CN101446337A/en active Pending
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101985980B (en) * | 2009-07-28 | 2015-04-15 | 现代自动车株式会社 | Shifting mechanism for double clutch transmission |
| CN101737462B (en) * | 2009-12-17 | 2012-05-16 | 重庆青山工业有限责任公司 | Double-clutch transmission mechanism |
| CN102425647A (en) * | 2011-11-30 | 2012-04-25 | 重庆青山工业有限责任公司 | Power transmission mechanism for double-clutch automatic transmission |
| CN102425647B (en) * | 2011-11-30 | 2013-12-04 | 重庆青山工业有限责任公司 | Power transmission mechanism for double-clutch automatic transmission |
| WO2017185901A1 (en) * | 2016-04-28 | 2017-11-02 | 舍弗勒技术股份两合公司 | Transaxle and two-speed drive module thereof |
| CN107323255A (en) * | 2016-04-28 | 2017-11-07 | 舍弗勒技术股份两合公司 | Transaxle and its double speed drive module |
| US10808814B2 (en) | 2016-04-28 | 2020-10-20 | Schaeffler Technologies AG & Co. KG | Transaxle and two-speed drive module thereof |
| CN108278336A (en) * | 2018-03-29 | 2018-07-13 | 徐州徐工矿山机械有限公司 | Articulated truck fourth gear dead axle and the hybrid gearbox of planetary gear and implementation method |
| CN108278336B (en) * | 2018-03-29 | 2023-06-23 | 徐州徐工矿业机械有限公司 | Four-gear fixed shaft and planetary gear hybrid gearbox of hinged dumper and implementation method |
| CN109723769A (en) * | 2019-03-08 | 2019-05-07 | 重庆青山工业有限责任公司 | The two reduction gear of pure electric vehicle retarder |
| WO2021087946A1 (en) * | 2019-11-08 | 2021-05-14 | 舍弗勒技术股份两合公司 | Two-gear variable-speed bridge drive system having dual clutch |
| CN114222677A (en) * | 2019-11-08 | 2022-03-22 | 舍弗勒技术股份两合公司 | Two-gear speed change bridge driving system with double clutches |
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Open date: 20090603 |