CN201502667U - Double-clutch gearbox - Google Patents
Double-clutch gearbox Download PDFInfo
- Publication number
- CN201502667U CN201502667U CN2009200750144U CN200920075014U CN201502667U CN 201502667 U CN201502667 U CN 201502667U CN 2009200750144 U CN2009200750144 U CN 2009200750144U CN 200920075014 U CN200920075014 U CN 200920075014U CN 201502667 U CN201502667 U CN 201502667U
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- Prior art keywords
- gear
- retaining
- gears
- driving
- driven
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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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- 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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The utility model discloses a double-clutch gearbox which comprises two input shafts, two middle shafts and a reversing shaft, wherein the two input shafts are divided into an inner input shaft and an outer input shaft which are coaxially arranged, driving gears of each gear are arranged on the two input shafts, driven gears of each gear, which are engaged with the driving gears, are arranged on the two middle shafts, and a first-gear driving gear and a second-gear driving gear are positioned at both sides of all the driving gears of other gears. The low-gear first-gear gears and the low-gear second-gear gears are respectively arranged at both ends of a shafting, which has the advantages that supporting bearings are existed at both ends of the shafting, the rigidity of the system is better, and the influence of the maximum load and the alternating torque can be borne. In a similar way, a reversing driven gear and a first-gear driven gear are driven by sharing the first-gear driving gear, and the influence of bearing large load and alternating torque during reversing is resisted. By the structure, the damage rate caused by the deformation of the shafting to the gears can be reduced, and the service life of the low-gear gears under high load is enhanced.
Description
Technical field
The utility model relates to double clutch gearbox, is specifically related to the structural configuration of a kind of double clutch gearbox middle gear and axle.
Background technique
Use at present the general car of traditional speed changer, under the road conditions more than 80%, can only utilize 40% of power potential, and can only utilize 25% of power potential in that the road conditions in urban district is next.Analysis expert shows: AT (traditional hydraulic machine automatic transmission) can carry out functions such as complicated acceleration, deceleration, gearshift automatically, have speed change level and smooth, drive advantages such as light, but its aspect oil consumption than the high 5%-15% of manual transmission; CVT (stepless speed variator) though have soft, the comfortable characteristics of speed ratio, the excessive not fuel-economizing of energy loss in the speed changer, bearing torque also has narrow limitation, the manufacture cost height; AMT (manual-automatic integral speed changer) is more energy-conservation than AT and MT (manual transmission), is the single clutch structure but its adopts, has impassable technology and hinders---the power interruption phenomenon, generally be applied on the large-scale passenger car and commercial car on.
The employing of DCT (double clutch gearbox) not only can guarantee to improve most effectively toxic emission, improves transmission efficiency, reduces energy consumption, and only energy-conservation just high by 15% than 5 fast AT, if be complementary with mixed power, energy-saving effect can be more obvious.
DCT all has outstanding advantage on transmission efficiency and manufacture cost.DCT is made up of following major component: its body portion is made up of shift gear, main driven shaft, bearing, synchronizer, shift fork, housing etc., and the axle sleeve axle construction technology content that is adopted is very high; The information that electronic control unit is sent to according to each ECU on each sensor and the CAN bus, judge the gearshift demand, and calculate and select best gearshift opportunity according to setting program, send shifting commands, allow the gearshift performance element finish the gearshift action, its control program than traditional automatic transmission complexity many, whole process all automatically performs and finishes; The gearshift performance element is converted into the hydraulic machinery action to the instruction of TCU, promotes the clutch of double clutch and the slippage of selector fork and finally realizes self shifter and speed change.
Chinese invention patent application 200410070324.9 discloses a kind of double clutch gearbox, it has two coaxial input shafts, two output shafts that are arranged in parallel and a reverse gear shaft, be fixed with a retaining, three retaining driving gears in its input shaft on the axle, be fixed with two retainings, four retaining driving gears on its input shaft outer shaft, be furnished with a retaining, two retainings, three retainings and four retaining driven gears on first output shaft, be furnished with five retainings, six retaining and the driven gears that reverse gear on second output shaft.Wherein a retaining driving gear and a retaining driven gear, the driven gear that reverses gear mesh simultaneously; Two retaining driving gears are meshed with two retaining driven gears; Three retaining driving gears and three retaining driven gears, five retaining driven gears mesh simultaneously; Four retaining driving gears keep off driven gears with four retaining driven gears, six and mesh simultaneously, like this, on the input shaft only four driving gears just can realize that six forward gears and one reverses gear, can reduce the quantity of gear, the length of gearbox is shortened dramatically.But, in this double clutch gearbox, four driving gears are according to three retaining driving gears, one retaining driving gear, the order of two retaining driving gears and four retaining driving gears is arranged successively, that is to say, the driving gear of its high gear is arranged in the two ends of input shaft, and the driving gear of low gear is arranged in the centre of input shaft, the defective that this structure exists is: a retaining (reversing gear) that will bear maximum load, two retaining driving gears are arranged in the neutral position of input shaft, the rigidity of system is relatively poor, axle system distortion causes the damage of low gear gear easily, reduces the working life of low gear gear under high capacity.
The model utility content
It is good that the technical problems to be solved in the utility model provides a kind of system rigidity, the double clutch gearbox of long service life.
In order to solve the problems of the technologies described above, the utility model adopts following technological scheme: a kind of double clutch gearbox, comprise two input shafts, two jack shafts and a reverse gear shaft, two input shafts are divided into the interior input shaft and the outer input shaft of coaxial arrangement, two input shafts are provided with each gear driving gear, two jack shafts are provided with each the gear driven gear that is meshed with described driving gear, and a described retaining driving gear and two retaining driving gears are positioned at the both sides of all other gear driving gears.
Preferably, a described retaining driving gear is positioned at the rear end of input shaft, and described two retaining driving gears are positioned at the front end of input shaft.
Preferably, input shaft is provided with a described retaining driving gear and three retaining driving gears in described, described outer input shaft is provided with described two retaining driving gears and four retaining driving gears, described first jack shaft is provided with a retaining, two retainings, three retainings and four retaining driven gears, described second jack shaft is provided with five retainings, six retaining driven gears, described reverse gear shaft is provided with the driven gear that reverses gear, a described retaining driving gear and a retaining driven gear, the driven gear that reverses gear meshes simultaneously, described two retaining driving gears are meshed with two retaining driven gears, described three retaining driving gears and three retaining driven gears, five retaining driven gears mesh simultaneously, described four retaining driving gears and four retaining driven gears, six retaining driven gears mesh simultaneously.
Further, described each gear driving gear is fixedly mounted on the input shaft, and described each gear driven gear is installed in rotation on the jack shaft and can be synchronous by synchronizer and jack shaft.
Further, also be provided with the driving gear that reverses gear on the described reverse gear shaft, be rotatably mounted with second driven gear that reverses gear on described second jack shaft, second driven gear that reverses gear is meshed with the driving gear that reverses gear, and second reverses gear is provided with synchronizer between the driven gear and second jack shaft.
Further, the described driving gear that reverses gear axially is being in concordant position with two retaining driving gears.
Further, described two jack shafts are connected with differential mechanism by a main gear down device.
Further, described main gear down device comprises two the main deceleration driving gears and a main deceleration driven gear that is connected with differential mechanism that are separately fixed on two jack shafts, and main deceleration driven gear and two main deceleration driving gears mesh simultaneously.
Further, the two ends of described first jack shaft are equipped with bearing, and described main deceleration driving gear, blocks to four retaining driven gears all between the bearing at two ends.
Further, the two ends of described second jack shaft are equipped with bearing, and described main deceleration driving gear, second reverses gear driven gear, five retaining driven gears and six retaining driven gears all between the bearing at two ends.
The beneficial effects of the utility model are: the two ends that a retaining of bottom gear, second gear are arranged in axle system, the benefit of this layout is, axle is that two ends all exist spring bearing, and the rigidity of system is better, can bear the maximum load and the influence of alternate torque.The shared retaining driving gear of a driven gear and a retaining driven gear that reverses gear equally drives heavy load and alternate torque are born in opposing when reversing gear influence.This structure can reduce the damage ratio that the distortion of axle system causes gear, improves the working life of low gear gear under high capacity.
Another advantage of the present utility model be adopted many to shared gear, wherein one the retaining driven gear with reverse gear driven gear shared one the retaining driving gear; The shared three retaining driving gears of three retaining driven gears and five retaining driven gears; The shared four retaining driving gears of four retaining driven gears and six retaining driven gears; Two shared main deceleration driven gears of main deceleration driving gear, such structure has been saved axial space greatly, for the horizontal speed changer of compact type, improve the flexibility of engine compartment layout, reduced part simultaneously, greatly reduced the cost of speed changer.The shortening of speed changer axial length has also improved the rigidity of axle system, and the minimizing axle ties up to the distortion under the big load, improves the transmission accuracy of gear.
Description of drawings
Below in conjunction with the drawings and specific embodiments the utility model is described in further detail.
Fig. 1 is the structural representation of the utility model double clutch gearbox.
Fig. 2 shows a retaining driving gear, a retaining driven gear, the driven gear that reverses gear, the driving gear that reverses gear, main deceleration driving gear and main deceleration driven gear, and the correlation of each.
Fig. 3 is the sectional structure chart of the utility model double clutch gearbox.
Among the figure:
1, outer clutch 2, internal clutch 3, clutch driving shaft 4, interior input shaft
5, outer input shaft 6, a retaining driving gear 7, a retaining driven gear 8, two retaining driving gears
9, two retaining driven gears 10, three retaining driving gears 11, three retaining driven gears 12, four retaining driving gears
13, four retaining driven gears 14, five retaining driven gears 15, six keep off driven gears 16, driven gear reverses gear
17, reverse gear driving gear 18, second reverse gear driven gear 19, main deceleration driving gear
20, main deceleration driving gear 21, main deceleration driven gear 22, differential mechanism 23-26, synchronizer
27, first jack shaft 28, second jack shaft 29, reverse gear shaft 33, bearing
35, bearing G1-G6, one the retaining---six the retaining RG, reverse gear
Embodiment
As Fig. 1, shown in Figure 3, a kind of double clutch gearbox of the utility model, the input shaft 4,5 of its two coaxial arrangement is connected with two clutches 1,2 respectively, the output shaft of motor is connected with clutch driving shaft 3, input shaft 4 or outer input shaft 5 in the moment of torsion of motor can optionally be delivered to by two clutches 1,2.Wherein, be installed with the rear end (away from an end of motor) that a retaining driving gear 6 and three retaining driving gears, 10, one retaining driving gears 6 are positioned at input shaft 4 on the interior input shaft 4; Be installed with two retaining driving gears 8 and four retaining driving gears 12 on the outer input shaft 5, two retaining driving gears 8 are positioned at the front end (near an end of motor) of outer input shaft 5, like this, from whole input shaft 4,5, two retaining driving gears 8 and a retaining driving gear 6 are positioned at forward and backward both sides, and three gear driving gears 10 and four retaining driving gears 12 are between them.
Two jack shafts 27,28 and reverse gear shaft 29 all parallel with input shaft 4,5, and wherein first jack shaft 27 is provided with one to four retaining driven gear, they respectively with input shaft on the driving gear of corresponding gear be meshed, constituted different gears.Therefore two retaining driven gears 9, four retaining driven gears 13, three retaining driven gears 11 and a retaining driven gear 7 are arranged in order from front to back on first jack shaft 27.These four driven gears all by bearings on first jack shaft 27, therefore can rotate with respect to first jack shaft 27.Between two retaining driven gears 9 and four retaining driven gears 13, be provided with synchronizer 24, between three retaining driven gears 11 and a retaining driven gear 7, be provided with synchronizer 23, by synchronizer 23,24, each driven gear can optionally rotate with first jack shaft 27 synchronously.First jack shaft 27 also fixedly mount a main deceleration driving gear 19 foremost, to export the moment of torsion of first jack shaft 27.The two ends of first jack shaft 27 are equipped with bearing 33, and main deceleration driving gear 19, blocks to four retaining driven gears 7,9,11,13 all between the bearing 33 at two ends.This structure has improved the rigidity of support of main deceleration driving gear 19, has reduced the magnitude of misalignment of gear in transmission, helps guaranteeing the transmission accuracy of final gear, reduces noise; Simultaneously, this structure can reduce quantity and a plurality of housing of case of transmission the integrating error that produce are installed, and the bolt quantity that connects housing also significantly reduces, and has reduced assembly cost and installation difficulty.
Be installed with the driven gear 16 that reverses gear on the reverse gear shaft 29, reverse gear driven gear 16 also with one the retaining driving gear 6 be meshed, see shown in Figure 2, promptly reverse gear and one the retaining a shared driving gear 6.At the front end of reverse gear shaft 29, in axially concordant fixed-site the driving gear 17 that reverses gear is installed with two retaining driving gears 8.
The moment of torsion of two jack shafts 27,28 all outputs to differential mechanism 22, connection-main deceleration driven gear 21 on the differential mechanism 22, two main deceleration driving gears 19,20 on main deceleration driven gear 21 and two jack shafts 27,28 mesh simultaneously, as shown in Figure 2, like this, main deceleration driving gear 19,20 and main deceleration driven gear 21 just constitute a main gear down device, and this main gear down device couples together two jack shafts 27,28 and differential mechanism 22.
Synchronizer is in company with the jack shaft rotation and utilize free-sliding spline to move axially on axle.When shifting gears, by the shift fork in the gearshift actuator synchronizer is dialled vertically to the gear driven gear, tooth cover in the synchronizer carries out combination with the tooth that combines on the gear driven gear, make gear driven gear and jack shaft be combined as a whole, because driving gear and gear driven gear fixing on the input shaft are in normal engagement, and driving gear driven gear, thereby input shaft will drive jack shaft according to this speed ratio to the active/driven shift gear of engagement, finish the driving between the disalignment, the process of transmission power.Owing to adopted double clutch, dual input shaft structure in the double clutch gearbox, have two power transfer path, therefore when carrying out the gear switching, a pair of gear on next gear (being positioned on another root input shaft) can be meshed in advance by synchronizer, carry out the clutch exchange then, finish gearshift, can avoid the power interruption phenomenon in the shift process like this.
In the utility model, double clutch is coaxial wet-type dual-clutch, and internal clutch 2 is even number gear clutches, combines with the outer input shaft 5 of speed changer by spline, outer clutch 1 is an odd number gear clutch, combines with the interior input shaft 4 of speed changer by spline.When gear switches, the target gear can be under the state of current shift combination, carry out combination in advance, in conjunction with principle be that the odd number gear replaces with the even number gear and combines, two odd number gears or two even number gear combinations simultaneously, be current shift when being the odd number gear, the target gear of pre-combination can only be the even number gear, can not be odd number gear (control of this function is controlled by the TCU of speed changer).Early stage in shift process, under the situation of current shift and target gear combination simultaneously, one on the odd number clutch of double clutch and even number clutch are the states of combination, another is the state that separates, continuation along with shift process, the clutch that separates carries out combination, the clutch of combination simultaneously separates, in conjunction with separating process in, between the active friction plate of clutch inside and the driven friction owing to the decline of combination force, the sliding phenomenon of rubbing can appear, like this, though the combination simultaneously of current shift and target gear can be because of the different phenomenon that interference occurs of rotating speed between the axle system in shift process yet.
Claims (10)
1. double clutch gearbox, comprise two input shafts (4,5), two jack shafts (27,28) and a reverse gear shaft (29), two input shafts are divided into the interior input shaft (4) and the outer input shaft (5) of coaxial arrangement, and two input shafts are provided with each gear driving gear (6,8,10,12), two jack shafts are provided with each the gear driven gear (7,9 that is meshed with described driving gear, 11,13,14,15), it is characterized in that: a described retaining driving gear (6) and two retaining driving gears (8) are positioned at the both sides of all other gear driving gears (10,12).
2. double clutch gearbox according to claim 1 is characterized in that: a described retaining driving gear (6) is positioned at the rear end of input shaft, and described two retaining driving gears (8) are positioned at the front end of input shaft.
3. double clutch gearbox according to claim 1, it is characterized in that: input shaft (4) is provided with a described retaining driving gear (6) and three retaining driving gears (10) in described, described outer input shaft (5) is provided with described two retaining driving gears (8) and four retaining driving gears (12), described first jack shaft (27) is provided with a retaining, two retainings, three retainings and four retaining driven gears (7,9,11,13), described second jack shaft (28) is provided with five retainings, six retaining driven gears (14,15), described reverse gear shaft (29) is provided with the driven gear that reverses gear (16), a described retaining driving gear (6) and a retaining driven gear (7), the driven gear (16) that reverses gear meshes simultaneously, described two retaining driving gears (8) are meshed with two retaining driven gears (9), described three retaining driving gears (10) and three retaining driven gears (11), five retaining driven gears (14) mesh simultaneously, described four retaining driving gears (12) and four retaining driven gears (13), six retaining driven gears (15) mesh simultaneously.
4. double clutch gearbox according to claim 3 is characterized in that: described each gear driving gear (6,8,10,12) be fixedly mounted on the input shaft (4,5), described each gear driven gear (7,9,11,13,14,15) be installed in rotation on jack shaft (27,28) go up and can pass through synchronizer (23,24,25,26) synchronous with jack shaft.
5. double clutch gearbox according to claim 3, it is characterized in that: also be provided with the driving gear that reverses gear (17) on the described reverse gear shaft (29), be rotatably mounted with second driven gear (18) that reverses gear on described second jack shaft (28), second driven gear (18) that reverses gear is meshed with the driving gear that reverses gear (17), and second reverses gear is provided with synchronizer (26) between the driven gear (18) and second jack shaft.
6. double clutch gearbox according to claim 5 is characterized in that: the described driving gear that reverses gear (17) axially is being in concordant position with two retaining driving gears (8).
7. double clutch gearbox according to claim 3 is characterized in that: described two jack shafts (27,28) are connected with differential mechanism (22) by a main gear down device.
8. double clutch gearbox according to claim 7, it is characterized in that: described main gear down device comprises two main deceleration driving gears (19 that are separately fixed on two jack shafts, 20) with a main deceleration driven gear (21) that is connected with differential mechanism, main deceleration driven gear (21) meshes simultaneously with two main deceleration driving gears (19,20).
9. double clutch gearbox according to claim 8, it is characterized in that: the two ends of described first jack shaft (27) are equipped with bearing (33), and described main deceleration driving gear (19), blocks to four retaining driven gears (7,9,11,13) all be positioned between the bearing (33) at two ends.
10. double clutch gearbox according to claim 8, it is characterized in that: the two ends of described second jack shaft (28) are equipped with bearing (35), and described main deceleration driving gear (20), second reverses gear, and driven gear (18), five keeps off driven gears (14) and six retaining driven gears (15) all are positioned between the bearing (35) at two ends.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200750144U CN201502667U (en) | 2009-07-21 | 2009-07-21 | Double-clutch gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200750144U CN201502667U (en) | 2009-07-21 | 2009-07-21 | Double-clutch gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201502667U true CN201502667U (en) | 2010-06-09 |
Family
ID=42453600
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009200750144U Expired - Lifetime CN201502667U (en) | 2009-07-21 | 2009-07-21 | Double-clutch gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201502667U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102278428A (en) * | 2010-06-13 | 2011-12-14 | 上海汽车集团股份有限公司 | Dual-clutch transmission gearbox |
| CN103649589A (en) * | 2011-07-08 | 2014-03-19 | 三菱自动车工业株式会社 | Transmission |
-
2009
- 2009-07-21 CN CN2009200750144U patent/CN201502667U/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102278428A (en) * | 2010-06-13 | 2011-12-14 | 上海汽车集团股份有限公司 | Dual-clutch transmission gearbox |
| CN103649589A (en) * | 2011-07-08 | 2014-03-19 | 三菱自动车工业株式会社 | Transmission |
| CN103649589B (en) * | 2011-07-08 | 2016-03-30 | 三菱自动车工业株式会社 | Speed change gear |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20100609 |