CN102269240B - Arrangement structure of gear shaft system of gearbox - Google Patents
Arrangement structure of gear shaft system of gearbox Download PDFInfo
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- CN102269240B CN102269240B CN201010188708.6A CN201010188708A CN102269240B CN 102269240 B CN102269240 B CN 102269240B CN 201010188708 A CN201010188708 A CN 201010188708A CN 102269240 B CN102269240 B CN 102269240B
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Abstract
The invention relates to an arrangement structure of a gear shaft system of a gearbox. The arrangement structure comprises an input shaft as well as a first output shaft and a second output shaft which are in parallel with the input shaft and are arranged at the two sides of the input shaft, wherein driving gears are fixed on the input shaft; driven gears are sleeved on the output shafts in an idle manner; the driving gears are meshed with corresponding driven gears and drive the driven gears to rotate; at the same time, the first and second output shafts are provided with joint devices which are matched with the driven gears and are used for switching gears; and the first and second output shafts are driven by the joint devices to rotate to output power. Compared with the prior art, the arrangement structure has the following beneficial effects: the arrangement of the inner space of the gearbox is balanced and reasonable; the number ratio is easy to match; and the axial distance is shorter.
Description
Technical field
The present invention relates to a kind of layout of gear shafts of gearbox, relate in particular to a kind of geared rotor system arrangement of six grades of manual transmission.
Background technique
At the nineties initial stage, the gearbox of five gears quietly rises.Each large automobile brand, comprises benz, Mitsubishi, Honda, Santana etc., all starts successively to release the vehicle that is equipped with five gear gearboxes.Generally speaking, the 5th gear is generally the second overdirve gear, reduces variable velocity ratio, improves the speed of a motor vehicle, is after expressway started to popularize at home at that time, the new demand of user to automotive performance.In the near future, the development in market makes the automobile that is equipped with five gear gearboxes become main flow.The structural principle of great majority five gear gearboxes is all that the direct engagement by input shaft and output shaft gear realizes speed change.
And six grades of manual transmission of rising in recent years belong to advanced technology at home, from market, use, compare traditional five speed gearbox, advantage is: 1, gearshift is more level and smooth, and transition is more steady, drives more comfortable; 2, more reduction speed ratio provides more output speed to select, thereby can adapt to more road conditions and driving demand; 3, reduce the burden of motor, possessed more outstanding fuel-economizing performance simultaneously; 4, the higher speed of a motor vehicle, feel.From structural design, an input shaft, the layout of two output shafts makes whole chest balance more.
But the layout of existing six grades of gear shafts of gearboxes is subject to various factors: the coupling of number ratio, the coupling of centre distance, the restriction in space, the space of bonding apparatus and gear, axial size, stressed equilibrium etc., its geared rotor system is arranged mostly reasonable not, as Japanese laid-open patent discloses a manual transmission No. 4382973 on October 2nd, 2009, its shaft system arrangement by gear has been realized six grades of hand gears, but the shift sequence of these manual transmission three fourth gear and one two and 56 grades are not inconsistent, need extra gear shift transformation mechanism to realize, simultaneously, the more difficult coupling of number, and axial distance is long.
In view of this, be necessary to provide a kind of layout more reasonable, six grades of less manual transmission take up space.
Summary of the invention
For the deficiencies in the prior art, the technical problem that the present invention solves is to provide a kind of layout of novel gear shafts of gearbox, and it,, by changing the layout of conventional gears, makes gearbox internal structure more succinct.
For solving the problems of the technologies described above, technological scheme of the present invention is achieved in that
A kind of layout of gear shafts of gearbox, comprise an input shaft, be parallel to described input shaft and be positioned at the first output shaft and second output shaft of described input shaft both sides, on described input shaft, be fixed with driving gear, on described output shaft, be set with driven gear, wherein, on described the first output shaft, be set with third gear driven gear, fourth gear driven gear and reverse gear, on described the second output shaft, be set with first speed driven gear, second gear driven gear, five grades of driven gears and six grades of driven gears, on described input shaft, be installed with one grade of driving gear, two third speed drive gears, input shaft fourth gear/five grade duplicate gear and six grades of driving gears, described six grades of driving gears are arranged between described two third speed drive gears and described four or five grades of driving gears, described first speed driven gear and described one grade of driving gear engagement, described second gear driven gear and described third gear driven gear and described two third speed drive gear engagements, described fourth gear driven gear and described five grades of driven gears and described four or five grades of driving gears engagement, described six grades of driven gears and described six grades of driving gears engagement, described reverse gear and the engagement of described first speed driven gear, and can be driven rotation by described first speed driven gear, on described the first output shaft and on described the second output shaft, be also provided with described driven gear and match and merge for switching the bonding apparatus of gear.
Further, be also provided with the one first main driving gear that subtracts on described the first output shaft, described reverse gear is arranged at the described first main subtracting between driving gear and described third gear driven gear.
Described bonding apparatus comprises reverse gear bonding apparatus, and it is arranged on described the first output shaft, is arranged between described third gear driven gear and described reverse gear, and during reverse gear, described reverse gear bonding apparatus engages with described reverse gear.
Described bonding apparatus also comprises the first bonding apparatus being arranged between described first speed driven gear and described second gear driven gear.
Described bonding apparatus also comprises the second bonding apparatus being arranged between described third gear driven gear and described fourth gear driven gear.
Described bonding apparatus also comprises the 3rd bonding apparatus being arranged between described five grades of driven gears and described six grades of driven gears.
Compared with prior art, the invention has the beneficial effects as follows: gearbox inner space arranges balance and rationally, number is than good coupling, and axial distance is shorter.
Accompanying drawing explanation
Figure 1 shows that the layout schematic diagram of best mode for carrying out the invention gear shafts of gearbox.
Embodiment
As shown in Figure 1, in the layout preferred forms of manual transmission geared rotor system of the present invention, in described manual transmission, be provided with an input shaft 10, parallel and be positioned at the first output shaft 20 and second output shaft 30 of described input shaft 10 both sides, on this input shaft 10, be fixed with one grade of driving gear 101,102,45 grades of driving gears 104 of two third speed drive gears and six grades of driving gears 106, wherein, described six grades of driving gears 106 are arranged between described two third speed drive gears 102 and described four or five grades of driving gears 104.
On described the first output shaft 20, be set with reverse gear 205, third gear driven gear 203, and fourth gear driven gear 204.Described third gear driven gear 203 is meshed with one end of two third speed drive gears 102, and can be driven rotation by two third speed drive gears 102; Fourth gear driven gear 204 is meshed with one end of four or five grades of driving gears 104, and can be driven rotation by four or five grades of driving gears 104.In addition, the first main driving gear 210 that subtracts is also installed on described the first output shaft 20, this first main driving gear 210 that subtracts subtracts driven gear (not shown) by the master who is mated and forms certain gear ratio, to reach decelerating effect when exporting, described reverse gear 205 is arranged at described third gear driven gear 203 and the described first main subtracting between driving gear 210.
On described the second output shaft 30, be set with first speed driven gear 301, second gear driven gear 302, five grades of driven gears 305 and six grades of driven gears 306.Wherein, described first speed driven gear 301 is meshed with one grade of driving gear 101, and can be driven rotation by one grade of driving gear 101; Described second gear driven gear 302 is meshed with one end of two third speed drive gears 102, and can be transfused to axle two gears 102 driving rotations; Described five grades of driven gears 305 are meshed with one end of four or five grades of driving gears 104, and can be driven and rotate by four or five grades of driving gears 104; Six grades of driven gears 306 are meshed with six grades of driving gears 106, and are driven rotation by six grades of driving gears 106.In addition, the second main main driving gear 310 that subtracts of driving gear 310, the second that subtracts is also installed on this second output shaft 30 and by the master who is mated, subtracts driven gear (not shown) and form certain gear ratio, to reach decelerating effect when the output.
In best mode for carrying out the invention, on the second output shaft 30 between first speed driven gear 301 and second gear driven gear 302, be also installed on one first bonding apparatus 401, on the first output shaft 20 between third gear driven gear 203 and fourth gear driven gear 204, be also installed on one second bonding apparatus 402, on the second output shaft 30 between five grades of driven gears 305 and six grades of driven gears 306, be also installed on one the 3rd bonding apparatus 403, described the first bonding apparatus 401 can keep relative static with described the second output shaft 30 with the 3rd bonding apparatus 403, described the second bonding apparatus 402 can keep relative static with described the first output shaft 20.
Below each gear switch and transmission principle when utilizing manual transmission geared rotor system of the present invention to carry out speed change are elaborated:
When neutral:
Engine-driving input shaft 10 rotates, and can drive with each driving gear of fixedly installing thereon and rotate in the lump, and then drive each driven gear to rotate, but because driven gear is that empty set is on output shaft, with output shaft without moment of torsion transmission, therefore the not driven rotation of output shaft.
In the time of one grade:
The first bonding apparatus 401 engages with first speed driven gear 301, so that the first bonding apparatus 401 is by described first speed driven gear 301 driven rotary, power transmission step is as follows:
A, engine-driving input shaft 10 rotate;
B, input shaft 10 drive one grade of driving gear 101 to rotate;
C, one grade of driving gear 101 drive first speed driven gear 301 to rotate;
D, first speed driven gear 301 engage with the first bonding apparatus 401, and drive the second output shaft 30 to rotate by the first bonding apparatus 401;
E, the second output shaft 30 drive the second main subtracting after driving gear 310 rotates to export.
When second gear:
The first bonding apparatus 401 engages with second gear driven gear 302, so that the first bonding apparatus 401 is by described second gear driven gear 302 driven rotary, its power transmission route is as follows:
A, engine-driving input shaft 10 rotate;
B, input shaft 10 drive two third speed drive gears 102 to rotate;
C, two third speed drive gears 102 drive second gear driven gear 302 to rotate;
D, second gear driven gear 302 engage with the first bonding apparatus 401, and drive the second output shaft 30 to rotate by the first bonding apparatus 401;
E, the second output shaft 30 drive the second main subtracting after driving gear 310 rotates to export.
When third gear:
The second bonding apparatus 402 engages with third gear driven gear 203, so that the second bonding apparatus 402 is by described third gear driven gear 203 driven rotary, its power transmission step is as follows:
A, engine-driving input shaft 10 rotate;
B, input shaft 10 drive two third speed drive gears 102 to rotate;
C, two third speed drive gears 102 drive third gear driven gear 203 to rotate;
D, third gear driven gear 203 engage with the second bonding apparatus 402, and drive the first output shaft 20 to rotate by the second bonding apparatus 402;
E, the first output shaft 20 drive the first main subtracting after driving gear 210 rotates to export.
When fourth gear:
The second bonding apparatus 402 engages with fourth gear driven gear 204, so that bonding apparatus 403 is by described fourth gear driven gear 204 driven rotary, its power transmission step is as follows:
A, engine-driving input shaft 10 rotate;
B, input shaft 10 drive four or five grades of driving gears 104 to rotate;
C, four or five grades of driving gears 104 drive fourth gear driven gear 204 to rotate;
D, fourth gear driven gear 204 engage with the second bonding apparatus 402, and drive the first output shaft 20 to rotate by the second bonding apparatus 402;
E, the first output shaft 20 drive the first main subtracting after driving gear 210 rotates to export.
In the time of five grades:
The 3rd bonding apparatus 403 engages with five grades of driven gears 305, so that the 3rd bonding apparatus 403 is by described five grades of driven gear 305 driven rotary, its power transmission step is as follows:
A, engine-driving input shaft 10 rotate;
B, input shaft 10 drive four or five grades of driving gears 104 to rotate;
C, four or five grades of driving gears 104 drive five grades of driven gears 305 to rotate;
D, five grades of driven gears 305 engage with the 3rd bonding apparatus 403, and drive the second output shaft 30 to rotate by the 3rd bonding apparatus 403;
E, the second output shaft 30 drive the second main subtracting after driving gear 310 rotates to export.
In the time of six grades:
The 3rd bonding apparatus 403 engages with six grades of driven gears 306, so that the 3rd bonding apparatus 403 is by described six grades of driven gear 306 driven rotary, its power transmission step is as follows:
A, engine-driving input shaft 10 rotate;
B, input shaft 10 drive six grades of driving gears 106 to rotate;
C, six grades of driving gears 106 drive six grades of driven gears 306 to rotate;
D, six grades of driven gears 306 engage with the 3rd bonding apparatus 403, and drive the second output shaft 30 to rotate by the 3rd bonding apparatus 403;
E, the second output shaft 30 drive the second main subtracting after driving gear 310 rotates to export.
It is worth mentioning that: in the layout preferred forms of manual transmission geared rotor system of the present invention, on described the first output shaft 20, reverse gear bonding apparatus 404 is also installed, described reverse gear bonding apparatus 404 is between third gear driven gear 203 and reverse gear 205, described reverse gear 205 empty sets are on the first output shaft 20, and the described first speed driven gear 301 of described reverse gear 205 engagement, and can be driven rotation by described first speed driven gear 301.The moment of torsion transmission of forward gears is to be delivered to corresponding driven gear by input shaft, and the first output shaft 20 is rotated in a first direction.And when reverse gear, reverse gear 205 coordinates reverse gear bonding apparatus 404 to drive the first output shaft 20 along rotating in the opposite direction with first party.
The power transmission step of reverse gear 205 is as follows:
When carrying out reverse gear, reverse gear bonding apparatus 404 engages with reverse gear 205, so that reverse gear bonding apparatus 404 is by described reverse gear 205 driven rotary, its power transmission step is as follows:
A, engine-driving input shaft 10 rotate;
B, input shaft 10 drive one grade of driving gear 101 to rotate;
C, one grade of driving gear 101 drive first speed driven gear 301 to rotate;
D, first speed driven gear 301 drive reverse gear 205 to rotate; Now the sense of rotation of reverse gear 205 is contrary with described first direction;
E, reverse gear 205 engage with reverse gear bonding apparatus 404, and drive the first output shaft 20 to rotate by reverse gear bonding apparatus 404;
F, the first output shaft 20 drive the first main driving gear 210 that subtracts to rotate, and because reverse gear 205 sense of rotation are contrary with first direction, thereby when reverse gear, the first output shaft 20 sense of rotation are contrary with first direction, realize falling back of vehicle.
In the present invention, by a duplicate gear, effectively reduced axial space, the relatively good coupling of number, meanwhile, bonding apparatus is arranged on the first output shaft 20 and the second output shaft 30 between two, layout structure balance and simple for structure, and axial distance is shorter.
It should be noted that simultaneously, in the present invention, bonding apparatus be arranged as optimum implementation, as long as bonding apparatus is installed but meet on the first output shaft 20 of each one of them side of driven gear or the second output shaft 30, on the first output shaft 20 and the second output shaft 30, be equipped with the bonding apparatus that coordinates each driven gear gear shift, can successfully realize gear shift function.
Above embodiment is only unrestricted in order to technological scheme of the present invention to be described, although the present invention is had been described in detail with reference to preferred embodiment, those of ordinary skill in the art is to be understood that, can modify or be equal to replacement technological scheme of the present invention, and not depart from the spirit and scope of technical solution of the present invention.
Claims (6)
1. the layout of a gear shafts of gearbox, comprise an input shaft, be parallel to described input shaft and be positioned at the first output shaft and second output shaft of described input shaft both sides, on described input shaft, be fixed with driving gear, on described output shaft, be set with driven gear, it is characterized in that: on described the first output shaft, be set with third gear driven gear, fourth gear driven gear and reverse gear, on described the second output shaft, be set with first speed driven gear, second gear driven gear, five grades of driven gears and six grades of driven gears, on described input shaft, be installed with one grade of driving gear, two third speed drive gears, four or five grades of driving gears and six grades of driving gears, described six grades of driving gears are arranged between described two third speed drive gears and described four or five grades of driving gears, described first speed driven gear and described one grade of driving gear engagement, described second gear driven gear and described third gear driven gear and described two third speed drive gear engagements, described fourth gear driven gear and described five grades of driven gears and described four or five grades of driving gears engagement, described six grades of driven gears and described six grades of driving gears engagement, described reverse gear and the engagement of described first speed driven gear, and can be driven rotation by described first speed driven gear, on described the first output shaft and on described the second output shaft, be also provided with described driven gear and match and merge for switching the bonding apparatus of gear.
2. the layout of gear shafts of gearbox according to claim 1, it is characterized in that: on described the first output shaft, be also provided with the one first main driving gear that subtracts, described reverse gear is arranged at the described first main subtracting between driving gear and described third gear driven gear.
3. the layout of gear shafts of gearbox according to claim 2, it is characterized in that: described bonding apparatus comprises reverse gear bonding apparatus, it is arranged on described the first output shaft, be arranged between described third gear driven gear and described reverse gear, during reverse gear, described reverse gear bonding apparatus engages with described reverse gear.
4. according to the layout of the gear shafts of gearbox described in any one in claims 1 to 3, it is characterized in that: described bonding apparatus also comprises the first bonding apparatus being arranged between described first speed driven gear and described second gear driven gear.
5. according to the layout of the gear shafts of gearbox described in any one in claims 1 to 3, it is characterized in that: described bonding apparatus also comprises the second bonding apparatus being arranged between described third gear driven gear and described fourth gear driven gear.
6. according to the layout of the gear shafts of gearbox described in any one in claims 1 to 3, it is characterized in that: described bonding apparatus also comprises the 3rd bonding apparatus being arranged between described five grades of driven gears and described six grades of driven gears.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010188708.6A CN102269240B (en) | 2010-06-01 | 2010-06-01 | Arrangement structure of gear shaft system of gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010188708.6A CN102269240B (en) | 2010-06-01 | 2010-06-01 | Arrangement structure of gear shaft system of gearbox |
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| Publication Number | Publication Date |
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| CN102269240A CN102269240A (en) | 2011-12-07 |
| CN102269240B true CN102269240B (en) | 2014-04-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201010188708.6A Active CN102269240B (en) | 2010-06-01 | 2010-06-01 | Arrangement structure of gear shaft system of gearbox |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2799978Y (en) * | 2005-06-02 | 2006-07-26 | 杭州依维柯汽车变速器有限公司 | Transmission with double output shafts |
| CN2828451Y (en) * | 2004-11-22 | 2006-10-18 | 南京汽车变速箱有限公司 | Vehicle speed transmission |
| CN101260918A (en) * | 2006-12-04 | 2008-09-10 | C.R.F.阿西安尼顾问公司 | Gearbox with six or more forward gears for single-clutch or twin-clutch motor-vehicle transmissions |
| KR20090009558A (en) * | 2007-07-20 | 2009-01-23 | 지엠대우오토앤테크놀로지주식회사 | Transmission swichable between forward 6 steps and 7 steps |
| EP2055988A1 (en) * | 2007-10-29 | 2009-05-06 | Peugeot Citroen Automobiles SA | Gearbox with double synchroniser comprising at least two secondary shafts and associated upward and downward shifting methods |
| CN201250882Y (en) * | 2008-06-03 | 2009-06-03 | 浙江吉利汽车研究院有限公司 | Six-speed all-synchronous mechanical transmission |
| CN201420838Y (en) * | 2009-04-16 | 2010-03-10 | 浙江吉利汽车研究院有限公司 | Manual dual-output shaft speed changer |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009030753A (en) * | 2007-07-30 | 2009-02-12 | Aisin Ai Co Ltd | Transmission with six pairs of forward travel shift gears |
-
2010
- 2010-06-01 CN CN201010188708.6A patent/CN102269240B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2828451Y (en) * | 2004-11-22 | 2006-10-18 | 南京汽车变速箱有限公司 | Vehicle speed transmission |
| CN2799978Y (en) * | 2005-06-02 | 2006-07-26 | 杭州依维柯汽车变速器有限公司 | Transmission with double output shafts |
| CN101260918A (en) * | 2006-12-04 | 2008-09-10 | C.R.F.阿西安尼顾问公司 | Gearbox with six or more forward gears for single-clutch or twin-clutch motor-vehicle transmissions |
| KR20090009558A (en) * | 2007-07-20 | 2009-01-23 | 지엠대우오토앤테크놀로지주식회사 | Transmission swichable between forward 6 steps and 7 steps |
| EP2055988A1 (en) * | 2007-10-29 | 2009-05-06 | Peugeot Citroen Automobiles SA | Gearbox with double synchroniser comprising at least two secondary shafts and associated upward and downward shifting methods |
| CN201250882Y (en) * | 2008-06-03 | 2009-06-03 | 浙江吉利汽车研究院有限公司 | Six-speed all-synchronous mechanical transmission |
| CN201420838Y (en) * | 2009-04-16 | 2010-03-10 | 浙江吉利汽车研究院有限公司 | Manual dual-output shaft speed changer |
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| CN102269240A (en) | 2011-12-07 |
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