CN203585231U - All-synchromesh twelve-gear transmission for heavy motor truck - Google Patents
All-synchromesh twelve-gear transmission for heavy motor truck Download PDFInfo
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- CN203585231U CN203585231U CN201320806393.6U CN201320806393U CN203585231U CN 203585231 U CN203585231 U CN 203585231U CN 201320806393 U CN201320806393 U CN 201320806393U CN 203585231 U CN203585231 U CN 203585231U
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- gear
- main shaft
- speed ratio
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- gears
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Abstract
The utility model provides an all-synchromesh twelve-gear transmission for a heavy motor truck. According to the scheme, the transmission comprises a main transmission body and an auxiliary transmission body, wherein the main transmission body is provided with two insertion gears, three forward gears and a reverse gear, the auxiliary transmission body is provided with a high gear and a lower gear, and the main transmission body and the auxiliary transmission body together form a 2*3*2 structure and form twelve forward gears and two reverse gears. The all-synchromesh twelve-gear transmission is reasonable in structural design and axle distance design, strong in bearing capacity and convenient to operate, reduces labor intensity, guarantees effective integration of driving comfort and running smoothness, and has good practicality, reliability and economy.
Description
Technical field
The utility model relates to a kind of speed changer, full synchronizer 12 shift transmissions for especially a kind of heavy motor truck.
Background technique
It is excellent that the speed changer of two intermediate shaft structures has compact structure, transmitting torque is large, the life-span is long etc., be widely used in medium and heavy truck, if but its structural design of the speed changer of two intermediate shaft structures or distance between shafts design are unreasonable, can produce the problem that transmitting torque is little, ratio coverage is narrow equally, and for heavy motor truck, need powerful driving force to complete the transportation of goods; Meanwhile, domestic heavy duty automobile gear box is of a great variety, but great majority are sliding sleeve gearshifts, impact sense strong in sliding sleeve shift process, to driver requested higher, and easily make driver fatigue; The existing deficiency of prior art that Here it is.
Summary of the invention
Technical problem to be solved in the utility model, be exactly for the existing deficiency of prior art, and providing the technological scheme of a kind of heavy-duty car with full synchronizer 12 shift transmissions, this scheme basic trnasmission and auxiliary transmission all to adopt the gearshift of lock ring type synchronizer, shift process is smooth-going; Basic trnasmission and auxiliary transmission form 2 * 3 * 2 structures jointly simultaneously, and speed changer structure is reasonable in design, and slewing range is large, and bearing capacity is strong, handiness.
This programme is achieved by the following technical measures: full synchronizer 12 shift transmissions for a kind of heavy-duty car, comprise basic trnasmission and auxiliary transmission, the feature of this programme is: what described basic trnasmission and auxiliary transmission all adopted is lock ring type synchronizer, described basic trnasmission has two to insert a minute gear, three forward gears and one are reversed gear, described auxiliary transmission has two gears of height, and common 2 * 3 * 2 structures that form of basic trnasmission and auxiliary transmission form 12 forward gears and two and reverse gear;
Described basic trnasmission comprises input mechanism and gear, two countershafts that described input mechanism comprises input shaft, driving gear I, driving gear II, is arranged on the input shaft synchronizer between driving gear I and driving gear II and driven by main shaft; Described gear comprises main shaft, idle pulley, be connected with main spindle multiple spline and the spindle synchronous device I that can horizontally slip along main shaft and spindle synchronous device II, with the gear counter shaft gear of countershaft spline joint and the gear mainshaft gear matching with spindle synchronous device;
Described auxiliary transmission comprises output shaft, sun gear, planet wheel and gear ring, and the main shaft of described basic trnasmission is connected with the sun gear of auxiliary transmission by spline; Described output shaft has output shaft synchronous device by spline joint, and the output terminal of output shaft is connected with output flange.
The feature of this programme also has, and described gear mainshaft gear comprises main shaft first gear, main shaft second gear and main shaft reverse gear.Described gear counter shaft gear comprises countershaft first gear, countershaft second gear, countershaft driver gear I, countershaft driver gear II and countershaft reverse gear, described countershaft first gear and countershaft second gear are meshed with described main shaft first gear and main shaft second gear respectively, described countershaft driver gear I and countershaft driver gear II are meshed with driving gear I and driving gear II respectively, described countershaft reverse gear is meshed with described main shaft reverse gear, and described countershaft reverse gear is also meshed with described idle pulley.Described spindle synchronous device I is arranged on the spindle nose near main shaft second gear, and spindle synchronous device II is arranged on the main shaft between main shaft first gear and main shaft reverse gear.One gear of described speed changer transmits speed ratio and is: 15.00, two gears transmit speed ratio: 11.67, three gears transmit speed ratio and are: 9.19, four gears transmit speed ratio and are: 7.14, five gears transmit speed ratio: 5.63, six gears transmit speed ratio: 4.38, seven gears transmit speed ratio and are: 3.43, eight gears transmit speed ratio and are: 2.67, nine gears transmit speed ratio: 2.1, ten gears transmit speed ratio: 1.63, ten one gears transmit speed ratio and are: 1.29, ten two gears transmit speed ratio and are: 1.
It is 17.76 that the high gear of described transmission reverse gear is transmitted speed ratio, and it is 11.84 that the low gear of described transmission reverse gear is transmitted speed ratio.Distance between described main shaft and two countershafts is 155cm.
The beneficial effects of the utility model are: in speed changer of the present utility model, described basic trnasmission has two to insert a minute gear, three forward gears and one are reversed gear, described auxiliary transmission has two gears of height, common 2 * 3 * 2 structures that form of basic trnasmission and auxiliary transmission, form 12 forward gears and two and reverse gear; Its structural design and distance between shafts are reasonable, bearing capacity is strong, handiness, input torque is 2100N/M, can meet the heavy vehicular engine between 380-440 horsepower, can mate pull-type, push type clutch, single pole, two lever operation form, mate novel electromagnetic sensor and the power take-off of various power, alleviated labor intensity, its life-span is long, fuel economy good, and using scope is wide.Adopt the full synchronizer gearshift of lock ring type, guaranteed effective combination of driving comfortability and run smoothness, effectively improved the quality of car load.As can be seen here, the utility model compared with prior art, has substantive distinguishing features and progress, and the beneficial effect of its enforcement is also apparent.
Accompanying drawing explanation
Fig. 1 is the structural representation of the utility model embodiment.
In figure, 1 is input shaft, 2 is main shaft, 3 is countershaft, 4 is output shaft, 5 is driving gear I, 6 is driving gear II, 7 is main shaft second gear, 8 is main shaft first gear, 9 is main shaft reverse gear, 10 is idle pulley, 11 is countershaft driver gear I, 12 is input shaft synchronizer, 13 is countershaft driver gear II, 14 is spindle synchronous device I, 15 is countershaft second gear, 16 is countershaft first gear, 17 is spindle synchronous device II, 18 is countershaft reverse gear, 19 is planet wheel, 20 is sun gear, 21 is output shaft synchronous device, 22 is Synchronizer Cone drum, 23 is gear ring, 24 is planetary mechanism, 25 is output flange.
Embodiment
For clearly demonstrating the technical characterstic of this programme, below by an embodiment, and in conjunction with its accompanying drawing, this programme is set forth.
By accompanying drawing, can find out, full synchronizer 12 shift transmissions for a kind of heavy motor truck of this programme, comprise basic trnasmission and auxiliary transmission, basic trnasmission is two intermediate shaft structures, auxiliary transmission designs for planetary mechanism, what described basic trnasmission and auxiliary transmission all adopted is lock ring type synchronizer, described basic trnasmission has two to insert a minute gear, three forward gears and one are reversed gear, described auxiliary transmission has two gears of height, common 2 * 3 * 2 structures that form of basic trnasmission and auxiliary transmission, form 12 forward gears and two and reverse gear.
Described basic trnasmission comprises input mechanism and gear, two countershafts 3 that described input mechanism comprises input shaft 1, driving gear I 5, driving gear II 6, is arranged on the input shaft synchronizer 12 between driving gear I 5 and driving gear II 6 and driven by main shaft 2; Described gear comprise main shaft 2, idle pulley 10, with main shaft 2 spline joints the spindle synchronous device I 14 that can horizontally slip along main shaft 2 and spindle synchronous device II 17, with the gear counter shaft gear of countershaft 3 spline joints and the gear mainshaft gear matching with main shaft 2 synchronizers; Described gear mainshaft gear comprises main shaft first gear 8, main shaft second gear 7 and main shaft reverse gear 9.Described gear counter shaft gear comprises countershaft first gear 16, countershaft second gear 15, countershaft driver gear I 11, countershaft driver gear II 13 and countershaft reverse gear 18, described countershaft first gear 16 and countershaft second gear 15 are meshed with described main shaft first gear 8 and main shaft second gear 7 respectively, described countershaft driver gear I 11 and countershaft driver gear II 13 are meshed with driving gear I 5 and driving gear II 6 respectively, described countershaft reverse gear 18 is meshed with described main shaft reverse gear 9, described countershaft reverse gear 18 is also meshed with described idle pulley 10.Described auxiliary transmission comprises output shaft 4, sun gear 20, planet wheel 19 and gear ring 23, and the main shaft 2 of described basic trnasmission is connected with the sun gear 20 of auxiliary transmission by spline; Described output shaft 4 has output shaft synchronous device by spline joint, and the output terminal of output shaft is connected with output flange 25.Described spindle synchronous device I 14 is arranged on main shaft 2 ends near main shaft second gear 7, and spindle synchronous device II 17 is arranged on the main shaft 2 between main shaft first gear 8 and main shaft reverse gear 9.Distance between described main shaft 2 and two countershafts 3 is 155cm.
The concrete transmission process of this programme is as follows: when auxiliary transmission is in low gear, insert minute gear in low gear, the transmission of power of motor is to input shaft 1, input shaft synchronizer 12 engages input shaft 1 with I 5, power passes to driving gear I 5 by input shaft 1, driving gear I 5 and 11 engagements of countershaft driver gear I, therefore countershaft driver gear I 11 drives and rotates, power passes to two countershafts 3 by driving gear I 5, on countershaft, rigid connecting is connected to countershaft driver gear I, countershaft driver gear II, countershaft second gear, countershaft first gear and countershaft reverse gear, on main shaft, empty set mainshaft gear.So when spindle synchronous device II 17 meshes with main shaft first gear 8, the countershaft first gear 16 of power on two countershafts 3 is pooled to the main shaft first gear 8 with its engagement, main shaft first gear 8 passes to the main shaft 2 with its spline joint through spindle synchronous device I 14, main shaft 2 is passed to the sun gear 20 with its spline joint by power, sun gear 20 is passed to power the planetary mechanism 24 meshing with it, planetary mechanism 24 is by transmission of power to output flange 25, and such gear (speed ratio 15.0) has transmitted.
When spindle synchronous device I 14 meshes with main shaft second gear 7, the second gear 15 of power on two countershafts is pooled to the main shaft second gear 7 with its engagement, main shaft second gear 7 passes to the main shaft 2 with its spline joint through spindle synchronous device I 14, main shaft 2 is passed to the sun gear 20 with its spline joint by power, sun gear 20 is passed to power the planetary mechanism 24 meshing with it, planetary mechanism 24 is by transmission of power to the output flange 25 with its spline joint, and such three gears (speed ratio 9.19) have transmitted.
When spindle synchronous device I 14 meshes with driving gear II 6, the countershaft driver gear II 13 of power on two countershafts is pooled to the driving gear II 6 with its engagement, driving gear II 6 passes to the main shaft 2 with its spline joint through spindle synchronous device I 14, main shaft 2 is passed to the sun gear 20 with its spline joint by power, sun gear 20 is passed to power the planetary mechanism 24 meshing with it, planetary mechanism 24 is by transmission of power to the output flange 25 with its spline joint, and such five gears (speed ratio 5.63) have transmitted.
When spindle synchronous device II 17 meshes with the mainshaft gear 9 that reverses gear, the reverse gear 18 of power on two countershafts is delivered to respectively on the idle pulley 10 being engaged with, then power is pooled to the main shaft reverse gear 9 meshing with them by two idle pulleys 10, the mainshaft gear 9 that reverses gear passes to the main shaft 2 with its spline joint through spindle synchronous device II 17, main shaft 2 is passed to the sun gear 20 with its spline joint by power, sun gear 20 is passed to power the planetary mechanism 24 meshing with it, planetary mechanism 24 is given the output flange 25 with its spline joint by transmission of power, 1(speed ratio 17.76 like this reverses gear) transmitted.
When auxiliary transmission is in low gear, insert minute gear in high gear, the transmission of power of motor is to input shaft 1, input shaft synchronizer 12 engages input shaft 1 with driving gear II 6, power passes to driving gear II 6 by input shaft 1, driving gear II 6 and 13 engagements of countershaft driver gear II, so the 13 driving rotations of countershaft driver gear II, power passes to two countershafts 3 by countershaft driver gear II 13.Each gear completes transmission according to said process, realizes the speed ratio of two gears (speed ratio 11.67), four gears (speed ratio 7.14), six gear (speed ratio 4.38) different gears.
Auxiliary transmission comprises gearshift synchronizer, sun gear, planet wheel and gear ring, and the main shaft of basic trnasmission is connected with the sun gear of auxiliary transmission by spline.There is high gear and low gear in planetary mechanism, when when in high gear position, each gear completes transmission according to said process, realizes seven gears (speed ratio 3.43), eight gears (speed ratio 2.67), nine gears (speed ratio 2.1), ten gears (speed ratio 1.63), 11 gears (speed ratio 1.29), 12 gear (speed ratio 1) and reverse gear 2(speed ratios 11.84) speed ratio of different gears.
Although above-mentioned, by reference to the accompanying drawings the embodiment of model utility is described; but the not restriction to the utility model protection domain; one of ordinary skill in the art should be understood that; on the basis of the technical solution of the utility model, those skilled in the art do not need to pay various modifications that creative work can make or distortion still in protection domain of the present utility model.
Claims (7)
1. full synchronizer 12 shift transmissions for heavy motor truck, comprise basic trnasmission and auxiliary transmission, it is characterized in that: what described basic trnasmission and auxiliary transmission all adopted is lock ring type synchronizer, described basic trnasmission has two to insert a minute gear, three forward gears and one are reversed gear, described auxiliary transmission has two gears of height, and common 2 * 3 * 2 structures that form of basic trnasmission and auxiliary transmission form 12 forward gears and two and reverse gear;
Described basic trnasmission comprises input mechanism and gear, two countershafts that described input mechanism comprises input shaft, driving gear I, driving gear II, is arranged on the input shaft synchronizer between driving gear I and driving gear II and driven by main shaft; Described gear comprises main shaft, idle pulley, be connected with main spindle multiple spline and the spindle synchronous device I that can horizontally slip along main shaft and spindle synchronous device II, with the gear counter shaft gear of countershaft spline joint and the gear mainshaft gear matching with spindle synchronous device;
Described auxiliary transmission comprises output shaft, sun gear, planet wheel and gear ring, and the main shaft of described basic trnasmission is connected with the sun gear of auxiliary transmission by spline; Described output shaft has output shaft synchronous device by spline joint, and the output terminal of output shaft is connected with output flange.
2. full synchronizer 12 shift transmissions for heavy motor truck according to claim 1, is characterized in that: described gear mainshaft gear comprises main shaft first gear, main shaft second gear and main shaft reverse gear.
3. full synchronizer 12 shift transmissions for heavy motor truck according to claim 1 and 2, it is characterized in that: described gear counter shaft gear comprises countershaft first gear, countershaft second gear, countershaft driver gear I, countershaft driver gear II and countershaft reverse gear, described countershaft first gear and countershaft second gear are meshed with described main shaft first gear and main shaft second gear respectively, described countershaft driver gear I and countershaft driver gear II are meshed with driving gear I and driving gear II respectively, described countershaft reverse gear is meshed with described main shaft reverse gear, described countershaft reverse gear is also meshed with described idle pulley.
4. full synchronizer 12 shift transmissions for heavy motor truck according to claim 1 and 2, it is characterized in that: described spindle synchronous device I is arranged on the spindle nose near main shaft second gear, and spindle synchronous device II is arranged on the main shaft between main shaft first gear and main shaft reverse gear.
5. full synchronizer 12 shift transmissions for heavy motor truck according to claim 1, it is characterized in that: a gear of described speed changer transmits speed ratio and is: 15.00, two gears transmit speed ratio: 11.67, three gears transmit speed ratio: 9.19, four gears transmit speed ratio: 7.14, five gears transmit speed ratio: 5.63, six gears transmit speed ratio: 4.38, seven gears transmit speed ratio: 3.43, eight gears transmit speed ratio: 2.67, nine gears transmit speed ratio and are: 2.1, ten gears transmit speed ratio and are: 1.63,11 gears transmit speed ratio: 1.29, ten two gears transmit speed ratio and are: 1.
6. full synchronizer 12 shift transmissions for heavy motor truck according to claim 1, is characterized in that: it is 17.76 that the high gear of described transmission reverse gear is transmitted speed ratio, and it is 11.84 that the low gear of described transmission reverse gear is transmitted speed ratio.
7. full synchronizer 12 shift transmissions for heavy motor truck according to claim 1, is characterized in that: the distance between described main shaft and two countershafts is 155cm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320806393.6U CN203585231U (en) | 2013-12-10 | 2013-12-10 | All-synchromesh twelve-gear transmission for heavy motor truck |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320806393.6U CN203585231U (en) | 2013-12-10 | 2013-12-10 | All-synchromesh twelve-gear transmission for heavy motor truck |
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| Publication Number | Publication Date |
|---|---|
| CN203585231U true CN203585231U (en) | 2014-05-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320806393.6U Expired - Fee Related CN203585231U (en) | 2013-12-10 | 2013-12-10 | All-synchromesh twelve-gear transmission for heavy motor truck |
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| Country | Link |
|---|---|
| CN (1) | CN203585231U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107264261A (en) * | 2017-05-22 | 2017-10-20 | 安徽纽恩卡自控科技有限公司 | One kind 11 keeps off mixed power automobile driving system |
| CN110177959A (en) * | 2016-12-22 | 2019-08-27 | 伊顿康明斯自动传输技术有限责任公司 | The high output speed changer of high efficiency |
-
2013
- 2013-12-10 CN CN201320806393.6U patent/CN203585231U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110177959A (en) * | 2016-12-22 | 2019-08-27 | 伊顿康明斯自动传输技术有限责任公司 | The high output speed changer of high efficiency |
| CN110177959B (en) * | 2016-12-22 | 2023-03-03 | 伊顿康明斯自动传输技术有限责任公司 | High-efficiency high-output speed variator |
| CN107264261A (en) * | 2017-05-22 | 2017-10-20 | 安徽纽恩卡自控科技有限公司 | One kind 11 keeps off mixed power automobile driving system |
| CN107264261B (en) * | 2017-05-22 | 2019-05-24 | 安徽纽恩卡自控科技有限公司 | One kind 11 keeps off mixed power automobile driving system |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140507 Termination date: 20191210 |