CN203686004U - Mechanical three-shaft type high-speed-ratio vehicle transmission - Google Patents
Mechanical three-shaft type high-speed-ratio vehicle transmission Download PDFInfo
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- CN203686004U CN203686004U CN201420055268.0U CN201420055268U CN203686004U CN 203686004 U CN203686004 U CN 203686004U CN 201420055268 U CN201420055268 U CN 201420055268U CN 203686004 U CN203686004 U CN 203686004U
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Abstract
The utility model discloses a mechanical three-shaft type high-speed-ratio vehicle transmission. The mechanical three-shaft type high-speed-ratio vehicle transmission comprises an input shaft, an output shaft, a middle shaft and transmission gears arranged on the shaft. As each transmission gear of the transmission is a point-line gear, the transmission can operate more stably, working noise of the transmission is lowered, and the service life of the transmission is prolonged; high gear ratio can be achieved as the point-line gears are large short-addendum gears; due to the limit design of the gear ratio of the transmission gears, the highest transmission ratio of a first gear of the transmission reaches more than 12, the transmission ratio of the first gear of the transmission is maximized, the transportation requirement for abrupt slope heavy loading of a vehicle is met, it is unnecessary to additionally arrange an auxiliary transmission in front of or behind the transmission, the manufacturing cost of the transmission of the overloaded vehicle is lowered, the failure rate of the transmission is decreased, reliability of the transmission is improved, a transmission structure of the transmission does not need to be changed, and gear shifting operation is more convenient and flexible.
Description
Technical field
The utility model relates to the variable speed drive of automobile, particularly relates to a kind of gearbox of heavy-load automobile.
Background technique
In prior art, mechanical three-shaft type automobile gearbox is made up of input shaft, output shaft, jack shaft and the gear that is arranged on axle, wherein, on input shaft, being provided with can be with its synchronous driving gear rotating, on jack shaft, being provided with can be with its synchronous jack shaft constant mesh gear rotating, jack shaft constant mesh gear engages with the driving gear on input shaft, forms primary speed-down transmission; On jack shaft and output shaft, correspondence is provided with the intermeshing shifting gear of many groups, shifting gear on jack shaft is contained on jack shaft and can synchronously rotates with jack shaft by key or interference fit, shifting gear on output shaft is sleeved on output shaft and can be freely rotated at output shaft by needle bearing, shifting gear on jack shaft and output shaft forms secondary transmission, be used for realizing speedup or deceleration, on output shaft, be also provided with the gearshift that arrives output shaft for the transmission of torque of carrying out gear switch and input shaft can be exported simultaneously.When work, handle gear level, the now selector fork of gearshift action, drive synchronizer sliding sleeve to engage with corresponding shifting gear, first the torque of now input shaft output is delivered to jack shaft by constant mesh gear, and then be delivered to gearshift by shifting gear, be finally delivered on output shaft by the synchronizer gear seat of gearshift again.But, owing to being subject to the size restrictions in structure and space, one grade of velocity ratio of current five grades, six grades and seven grades gearboxes is between 7-8, cannot meet the heavy haul transport requirement of automobile abrupt slope, need to before or after gearbox, increase auxiliary transmission and increase the maximum transmission ratio of gearbox, not only can change vehicle transmission structure but increase auxiliary transmission, increase manufacture cost, also can make Gearbox Fault increase, reliability reduces, and operates convenient, flexible not simultaneously.
Model utility content
For the deficiencies in the prior art, the purpose of this utility model is to solve need to increase the problems such as the caused manufacture cost of auxiliary transmission is high, reliability is low, fault increases, operation inconvenience because each stage gear ratio of gearbox is little, provide one do not need to increase auxiliary transmission and do not change vehicle transmission structure, there is reasonable in design, the relatively simple new automobile gearbox designs of structure; Meanwhile, the present invention will put line gear and apply wherein, to reduce the operating noise of gearbox, extend the working life of gearbox, in addition, can design large speed ratio gearbox, be conducive to improve the heavily loaded grade ability of automobile.
In order to solve the problems of the technologies described above, the utility model has adopted following technological scheme:
A kind of mechanical three-shaft type large speed ratio automobile gearbox, comprise gear box casing and be arranged on input shaft, output shaft, jack shaft and the reverse gear shaft in gear box casing, the central axis conllinear of described input shaft and output shaft, described output shaft, jack shaft and reverse gear shaft three are parallel to each other, and reverse gear shaft is between output shaft and jack shaft; On described input shaft, being provided with can be with its synchronous driving gear rotating, and on jack shaft, being provided with can be with its synchronous jack shaft constant mesh gear rotating, and the driving gear on described jack shaft constant mesh gear and input shaft is intermeshing;
On described jack shaft, being provided with can be with its synchronous at least third gear countershaft-gear rotating, on described output shaft, correspondence is provided with at least third gear output shaft gear engaging with described countershaft-gear successively, and described output shaft gear is arranged on output shaft by needle bearing; On described output shaft, be also provided with output shaft reverse gear, described output shaft reverse gear is arranged on output shaft by needle bearing; On described reverse gear shaft, be provided with reverse idler gear, described reverse idler gear is arranged on reverse gear shaft by needle bearing; Described countershaft-gear comprises one grade of gear of jack shaft, and one grade of gear of reverse idler gear and jack shaft and output shaft reverse gear engage; On described output shaft, correspondence is provided with several grades of gearshifts, gearshifts at different levels can engage with corresponding output shaft gear or output shaft reverse gear and by the transmission of torque of input shaft output to output shaft;
Described driving gear, jack shaft constant mesh gear, output shaft reverse gear, countershaft-gear at different levels and output shaft gear at different levels all adopt a line gear, the number of teeth of described driving gear is 19, the number of teeth of described jack shaft constant mesh gear is 48, the number of teeth of one grade of gear of described jack shaft is 9, described output shaft gear comprises the one grade of gear of output shaft engaging with one grade of gear of jack shaft, and the number of teeth of one grade of gear of described output shaft is 43 or 45.
As preferably, described countershaft-gear comprises counter 5th gear, jack shaft fourth gear, third-speed gear of intermediate shaft, secondary gear of intermediate shaft and one grade of gear of jack shaft, output shaft gear comprise five grades of gears of output shaft of and engagement corresponding with counter 5th gear, and the output shaft fourth gear that engage corresponding with jack shaft fourth gear, with the corresponding output shaft three-range transmission also engaging of third-speed gear of intermediate shaft, with the corresponding output shaft intermediate gear also engaging of secondary gear of intermediate shaft and one grade of gear of output shaft that should also engage with one grade of gear mesh of jack shaft, on described output shaft, be provided with can with driving gear or five grades of gear engagement of output shaft and by the transmission of torque of input shaft output five or six grades of gearshifts to output shaft, can engage with output shaft fourth gear or output shaft three-range transmission and the three fourth gear gearshifts to output shaft by the transmission of torque of input shaft output, can and the transmission of torque of input shaft output be arrived to the reverse gear gearshift of output shaft to a second gear gearshift of output shaft and the transmission of torque that can engage with output shaft reverse gear and input shaft is exported with output shaft intermediate gear or one grade of gear engagement of output shaft.
As preferably, the number of teeth of described output shaft intermediate gear is 43, the number of teeth of described secondary gear of intermediate shaft is 17, the number of teeth of described output shaft three-range transmission is 36, and the number of teeth of described third-speed gear of intermediate shaft is 23, and the number of teeth of described output shaft fourth gear is 32, the number of teeth of described jack shaft fourth gear is 33, the number of teeth of five grades of gears of described output shaft is 24, and the number of teeth of described counter 5th gear is 39, and the number of teeth of described output shaft reverse gear is 38 or 40.
As preferably, described gearshift comprises synchronizer gear seat, synchronizer sliding sleeve and selector fork, described synchronizer gear seat is contained on output shaft by inner spline housing, described synchronizer sliding sleeve is enclosed within on synchronizer gear seat, and synchronizer sliding sleeve is connected with the external splines of synchronizer gear seat by internal spline, described selector fork is connected with synchronizer sliding sleeve and can drives synchronizer sliding sleeve to move vertically.
The beneficial effects of the utility model are:
The utility model is applied to a line gear driving gears at different levels of automobile gearbox dexterously, dotted line gear transmission is that the Li Haixiang of Wuhan University of Technology teaches 20 years of researches achievements, due to its have manufacture simple, have separability, the feature such as intensity is high, the life-span is long and noise is low, therefore a line gear is applied to automobile gearbox just can play reduction noise, increase the service life, improve the effects such as bearing capacity, in addition, because a line gear is large negative addendum modification gear, therefore it can realize larger gear ratio, so just is more conducive to improve each stage gear ratio of automobile gearbox, meets the abrupt slope heavy haul transport requirement of automobile, simultaneously, the utility model is by having carried out limit design to the gear ratio of driving gear, one grade of maximum transmission ratio of gearbox is reached more than 12, realize the maximization of one grade of velocity ratio of gearbox, guarantee that the maximum transmission ratio obtaining with increase auxiliary transmission is close, so no longer need to before or after automobile gearbox, increase auxiliary transmission, reduce the manufacture cost of heavy-load automobile gearbox, reduce the rate of fault of automobile gearbox, improve the reliability of automobile gearbox, also do not need to change in addition the drive mechanism of automobile gearbox, make gear shift operation convenient, flexibly, reliably.
accompanying drawing explanation
Fig. 1 is the structure diagram of the utility model mechanical three-shaft type large speed ratio automobile gearbox.
Embodiment
Below in conjunction with accompanying drawing, the utility model is described in further detail.
Referring to Fig. 1, a kind of mechanical three-shaft type large speed ratio automobile gearbox, comprise gear box casing 1 and be arranged on input shaft 2, output shaft 3, jack shaft 4 and the reverse gear shaft 5 in gear box casing 1, wherein, between input shaft 2, output shaft 3 and jack shaft 4 and gear box casing 1, rolling bearing 10 is installed.
On input shaft 2, being provided with can be with its synchronous driving gear 21 rotating, and driving gear 21 is structure as a whole with input shaft 2, and certainly, driving gear 21 also can be enclosed within on input shaft 2 by the mode of interference fit or spline joint, jack shaft 4 is parallel with input shaft 2, on jack shaft 4, being provided with can be with its synchronous jack shaft constant mesh gear 41 rotating, counter 5th gear 42, jack shaft fourth gear 43, third-speed gear of intermediate shaft 44, one grade of gear 46 of secondary gear of intermediate shaft 45 and jack shaft, jack shaft constant mesh gear 41, counter 5th gear 42, jack shaft fourth gear 43, third-speed gear of intermediate shaft 44, one grade of gear 46 of secondary gear of intermediate shaft 45 and jack shaft is connected by singly-bound, the mode such as spline joint or interference fit is socketed on jack shaft 4, jack shaft constant mesh gear 41 is intermeshing with driving gear 21.
The central axis conllinear of output shaft 3 and input shaft 2, on output shaft 3, correspondence is provided with five grades of gears 31 of output shaft corresponding with counter 5th gear 42 and engagement successively, corresponding with jack shaft fourth gear 43 and engage output shaft fourth gear 32, corresponding with third-speed gear of intermediate shaft 44 and engage output shaft three-range transmission 33, corresponding with secondary gear of intermediate shaft 45 and engage output shaft intermediate gear 34 and one grade of gear 35 of output shaft corresponding with one grade of gear 46 of jack shaft and that engage, five grades of gears 31 of output shaft, output shaft fourth gear 32, output shaft three-range transmission 33, one grade of gear 35 of output shaft intermediate gear 34 and output shaft is arranged on output shaft 3 by needle bearing 6, output shaft 3, jack shaft 4 and reverse gear shaft 5 threes are parallel to each other, and reverse gear shaft 5, between output shaft 3 and jack shaft 4, and is provided with reverse idler gear 51 on reverse gear shaft 5, and reverse idler gear 51 is arranged on reverse gear shaft 5 by needle bearing 6, on output shaft 3, be also provided with output shaft reverse gear 36, output shaft reverse gear 36 is arranged on output shaft 3 by needle bearing 6, reverse idler gear 51, between one grade of gear 46 of jack shaft and output shaft reverse gear 36, and engages with one grade of gear 46 of jack shaft and output shaft reverse gear 36.
On output shaft 3, be provided with five or six grades of gearshifts, three fourth gear gearshifts, one second gear gearshift and reverse gear gearshift, the structure of four gearshifts is identical, include synchronizer gear seat 7, synchronizer sliding sleeve 8 and selector fork 9, synchronizer gear seat 7 by spline package on output shaft 3, synchronizer sliding sleeve 8 is enclosed within on synchronizer gear seat 7, and synchronizer sliding sleeve 8 is connected with the external splines of synchronizer gear seat 7 by internal spline, selector fork 9 is connected with synchronizer sliding sleeve 8 and can drives synchronizer sliding sleeve 8 to move vertically, when work, driver drives selector fork 9 to move by automobile shifting rod, selector fork 9 drives synchronizer sliding sleeve 8 to slide axially, synchronizer sliding sleeve 8 drives slide block (not marking in the figure) motion being arranged on synchronizer gear seat 7, the motion of slipper push lock ring makes the inner conical surface of lock ring engage with the male cone (strobilus masculinus) of driving gear 21 or output shaft gears at different levels, then the outer driving cog on lock ring engages with the interior driving cog of synchronizer sliding sleeve 8, the torque that now input shaft 2 is exported is successively by jack shaft constant mesh gear 41, jack shaft 4, countershaft-gear, output shaft gear, synchronizer sliding sleeve 8 and synchronizer gear seat 9 are delivered on output shaft 3.It is pointed out that the utility model adopts lock ring type synchronizer gearshift to belong to prior art, therefore no longer the structure to gearshift, know-why are elaborated in the utility model.
Five or six grades of gearshifts are between driving gear 21 or five grades of gears 31 of output shaft, when the synchronizer sliding sleeve 8 of five or six grades of gearshifts slides left while engaging with driving gear 21, the torque that input shaft 2 is exported is directly delivered on output shaft 3 with the form of 1:1, and now automobile gearbox is in six grades of states; When the synchronizer sliding sleeve 8 of five or six grades of gearshifts slides to the right while engaging with five grades of gears 31 of output shaft, first the torque that now input shaft 2 is exported is delivered on jack shaft 4 after jack shaft constant mesh gear 41 carries out primary speed-down, and then undertaken being delivered on output shaft 3 after two stage speed change by counter 5th gear 42 and five grades of gears of output shaft 31, now automobile gearbox is in five grades of states.
Three fourth gear gearshifts are between output shaft fourth gear 32 and output shaft three-range transmission 33, when the synchronizer sliding sleeve 8 of three fourth gear gearshifts slides left while engaging with output shaft fourth gear 32, first the torque that input shaft 2 is exported is delivered on jack shaft 4 after jack shaft constant mesh gear 41 carries out primary speed-down, and then undertaken being delivered on output shaft 3 after two stage speed change by jack shaft fourth gear 43 and output shaft fourth gear 32, now automobile gearbox is in fourth gear state; When the synchronizer sliding sleeve 8 of three fourth gear gearshifts slides to the right while engaging with output shaft three-range transmission 33, first the torque that input shaft 2 is exported is delivered on jack shaft 4 after jack shaft constant mesh gear 41 carries out primary speed-down, and then undertaken being delivered on output shaft 3 after two stage speed change by third-speed gear of intermediate shaft 44 and output shaft three-range transmission 33, now automobile gearbox is in third gear state.
Between one second gear gearshift output shaft intermediate gear 34 and one grade of gear 35 of output shaft, when the synchronizer sliding sleeve 8 of a second gear gearshift slides left while engaging with output shaft intermediate gear 34, first the torque that input shaft 2 is exported is delivered on jack shaft 4 after jack shaft constant mesh gear 41 carries out primary speed-down, and then undertaken being delivered on output shaft 3 after two stage speed change by secondary gear of intermediate shaft 45 and output shaft intermediate gear 34, now automobile gearbox is in second gear state; When the synchronizer sliding sleeve 8 of a second gear gearshift slides to the right while engaging with one grade of gear 35 of output shaft, first the torque that input shaft 2 is exported is delivered on jack shaft 4 after jack shaft constant mesh gear 41 carries out primary speed-down, and then undertaken being delivered on output shaft 3 after two stage speed change by one grade of gear 46 of jack shaft and one grade of gear of output shaft 35, now automobile gearbox is in one grade of state.
Reverse gear gearshift is adjacent with output shaft reverse gear 36, in the present embodiment, reverse gear gearshift is positioned at the right side of output shaft reverse gear 36, when the synchronizer sliding sleeve 8 of reverse gear gearshift slides left while engaging with output shaft reverse gear 36, first the torque that input shaft 2 is exported is delivered on jack shaft 4 after jack shaft constant mesh gear 41 carries out primary speed-down, and then undertaken being delivered on output shaft 3 after reverse speed change by one grade of gear 46 of jack shaft, reverse idler gear 51 and output shaft reverse gear 36, now automobile gearbox is in reverse gear state.
6T60DX and the 6T50DX automobile gearbox that our company develops on achievement in research basis below, existing by 6T53(CA142) contrast as follows with the velocity ratio of 6T60DX and 6T50DX automobile gearbox:
One, 6T53(CA142) automobile gearbox
| Gear | One grade | Second gear | Third gear | Fourth gear | Five grades | Six grades | Reverse gear | Normal engaging tooth |
| The input shaft gear number of teeth | ? | ? | ? | ? | ? | ? | ? | 22 |
| The output shaft gear number of |
43 | 47 | 38 | 32 | 26 | 1 | 40 | ? |
| The countershaft-gear number of teeth | 11 | 19 | 26 | 33 | 38 | 1 | 11 | 43 |
| Velocity ratio | 7.640 | 4.835 | 2.857 | 1.895 | 1.337 | 1 | 7.107 | 1.954545455 |
Two, band auxiliary transmission
| Gear | One grade | Second gear | Third gear | Fourth gear | Five grades | Six grades | Reverse gear | Normal engaging tooth |
| Odd-side speed ratio | 12.682 | 8.0261 | 4.743 | 3.146 | 2.219 | 1.66 | 11.736 | ? |
Three, 6T60DX large speed ratio automobile gearbox
| Gear | One grade | Second gear | Third gear | Fourth gear | Five grades | Six grades | Reverse gear | Normal engaging tooth |
| The input shaft gear number of teeth | ? | ? | ? | ? | ? | ? | ? | 19 |
| The output shaft gear number of |
43 | 43 | 36 | 32 | 24 | 1 | 38 | ? |
| The countershaft-gear number of |
9 | 17 | 23 | 33 | 39 | 1 | 9 | 48 |
| Velocity ratio | 12.070 | 6.390 | 3.692 | 2.450 | 1.555 | 1 | 10.667 | 2.526315789 |
Four, 6T50DX large speed ratio automobile gearbox
| Gear | One grade | Second gear | Third gear | Fourth gear | Five grades | Six grades | Reverse gear | Normal engaging tooth |
| The input shaft gear number of teeth | ? | ? | ? | ? | ? | ? | ? | 19 |
| The mainshaft gear number of |
45 | 43 | 36 | 32 | 24 | 1 | 40 | ? |
| The counter shaft gear number of |
9 | 17 | 23 | 33 | 39 | 1 | 9 | 48 |
| Velocity ratio | 12.632 | 6.390 | 3.692 | 2.450 | 1.555 | 1 | 11.228 | 2.526315789 |
Can draw by above-mentioned contrast form: after improving, 6T60DX gearbox or 6T50DX gearbox are than 6T53(CA142 before improving) each stage gear ratio of gearbox is large, especially one grade of maximum transmission ratio, 6T53(CA142 before improving) one grade of maximum transmission ratio of gearbox is 7.640, one grade of maximum transmission ratio that increase auxiliary transmission obtains is 12.682, and one grade of maximum transmission ratio of 6T60DX large speed ratio automobile gearbox after improving is 12.070, one grade of maximum transmission ratio of the 6T50DX large speed ratio automobile gearbox after improvement is 12.632, that is to say, large speed ratio automobile gearbox after improvement reaches more than 12 in next grade of maximum transmission ratio of situation that does not increase auxiliary transmission, the maximum transmission ratio obtaining with increase auxiliary transmission is close, meet the transportation demand of automobile abrupt slope heavy duty.
Finally it should be noted that, above embodiment is only in order to the technical solution of the utility model to be described but not restriction technologies scheme, although claimant has been described in detail the utility model with reference to preferred embodiment, those of ordinary skill in the art is to be understood that, those are modified to the technical solution of the utility model or are equal to replacement, and do not depart from aim and the scope of the technical program, all should be encompassed in the middle of claim scope of the present utility model.
Claims (4)
1. a mechanical three-shaft type large speed ratio automobile gearbox, comprise gear box casing (1) and be arranged on input shaft (2), output shaft (3), jack shaft (4) and the reverse gear shaft (5) in gear box casing (1), it is characterized in that, the central axis conllinear of described input shaft (2) and output shaft (3), described output shaft (3), jack shaft (4) and reverse gear shaft (5) three are parallel to each other, and reverse gear shaft (5) is positioned between output shaft (3) and jack shaft (4); On described input shaft (2), being provided with can be with its synchronous driving gear (21) rotating, on jack shaft (4), being provided with can be with its synchronous jack shaft constant mesh gear (41) rotating, and described jack shaft constant mesh gear (41) is intermeshing with the driving gear (21) on input shaft (2); On described jack shaft (4), being provided with can be with its synchronous at least third gear countershaft-gear rotating, on described output shaft (3), correspondence is provided with at least third gear output shaft gear engaging with described countershaft-gear successively, and described output shaft gear is arranged on output shaft by needle bearing; On described output shaft (3), be also provided with output shaft reverse gear (36), described output shaft reverse gear (36) is arranged on output shaft (3) by needle bearing; On described reverse gear shaft (5), be provided with reverse idler gear (51), described reverse idler gear (51) is arranged on reverse gear shaft (5) by needle bearing; Described countershaft-gear comprises one grade of gear of jack shaft (46), and reverse idler gear (51) engages with one grade of gear of jack shaft (46) and output shaft reverse gear (36); The upper correspondence of described output shaft (3) is provided with several grades of gearshifts, gearshifts at different levels can with corresponding output shaft gear or output shaft reverse gear (36) engages and by the transmission of torque of input shaft (2) output to output shaft (3); Described driving gear (21), jack shaft constant mesh gear (41), output shaft reverse gear (36), countershaft-gear at different levels and output shaft gear at different levels all adopt a line gear, the number of teeth of described driving gear (21) is 19, the number of teeth of described jack shaft constant mesh gear (41) is 48, the number of teeth of one grade of gear of described jack shaft (46) is 9, described output shaft gear comprises the one grade of gear of output shaft (35) engaging with one grade of gear of jack shaft (46), and the number of teeth of one grade of gear of described output shaft (35) is 43 or 45.
2. mechanical three-shaft type large speed ratio automobile gearbox according to claim 1, it is characterized in that, described countershaft-gear comprises counter 5th gear (42), jack shaft fourth gear (43), third-speed gear of intermediate shaft (44), secondary gear of intermediate shaft (45) and one grade of gear of jack shaft (46); Output shaft gear comprise five grades of gears of output shaft (31) of and engagement corresponding with counter 5th gear (42), and the output shaft fourth gear (32) that engage corresponding with jack shaft fourth gear (43), with the corresponding output shaft three-range transmission (33) also engaging of third-speed gear of intermediate shaft (44), with the corresponding output shaft intermediate gear (34) also engaging of secondary gear of intermediate shaft (45) and with the corresponding one grade of gear of output shaft (35) also engaging of one grade of gear of jack shaft (46); On described output shaft (3), being provided with the transmission of torque that can engage with driving gear (21) or five grades of gears of output shaft (31) and input shaft (2) is exported arrives a second gear gearshift of output shaft (3) and can engage with output shaft reverse gear (36) and the transmission of torque of input shaft (2) output is arrived the reverse gear gearshift of output shaft (3) to three fourth gear gearshifts of output shaft (3), the transmission of torque that can engage with output shaft intermediate gear (34) or one grade of gear of output shaft (35) and input shaft (2) is exported to five or six grades of gearshifts of output shaft (3), the transmission of torque that can engage with output shaft fourth gear (32) or output shaft three-range transmission (33) and input shaft (2) is exported.
3. mechanical three-shaft type large speed ratio automobile gearbox according to claim 2, it is characterized in that, the number of teeth of described output shaft intermediate gear (34) is 43, the number of teeth of described secondary gear of intermediate shaft (45) is 17, the number of teeth of described output shaft three-range transmission (33) is 36, the number of teeth of described third-speed gear of intermediate shaft (44) is 23, the number of teeth of described output shaft fourth gear (32) is 32, the number of teeth of described jack shaft fourth gear (43) is 33, the number of teeth of five grades of gears of described output shaft (31) is 24, the number of teeth of described counter 5th gear (42) is 39, the number of teeth of described output shaft reverse gear (36) is 38 or 40.
4. mechanical three-shaft type large speed ratio automobile gearbox according to claim 1, it is characterized in that, described gearshift comprises synchronizer gear seat (7), synchronizer sliding sleeve (8) and selector fork (9), described synchronizer gear seat (7) is contained on output shaft (3) by inner spline housing, described synchronizer sliding sleeve (8) is enclosed within on synchronizer gear seat (7), and synchronizer sliding sleeve (8) is connected with the external splines of synchronizer gear seat (7) by internal spline, described selector fork (9) is connected with synchronizer sliding sleeve (8) and can drives synchronizer sliding sleeve (8) to move vertically.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420055268.0U CN203686004U (en) | 2014-01-28 | 2014-01-28 | Mechanical three-shaft type high-speed-ratio vehicle transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420055268.0U CN203686004U (en) | 2014-01-28 | 2014-01-28 | Mechanical three-shaft type high-speed-ratio vehicle transmission |
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| CN203686004U true CN203686004U (en) | 2014-07-02 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103758947A (en) * | 2014-01-28 | 2014-04-30 | 綦江大力神齿轮有限公司 | Mechanical three-shaft type high-speed-ratio automobile gearbox |
| CN105221682A (en) * | 2015-10-29 | 2016-01-06 | 綦江大力神齿轮有限公司 | Automotive transmission |
-
2014
- 2014-01-28 CN CN201420055268.0U patent/CN203686004U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103758947A (en) * | 2014-01-28 | 2014-04-30 | 綦江大力神齿轮有限公司 | Mechanical three-shaft type high-speed-ratio automobile gearbox |
| CN105221682A (en) * | 2015-10-29 | 2016-01-06 | 綦江大力神齿轮有限公司 | Automotive transmission |
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Effective date of registration: 20150603 Address after: 400000 Chongqing village, Sanjiang Road, Qijiang District, Qijiang city (seven industrial parks) Patentee after: Qijiang Chongqing source electromechanical Co., Ltd. Address before: Chongqing city Qijiang County Gunan town 401420 sunshine court No. 1-6-8 Patentee before: Tan Fuchun Patentee before: Wang Wei |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140702 Termination date: 20160128 |
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| CF01 | Termination of patent right due to non-payment of annual fee |