CN203796871U - Planetary gearbox for vehicles - Google Patents
Planetary gearbox for vehicles Download PDFInfo
- Publication number
- CN203796871U CN203796871U CN201420108016.XU CN201420108016U CN203796871U CN 203796871 U CN203796871 U CN 203796871U CN 201420108016 U CN201420108016 U CN 201420108016U CN 203796871 U CN203796871 U CN 203796871U
- Authority
- CN
- China
- Prior art keywords
- gear
- planet carrier
- epicyclic transmission
- planetary
- transmission mechanism
- Prior art date
- 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.)
- Expired - Fee Related
Links
Landscapes
- Structure Of Transmissions (AREA)
Abstract
The utility model relates to a planetary gearbox for vehicles. The planetary gearbox for the vehicles comprises a planetary speed change mechanism and a reversing speed increase mechanism which are arranged in a box body. The planetary speed change mechanism comprises a plurality of planetary transmission mechanisms, sun gears of the planetary transmission mechanisms are arranged on a shared input shaft in a matched mode, and planetary gears of the planetary transmission mechanisms are matched with a planetary gear shaft on a shared planetary carrier through bearings. One end of the shared input shaft is matched with one end plate of the shared planetary carrier and stretches out of the box body to be connected with an engine in a matched mode, the other end of the shared input shaft is matched with one side of the other end plate of the shared planetary carrier, and the other side of the other end plate of the shared planetary carrier is provided with a shared planetary carrier output shaft coaxial with the shared input shaft. The planetary speed change mechanism is matched with the reversing speed increase mechanism. Inner gear rings of the planetary transmission mechanisms are matched with steel belt braking components respectively. The planetary gearbox for the vehicles is rapid and smooth in gear shifting and speed change, quite easy to operate; an output shaft is good in stress state and high in reliability, and the bearing capacity is improved.
Description
Technical field
The utility model relates to automobile component, is specifically related to a kind of automobile-used planetary transmission.
Background technique
Now is at the most Mining speed-changing gear box of gearbox of sedan car.This is that rigidity is large because gear transmission is simple and reliable.Cost performance is high.Especially the gearbox of double clutch DSG is the most advanced. and comfortable, leader world new trend. BMW, Magotan, Australia's enlightening is all with double clutch DSG gearbox.Germany volkswagen six speed transmission (see figure 7)s for example, its principle is as follows: in the time will being changed to second gear by one grade, now single grade of clutch is connected, transferring power.Electronic control mechanism carries out the work of preliminary election second gear, and its synchronizer engage a gear closes.The now unpowered transmission of second gear, but can only on double clutch Control Shaft, hang shelves simultaneously.Then open single grade of clutch, thereby cut off power, then the folk art term clutch that closes connects power ， The and need pass through brief stay, could become second gear transferring power from one grade, realize steady seamless link.On the axle that now electronic control mechanism can only control at folk art term clutch, select any even numbers shelves of a Ge, because this axle is unpowered, can preliminary election collocation.But when becoming other odd number shelves of third gear Ge from one grade, must be through first changing even numbers shelves into, then open odd number shelves clutch, preliminary election odd number shelves (this is because gear shift must be carried out on unpowered axle), open folk art term clutch, the single grade of clutch that closes, could successful gear shift again.Want altogether single grade of twice of folding and folk art term clutch, preliminary election engage a gear twice, twice synchronizer of folding.Although these actions are completed by electronic control mechanism, one of working procedure can not be lacked.But usually need the to skip a grade situation of engage a gear that Now is real, as upward slope, Ge pursues and attacks suddenly.Engage a gear is frequent, and synchronizer and clutch folding are too many, is just easily out of order.Besides the major axis of the axle sleeve axle that single double clutch is controlled will be subject to the effect of radial force and the tangential force of gear when gear transmission power, produces larger moment of flexure and moment of torsion and form composite force and easily make shaft distortion, the time has been grown and has affected gear and mesh, and is easily out of order.In order to address the above problem better, further add again bearing capacity and the reliability of Strong gearbox simultaneously, so planetary transmission arises at the historic moment.As disclosed in CN101936368A " planetary transmission ", fixed size gear ring on the inwall of casing, greatly, little gear ring can only forward slide, size gear ring is linked together by speed governing pull bar, speed governing pull bar passes case lid, input shaft is installed in one end at casing, the big or small sun gear of coaxial installation on input shaft, the other end at casing is installed output shaft, on output shaft in casing, connect planet carrier, at least three pairs of large small planetary gears of coaxial installation on planet carrier, mafor planet gear engagement Sunny gear and little gear ring, small planetary gear engagement large sun gear and bull gear.This planetary transmission obtains speed change by two groups of epicyclic trains, but can not meet the requirement of automobile variable speed.
Summary of the invention
The purpose of this utility model is to provide a kind of automobile-used planetary transmission, and its shifted quick and stable operates very simply, and the force-bearing situation of output shaft is good, and reliability is high, and carrying improves.
A kind of automobile-used planetary transmission described in the utility model, comprise the planet speed change mechanism and the commutation raising speed mechanism that are located in casing, it is characterized in that: described planet speed change mechanism comprises a plurality of epicyclic transmission mechanisms, the sun gear of each epicyclic transmission mechanism is all engaged in and shares on input shaft;
The planetary pinion of each epicyclic transmission mechanism coordinates (being that empty set coordinates) by bearing respectively with the planet pin in common planet carrier; One end of described shared input shaft coordinates with an end plate of common planet carrier and stretches out casing and motor is connected, the other end of described shared input shaft coordinates with a side of another end plate of common planet carrier, the opposite side of another end plate of described common planet carrier is provided with the common planet carrier output shaft coaxial with described shared input shaft, the end of described common planet carrier output shaft is connected through dividing plate and the common planet carrier output gear in casing, and this common planet carrier output gear coordinates with described commutation raising speed mechanism;
The ring gear of each epicyclic transmission mechanism all coordinates with the inwall of casing by non-standard ball bearing, and the cylindrical of each ring gear is equipped with V-ring groove, and each V-ring groove coordinates with steel band brake member respectively.
Further, described planet speed change mechanism comprises five epicyclic transmission mechanisms, the 5th sun gear of the 3rd sun gear of the first sun gear of one grade of epicyclic transmission mechanism, the secondary sun wheel of second gear epicyclic transmission mechanism, third gear epicyclic transmission mechanism, the 4th sun gear of fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms successively by spline fitted on described shared input shaft;
Three fifth line star gears of three the first planetary pinions of one grade of epicyclic transmission mechanism, three the second planetary pinions of second gear epicyclic transmission mechanism, three third planet gears of third gear epicyclic transmission mechanism, three fourth planet gears of fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms coordinate (being that empty set coordinates) by bearing respectively with the planet pin on described combined planetary frame;
The 5th ring gear of the 3rd ring gear of the first ring gear of one grade of epicyclic transmission mechanism, the second ring gear of second gear epicyclic transmission mechanism, third gear epicyclic transmission mechanism, the 4th ring gear of fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms all coordinates with the inwall of casing by the non-standard ball bearing of two covers;
The cylindrical of described the first ring gear, the second ring gear, the 3rd ring gear, the 4th ring gear and the 5th ring gear is equipped with V-ring groove, and each V-ring groove coordinates with a steel band brake member respectively.
Further, described commutation raising speed mechanism comprises and is connected on casing and jack shaft and the output shaft parallel with described shared input shaft; One end of described jack shaft has an intermediate speed pinion, the other end to have a gear broad in the middle by spline fitted by spline fitted; One end of described output shaft has a reverse gear, middle part to have a commutation synchronizer, the other end to have a forward gear by bearing fit by spline fitted by bearing fit;
Described intermediate speed pinion and the engagement of described common planet carrier output gear, described gear broad in the middle and the engagement of described forward gear, described reverse gear and the engagement of described common planet carrier output gear, described commutation synchronizer engages with the end face of forward gear, or engages with the end face of reverse gear.
Further, described steel band brake member is the opening annulus that three sections of sections are the trapezoidal hinged formation of circular arc steel band, the middle part of first paragraph circular arc steel band exterior arc surface is provided with projection, and this projection and cabinet wall are hinged, and second segment circular arc steel band is identical with the 3rd section of Circular Steel band structure; One end of one end of second segment circular arc steel band and described first paragraph circular arc steel band is hinged, and the other end of second segment circular arc steel band is provided with projection; The other end of one end of the 3rd section of circular arc steel band and described first paragraph circular arc steel band is hinged, and the other end of the 3rd section of circular arc steel band is also provided with projection; The projection of the second segment circular arc steel band the other end is corresponding with the projection of the 3rd section of circular arc steel band the other end, and two projections coordinate connection with gear shift control member.
Described steel band brake member is by three sections of sections that trapezoidal circular arc steel band is hinged to be formed, form the annulus brake member of opening, at opening during in relaxed state, ring gear with its corresponding matching is not played to braking action, this ring gear only slides along cabinet wall, with common planet carrier, do not rotate, do not transmit torque; At opening, when tightening up state,, to enclosing braking action with the internal tooth of its corresponding matching, this ring gear does not rotate, and common planet carrier is rotated and transmitted torque.
Further, described common planet carrier is connected to form by input end planet carrier and output terminal planet carrier, and described input end planet carrier and output terminal planet carrier connect and compose by two end plates, three planet pins and three planet carrier connecting rods; Described one grade of epicyclic transmission mechanism and second gear epicyclic transmission mechanism are located on input end planet carrier, and described third gear epicyclic transmission mechanism, fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms are located on output terminal planet carrier.
Further, at described input end planet carrier, near the end plate cylindrical of one grade of epicyclic transmission mechanism, be provided with common planet carrier breaker slot, this common planet carrier breaker slot coordinates with brake member, can control common planet carrier and rotate.
Described a kind of automobile-used planetary transmission, described in it, the first planetary pinion and the second planetary pinion are duplicate gear.
Compared to the prior art the utility model has the following advantages: when shifted, only need unclamp the ring gear that oneself checks, go again to check after the ring gear of preparing shifted that grade, just by upper one grade, become next shelves, without the clutch of folding complexity and fragile synchronizer and Yu Xuan Change shelves, so, shifted very simple.Due to output shaft bearing radial force not, only bear tangential force, there is no moment of flexure, so the reliability of output shaft is high, thereby improved bearing capacity.
Accompanying drawing explanation
Fig. 1 is structural representation of the present utility model;
Fig. 2 is the A-A sectional view of Fig. 1;
Fig. 3 is the B-B sectional view of Fig. 1;
Fig. 4 is the structural representation of steel band brake member;
Fig. 5 is the A-A sectional view of Fig. 4:
Fig. 6 is the plan view of Fig. 4;
Fig. 7 is the structural representation of germany volkswagen six speed transmissions.
In figure: 1-casing, 2-input end planet carrier, 3-planet pin, 4-output terminal planet carrier, 5-planet carrier connecting rod; 6-common planet carrier output shaft, 61-common planet carrier output gear; 7-jack shaft, 71-intermediate speed pinion, 72-gear broad in the middle; 8-output shaft, 81-reverse gear, the 82-synchronizer that commutates, 83-forward gear; 9-steel band brake member, 90-first paragraph circular arc steel band, 91-projection, 92-second segment circular arc steel band, 93-second segment circular arc steel band; 10-shares input shaft; 11-the first sun gear, 12-the first planetary pinion, 13-the first ring gear, 15-common planet carrier breaker slot; The non-standard ball bearing of 20-, 21-secondary sun wheel, 22-the second planetary pinion, 23-the second ring gear, 24-the second V-ring groove; 31-the 3rd sun gear, 32-third planet gear, 33-the 3rd ring gear, 34-the 3rd V-ring groove; 41-the 4th sun gear, 42-fourth planet gear, 43-the 4th ring gear, 44-the 4th V-ring groove; 51-the 5th sun gear, 52-fifth line star gear, 53-the 5th ring gear, 54-the 5th V-ring groove.
Embodiment
Below in conjunction with accompanying drawing, the utility model will be further described.
Referring to Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5 and Fig. 6, described a kind of automobile-used planetary transmission, comprise the planet speed change mechanism and the commutation raising speed mechanism that are located in casing 1, described in it, planet speed change mechanism comprises a plurality of epicyclic transmission mechanisms, and the sun gear of each epicyclic transmission mechanism is all engaged in and shares on input shaft 10;
The planetary pinion of each epicyclic transmission mechanism coordinates (being that empty set coordinates) by bearing respectively with the planet pin in common planet carrier; One end of described shared input shaft 10 coordinates with an end plate of common planet carrier and stretches out casing 1 and is connected with motor, the other end of described shared input shaft 10 coordinates with a side of another end plate of common planet carrier, the opposite side of another end plate of described common planet carrier is provided with the common planet carrier output shaft 6 coaxial with described shared input shaft 10, the end of described common planet carrier output shaft is connected through dividing plate and the common planet carrier output gear 61 in casing 1, and this common planet carrier output gear coordinates with described commutation raising speed mechanism;
The ring gear of each epicyclic transmission mechanism all coordinates with the inwall of casing 1 by non-standard ball bearing 20, and the cylindrical of each ring gear is equipped with V-ring groove, and each V-ring groove coordinates with steel band brake member 9 respectively.
Further, described planet speed change mechanism comprises five epicyclic transmission mechanisms, the first sun gear 11 of one grade of epicyclic transmission mechanism, the secondary sun wheel 21 of second gear epicyclic transmission mechanism, the 3rd sun gear 31 of third gear epicyclic transmission mechanism, the 5th sun gear 51 of the 4th sun gear 41 of fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms successively by spline fitted on described shared input shaft 10;
Three the first planetary pinions 12 of one grade of epicyclic transmission mechanism, three the second planetary pinions 22 of second gear epicyclic transmission mechanism, three third planet gears 32 of third gear epicyclic transmission mechanism, three fifth line star gears 52 of three fourth planet gears 42 of fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms coordinate (being that empty set coordinates) by bearing respectively with the planet pin 3 on described combined planetary frame;
The first ring gear 13 of one grade of epicyclic transmission mechanism, the second ring gear 23 of second gear epicyclic transmission mechanism, the 3rd ring gear 33 of third gear epicyclic transmission mechanism, the 5th ring gear 53 of the 4th ring gear 43 of fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms all coordinate with the inwall of casing 1 by the non-standard ball bearing 20 of two covers;
The cylindrical of described the first ring gear 13, the second ring gear 23, the 3rd ring gear 33, the 4th ring gear 43 and the 5th ring gear 53 is equipped with V-ring groove, and each V-ring groove coordinates with a steel band brake member 9 respectively.
Further, described commutation raising speed mechanism comprises and is connected on casing 1 and jack shaft 7 and the output shaft 8 parallel with described shared input shaft 10; One end of described jack shaft 7 has an intermediate speed pinion 71, the other end to have a gear 71 broad in the middle by spline fitted by spline fitted; One end of described output shaft 8 has a reverse gear 81, middle part to have a commutation synchronizer 82, the other end to have a forward gear 83 by bearing fit by spline fitted by bearing fit;
Described intermediate speed pinion 71 and described common planet carrier output gear 61 engagements, described gear broad in the middle 71 and described forward gear 83 engagements, described reverse gear 81 and described common planet carrier output gear 61 engagements, when described commutation synchronizer 82 engages with the end face of forward gear 83, export forward torque, vehicle is moved ahead; When described commutation synchronizer 82 engages with the end face of reverse gear 81, export reverse torque, make vehicle rollback.
Further, described steel band brake member 9 is the opening annulus that three sections of sections are the trapezoidal hinged formation of circular arc steel band, the middle part of first paragraph circular arc steel band 90 exterior arc surfaces is provided with projection 91, and this projection and casing 1 inwall are hinged, and second segment circular arc steel band 92 is identical with the 3rd section of circular arc steel band 93 structures; One end of one end of second segment circular arc steel band 92 and described first paragraph circular arc steel band 90 is hinged, and the other end of second segment circular arc steel band 92 is provided with projection; The other end of one end of the 3rd section of circular arc steel band 93 and described first paragraph circular arc steel band 90 is hinged, and the other end of the 3rd section of circular arc steel band 93 is also provided with projection; The projection of second segment circular arc steel band 92 the other ends is corresponding with the projection of the 3rd section of circular arc steel band 93 the other ends, and two projections and gear shift control member are connected.
Further, described common planet carrier is connected to form by input end planet carrier 2 and output terminal planet carrier 4, and described input end planet carrier 2 and output terminal planet carrier 4 connect and compose by two end plates, three planet pins 3 and three planet carrier connecting rods 5; Described one grade of epicyclic transmission mechanism and second gear epicyclic transmission mechanism are located on input end planet carrier 2, and described third gear epicyclic transmission mechanism, fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms are located on output terminal planet carrier 4.
Further, at described input end planet carrier 2, near the end plate cylindrical of one grade of epicyclic transmission mechanism, be provided with common planet carrier breaker slot 15, this common planet carrier breaker slot coordinates with brake member, can control common planet carrier and rotate.
Described the first planetary pinion 12 and the second planetary pinion 22 are duplicate gear.
Described gear shift control member is conventional electromagnetic structure or mechanical structure.
The utility model is fixed in the above the sun gear of each grade of epicyclic transmission mechanism with an input shaft, and is arranged in order; Each grade of epicyclic transmission mechanism be corresponding a ring gear independently separately all, and each ring gear is engaged on casing by the nonstandard ball bearing of two covers, and non-mark Roll pearl bearing is fixed on casing by two Ge semi-rings, and casing is semi-synthetic by two.On each ring gear, be respectively equipped with a V-shaped groove, as brake groove.Steel band brake member is the trapezoidal opening annulus of section.When steel band brake member openings get smaller girth shortens, can check ring gear and not rotate.When steel band brake member opening becomes large girth lengthening, ring gear can freely rotate, when ring gear is not checked, share output shaft and drive sun gear, make planetary pinion rotation, ring gear is transmitted idle running, become a Ge differential attachment, common planet carrier is not rotated.Common planet carrier turns with vehicle condition, and car is quiet not to be turned, and car is moving to be turned.When ring gear is checked, can not rotate.At shared output shaft, drive sun gear to rotate, when ring gear is checked, when making planetary pinion rotation, revolution, becomes an epicyclic transmission mechanism.When planetary pinion revolves round the sun, just drive common planet carrier to rotate, the gear that drives commutation to rise mechanism when common planet carrier is rotated rotates.Thereby give speed of output shaft.During speed change, be exactly to unclamp the ring gear that oneself checks, then go to check after the ring gear of preparing that grade of speed change, just by upper one grade, become next shelves, very simple, without the clutch of folding complexity and fragile synchronizer, and Yu Xuan Change shelves.It should be noted that and at any time can only check a ring gear, this speed change work can be manual, also can be electronic. and check ring gear, other planetary pinion will dally along with common planet carrier.The sense of rotation that sun gear shares combination planet carrier is consistent with power engine sense of rotation, thereby has increased the rotary inertia of power engine flywheel, does not waste power.Share sun gear on output shaft simultaneously and several planetary pinion mesh, they are with axle Central Symmetry, the mutual balance of the radial force of transmission.Shared output shaft is not subject to radial force, there is no moment of flexure, only has tangential force, bears moment of torsion, and the Gong Zuo Qing Condition that shares output shaft is far better.Ordinary gear transmission, gear is one-sided stressed, and Hang star Chi Lun Chuan Dong The has N planetary pinion, and it is stressed that sun gear and inner ring just have N Ge flank so, so its carrying improves greatly.
Claims (6)
1. an automobile-used planetary transmission, comprises the planet speed change mechanism and the commutation raising speed mechanism that are located in casing (1), it is characterized in that:
Described planet speed change mechanism comprises a plurality of epicyclic transmission mechanisms, and the sun gear of each epicyclic transmission mechanism is all engaged on shared input shaft (10);
The planetary pinion of each epicyclic transmission mechanism coordinates with the planet pin in common planet carrier by bearing respectively, one end of described shared input shaft (10) coordinates with an end plate of common planet carrier and stretches out casing (1) and motor and is connected, the other end of described shared input shaft (10) coordinates with a side of another end plate of common planet carrier, the opposite side of another end plate of described common planet carrier is provided with the common planet carrier output shaft (6) coaxial with described shared input shaft (10), the end of described common planet carrier output shaft is connected through dividing plate and the common planet carrier output gear (61) in casing (1), this common planet carrier output gear coordinates with described commutation raising speed mechanism,
The ring gear of each epicyclic transmission mechanism all coordinates with the inwall of casing (1) by non-standard ball bearing (20), and the cylindrical of each ring gear is equipped with V-ring groove, and each V-ring groove coordinates with steel band brake member (9) respectively.
2. a kind of automobile-used planetary transmission according to claim 1, it is characterized in that: described planet speed change mechanism comprises five epicyclic transmission mechanisms, the 5th sun gear (51) of the 3rd sun gear (31) of first sun gear (11) of one grade of epicyclic transmission mechanism, the secondary sun wheel (21) of second gear epicyclic transmission mechanism, third gear epicyclic transmission mechanism, the 4th sun gear (41) of fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms successively by spline fitted on described shared input shaft (10);
Three first planetary pinions (12) of one grade of epicyclic transmission mechanism, three second planetary pinions (22) of second gear epicyclic transmission mechanism, three third planet gears (32) of third gear epicyclic transmission mechanism, three fifth line star gears (52) of three fourth planet gears (42) of fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms coordinate with the planet pin (3) in described common planet carrier by bearing respectively;
The 5th ring gear (53) of the 3rd ring gear (33) of first ring gear (13) of one grade of epicyclic transmission mechanism, second ring gear (23) of second gear epicyclic transmission mechanism, third gear epicyclic transmission mechanism, the 4th ring gear (43) of fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms all coordinates with the inwall of casing (1) by the two non-standard ball bearings of cover (20);
The cylindrical of described the first ring gear (13), the second ring gear (23), the 3rd ring gear (33), the 4th ring gear (43) and the 5th ring gear (53) is equipped with V-ring groove, and each V-ring groove coordinates with a steel band brake member (9) respectively.
3. a kind of automobile-used planetary transmission according to claim 1 and 2, is characterized in that: described commutation raising speed mechanism comprises be connected and with described shared input shaft (10) parallel jack shaft (7) and output shaft (8) upper at casing (1); One end of described jack shaft (7) has an intermediate speed pinion (71), the other end to have a gear broad in the middle (71) by spline fitted by spline fitted; One end of described output shaft (8) has a reverse gear (81), middle part to have a commutation synchronizer (82), the other end to have a forward gear (83) by bearing fit by spline fitted by bearing fit;
Described intermediate speed pinion (71) and described common planet carrier output gear (61) engagement, described gear broad in the middle (71) and described forward gear (83) engagement, described reverse gear (81) and described common planet carrier output gear (61) engagement, described commutation synchronizer (82) engages with the end face of forward gear (83), or engages with the end face of reverse gear (81).
4. a kind of automobile-used planetary transmission according to claim 1 and 2, it is characterized in that: described steel band brake member (9) is the opening annulus that three sections of sections are the trapezoidal hinged formation of circular arc steel band, the middle part of first paragraph circular arc steel band (90) exterior arc surface is provided with projection (91), this projection and casing (1) inwall is hinged, and second segment circular arc steel band (92) is identical with the 3rd section of circular arc steel band (93) structure; One end of one end of second segment circular arc steel band (92) and described first paragraph circular arc steel band (90) is hinged, and the other end of second segment circular arc steel band (92) is provided with projection; The other end of one end of the 3rd section of circular arc steel band (93) and described first paragraph circular arc steel band (90) is hinged, and the other end of the 3rd section of circular arc steel band (93) is also provided with projection; The projection of second segment circular arc steel band (92) the other end is corresponding with the projection of the 3rd section of circular arc steel band (93) the other end, and two projections coordinate connection with gear shift control member.
5. a kind of automobile-used planetary transmission according to claim 2, it is characterized in that: described common planet carrier is connected to form by input end planet carrier (2) and output terminal planet carrier (4), described input end planet carrier (2) and output terminal planet carrier (4) connect and compose by two end plates, three planet pins (3) and three planet carrier connecting rods (5); It is upper that described one grade of epicyclic transmission mechanism and second gear epicyclic transmission mechanism are located at input end planet carrier (2), and described third gear epicyclic transmission mechanism, fourth gear epicyclic transmission mechanism and five grades of epicyclic transmission mechanisms are located on output terminal planet carrier (4).
6. a kind of automobile-used planetary transmission according to claim 2, is characterized in that: described the first planetary pinion (12) and the second planetary pinion (22) are duplicate gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420108016.XU CN203796871U (en) | 2014-03-11 | 2014-03-11 | Planetary gearbox for vehicles |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420108016.XU CN203796871U (en) | 2014-03-11 | 2014-03-11 | Planetary gearbox for vehicles |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203796871U true CN203796871U (en) | 2014-08-27 |
Family
ID=51379083
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420108016.XU Expired - Fee Related CN203796871U (en) | 2014-03-11 | 2014-03-11 | Planetary gearbox for vehicles |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203796871U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109185402A (en) * | 2018-09-28 | 2019-01-11 | 江苏荣圣汽车零部件有限公司 | One shaft type two-stage multi gear planetary transmission |
-
2014
- 2014-03-11 CN CN201420108016.XU patent/CN203796871U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109185402A (en) * | 2018-09-28 | 2019-01-11 | 江苏荣圣汽车零部件有限公司 | One shaft type two-stage multi gear planetary transmission |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8801566B2 (en) | Quad-clutch multi-speed transmission | |
| US8151662B2 (en) | Electric dual input clutch transmission | |
| CN105202123B (en) | Seven speed dual clutch formula automatic transmission | |
| CN202431850U (en) | Double-clutch transmission | |
| CN101949431B (en) | Rear drive gearbox of micro automobile | |
| CN103842690B (en) | Speed change gear | |
| KR101181746B1 (en) | Double Clutch Transmission | |
| CN101825161A (en) | The multi-speed transmission that has stacked planetary gear set | |
| US20130036848A1 (en) | Vehicle Transmissions | |
| CN103711877A (en) | Double-clutch automatic gearbox transmission device | |
| CN106838188B (en) | A kind of double-clutch automatic gearbox transmission device | |
| US8960032B2 (en) | Multi-clutch transmission for a motor vehicle | |
| CN109737188A (en) | Double-clutch speed changer | |
| CN103671748A (en) | Transmission device of dual-clutch transmission | |
| CN101730805B (en) | Transmission for a vehicle | |
| CN107191552A (en) | A kind of double-clutch automatic gearbox transmission device | |
| JP5276272B2 (en) | Industrial vehicle transmission | |
| CN106321748A (en) | Eight-speed double clutch speed change device | |
| CN104930134A (en) | Multiwheel axle-structured transmission | |
| CN103758944A (en) | Driving device for dual-clutch transmission | |
| CN203796871U (en) | Planetary gearbox for vehicles | |
| CN103629308A (en) | Double-clutch multi-stage automatic transmission | |
| CN203463568U (en) | Double-clutch automatic transmission | |
| CN103758970A (en) | Driving device for dual-clutch transmission | |
| CN106337905B (en) | A kind of gear arrangement for hybrid vehicle |
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: 20140827 Termination date: 20160311 |