CN202091448U - Multi-gear planetary gearbox - Google Patents
Multi-gear planetary gearbox Download PDFInfo
- Publication number
- CN202091448U CN202091448U CN2011201553511U CN201120155351U CN202091448U CN 202091448 U CN202091448 U CN 202091448U CN 2011201553511 U CN2011201553511 U CN 2011201553511U CN 201120155351 U CN201120155351 U CN 201120155351U CN 202091448 U CN202091448 U CN 202091448U
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- CN
- China
- Prior art keywords
- gear
- clutch
- sun gear
- sun
- planet carrier
- 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
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Abstract
Provided is a multi-gear planetary gearbox, wherein a first planet carrier, a second planet carrier and a third planet carrier are a unitary planet carrier; the second planet gear mechanism is a double planet gear structure; five sun gears are coaxial, wherein a third sun gear and a fourth sun gear are duplex gears. According to the utility model, gears are increased to realize large speed ratio transmission and to make the gradient change of the speed ratio more reasonable; the speedup or deceleration values are controlled within a certain scope, which can effectively avoid impact to the gears in gearshift operation, and then can prolong gear service life and raise gearbox quality.
Description
Technical field
The utility model relates to a kind of many gears planetary transmission, especially for many gears planetary transmission of high speed bulldozer power transmission system.
Background technique
Present conventional bulldozer power transmission gearbox can realize advancing third gear, retreat the transmission of third gear, the gear of this gearbox is less, velocity ratio there is certain restriction, when the high speed bulldozer need transmit bigger velocity ratio, the negligible amounts of gear causes the distribution gradient of speed ratio unreasonable, gear shift operation when speedup or reduction of speed are excessive is bigger to the impact of gear, can cause adverse effect to the life-span of gear to a certain extent.
The model utility content
The purpose of this utility model provides a kind of many gears planetary transmission, be applied to high speed bulldozer power transmission system, the negligible amounts that solves existing bulldozer gear causes the distribution gradient of speed ratio unreasonable, gear shift operation when speedup or reduction of speed are excessive is bigger to the impact of gear, is caused the problem of adverse effect the life-span of gear.
The technological scheme that its technical problem that solves the utility model adopts is: a kind of many gears planetary transmission, mainly comprise first planet carrier, first sun gear, second sun gear, the 3rd sun gear, the 4th sun gear, the 5th sun gear, first planetary pinion, first gear ring, second planetary pinion, second gear ring, the third line star gear, the 3rd gear ring, fourth line star gear, the 4th gear ring, fifth line star gear, the 5th gear ring, the gear I, the gear II, output shaft, the V outer clutch drum, fourth line star frame, the VII outer clutch drum, fifth line star frame, second falls back uses planetary pinion, input shaft, second planet carrier, the third line star frame, the I clutch, the II clutch, the III clutch, the IV clutch, the V clutch, the VI clutch, the VII clutch, first planet carrier wherein, second planet carrier, the third line star frame is an integral planet carrier, and second planetary gears is the dual planetary gear structure; Five sun gears are coaxial construction, and wherein the 3rd sun gear, the 4th sun gear are a duplex gear.
Described first sun gear, second sun gear, the 3rd sun gear, the 4th sun gear, the 5th sun gear are connected by spline with input shaft.
Described clutch is the hydraulic coupling that has piston, backing plate, friction plate.
Described first gear ring is meshed with the friction plate internal tooth of I clutch by its external tooth; Second gear ring is meshed with the friction plate internal tooth of II clutch by its external tooth; The 3rd gear ring is meshed with the friction plate internal tooth of III clutch by its external tooth; The 4th gear ring is meshed with the friction plate internal tooth of IV clutch by its external tooth; The 5th gear ring is meshed with the friction plate internal tooth of VI clutch by its external tooth.
Described gear I is connected by spline with the VII outer clutch drum; The gear II is connected by spline with output shaft.
The utility model is realized the transmission of large speed ratio by the increase of gear, make the graded of speed ratio more reasonable, the numerical value of control speedup or deceleration within the specific limits, when avoiding gear shift operation effectively to the impact of gear, and then the working life of prolongation gear, the quality of raising gearbox.
Description of drawings
Fig. 1 is a structure principle chart of the present utility model.
1-first planet carrier among the figure, 2-first sun gear, 3-second sun gear, 4-the 3rd sun gear, 5-the 4th sun gear, 6-the 5th sun gear, 7-first planetary pinion, 8-first gear ring, 9-second planetary pinion, 10-second gear ring, 11-the third line star gear, 12-the 3rd gear ring, 13-fourth line star gear, 14-the 4th gear ring, 15-fifth line star gear, 16-the 5th gear ring, 17-gear I, 18-gear II, the 19-output shaft, 20-V outer clutch drum, 21-fourth line star frame, 22-VII outer clutch drum, 23-fifth line star frame, 24-second falls back and uses planetary pinion, the 25-input shaft, 26-second planet carrier, 27-the third line star frame.
Embodiment
A kind of many gears planetary transmission, mainly comprise first planet carrier 1, first sun gear 2, second sun gear 3, the 3rd sun gear 4, the 4th sun gear 5, the 5th sun gear 6, first planetary pinion 7, first gear ring 8, second planetary pinion 9, second gear ring 10, the third line star gear 11, the 3rd gear ring 12, fourth line star gear 13, the 4th gear ring 14, fifth line star gear 15, the 5th gear ring 16, gear I 17, gear II 18, output shaft 19, V outer clutch drum 20, fourth line star frame 21, VII outer clutch drum 22, fifth line star frame 23, second falls back with planetary pinion 24, input shaft 25, second planet carrier 26, the third line star frame 27, the I clutch, the II clutch, the III clutch, the IV clutch, the V clutch, the VI clutch, the VII clutch, first planet carrier 1 wherein, second planet carrier 26, the third line star frame 27 is an integral planet carrier, and second planetary gears is the dual planetary gear structure; Five sun gears are coaxial construction, and wherein the 3rd sun gear 4, the 4th sun gear 5 are a duplex gear.
Described first sun gear 2, second sun gear 3, the 3rd sun gear 4, the 4th sun gear 5, the 5th sun gear 6 and input shaft 25 are connected by spline.
Described clutch is the hydraulic coupling that has piston, backing plate, friction plate.
Described first gear ring 8 is meshed with the friction plate internal tooth of I clutch by its external tooth; Second gear ring 10 is meshed with the friction plate internal tooth of II clutch by its external tooth; The 3rd gear ring 12) is meshed with the friction plate internal tooth of III clutch by its external tooth; The 4th gear ring 14 is meshed with the friction plate internal tooth of IV clutch by its external tooth; The 5th gear ring 16 is meshed with the friction plate internal tooth of VI clutch by its external tooth.
Described gear I 17 is connected by spline with VII outer clutch drum 22; Gear II 18 and output shaft 19 are connected by spline.
Claims (5)
1. gear planetary transmission more than a kind, mainly comprise first planet carrier (1), first sun gear (2), second sun gear (3), the 3rd sun gear (4), the 4th sun gear (5), the 5th sun gear (6), first planetary pinion (7), first gear ring (8), second planetary pinion (9), second gear ring (10), the third line star gear (11), the 3rd gear ring (12), fourth line star gear (13), the 4th gear ring (14), fifth line star gear (15), the 5th gear ring (16), gear I (17), gear II (18), output shaft (19), V outer clutch drum (20), fourth line star frame (21), VII outer clutch drum (22), fifth line star frame (23), second falls back with planetary pinion (24), input shaft (25), second planet carrier (26), the third line star frame (27), the I clutch, the II clutch, the III clutch, the IV clutch, the V clutch, the VI clutch, the VII clutch, it is characterized in that: first planet carrier (1) wherein, second planet carrier (1), the third line star frame (1) is an integral planet carrier, and second planetary gears is the dual planetary gear structure; Five sun gears are coaxial construction, and wherein the 3rd sun gear (4), the 4th sun gear (5) are a duplex gear.
2. a kind of many gears planetary transmission according to claim 1 is characterized in that: described first sun gear (2), second sun gear (3), the 3rd sun gear (4), the 4th sun gear (5), the 5th sun gear (6) are connected by spline with input shaft (25).
3. a kind of many gears planetary transmission according to claim 1 is characterized in that: described clutch is the hydraulic coupling that has piston, backing plate, friction plate.
4. a kind of many gears planetary transmission according to claim 1 is characterized in that: described first gear ring (8) is meshed with the friction plate internal tooth of I clutch by its external tooth; Second gear ring (10) is meshed with the friction plate internal tooth of II clutch by its external tooth; The 3rd gear ring (12) is meshed with the friction plate internal tooth of III clutch by its external tooth; The 4th gear ring (14) is meshed with the friction plate internal tooth of IV clutch by its external tooth; The 5th gear ring (16) is meshed with the friction plate internal tooth of VI clutch by its external tooth.
5. a kind of many gears planetary transmission according to claim 1 is characterized in that: described gear I (17) is connected by spline with VII outer clutch drum (22); Gear II (18) is connected by spline with output shaft (19).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011201553511U CN202091448U (en) | 2011-05-16 | 2011-05-16 | Multi-gear planetary gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011201553511U CN202091448U (en) | 2011-05-16 | 2011-05-16 | Multi-gear planetary gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202091448U true CN202091448U (en) | 2011-12-28 |
Family
ID=45366517
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011201553511U Expired - Fee Related CN202091448U (en) | 2011-05-16 | 2011-05-16 | Multi-gear planetary gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202091448U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103256355A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Double-planet-row converging type multi-clutch transmission |
| CN104412005A (en) * | 2012-07-02 | 2015-03-11 | 卡特彼勒公司 | Configuration for compact five speed planetary transmission |
| CN105351462A (en) * | 2015-11-24 | 2016-02-24 | 山推工程机械股份有限公司 | Transmission for bulldozer |
| CN105835695A (en) * | 2016-05-25 | 2016-08-10 | 广州市新域动力技术有限公司 | Single and double-plate clutch combined type dual-motor hybrid power assembly |
| CN106004410A (en) * | 2016-05-25 | 2016-10-12 | 广州市新域动力技术有限公司 | Double-plate clutch hybrid power assembly suitable for new energy automobile |
| 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 |
-
2011
- 2011-05-16 CN CN2011201553511U patent/CN202091448U/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104412005A (en) * | 2012-07-02 | 2015-03-11 | 卡特彼勒公司 | Configuration for compact five speed planetary transmission |
| CN104412005B (en) * | 2012-07-02 | 2017-04-19 | 卡特彼勒公司 | Configuration for compact five speed planetary transmission |
| CN103256355A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Double-planet-row converging type multi-clutch transmission |
| CN103256355B (en) * | 2013-04-28 | 2015-07-15 | 河南科技大学 | Double-planet-row converging type multi-clutch transmission |
| CN105351462A (en) * | 2015-11-24 | 2016-02-24 | 山推工程机械股份有限公司 | Transmission for bulldozer |
| CN105835695A (en) * | 2016-05-25 | 2016-08-10 | 广州市新域动力技术有限公司 | Single and double-plate clutch combined type dual-motor hybrid power assembly |
| CN106004410A (en) * | 2016-05-25 | 2016-10-12 | 广州市新域动力技术有限公司 | Double-plate clutch hybrid power assembly suitable for new energy automobile |
| 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 |
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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 |
Granted publication date: 20111228 Termination date: 20160516 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |