CN102748435B - Planetary gear transmission based on double brakes - Google Patents
Planetary gear transmission based on double brakes Download PDFInfo
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- CN102748435B CN102748435B CN201210256717.3A CN201210256717A CN102748435B CN 102748435 B CN102748435 B CN 102748435B CN 201210256717 A CN201210256717 A CN 201210256717A CN 102748435 B CN102748435 B CN 102748435B
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- gear
- planetary gear
- planetary
- pto
- power take
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Abstract
The invention discloses a planetary gear transmission based on double brakes. The planetary gear transmission based on double brakes comprises two planetary gear sets which are arranged in parallel, sun wheels, big gear rings and a planet carrier, wherein a first sun wheel centre is connected with a power input shaft; a first planetary gear set is connected with the first sun wheel; the first planetary gear set is connected with a first big gear ring; the first big gear ring is provided with a first brake; a second sun wheel centre is connected with a power output shaft; a second planetary gear set is connected with a second sun wheel; the second planetary gear set is connected with a second big gear ring; the second big gear ring is provided with a second brake; one rotating shaft of the planet carrier is rotatably arranged in the centre holes of the first planetary gear set and the second planetary gear set in a passing manner; the other rotating shaft of the planet carrier is connected with the power output shaft; and an overrun clutch is arranged between the other rotating shaft of the planet carrier and the power output shaft. The structure of the planetary gear transmission based on double brakes is simple; and with the adoption of the double brakes, the planetary gear transmission is conveniently controlled, and an axial force is not generated during the process of the power driving.
Description
Technical field
The present invention relates to a kind of planetary transmission, particularly relate to a kind of planetary transmission based on dual brake in oil, cell mixed power automobile.
Background technique
In existing oil, cell mixed power automobile technology, in order to avoid the dynamic overload that drive motor often occurs, need to arrange speed changer between motor power input shaft and pto＝power take-off, to guarantee that the velocity ratio between motor power output shaft and main drive shaft is 1:1 under the normal condition travelled; When dynamic load is larger, the velocity ratio between the pto＝power take-off of motor and main drive shaft is (3-4): 1.
For realizing above-mentioned speed change request, usually utilizing gearbox to regulate pto＝power take-off output speed, reducing the input power of drive motor.Many use clutches and the multiple velocity ratio of the incompatible acquisition of planetary gear set at present, existing clutch generally adopts jaw clutch or friction clutcch to complete the switching of velocity variations, but only adopts jaw clutch cannot realize power not shift gears under interrupt condition; And friction clutcch can produce additional axial force (impacting force) and is directly delivered to bearing, make that bearing is fragile, working life reduces.
Summary of the invention
The object of the invention is to provide one can be applicable to oil-electric vehicle driving requirements, and structure is simple, and it is convenient to control, and can realize power and not interrupt gearshift, and not produce the planetary transmission based on dual brake of additional axial force.
The present invention is by the following technical solutions: planetary transmission comprises two groups of parallel planetary gear set set up, sun gear, bull gear and a planet carrier, first planet gear train and the second planetary gear set respectively comprise three with upper planetary gear, the first wherein said sun gear center is connected with power input shaft, first planet gear train is connected with the first sun gear, first planet gear train connects first gear ring, first gear ring is provided with the first break, control it by the first break decontrol or check, the second described sun gear center is connected with pto＝power take-off, second planetary gear set is connected with the second sun gear, second planetary gear set connects second largest gear ring, second largest gear ring is provided with second brake, control it by second brake decontrol or check, one rotatingshaft of planet carrier rotates and is located in first planet gear and the second center planetary gear hole, its another rotatingshaft is connected with pto＝power take-off, free wheel device is provided with between another rotatingshaft and pto＝power take-off.
Described power input shaft and pto＝power take-off are positioned on same shaft axis.
The gear of described first planet gear train is equal with the number of teeth of the gear of the second planetary gear set, and the first sun gear is equal with the second sun gear number of teeth, and first gear ring is equal with the second largest gear ring number of teeth.
Described is also provided with jaw clutch between another rotatingshaft and pto＝power take-off.
The present invention adopts above technological scheme, utilize two groups of parallel planetary gear set, sun gear, bull gear and planet carriers set up, adopt break to control bull gear decontrol or check, regulate pto＝power take-off output speed, the braking force of break can progressively strengthen, make pto＝power take-off softer to switch step work at a high speed at starting stage and low speed, power can be realized like this and do not interrupt gearshift; Adopt free wheel device between planet carrier rotatingshaft and pto＝power take-off, guarantee that pto＝power take-off is when slow speed turbine stage, output shaft connects with planet carrier, and during high speed level, output shaft and planet carrier are thrown off simultaneously.
The present invention can also increase between planet carrier rotatingshaft and pto＝power take-off and arranges jaw clutch, and such vehicle is when braking, and this speed changer has speedup function, obtains better oil-saving effect, simultaneously when moveing backward, realizes low speed rotation reversing.
Said structure of the present invention is simple, adopt dual brake to control convenient, and power train process does not have axial force to produce.
Accompanying drawing explanation
Now by reference to the accompanying drawings the present invention is further described:
Fig. 1 is planetary transmission transmission principle schematic diagram of the present invention.
Embodiment
Refer to shown in Fig. 1, the present invention includes two groups of parallel planetary gear set 4,9 set up, sun gear 3,8, bull gear 5,10 and planet carrier 13, described first planet gear train 4 and the second planetary gear set 9 respectively comprise three with upper planetary gear, the number of teeth z of the gear of first planet gear train 4 and the gear of the second planetary gear set 9
4, z
9equal, the first sun gear 3 and the second sun gear 8 number of teeth z
3, z
8equal, first gear ring and second largest gear ring number of teeth z
5, z
10equal.The first wherein said sun gear 3 center is connected with power input shaft 1, first planet gear train 4 is connected with the first sun gear 3, first planet gear train 4 connects first gear ring 5, first gear ring 5 is provided with the first break 6, control it by the first break 6 decontrol or check, the second described sun gear 8 center is connected with pto＝power take-off 2, described power input shaft 1 is positioned on same shaft axis with pto＝power take-off 2, second planetary gear set 9 is connected with the second sun gear 8, second planetary gear set 9 connects second largest gear ring 10, second largest gear ring 10 is provided with second brake 7, control it by second brake 7 decontrol or check, one rotatingshaft 131 of planet carrier 13 rotates and is located in first planet gear 4 and the second planetary pinion 9 center hole, its another rotatingshaft 132 is connected with pto＝power take-off 2, free wheel device 11 is provided with between another rotatingshaft 132 and pto＝power take-off 2, jaw clutch 12 can also be set up.
Said structure working principle of the present invention is as follows:
1, when the first break and second brake are decontroled simultaneously, power input shaft 1 drives the first sun gear 3 to rotate, and rotating speed is n
1, give first gear ring 5 by first planet gear train 4 transmission, planet carrier 13 is motionless, then the unpowered output of pto＝power take-off 2.
2, the first break is checked, second brake is decontroled, when jaw clutch 12 is separated, first gear ring 5 is motionless, first planet gear train 4 is driven by the first sun gear 3 and does planetary motion around the first sun gear 3, drives planet carrier 13 to rotate, by free wheel device 11, planet carrier 13 drives pto＝power take-off 2 to rotate, now the rotating speed n of dynamic pto＝power take-off 2
2equal the rotating speed n of planet carrier 13
13, so
pto＝power take-off 2 obtains low speed and exports.
3, when the first break and second brake are checked simultaneously, first gear ring 5 and second largest gear ring 5 motionless, power input shaft 1 drives the first sun gear 3 to rotate, first planet gear train 4 is driven by the first sun gear 3 and does planetary motion around the first sun gear 3, the second planetary gear set 9 is driven to do planetary motion around the second sun gear 8 by planet carrier 13, thus drive the second sun gear 8 to rotate, because
z
3=z
8, z
5=z
10, so n
2=n
1, n
2be greater than n
13, free wheel device is separated, and can not move interference between planet carrier 13 and pto＝power take-off 2, pto＝power take-off 2 obtains speedy carding process
The braking force of above-mentioned break 6,7 can progressively strengthen, and pto＝power take-off can be made softer to switch step work at a high speed at starting stage and low speed.
4, the first break is checked, and second brake is decontroled, and jaw clutch 12 closes, and when corresponding vehicle is in braking state, motive force output shaft 2 becomes power input shaft, and motive force input shaft 1 becomes pto＝power take-off, due to
so n
1be greater than n
2, pto＝power take-off now obtains speedup effect, plays good effect like this to the recovery of Brake Energy.
5, the first break is checked, and second brake is decontroled, and jaw clutch 12 closes, when corresponding vehicle is in reversing, due to
so n
2be less than n
1, can low-reverse be realized.
Claims (4)
1. the planetary transmission based on dual brake, comprise two groups of parallel planetary gear set set up, sun gear, bull gear and a planet carrier, first planet gear train and the second planetary gear set respectively comprise three with upper planetary gear, it is characterized in that: the first sun gear center is connected with power input shaft, first planet gear train is connected with the first sun gear, first planet gear train connects first gear ring, first gear ring is provided with the first break, control it by the first break decontrol or check, second sun gear center is connected with pto＝power take-off, second planetary gear set is connected with the second sun gear, second planetary gear set connects second largest gear ring, second largest gear ring is provided with second brake, control it by second brake decontrol or check, one rotatingshaft of planet carrier rotates and is located in first planet gear train and the second planetary gear set center hole, its another rotatingshaft is connected with pto＝power take-off, free wheel device is provided with between another rotatingshaft and pto＝power take-off.
2. a kind of planetary transmission based on dual brake according to claim 1, is characterized in that: described power input shaft and pto＝power take-off are positioned on same shaft axis.
3. a kind of planetary transmission based on dual brake according to claim 1, it is characterized in that: the planetary pinion of described first planet gear train is equal with the planetary number of teeth of the second planetary gear set, first sun gear is equal with the second sun gear number of teeth, and first gear ring is equal with the second largest gear ring number of teeth.
4. a kind of planetary transmission based on dual brake according to claim 1, is characterized in that: described is also provided with jaw clutch between another rotatingshaft and pto＝power take-off.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210256717.3A CN102748435B (en) | 2012-07-23 | 2012-07-23 | Planetary gear transmission based on double brakes |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210256717.3A CN102748435B (en) | 2012-07-23 | 2012-07-23 | Planetary gear transmission based on double brakes |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102748435A CN102748435A (en) | 2012-10-24 |
| CN102748435B true CN102748435B (en) | 2015-06-17 |
Family
ID=47028844
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210256717.3A Active CN102748435B (en) | 2012-07-23 | 2012-07-23 | Planetary gear transmission based on double brakes |
Country Status (1)
| Country | Link |
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| CN (1) | CN102748435B (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103511596B (en) * | 2013-09-30 | 2016-05-04 | 宁波新宏液压有限公司 | A kind of planet-gear speed reducer |
| CN103644265A (en) * | 2013-12-09 | 2014-03-19 | 中联重科股份有限公司 | Engineering machine and planetary reducing mechanism thereof |
| CN105114555B (en) * | 2015-08-28 | 2018-07-06 | 肖荣寿 | Multi gear is without the manual/automatic integrated one-way synchronization overrunning type speed variator of clutch |
| CN106122384A (en) * | 2016-08-02 | 2016-11-16 | 无锡艾尔特线性运动机械有限公司 | Double reduction device |
| CN107131264B (en) * | 2017-06-21 | 2019-05-21 | 北京理工大学 | A kind of epicyclic transmission mechanism and method based on the shift of belt flute profile brake |
| CN110005764A (en) * | 2019-04-25 | 2019-07-12 | 湖北星星电驱动有限公司 | A kind of two grades of speed changing type electric drive axles |
| CN112895883B (en) * | 2021-02-19 | 2022-06-03 | 西安交通大学 | Dual-drive-source and double-row planetary gear train multi-mode coupling driving system and automobile |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1236175A (en) * | 1968-05-18 | 1971-06-23 | Toyota Motor Co Ltd | A hydraulic control system of an automatic transmission |
| DE2926425A1 (en) * | 1979-06-28 | 1981-01-08 | Mannesmann Ag | Mechano-hydrostatic drive with divided output - has differential with planet carrier and driven shaft coupled to hydrostatic pump or motor |
| CN1793695A (en) * | 2004-12-21 | 2006-06-28 | 光洋精工株式会社 | Planetary gear apparatus |
| CN2859089Y (en) * | 2005-12-15 | 2007-01-17 | 江苏常发实业集团有限公司 | Planetary speed variator |
| CN201090689Y (en) * | 2007-10-23 | 2008-07-23 | 叶胜康 | Full-automatic control variable speed drive |
| CN202690911U (en) * | 2012-07-23 | 2013-01-23 | 福建省福工动力技术股份公司 | Planetary gearbox based on double brakes |
-
2012
- 2012-07-23 CN CN201210256717.3A patent/CN102748435B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1236175A (en) * | 1968-05-18 | 1971-06-23 | Toyota Motor Co Ltd | A hydraulic control system of an automatic transmission |
| DE2926425A1 (en) * | 1979-06-28 | 1981-01-08 | Mannesmann Ag | Mechano-hydrostatic drive with divided output - has differential with planet carrier and driven shaft coupled to hydrostatic pump or motor |
| CN1793695A (en) * | 2004-12-21 | 2006-06-28 | 光洋精工株式会社 | Planetary gear apparatus |
| CN2859089Y (en) * | 2005-12-15 | 2007-01-17 | 江苏常发实业集团有限公司 | Planetary speed variator |
| CN201090689Y (en) * | 2007-10-23 | 2008-07-23 | 叶胜康 | Full-automatic control variable speed drive |
| CN202690911U (en) * | 2012-07-23 | 2013-01-23 | 福建省福工动力技术股份公司 | Planetary gearbox based on double brakes |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102748435A (en) | 2012-10-24 |
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Address after: 350000, Gulou District, Fujian Province, 89 software Avenue, Fuzhou Software Park industrial base two, building 9, No. 1, Fuzhou Applicant after: FUJIAN FUGONG POWER TECHNOLOGY CO., LTD. Address before: 350000, Gulou District, Fujian Province, 89 software Avenue, Fuzhou Software Park industrial base two, building 9, No. 1, Fuzhou Applicant before: Fujian Fugong HEV Technology Co., Ltd. |
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Free format text: CORRECT: APPLICANT; FROM: FUJIAN FUGONG HEV TECHNOLOGIES DEVELOPMENT CO., LTD. TO: FUJIAN FUGONG POWER TECHNOLOGY CO., LTD. |
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