CN201359060Y - Multi-gear power shift planetary gearbox - Google Patents
Multi-gear power shift planetary gearbox Download PDFInfo
- Publication number
- CN201359060Y CN201359060Y CNU2008202275761U CN200820227576U CN201359060Y CN 201359060 Y CN201359060 Y CN 201359060Y CN U2008202275761 U CNU2008202275761 U CN U2008202275761U CN 200820227576 U CN200820227576 U CN 200820227576U CN 201359060 Y CN201359060 Y CN 201359060Y
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- gear
- input shaft
- clutch
- output shaft
- cylindrical
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Abstract
The utility model relates to multi-gear power shift planetary gearbox, which comprises an input shaft and an output shaft. Three planet rows, three cylindrical gear sets and a brake are arranged between the input shaft and the output shaft. Each planet row includes a frame, a gear ring and a sun gear. Each cylindrical gear set includes two gears respectively arranged on the input shaft and the output shaft and engaged together. A first clutch, a second clutch and a third clutch are arranged between the input shaft and the output shaft. The frame of the first planet row is fixedly connected with the input shaft. The frame is connected with the gear of the second cylindrical gear set arranged on the input shaft through the first clutch and the third clutch. A gear shift mechanism with five forward gears and one reverse gear is obtained under a small geometric volume. The purpose of obtaining the most useful gears through using the least controls and simple planet rows is realized.
Description
Technical field
The utility model relates to a kind of gearbox, specifically, relates to a kind of a kind of many gears power shfit planetary transmission that main transmission is used for vehicle driveline that is suitable as.
Background technique
Japan likes that letter company has produced a kind of five gear automatic speed changing casees, comprises two axle systems, a cylindrical gear pair and three planet schedule mechanisms, realizes the variation of gearbox velocity ratio with this, and this gearbox is applicable to the horizontal structure of forerunner.Each gear at this speed changer, power circuit is only passed through a cylindrical gear pair from the input shaft to the transmission shaft, this speed changer has nine gear-changing components, these nine gear-changing components comprise that three breaks, four clutches and two overrunning clutchs realize five forward and a reverse gear, all need three or four gear-changing components to engage at each gear.This gearbox can be realized five gears by planet row mechanism, actuating element and the cylindrical gears group that links to each other, but annexation realizes difficulty, and operator quantity is too much, the shift logic complexity, and band row loss is big, consumes relatively very greatly, and efficient is low.
What HOII P WO described for 2005/050060 A1 number is a kind of six gear automatic speed changing casees, and the existing cylindrical gears group of this gearbox also has planet schedule mechanism, realizes the gearbox velocity ratio with this.It only shows as by interconnective three the parallel axes systems of cylindrical gears group, and a cover has respectively been installed in order to realize the planet schedule mechanism and the actuating element of at least three gears by two axle systems, at the 3rd axle-system axial live axle and driven shaft is installed.The whole drive system that is split on three axle systems obtains short total length, is specially adapted to the horizontal structure of forerunner.At each gear, power circuit is only by an axle system in live axle, driven shaft and two other system, and the control system in these two axle systems respectively realizes three gears.To in such axle system, realize three gears, need at least two be mutually related planet schedule mechanism and three actuating elements.Four the planets row mechanisms of this gearbox by linking to each other, six actuating elements and cylindrical gears group can only realize six gears, and planet row and operator quantity are too much.The operator of this gearbox is many, and band row loss is big, consumes relatively very greatly, and efficient is low.
The model utility content
The technical problems to be solved in the utility model is to overcome above-mentioned shortcoming, provides a kind of band row loss little, transmission efficiency height, can be at many gears power shfit planetary transmission of gear shift under the load.
For addressing the above problem, the technical solution adopted in the utility model is: a kind of many gears power shfit planetary transmission comprises:
Input shaft and output shaft;
Be provided with first planet row, second planet row and the third line star row between described input shaft and the output shaft, and
The first cylindrical gears group, the second cylindrical gears group, three cylindrical gear train and a break;
Wherein, each planet row is made up of framework, gear ring and sun gear respectively;
Each cylindrical gears group is formed by two gear engagement that are arranged on input shaft and the output shaft respectively, it is characterized in that:
Between input shaft and output shaft, be provided with first clutch, second clutch and three-clutch, described first planet row's framework is fixedlyed connected with input shaft, and this framework is connected by the gear that is arranged on the input shaft in first clutch and three-clutch and the second cylindrical gears group.
The gear that is arranged on the input shaft in first planet row's the concrete optimized project, described first planet row's gear ring and the second cylindrical gears group is fixedlyed connected.
The gear that is arranged on the input shaft in first planet row's the concrete optimized project, first planet row's sun gear and the first cylindrical gears group is fixedlyed connected.
Second planet row's concrete optimized project, described second planet row and the coaxial setting of output shaft, its framework is connected with the third line star row's frame fixation.
Second planet row's concrete optimized project is provided with second clutch in described second planet row's gear ring and the three cylindrical gear train with between the gear of the coaxial setting of output shaft.
The gear that is arranged on the output shaft in second planet row's the concrete optimized project, described second planet row's sun gear and the second cylindrical gears group is fixedlyed connected.
The third line star row's concrete optimized project, described the third line star row is arranged on the output shaft, and its framework is fixedlyed connected with output shaft.
The gear that is arranged on the output shaft in the third line star row's the concrete optimized project, described the third line star row's gear ring and the first cylindrical gears group is fixedlyed connected.
Fixedly connected with the gear of the coaxial setting of output shaft in the third line star row's the concrete optimized project, described the third line star row's sun gear and three cylindrical gear train.
The concrete optimized project of technique scheme, the gear that is arranged in the described second cylindrical gears group on the input shaft is connected with the gear of the coaxial setting of input shaft by in three-clutch and the three cylindrical gear train.
The concrete optimized project of technique scheme, described break and the coaxial setting of input shaft, described break are arranged between first planet row's the sun gear and gear box.
The concrete optimized project of technique scheme, described input shaft links to each other with motor, main clutch or fluid torque converter.
The concrete optimized project of technique scheme, described output shaft is connected with differential mechanism or main reducing gear.
The utility model adopts above technological scheme, has the following advantages:
(1), can under less geometric volume, obtain 5 forward gears and 1 gear that reverses gear, realized having obtained maximum useful gears with minimum operator and simple planet row structure.Many gears gearbox can better make motor work in the speed range of fuel-economizing, and band row loss is little, and the transmission efficiency height has reduced fuel consumption greatly, and simultaneously, the expansion of speed range has improved the acceleration performance of vehicle.
(2), adopt two transmission shafts, can shorten the axial length of gearbox, make gearbox adapt to the horizontal structure of automobile forerunner, also adapt to forerunner vertical interposed structure, particularly four-wheel drive vehicle, be suitable for too.Therefore, it is more extensive to adapt to vehicle, can one the case uses more.
(3), the cylindrical gears shunting transmission on two transmission shafts, can be easily according to the type of car and the differential and total transmission range of velocity ratio, velocity ratio of use variation gearbox.Be convenient to vehicle platformization and generalization, be convenient to produce in batches, save cost.
(4), adopt column gear transmission and two transmission shafts, make the sleeve decreased number two-layer to having only, reduced manufacturing and technical difficulty, saved manufacture cost, simultaneously, planet toothrow circle is shorter, the clutch rotation oil is simple in structure.Compare with other planetary transmission, structure is simpler.
(5), adopt column gear transmission, can on only transmission shaft, drive motor be installed, match only velocity ratio, repack mixed power into, adapt to the upgrading of gearbox, change the motor machine mixed power system into.
The utility model is described in further detail below in conjunction with drawings and Examples.
Description of drawings
Accompanying drawing is the structural representation of gearbox among the utility model embodiment.
Among the figure:
The 1-input shaft
The 2-output shaft
Be positioned at the gear on the input shaft in the 3-first cylindrical gears group
Be positioned at the gear on the input shaft in the 4-second cylindrical gears group
Be positioned at the gear on the input shaft in the 5-three cylindrical gear train
Be positioned at the gear on the output shaft in the 6-first cylindrical gears group
Be positioned at the gear on the output shaft in the 7-second cylindrical gears group
Be positioned at the gear on the output shaft in the 8-three cylindrical gear train
12-first planet row
13-second planet row
14-the third line star row
The 15-break
The 16-first clutch
The 17-second clutch
The 18-three-clutch
Clutch between 23-motor and the gearbox or fluid torque converter
The 24-differential mechanism
The 25-live axle connects left and right sides tire
The 26-gear box
121-first planet row's framework
122-first planet row's gear ring
123-first planet row's sun gear
131-second planet row's framework
132-second planet row's gear ring
133-second planet row's sun gear
141-the third line star row's framework
142-the third line star row's gear ring
143-the third line star row's sun gear
Embodiment
Embodiment, as shown in the figure, a kind of many gears power shfit planetary transmission, input shaft 1 that comprises gear box 26 and in gear box 26, be arranged in parallel and output shaft 2, wherein input shaft 1 links to each other with fluid torque converter 23 with input power, output shaft 2 is connected with outputting power with differential mechanism 24, be provided with three planet rows at input shaft 1 and output shaft 2, three cylindrical gears groups, three clutches with a break 15, first planet row 12 is drawn together in three planet packages, second planet row 13 and the third line star row 14, three cylindrical gears groups comprise the first cylindrical gears group, second cylindrical gears group and the three cylindrical gear train, three clutches comprise first clutch 16, second clutch 17 and three-clutch 18.
Be provided with three-clutch 18 between the gear 4 of the second cylindrical gears group and the gear 5 of three cylindrical gear train, when three-clutch 18 is in jointing state, gear 4 is connected with gear 5, be provided with first clutch 16 and three-clutch 18 between the gear 4 of the second cylindrical gears group and first planet row's 12 the framework 121, when first clutch 16 and three-clutch 18 engage simultaneously, gear 4 is connected with first planet row 12 framework 121, be provided with second clutch 17 between the gear 8 of three cylindrical gear train and second planet row's 13 the gear ring 132, when second clutch 17 engages, gear 8 is connected with gear ring 132, break 15 and input shaft 1 coaxial setting, this break 15 is arranged between first planet row 12 the sun gear 123 and gear box 26, simultaneously the gear 3 of the first cylindrical gears group is braked with first planet row 12 sun gear 123 or separated, output shaft 2 drives differential mechanism 24 by other gear train, and differential mechanism 24 drives live axle 25 and rotates.
It below is the shift logic table of the utility model mode of execution
The shift logic table has shown how the various combination that uses these operator realizes that 1 reverses gear and 5 forward gear gear shift, and wherein line part is for being used in combination member, and blank parts is the gear-changing component of opening, and summary gearbox gear-shift principle is as follows:
The gearshift procedure that reverses gear is: break 15 and second clutch 17 combinations simultaneously, first planet row 12 the sun gear 123 and the gear 3 of the first cylindrical gears group are braked, cause the gear 6 of the first cylindrical gears group and the third line star row 14 gear ring 142 to be braked, power passes to second planet row 13 and the third line star row 14 by first planet row, the 12 and second cylindrical gears group, and counterrotating is by output shaft 2 outputting powers.
The gearshift procedure of the 1st retaining is: break 15 and first clutch 16 combinations simultaneously, first planet row 12 the sun gear 123 and the gear 3 of the first cylindrical gears group are braked, cause the gear 6 of the first cylindrical gears group and the third line star row 14 gear ring 142 to be braked, power directly passes to second planet row 13 by the three cylindrical gear train and the second cylindrical gears group, and outputting power then slows down.
The gearshift procedure of the 2nd retaining is: break 15 and three-clutch 18 combinations simultaneously, first planet row 12 the sun gear 123 and the gear 3 of the first cylindrical gears group are braked, cause the gear 6 of the first cylindrical gears group and the third line star row 14 gear ring 142 to be braked, power passes to second planet row 13 by first planet row, the 12 and second cylindrical gears group, and outputting power then slows down.
The gearshift procedure of the 3rd retaining is: first clutch 16 and three-clutch 18 combinations simultaneously, first planet is arranged 12 whole combinations, the power of input shaft 1 passes to second planet row 13 and the third line star row 14, outputting power then by the first cylindrical gears group, the second cylindrical gears group and three cylindrical gear train.
The gearshift procedure of the 4th retaining is: second clutch 17 and three-clutch 18 combinations simultaneously, the power of input shaft 1 arranges 12 speed changes by first planet and three cylindrical gear train, the first cylindrical gears group gear train and the second cylindrical gears group pass to second planet row 13 and the third line star row 14, speed change outputting power then.
The gearshift procedure of the 5th retaining is: first clutch 16 and second clutch 17 combinations simultaneously, the power of input shaft 1 arranges 12 speed changes by first planet and three cylindrical gear train gear, the first cylindrical gears group gear engagement group and the second cylindrical gears group pass to second planet row 13 and the third line star row 14, speed change outputting power then.
Claims (13)
1, a kind of many gears power shfit planetary transmission comprises:
Input shaft (1) and output shaft (2);
Be provided with first planet row (12), second planet row (13) and the third line star row (14) between described input shaft (1) and the output shaft (2), and
The first cylindrical gears group, the second cylindrical gears group, three cylindrical gear train and a break (15);
Wherein, each planet row is made up of framework, gear ring and sun gear respectively;
Each cylindrical gears group is formed by two gear engagement that are arranged on input shaft (1) and the output shaft (2) respectively, it is characterized in that:
Between input shaft (1) and output shaft (2), be provided with first clutch (16), second clutch (17) and three-clutch (18), described first planet row's (12) framework (121) is fixedlyed connected with input shaft (1), and this framework (121) is connected by the gear (4) that is arranged on the input shaft (1) in first clutch (16) and three-clutch (18) and the second cylindrical gears group.
2, a kind of many gears power shfit planetary transmission as claimed in claim 1 is characterized in that: the gear (4) that is arranged on the input shaft (1) in described first planet row's (12) gear ring (122) and the second cylindrical gears group is fixedlyed connected.
3, a kind of many gears power shfit planetary transmission as claimed in claim 2 is characterized in that: the gear (3) that is arranged on the input shaft (1) in first planet row's (12) sun gear (123) and the first cylindrical gears group is fixedlyed connected.
4, as claim 1,2,3 one of them described a kind of many gears power shfit planetary transmission, it is characterized in that: described second planet is arranged (13) and the coaxial setting of output shaft (2), and its framework (131) is fixedlyed connected with the third line star row's (14) framework (141).
5, a kind of many gears power shfit planetary transmission as claimed in claim 4 is characterized in that: take turns between (8) being provided with second clutch (17) in described second planet row's (13) gear ring (132) and the three cylindrical gear train with the octadentate of the coaxial setting of output shaft (2).
6, a kind of many gears power shfit planetary transmission as claimed in claim 5 is characterized in that: the gear (7) that is arranged on the output shaft (2) in described second planet row's (13) sun gear (133) and the second cylindrical gears group is fixedlyed connected.
7, a kind of many gears power shfit planetary transmission as claimed in claim 6 is characterized in that: described the third line star row (14) is arranged on the output shaft (2), and its framework (141) is fixedlyed connected with output shaft (2).
8, a kind of many gears power shfit planetary transmission as claimed in claim 7 is characterized in that: the gear (6) that is arranged on the output shaft (2) in described the third line star row's (14) gear ring (142) and the first cylindrical gears group is fixedlyed connected.
9, a kind of many gears power shfit planetary transmission as claimed in claim 8 is characterized in that: take turns (8) with the octadentate of the coaxial setting of output shaft (2) in described the third line star row's (14) sun gear (143) and the three cylindrical gear train and fixedly connected.
10, a kind of many gears power shfit planetary transmission as claimed in claim 9 is characterized in that: the gear (4) that is arranged in the described second cylindrical gears group on the input shaft (1) is connected with the 5th gear (5) of the coaxial setting of input shaft (1) by in three-clutch (18) and the three cylindrical gear train.
11, a kind of many gears power shfit planetary transmission as claimed in claim 10, it is characterized in that: described break (15) and the coaxial setting of input shaft (1), described break (15) are arranged between first planet row's (12) the sun gear (123) and gear box (26).
12, a kind of many gears power shfit planetary transmission as claimed in claim 11, it is characterized in that: described input shaft (1) links to each other with motor, main clutch or fluid torque converter.
13, a kind of many gears power shfit planetary transmission as claimed in claim 12, it is characterized in that: described output shaft (2) is connected with differential mechanism or main reducing gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008202275761U CN201359060Y (en) | 2008-12-18 | 2008-12-18 | Multi-gear power shift planetary gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008202275761U CN201359060Y (en) | 2008-12-18 | 2008-12-18 | Multi-gear power shift planetary gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201359060Y true CN201359060Y (en) | 2009-12-09 |
Family
ID=41424824
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008202275761U Expired - Lifetime CN201359060Y (en) | 2008-12-18 | 2008-12-18 | Multi-gear power shift planetary gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201359060Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102900816A (en) * | 2012-10-24 | 2013-01-30 | 重庆赛特尔机械有限公司 | Gearbox |
| CN103256352A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Double-planet-row converging type multi-gear multi-clutch transmission |
| CN103438164A (en) * | 2013-07-27 | 2013-12-11 | 顺德职业技术学院 | Multi-speed gearbox transmission mechanism |
-
2008
- 2008-12-18 CN CNU2008202275761U patent/CN201359060Y/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102900816A (en) * | 2012-10-24 | 2013-01-30 | 重庆赛特尔机械有限公司 | Gearbox |
| CN103256352A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Double-planet-row converging type multi-gear multi-clutch transmission |
| CN103256352B (en) * | 2013-04-28 | 2015-08-19 | 河南科技大学 | Double planet wheel rows of mixing convergent current type many grades of multi-clutch speed changers |
| CN103438164A (en) * | 2013-07-27 | 2013-12-11 | 顺德职业技术学院 | Multi-speed gearbox transmission mechanism |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20091209 Effective date of abandoning: 20081218 |