CN101446331B - Planetary gearbox with multi-gear power gear shifting - Google Patents
Planetary gearbox with multi-gear power gear shifting Download PDFInfo
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- CN101446331B CN101446331B CN2008102385639A CN200810238563A CN101446331B CN 101446331 B CN101446331 B CN 101446331B CN 2008102385639 A CN2008102385639 A CN 2008102385639A CN 200810238563 A CN200810238563 A CN 200810238563A CN 101446331 B CN101446331 B CN 101446331B
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Abstract
The invention relates to a planetary gearbox with multi-gear power gear shifting, which comprises an input shaft and an output shaft, wherein, three planetary rows, three circular gear units and a brake are arranged between the input shaft and the output shaft; each planetary row consists of a frame, a ring gear and a sun gear respectively; each circular gear unit is formed in the way that two gears arranged on the input shaft and the output shaft are meshed respectively; three clutches are arranged between the input shaft and the output shaft; the three clutches can be alternatively spliced so that the gears of the three circular gear units are interconnected with at least one component in the frames, the ring gears and the sun gears of three planetary rows; therefore, under smaller geometric volume, the planetary gearbox can obtain a gear shifting mechanism with five forward gears and one reverse gear, realize the structure with the least controlling components and simple planetary rows, and obtain the most useful gears. The gearbox has the advantages that an engine can work well in the range of most fuel-efficient rotating speed, the transmission efficiency is high, the towing loss is small, and the oil consumption is reduced.
Description
Technical field
The present invention relates to a kind of gearbox, specifically, relate to a kind of planetary gearbox with multi-gear power gear shifting 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 shifting elements, these nine shifting elements comprise that three breaks, four clutches and two overrunning clutchs realize five forward and a reverse gear, all need three or four shifting elements 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, gearshift logic complexity, and band row loss is big, consumes relatively very greatly, and transmission efficiency is low.
What HOII P WO described for 2005/050060A1 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 transmission efficiency is low.
Summary of the invention
The technical problem to be solved in the present invention is to overcome above-mentioned shortcoming, provides a kind of with arrange the planetary gearbox with multi-gear power gear shifting that loss is little, efficient is high, can shift gears under load.
For addressing the above problem, the technical solution used in the present invention is: planetary gearbox with multi-gear power gear shifting comprises:
Input shaft and output shaft;
Be provided with first planet row, second planet row and the third line star row between this 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, be provided with first clutch between described input shaft and the output shaft, second clutch and three-clutch, described three clutches can engage selectively, with gear and three frameworks that planet is arranged with described three cylindrical gears groups, at least one interconnection in gear ring and the sun gear, it is characterized in that: 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 second clutch and the second cylindrical gears group.
The gear that is arranged on the input shaft in first planet row's a kind of concrete optimized project, described first planet row's gear ring and the second cylindrical gears group is fixedlyed connected.
First planet row's a kind of concrete optimized project is arranged in described first planet row's the sun gear and the first cylindrical gears group between the gear on the input shaft and is provided with three-clutch.
Second planet row's a kind of concrete optimized project, described second planet row and the coaxial setting of output shaft, second planet row's framework is connected with the third line star row's frame fixation.
Fixedly connected with the gear of the coaxial setting of output shaft in second planet row's a kind of concrete optimized project, described second planet row's gear ring and three cylindrical gear train.
The gear that is arranged on the output shaft in second planet row's a kind of 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 the third line star row's 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 optimized project of above technological 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 second clutch and the three cylindrical gear train.
Another kind of optimized project, described break and the coaxial setting of input shaft, described break are arranged between first planet row's the sun gear and gear box.
Another kind of optimized project, described input shaft links to each other with motor, main clutch or fluid torque converter.
Another kind of optimized project, described output shaft is connected with differential mechanism or main reducing gear.
The present invention adopts above technological scheme, has the following advantages:
(1) can under less geometric volume, obtain 5 forward gears and 1 gear that reverses gear, realize having obtained maximum useful gears with minimum operator and simple planet row structure.This gearbox can make motor work in the speed range of fuel-economizing better, the transmission efficiency height, and band row loss is little, has reduced fuel consumption, 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.
Cylindrical gears shunting transmission on (3) 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.
(4) adopt column gear transmission and two transmission shafts, make the sleeve decreased number two-layer, reduced manufacturing and technical difficulty to having only, saved manufacture cost, simultaneously, planet toothrow circle is shorter, the clutch rotation oil is simple in structure, compares with other planetary transmission, and 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 invention will be further described below in conjunction with drawings and Examples.
Embodiment
Accompanying drawing is the structural representation of gearbox in the embodiment of the invention.
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, as shown in the figure, planetary gearbox with multi-gear power gear shifting, the power shaft 1 that comprises gear box 26 and in gear box 26, be arranged in parallel and output shaft 2, wherein power shaft 1 links to each other with input power with fluid torque-converter 23, output shaft 2 is connected with outputting power with differential mechanism 24, be provided with three planet rows at power shaft 1 and output shaft 2, three Cylinder Gear wheels, three clutches and a brake 15, three planet rows comprise first planet row 12, second planet row 13 and third planet row 14, three Cylinder Gear wheels comprise the first Cylinder Gear wheels, second Cylinder Gear wheels and the three cylindrical gear train, three clutches comprise first clutch 16, second clutch 17 and three-clutch 18.
First planet row 12 is arranged on the input shaft 1, by framework 121, gear ring 122 and sun gear 123 are formed, second planet row 13 and output shaft 2 coaxial settings, by framework 131, gear ring 132 and sun gear 133 are formed, the third line star row 14 is arranged on the output shaft 2, by framework 141, gear ring 142 and sun gear 143 are formed, the first cylindrical gears group is made up of meshed gears 3 and gear 6, gear 3 relies on bearings on input shaft 1, gear 6 by bearings on output shaft 2, the second cylindrical gears group is made up of meshed gears 4 and gear 7, gear 4 relies on bearings on input shaft 1, and on output shaft 2, be made up of meshed gears 5 and gear 8 by the three cylindrical gear train by bearings for gear 7, gear 5 and the coaxial setting of input shaft, gear 8 and the coaxial setting of output shaft.
First planet row 12 framework 121 is fixedlyed connected with input shaft 1, gear ring 122 is fixedlyed connected with the gear 4 of the second cylindrical gears group, second planet row 13 framework 131 is connected with the third line star row 14 framework 141, gear ring 132 is fixedlyed connected with the gear 8 of three cylindrical gear train, sun gear 133 is connected with the gear 7 of the second cylinder group, the third line star row 14 framework 141 is fixedlyed connected with output shaft 2, gear ring 142 is fixedlyed connected with the gear 6 of the first cylindrical gears group, and sun gear 143 is fixedlyed connected with the gear 8 of three cylindrical gear train.
Three-clutch 18 is arranged between the gear 3 of the first cylindrical gears group and first planet row's 12 the sun gear 123, when three-clutch 18 is in jointing state, sun gear 123 and gear 3 interconnection, 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, first planet row 12 sun gear 123 is braked or separated, the gear 3 of uniting 18 pairs first cylindrical gears groups of three-clutch is simultaneously braked or is separated, the gear 4 of the second cylindrical gears group is connected by second clutch 17 with the gear 5 of three cylindrical gear train, when second clutch 17 is in jointing state, gear 4 is connected with gear 5, gear 4 is connected with the framework 121 of second clutch 17 with first planet row 12 by first clutch 16, when first clutch 16 and second clutch 17 are in jointing state simultaneously, framework 121 and gear 4 interconnection, 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 gearshift logical table of embodiment of the present invention
The gearshift logical table has shown how the various combination that uses these operator realizes that 1 reverses gear and the gearshift of 5 forward gears, and wherein line part is for being used in combination member, and blank parts is the shifting element of opening, and summary gearbox gear-shift principle is as follows:
The shift process that reverses gear is: break 15 and three-clutch 18 engage simultaneously, first planet row 12 the sun gear 123 and the gear 3 of the first cylindrical gears group are braked, cause 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 shift process of the 1st retaining is: second clutch 17 and three-clutch 18 engage simultaneously, the power of input shaft 1 arranges 12 speed changes by first planet and three cylindrical gear train, the first cylindrical gears 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.
The shift process of the 2nd retaining is: first clutch 16 and three-clutch 18 engage 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 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.
The shift process of the 3rd retaining is: first clutch 16 and second clutch 17 engage simultaneously, first planet row, 12 whole joints, the power of input shaft 1 directly passes to second planet row 13, speed change outputting power then by the three cylindrical gear train and the second cylindrical gears group.
The shift process of the 4th retaining is: first clutch 16 and break 15 engage simultaneously, first planet row 12 sun gear 123 is braked, framework 121 and gear ring 122 and three cylindrical gear train and the second cylindrical gears group of the power of input shaft 1 by first planet row 12 passes to second planet row 13, speed change outputting power then.
The shift process of the 5th retaining is: second clutch 17 and break 15 engage simultaneously, first planet row 12 sun gear 123 is braked, gear ring 122 and three cylindrical gear train and the second cylindrical gears group of the power of input shaft 1 by first planet row 12 passes to second planet row 13, speed change outputting power then.
Claims (13)
1. planetary gearbox with multi-gear power gear shifting 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 this 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, be provided with first clutch (16) between described input shaft (1) and the output shaft (2), second clutch (17) and three-clutch (18), described three clutches can engage selectively, with gear and three frameworks that planet is arranged with described three cylindrical gears groups, at least one interconnection in gear ring and the sun gear, it is characterized in that: 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 second clutch (17) and the second cylindrical gears group.
2. planetary gearbox with multi-gear power gear shifting 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. planetary gearbox with multi-gear power gear shifting as claimed in claim 2 is characterized in that: be arranged in described first planet row's (12) the sun gear (123) and the first cylindrical gears group between the gear (3) on the input shaft (1) and be provided with three-clutch (18).
4. as one of them described planetary gearbox with multi-gear power gear shifting of claim 1-3, it is characterized in that: described second planet is arranged (13) and the coaxial setting of output shaft (2), and second planet row's (13) framework (131) is fixedlyed connected with the third line star row's (14) framework (141).
5. planetary gearbox with multi-gear power gear shifting as claimed in claim 4 is characterized in that: fixedly connected with the gear (8) of the coaxial setting of output shaft (2) in described second planet row's (13) gear ring (132) and the three cylindrical gear train.
6. planetary gearbox with multi-gear power gear shifting 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. planetary gearbox with multi-gear power gear shifting as claimed in claim 6 is characterized in that: described the third line star row (14) is arranged on the output shaft (2), and the third line star row's (14) framework (141) is fixedlyed connected with output shaft (2).
8. planetary gearbox with multi-gear power gear shifting 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. planetary gearbox with multi-gear power gear shifting as claimed in claim 8 is characterized in that: fixedly connected with the gear (8) 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.
10. planetary gearbox with multi-gear power gear shifting 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 gear (5) of the coaxial setting of input shaft (1) by in second clutch (17) and the three cylindrical gear train.
11. planetary gearbox with multi-gear power gear shifting 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. planetary gearbox with multi-gear power gear shifting as claimed in claim 11 is characterized in that: described input shaft (1) links to each other with motor, main clutch or fluid torque converter.
13. planetary gearbox with multi-gear power gear shifting as claimed in claim 12 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 |
|---|---|---|---|
| CN2008102385639A CN101446331B (en) | 2008-12-18 | 2008-12-18 | Planetary gearbox with multi-gear power gear shifting |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2008102385639A CN101446331B (en) | 2008-12-18 | 2008-12-18 | Planetary gearbox with multi-gear power gear shifting |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101446331A CN101446331A (en) | 2009-06-03 |
| CN101446331B true CN101446331B (en) | 2010-08-11 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008102385639A Active CN101446331B (en) | 2008-12-18 | 2008-12-18 | Planetary gearbox with multi-gear power gear shifting |
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| CN (1) | CN101446331B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104179903B (en) * | 2014-06-25 | 2016-06-08 | 盛瑞传动股份有限公司 | Automatic transmission |
| CN105678106A (en) * | 2016-04-12 | 2016-06-15 | 中国北方车辆研究所 | Method for selecting planetary transmission schemes |
| EP3530986B1 (en) * | 2018-02-27 | 2023-04-19 | FCA Italy S.p.A. | A motor vehicle differential with a low range device |
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| CN101446331A (en) | 2009-06-03 |
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Owner name: SHENGRUI TRANSMISSION CORPORATION LIMITED Free format text: FORMER OWNER: WEIFANG SHENGRUI POWER SCIENCE + TECHNOLOGY CO., LTD. Effective date: 20150618 |
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Effective date of registration: 20150618 Address after: 261205 Weifang high tech Industrial Development Zone, Shandong Sheng Rui street, No. 518 Patentee after: Shengrui Transmission Corporation limited Address before: 261205 Shandong city of Weifang province high tech Zone Weihe Road East of Cherry Street South Patentee before: Weifang Shengrui Power Science & Technology Co., Ltd. |