CN205298429U - Six keep off planetary gear automatic gearbox - Google Patents
Six keep off planetary gear automatic gearbox Download PDFInfo
- Publication number
- CN205298429U CN205298429U CN201620069520.2U CN201620069520U CN205298429U CN 205298429 U CN205298429 U CN 205298429U CN 201620069520 U CN201620069520 U CN 201620069520U CN 205298429 U CN205298429 U CN 205298429U
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- Prior art keywords
- clutch
- row
- gear
- planetary gear
- input shaft
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- 230000005540 biological transmission Effects 0.000 claims abstract description 29
- 230000007246 mechanism Effects 0.000 claims abstract description 26
- 230000033001 locomotion Effects 0.000 description 8
- 230000008859 change Effects 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 239000010718 automatic transmission oil Substances 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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Abstract
The utility model discloses a six-gear planetary gear automatic transmission, which comprises a power input shaft and a power output shaft; the first output end of the power input shaft is connected with a front row gear ring of the planetary gear mechanism through a first clutch, the second output end of the power input shaft is connected with a front row sun gear of the planetary gear mechanism through a second clutch, the third output end of the power input shaft is connected with a rear row gear ring of the planetary gear mechanism through a third clutch, the fourth output end of the power input shaft is connected with a rear row planet carrier of the planetary gear mechanism through a fourth clutch, and the fifth output end of the power input shaft is connected with a rear row sun gear of the planetary gear mechanism through a fifth clutch. The utility model discloses an automatic transmission comprises the double planetary gear mechanism of parameter difference, and two rows of planetary gear mechanism are relatively independent, can form the fender position that 6 drive ratio rational distribution go, and each keeps off the during operation by single row planetary gear mechanism transmission power, and the power transmission route is simple.
Description
Technical Field
The utility model relates to a six keep off planetary gear automatic gearbox.
Background
An automatic transmission generally includes friction engagement elements such as planetary gear units, clutches, and brakes. The automatic transmission performs energy conversion and power transmission through automatic transmission oil, realizes automatic speed change by utilizing parts such as an oil pump, an oil circuit, a clutch, a planetary gear set, a plurality of electromagnetic valves and the like, and brings easy and simple driving feeling for automobile driving of people.
The existing automatic transmission mainly comprises a Ravigneaux type planetary gear structure or a Simpson gear structure, and is a 4-speed transmission. The characteristics of the planetary gear structure of lavina: the planet carrier is of a double-row structure, and a gear ring and a planet carrier are shared by front and rear rows; on the planet carrier, the outer planet wheel is a long planet wheel and is meshed with the front row sun wheel, and the inner planet wheel is a short planet wheel and is simultaneously meshed with the rear row small sun wheel and the long planet wheel. The Simpson planetary gear structure has the characteristics that: the gear parameters of the front and the rear planet rows are the same, the sun gears of the front and the rear planet rows are connected into a whole, namely a common sun gear, and the planet carrier of the front row is connected with the gear ring of the rear row. However, the automatic transmission composed of a single ravigneaux or simpson planetary gear cannot realize a wider transmission ratio range and more gear performance requirements, and the structure and the power transmission route of the traditional automatic transmission are complex, the number of executing elements is excessive, and interference is easy to generate.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a six keep off planetary gear automatic gearbox to the defect that prior art exists.
The utility model discloses a realize above-mentioned purpose, adopt following technical scheme: a six-speed planetary gear automatic transmission comprises a power input shaft 1 and a power output shaft 22;
A first output end of the power input shaft 1 is connected with a front row gear ring 7 of the planetary gear mechanism through a first clutch 2, a second output end of the power input shaft is connected with a front row sun gear 5 of the planetary gear mechanism through a second clutch 4, a third output end of the power input shaft is connected with a rear row gear ring 16 of the planetary gear mechanism through a third clutch 10, a fourth output end of the power input shaft is connected with a rear row planet carrier 17 of the planetary gear mechanism through a fourth clutch 11, and a fifth output end of the power input shaft is connected with a rear row sun gear 14 of the planetary gear mechanism through a fifth clutch 13; wherein,
a front row planet carrier 8 with a front row planet gear 6 is arranged between the front row sun gear 5 and the front row gear ring 7;
the rear row planet carrier 17 with the rear row planet gears 15 is arranged between the rear row sun gear 14 and the rear row gear ring 16;
a first input end of the power output shaft 22 is connected with an output end of the front row planet carrier 8 through a sixth clutch 23, a second input end of the power output shaft is connected with an output end of the third clutch 10 through a seventh clutch 21, and a third input end of the power output shaft is connected with an output end of the rear row planet carrier 17 through an eighth clutch 20.
Further, be provided with between first clutch 2 and the front gear 7 right the first stopper 3 of front gear 7 braking, be provided with between second clutch 4 and the front gear sun gear 5 right the second stopper 9 of front gear sun gear 5 braking, be provided with between third clutch 10 and the back gear ring 16 right the third stopper 12 of back gear ring 16 braking, be provided with between fifth clutch 13 and the back gear sun gear 14 right the fourth stopper 18 of back gear sun gear 14 braking, be provided with between eighth clutch 20 and the back gear planet carrier 17 right the fifth stopper 19 of back gear planet carrier 17 braking.
The utility model has the advantages that: the utility model discloses an automatic transmission comprises the double planetary gear mechanism of parameter difference, and two rows of planetary gear mechanism are relatively independent, can form 6 drive ratio rational distribution's gear district, and each keeps off the during operation by single row planetary gear mechanism transmission power, and the power transmission route is simple. The automatic transmission has the characteristics of simple and compact structure, low cost, few executing elements, less executing element change during gear shifting and difficult movement interference.
Drawings
Fig. 1 is a schematic structural diagram of the present invention.
Detailed Description
Fig. 1 shows a six-speed planetary automatic transmission, which includes a power input shaft 1 and a power output shaft 22;
a first output end of the power input shaft 1 is connected with a front row gear ring 7 of the planetary gear mechanism through a first clutch 2, a second output end of the power input shaft is connected with a front row sun gear 5 of the planetary gear mechanism through a second clutch 4, a third output end of the power input shaft is connected with a rear row gear ring 16 of the planetary gear mechanism through a third clutch 10, a fourth output end of the power input shaft is connected with a rear row planet carrier 17 of the planetary gear mechanism through a fourth clutch 11, and a fifth output end of the power input shaft is connected with a rear row sun gear 14 of the planetary gear mechanism through a fifth clutch 13; wherein,
A front row planet carrier 8 with a front row planet gear 6 is arranged between the front row sun gear 5 and the front row gear ring 7;
the rear row planet carrier 17 with the rear row planet gears 15 is arranged between the rear row sun gear 14 and the rear row gear ring 16;
a first input end of the power output shaft 22 is connected with an output end of the front row planet carrier 8 through a sixth clutch 23, a second input end of the power output shaft is connected with an output end of the third clutch 10 through a seventh clutch 21, and a third input end of the power output shaft is connected with an output end of the rear row planet carrier 17 through an eighth clutch 20.
In a further scheme, a first brake 3 for braking the front-row gear ring 7 is arranged between the first clutch 2 and the front-row gear ring 7, a second brake 9 for braking the front-row sun gear 5 is arranged between the second clutch 4 and the front-row sun gear 5, a third brake 12 for braking the rear-row gear ring 16 is arranged between the third clutch 10 and the rear-row gear ring 16, a fourth brake 18 for braking the rear-row sun gear 14 is arranged between the fifth clutch 13 and the rear-row sun gear 14, and a fifth brake 19 for braking the rear-row planet carrier 17 is arranged between the eighth clutch 20 and the rear-row planet carrier 17.
When in use, the number of the front sun gear teeth is assumed to be Z1 frontThe number of teeth of the gear ring is Z2 frontThen can let alphaFront side＝Z2 front/Z1 front(ii) a Number of rear sun gear teeth Z1 afterThe number of teeth of the gear ring is Z2 afterThen can let alphaRear end＝Z2 after/Z1 after(ii) a And alpha isRear end＞αFront side. The following is the power transmission route and gear ratio calculation for each gear.
1, gear 1: the third brake 12, the fifth clutch 13, and the eighth clutch 20 are operated. The power is input from the power input shaft 1 through the fifth clutch 13 by the rear sun gear 14, and is output through the rear planetary gears 15, the rear carrier 17, the eighth clutch 20 and the power output shaft 22. Calculating the 1-gear transmission ratio i according to the motion relation1＝1+αRear end。
And 2, gear: the first brake 3, the second clutch 4, and the sixth clutch 23 are operated. The power is input from the power input shaft 1 through the second clutch 4 by the front row sun gear 5, and is output through the front row planetary gear 6, the front row planetary carrier 8, the sixth clutch 23 and the power output shaft 22. Calculating the 2-gear transmission ratio i according to the motion relation2＝1+αFront side。
And 3, gear shifting: the first clutch 2, the second brake 9, and the sixth clutch 23 are operated. The power is transmitted from the power input shaft 1 to the front row gear ring 7 through the first clutch 2, and then is output through the front row planetary gear 6, the front row planet carrier 8, the sixth clutch 23 and the power output shaft 22. Calculating a 3-gear transmission ratio i according to the motion relation 3＝1+1/αFront side。
4, gear shifting: third clutch 10, fourth brakeThe clutch 18 and the eighth clutch 20 are operated. The power is transmitted from the power input shaft 1 to the rear row of gear rings 16 through the third clutch 10, and then is output through the rear row of planetary gears 15, the rear row of planet carriers 17, the eighth clutch 20 and the power output shaft 22. Calculating a 4-gear transmission ratio i according to the motion relation4＝1+1/αRear end。
And 5, gear shifting: the first clutch 2, the second clutch 4, and the sixth clutch 23 are operated. The power is transmitted from the power input shaft 1 to the front row gear ring 7 by the first clutch 2, transmitted to the front row sun gear 5 by the second clutch 4, and then output by the front row planetary gear 6, the front row planet carrier 8, the sixth clutch 23 and the power output shaft 22. Calculating a 5-gear transmission ratio i according to the motion relation5＝1。
6, gear 6: the fourth clutch 11, the fourth brake 18, and the seventh clutch 21 are operated. The power is transmitted to the rear row planet carrier 17 through the power input shaft 1 and the fourth clutch 11, and is output through the rear row planet gear 15, the rear row gear ring 16, the seventh clutch 21 and the power output shaft 22. Calculating a 6-gear transmission ratio i according to the motion relation6After/(1 + α ═ αRear end)
Reverse gear R gear]: the fifth clutch 13, the fifth brake 19, and the seventh clutch 21 are operated. The power is transmitted to the rear row sun gear 14 through the power input shaft 1 and the fifth clutch 13, and is output through the rear row planetary gear 15, the rear row gear ring 16, the seventh clutch 21 and the power output shaft 22. Calculating the reverse gear transmission ratio i according to the motion relation R＝-αRear end。
The above description is only for the preferred embodiment of the present invention, and is not intended to limit the present invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included within the protection scope of the present invention.
Claims (2)
1. A six-gear planetary gear automatic transmission is characterized in that,
comprises a power input shaft (1) and a power output shaft (22);
the first output end of the power input shaft (1) is connected with a front row gear ring (7) of the planetary gear mechanism through a first clutch (2), the second output end of the power input shaft is connected with a front row sun gear (5) of the planetary gear mechanism through a second clutch (4), the third output end of the power input shaft is connected with a rear row gear ring (16) of the planetary gear mechanism through a third clutch (10), the fourth output end of the power input shaft is connected with a rear row planet carrier (17) of the planetary gear mechanism through a fourth clutch (11), and the fifth output end of the power input shaft is connected with a rear row sun gear (14) of the planetary gear mechanism through a fifth clutch (13); wherein,
a front row planet carrier (8) with a front row planet gear (6) is arranged between the front row sun gear (5) and the front row gear ring (7);
the rear row planet carrier (17) with a rear row planet gear (15) is arranged between the rear row sun gear (14) and the rear row gear ring (16);
the first input end of the power output shaft (22) is connected with the output end of the front row planet carrier (8) through a sixth clutch (23), the second input end of the power output shaft is connected with the output end of the third clutch (10) through a seventh clutch (21), and the third input end of the power output shaft is connected with the output end of the rear row planet carrier (17) through an eighth clutch (20).
2. A six speed planetary automatic transmission as in claim 1, a first brake (3) for braking the front-row gear ring (7) is arranged between the first clutch (2) and the front-row gear ring (7), a second brake (9) for braking the front-row sun gear (5) is arranged between the second clutch (4) and the front-row sun gear (5), a third brake (12) for braking the back row gear ring (16) is arranged between the third clutch (10) and the back row gear ring (16), a fourth brake (18) for braking the rear-row sun gear (14) is arranged between the fifth clutch (13) and the rear-row sun gear (14), and a fifth brake (19) for braking the rear row planet carrier (17) is arranged between the eighth clutch (20) and the rear row planet carrier (17).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620069520.2U CN205298429U (en) | 2016-01-19 | 2016-01-19 | Six keep off planetary gear automatic gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620069520.2U CN205298429U (en) | 2016-01-19 | 2016-01-19 | Six keep off planetary gear automatic gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205298429U true CN205298429U (en) | 2016-06-08 |
Family
ID=56427190
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620069520.2U Withdrawn - After Issue CN205298429U (en) | 2016-01-19 | 2016-01-19 | Six keep off planetary gear automatic gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205298429U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105546058A (en) * | 2016-01-19 | 2016-05-04 | 无锡商业职业技术学院 | Six-gear planetary gear automatic transmission |
-
2016
- 2016-01-19 CN CN201620069520.2U patent/CN205298429U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105546058A (en) * | 2016-01-19 | 2016-05-04 | 无锡商业职业技术学院 | Six-gear planetary gear automatic transmission |
| CN105546058B (en) * | 2016-01-19 | 2017-10-31 | 无锡商业职业技术学院 | One kind six keeps off planetary gear automatic transmission |
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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: 20160608 Effective date of abandoning: 20171031 |
|
| AV01 | Patent right actively abandoned |
Granted publication date: 20160608 Effective date of abandoning: 20171031 |
|
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |