CN104633024A - Six-speed automatic gearbox transmission mechanism for optimizing transmission ratio - Google Patents
Six-speed automatic gearbox transmission mechanism for optimizing transmission ratio Download PDFInfo
- Publication number
- CN104633024A CN104633024A CN201410826425.8A CN201410826425A CN104633024A CN 104633024 A CN104633024 A CN 104633024A CN 201410826425 A CN201410826425 A CN 201410826425A CN 104633024 A CN104633024 A CN 104633024A
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- China
- Prior art keywords
- planetary gear
- gear set
- friction clutch
- interconnects
- row planetary
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 29
- 230000007246 mechanism Effects 0.000 title claims abstract description 8
- 230000000712 assembly Effects 0.000 abstract description 2
- 238000000429 assembly Methods 0.000 abstract description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 230000004043 responsiveness Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Disclosed is a six-speed automatic gearbox transmission mechanism for optimizing a transmission ratio. The six-speed automatic gearbox transmission mechanism comprises an input device, an output device, three planetary gear assemblies, three connecting components, three brakes and three friction clutches, and all the components are arranged in a gearbox shell. According to the six-speed automatic gearbox transmission mechanism, six advancing speed ratios or transmission ratios and reverse gears can be achieved, the structure is compact, the size is small, mounting space is saved, the transmission ratio drive power achieves 0.8632, the efficiency of a gearbox is excellent, and the minimum efficiency value achieves 0.955.
Description
Technical field the invention belongs to system of vehicle transmission technical field, particularly a kind of automatic transmission.
Background technique automatic transmission is one of main parts in automotive transmission, by changing velocity ratio, change the torque of engine crankshaft, meet and starting to walk, accelerate, travel and overcoming under the different driving conditions such as different kinds of roads obstruction the demand driving net tractive force of wheel and speed of a motor vehicle difference to require.Although existing speed changer achieves its expection object, along with the development of automotive industry, the performance of new speed changer to aspects such as efficiency, responsiveness and smoothnesss is had higher requirement, and is badly in need of the size and the weight that reduce conventional transmissions.
Summary of the invention the object of the present invention is to provide 6 gear transmission driving mechanisms of the optimization velocity ratio that a kind of compact structure, volume are little, efficiency is high.
The present invention includes input shaft, output shaft, planetary gear set, connector element, friction brake and friction clutch, above-mentioned component is all located in case of transmission.Described input shaft and the first friction clutch, the second friction clutch, the 3rd friction clutch interconnect, the gear ring of described first friction clutch and first row planetary gear set interconnects, the planet carrier of described second friction clutch and first row planetary gear set interconnects, and described 3rd friction clutch connects and interconnects with the sun gear of first row planetary gear set and the second interconnecting component.The planet carrier of output shaft and the 3rd rows of planetary gear train interconnects, and is driven by this output shaft.The gear ring of the planet carrier of first row planetary gear set and second row star gear assembly interconnects by the first interconnecting component, the sun gear of the sun gear of first row planetary gear set and second row planetary gear set interconnects by the second interconnecting component, the planet carrier of the planet carrier of second row planetary gear set and the 3rd rows of planetary gear assembly interconnects by the 3rd interconnecting component, and the sun gear of the sun gear of second row planetary gear set and the 3rd rows of planetary gear assembly interconnects by the 4th interconnecting component.
The gear ring of first row planetary gear set is fixedly connected with case of transmission by the first break, the gear ring of second row planetary gear set is fixedly connected with case of transmission with the first interconnecting component by second brake, and the gear ring of the 3rd rows of planetary gear assembly is fixedly connected with case of transmission by the 3rd break.
The gear ring of input shaft and first row planetary gear set interconnects by the first friction clutch, the planet carrier of input shaft and first row planetary gear set interconnects by the second friction clutch, and the sun gear of input shaft and first row planetary gear set and the second interconnecting component interconnect by the 3rd friction clutch.
The present invention compared with prior art tool has the following advantages:
1, velocity ratio is through optimizing, and makes driving power limit performance rate reach 0.8362, and velocity ratio distributes rationally, gear step ratio remain on 1-2 more among a small circle in;
2, compact structure, volume is little, and contrast and its volume of patent CN102797809A reduce 1/3 substantially, save installing space;
3, the good efficiency of speed changer, minimum efficiency value reaches 0.955.
Accompanying drawing explanation
Fig. 1 is that each component of the present invention is arranged and connection diagram.
In figure: 1-input shaft, 2-first interconnecting component, 3-second interconnecting component, 4-the 3rd interconnecting component, 5-the 4th interconnecting component, 6-first clutch, 7-second clutch, 8-the 3rd clutch, 9-first break, 10-second brake, 11-the 3rd break, 12-output shaft, 13-case of transmission, 14-first row gear ring, 15-first row planet wheel, 16-first row planet carrier, 17-first row sun gear, 18-second row gear ring, 19-second row planet wheel, 20-second row planet carrier, 21-secondary sun gear, 22-the 3rd toothrow circle, 23-the 3rd ranks star-wheel, 24-the 3rd ranks carrier, 25-the 3rd arranges sun gear.
Embodiment
In the schematic diagram of 6 gear transmission driving mechanisms of the optimization velocity ratio shown in Fig. 1, input shaft 1 and the first friction clutch 6, second friction clutch 7, the 3rd friction clutch 8 interconnect, the gear ring 14 of described first friction clutch and first row planetary gear set interconnects, the planet carrier 16 of described second friction clutch and first row planetary gear set interconnects, and described 3rd friction clutch connects and interconnects with the sun gear 17 of first row planetary gear set and the second interconnecting component 3.The planet carrier 24 of output shaft 12 and the 3rd rows of planetary gear train interconnects, and is driven by output shaft.The gear ring 18 of the planet carrier of first row planetary gear set and second row star gear assembly interconnects by the first interconnecting component 2, the sun gear 17 of first row planetary gear set interconnects with the sun gear 21 of second row planetary gear set by the second interconnecting component, the planet carrier of the planet carrier 20 of second row planetary gear set and the 3rd rows of planetary gear assembly interconnects by the 3rd interconnecting component 4, and the sun gear 25 of the sun gear of second row planetary gear set and the 3rd rows of planetary gear assembly interconnects by the 4th interconnecting component 5.
The gear ring of first row planetary gear set is fixedly connected with case of transmission 13 by the first break 9, the gear ring of second row planetary gear set is fixedly connected with case of transmission with the first interconnecting component by second brake 10, and the gear ring 22 of 11 the 3rd rows of planetary gear assemblies is fixedly connected with case of transmission by the 3rd break.
The gear ring of input shaft and first row planetary gear set interconnects by the first friction clutch, the planet carrier of input shaft and first row planetary gear set interconnects by the second friction clutch, the 3rd friction clutch by the sun gear of input shaft and first row planetary gear set and the second interconnecting component interconnect.
The planet wheel 15 of first row passes through revolute pair device on the planet carrier of first row planetary set, the planet wheel 19 of second row is by revolute pair device on the planet carrier of second row planetary set, and the planet wheel 23 of the 3rd row passes through revolute pair device on the planet carrier of the 3rd rows of planetary group.
As shown in table 1, in reversing situation, to enable or in conjunction with the first friction clutch 6 and second brake 10.
In first gear, the 3rd friction clutch 8 and second brake 10 are activated or engage.
By stopping using or being separated second brake 10 and enabling or engage the 3rd friction brake 11, maintain the 3rd friction clutch 8 simultaneously and enable or engage to realize two gears.
By stopping using or being separated the 3rd friction brake 11 and enabling or engage the first friction brake 9, maintain the 3rd friction clutch 8 simultaneously and enable or engage to realize three gears.
By stopping using or being separated the first break 9 and enabling or engage the second friction clutch 7, maintain the 3rd friction clutch 8 simultaneously and enable or engage to realize four gears.
By stopping using or being separated the 3rd friction clutch 8 and enabling or engage the first break 9, maintain the second friction clutch 10 simultaneously and enable or engage to realize five gears.
By stopping using or being separated the first break 9 and enabling or engage the 3rd break 11, maintain the second friction clutch 7 simultaneously and enable or engage to realize six gears.
Table 1: each gear of the invention process and binding member meshing relation table.
Claims (1)
1. optimize 6 gear transmission driving mechanisms of velocity ratio for one kind, it comprises input shaft, output shaft, planetary gear set, connector element, friction brake and friction clutch, above-mentioned component is all located in case of transmission, it is characterized in that: described input shaft and the first friction clutch, second friction clutch, 3rd friction clutch interconnection, the gear ring of described first friction clutch and first row planetary gear set interconnects, the planet carrier of described second friction clutch and first row planetary gear set interconnects, described 3rd friction clutch connects and interconnects with the sun gear of first row planetary gear set and the second interconnecting component, the planet carrier of output shaft and the 3rd rows of planetary gear train interconnects, and is driven by this output shaft, the gear ring of the planet carrier of first row planetary gear set and second row planetary gear set interconnects by the first interconnecting component, the sun gear of the sun gear of first row planetary gear set and second row planetary gear set interconnects by the second interconnecting component, the planet carrier of the planet carrier of second row planetary gear set and the 3rd rows of planetary gear assembly interconnects by the 3rd interconnecting component, and the sun gear of the sun gear of second row planetary gear set and the 3rd rows of planetary gear assembly interconnects by the 4th interconnecting component,
The gear ring of first row planetary gear set is fixedly connected with case of transmission by the first break, the gear ring of second row planetary gear set is fixedly connected with case of transmission with the first interconnecting component by second brake, and the gear ring of the 3rd rows of planetary gear assembly is fixedly connected with case of transmission by the 3rd break;
The gear ring of input shaft and first row planetary gear set interconnects by the first friction clutch, the planet carrier of input shaft and first row planetary gear set interconnects by the second friction clutch, and the sun gear of input shaft and first row planetary gear set and the second interconnecting component interconnect by the 3rd friction clutch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410826425.8A CN104633024B (en) | 2014-12-26 | 2014-12-26 | Six-speed automatic gearbox transmission mechanism for optimizing transmission ratio |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410826425.8A CN104633024B (en) | 2014-12-26 | 2014-12-26 | Six-speed automatic gearbox transmission mechanism for optimizing transmission ratio |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104633024A true CN104633024A (en) | 2015-05-20 |
| CN104633024B CN104633024B (en) | 2017-02-01 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410826425.8A Expired - Fee Related CN104633024B (en) | 2014-12-26 | 2014-12-26 | Six-speed automatic gearbox transmission mechanism for optimizing transmission ratio |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104633024B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043260A (en) * | 2020-01-03 | 2020-04-21 | 中国地质大学（武汉） | Six-gear transmission |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4070927A (en) * | 1976-06-04 | 1978-01-31 | General Motors Corporation | Planetary gearing arrangement for a transmission |
| DE10162878A1 (en) * | 2001-12-20 | 2003-07-24 | Zahnradfabrik Friedrichshafen | Multi-step automatic planetary reduction gearbox for a motor vehicle has drive and driven shafts, single-link planet sets, rotary shafts and gearshift devices. |
| US7238141B2 (en) * | 2005-09-07 | 2007-07-03 | Hyundai Motor Company | Seven-speed powertrain of an automatic transmission for a vehicle |
| TW201038420A (en) * | 2009-04-24 | 2010-11-01 | Univ Nat Sun Yat Sen | Six-speed automobile automatic transmission |
| WO2014154417A1 (en) * | 2013-03-27 | 2014-10-02 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
-
2014
- 2014-12-26 CN CN201410826425.8A patent/CN104633024B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4070927A (en) * | 1976-06-04 | 1978-01-31 | General Motors Corporation | Planetary gearing arrangement for a transmission |
| DE10162878A1 (en) * | 2001-12-20 | 2003-07-24 | Zahnradfabrik Friedrichshafen | Multi-step automatic planetary reduction gearbox for a motor vehicle has drive and driven shafts, single-link planet sets, rotary shafts and gearshift devices. |
| US7238141B2 (en) * | 2005-09-07 | 2007-07-03 | Hyundai Motor Company | Seven-speed powertrain of an automatic transmission for a vehicle |
| TW201038420A (en) * | 2009-04-24 | 2010-11-01 | Univ Nat Sun Yat Sen | Six-speed automobile automatic transmission |
| WO2014154417A1 (en) * | 2013-03-27 | 2014-10-02 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043260A (en) * | 2020-01-03 | 2020-04-21 | 中国地质大学（武汉） | Six-gear transmission |
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| Publication number | Publication date |
|---|---|
| CN104633024B (en) | 2017-02-01 |
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Granted publication date: 20170201 |
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