CN104033546A - Eleven-gear transmission - Google Patents
Eleven-gear transmission Download PDFInfo
- Publication number
- CN104033546A CN104033546A CN201410256053.XA CN201410256053A CN104033546A CN 104033546 A CN104033546 A CN 104033546A CN 201410256053 A CN201410256053 A CN 201410256053A CN 104033546 A CN104033546 A CN 104033546A
- Authority
- CN
- China
- Prior art keywords
- connector element
- gear
- clutch
- sun gear
- planet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0073—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eleven forward speeds
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention relates to an eleven-gear transmission. The transmission comprises an input component, an output component, four planetary gear rows, four clutches, two brakes and four connecting components. Each planetary gear row comprises a sun gear, a planet carrier and a gear ring. Eleven forward gears and one reverse gear can be realized by using the planetary gear row connection type of the transmission and combining the component layout form, the total transmission ratio is 8.35, the K values of the four planetary gear rows are all within the range of 1.62-3.39, and each planetary gear row is a single planetary gear planetary gear row.
Description
Technical field
The invention belongs to vehicle (automobile, special vehicle, engineering machinery) drive technology field, be specifically related to a kind of 11 shift transmissions.
Background technique
For improving the performance (power performance, fuel economy, gearshift performance) of vehicle, the above development of car gear number forward six gear more than dumping car also requires six gears, will be found gear more, simultaneously planet row and binding member transmission scheme still less for this reason.
Summary of the invention
The object of the present invention is to provide 11 gear planetary automatic transmissions for a kind of vehicle, use less planet row and binding member to make speed changer realize more gear.
The invention provides a kind of speed changer, comprise planet row, input link 23, output link (24), connector element, clutch and break.Described planet row has four and for single planetary bevel gear planet row, the first planet row 25 comprises the first gear ring 1, the first planet carrier 2, the first sun gear 3, the second planet row 26 comprises the second gear ring 4, the second planet carrier 5, the second sun gear 6, third planet row 27 comprises the 3rd gear ring 7, third planet frame 8, the 3rd sun gear 9, and fourth planet row 28 comprises the 4th gear ring 10, fourth planet frame 11, the 4th sun gear 12; Described connector element has four to be respectively the first connector element 19, the second connector element 20, the 3rd connector element 21, the 4th connector element 22; Described clutch has four, is respectively first clutch 13, second clutch 14, the 3rd clutch 15, four clutches 16; Described break has two to be respectively the first break 17, second brake 18;
Described the first connector element 19, it interconnects described the second sun gear 6 regularly with described the 3rd sun gear 9;
Described the second connector element 20, it interconnects described the second planet carrier 5 regularly with described the 4th sun gear 12;
Described the 3rd connector element 21, it interconnects described the second gear ring 4 regularly with described third planet frame 8;
Described the 4th connector element 22, it interconnects described the 3rd gear ring 7 regularly with described fourth planet frame 11;
The combination selectively of described first clutch 13, to interconnect described the first planet carrier 2 with described the first connector element 19;
The combination selectively of described second clutch 14, to interconnect described the first planet carrier 2 with described the 3rd connector element 21;
Described the 3rd clutch 15 combination selectively, to interconnect described the first sun gear 3 with described the 3rd connector element 21;
The combination selectively of described four clutches 16, to interconnect described the first sun gear 3 with described the 4th gear ring 10;
Described the first break 17 combination selectively, to interconnect described the first connector element 19 with described fixed component.
The combination selectively of described second brake 18, to interconnect described the second connector element 20 with described fixed component;
Described input link 23 interconnects with described the first sun gear 3 regularly, and described output link 24 interconnects with described the 4th connector element 22 regularly, and described fixed component interconnects with described the first gear ring 1 regularly.
In the present invention, described planet row is single planetary bevel gear planet row.
In the present invention, described fixed component is case of transmission.
The present invention uses four single planetary bevel gear planet rows, and six binding members comprise four clutches and two breaks, in conjunction with wherein two, realizes 11 forward gears and one and reverses gear.Between gear, speed ratio interval, between 1.06 to 1.46, meets the Speed Ratio Distribution requirement of vehicle, and simple in structure, and idle running element is few, and between gear, possibility of transformation is large mutually.
Brief description of the drawings
fig. 1 is layout and the connection diagram of the each member of 11 shift transmission of the present invention.
fig. 2 is the transition diagram between the gear of interval.
Number in the figure: 1 is the first gear ring, 2 is the first planet carrier, 3 is the first sun gear, 4 is the second gear ring, 5 is the second planet carrier, 6 is the second sun gear, 7 is the 3rd gear ring, 8 is third planet frame, 9 is the 3rd sun gear, 10 is the 4th gear ring, 11 is fourth planet frame, 12 is the 4th sun gear, 13 is first clutch, 14 is second clutch, 15 is the 3rd clutch, 16 is four clutches, 17 is the first break, 18 is second brake, 19 is the first connector element, 20 is the second connector element, 21 is the 3rd connector element, 22 is the 4th connector element, 23 is input link, 24 is output link, 25 is the first planet row, 26 is the second planet row, 27 is third planet row, 28 is fourth planet row.
Embodiment
Below in conjunction with the drawings and specific embodiments, the present invention will be further described.
Embodiment 1:
1. member connects and binding member
Member between planet row connects:
Referring to Fig. 1: the first planet row 25 comprises the first sun gear 3, the first planet carrier 2, the first gear ring 1; The first sun gear 3 is connected with four clutches 16 with input link 23, the 3rd clutch 15; The first planet carrier 2 is connected with first clutch 13 and second clutch 14; The first gear ring 1 is connected with fixed component.
The second planet row 26 comprises the second sun gear 6, the second planet carrier 5, the second gear ring 4; The second sun gear 6 is connected with first clutch 13, the first break 17 and the first connector element 19; The second planet carrier 5 is connected with the second connector element 20 and second brake 18; The second gear ring 4 is connected with the 3rd connector element 21.
Third planet row 27 comprises the 3rd sun gear 9, third planet frame 8, the 3rd gear ring 7; The 3rd sun gear 9 is connected with the first connector element 19; Third planet frame 8 is connected with the 3rd connector element 21, second clutch 14 and the 3rd clutch 15; The 3rd gear ring 7 is connected with the 4th connector element 22.
Fourth planet row 28 comprises the 4th sun gear 12, fourth planet frame 11, the 4th gear ring 10; The 4th sun gear 12 is connected with the second connector element 20 and second brake 18; Fourth planet frame 11 is connected with output link 24 and the 4th connector element 22; The 4th gear ring 10 is connected with four clutches 16.
The layout of binding member:
First clutch 13 couples together the first planet carrier 2 and the first connector element 19.Second clutch 14 couples together the first planet carrier 2 and the 3rd connector element 21.The 3rd clutch 15 couples together the first sun gear 3 and the 3rd connector element 21.Four clutches 16 couples together the first sun gear 3 and the 4th gear ring 10.The first break 17 couples together the first connector element 19 with housing.Second brake 18 couples together the second connector element 20 with housing.
2. the implementation method of each gear
Referring to Fig. 1 and table 1, with the routine explanation of being operating as of 11 shift transmissions, ten shift transmission gear implementation methods in table 2 and 11 gears are similar.
By in conjunction with two in six binding members, can obtain 11 forward gears and 1 gear that falls back including 3 overgears.Table 1 is the bonding state table that represents the binding member while being shown in each gear.In table, "●" representative shows that binding member is in bonding state.In table, also has the speed ratio interval between speed ratio and two adjacent gears of each gear.But it is noted that these numerals are exemplary, and can in very big scope, adjust these numerical value.Described speed ratio refers to the ratio of input speed and output speed, and planet row K value refers to the ratio of the gear ring number of teeth with the sun gear number of teeth of planet row.
Table 1 11 shift transmission speed ratios, speed ratio interval and binding member bonding state table
k1=3.39;k2=1.95;k3=3.27;k4=1.62;i=8.35
When first clutch 13 and second brake 18 in conjunction with time, the first planet carrier 2 and the first connector element 19 rotate jointly, the second connector element 20 is braked, realization is reversed gear.
When first clutch 13 and second clutch 14 in conjunction with time, the first planet carrier 2 and the first connector element 19 rotate jointly, the first planet carrier 2 and the 3rd connector element 21 rotate jointly, realize the first gear.
When second clutch 14 and the first break 17 in conjunction with time, the first planet carrier 2 and the 3rd connector element 21 rotate jointly, the first connector element 19 is braked, and realizes the second gear.
When second clutch 14 and second brake 18 in conjunction with time, the first planet carrier 2 and the 3rd connector element 21 rotate jointly, the second connector element 20 is braked, and realizes the 3rd gear.
When second clutch 14 and four clutches 16 in conjunction with time, the first planet carrier 2 and the 3rd connector element 21 rotate jointly, the first sun gear 3 and the 4th gear ring 10 rotate jointly, realize the 4th gear.
When four clutches 16 and second brake 18 in conjunction with time, the first sun gear 3 and the 4th gear ring 10 rotate jointly, the second connector element 20 is braked, and realizes the 5th gear.
When four clutches 16 and the first break 17 in conjunction with time, the first sun gear 3 and the 4th gear ring 10 rotate jointly, the first connector element 19 is braked, and realizes the 6th gear.
When first clutch 13 and four clutches 16 in conjunction with time, the first planet carrier 2 and the first connector element 19 rotate jointly, the first sun gear 3 and the 4th gear ring 10 rotate jointly, realize the 7th gear.
When the 3rd clutch 15 and four clutches 16 in conjunction with time, the first sun gear 3 and the 3rd connector element 21 and the 4th gear ring 10 rotate jointly, realize the 8th gear.
When first clutch 13 and the 3rd clutch 15 in conjunction with time, the first planet carrier 2 and the first connector element 19 rotate jointly, the first sun gear 3 and the 3rd connector element 21 rotate jointly, realize the 9th gear.
When the 3rd clutch 15 and the first break 17 in conjunction with time, the first sun gear 3 and the 3rd connector element 21 rotate jointly, the first connector element 19 is braked, and realizes the tenth gear.
When the 3rd clutch 15 and second brake 18 in conjunction with time, the first sun gear 3 and the 3rd connector element 21 rotate jointly, the second connector element 20 is braked, and realizes the 11 gear.
3. lower than the 11 speed changer schemes of keeping off
Referring to Fig. 2, also convertible between non-conterminous gear.For example first keep off the 3rd gear of can directly shifting gears, meet oneshift simultaneously and require (only changing the bonding state of two binding members).Can realize the jump between gear under certain condition, skip some unwanted gears, therefore the present invention also can be used as the following speed changer use of 11 gear.Be that 11 shift transmissions are removed the ten shift transmission schemes that obtain after a gear referring to table 2.
Table 20 shift transmission speed ratios, speed ratio interval and binding member bonding state table
k1=3.39;k2=1.95;k3=3.27;k4=1.62;i=8.35
In the present embodiment, k1=3.39; K2=1.95; K3=3.27; K4=1.62; Resultant gear ratio scope is 8.35.But description of the invention is only exemplary in nature, can significantly change each gear speed ratio and speed ratio interval by adjusting K value value, thereby do not depart from distortion and the improvement that the present invention will put under prerequisite will be in scope of the present invention.
Claims (4)
1. a shift transmission, comprise planet row, input link (23), output link (24), connector element, clutch and break, it is characterized in that: described planet row has four, and be single planetary bevel gear planet row, the first planet row (25) comprises the first gear ring (1), the first planet carrier (2), the first sun gear (3), the second planet row (26) comprises the second gear ring (4), the second planet carrier (5), the second sun gear (6), third planet row (27) comprises the 3rd gear ring (7), third planet frame (8), the 3rd sun gear (9), fourth planet row (28) comprises the 4th gear ring (10), fourth planet frame (11), the 4th sun gear (12), described connector element has four, is respectively the first connector element (19), the second connector element (20), the 3rd connector element (21) and the 4th connector element (22), described clutch has four, is respectively first clutch (13), second clutch (14), the 3rd clutch (15) and four clutches (16), described break has two, is respectively the first break (17) and second brake (18),
Described the first connector element (19) interconnects described the second sun gear (6) and described the 3rd sun gear (9) regularly;
Described the second connector element (20) interconnects described the second planet carrier (5) and described the 4th sun gear (12) regularly;
Described the 3rd connector element (21) interconnects described the second gear ring (4) and described third planet frame (8) regularly;
Described the 4th connector element (22) interconnects described the 3rd gear ring (7) and described fourth planet frame (11) regularly;
Described first clutch (13) interconnects described the first planet carrier (2) and described the first connector element (19);
Described second clutch (14) interconnects described the first planet carrier (2) and described the 3rd connector element (21);
Described the 3rd clutch (15) interconnects described the first sun gear (3) and described the 3rd connector element (21);
Described four clutches (16) interconnects described the first sun gear (3) and described the 4th gear ring (10);
Described the first break (17) interconnects described the first connector element (19) and fixed component;
Described second brake (18) interconnects described the second connector element (20) and fixed component.
2. speed changer according to claim 1, it is characterized in that, described input link (23) interconnects regularly with described the first sun gear (3), described output link (24) interconnects regularly with described the 4th connector element (22), the interconnection that described fixed component and described the first gear ring (1) are fixing.
3. speed changer according to claim 1, is characterized in that, described fixed component is case of transmission.
4. speed changer according to claim 1, is characterized in that, speed changer is set up at least ten forward speed ratios and the speed ratio that reverses gear, and is specially:
When first clutch (13) and second brake (18) in conjunction with time, the first planet carrier (2) and the first connector element (19) rotate jointly, the second connector element (20) braking, realization is reversed gear;
When first clutch (13) and second clutch (14) in conjunction with time, the first planet carrier (2) and the first connector element (19) rotate jointly, the first planet carrier (2) and the 3rd connector element (21) rotate jointly, realize the first gear;
When second clutch (14) and the first break (17) in conjunction with time, the first planet carrier (2) and the 3rd connector element (21) rotate jointly, the first connector element (19) braking, realizes the second gear;
When second clutch (14) and second brake (18) in conjunction with time, the first planet carrier (2) and the 3rd connector element (21) rotate jointly, the second connector element (20) braking, realizes the 3rd gear;
When second clutch (14) and four clutches (16) in conjunction with time, the first planet carrier (2) and the 3rd connector element (21) rotate jointly, the first sun gear (3) and the 4th gear ring (10) rotate jointly, realize the 4th gear;
When four clutches (16) and second brake (18) in conjunction with time, the first sun gear (3) and the 4th gear ring (10) rotate jointly, the second connector element (20) braking, realizes the 5th gear;
When four clutches (16) and the first break (17) in conjunction with time, the first sun gear (3) and the 4th gear ring (10) rotate jointly, the first connector element (19) braking, realizes the 6th gear;
When first clutch (13) and four clutches (16) in conjunction with time, the first planet carrier (2) and the first connector element (19) rotate jointly, the first sun gear (3) and the 4th gear ring (10) rotate jointly, realize the 7th gear;
When the 3rd clutch (15) and four clutches (16) in conjunction with time, the first sun gear (3) and the 3rd connector element (21) and the 4th gear ring (10) rotate jointly, realize the 8th gear;
When first clutch (13) and the 3rd clutch (15) in conjunction with time, the first planet carrier (2) and the first connector element (19) rotate jointly, the first sun gear (3) and the 3rd connector element (21) rotate jointly, realize the 9th gear;
When the 3rd clutch (15) and the first break (17) in conjunction with time, the first sun gear (3) and the 3rd connector element (21) rotate jointly, the first connector element (19) braking, realizes the tenth gear;
When the 3rd clutch (15) and second brake (18) in conjunction with time, the first sun gear (3) and the 3rd connector element (21) rotate jointly, the second connector element (20) braking, realizes the 11 gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410256053.XA CN104033546B (en) | 2014-06-11 | 2014-06-11 | 11 shift transmissions |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410256053.XA CN104033546B (en) | 2014-06-11 | 2014-06-11 | 11 shift transmissions |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104033546A true CN104033546A (en) | 2014-09-10 |
| CN104033546B CN104033546B (en) | 2016-04-20 |
Family
ID=51464460
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410256053.XA Expired - Fee Related CN104033546B (en) | 2014-06-11 | 2014-06-11 | 11 shift transmissions |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104033546B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105697673A (en) * | 2014-12-10 | 2016-06-22 | 现代自动车株式会社 | Multi-stage transmission for vehicle |
| CN106641135A (en) * | 2016-12-16 | 2017-05-10 | 贵州凯星液力传动机械有限公司 | Twelve-gear automatic transmission |
| CN107289079A (en) * | 2016-03-30 | 2017-10-24 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| GB2585082A (en) * | 2019-06-28 | 2020-12-30 | Involution Tech Limited | Drive unit for electric vehicle |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4420992A (en) * | 1981-07-07 | 1983-12-20 | Caterpillar Tractor Co. | Planetary transmission |
| US20120172172A1 (en) * | 2009-08-20 | 2012-07-05 | Zf Friedrichshafen Ag | Multi-ratio transmission |
| CN103032532A (en) * | 2011-10-03 | 2013-04-10 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
| US20130203546A1 (en) * | 2012-02-06 | 2013-08-08 | GM Global Technology Operations LLC | Multi-speed transmission |
-
2014
- 2014-06-11 CN CN201410256053.XA patent/CN104033546B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4420992A (en) * | 1981-07-07 | 1983-12-20 | Caterpillar Tractor Co. | Planetary transmission |
| US20120172172A1 (en) * | 2009-08-20 | 2012-07-05 | Zf Friedrichshafen Ag | Multi-ratio transmission |
| CN103032532A (en) * | 2011-10-03 | 2013-04-10 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
| US20130203546A1 (en) * | 2012-02-06 | 2013-08-08 | GM Global Technology Operations LLC | Multi-speed transmission |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105697673A (en) * | 2014-12-10 | 2016-06-22 | 现代自动车株式会社 | Multi-stage transmission for vehicle |
| CN107289079A (en) * | 2016-03-30 | 2017-10-24 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN106641135A (en) * | 2016-12-16 | 2017-05-10 | 贵州凯星液力传动机械有限公司 | Twelve-gear automatic transmission |
| CN106641135B (en) * | 2016-12-16 | 2019-05-14 | 贵州凯星液力传动机械有限公司 | A kind of 12 speed automatic transmissions |
| GB2585082A (en) * | 2019-06-28 | 2020-12-30 | Involution Tech Limited | Drive unit for electric vehicle |
| GB2585082B (en) * | 2019-06-28 | 2023-09-20 | Involution Tech Limited | Drive unit for electric vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104033546B (en) | 2016-04-20 |
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