CN102817974B - Eight-gear planetary automatic speed changer - Google Patents
Eight-gear planetary automatic speed changer Download PDFInfo
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- CN102817974B CN102817974B CN201210304352.7A CN201210304352A CN102817974B CN 102817974 B CN102817974 B CN 102817974B CN 201210304352 A CN201210304352 A CN 201210304352A CN 102817974 B CN102817974 B CN 102817974B
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- 230000007246 mechanism Effects 0.000 claims abstract description 96
- 230000005540 biological transmission Effects 0.000 claims abstract description 82
- 244000309464 bull Species 0.000 claims description 26
- 230000008901 benefit Effects 0.000 abstract description 3
- 239000000446 fuel Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 239000002243 precursor Substances 0.000 description 1
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Abstract
The invention belongs to the technical field of power transmission and relates to a speed changer, in particular to an eight-gear planetary automatic speed changer, which comprises an input shaft, a k1 planetary row, a Ravigneaux planetary mechanism, a gear shifting operation element and a speed changer support frame, wherein the k1 planetary row consists of a k1 planetary row planetary frame, a k1 planetary row gear ring and a k1 planetary row sun wheel, the Ravigneaux planetary mechanism consists of a Ravigneaux mechanism planetary frame input shaft, a planetary mechanism planetary frame, a long planetary wheel, a large gear ring, a large sun wheel, a short planetary wheel, a small gear ring, a small planetary wheel and a sun wheel input shaft, and the gear shifting operation element comprises a clutch a, a clutch b, a clutch c, a brake a, a brake b and a brake c. Compared with a four-gear automatic speed changer of the Ravigneaux planetary mechanism, the eight-gear planetary automatic speed changer has the advantages that only one simple planetary mechanism and one brake are added, the doubling of the gear number is realized, the Ravigneaux planetary mechanism can utilize the existing technological base, and the economy is good.
Description
Technical field
The invention belongs to technical field of power transmission, relate to a kind of speed changer, particularly a kind of eight gear planetary automatic transmissions.
Background technique
What require along with power performance and fuel economy improves constantly, and vehicular automatic transmission develops to many gears, and from 4 gears to 8 ~ 9 gear development, its gear range also rises to 7 ~ 8 from about 4.Vehicular automatic transmission great majority are made up of planet speed change mechanism and the shift control such as clutch, break element, and each gear can reuse each actuating element and planetary structure, reaches the volume and weight reducing automatic transmission.
Summary of the invention
The object of the invention is to overcome the defect existed in prior art, a kind of eight gear planetary automatic transmissions of design, have structure simple, compact, all clutches and break coaxially arranged, rational in infrastructure with input shaft, join oil conveniently.
To achieve these goals, technological scheme of the present invention is a kind of eight gear planetary automatic transmissions of design, comprises input shaft, k1 planet row, La Weina planetary mechanism, shift control element and transmission support bracket;
Wherein, k1 planet row is made up of k1 planet row planet carrier, k1 planet row gear ring and k1 planet row sun gear; La Weina planetary mechanism is by La Weina mechanism planet carrier input shaft, La Weina mechanism planet carrier, long row star-wheel, bull gear, large sun gear, short planet wheel, little gear ring, small sun gear and sun gear input shaft; Shift control element comprises clutch a, clutch b, clutch c, break a, break b and break c;
Its position relationship is: described clutch a, clutch b, clutch c and break a are arranged between k1 planet row and La Weina planetary mechanism;
Its annexation is: k1 planet row sun gear is connected with transmission support bracket, input shaft is connected with k1 planet row planet carrier, clutch c drive end, k1 planet row gear ring is connected with the drive end of clutch a, clutch b, clutch a Partner is connected with large sun gear, break c by sun gear input shaft, the Partner of clutch b is connected with small sun gear, the Partner of clutch c is connected with break a by La Weina mechanism planet carrier input shaft, and little gear ring is meshed with short planet wheel and little gear ring is connected with break b.
Advantage of the present invention and beneficial effect are: one, utilize two planetary mechanism tectonic kinetics drive paths, and compared to 3 ~ 4 planetary mechanisms of other eight gears planetary automatic speed-changing schemes, structure is simple, compact.Two, all clutches and break and input shaft coaxially arranged, rational in infrastructure, it is convenient to join oil.Three, six actuating elements and two planetary mechanisms form Three Degree Of Freedom planet speed-change scheme, and each gear needs joint two elements; During contiguous gear switch, only need handle an element, gearshift controls simple.Four, have five deceleration gears, three speedup gears, gear arranges rationally, and gear maximum transmission ratio of slowing down can be greater than 4.6, can improve car load power performance; Speedup gear velocity ratio is less than 0.6, can further improve fuel economy.Five, make full use of the advantage of La Weinashi planetary mechanism compact structure, axial dimension is little, is suitable for preposition precursor vehicle and arranges.Six, compared to four speed automatic transmissions of La Weina planetary mechanism, merely add a simple planetary mechanism and a break, achieve the double of number of gear; La Weina planetary mechanism can utilize existing technical foundation, good economy performance.
Accompanying drawing explanation
Fig. 1 is transmission schematic diagram of the present invention;
Fig. 2 is the axial schematic diagram of La Weinashi planetary mechanism of the present invention;
Fig. 3 is that each operating mode operating element handles abridged table.
Wherein, 1-k1 planet row planet carrier; 2-k1 planet row gear ring; 3-clutch a; 4-clutch b; 5-clutch c; 6-La Weina mechanism planet carrier input shaft; 7-break a; 8-break b; 9-La Weina mechanism planet carrier; 10-long row star-wheel; 11-bull gear; 12-break c; The large sun gear of 13-; The short planet wheel of 14-; The little gear ring of 15-; 16-small sun gear; 17-sun gear input shaft; 18-input shaft; 19-k1 planet row sun gear; 20-transmission support bracket.
Embodiment
Be further described the specific embodiment of the present invention below in conjunction with drawings and Examples, following examples only for technological scheme of the present invention is clearly described, and can not limit the scope of the invention with this.
As shown in Figure 1 and Figure 2, the technological scheme that the present invention specifically implements is: a kind of eight gear planetary automatic transmissions, comprise input shaft 18, k1 planet row, La Weina planetary mechanism, shift control element and transmission support bracket 20;
Wherein, k1 planet row is made up of k1 planet row planet carrier 1, k1 planet row gear ring 2 and k1 planet row sun gear 19; La Weina planetary mechanism is by La Weina mechanism planet carrier input shaft 6, La Weina mechanism planet carrier 9, long row star-wheel 10, bull gear 11, large sun gear 13, short planet wheel 14, little gear ring 15, small sun gear 16 and sun gear input shaft 17; Shift control element comprises clutch a3, clutch b4, clutch c5, break a7, break b8 and break c12;
Its position relationship is: described clutch a3, clutch b4, clutch c5 and break a7 are arranged between k1 planet row and La Weina planetary mechanism;
Its annexation is: k1 planet row sun gear 19 is connected with transmission support bracket 20, input shaft 18 and k1 planet row planet carrier 1, clutch c5 drive end connects, k1 planet row gear ring 2 and clutch a3, the drive end of clutch b4 connects, clutch a3 Partner is by sun gear input shaft 17 and large sun gear 13, break c12 connects, the Partner of clutch b4 is connected with small sun gear 16, the Partner of clutch c5 is connected with break a7 by La Weina mechanism planet carrier input shaft 6, little gear ring 15 is meshed with short planet wheel 14 and little gear ring 15 is connected with break b8.
As shown in Figure 2, k2 planet row and k3 planet row form La Weina planetary mechanism, with conventional 7 component La Weina planetary mechanisms unlike, this programme adds little gear ring 15, becomes 8 component La Weina planetary mechanisms.The small sun gear 16 of 8 component La Weina planetary mechanisms is connected with clutch b4, planet carrier 9 connects clutch c5 and break a7, little gear ring 15 is connected with break b8, and large sun gear 13 is connected with break c12, clutch a3, and bull gear 11 is the pto＝power take-off of speed changer; Long row star-wheel 10 and large sun gear 13, bull gear 11, short planet wheel 14 are meshed, and short planet wheel 14 is meshed with small sun gear 16, little gear ring 15, long row star-wheel 10.The little gear ring 15 increased is meshed with short planet wheel 14, and is connected with break b8.The little gear ring 15 increased becomes 8 component 5 bar planetary structures 7 component 4 bar planetary structures, is equivalent to traditional La Weina mechanism and adds a planet row be made up of small sun gear 16, short planet wheel 14 and little gear ring 15.
Clutch a3, clutch b4 and clutch c5 are coaxial with transmission input shaft, are arranged between k1 planet row and La Weina planetary mechanism; Break a7, break b8 and break c12 are coaxial with transmission input shaft, are arranged in outside La Weina planetary mechanism.
As shown in Figure 3, in specific embodiment, ● represent this element engaging work:
One gear: power inputs from transmission input shaft 18, k1 planet row sun gear 19 is fixed with transmission support bracket 20, power slows down through k1 planet row gear ring 2 and exports, by engaging clutch b4, power is input to the small sun gear 16 of La Weina planetary mechanism, break a7 brakes the planet carrier 9 of La Weina planetary mechanism, and transmission power finally slows down from the bull gear 11 of La Weina planetary mechanism and exports.
Two gears: power inputs from transmission input shaft 18, k1 planet row sun gear 19 is fixed with transmission support bracket 20, power slows down through k1 planet row gear ring 2 and exports, by engaging clutch b4, power is input to the small sun gear 16 of La Weina planetary mechanism, break b8 brakes the little gear ring 15 of La Weina planetary mechanism, and transmission power finally slows down from the bull gear 11 of La Weina planetary mechanism and exports.
Three gears: power inputs from transmission input shaft 18, k1 planet row sun gear 19 is fixed with transmission support bracket 20, power slows down through k1 planet row gear ring 2 and exports, by engaging clutch b4, power is input to the small sun gear 16 of La Weina planetary mechanism, break c12 brakes the large sun gear 13 of La Weina planetary mechanism, and transmission power finally slows down from the bull gear 11 of La Weina planetary mechanism and exports.
Four gears: power inputs from transmission input shaft 18, k1 planet row sun gear 19 is fixed with transmission support bracket 20, power slows down through k1 planet row gear ring 2 and exports, by engaging clutch b4 and clutch a3, power is input to small sun gear 16 and the too sun gear 13 of La Weina planetary mechanism respectively, the revolution of La Weina planetary mechanism entirety, transmission power finally exports from the bull gear 11 of La Weina planetary mechanism.
Five gears: power inputs from transmission input shaft 18, k1 planet row sun gear 19 is fixed with transmission support bracket 20, and a part of power slows down through k1 planet row gear ring 2 and exports, and by engaging clutch b4, is input to the small sun gear 16 of La Weina planetary mechanism; Another part power, through transmission input shaft 18 and k1 planet row planet carrier 1, by engaging clutch c5, is input to La Weina planetary mechanism planet carrier 9; Two-way power converging in La Weina mechanism, finally slow down from bull gear 11 and export.
Six gears: power inputs from transmission input shaft 18, k1 planet row sun gear 19 is fixed with transmission support bracket 20, and a part of power slows down through k1 planet row gear ring 2 and exports, and by engaging clutch a3, is input to the large sun gear 13 of La Weina planetary mechanism; Another part power, through transmission input shaft 18 and k1 planet row planet carrier 1, by engaging clutch c5, is input to La Weina planetary mechanism planet carrier 9; Two-way power converging in La Weina mechanism, finally export from bull gear 11 speedup.
Seven gears: power inputs from transmission input shaft 18, power is through transmission input shaft 18 and k1 planet row planet carrier 1, by engaging clutch c5, be input to La Weina planetary mechanism planet carrier 9, break c12 brakes large for La Weina planetary mechanism sun gear 13, and power finally exports from bull gear 11 speedup.
Eight gears: power inputs from transmission input shaft 18, power is through transmission input shaft 18 and k1 planet row planet carrier 1, by engaging clutch c5, be input to La Weina planetary mechanism planet carrier 9, break b8 brakes little for La Weina planetary mechanism gear ring 15, and power finally exports from bull gear 11 speedup.
Reverse gear a power transmission line: power inputs from transmission input shaft 18, k1 planet row sun gear 19 is fixed with transmission support bracket 20, power slows down through k1 planet row gear ring 2 and exports, and by the clutch 3 engaged, is input to the large sun gear 13 of La Weina planetary mechanism; La Weina planetary mechanism planet carrier 9 braked by break 7, and power finally oppositely exports from bull gear 11.
Reverse gear two power transmission lines: power inputs from transmission input shaft 18, k1 planet row sun gear 19 is fixed with transmission support bracket 20, power slows down through k1 planet row gear ring 2 and exports, and by the clutch 3 engaged, is input to the large sun gear 13 of La Weina planetary mechanism; Little for La Weina planetary mechanism gear ring 15 braked by break 8, and power finally oppositely exports from bull gear 11.
When clutch 3, clutch 4 and clutch 5 do not engage, form neutral, unpowered output.
According to the planet wheel neighbor of 8 component La Weina planetary mechanisms, the parameter of La Weina planetary mechanism is optional as follows: Z
15/ Z
16=2.455, Z
15/ Z
13=2.455, Z
11/ Z
13=3, wherein Z
15for the little gear ring number of teeth, Z
16for the small sun gear number of teeth, Z
13for the large sun gear number of teeth, Z
11for the bull gear number of teeth.According to a gear velocity ratio requirement, the parameter of k1 planet row is optional as follows: Z
2/ Z
19=2.7, wherein Z
2for the gear ring number of teeth, Z
19for the sun gear number of teeth.
8 gear planetary automatic transmission transmission scheme gears of the present invention arrange and gear range can further improve power performance and fuel economy.
The above is only the preferred embodiment of the present invention; it should be pointed out that for those skilled in the art, under the prerequisite not departing from the technology of the present invention principle; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.
Claims (9)
1. eight gear planetary automatic transmissions, is characterized in that: comprise input shaft (18), k1 planet row, La Weina planetary mechanism, shift control element and transmission support bracket (20);
Wherein, k1 planet row is made up of k1 planet row planet carrier (1), k1 planet row gear ring (2) and k1 planet row sun gear (19); La Weina planetary mechanism is made up of La Weina mechanism planet carrier input shaft (6), La Weina mechanism planet carrier (9), long row star-wheel (10), bull gear (11), large sun gear (13), short planet wheel (14), little gear ring (15), small sun gear (16) and sun gear input shaft (17); Shift control element comprises clutch a (3), clutch b (4), clutch c (5), break a (7), break b (8) and break c (12);
Its position relationship is: described clutch a (3), clutch b (4), clutch c (5) and break a (7) are arranged between k1 planet row and La Weina planetary mechanism;
Its annexation is: k1 planet row sun gear (19) is connected with transmission support bracket (20), input shaft (18) and k1 planet row planet carrier (1), clutch c (5) drive end connects, k1 planet row gear ring (2) and clutch a (3), the drive end of clutch b (4) connects, clutch a (3) Partner is by sun gear input shaft (17) and large sun gear (13), break c (12) connects, the Partner of clutch b (4) is connected with small sun gear (16), the Partner of clutch c (5) is connected with break a (7) by La Weina mechanism planet carrier input shaft (6), little gear ring (15) is meshed with short planet wheel (14) and little gear ring (15) is connected with break b (8), La Weina mechanism planet carrier input shaft (6) is connected with La Weina mechanism planet carrier (9), La Weina mechanism planet carrier (9) is arranged long row star-wheel (10) and short planet wheel (14), long row star-wheel (10) and large sun gear (13), bull gear (11), short planet wheel (14) are meshed, short planet wheel (14) is also meshed with small sun gear (16), little gear ring (15), the pto＝power take-off that bull gear (11) is speed changer.
2. a kind of eight keep off planetary automatic transmissions according to claim 1, it is characterized in that: a gear: power inputs from transmission input shaft (18), k1 planet row sun gear (19) is fixed with transmission support bracket (20), power slows down through k1 planet row gear ring (2) and exports, by engaging clutch b (4), power is input to the small sun gear (16) of La Weina planetary mechanism, break a (7) is La Weina mechanism planet carrier (9) braking, and transmission power finally slows down from the bull gear (11) of La Weina planetary mechanism and exports.
3. a kind of eight keep off planetary automatic transmissions according to claim 1, it is characterized in that: two gears: power inputs from transmission input shaft (18), k1 planet row sun gear (19) is fixed with transmission support bracket (20), power slows down through k1 planet row gear ring (2) and exports, by engaging clutch b (4), power is input to the small sun gear (16) of La Weina planetary mechanism, break b (8) brakes the little gear ring (15) of La Weina planetary mechanism, transmission power finally slows down from the bull gear (11) of La Weina planetary mechanism and exports.
4. a kind of eight keep off planetary automatic transmissions according to claim 1, it is characterized in that: three gears: power inputs from transmission input shaft (18), k1 planet row sun gear (19) is fixed with transmission support bracket (20), power slows down through k1 planet row gear ring (2) and exports, by engaging clutch b (4), power is input to the small sun gear (16) of La Weina planetary mechanism, break c (12) brakes the large sun gear (13) of La Weina planetary mechanism, transmission power finally slows down from the bull gear (11) of La Weina planetary mechanism and exports.
5. a kind of eight keep off planetary automatic transmissions according to claim 1, it is characterized in that: four gears: power inputs from transmission input shaft (18), k1 planet row sun gear (19) is fixed with transmission support bracket (20), power slows down through k1 planet row gear ring (2) and exports, by engaging clutch b (4) and clutch a (3), power is input to small sun gear (16) and the large sun gear (13) of La Weina planetary mechanism respectively, the revolution of La Weina planetary mechanism entirety, transmission power finally exports from the bull gear (11) of La Weina planetary mechanism.
6. a kind of eight keep off planetary automatic transmissions according to claim 1, it is characterized in that: five gears: power inputs from transmission input shaft (18), k1 planet row sun gear (19) is fixed with transmission support bracket (20), part power slows down through k1 planet row gear ring (2) and exports, by engaging clutch b (4), be input to the small sun gear (16) of La Weina planetary mechanism; Another part power, through transmission input shaft (18) and k1 planet row planet carrier (1), by engaging clutch c (5), is input to La Weina mechanism planet carrier (9); Two-way power converging in La Weina mechanism, finally slow down from bull gear (11) and export.
7. a kind of eight keep off planetary automatic transmissions according to claim 1, it is characterized in that: six gears: power inputs from transmission input shaft (18), k1 planet row sun gear (19) is fixed with transmission support bracket (20), part power slows down through k1 planet row gear ring (2) and exports, by engaging clutch a (3), be input to the large sun gear (13) of La Weina planetary mechanism; Another part power through transmission input shaft (18) and k1 planet row planet carrier (1), by engaging clutch c (5), La Weina mechanism planet carrier (9); Two-way power converging in La Weina mechanism, finally export from bull gear (11) speedup.
8. a kind of eight keep off planetary automatic transmissions according to claim 1, it is characterized in that: seven gears: power inputs from transmission input shaft (18), power is through transmission input shaft (18) and k1 planet row planet carrier (1), by engaging clutch c (5), be input to La Weina mechanism planet carrier (9), break c (12) brakes large for La Weina planetary mechanism sun gear (13), and power finally exports from bull gear (11) speedup.
9. a kind of eight keep off planetary automatic transmissions according to claim 1, it is characterized in that: eight gears: power inputs from transmission input shaft (18), power is through transmission input shaft (18) and k1 planet row planet carrier (1), by engaging clutch c (5), be input to La Weina mechanism planet carrier (9), break b (8) brakes little for La Weina planetary mechanism gear ring (15), and power finally exports from bull gear (11) speedup.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210304352.7A CN102817974B (en) | 2012-08-24 | 2012-08-24 | Eight-gear planetary automatic speed changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210304352.7A CN102817974B (en) | 2012-08-24 | 2012-08-24 | Eight-gear planetary automatic speed changer |
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| Publication Number | Publication Date |
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| CN102817974A CN102817974A (en) | 2012-12-12 |
| CN102817974B true CN102817974B (en) | 2015-03-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201210304352.7A Expired - Fee Related CN102817974B (en) | 2012-08-24 | 2012-08-24 | Eight-gear planetary automatic speed changer |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013202885A1 (en) * | 2013-02-22 | 2014-08-28 | Zf Friedrichshafen Ag | Multi-speed transmission in planetary construction |
| CN105546061B (en) * | 2016-01-19 | 2018-02-13 | 无锡商业职业技术学院 | One kind seven keeps off planetary gear automatic transmission |
| CN108278338A (en) * | 2018-01-23 | 2018-07-13 | 柳州职业技术学院 | A kind of new 7 speed automobile automatic transmission |
| CN110107661A (en) * | 2019-04-30 | 2019-08-09 | 柳州职业技术学院 | The new 8 speed automobile automatic transmission of one kind and its power transmission scheme |
| CN110578775A (en) * | 2019-07-12 | 2019-12-17 | 福州锐智新能源科技有限公司 | three-gear transmission based on Ravigneaux planetary gear train and linkage actuating mechanism |
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| DE10115987A1 (en) * | 2001-03-30 | 2002-10-02 | Zahnradfabrik Friedrichshafen | Multi-speed transmission |
| DE10318565A1 (en) * | 2003-04-24 | 2004-11-11 | Zf Friedrichshafen Ag | Multiple-stage automatic transmission with kinematic coupling of wheel set elements to each other for eight forward gears and two reverse gears |
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| DE102005022011A1 (en) * | 2005-05-12 | 2005-12-08 | Daimlerchrysler Ag | Drive chain for use in motor vehicle, has input and output planetary gear sets, clutches and two brakes that are arranged in such manner that six different forward gears are adjustable between input shaft and output shaft |
| JP3777929B2 (en) * | 1999-12-24 | 2006-05-24 | アイシン精機株式会社 | Transmission |
| CN202165552U (en) * | 2011-06-30 | 2012-03-14 | 长城汽车股份有限公司 | Eight-speed automatic transmission |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7766785B2 (en) * | 2007-01-25 | 2010-08-03 | Ford Global Technologies, Llc | Multiple speed automatic transmission |
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2012
- 2012-08-24 CN CN201210304352.7A patent/CN102817974B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3777929B2 (en) * | 1999-12-24 | 2006-05-24 | アイシン精機株式会社 | Transmission |
| DE10115987A1 (en) * | 2001-03-30 | 2002-10-02 | Zahnradfabrik Friedrichshafen | Multi-speed transmission |
| CN1650119A (en) * | 2002-05-11 | 2005-08-03 | 腓特烈斯港齿轮工厂股份公司 | Multi-stage transmission |
| CN1653282A (en) * | 2002-05-11 | 2005-08-10 | 腓特烈斯港齿轮工厂股份公司 | Six-speed automatic gearbox |
| DE10318565A1 (en) * | 2003-04-24 | 2004-11-11 | Zf Friedrichshafen Ag | Multiple-stage automatic transmission with kinematic coupling of wheel set elements to each other for eight forward gears and two reverse gears |
| DE102005022011A1 (en) * | 2005-05-12 | 2005-12-08 | Daimlerchrysler Ag | Drive chain for use in motor vehicle, has input and output planetary gear sets, clutches and two brakes that are arranged in such manner that six different forward gears are adjustable between input shaft and output shaft |
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| CN102817974A (en) | 2012-12-12 |
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Granted publication date: 20150311 |