CN103267093A - Eight-gear planetary automatic gearbox - Google Patents
Eight-gear planetary automatic gearbox Download PDFInfo
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- CN103267093A CN103267093A CN2013102042470A CN201310204247A CN103267093A CN 103267093 A CN103267093 A CN 103267093A CN 2013102042470 A CN2013102042470 A CN 2013102042470A CN 201310204247 A CN201310204247 A CN 201310204247A CN 103267093 A CN103267093 A CN 103267093A
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Abstract
The invention belongs to the technical field of power transmission, and relates to a gearbox, in particular to an eight-gear planetary automatic gearbox. The eight-gear planetary automatic gearbox comprises an input shaft, a k1 planet row, a k2 planet row, a k3 planet row, a k4 planet row, a gear-shift control element and an output shaft, wherein each planet row is composed of a planet row planet carrier, a planet row gear ring and a planet row sun gear, and the gear-shift control element comprises a clutch a, a clutch b, a brake a, a brake b, a brake c and a brake d. The eight-gear planetary automatic gearbox is provided with eight forward gears and obtains a transmission ratio with good overall performance.
Description
Technical field
The invention belongs to the power transmission technical field, relate to a kind of speed changer, particularly a kind of eight retaining planetary automatic transmissions.
Background technique
Along with improving constantly of requirements such as environmental protection and Green Travel, the power character of vehicle and fuel economy require automatic transmission is developed to wide gear range, many gears, little differential direction, in, the gear range of heavy-duty commercial vehicle automatic transmission reached more than 9.The more employing planet speed change mechanism of vehicle automatic transmission is as the speed changing function parts, and planet speed change mechanism mainly is made up of planet row and multidisc shift control element, to reach light-weighted requirement.
Summary of the invention
In the objective of the invention is to seek to satisfy, the big speed ratio scope planetary automatic transmission transmission scheme of heavy-duty commercial vehicle usage requirement, claimed structure compactness, pilot oil oil circuit arrangement convenience, coaxial output.
For achieving the above object, technological scheme of the present invention is a kind of eight retaining planetary automatic transmissions of design, comprises input shaft, k1 planet row, k2 planet row, k3 planet row, k4 planet row, shift control element and output shaft;
Wherein, k1 planet row is made up of k1 planet rows of planetary frame 3, k1 planet toothrow circle 5 and k1 planet row sun gear 19, k2 planet row is made up of k2 planet rows of planetary frame 6, k2 planet toothrow circle 7 and k2 planet row sun gear 18, k3 planet row is made up of k3 planet rows of planetary frame 9, k3 planet toothrow circle 11 and k3 planet row sun gear 17, and k4 planet row is made up of k4 planet rows of planetary frame 14, k4 planet toothrow circle 13 and k4 planet row sun gear 16; The shift control element comprises clutch a1, clutch b2, break a4, break b8, break c10 and break d12;
Its position relation is: described clutch a1 and clutch b2 are positioned at k1 planet row left side, and break a4, break b8, break c10 and break d12 are positioned at the exclusive layer of planet;
Its annexation is: input shaft 20 and the drive end of clutch a1 and the drive end of clutch b2, k1 planet row sun gear 19 connects, k1 planet rows of planetary frame 3 is connected with k2 planet toothrow circle 7 with break a4, k1 planet toothrow circle 5 and k2 planet rows of planetary frame 6, k3 planet toothrow circle 11 is connected with break c10, k2 planet row sun gear 18 is connected with break b8, the Partner of k3 planet rows of planetary frame 9 and clutch b2, k4 planet toothrow circle 13 is connected with break d12, k3 planet row sun gear 17 is connected with k4 planet row sun gear 16 with the Partner of clutch a1, and k4 planet rows of planetary frame 14 is connected with output shaft 15.
Advantage of the present invention and effect are: one, utilize scheme in parallel to set up a plurality of power streams, compare other planetary automatic transmission, gear is more.Two, two clutches are adjacent, are convenient to centralized arrangement pilot oil oil circuit, compact structure, manipulation oil circuit arrangement convenience.Three, adopt the Three Degree Of Freedom scheme, every retaining engages two actuating elements, when adjacent gear switches, only needs to switch an actuating element, can simplify gearshift control.Four, can realize five deceleration gears, two speedup gears, gear is differential rationally, and gear range can reach more than 9.9.Five, coaxial output is convenient to rear-guard and is driven layout entirely, in being applicable to, heavy-duty commercial vehicle.
Description of drawings
Fig. 1 is transmission sketch of the present invention;
Fig. 2 is each gear actuating element worksheet.
Among the figure, 1-clutch a, 2-clutch b, 3-k1 planet rows of planetary frame, 4-break a, 5-k1 planet toothrow circle, 6-k2 planet rows of planetary frame, 7-k2 planet toothrow circle, 8-break b, 9-k3 planet rows of planetary frame, 10-break c, 11-k3 planet toothrow circle, 12-break d, 13-k4 planet toothrow circle, 14-k4 planet rows of planetary frame, 15-output shaft, 16-k4 planet row sun gear, 17-k3 planet row sun gear, 18-k2 planet row sun gear, 19-k1 planet row sun gear, 20-input shaft.
Embodiment
Below in conjunction with drawings and Examples the specific embodiment of the present invention is carried out concrete description, this embodiment only technological scheme of the present invention can not limit protection scope of the present invention with this for more clearly illustrating.
As shown in Figure 1, the concrete technological scheme of implementing of the present invention is: a kind of eight retaining planetary automatic transmissions comprise input shaft 20, k1 planet row, k2 planet row, k3 planet row, k4 planet row, shift control element and output shaft 15;
Wherein, k1 planet row is made up of k1 planet rows of planetary frame 3, k1 planet toothrow circle 5 and k1 planet row sun gear 19, k2 planet row is made up of k2 planet rows of planetary frame 6, k2 planet toothrow circle 7 and k2 planet row sun gear 18, k3 planet row is made up of k3 planet rows of planetary frame 9, k3 planet toothrow circle 11 and k3 planet row sun gear 17, and k4 planet row is made up of k4 planet rows of planetary frame 14, k4 planet toothrow circle 13 and k4 planet row sun gear 16; The shift control element comprises clutch a1, clutch b2, break a4, break b8, break c10 and break d12;
Its position relation is: clutch a1 and clutch b2 are positioned at k1 planet row left side, and break a4, break b8, break c10 and break d12 are positioned at the exclusive layer of planet;
Its annexation is: input shaft 20 and the drive end of clutch a1 and the drive end of clutch b2, k1 planet row sun gear 19 connects, k1 planet rows of planetary frame 3 is connected with k2 planet toothrow circle 7 with break a4, k1 planet toothrow circle 5 and k2 planet rows of planetary frame 6, k3 planet toothrow circle 11 is connected with break c10, k2 planet row sun gear 18 is connected with break b8, k3 planet rows of planetary frame 9 and clutch b2 Partner, k4 planet toothrow circle 13 is connected with break d12, k3 planet row sun gear 17 is connected with k4 planet row sun gear 16 with clutch a1 Partner, and k4 planet rows of planetary frame 14 is connected with output shaft 15.
Clutch a1 and clutch b2 are coaxial with transmission input shaft, are arranged in k1 planet row left side, and break a4, break b8, break c10 and break d12 are coaxial with transmission input shaft, are arranged in the exclusive layer of planet.
As shown in Figure 2, in the specific embodiment, ● the expression actuating element engages.
One retaining: realize that by engage brake a4 and break d12 k1 planet rows of planetary frame 3, k2 planet toothrow circle 7, k3 planet rows of planetary frame 9 and k4 planet toothrow circle 13 are fixing; Power is input to k1 planet row sun gear 19 from input shaft 20, output to k3 planet toothrow circle 11 through 5 decelerations of k1 planet toothrow circle, output to k4 planet row sun gear 16 through k3 planet row sun gear 17 speedups again, slowing down finally by k4 planet rows of planetary frame 14 outputs to output shaft 15.
Two retainings: realize that by engaging clutch a1 and break d12 input shaft 20 is connected with k4 planet row sun gear 16 with k3 planet row sun gear 17, k3 planet rows of planetary frame 9 and k4 planet toothrow circle 13 are fixing; Power is input to k4 planet row sun gear 16 from input shaft 20, and slowing down through k4 planet rows of planetary frame 14 outputs to output shaft 15.
Three retainings: realize that by engaging clutch a1 and break a4 input shaft 20 is connected with k4 planet row sun gear 16 with k3 planet row sun gear 17, k1 planet rows of planetary frame 3 and k2 planet toothrow circle 7 are fixing; Power is from input shaft 20 inputs, a part is directly inputted to k3 planet row sun gear 17, part power slows down through k3 planet rows of planetary frame 9 and outputs to k4 planet toothrow circle 13, after confluxing with the power that is directly inputted to k4 planet row sun gear 16 from input shaft 20, slowing down through k4 planet rows of planetary frame 14 outputs to output shaft 15; And the part power that enters k3 planet row sun gear 17 outputs to k1 planet toothrow circle 5 through 11 decelerations of k3 planet toothrow circle, output to input shaft 20 through k1 planet row sun gear 19 speedups again, continue to be directly inputted to k3 planet row sun gear 17 after confluxing with power, form circulating power load, cause this gear transmission efficiency to descend to some extent.
Four retainings: realize that by engaging clutch a1 and break c10 input shaft 20 is connected with k4 planet row sun gear 16 with k3 planet row sun gear 17, k3 planet toothrow circle 11 is fixing; Power is from input shaft 20 inputs, a part is slowed down through k3 planet rows of planetary frame 9 by k3 planet row sun gear 17 and is outputed to k4 planet toothrow circle 13, after the power that is directly inputted to k4 planet row sun gear 16 with another part confluxed, slowing down through k4 planet rows of planetary frame 14 outputed to output shaft 15 again.
Five retainings: realize that by engaging clutch a1 and break b8 input shaft 20 is connected with k4 planet row sun gear 16 with k3 planet row sun gear 17, k2 planet row sun gear 18 is fixing; Power is from input shaft 20 inputs, a part is slowed down through k1 planet rows of planetary frame 3 by k1 planet row sun gear 19 and is outputed to k2 planet toothrow circle 7, part directly outputs to k1 planet toothrow circle 5 through k2 planet rows of planetary frame 6, forms circulating power load, causes this gear transmission efficiency to descend to some extent; Part is slowed down through k2 planet rows of planetary frame 6 and is outputed to k3 planet toothrow circle 11; After the power that is directly inputted to k3 planet row sun gear 17 with another part confluxed, slowing down through k3 planet rows of planetary frame 9 outputed to k4 planet toothrow circle 13; After the power that is directly inputted to k4 planet row sun gear 16 with another part confluxed again, slowing down through k4 planet rows of planetary frame 14 outputed to output shaft 15.
Six retainings: realize that by engaging clutch a1 and clutch b2 input shaft 20 is connected with k4 planet toothrow circle 13 with k3 planet row sun gear 17, k4 planet row sun gear 16, k3 planet rows of planetary frame 9; At this moment, the whole revolution of all members, power is from input shaft 20 inputs, after entering k4 planet row's sun gear 16 and k4 planet toothrow circle 13 respectively and confluxing, directly outputs to output shaft 15 through k4 planet rows of planetary frame 14.
Seven retainings: realize that by engaging clutch b2 and break b8 input shaft 20 is connected with k4 planet toothrow circle 13 with k3 planet rows of planetary frame 9, k2 planet row sun gear 18 is fixing; Power is from input shaft 20 inputs, a part outputs to k4 planet row sun gear 16 by k3 planet rows of planetary frame 9 through k3 planet row sun gear 17 speedups, after the power that is directly inputted to k4 planet toothrow circle 13 with another part confluxed, slowing down through k4 planet rows of planetary frame 14 outputed to output shaft 15.
Eight retainings: realize that by engaging clutch b2 and break a4 input shaft 20 is connected with k4 planet toothrow circle 13 with k3 planet rows of planetary frame 9, k1 planet rows of planetary frame 3 and k2 planet toothrow circle 7 are fixing; Power is from input shaft 20 inputs, a part is slowed down through k1 planet toothrow circle 5 by k1 planet row sun gear 19 and is outputed to k3 planet toothrow circle 11, after the power that is directly inputted to k3 planet rows of planetary frame 9 with another part confluxes, output to k4 planet row sun gear 16 through k3 planet row sun gear 17 speedups, after the power that is directly inputted to k4 planet toothrow circle 13 with another part confluxed again, slowing down through k4 planet rows of planetary frame 14 outputed to output shaft 15.
Reverse gear: realize that by engage brake b8 and break d12 k2 planet row sun gear 18, k3 planet rows of planetary frame 9 and k4 planet toothrow circle 13 are fixing; Power is from input shaft 20 inputs, output to k2 planet toothrow circle 7 by k1 planet row sun gear 19 through 3 decelerations of k1 planet rows of planetary frame, slow down through k2 planet rows of planetary frame 6 again and output to k3 planet toothrow circle 11, output to k4 planet row sun gear 16 through k3 planet row sun gear 17 speedups, slowing down finally by k4 planet rows of planetary frame 14 outputs to output shaft 15.
Defining planet row parameter herein is the ratio of the gear ring number of teeth and the sun gear number of teeth, and then k1 planet row parameter is 2.400 among the embodiment, k2 planet row parameter is 1.200, k3 planet row parameter is 1.800, to arrange parameter be 3.900 to the k4 planet.
Eight retaining planetary automatic transmission gear ranges of the present invention reach 9.933, can satisfy the requirement of commerial vehicle power character and fuel economy.
The above only is preferred implementation of the present invention; should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the technology of the present invention principle; can also develop out some improvement projects, these improvement projects are also in protection scope of the present invention.
Claims (9)
1. a retaining planetary automatic transmission is characterized in that: comprise input shaft (20), k1 planet row, k2 planet row, k3 planet row, k4 planet row, shift control element and output shaft (15);
Wherein, k1 planet row is made up of k1 planet rows of planetary frame (3), k1 planet toothrow circle (5) and k1 planet row's sun gear (19), k2 planet row is made up of k2 planet rows of planetary frame (6), k2 planet toothrow circle (7) and k2 planet row's sun gear (18), k3 planet row is made up of k3 planet rows of planetary frame (9), k3 planet toothrow circle (11) and k3 planet row's sun gear (17), and k4 planet row is made up of k4 planet rows of planetary frame (14), k4 planet toothrow circle (13) and k4 planet row's sun gear (16); The shift control element comprises clutch a (1), clutch b (2), break a (4), break b (8), break c (10) and break d (12);
Its position relation is: described clutch a (1) and clutch b (2) are positioned at k1 planet row left side, and break a (4), break b (8), break c (10) and break d (12) are positioned at the exclusive layer of planet;
Its annexation is: input shaft (20) and clutch a (1) drive end and clutch b (2) drive end, k1 planet row's sun gear (19) connects, k1 planet rows of planetary frame (3) is connected with k2 planet toothrow circle (7) with break a (4), k1 planet toothrow circle (5) and k2 planet rows of planetary frame (6), k3 planet toothrow circle (11) is connected with break c (10), k2 planet row's sun gear (18) is connected with break b (8), k3 planet rows of planetary frame (9) and clutch b (2) Partner, k4 planet toothrow circle (13) is connected with break d (12), k3 planet row's sun gear (17) is connected with k4 planet row's sun gear (16) with clutch a (1) Partner, and k4 planet rows of planetary frame (14) is connected with output shaft (15).
2. a kind of eight retaining planetary automatic transmissions according to claim 1 is characterized in that: realize a retaining by engage brake a (4) and break d (12); K1 planet rows of planetary frame (3), k2 planet toothrow circle (7), k3 planet rows of planetary frame (9) and k4 planet toothrow circle (13) are fixing; Power is input to k1 planet row sun gear (19) from input shaft (20), output to k3 planet toothrow circle (11) through k1 planet toothrow circle (5) deceleration, output to k4 planet row sun gear (16) through k3 planet row sun gear (17) speedup again, slowing down finally by k4 planet rows of planetary frame (14) outputs to output shaft (15).
3. a kind of eight retaining planetary automatic transmissions according to claim 1 is characterized in that: realize two retainings by engaging clutch a (1) and break d (12); Input shaft (20) is connected with k4 planet row's sun gear (16) with k3 planet row's sun gear (17), and k4 planet toothrow circle (13) is fixing; Power is input to k4 planet row sun gear (16) from input shaft (20), and slowing down through k4 planet rows of planetary frame (14) outputs to output shaft (15).
4. a kind of eight retaining planetary automatic transmissions according to claim 1 is characterized in that: realize three retainings by engaging clutch a (1) and break a (4); Input shaft (20) is connected with k4 planet row's sun gear (16) with k3 planet row's sun gear (17), and k1 planet rows of planetary frame (3) and k2 planet toothrow circle (7) are fixing; Power is from input shaft (20) input, and a part is slowed down through k3 planet rows of planetary frame (9) by k3 planet row's sun gear (17) and outputed to k4 planet toothrow circle (13); After the power that is directly inputted to k4 planet row sun gear (16) with another part confluxed, slowing down through k4 planet rows of planetary frame (14) outputed to output shaft (15).
5. a kind of eight retaining planetary automatic transmissions according to claim 1 is characterized in that: realize four retainings by engaging clutch a (1) and break c (10); Input shaft (20) is connected with k4 planet row's sun gear (16) with k3 planet row's sun gear (17), and k3 planet toothrow circle (11) is fixing; Power is imported from input shaft (20), a part is slowed down through k3 planet rows of planetary frame (9) by k3 planet row's sun gear (17) and is outputed to k4 planet toothrow circle (13), after the power that is directly inputted to k4 planet row sun gear (16) with another part confluxed, slowing down through k4 planet rows of planetary frame (14) outputed to output shaft (15) again.
6. a kind of eight retaining planetary automatic transmissions according to claim 1 is characterized in that: realize five retainings by engaging clutch a (1) and break b (8); Input shaft (20) is connected with k4 planet row's sun gear (16) with k3 planet row's sun gear (17), and k2 planet row's sun gear (18) is fixing; Power is from input shaft (20) input, and a part is slowed down through k1 planet rows of planetary frame (3) by k1 planet row's sun gear (19) and outputed to k2 planet toothrow circle (7), and slowing down through k2 planet rows of planetary frame (6) outputs to k3 planet toothrow circle (11) again; After the power that is directly inputted to k3 planet row sun gear (17) with another part confluxed, slowing down through k3 planet rows of planetary frame (9) outputed to k4 planet toothrow circle (13); After the power that is directly inputted to k4 planet row sun gear (16) with another part confluxed again, slowing down through k4 planet rows of planetary frame (14) outputed to output shaft (15).
7. a kind of eight retaining planetary automatic transmissions according to claim 1 is characterized in that: realize six retainings by engaging clutch a (1) and clutch b (2); Input shaft (20) is connected with k4 planet toothrow circle (13) with k3 planet row sun gear (17), k4 planet row sun gear (16), k3 planet rows of planetary frame (9); At this moment, the whole revolution of all members, power is from input shaft (20) input, after entering k4 planet row's sun gear (16) and k4 planet toothrow circle (13) respectively and confluxing, directly outputs to output shaft (15) through k4 planet rows of planetary frame (14).
8. a kind of eight retaining planetary automatic transmissions according to claim 1 is characterized in that: realize seven retainings by engaging clutch b (2) and break b (8); Input shaft (20) is connected with k4 planet toothrow circle (13) with k3 planet rows of planetary frame (9), and k2 planet row's sun gear (18) is fixing; Power is imported from input shaft (20), a part outputs to k4 planet row sun gear (16) by k3 planet rows of planetary frame (9) through k3 planet row sun gear (17) speedup, after the power that is directly inputted to k4 planet toothrow circle (13) with another part confluxed, slowing down through k4 planet rows of planetary frame (14) outputed to output shaft (15).
9. a kind of eight retaining planetary automatic transmissions according to claim 1 is characterized in that: realize eight retainings by engaging clutch b (2) and break a (4); Input shaft (20) is connected with k4 planet toothrow circle (13) with k3 planet rows of planetary frame (9), and k1 planet rows of planetary frame (3) and k2 planet toothrow circle (7) are fixing; Power is from input shaft (20) input, and a part is slowed down through k1 planet toothrow circle (5) by k1 planet sun gear (19) and outputed to k3 planet toothrow circle (11); After the power that is directly inputted to k3 planet rows of planetary frame (9) with another part confluxes, output to k4 planet row sun gear (16) through k3 planet row sun gear (17) speedup; After the power that is directly inputted to k4 planet toothrow circle (13) with another part confluxed again, slowing down through k4 planet rows of planetary frame (14) outputed to output shaft (15).
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| CN201310204247.0A CN103267093B (en) | 2013-05-29 | 2013-05-29 | A kind of eight gear planetary automatic transmissions |
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| CN201310204247.0A CN103267093B (en) | 2013-05-29 | 2013-05-29 | A kind of eight gear planetary automatic transmissions |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104595435A (en) * | 2014-12-26 | 2015-05-06 | 燕山大学 | Eight-gear transmission |
| CN106438878A (en) * | 2016-09-30 | 2017-02-22 | 中国北方车辆研究所 | Nine-gear planet automatic transmission |
| EP3312465A1 (en) * | 2016-09-28 | 2018-04-25 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| WO2019020129A1 (en) * | 2017-07-25 | 2019-01-31 | 罗灿 | Reverse-type connection planetary row transmission mechanism |
| US10598261B2 (en) | 2016-09-28 | 2020-03-24 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10634221B2 (en) | 2016-09-28 | 2020-04-28 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10704655B2 (en) | 2016-09-28 | 2020-07-07 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| CN111550531A (en) * | 2020-06-11 | 2020-08-18 | 山东科技大学 | 12-speed automatic transmission |
| US10808806B2 (en) | 2016-09-28 | 2020-10-20 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10876598B2 (en) | 2016-09-28 | 2020-12-29 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| CN113251119A (en) * | 2021-06-03 | 2021-08-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission |
Citations (7)
| 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 |
| EP0239205B1 (en) * | 1986-02-27 | 1991-04-17 | General Motors Corporation | Transmission gearing arrangement |
| US6176803B1 (en) * | 1999-09-28 | 2001-01-23 | Caterpillar Inc. | Transmission assembly with four planetary gear sets providing nine forward and one reverse gear ratio |
| CN1828089A (en) * | 2005-03-03 | 2006-09-06 | 通用汽车公司 | Nine-speed transmissions with four planetary gear sets |
| CN1936363A (en) * | 2005-09-23 | 2007-03-28 | 通用汽车公司 | Nine speed automatic transmission with six torque-transmitting mechanisms |
| CN101688589A (en) * | 2007-05-04 | 2010-03-31 | 通用汽车环球科技运作公司 | Wide ratio transmission with four planetary gear sets and four brakes |
| CN102203458A (en) * | 2008-11-03 | 2011-09-28 | 戴姆勒股份公司 | Transmission unit |
-
2013
- 2013-05-29 CN CN201310204247.0A patent/CN103267093B/en not_active Expired - Fee Related
Patent Citations (7)
| 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 |
| EP0239205B1 (en) * | 1986-02-27 | 1991-04-17 | General Motors Corporation | Transmission gearing arrangement |
| US6176803B1 (en) * | 1999-09-28 | 2001-01-23 | Caterpillar Inc. | Transmission assembly with four planetary gear sets providing nine forward and one reverse gear ratio |
| CN1828089A (en) * | 2005-03-03 | 2006-09-06 | 通用汽车公司 | Nine-speed transmissions with four planetary gear sets |
| CN1936363A (en) * | 2005-09-23 | 2007-03-28 | 通用汽车公司 | Nine speed automatic transmission with six torque-transmitting mechanisms |
| CN101688589A (en) * | 2007-05-04 | 2010-03-31 | 通用汽车环球科技运作公司 | Wide ratio transmission with four planetary gear sets and four brakes |
| CN102203458A (en) * | 2008-11-03 | 2011-09-28 | 戴姆勒股份公司 | Transmission unit |
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104595435A (en) * | 2014-12-26 | 2015-05-06 | 燕山大学 | Eight-gear transmission |
| US10634221B2 (en) | 2016-09-28 | 2020-04-28 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10626958B2 (en) | 2016-09-28 | 2020-04-21 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| EP4198345A1 (en) * | 2016-09-28 | 2023-06-21 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10316940B2 (en) | 2016-09-28 | 2019-06-11 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10704655B2 (en) | 2016-09-28 | 2020-07-07 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10598260B2 (en) | 2016-09-28 | 2020-03-24 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| EP3312465A1 (en) * | 2016-09-28 | 2018-04-25 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10876598B2 (en) | 2016-09-28 | 2020-12-29 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10598261B2 (en) | 2016-09-28 | 2020-03-24 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10808806B2 (en) | 2016-09-28 | 2020-10-20 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10808807B2 (en) | 2016-09-28 | 2020-10-20 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| CN106438878A (en) * | 2016-09-30 | 2017-02-22 | 中国北方车辆研究所 | Nine-gear planet automatic transmission |
| WO2019020129A1 (en) * | 2017-07-25 | 2019-01-31 | 罗灿 | Reverse-type connection planetary row transmission mechanism |
| CN111550531A (en) * | 2020-06-11 | 2020-08-18 | 山东科技大学 | 12-speed automatic transmission |
| CN111550531B (en) * | 2020-06-11 | 2023-03-21 | 山东科技大学 | 12-speed automatic transmission |
| CN113251119A (en) * | 2021-06-03 | 2021-08-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission |
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| CN103267093B (en) | 2016-01-20 |
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