HK1211655A1 - A composite type double cavity of hydraulic coupler and starter - Google Patents
A composite type double cavity of hydraulic coupler and starter Download PDFInfo
- Publication number
- HK1211655A1 HK1211655A1 HK15110170.4A HK15110170A HK1211655A1 HK 1211655 A1 HK1211655 A1 HK 1211655A1 HK 15110170 A HK15110170 A HK 15110170A HK 1211655 A1 HK1211655 A1 HK 1211655A1
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- Hong Kong
- Prior art keywords
- output
- gear
- input
- planet carrier
- pair
- Prior art date
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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
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
-
- 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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
- F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention provides a compound type double-cavity fluid coupling and a starter. According to the technical scheme, an overrunning clutch (13) is connected with an input shaft (1), an output duplex planet carrier (21) is connected with a connecting gear pair (4), the connecting gear pair (4) is connected with an input large gear (24), an output small gear (26) is connected with an input planet carrier (27), an output small gear ring (29), an output gear pair (6) and an output planet carrier (25) are connected, an output large gear ring (28) is connected with a speed change mechanism (8), the speed change mechanism (8) is connected with an input gear pair (10) and the double-cavity fluid coupling (11), the input gear pair (10) is connected with an input gear (22), and the double-cavity fluid coupling (11) is connected with a starting gear pair (12).
Description
Technical Field
The invention belongs to the field of hydraulic couplers and starting, and particularly relates to a composite double-cavity hydraulic coupler and a starter for various ground vehicles, ships, railway locomotives and machine tools.
Background
At present, the hydraulic coupler is designed according to principles such as fluid statics, and the like, and the hydraulic coupler can transfer low power and is low in efficiency; in addition, the cost is high.
Disclosure of Invention
The invention overcomes the defects of the prior art and provides the composite double-cavity hydraulic coupler and the starter which have the advantages of prolonging the service life of the engine, along with simple structure, convenient operation and control, low cost, energy conservation and high efficiency.
In order to realize the purpose of the invention, the technical scheme adopted by the invention is as follows:
a composite double-cavity hydraulic coupler and a starter comprise an input shaft (1), an output shaft (3), a coupling gear pair (4), a one-way clutch (5), an output gear pair (6), a neutral gear-engaging mechanism (7), a speed change mechanism (8), a fixed one-way clutch (9), an input gear pair (10), a double-cavity hydraulic coupler (11), a starting gear pair (12), an overrunning clutch (13) and a starting gear (14), wherein an input end (91) of the fixed one-way clutch (9) is coupled with a fixed element, and a planetary gear (20), an output double-coupling planetary carrier (21), an input gear (22), an input pinion (23), an input gearwheel (24), an output planetary carrier (25), an output pinion (26), an input planetary carrier (27) and an output large gear ring (28) are arranged between the input shaft (1) and the output shaft (3), An output small gear ring (29), an input small gear (23) is connected with an output gear (122) of a starting gear pair (12) and an output end (132) of an overrunning clutch (13), an input end (131) of the overrunning clutch (13) is connected with an input shaft (1), the input small gear (23) is mutually matched with an output duplex planet carrier (21) and an input gear (22) through a planetary gear (20) on the output duplex planet carrier (21), the output duplex planet carrier (21) is connected with an input gear (41) of a connecting gear pair (4), an output gear (42) of the connecting gear pair (4) is connected with an input large gear (24), the input large gear (24) is mutually matched with an output planet carrier (25) and an output small gear (26) through a planetary gear (20) on the output planet carrier (25), and the output small gear (26) is connected with an input planet carrier (27), the input planet carrier (27) is matched with the output large gear ring (28) and the output small gear ring (29) through the planet gear (20) on the input planet carrier, the output small gear ring (29) and the input gear (61) of the output gear pair (6) are connected with the output planet carrier (25), the output gear (62) of the output gear pair (6) and the input end (51) of the one-way clutch (5) are connected with the input end (71) of the idle gear mechanism (7), the output end (52) of the one-way clutch (5) is connected with the input shaft (1), the output end (72) of the idle gear mechanism (7) is connected with the output shaft (3), the output large gear ring (28) is connected with the input end (81) of the speed change mechanism (8), the output end (82) of the speed change mechanism (8) is connected with the output end (92) of the fixed one-way clutch (9), the input gear (101) of the input gear pair (10) and the input end (111) of the double-cavity hydraulic coupler (11, an output gear (102) of the input gear pair (10) is connected with an input gear (22), an output end (112) of the double-cavity hydraulic coupler (11) is connected with an input gear (121) of the starting gear pair (12), and an output gear (122) of the starting gear pair (12) is connected with a starting gear (14).
Each element needing to be connected and the elements separated by the other elements can be connected with the other elements by adopting a hollow or connecting frame method through or across the other elements; when the coupled elements are gears or ring gears, they are meshed or coupled with each other; the transmission ratios of the gear pairs and the speed change mechanism are designed according to actual requirements.
The double-cavity hydraulic coupler can be replaced by a hydraulic torque converter.
When the invention is applied to a vehicle, the change of the output torque and the speed can be automatically changed according to the magnitude of resistance received when the vehicle runs.
The invention has the following advantages:
(1) most of power of the invention is transmitted by the gear ring, the planetary gear, the planet carrier and the gear, so that the transmission power and the transmission efficiency are greatly improved, and the invention has simple structure and is easier to maintain;
(2) the torque conversion and the speed change are automatically completed, high-efficiency transmission can be realized, and the engine and the starter can work in the optimal range except starting;
(3) the invention enables the engine and the starter to run in an economic rotating speed area, namely the engine to work in a rotating speed range with very small pollution emission, and avoids the emission of a large amount of waste gas when the engine runs at idle speed and high speed, thereby reducing the emission of the waste gas and being beneficial to protecting the environment;
(4) the invention can utilize the internal rotation speed difference to play the roles of buffering and overload protection, is beneficial to prolonging the service life of the engine, a transmission system and a starter, and can lead the vehicle to automatically reduce the speed when the running resistance is increased, otherwise, the vehicle can increase the speed, thereby being beneficial to improving the running performance of the vehicle;
(5) the invention ensures that the input power is uninterrupted, can ensure that the vehicle has good acceleration and higher average speed, reduces the abrasion of the engine, prolongs the overhaul interval mileage and is beneficial to improving the productivity;
(6) when the invention is started, the invention has the performance of automatic torque conversion and speed change, the input power is uninterrupted, the impact phenomenon can not occur, the stable starting of the engine can be ensured, the noise is reduced, the starting abrasion of the engine is reduced, and the service lives of the starting motor and the storage battery are prolonged;
(7) the invention reduces the transmission mechanism of the existing starter, reduces the manufacturing cost, and only needs to take braking measures to the starting motor after the engine is started to stop the transmission.
The present invention also relates to a hybrid double-chamber fluid coupling and a starter used for various land vehicles, ships, railway locomotives and machine tools.
Drawings
The attached drawings in the specification are structural diagrams of embodiments of the invention, wherein the joint between two elements in the attached drawings uses a thick solid line to represent fixed connection, and a thin solid line to represent that the two elements can rotate relatively.
Detailed Description
The invention will be described in further detail with reference to the following description and accompanying drawings:
example (b):
as shown in fig. 1, a composite double-chamber fluid coupling and starter comprises an input shaft 1, an output shaft 3, a coupling gear pair 4, a one-way clutch 5, an output gear pair 6, a neutral gear mechanism 7, a speed change mechanism 8, a fixed one-way clutch 9, an input gear pair 10, a double-chamber fluid coupling 11, a starting gear pair 12, an overrunning clutch 13 and a starting gear 14, wherein an input end 91 of the fixed one-way clutch 9 is coupled with a fixed element, a planetary gear 20, an output double planet carrier 21, an input gear 22, an input pinion 23, an input large gear 24, an output planet carrier 25, an output pinion 26, an input planet carrier 27, an output large gear ring 28 and an output small gear ring 29 are arranged between the input shaft 1 and the output shaft 3, the input pinion 23 is coupled with an output gear 122 of the starting gear pair 12 and an output end 132 of the overrunning clutch 13, the input end 131 of the overrunning clutch 13 is connected with the input shaft 1, the input pinion 23 is mutually matched with the output double planet carrier 21 and the input gear 22 through the planet gear 20 on the output double planet carrier 21, the output double planet carrier 21 is connected with the input gear 41 of the connecting gear pair 4, the output gear 42 of the connecting gear pair 4 is connected with the input big gear 24, the input big gear 24 is mutually matched with the output planet carrier 25 and the output pinion 26 through the planet gear 20 on the output planet carrier 25, the output pinion 26 is connected with the input planet carrier 27, the input planet carrier 27 is mutually matched with the output big gear ring 28 and the output small gear ring 29 through the planet gear 20 on the input planet carrier, the output small gear ring 29 and the input gear 61 of the output gear pair 6 are connected with the output planet carrier 25, the output gear 62 of the output gear pair 6 and the input end 51 of the one-way clutch 5 are connected with the input end 71 of the idle gear mechanism 7, the output 52 of the one-way clutch 5 is connected with the input shaft 1, the output 72 of the idle gear mechanism 7 is connected with the output shaft 3, the output large gear ring 28 is connected with the input 81 of the speed change mechanism 8, the output 82 of the speed change mechanism 8 is connected with the output 92 of the fixed one-way clutch 9, the input gear 101 of the input gear pair 10 and the input 111 of the double-chamber hydraulic coupling 11, the output gear 102 of the input gear pair 10 is connected with the input gear 22, the output 112 of the double-chamber hydraulic coupling 11 is connected with the input gear 121 of the starting gear pair 12, and the output gear 122 of the starting gear pair 12 is connected with the starting gear 14.
The input large gear 24 divides the power transmitted to the input large gear into two paths through the planetary gears 20 on the output planet carrier 25, one path flows into the output planet carrier 25, the other path passes through the output small gear 26 and is transmitted to the input planet carrier 27, the input planet carrier 27 divides the power transmitted to the input large gear into two paths through the planetary gears 20 on the input planet carrier 27, one path flows into the output large gear ring 28, and the other path flows into the output small gear ring 29.
Because the rotating speed distribution relation of each element can be changed, the two power flows are changed according to the change of the rotating speed distribution between the two power flows, when the rotating speeds of the output planet carrier 25 and the output small gear ring 29 are zero, the output power is zero, but the moment is not zero, at this time, the input power of the output planet carrier 25 and the output small gear ring 29 is changed from a certain value to the maximum value, the constant value refers to a value obtained by distributing input power according to the ratio of the planetary row moments when the rotation speeds of the output planet carrier 25 and the output small gear ring 29 are the same as the rotation speeds of the input large gear 24 and the input planet carrier 27 which are matched with the output small gear ring 29, the maximum value refers to the total power input by the input gearwheel 24, the input carrier 27, that is, when the two paths of power change, the torque transmitted to the output planet carrier 25, the output small gear ring 29 and the output shaft 3 also changes.
The input power of the starter is transmitted to the input pinion 23 by the starting gear 14 and the output gear 122 of the starting gear pair 12 or the input power of the engine through the input shaft 1 and then the overrunning clutch 13, and the power is transmitted to the output duplex planet carrier 21 by the planet gear 20 on the output duplex planet carrier 21, the output duplex planet carrier 21 transmits the power to the input big gear 24 through the coupling gear pair 4, the input big gear 24 splits the power into two paths by the planet gear 20 on the output planet carrier 25, one path flows into the output planet carrier 25, the other path flows into the output pinion 26 and then flows into the input planet carrier 27, the input planet carrier 27 splits the power into two paths by the planet gear 20 on the input planet carrier 27, one path flows into the output small gear ring 29, the other path flows into the input end 81 of the speed change mechanism 8 through the output big gear ring 28, the output end 82 of the speed change mechanism 8 splits the power into two paths, one path flows into the input gear 22 through the input gear pair 10, the other path flows into the input end 111 of the double-chamber hydraulic coupling 11, the output end 112 of the double-chamber hydraulic coupling 11 flows into the input pinion 23 through the starting gear pair 12, the power transmitted to the input pinion 23 is combined with the power transmitted to the input pinion 23 by the starter or the engine, and the power flowing into the input gear 22 is transmitted to the output double planet carrier 21 through the planet gear 20 on the output double planet carrier 21, the output double planet carrier 21 repeats the process, so that the torque transmitted to the output planet carrier 25 and the output small gear ring 29 is increased continuously, before the engine is started, the power transmitted to the output planet carrier 25 and the power transmitted to the output planet carrier 25 through the output small gear ring 29 are transmitted to the engine crankshaft through the output gear pair 6, the input end 71 of the idle gear mechanism 7, the one-way clutch 5 and the input shaft 1, after the engine is started, the power transmitted to the output carrier 25 by engaging the neutral gear mechanism 7 and the power transmitted to the output carrier 25 via the output small ring gear 29 are transmitted to the output shaft 3 of the present invention via the output gear pair 6 and the neutral gear mechanism 7, so that the power of the engine is output to the outside via the output shaft 3.
According to the invention, when the rotating speed of the input shaft 1 is unchanged, the torques on the output planet carrier 25, the output small gear ring 29 and the output shaft 3 are changed along with the change of the rotating speed, the lower the rotating speed, the larger the torque transmitted to the output planet carrier 25, the output small gear ring 29 and the output shaft 3 is, and vice versa, so that the composite type double-cavity hydraulic coupler and the starter can change the torque and the speed along with the difference of the running resistance of the vehicle.
When the invention is used, the power, the rotating speed and the load of the starter input through the starting gear 14 are constant, namely the rotating speed and the torque of the input pinion 23 are constant, before the engine is started, the rotating speed of the engine is zero, when the starter is started, because the output shaft 3 is still, namely the output carrier 25 and the output pinion 29 are still, the input power of the starter is transmitted to the output duplex carrier 21 through the starting gear 14 and the output gear 122 of the starting gear pair 12, wherein, because no power flows into the input gear 22 at the time, and the input end 91 of the fixed one-way clutch 9 is connected with a fixed element, the function of limiting the rotation direction is realized, the input gear 22 can not rotate in the opposite rotation direction of the engine, the rotating speed is zero, at the time, the power transmitted to the input pinion 23 is transmitted to the output duplex carrier 21 through the planetary gear 20 on the output duplex carrier 21, the output double planet carrier 21 transmits power to the input big gear 24 through the coupling gear pair 4, the input big gear 24 splits the power into two paths through the planet gear 20 on the output planet carrier 25, one path is transmitted to the output planet carrier 25, the other path is transmitted to the output small gear 26, because the output shaft 3 is still, namely the output planet carrier 25 is still, the power of the starter completely flows into the output small gear 26 and then is transmitted to the input planet carrier 27, the input planet carrier 27 splits the power into two paths through the planet gear 20 on the input planet carrier 27, one path is transmitted to the output big gear ring 28, the other path is transmitted to the output small gear ring 29, because the output shaft 3 is still, namely the output small gear ring 29 is still, the power completely flows into the output big gear ring 28, the output big gear ring 28 flows into the input end 81 of the speed change mechanism 8, the output end 82 of the speed change mechanism 8 splits the power into two paths, one path flows into the input gear 22 through the input gear pair 10, the other path flows into the input end 111 of the double-chamber fluid coupling 11, the output end 112 of the double-chamber fluid coupling 11 flows into the input pinion 23 through the starting gear pair 12, the power transmitted to the input pinion 23 is merged with the power transmitted to the input pinion 23 by the starter or the engine, the power flowing into the input gear 22 is transmitted to the output double planet carrier 21 through the planet gears 20 on the output double planet carrier 21, the output double planet carrier 21 repeats the above process, and repeated cycles of moment division, moment conversion and moment combination are continuously performed among the elements, so that the moment transmitted to the output planet carrier 25 and the output small ring gear 29 is continuously increased, the power transmitted to the output planet carrier 25 and the power transmitted to the output planet carrier 25 through the output small ring gear 29 are all transmitted through the output gear pair 6, The input 71 of the neutral gear mechanism 7, the one-way clutch 5 and the input shaft 1 are transmitted to the engine crankshaft, and the engine is started and starts to accelerate when the starting force generated by the torque transmitted to the engine crankshaft is sufficient to overcome the starting resistance of the engine.
After the engine is started, the input power, the input rotating speed and the load of the engine are unchanged, namely the rotating speed and the torque of the input shaft 1 are constant, before the automobile starts, the idle gear mechanism 7 is engaged, the rotating speed of the output shaft 3 is zero, the input power of the engine is transmitted to the input pinion 23 through the input shaft 1 and the overrunning clutch 13, wherein, because no power flows into the input gear 22 at the moment, the input end 91 of the fixed one-way clutch 9 is connected with a fixed element to play a role of limiting the steering, the input gear 22 cannot rotate in the direction opposite to the engine, the rotating speed is zero, at the moment, the power transmitted to the input pinion 23 is transmitted to the output duplex planet carrier 21 through the planet gear 20 on the output duplex planet carrier 21, the output duplex planet carrier 21 transmits the power to the input gearwheel 24 through the gear coupling pair 4, the input gearwheel 24 divides the power into two paths through the planet gear 20 on the output planet carrier 25, one path is transmitted to the output planet carrier 25, the other path is transmitted to the output pinion 26, because the output shaft 3 is still, namely the output planet carrier 25 is still, the power of the starter completely flows into the output pinion 26, and then is transmitted to the input planet carrier 27, the input planet carrier 27 divides the power into two paths through the planet gears 20 on the input planet carrier, one path is transmitted to the output large ring gear 28, the other path is transmitted to the output small ring gear 29, because the output shaft 3 is still, namely the output small ring gear 29 is still, the power completely flows into the output large ring gear 28, the output large ring gear 28 further flows into the input end 81 of the speed change mechanism 8, the output end 82 of the speed change mechanism 8 divides the power into two paths, one path flows into the input gear 22 through the input gear pair 10, the other path flows into the input end 111 of the double-cavity hydraulic coupler 11, the output end 112 of the double-cavity hydraulic coupler 11 further flows into the, the power transmitted to the input pinion 23 is combined with the power transmitted to the input pinion 23 by the starter or the engine, and is combined with the power flowing into the input gear 22, and the power is transmitted to the output double planet carrier 21 through the planet gears 20 on the output double planet carrier 21, the output double planet carrier 21 repeats the processes, and the repeated circulation of torque splitting, torque converting and torque combining is continuously carried out among all elements, so that the torque transmitted to the output planet carrier 25 and the output small ring gear 29 is continuously increased, the power transmitted to the output planet carrier 25 and the power transmitted to the output planet carrier 25 through the output small ring gear 29 are transmitted to the output shaft 3 of the invention through the output gear pair 6 and the idle gear mechanism 7, when the torque transmitted to the output shaft 3 generates traction force which is transmitted to the driving wheels through the transmission system and is enough to overcome the starting resistance of the automobile, the vehicle starts to accelerate, and the rotational speed of the output carrier 25, the output ring gear 29 and the output shaft 3 connected thereto also gradually increases from zero, at which time the power flowing into the input gear 22 gradually decreases, so that the torque of the output shaft 3 decreases with increasing rotational speed.
Claims (1)
1. The utility model provides a compound two-chamber hydraulic coupling and starter, includes input shaft (1), output shaft (3), coupling gear pair (4), one-way clutch (5), output gear pair (6), neutral gear mechanism (7), speed change mechanism (8), fixed one-way clutch (9), input gear pair (10), two-chamber hydraulic coupling (11), starting gear pair (12), freewheel clutch (13), starting gear (14), input (91) and the fixed component hookup of fixed one-way clutch (9), its characterized in that: a planetary gear (20), an output duplex planet carrier (21), an input gear (22), an input pinion (23), an input big gear (24), an output planet carrier (25), an output pinion (26), an input planet carrier (27), an output big gear ring (28) and an output small gear ring (29) are arranged between the input shaft (1) and the output shaft (3), the input pinion (23) is connected with an output gear (122) of the starting gear pair (12) and an output end (132) of the overrunning clutch (13), an input end (131) of the overrunning clutch (13) is connected with the input shaft (1), the input pinion (23) is mutually matched with the output duplex planet carrier (21) and the input gear (22) through the planetary gear (20) on the output duplex planet carrier (21), the output duplex planet carrier (21) is connected with an input gear (41) of the connecting gear pair (4), an output gear (42) of a connecting gear pair (4) is connected with an input large gear (24), the input large gear (24) is mutually matched with an output planet carrier (25) and an output small gear (26) through a planetary gear (20) on the output planet carrier (25), the output small gear (26) is connected with an input planet carrier (27), the input planet carrier (27) is mutually matched with an output large gear ring (28) and an output small gear ring (29) through the planetary gear (20) on the input planet carrier, the output small gear ring (29) and an input gear (61) of an output gear pair (6) are connected with the output planet carrier (25), an output gear (62) of the output gear pair (6) and an input end (51) of a one-way clutch (5) are connected with an input end (71) of a neutral gear engaging mechanism (7), and an output end (52) of the one-way clutch (5) is connected with an input shaft (1), an output end (72) of the idle gear mechanism (7) is connected with an output shaft (3), an output large gear ring (28) is connected with an input end (81) of a speed change mechanism (8), an output end (82) of the speed change mechanism (8) is connected with an output end (92) of a fixed one-way clutch (9), an input gear (101) of an input gear pair (10) and an input end (111) of a double-cavity hydraulic coupler (11), an output gear (102) of the input gear pair (10) is connected with an input gear (22), an output end (112) of the double-cavity hydraulic coupler (11) is connected with an input gear (121) of a starting gear pair (12), and an output gear (122) of the starting gear pair (12) is connected with a starting gear (14).
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410759502.2A CN104633040A (en) | 2014-12-12 | 2014-12-12 | A composite double-cavity hydraulic coupling and starter |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| HK1211655A1 true HK1211655A1 (en) | 2016-05-27 |
Family
ID=53212124
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| HK15110170.4A HK1211655A1 (en) | 2014-12-12 | 2015-10-16 | A composite type double cavity of hydraulic coupler and starter |
Country Status (2)
| Country | Link |
|---|---|
| CN (2) | CN104633040A (en) |
| HK (1) | HK1211655A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105134904A (en) * | 2015-07-07 | 2015-12-09 | 吴志强 | Compound type dual-cavity fluid coupling and actuator |
| CN104976304A (en) * | 2015-07-07 | 2015-10-14 | 吴志强 | Compound type hydraulic special-shaped coupler and starter |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB837641A (en) * | 1957-09-16 | 1960-06-15 | Hans Thoma | Hydraulic drive with coupling |
| US4430908A (en) * | 1981-09-08 | 1984-02-14 | Ford Motor Company | Split path electric vehicle powertrain |
| WO1989009899A1 (en) * | 1988-04-06 | 1989-10-19 | Zahnradfabrik Friedrichshafen Ag | Hydrostatic-mecanical power-distribution gearbox |
| DE19527754A1 (en) * | 1994-08-30 | 1996-03-07 | Steyr Daimler Puch Ag | Hydrostatic transmission with summating gear and synchro=engagement point |
| EP0975903B1 (en) * | 1997-04-25 | 2002-01-02 | General Dynamics Land Systems, Inc. | Multi- range hydromechanical transmission |
| CN101012871A (en) * | 2007-02-02 | 2007-08-08 | 吴志强 | Coupler |
| CN101457817A (en) * | 2007-12-12 | 2009-06-17 | 吴志强 | Speed reducing mechanism for starter |
| CN103148181B (en) * | 2008-06-06 | 2015-07-29 | 吴志强 | A kind of multi-gear simultaneous meshing variable speed unit |
| JP2010083230A (en) * | 2008-09-30 | 2010-04-15 | Aisin Seiki Co Ltd | Hybrid drive device |
| CN102022514B (en) * | 2009-09-09 | 2014-05-07 | 吴志强 | Composite axial-flow hydrotransmitter |
| CN102312982B (en) * | 2010-07-07 | 2015-07-08 | 吴志强 | Composite torque limiting water medium hydraulic coupler |
| CN103939562B (en) * | 2010-07-07 | 2016-04-13 | 吴志强 | A kind of compound rear auxiliary room prolonged type load limiting type of constant filling fluid coupling |
| CN102312938B (en) * | 2010-07-07 | 2015-07-08 | 吴志强 | Composite box grind type hydraulic coupler |
-
2014
- 2014-12-12 CN CN201410759502.2A patent/CN104633040A/en active Pending
- 2014-12-12 CN CN201610692786.7A patent/CN106122425A/en not_active Withdrawn
-
2015
- 2015-10-16 HK HK15110170.4A patent/HK1211655A1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| CN106122425A (en) | 2016-11-16 |
| CN104633040A (en) | 2015-05-20 |
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