HK1211653A1 - A composite type variable speed hydraulic coupler and starter - Google Patents
A composite type variable speed hydraulic coupler and starter Download PDFInfo
- Publication number
- HK1211653A1 HK1211653A1 HK15110168.8A HK15110168A HK1211653A1 HK 1211653 A1 HK1211653 A1 HK 1211653A1 HK 15110168 A HK15110168 A HK 15110168A HK 1211653 A1 HK1211653 A1 HK 1211653A1
- Authority
- HK
- Hong Kong
- Prior art keywords
- gear
- output
- 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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
- F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
- F02N15/022—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch
- F02N15/023—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch of the overrunning type
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structure Of Transmissions (AREA)
- Retarders (AREA)
Abstract
The invention provides a combined variable speed fluid coupling and starter. According to the technical scheme, the combined variable speed fluid coupling and starter is characterized in that an input gear (23) is connected with a starting gear pair (11) and an overrunning clutch (12), an output gear ring (22) is connected with an input planet carrier (26), a big output gear ring (24) is connected with an input gear (51), an output gear (52) is connected with a big input gear (28), an output duplex planet carrier (29) is connected with an output gear pair (6), a small output gear (27) is connected with a speed changing mechanism (7), the speed changing mechanism (7) is connected with an input gear pair (9) and a variable speed fluid coupling (10), the variable speed fluid coupling (10) is connected with the starting gear pair (11), and the input gear pair (9) is connected with an input planet carrier (21).
Description
Technical Field
The invention belongs to the field of hydraulic couplers and starting, and particularly relates to a combined type speed-regulating 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 speed-regulating type hydraulic coupler and the starter which have the advantages of prolonged service life of the engine, 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 combined speed-regulating hydraulic coupler and a starter comprise an input shaft (1), an output shaft (3), a one-way clutch (4), a coupling gear pair (5), an output gear pair (6), a speed change mechanism (7), a fixed one-way clutch (8), an input gear pair (9), a speed-regulating hydraulic coupler (10), a starting gear pair (11), an overrunning clutch (12), a starting gear (13) and an idle gear engaging mechanism (14), wherein an input end (81) of the fixed one-way clutch (8) is coupled with a fixed element, and a planetary gear (20), an input planetary carrier (21), an output gear ring (22), an input gear (23), an output large gear ring (24), an output small gear ring (25), an input planetary carrier (26), an output small gear (27), an input large gear (28) are arranged between the input shaft (1) and the output shaft (3), An output double planet carrier (29), an input gear (23) is connected with an output gear (112) of a starting gear pair (11) and an output end (122) of an overrunning clutch (12), an input end (121) of the overrunning clutch (12) and an output end (42) of a one-way clutch (4) are connected with an input shaft (1), the input gear (23) is mutually matched with an input planet carrier (21) and an output gear ring (22) through a planet gear (20) on the input planet carrier (21), the output gear ring (22) is connected with an input planet carrier (26), the input planet carrier (26) is mutually matched with an output large gear ring (24) and an output small gear ring (25) through a planet gear (20) on the input planet carrier, the output large gear ring (24) is connected with an input gear (51) of a gear connecting gear pair (5), an output gear (52) of the connecting gear pair (5) is connected with an input large gear (28), the input big gear (28) is matched with the output small gear (27) and the output duplex planet carrier (29) through the planet gear (20) on the output duplex planet carrier (29), the output duplex planet carrier (29) is connected with the input gear (61) of the output gear pair (6), the output gear (62) of the output gear pair (6), the output small gear ring (25) and the input end (41) of the one-way clutch (4) are connected with the input end (141) of the idle gear mechanism (14), the output end (142) of the idle gear mechanism (14) is connected with the output shaft (3), the output small gear (27) is connected with the input end (71) of the speed change mechanism (7), the output end (72) of the speed change mechanism (7) is connected with the output end (82) of the fixed one-way clutch (8), the input gear (91) of the input gear pair (9) and the input end (101) of the speed regulation type hydraulic coupling (10), an output end (102) of the speed-regulating type hydraulic coupler (10) is connected with an input gear (111) of a starting gear pair (11), an output gear (112) of the starting gear pair (11) is connected with a starting gear (13), and an output gear (92) of an input gear pair (9) is connected with an input planet carrier (21).
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 speed-regulating type 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 variable speed fluid coupling and a starter used for various land vehicles, ships, railroad 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 compound speed-regulating type hydraulic coupling and starter comprises an input shaft 1, an output shaft 3, a one-way clutch 4, a coupling gear pair 5, an output gear pair 6, a speed change mechanism 7, a fixed one-way clutch 8, an input gear pair 9, a speed-regulating type hydraulic coupling 10, a starting gear pair 11, an overrunning clutch 12, a starting gear 13 and a neutral gear mechanism 14, wherein an input end 81 of the fixed one-way clutch 8 is coupled with a fixed element, a planetary gear 20, an input planet carrier 21, an output ring gear 22, an input gear 23, an output large ring gear 24, an output small ring gear 25, an input planet carrier 26, an output pinion 27, an input large gear 28 and an output duplex planet carrier 29 are arranged between the input shaft 1 and the output shaft 3, the input gear 23 is coupled with an output gear 112 of the starting gear pair 11 and an output end 122 of the overrunning clutch 12, the input end 121 of the overrunning clutch 12 and the output end 42 of the one-way clutch 4 are connected with the input shaft 1, the input gear 23 is mutually matched with the input planet carrier 21 and the output gear ring 22 through the planet gear 20 on the input planet carrier 21, the output gear ring 22 is connected with the input planet carrier 26, the input planet carrier 26 is mutually matched with the output large gear ring 24 and the output small gear ring 25 through the planet gear 20 on the input planet carrier, the output large gear ring 24 is connected with the input gear 51 of the coupling gear pair 5, the output gear 52 of the coupling gear pair 5 is connected with the input large gear 28, the input large gear 28 is mutually matched with the output small gear 27 and the output double planet carrier 29 through the planet gear 20 on the output double planet carrier 29, the output double planet carrier 29 is connected with the input gear 61 of the output gear pair 6, the output gear 62 of the output gear pair 6, the output small gear ring 25 and the input end 41 of the one-way clutch 4 are connected with the input end, the output 142 of the neutral gear mechanism 14 is coupled to the output shaft 3, the output pinion 27 is coupled to the input 71 of the speed change mechanism 7, the output 72 of the speed change mechanism 7 is coupled to the output 82 of the fixed one-way clutch 8, the input gear 91 of the input gear pair 9, and the input 101 of the variable speed fluid coupling 10, the output 102 of the variable speed fluid coupling 10 is coupled to the input gear 111 of the starting gear pair 11, the output gear 112 of the starting gear pair 11 is coupled to the starting gear 13, and the output gear 92 of the input gear pair 9 is coupled to the input carrier 21.
The input planet carrier 26 divides the power transmitted to the input planet carrier into two paths through the planet gears 20 on the input planet carrier, wherein one path flows into the output small gear ring 25, the other path passes through the output large gear ring 24 and the connecting gear pair 5 and is transmitted to the input large gear 28, the input large gear 28 divides the power transmitted to the input planet carrier into two paths through the planet gears 20 on the output duplex planet carrier 29, one path flows into the output small gear 27, and the other path flows into the output duplex planet carrier 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 small gear ring 25 and the output double planet carrier 29 are zero, the output power is zero, but the moment is not zero, at this time, the input power of the output small gear ring 25 and the output double planet carrier 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 a planetary row torque ratio when the rotating speeds of the output small gear ring 25 and the output double planet carrier 29 are the same as the rotating speeds of the input planet carrier 26 and the input large gear 28 which are matched with each other, the maximum value refers to the total power input by the input carrier 26, the input gearwheel 28, that is, when the two paths of power change, the torque transmitted to the output small gear ring 25, the output double planet carrier 29 and the output shaft 3 also changes.
The input power of the starter is transmitted from the starting gear 13 to the input gear 23 through the output gear 112 of the starting gear pair 11 or the input power of the engine through the input shaft 1 and then the overrunning clutch 12, and the power is transmitted to the output gear ring 22 through the planetary gear 20 on the input planet carrier 21, the output gear ring 22 transmits the power to the input planet carrier 26, the input planet carrier 26 divides the power into two paths through the planetary gear 20 on the input planet carrier, one path flows into the output small gear ring 25, the other path flows into the output large gear ring 24 and then flows into the input large gear 28 through the coupling gear pair 5, the input large gear 28 divides the power into two paths through the planetary gear 20 on the output double-coupling planet carrier 29, one path flows into the output double-coupling planet carrier 29, the other path flows into the input end 71 of the speed change mechanism 7 through the output small gear 27, and the output end 72 of the speed change mechanism 7 divides the, one path flows into the input planet carrier 21 through the input gear pair 9, the other path flows into the input gear 111 of the starting gear pair 11 through the speed-regulating type hydraulic coupling 10, then flows into the input gear 23 through the output gear 112 of the starting gear pair 11, the power transmitted to the input gear 23 is merged with the power transmitted to the input gear 23 by the starter or the engine, and is transmitted to the output gear ring 22 through the planet gear 20 on the input planet carrier 21, the output gear ring 22 repeats the process, so that the torque transmitted to the output small gear ring 25 and the output double-connection planet carrier 29 is continuously increased, before the engine is started, the power transmitted to the output small gear ring 25 and the power transmitted to the output gear pair 6 through the output double-connection planet carrier 29 are transmitted to the engine crankshaft through the input end 141 of the idle gear mechanism 14, the one-way clutch 4 and the input shaft 1, after the engine is started, the neutral gear mechanism 14 is engaged, and the power transmitted to the output small ring gear 25 and the power transmitted to the output gear pair 6 by the output double carrier 29 are transmitted to the output shaft 3 of the invention through the neutral gear mechanism 14, so that the power of the engine is output to the outside through the output shaft 3.
According to the invention, when the rotating speed of the input shaft 1 is unchanged, the torques on the output small gear ring 25, the output double-planet carrier 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 small gear ring 25, the output double-planet carrier 29 and the output shaft 3 is, and the smaller the torque is on the contrary, so that the combined speed-regulating 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 13 are constant, namely the rotating speed and the torque of the output planet carrier 21 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 small gear ring 25 and the output double-coupling planet carrier 29 are still, the input power of the starter is transmitted to the output planet carrier 21 through the starting gear pair 11, wherein, because no power flows into the input planet carrier 21 at the moment, and the input end 81 of the fixed one-way clutch 8 is connected with a fixed element, the effect of limiting the rotation direction is realized, the input planet carrier 21 can not rotate in the opposite rotation direction of the engine, the rotating speed is zero, at the moment, the power transmitted to the input gear 23 is transmitted to the output ring gear 22 through the planet gear 20 on the input planet carrier 21, the output ring gear 22 transmits the power to the input, the input carrier 26 splits the power into two paths through the planetary gears 20 thereon, one path flows into the output small gear ring 25, the other path flows into the output large gear ring 24, and then flows into the input large gear 28 through the coupling gear pair 5, the input large gear 28 splits the power into two paths through the planetary gears 20 on the output double carrier 29, one path flows into the output double carrier 29, the other path flows into the input end 71 of the speed change mechanism 7 through the output small gear 27, the output end 72 of the speed change mechanism 7 splits the power into two paths, one path flows into the input carrier 21 through the input gear pair 9, the other path flows into the input gear 111 of the starting gear pair 11 through the speed-adjusting type fluid coupling 10, then flows into the input gear 23 through the output gear 112 of the starting gear pair 11, the power transmitted to the input gear 23 is combined with the power transmitted to the input gear 23 by the starter or the engine, the power flowing into the input planet carrier 21 is transmitted to the output gear ring 22 through the planet gears 20 on the input planet carrier 21, the output gear ring 22 repeats the process again, so that the torque transmitted to the output small gear ring 25 and the output double-connection planet carrier 29 is continuously increased, the power transmitted to the output small gear ring 25 and the power transmitted to the output gear pair 6 by the output double-connection planet carrier 29 are transmitted to the crankshaft of the engine through the input end 141 of the idle gear mechanism 14 and then through the one-way clutch 4 and the input shaft 1, and when the starting force generated by the torque transmitted to the crankshaft of the engine is enough to overcome the starting resistance of the engine, the engine is started and starts to accelerate.
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 14 is engaged, the rotating speed of the output shaft 3 is zero, the input power of the engine is transmitted to the input gear 23 through the input shaft 1 and the overrunning clutch 12, wherein, because no power flows into the input planet carrier 21 at the moment, the input end 81 of the fixed one-way clutch 8 is connected with a fixed element to play a role of limiting the steering, the input planet carrier 21 can not rotate in the opposite direction of the engine, the rotating speed is zero, at the moment, the power transmitted to the input gear 23 is transmitted to the output ring gear 22 through the planet gear 20 on the input planet carrier 21, the output ring gear 22 transmits the power to the input planet carrier 26, and the input planet carrier 26 divides the power into two paths through the planet gear 20 on the input planet carrier 26, one path flows into the output small gear ring 25, the other path flows into the output large gear ring 24, then flows into the input large gear 28 through the coupling gear pair 5, the input large gear 28 splits the power into two paths through the planetary gears 20 on the output double planetary carrier 29, one path flows into the output double planetary carrier 29, the other path flows into the input end 71 of the speed change mechanism 7 through the output small gear 27, the output end 72 of the speed change mechanism 7 splits the power into two paths, one path flows into the input planetary carrier 21 through the input gear pair 9, the other path flows into the input gear 111 of the starting gear pair 11 through the speed-adjusting type hydraulic coupling 10, then flows into the input gear 23 through the output gear 112 of the starting gear pair 11, the power transmitted to the input gear 23 is merged with the power transmitted to the input gear 23 by the starter or the engine, and the power transmitted to the output gear ring 22 through the planetary gears 20 on the input planetary carrier 21, the output gear ring 22 repeats the above process again, so that the torque transmitted to the output small gear ring 25 and the output double-link planet carrier 29 is continuously increased, the power transmitted to the output small gear ring 25 and the power transmitted to the output gear pair 6 by the output double-link planet carrier 29 are transmitted to the output shaft 3 of the invention through the idle gear mechanism 14, when the torque transmitted to the output shaft 3 and the traction force generated by the transmission to the driving wheels through the transmission system are enough to overcome the starting resistance of the automobile, the automobile starts and starts to accelerate, the rotating speeds of the output small gear ring 25, the output double-link planet carrier 29 and the output shaft 3 which are connected with the automobile are also gradually increased from zero, at the moment, the power flowing into the input planet carrier 21 is gradually reduced, and the torque of the output shaft 3 is reduced along with the increase of the rotating speed.
Claims (1)
1. The utility model provides a combined type speed governing type fluid coupling and starter, includes input shaft (1), output shaft (3), one way clutch (4), coupling gear pair (5), output gear pair (6), speed change mechanism (7), fixed one way clutch (8), input gear pair (9), speed governing type fluid coupling (10), starting gear pair (11), freewheel clutch (12), starting gear (13), empty gear engaging mechanism (14), input (81) and the fixed component hookup of fixed one way clutch (8), its characterized in that: a planetary gear (20), an input planetary carrier (21), an output gear ring (22), an input gear (23), an output large gear ring (24), an output small gear ring (25), an input planetary carrier (26), an output small gear (27), an input large gear (28) and an output double planetary carrier (29) are arranged between the input shaft (1) and the output shaft (3), the input gear (23) is connected with an output gear (112) of a starting gear pair (11) and an output end (122) of an overrunning clutch (12), an input end (121) of the overrunning clutch (12) and an output end (42) of a one-way clutch (4) are connected with the input shaft (1), the input gear (23) is mutually matched with the input planetary carrier (21) and the output gear ring (22) through the planetary gear (20) on the input planetary carrier (21), and the output gear ring (22) is connected with the input planetary carrier (26), the input planet carrier (26) is mutually matched with an output large gear ring (24) and an output small gear ring (25) through a planet gear (20) on the input planet carrier, the output large gear ring (24) is connected with an input gear (51) of a connecting gear pair (5), an output gear (52) of the connecting gear pair (5) is connected with an input large gear (28), the input large gear (28) is mutually matched with an output small gear (27) and an output duplex planet carrier (29) through a planet gear (20) on an output duplex planet carrier (29), the output duplex planet carrier (29) is connected with an input gear (61) of an output gear pair (6), an output gear (62) of the output gear pair (6), the output small gear ring (25) and an input end (41) of a one-way clutch (4) are connected with an input end (141) of an idle gear mechanism (14), and an output end (142) of the idle gear mechanism (14) is connected with an output shaft (3), the output pinion (27) is connected with the input end (71) of the speed change mechanism (7), the output end (72) of the speed change mechanism (7) is connected with the output end (82) of the fixed one-way clutch (8), the input gear (91) of the input gear pair (9) and the input end (101) of the speed-regulating type hydraulic coupling (10), the output end (102) of the speed-regulating type hydraulic coupling (10) is connected with the input gear (111) of the starting gear pair (11), the output gear (112) of the starting gear pair (11) is connected with the starting gear (13), and the output gear (92) of the input gear pair (9) is connected with the input planet carrier (21).
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410759503.7A CN104534054A (en) | 2014-12-12 | 2014-12-12 | A composite speed-regulating hydraulic coupling and starter |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| HK1211653A1 true HK1211653A1 (en) | 2016-05-27 |
Family
ID=52849641
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| HK15110168.8A HK1211653A1 (en) | 2014-12-12 | 2015-10-16 | A composite type variable speed hydraulic coupler and starter |
Country Status (2)
| Country | Link |
|---|---|
| CN (2) | CN104534054A (en) |
| HK (1) | HK1211653A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105003608A (en) * | 2015-07-07 | 2015-10-28 | 吴志强 | Compound variable speed fluid coupling and starter |
| CN105042013A (en) * | 2015-07-07 | 2015-11-11 | 吴志强 | Compound box grinding type hydraulic coupler and starter |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB624858A (en) * | 1942-01-09 | 1949-06-17 | Borg Warner | Improvements in or relating to variable-speed transmissions and control mechanisms therefor |
| WO1999045296A1 (en) * | 1998-03-06 | 1999-09-10 | Voith Turbo Gmbh & Co. Kg | Hydrodynamic-mechanical multi-speed compound transmission, especially a six-speed torque-converter transmission |
| RU2192572C1 (en) * | 2001-08-17 | 2002-11-10 | Коротков Эдуард Константинович | Universal holonomic drive with stepless change of torque (versions) |
| JP2004353685A (en) * | 2003-05-27 | 2004-12-16 | Komatsu Ltd | Hydraulic mechanical transmission |
| CN101012870A (en) * | 2007-02-02 | 2007-08-08 | 吴志强 | Torque convertor |
| DE102007047193A1 (en) * | 2007-10-02 | 2009-04-09 | Zf Friedrichshafen Ag | Adjustment of the stroke volume of hydraulic piston machines |
| CN102312976B (en) * | 2010-07-07 | 2015-09-02 | 吴志强 | A kind of composite constant charge type hydraulic coupler |
| CN102062193B (en) * | 2010-07-07 | 2013-01-23 | 吴志强 | Composite variable speed fluid coupling |
| CN102358159B (en) * | 2011-08-05 | 2013-12-18 | 上海中科深江电动车辆有限公司 | Hybrid drive system with hydraulic torque converter |
-
2014
- 2014-12-12 CN CN201410759503.7A patent/CN104534054A/en active Pending
- 2014-12-12 CN CN201610692787.1A patent/CN106286758A/en not_active Withdrawn
-
2015
- 2015-10-16 HK HK15110168.8A patent/HK1211653A1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| CN106286758A (en) | 2017-01-04 |
| CN104534054A (en) | 2015-04-22 |
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