HK1211662A1 - A compound leaf wheel type hydraulic torque converte - Google Patents
A compound leaf wheel type hydraulic torque converteInfo
- Publication number
- HK1211662A1 HK1211662A1 HK15111098.1A HK15111098A HK1211662A1 HK 1211662 A1 HK1211662 A1 HK 1211662A1 HK 15111098 A HK15111098 A HK 15111098A HK 1211662 A1 HK1211662 A1 HK 1211662A1
- Authority
- HK
- Hong Kong
- Prior art keywords
- gear
- input
- output
- planet carrier
- ring
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Retarders (AREA)
Abstract
A composite impeller-type hydraulic torque converter. A large output gear ring (22) is connected to a connection input gear pair (6). The connection input gear pair (6) is connected to a connection gear ring (25). An output planet carrier (24) is connected to a connection output gear (5). The connection output gear (5) is connected to an input gear ring (28). An input planet carrier (27) is connected to an input gear pair (4). An input gear (26), an input gear pair (4) and an overrun clutch (7) are connected to an impeller-type hydraulic torque converter (8). The impeller-type hydraulic torque converter (8) is connected to an output gear pair (9). The output gear pair (9) and an input pinion (21) are connected to an input shaft (1). An output gear ring (29) is connected to an output shaft (3). In addition, further provided is a continuously variable transmission of a composite impeller-type hydraulic torque converter.
Description
Technical Field
The invention belongs to the field of hydraulic torque converters and speed change, and particularly relates to a composite impeller type hydraulic torque converter and a continuously variable transmission for various ground vehicles, ships, railway locomotives and machine tools.
Background
At present, hydraulic torque converters are designed according to the principles of fluid statics and the like, and have low transmitted power and low efficiency; in addition, the cost is high.
Disclosure of Invention
The invention overcomes the defects of the prior art and provides the composite impeller type hydraulic torque converter and the continuously variable transmission 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 composite impeller type hydraulic torque converter comprises an input shaft (1), an output shaft (3), an input gear pair (4), a connection output gear (5), a connection input gear pair (6), an overrunning clutch (7), an impeller type hydraulic torque converter (8) and an output gear pair (9), wherein a planetary gear (20), an input small gear ring (21), an output large gear ring (22), a fixed planet carrier (23), an output planet carrier (24), a connection gear ring (25), an input gear (26), an input planet carrier (27), an input ring gear (28) and an output ring gear (29) are arranged between the input shaft (1) and the output shaft (3), the input small gear ring (21) is matched with the output large gear ring (22) and the fixed planet carrier (23) through the planetary gear (20) on the fixed planet carrier (23), the input end (71) of the fixed planet carrier (23) and the overrunning clutch (7) is connected with a fixed element, the large output gear ring (22) is connected with an input gear (61) connected with the input gear pair (6), an output gear (62) connected with the input gear pair (6) is connected with a connecting gear ring (25), the connecting gear ring (25) is matched with an output planet carrier (24) and an input gear (26) through a planetary gear (20) on the output planet carrier (24), the output planet carrier (24) is connected with an input gear (51) connected with the output gear (5), an output gear (52) connected with the output gear (5) is connected with an input gear ring (28), the input gear ring (28) is matched with an input planet carrier (27) and an output gear ring (29) through a planetary gear (20) on the input planet carrier (27), the input planet carrier (27) is connected with an output gear (42) of the input gear pair (4), the input gear (26), an input gear (41) of the input gear pair (4) and an output end (72) of an overrunning clutch (7) are connected with an impeller The output end (82) of the impeller type hydraulic torque converter (8) is connected, the input end (81) of the impeller type hydraulic torque converter (8) is connected with the output gear (92) of the output gear pair (9), the input gear (91) and the input pinion (21) of the output gear pair (9) are connected with the input shaft (1), and the output gear ring (29) is connected with the output shaft (3).
A continuously variable transmission of a composite impeller type hydraulic torque converter comprises an input shaft (1), an output shaft (3), a coupling gear pair (4), an input coupling gear pair (5), a coupling input gear pair (6), an output coupling gear pair (7), a coupling output gear pair (8), an overrunning clutch (9), an impeller type hydraulic torque converter (10) and an output gear pair (11), wherein a planetary gear (20), an input gear (21), an output planet carrier (22), a fixed gear (23), a coupling gear (24), an input planet carrier (25), an output large gear (26), a coupling planet carrier (27), an input gear ring (28), an output gear ring (29), a coupling input planet carrier (30), an output large gear ring (31) and an input small gear (32) are arranged between the input shaft (1) and the output shaft (3), and the input gear (21) and the output planet carrier (22) through the planetary gear (20) on the output planet carrier (22), The fixed gear (23) cooperates and works, the input end (91) of the fixed gear (23) and overrunning clutch (9) is connected with the fixed element, the output planet carrier (22) 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 planet carrier (25), the input planet carrier (25) cooperates and works with the connecting gear (24) and the output big gear (26) through the planetary gear (20) on the input planet carrier (25), the output big gear (26) is connected with the input gear (81) of the connecting output gear pair (8), the output gear (82) of the connecting output gear pair (8) is connected with the input gear ring (28), the input gear ring (28) cooperates and works with the connecting planet carrier (27) and the output gear ring (29) through the planetary gear (20) on the connecting planet carrier (27), the output gear ring (29) is connected with the input gear (61) of the connecting input gear pair (6), an output gear (62) connected with an input gear pair (6) is connected with an input pinion (32), the input pinion (32) is matched with a connected input planet carrier (30) and an output large gear ring (31) through a planet gear (20) connected with the input planet carrier (30), the output large gear ring (31) is connected with an output shaft (3), the connected input planet carrier (30) is connected with an output gear (52) of an input connected gear pair (5), an input gear (21), an input gear (51) of the input connected gear pair (5) and an input gear (111) of an output gear pair (11) are connected with an input shaft (1), an output gear (112) of the output gear pair (11) is connected with an input end (101) of a vane type hydraulic torque converter (10), a connecting gear (24), an input gear (71) of an output connected gear pair (7) and an output end (92) of an overrunning clutch (9) are connected with an output end (92) of the vane type hydraulic torque converter (10) The output end (102) is connected, and the output gear (72) of the output connecting gear pair (7) is connected with the connecting planet carrier (27).
The elements to be connected can be directly connected, and when the elements are separated by other elements, the elements can be connected with the elements by passing through or across the other elements by adopting a connecting shaft, a hollow or a connecting frame; when the coupled elements are gears or ring gears, they are meshed or coupled with each other; the components which do not need to be connected can rotate relatively.
The transmission ratios of the gear pairs and the speed change mechanism are designed according to actual requirements.
The hydraulic torque converter can be selected from a hydraulic coupler, a pressure motor, a hydraulic pump and an electromagnetic clutch.
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.
The present invention also relates to a composite impeller type torque converter and a continuously variable transmission used for various land vehicles, ships, railroad locomotives, and machine tools.
Drawings
Description fig. 1 is a structural diagram of a first embodiment of the present invention; description fig. 2 is a structural diagram of a second embodiment of the present invention; in the drawings, the joint between two elements is represented by a thick solid line for fixed connection, and a thin solid line for relative rotation.
Detailed Description
The invention will be described in further detail with reference to the following description and accompanying drawings:
the first embodiment is as follows:
as shown in fig. 1, a composite impeller type hydraulic torque converter comprises an input shaft 1, an output shaft 3, an input gear pair 4, a coupling output gear 5, a coupling input gear pair 6, an overrunning clutch 7, an impeller type hydraulic torque converter 8 and an output gear pair 9, wherein a planetary gear 20, an input small gear ring 21, an output large gear ring 22, a fixed planet carrier 23, an output planet carrier 24, a coupling gear ring 25, an input gear 26, an input planet carrier 27, an input gear ring 28 and an output gear ring 29 are arranged between the input shaft 1 and the output shaft 3, the input small gear ring 21 is matched with the output large gear ring 22 and the fixed planet carrier 23 through the planetary gear 20 on the fixed planet carrier 23, the input end 71 of the fixed planet carrier 23 and the overrunning clutch 7 is coupled with a fixed element, the output large gear ring 22 is coupled with an input gear 61 coupled with the input gear pair 6, an output gear 62 coupled with the input gear pair 25, the coupling ring gear 25 cooperates with the output carrier 24, the input gear 26 via the planet gears 20 on the output carrier 24, the output carrier 24 is coupled with the input gear 51 coupled with the output gear 5, the output gear 52 coupled with the output gear 5 is coupled with the input ring gear 28, the input ring gear 28 is coupled with the input carrier 27 via the planet gears 20 on the input carrier 27, the output ring gear 29 is engaged, the input carrier 27 is coupled to the output gear 42 of the input gear pair 4, the input gear 26, the input gear 41 of the input gear pair 4, and the output 72 of the overrunning clutch 7 are coupled to the output 82 of the impeller torque converter 8, the input 81 of the impeller torque converter 8 is coupled to the output gear 92 of the output gear pair 9, the input gear 91 of the output gear pair 9 and the input pinion 21 are coupled to the input shaft 1, and the output ring gear 29 is coupled to the output shaft 3.
The coupling ring gear 25, the input gear 26, the output carrier 24, the input ring gear 28, the input carrier 27, the input ring gear 28, the planet gears 20 on the input carrier 27, and the output carrier 29.
Since the distribution of the rotational speeds of the above-mentioned components can be changed, the two power flows will change according to the change of the rotational speed distribution between the two, when the rotational speeds of the input gear 26 and the input carrier 27 are zero, the coupling ring gear 25 and the input ring gear 28 will decrease the speed and increase the torque, when the rotational speeds of the input gear 26 and the input carrier 27 are continuously increased, the rotational speeds of the output carrier 24 and the output ring gear 29 will also increase, that is, when the rotational speeds of the input gear 26 and the input carrier 27 are changed, the rotational speeds of the output carrier 24, the output ring gear 29 and the output shaft 3 will also change accordingly.
The input power is divided into two paths by the input shaft 1, the first path is transmitted to the impeller type hydraulic torque converter 8 through the output gear pair 9, the impeller type hydraulic torque converter 8 is divided into two paths, one path is transmitted to the input gear 26, and the other path is transmitted to the input planet carrier 27 through the input gear pair 4; the second path is transmitted to the large output gear 22 through the small input gear ring 21 and the planetary gear 20 on the fixed planet carrier 23, the large output gear 22 is transmitted to the coupling gear ring 25 through the coupling input gear pair 6, the coupling gear ring 25 and the input gear 26 converge the power transmitted to the large output gear ring 24 through the planetary gear 20 on the large output gear carrier 24, and then are transmitted to the input gear ring 28 through the coupling output gear 5, the input planet carrier 27 and the input gear ring 28 converge the power transmitted to the large output gear ring 29 through the planetary gear 20 on the input planet carrier 27 and then are transmitted to the output shaft 3, and therefore the power of the engine is output outwards through the output shaft 3.
With the present invention, when the rotation speed of the input shaft 1 is constant, the torque on the output carrier 24, the output ring gear 29 and the output shaft 3 varies with the variation of the rotation speed, and the lower the rotation speed, the greater the torque transmitted to the output carrier 24, the output ring gear 29 and the output shaft 3, and vice versa, and in this process, the impeller type torque converter 8 also functions as a torque converter, thereby realizing the composite impeller type torque converter of the present invention that can vary the torque and the speed with the variation of the running resistance of the vehicle.
When the invention is used, 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 rotating speed of the output shaft 3 is zero, the input power of the engine is transmitted to the input small gear ring 21 through the input shaft 1, then the power is transmitted to the output large gear 22 through the planetary gears 20 on the fixed planet carrier 23, and the output large gear 22 is transmitted to the connecting ring gear 25 through the connecting input gear pair 6, wherein, because no power or less power flows into the input gear 26 and the input planet carrier 27 at the moment and the input end 71 of the overrunning clutch 7 is connected with a fixed element, the effect of limiting the steering is realized, the steering of the input gear 26 and the input planet carrier 27 can not be opposite to the input steering, the rotating speed is zero, at the moment, the power transmitted to the connecting ring gear 25 is converged to the output planet carrier 24 through the planetary gears 20 on the output planet carrier 24, the torque transmitted to the input gear ring 28 through the coupling output gear 5 is transmitted to the input gear ring 28, the input gear ring 28 then converges the power transmitted to the output gear ring 29 through the planetary gears 20 on the input planet carrier 27 and then transmits the power to the output shaft 3, when the torque transmitted to the output shaft 3 and the traction force generated by the transmission system transmission to the driving wheels are enough to overcome the starting resistance of the automobile, the automobile starts and starts to accelerate, the rotating speed of the output end 82 of the impeller type hydraulic torque converter 8 is gradually increased, and the rotating speeds of the input gear 26 and the input planet carrier 27 which are connected with the output gear ring 8 are also gradually increased, so that the torques of the output planet carrier 24, the output planet carrier 29 and the output shaft 3 are reduced along with the increase of the rotating.
Example two:
as shown in fig. 2, a continuously variable transmission of a compound impeller type torque converter comprises an input shaft 1, an output shaft 3, a coupling gear pair 4, an input coupling gear pair 5, a coupling input gear pair 6, an output coupling gear pair 7, a coupling output gear pair 8, an overrunning clutch 9, an impeller type torque converter 10 and an output gear pair 11, wherein a planetary gear 20, an input gear 21, an output planet carrier 22, a fixed gear 23, a coupling gear 24, an input planet carrier 25, an output large gear 26, a coupling planet carrier 27, an input ring gear 28, an output ring gear 29, a coupling input planet carrier 30, an output large gear 31 and an input small gear 32 are arranged between the input shaft 1 and the output shaft 3, the input gear 21 is matched with the output planet carrier 22 and the fixed gear 23 through the planetary gear 20 on the output planet carrier 22, the input large gear 23, the fixed gear 23 and an input end 91 of the overrunning clutch 9 are coupled with fixed elements, the output planet carrier 22 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 planet carrier 25, the input planet carrier 25 is matched with the connecting gear 24 and the output big gear 26 through the planet gear 20 on the input planet carrier 25, the output big gear 26 is connected with the input gear 81 of the connecting output gear pair 8, the output gear 82 of the connecting output gear pair 8 is connected with the input gear ring 28, the input gear ring 28 is matched with the connecting planet carrier 27 and the output gear ring 29 through the planet gear 20 on the connecting planet carrier 27, the output gear ring 29 is connected with the input gear 61 of the connecting input gear pair 6, the output gear 62 of the connecting input gear pair 6 is connected with the input pinion 32, the input pinion 32 is matched with the connecting input planet carrier 30 and the output big gear ring 31 through the planet gear 20 on the connecting input planet carrier 30, the output large ring gear 31 is coupled to the output shaft 3, the coupling input carrier 30 is coupled to the output gear 52 of the input coupling gear pair 5, the input gear 21, the input gear 51 of the input coupling gear pair 5, and the input gear 111 of the output gear pair 11 are coupled to the input shaft 1, the output gear 112 of the output gear pair 11 is coupled to the input 101 of the impeller torque converter 10, the coupling gear 24, the input gear 71 of the output coupling gear pair 7, and the output 92 of the overrunning clutch 9 are coupled to the output 102 of the impeller torque converter 10, and the output gear 72 of the output coupling gear pair 7 is coupled to the coupling carrier 27.
The coupling gear 24 and the input planet carrier 25 converge the power transmitted to the output large gear 26 through the planet gears 20 on the input planet carrier 25, the output large gear 26 is transmitted to the input ring gear 28 through the coupling output gear pair 8, and the coupling planet carrier 27 and the input ring gear 28 converge the power transmitted to the output ring gear 29 through the planet gears 20 on the coupling planet carrier 27.
Since the distribution relationship of the rotation speeds of the above elements can be changed, the two power flows will change according to the change of the rotation speed distribution between the two, when the rotation speeds of the coupling gear 24 and the coupling planet carrier 27 are zero, the input planet carrier 25 and the input ring gear 28 will decrease the speed and increase the moment, when the rotation speeds of the coupling gear 24 and the coupling planet carrier 27 are continuously increased, the rotation speeds of the output gearwheel 26 and the output ring gear 29 will also be increased, that is, when the rotation speeds of the coupling gear 24 and the coupling planet carrier 27 are changed, the rotation speeds of the output gearwheel 26, the output ring gear 29 and the output shaft 3 will also change accordingly.
The input power is divided into three paths by the input shaft 1, and the first path is transmitted to the input planet carrier 30 through the input connecting gear pair 5; the second path is transmitted to the impeller type hydraulic torque converter 10 through the output gear pair 11, the impeller type hydraulic torque converter 10 is divided into two paths, one path is transmitted to the connecting gear 24, and the other path is transmitted to the connecting planet carrier 27 through the output connecting gear pair 7; the third path passes through the input gear 21, transmits power to the output planet carrier 22 through the planet gears 20 on the output planet carrier 22, then transmits the power to the input planet carrier 25 through the coupling gear pair 4, the coupling gear 24 and the input planet carrier 25 converge the power transmitted to the output large gear 26 through the planet gears 20 on the input planet carrier 25, then transmits the power to the input ring gear 28 through the coupling output gear pair 8, the coupling planet carrier 27 and the input ring gear 28 converge the power transmitted to the output ring gear 29 through the planet gears 20 on the coupling planet carrier 27, the output ring gear 29 transmits the power to the input small gear 32 through the coupling input gear pair 6, the coupling input planet carrier 30 and the input large gear 32 converge the power transmitted to the output large gear 31 through the planet gears 20 on the coupling input planet carrier 30, the output large gear ring 31 is transmitted to the output shaft 3, so that the power of the engine is output outwards through the output shaft 3.
With the present invention, when the rotation speed of the input shaft 1 is unchanged, the torque on the output gearwheel 26, the output ring gear 29 and the output shaft 3 changes with the change of the rotation speed, the lower the rotation speed, the larger the torque transmitted to the output gearwheel 26, the output ring gear 29 and the output shaft 3, and vice versa, in the process, the impeller-type torque converter 10 also plays a role of torque conversion, thereby realizing the continuously variable transmission of the composite impeller-type torque converter capable of changing the torque and the speed with the difference of the vehicle running resistance.
When the invention is used, the input power, the input rotating speed and the load of the engine are not changed, namely the rotating speed and the torque of the input shaft 1 are constant, before the automobile starts, the rotating speed of the output shaft 3 is zero, and the input power of the engine is transmitted to the engine through the input shaft 1
An input gear 21, and transmits power to an output carrier 22 through a planetary gear 20 on the output carrier 22, and then to an input carrier 25 through a coupling gear pair 4, wherein, because no or relatively little power flows into an input large gear 26 and a coupling ring gear 28 at this time, and an input end 91 of an overrunning clutch 9 is coupled with a fixed element, and the function of limiting the steering is realized, the steering of the input large gear 26 and the coupling ring gear 28 cannot be opposite to the input steering, and the rotating speed is zero, at this time, the power transmitted to the input carrier 25 is converged to an output large gear 26 through the planetary gear 20 on the input carrier 25, and then is transmitted to the input ring gear 28 through the coupling output gear pair 8, and the power transmitted to the input ring gear 28 is converged to an output ring gear 29 through the planetary gear 20 on the coupling carrier 27, the output gear 29 is transmitted to the input pinion 32 through the coupling input gear pair 6, the coupling input planet carrier 30 and the input gearwheel 32 converge the power transmitted to the output gearwheel 31 through the planet gear 20 on the coupling input planet carrier 30, the output gearwheel 31 is transmitted to the output shaft 3, when the torque transmitted to the output shaft 3 and the traction force generated by the transmission to the driving wheel through the transmission system is enough to overcome the starting resistance of the automobile, the automobile starts to accelerate, the rotating speed of the output end 102 of the impeller type hydraulic torque converter 10 is gradually increased, the rotating speed of the coupling gear 24 and the coupling planet carrier 27 connected with the output gearwheel is also gradually increased, and therefore the torque of the output gearwheel 26, the output gearwheel 29 and the output shaft 3 is reduced along with the increase of the rotating speed.
Claims (2)
1. The utility model provides a compound impeller formula torque converter, includes input shaft (1), output shaft (3), input gear pair (4), hookup output gear (5), hookup input gear pair (6), freewheel clutch (7), impeller formula torque converter (8), output gear pair (9), its characterized in that: a planetary gear (20), an input small gear ring (21), an output large gear ring (22), a fixed planet carrier (23), an output planet carrier (24), a connecting gear ring (25), an input gear (26), an input planet carrier (27), an input gear ring (28) and an output gear ring (29) are arranged between the input shaft (1) and the output shaft (3), the input small gear ring (21) is matched with the output large gear ring (22) and the fixed planet carrier (23) through the planetary gear (20) on the fixed planet carrier (23), the input ends (71) of the fixed planet carrier (23) and the overrunning clutch (7) are connected with a fixed element, the output large gear ring (22) is connected with an input gear (61) connected with the input gear pair (6), an output gear (62) connected with the input gear pair (6) is connected with the connecting gear ring (25), and the connecting gear ring (25) is connected with the output planet carrier (24) through the planetary gear (20) on the output planet carrier (24), An input gear (26) is matched to work, an output planet carrier (24) is connected with an input gear (51) connected with an output gear (5), an output gear (52) connected with the output gear (5) is connected with an input gear ring (28), the input gear ring (28) is matched with the input planet carrier (27) and an output gear ring (29) to work through a planet gear (20) on the input planet carrier (27), the input planet carrier (27) is connected with an output gear (42) of an input gear pair (4), the input gear (26), an input gear (41) of the input gear pair (4) and an output end (72) of an overrunning clutch (7) are connected with an output end (82) of an impeller type hydraulic torque converter (8), an input end (81) of the impeller type hydraulic torque converter (8) is connected with an output gear (92) of the output gear pair (9), a pinion input gear (91) of the output gear pair (9) and an input shaft (21) are connected with an input shaft (1), the output ring gear (29) is coupled with the output shaft (3).
2. The utility model provides a continuously variable transmission of compound impeller-type torque converter, includes input shaft (1), output shaft (3), coupling gear pair (4), input coupling gear pair (5), coupling input gear pair (6), output coupling gear pair (7), coupling output gear pair (8), freewheel clutch (9), impeller-type torque converter (10), output gear pair (11), its characterized in that: a planetary gear (20), an input gear (21), an output planet carrier (22), a fixed gear (23), a connecting gear (24), an input planet carrier (25), an output large gear (26), a connecting planet carrier (27), an input gear ring (28), an output gear ring (29), a connecting input planet carrier (30), an output large gear ring (31) and an input small gear (32) are arranged between the input shaft (1) and the output shaft (3), the input gear (21) is matched with the output planet carrier (22) and the fixed gear (23) through the planetary gear (20) on the output planet carrier (22), the input end (91) of the fixed gear (23) and the overrunning clutch (9) is connected with a fixed element, the output planet carrier (22) is connected with an input gear (41) of the connecting gear pair (4), and an output gear (42) of the gear pair (4) is connected with the input planet carrier (25), the input planet carrier (25) cooperates with the connecting gear (24) and the output big gear (26) through the planet gear (20) on it, the output big gear (26) is connected with the input gear (81) connected with the output gear pair (8), the output gear (82) connected with the output gear pair (8) is connected with the input gear ring (28), the input gear ring (28) cooperates with the connecting planet carrier (27) and the output gear ring (29) through the planet gear (20) on the connecting planet carrier (27), the output gear ring (29) is connected with the input gear (61) connected with the input gear pair (6), the output gear (62) connected with the input gear pair (6) is connected with the input pinion (32), the input pinion (32) cooperates with the connecting input planet carrier (30) and the output big gear ring (31) through the planet gear (20) connected with the input planet carrier (30), the large output gear ring (31) is connected with the output shaft (3), the connecting input planet carrier (30) is connected with the output gear (52) of the input connecting gear pair (5), the input gear (21), the input gear (51) of the input connecting gear pair (5) and the input gear (111) of the output gear pair (11) are connected with the input shaft (1), the output gear (112) of the output gear pair (11) is connected with the input end (101) of the impeller type hydraulic torque converter (10), the connecting gear (24), the input gear (71) of the output connecting gear pair (7) and the output end (92) of the overrunning clutch (9) are connected with the output end (102) of the impeller type hydraulic torque converter (10), and the output gear (72) of the output connecting gear pair (7) is connected with the connecting planet carrier (27).
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510021394.3A CN104696476B (en) | 2015-01-16 | 2015-01-16 | A Composite Impeller Type Hydraulic Torque Converter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| HK1211662A1 true HK1211662A1 (en) | 2016-05-27 |
| HK1211662B HK1211662B (en) | 2018-11-16 |
Family
ID=
Also Published As
| Publication number | Publication date |
|---|---|
| CN107830142A (en) | 2018-03-23 |
| CN107906179A (en) | 2018-04-13 |
| CN107816529A (en) | 2018-03-20 |
| WO2016112810A1 (en) | 2016-07-21 |
| CN104696476B (en) | 2018-01-23 |
| CN107614936A (en) | 2018-01-19 |
| CN104696476A (en) | 2015-06-10 |
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| Date | Code | Title | Description |
|---|---|---|---|
| PC | Patent ceased (i.e. patent has lapsed due to the failure to pay the renewal fee) |
Effective date: 20220115 |