HK1211668A1 - A compound type box type hydraulic coupler - Google Patents
A compound type box type hydraulic coupler Download PDFInfo
- Publication number
- HK1211668A1 HK1211668A1 HK15111104.3A HK15111104A HK1211668A1 HK 1211668 A1 HK1211668 A1 HK 1211668A1 HK 15111104 A HK15111104 A HK 15111104A HK 1211668 A1 HK1211668 A1 HK 1211668A1
- 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
Provided are a compound case-type hydraulic coupler and a starter having said compound case-type hydraulic coupler; an input shaft (1) is connected to a starting gear pair (11) and an overrunning clutch (10); the overrunning clutch (10) is connected to an input gear (22) and a starter gear pair (9); a large output ring gear (23) engages an input ring gear (24); a connecting shaft (13) is connected to the input ring gear (24), an electromagnetic clutch (12), and an input gear pair (4); the input gear pair (4) is connected to a null shift mechanism (6); the null shift mechanism (6) is connected to an output shaft (5); the electromagnetic clutch (12) is connected to the starting gear pair (11); an output ring gear (26) engages an input gear (3); the input gear (3) is connected to a connecting input planet carrier (27); an output gear (29) is connected to a case-type hydraulic coupler (7); the case-type hydraulic coupler (7) and a fixed one-way clutch (8) are connected to an input planet carrier (21).
Description
Technical Field
The invention belongs to the field of hydraulic couplers and starting, and particularly relates to a composite box type 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 box 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 composite box type hydraulic coupler and a starter comprise an input shaft (1), an input gear (3), an input gear pair (4), an output shaft (5), a neutral gear-engaging mechanism (6), a box type hydraulic coupler (7), a fixed one-way clutch (8), a starter gear pair (9), an overrunning clutch (10), a starting gear pair (11), an electromagnetic clutch (12) and a connecting shaft (13), wherein a planetary gear (20), an input planet carrier (21), an input gear (22), an output large gear ring (23), an input gear ring (24), a fixed planet carrier (25), an output gear ring (26), a connecting input planet carrier (27), a fixed gear (28) and an output gear (29) are arranged between the input shaft (1) and the output shaft (5), the input shaft (1) is connected with an output gear (112) of the starting gear pair (11) and an input end (101) of the overrunning clutch (10), an output end (102) of the overrunning clutch (10) is connected with an input gear (22) and an output gear (92) of a starter gear pair (9), the output gear (92) of the starter gear pair (9) is mutually matched with an input gear (91) of the starter gear pair (9), the input gear (22) is mutually matched with an input planet carrier (21) and an output large gear ring (23) through a planet gear (20) on the input planet carrier (21), the output large gear ring (23) is meshed with the input gear ring (24), a connecting shaft (13) is connected with the input gear ring (24), an input end (121) of an electromagnetic clutch (12) and an input gear (41) of the input gear pair (4), an output gear (42) of the input gear pair (4) is connected with an input end (61) of an idle gear-engaging mechanism (6), an output end (62) of the idle gear-engaging mechanism (6) is connected with an output shaft (5), an output end (122) of the electromagnetic clutch (12) is connected with an input gear (111) of the starting gear pair (11), an input gear ring (24) is matched with a fixed planet carrier (25) and an output gear ring (26) through a planet gear (20) on the fixed planet carrier (25) to work, the output gear ring (26) is meshed with an input gear (3), the input gear (3) is connected with a connected input planet carrier (27), the connected input planet carrier (27) is matched with a fixed gear (28) and an output gear (29) through a planet gear (20) on the connected input planet carrier (27) to work, the fixed planet carrier (25), the fixed gear (28) and an input end (81) of the fixed one-way clutch (8) are connected with a fixed element, the output gear (29) is connected with an input end (71) of the box-type hydraulic coupler (7), an output end (72) of the box-type hydraulic coupler (7) and an output end (82) of the fixed one-way clutch (8) are connected And (6) connecting.
A compound box type hydraulic coupler comprises an input shaft (1), a one-way clutch (3), a box type hydraulic coupler (4), an output shaft (5), an input gear pair (6), a coupling output gear pair (7) and an output gear pair (8), wherein a planetary gear (20), an input small gear ring (21), an input large gear ring (22), an output planet carrier (23), an output gear (24), a fixed planet carrier (25), an input gear (26), an input planet carrier (27), an input small gear (28) and an output gear ring (29) are arranged between the input shaft (1) and the output shaft (5), the input shaft (1) is coupled with the input small gear ring (21) and an input gear (81) of the output gear pair (8), an output gear (82) of the output gear pair (8) is coupled with the input small gear (28), and the input small gear ring (21) is coupled with the input large gear ring (22) through the planetary gear (20) on the output planet carrier (23), The output planet carrier (23) is matched with each other to work, the output planet carrier (23) is connected with an input gear (71) connected with an output gear pair (7), an output gear (72) connected with the output gear pair (7) is connected with an input planet carrier (27) and an input gear (61) of an input gear pair (6), an output gear (62) of the input gear pair (6) is connected with an input gear (26), the input gear (26) is matched with an output gear (24) and a fixed planet carrier (25) through a planet gear (20) on the fixed planet carrier (25) to work, the fixed planet carrier (25) and an input end (31) of a one-way clutch (3) are fixedly connected with a fixed element, the output gear (24) is connected with an input end (41) of a box-type hydraulic coupler (4), an output end (42) of the box-type hydraulic coupler (4) is connected with an output end (32) of the one-way clutch (3) and an input large gear ring (22), the input planet carrier (27) is matched with an input pinion (28) and an output ring gear (29) through a planet gear (20) on the input planet carrier, and the output ring gear (29) is connected with the output shaft (5).
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 box type hydraulic coupler can be replaced by a double-impeller hydraulic torque converter.
The neutral gear mechanism can be replaced by a selective 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;
(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 and separating measures to the starting motor after the engine is started to stop the transmission.
The present invention also relates to a hybrid box type fluid coupling and a starter used for various land vehicles, ships, railroad locomotives, and machine tools.
Drawings
Description figure 1 is a block diagram of a first embodiment of the present invention;
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 compound box type hydraulic coupling and starter comprises an input shaft 1, an input gear 3, an input gear pair 4, an output shaft 5, a neutral gear mechanism 6, a box type hydraulic coupling 7, a fixed one-way clutch 8, a starter gear pair 9, an overrunning clutch 10, a starting gear pair 11, an electromagnetic clutch 12 and a coupling shaft 13, wherein a planetary gear 20, an input planet carrier 21, an input gear 22, an output large gear ring 23, an input ring gear 24, a fixed planet carrier 25, an output ring gear 26, a coupling input planet carrier 27, a fixed gear 28 and an output gear 29 are arranged between the input shaft 1 and the output shaft 5, the input shaft 1 is coupled with an output gear 112 of the starting gear pair 11 and an input end 101 of the overrunning clutch 10, an output end 102 of the overrunning clutch 10 is coupled with the input gear 22 and an output gear 92 of the starter gear pair 9, the output gear 92 of the starter gear pair 9 and the input gear 91 of the starter gear pair 9 work in a matched mode, the input gear 22 works in a matched mode with the input planet carrier 21 and the output large gear ring 23 through the planet gear 20 on the input planet carrier 21, the output large gear ring 23 is meshed with the input gear ring 24, the coupling shaft 13 is connected with the input gear ring 24, the input end 121 of the electromagnetic clutch 12 and the input gear 41 of the input gear pair 4, the output gear 42 of the input gear pair 4 is connected with the input end 61 of the idle gear mechanism 6, the output end 62 of the idle gear mechanism 6 is connected with the output shaft 5, the output end 122 of the electromagnetic clutch 12 is connected with the input gear 111 of the starter gear pair 11, the input gear ring 24 works in a matched mode with the fixed planet carrier 25 and the output gear ring 26 through the planet gear 20 on the fixed planet carrier 25, and the output, the input gear 3 is connected with a connecting input planet carrier 27, the connecting input planet carrier 27 is matched with a fixed gear 28 and an output gear 29 through planet gears 20 on the connecting input planet carrier 27 to work, the fixed planet carrier 25, the fixed gear 28 and an input end 81 of a fixed one-way clutch 8 are connected with fixed elements, the output gear 29 is connected with an input end 71 of a box type hydraulic coupler 7, and an output end 72 of the box type hydraulic coupler 7 and an output end 82 of the fixed one-way clutch 8 are connected with an input planet carrier 21.
Before the engine is started, the idle gear mechanism 6 is disengaged, the electromagnetic clutch 12 is engaged, the input power of a starter is transmitted to the input gear 22 through the starter gear pair 9, the input gear 22 is transmitted to the output large gear ring 23 through the planet gear 20 on the input planet carrier 21, the output large gear ring 23 is transmitted to the input shaft 1 through the input gear ring 24, the coupling shaft 13, the electromagnetic clutch 12 and the starting gear pair 11 and then transmitted to the crankshaft of the engine, and the engine is started when the generated starting force is enough to overcome the starting resistance of the engine.
After the engine is started, the idle gear mechanism 6 is engaged, the electromagnetic clutch 12 is separated, the input gear 22 transmits the power transmitted to the engine through the input shaft 1 and the overrunning clutch 12 to the output large gear ring 23 through the planetary gear 20 on the input planet carrier 21, the output large gear ring 23 is transmitted to the input gear ring 24, the input gear ring 24 divides the power transmitted to the output gear ring into two paths, and one path is transmitted to the output shaft 5 of the invention through the coupling shaft 13, the input gear pair 4 and the idle gear mechanism 6; the other path is transmitted to an output ring gear 26 through the planetary gears 20 on the fixed carrier 25, the output ring gear 26 is transmitted to a connecting input planet carrier 27 through the input gear 3, the connecting input planet carrier 27 is transmitted to an output gear 29 through the planetary gears 20 on the connecting input planet carrier 27, the output gear 29 is transmitted to the input planet carrier 21 through the box type hydraulic coupling 7, the power transmitted to the input planet carrier 21 and the power transmitted to the input gear 22 by the engine through the input shaft 1 and the overrunning clutch 10 are transmitted to an output large ring gear 23 through the planetary gears 20 on the input planet carrier 21, the output large ring gear 23 continuously carries out repeated cycles of speed change among various elements, wherein the output speed of the box type hydraulic coupling 7 is continuously and steplessly changed along with the changes of the input power and the running resistance, so that the output speed of the output large ring gear 23 is also continuously changed, and is transmitted to the output shaft 5 of the present invention through the input ring gear 24, the coupling shaft 13, the input gear pair 4 and the neutral gear mechanism 6, thereby achieving the output of the power of the engine to the outside through the output shaft 5.
According to the invention, when the rotating speed of the input shaft 1 is unchanged, the torques on the input planet carrier 21, the output large gear ring 23 and the output shaft 5 are changed along with the change of the rotating speed, the lower the rotating speed, the larger the torque transmitted to the input planet carrier 21, the output large gear ring 23 and the output shaft 5 is, and on the contrary, the smaller the torque is, so that the composite box type 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, before the engine is started, the idle gear mechanism 6 is separated, the electromagnetic clutch 12 is engaged, the rotating speed of the engine is zero, when the starter is started, the input power of the starter is transmitted to the input gear 22 through the starter gear pair 9, 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 steering is realized, 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 22 is transmitted to the output large gear ring 23 through the planet gear 20 on the input planet carrier 21, the output large gear ring 23 is transmitted to the input shaft 1 through the input ring gear 24, the coupling shaft 13, the electromagnetic clutch 12 and the starting gear pair 11 and then transmitted to the crankshaft of the engine, when the torque is transmitted to the crankshaft of the engine, when the generated starting force is sufficient to overcome the starting resistance of the engine, the engine is started and starts accelerating.
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 6 is engaged, the electromagnetic clutch 12 is disengaged, the rotating speed of the output shaft 5 is zero, the input power of the engine is transmitted to the input gear 22 through the input shaft 1 and the overrunning clutch 10, 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 22 is transmitted to the output large gear ring 23 through the planet gear 20 on the input planet carrier 21, the output large gear ring 23 is transmitted to the input gear ring 24, the input gear ring 24 divides the power transmitted to the two ways, one path is transmitted to an output shaft 5 of the invention through a coupling shaft 13, an input gear pair 4 and an idle gear mechanism 6; the other path is transmitted to an output ring gear 26 through the planetary gears 20 on the fixed carrier 25, the output ring gear 26 is transmitted to a connecting input planet carrier 27 through the input gear 3, the connecting input planet carrier 27 is transmitted to an output gear 29 through the planetary gears 20 on the connecting input planet carrier 27, the output gear 29 is transmitted to the input planet carrier 21 through the box type hydraulic coupling 7, the power transmitted to the input planet carrier 21 and the power transmitted to the input gear 22 by the engine through the input shaft 1 and the overrunning clutch 10 are transmitted to the output large ring gear 23 through the planetary gears 20 on the input planet carrier 21, the output large ring gear 23 continuously carries out repeated cycles of speed change among various elements, wherein the output speed of the box type hydraulic coupling 7 is continuously and steplessly changed along with the change of running resistance, so that the output speed of the output large ring gear 23 is also continuously changed, and is transmitted to the output shaft 5 of the present invention through the input ring gear 24, the coupling shaft 13, the input gear pair 4, and the neutral mechanism 6, so that the torque of the output shaft 5 is reduced as the rotation speed increases.
Example two:
as shown in fig. 2, a compound box type fluid coupling comprises an input shaft 1, a one-way clutch 3, a box type fluid coupling 4, an output shaft 5, an input gear pair 6, a coupling output gear pair 7 and an output gear pair 8, wherein a planetary gear 20, an input small gear ring 21, an input large gear ring 22, an output planet carrier 23, an output gear 24, a fixed planet carrier 25, an input gear 26, an input planet carrier 27, an input small gear 28 and an output gear ring 29 are arranged between the input shaft 1 and the output shaft 5, the input shaft 1 is coupled with the input small gear ring 21 and an input gear 81 of the output gear pair 8, an output gear 82 of the output gear pair 8 is coupled with the input small gear 28, the input small gear ring 21 is mutually matched with the input large gear ring 22 and the output planet carrier 23 through the planetary gear 20 on the output planet carrier 23, the output planet carrier 23 is coupled with an input gear 71 of the coupling output gear pair 7, the output gear 72 of the coupled output gear pair 7 is coupled with the input carrier 27 and the input gear 61 of the input gear pair 6, the output gear 62 of the input gear pair 6 is coupled with the input gear 26, the input gear 26 is mutually matched with the output gear 24 and the fixed carrier 25 through the planet gear 20 on the fixed carrier 25, the fixed carrier 25 and the input end 31 of the one-way clutch 3 are fixedly connected with a fixed element, the output gear 24 is coupled with the input end 41 of the box-type hydraulic coupling 4, the output end 42 of the box-type hydraulic coupling 4 is coupled with the output end 32 of the one-way clutch 3 and the input large ring gear 22, the input carrier 27 is mutually matched with the input small gear 28 and the output ring gear 29 through the planet gear 20 on the input carrier, and the output ring gear 29 is coupled with the output shaft 5.
The input small ring gear 21 and the input large ring gear 22 converge the power transmitted to the respective members to the output carrier 23 through the pinion gears 20 on the output carrier 23, and since the box type fluid coupling 4 is coupled to the input large ring gear 22, the rotation speed of the input large ring gear 22 can be constantly changed in accordance with the change in the rotation speed of the box type fluid coupling 4, and the rotation speed of the output carrier 23 is also changed.
The input power is divided into two paths through the input shaft 1, one path is transmitted to the input small gear ring 21, the other path is transmitted to the input pinion 28 through the output gear pair 8, the input small gear ring 21 converges the power transmitted to the input small gear ring to the output planet carrier 23 through the planet gear 20 on the output planet carrier 23, the output planet carrier 23 is divided into two paths through the connection output gear pair 7, the other path is transmitted to the input planet carrier 27, at the moment, the input planet carrier 27 and the input pinion 28 converge the power transmitted to the output ring 29 through the planet gear 20 on the input planet carrier 27, and the output ring 29 is transmitted to the output shaft 5 of the invention, so that the power of the engine is output to the outside through the output shaft 5.
When the input power of the engine is increased or the resistance of the output shaft 5 is reduced, the power transmitted to the input gear 26 through the input gear pair 6 is increased along with the increase of the power transmitted to the input gear 26, the input gear 26 transmits the power to the output gear 24 through the planetary gears 20 on the fixed carrier 25, the output gear 24 transmits the power to the input large ring gear 22 through the box type fluid coupling 4, namely, the input power of the input large ring gear 22 is increased along with the increase of the power, the input small ring gear 21 and the input large ring gear 22 transmit the respective powers to the output carrier 23 through the planetary gears 20 on the output carrier 23, the output carrier 23 repeats the above process again, the rotating speed transmitted to the input carrier 27 is changed constantly, the input carrier 27 and the input pinion 28 transmit the respective powers to the output ring gear 29 through the planetary gears 20 on the input carrier 27, and the output ring gear 29 transmits the powers to the output shaft 5 of the invention, thereby realizing the output of the power of the engine through the output shaft 5.
In the present invention, when the rotation speed of the input shaft 1 is not changed, the rotation speed of the input carrier 27 is changed according to the difference of the vehicle input power or the driving resistance, and the lower the resistance is, the higher the rotation speed transmitted to the input carrier 27 is, and vice versa, thereby realizing the composite box type hydraulic coupling of the present invention capable of changing the speed according to the difference of the vehicle input power or the driving resistance.
When the invention is used, the input power of the engine is set, the input rotating speed and the load thereof 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 5 is zero, the input power of the engine is divided into two paths through the input shaft 1, one path is transmitted to the input small gear ring 21, the other path is transmitted to the input pinion 28 through the output gear pair 8, the power transmitted to the input small gear ring 21 is converged to the output planet carrier 23 through the planet gear 20 on the output planet carrier 23, the output planet carrier 23 is divided into two paths through the connection with the output gear pair 7, and one path is transmitted to the input planet carrier 27, at the moment, the input planet carrier 27 and the input pinion 28 converge the power transmitted to the output ring 29 through the planet gear 20 on the input planet carrier 27, and the output ring 29 is transmitted to the output shaft 5 of the invention, so that the power of the engine is output to the outside through the output shaft 5.
When the torque transmitted to the output shaft 5 is enough to overcome the resistance of the automobile, the automobile starts to accelerate, when the resistance of the output shaft 5 is reduced, the power transmitted to the input gear 26 through the input gear pair 6 is increased, the input gear 26 transmits the power to the output gear 24 through the planetary gears 20 on the fixed carrier 25, the output gear 24 transmits the power to the input large ring gear 22 through the box type hydraulic coupler 4, namely, the input power of the input large ring gear 22 is increased, the input small ring gear 21 and the input large ring gear 22 transmit the power to the output carrier 23 through the planetary gears 20 on the output carrier 23, the output carrier 23 repeats the above process again, the rotating speed transmitted to the input carrier 27 is changed constantly, and the input carrier 27 and the input small gear 28 transmit the power to the input carrier 27 through the planetary gears on the input carrier 27 20 converge on the output ring gear 29, the output ring gear 29 is transmitted to the output shaft 5 of the invention, when the torque transmitted to the output shaft 5 and the traction force generated by the transmission system to the driving wheels is enough to further overcome the running resistance of the automobile, the automobile continues to accelerate, the rotating speed of the output end 42 of the box type hydraulic coupling 4 is gradually increased, and the rotating speed of the input large ring gear 22 connected with the box type hydraulic coupling is also gradually increased, so that the rotating speeds of the output planet carrier 23, the input planet carrier 27 and the output shaft 5 are continuously increased.
Claims (2)
1. The utility model provides a compound box formula fluid coupling and starter, includes input shaft (1), input gear (3), input gear pair (4), output shaft (5), empty gear shifting mechanism (6), box formula fluid coupling (7), fixed one way clutch (8), starter gear pair (9), freewheel clutch (10), starting gear pair (11), electromagnetic clutch (12), coupling shaft (13), its characterized in that: a planetary gear (20), an input planetary carrier (21), an input gear (22), an output large gear ring (23), an input gear ring (24), a fixed planetary carrier (25), an output gear ring (26), a connection input planetary carrier (27), a fixed gear (28) and an output gear (29) are arranged between the input shaft (1) and the output shaft (5), the input shaft (1) is connected with an output gear (112) of a starting gear pair (11) and an input end (101) of an overrunning clutch (10), an output end (102) of the overrunning clutch (10) is connected with the input gear (22) and an output gear (92) of a starter gear pair (9), the output gear (92) of the starter gear pair (9) and an input gear (91) of the starter gear pair (9) are matched with each other to work, and the input gear (22) is connected with the input planetary carrier (21) through a planetary gear (20) on the input planetary carrier (21), The large output gear ring (23) is matched with the input gear ring (24) to work, the large output gear ring (23) is meshed with the input gear ring (24), the coupling shaft (13) is connected with the input gear ring (24), the input end (121) of the electromagnetic clutch (12) and the input gear (41) of the input gear pair (4), the output gear (42) of the input gear pair (4) is connected with the input end (61) of the idle gear mechanism (6), the output end (62) of the idle gear mechanism (6) is connected with the output shaft (5), the output end (122) of the electromagnetic clutch (12) is connected with the input gear (111) of the starting gear pair (11), the input gear ring (24) is matched with the fixed planet carrier (25) and the output gear ring (26) to work through the planet gear (20) on the fixed planet carrier (25), the output gear ring (26) is meshed with the input gear (3), the input gear (3) is connected with the input planet carrier (27), the connecting input planet carrier (27) is matched with the fixed gear (28) and the output gear (29) through the planet gear (20) on the connecting input planet carrier, the input end (81) of the fixed planet carrier (25), the fixed gear (28) and the fixed one-way clutch (8) is connected with a fixed element, the output gear (29) is connected with the input end (71) of the box type hydraulic coupler (7), and the output end (72) of the box type hydraulic coupler (7) and the output end (82) of the fixed one-way clutch (8) are connected with the input planet carrier (21).
2. The utility model provides a compound box formula fluid coupling, includes input shaft (1), one way clutch (3), box formula fluid coupling (4), output shaft (5), input gear pair (6), couples output gear pair (7), output gear pair (8), its characterized in that: the planetary gear set is characterized in that a planetary gear (20), an input small gear ring (21), an input large gear ring (22), an output planet carrier (23), an output gear (24), a fixed planet carrier (25), an input gear (26), an input planet carrier (27), an input small gear (28) and an output gear ring (29) are arranged between an input shaft (1) and an output shaft (5), the input shaft (1) is connected with the input small gear ring (21) and an input gear (81) of an output gear pair (8), an output gear (82) of the output gear pair (8) is connected with the input small gear (28), the input small gear ring (21) is mutually matched with the input large gear ring (22) and the output planet carrier (23) through a planetary gear (20) on the output planet carrier (23), the output planet carrier (23) is connected with an input gear (71) connected with the output gear pair (7), an output gear (72) connected with the output gear pair (7) is connected with the input planet carrier (27) and the input gear (6) The input gear (61) of the input gear pair (6) is connected, the output gear (62) of the input gear pair (6) is connected with the input gear (26), the input gear (26) is matched with the output gear (24) and the fixed planet carrier (25) through the planet gear (20) on the fixed planet carrier (25) to work, the fixed planet carrier (25) and the input end (31) of the one-way clutch (3) are fixedly connected with a fixed element, the output gear (24) is connected with the input end (41) of the box-type hydraulic coupler (4), the output end (42) of the box-type hydraulic coupler (4) is connected with the output end (32) of the one-way clutch (3) and the input large gear ring (22), the input planet carrier (27) is connected with the input small gear (28) through the planet gear (20) on the input, the output gear rings (29) are matched with each other to work, and the output gear rings (29) are connected with the output shaft (5).
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510389853.3A CN104976303B (en) | 2015-07-07 | 2015-07-07 | A compound box type hydraulic coupling |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| HK1211668A1 true HK1211668A1 (en) | 2016-05-27 |
| HK1211668B HK1211668B (en) | 2018-06-22 |
Family
ID=
Also Published As
| Publication number | Publication date |
|---|---|
| CN107448574A (en) | 2017-12-08 |
| WO2017005177A1 (en) | 2017-01-12 |
| CN104976303A (en) | 2015-10-14 |
| CN104976303B (en) | 2017-10-03 |
| CN108243617A (en) | 2018-07-03 |
| CN107869564A (en) | 2018-04-03 |
| CN107869562A (en) | 2018-04-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| HK1216332A1 (en) | A composite torque limiting type water medium hydraulic coupler and starter | |
| HK1216328A1 (en) | A composite of harmonic gear drive hydraulic coupler and starter | |
| HK1211653A1 (en) | A composite type variable speed hydraulic coupler and starter | |
| HK1211655A1 (en) | A composite type double cavity of hydraulic coupler and starter | |
| HK1216326A1 (en) | A composite type grinding box type hydraulic coupler and starter | |
| HK1216331A1 (en) | A composite type constant charging type hydraulic coupler and starter | |
| HK1216329A1 (en) | A composite type rear gear box type hydraulic coupler and starter | |
| HK1211671A1 (en) | A composite type of abnormal shape hydraulic coupler and starter | |
| HK1216333A1 (en) | A composite type double cavity of hydraulic coupler and starter | |
| HK1216330A1 (en) | A composite type auxiliary room extension type yox and starter | |
| HK1216327A1 (en) | A composite valve fluid filled type hydraulic coupler and starter | |
| HK1211670A1 (en) | A composite type hydraulic coupler shell with side auxiliary chamber and starter | |
| HK1211672A1 (en) | A composite type variable speed hydraulic coupler and starter | |
| HK1211668A1 (en) | A compound type box type hydraulic coupler | |
| HK1211668B (en) | A compound type box type hydraulic coupler | |
| HK1211654A1 (en) | A composite type hydraulic coupler shell with side auxiliary chamber and starter | |
| HK1227465A (en) | A composite type double cavity of hydraulic coupler and starter | |
| HK1227465A1 (en) | A composite type double cavity of hydraulic coupler and starter | |
| HK1227472A1 (en) | A composite type of double turbine hydraulic torque converter and starter | |
| HK1227472A (en) | A composite type of double turbine hydraulic torque converter and starter | |
| HK1227466A (en) | A composite starter of hydraulic coupler | |
| HK1227466A1 (en) | A composite starter of hydraulic coupler | |
| HK1239792A (en) | A continuously variable transmission of a composite type of abnormal shape hydraulic coupler | |
| HK1239792A1 (en) | A continuously variable transmission of a composite type of abnormal shape hydraulic coupler | |
| HK1239790A1 (en) | A continuously variable transmission of a composite type double cavity of hydraulic coupler |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PC | Patent ceased (i.e. patent has lapsed due to the failure to pay the renewal fee) |
Effective date: 20210709 |