WO2016112805A1 - Convertisseur de couple hydraulique à double turbine composite et transmission variable en continu - Google Patents

Convertisseur de couple hydraulique à double turbine composite et transmission variable en continu Download PDF

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Publication number
WO2016112805A1
WO2016112805A1 PCT/CN2016/070214 CN2016070214W WO2016112805A1 WO 2016112805 A1 WO2016112805 A1 WO 2016112805A1 CN 2016070214 W CN2016070214 W CN 2016070214W WO 2016112805 A1 WO2016112805 A1 WO 2016112805A1
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WIPO (PCT)
Prior art keywords
input
gear
output
carrier
coupled
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PCT/CN2016/070214
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English (en)
Chinese (zh)
Inventor
吴志强
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吴志强
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Publication date
Application filed by 吴志强 filed Critical 吴志强
Priority to CN201680004316.5A priority Critical patent/CN107407390A/zh
Publication of WO2016112805A1 publication Critical patent/WO2016112805A1/fr

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    • 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
    • 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

Definitions

  • the present invention is in the field of torque converters and shifting, and more particularly, it is a composite twin-turbo torque converter and a continuously variable transmission for various ground vehicles, ships, railway locomotives, and machine tools.
  • the torque converter is designed according to the principles of hydrostatics, etc. It can transmit little power and is not efficient; in addition, the cost is high.
  • the invention overcomes the deficiencies of the prior art, and provides a composite twin-turbo torque converter and a continuously variable transmission which have the advantages of shortening the service life of the engine, simple structure, convenient operation, low cost, energy saving and high efficiency.
  • a compound twin-turbo torque converter comprising an input shaft (1), an output shaft (3), a coupling gear pair (4), an input gear pair (5), an overrunning clutch (6), and a twin-turbo hydraulic force change a torque device (7) and an output gear pair (8), wherein the input shaft (1) and the output shaft (3) are provided with a planetary gear (20), an input gear (21), an output carrier (22), Fixed gear (23), input small ring gear (24), connecting planet carrier (25), input large ring gear (26), input ring gear (27), output ring gear (28), input planet carrier (29),
  • the input gear (21) cooperates with the output carrier (22) and the fixed gear (23) through the planetary gears (20) on the output carrier (22), and fixes the input of the gear (23) and the overrunning clutch (6) ( 61) coupled with the fixed component
  • the output carrier (22) is coupled with the input large ring gear (26), and the input large ring gear (26) passes the planetary gear (20) and the input small ring gear (24
  • the output gear (42) of the coupling gear pair (4) is coupled to the input carrier (29), input The star frame (29) cooperates with the input ring gear (27) and the output ring gear (28) through the planetary gears (20) thereon, and the output ring gear (28) is coupled with the output shaft (3), and the input ring gear (27)
  • the input gear (51) of the input gear pair (5) and the output end (62) of the overrunning clutch (6) are coupled to the output end (72) of the twin-turbine torque converter (7), and the twin-turbo hydraulic force is changed.
  • the input end (71) of the torque device (7) is coupled to the output gear (82) of the output gear pair (8), the input gear (81) of the output gear pair (8), and the input gear (21) and the input shaft (1) Join.
  • a continuously variable transmission of a composite twin-turbo torque converter comprising an input shaft (1), an output shaft (3), a twin-turbo torque converter (4), an input gear pair (5), an overrunning clutch ( 6), a coupling gear pair (7), an input gear (8), an output gear pair (9), a planetary gear (20), a fixed planet carrier between the input shaft (1) and the output shaft (3) (21), input ring gear (22), output ring gear (23), connecting planet carrier (24), input gear (25), output large ring gear (26), input large gear (27), output planet carrier ( 28) Input the input large ring gear (29), output gear (30), input carrier (31), input pinion (32), input ring gear (22), twin-turbo torque converter (4)
  • the input gear (91) of the end (41) and the output gear pair (9) is coupled to the input shaft (1), and the input ring gear (22) is fixed to the fixed planet carrier by the planetary gear (20) on the fixed carrier (21) ( 21), the output ring gear (23) works together,
  • the output end (62) of the overrunning clutch (6) and the output gear (72) of the coupling gear pair (7) are coupled with the output gear (52) of the input gear pair (5), and coupled to the gear pair (7)
  • the input gear (71) is coupled to the coupling carrier (24)
  • the input gear (51) of the input gear pair (5) is coupled to the output (42) of the twin-turbine torque converter (4)
  • the output gear (30) Coupling with the input large ring gear (29), the input large ring gear (29) cooperates with the input large gear (27) and the output planet carrier (28) through the planetary gear (20) on the output carrier (28), and the input is large.
  • the gear (27) is coupled to the output gear (92) of the output gear pair (9), and the output carrier (28) is coupled to the output shaft (3).
  • the components that need to be coupled may be directly connected.
  • the method of coupling a shaft, a hollow or a coupling frame may be adopted, and may be connected through or across several other components; when the coupled component is When the gears or ring gears are engaged or coupled with each other, the components that do not need to be coupled can be rotated relative to each other.
  • the gear ratios of the gear pairs and the shifting mechanism are designed according to actual needs.
  • the torque converter can be selected from a fluid coupling, a pressure motor and a hydraulic pump, and an electromagnetic clutch.
  • the present invention When the present invention is applied to a vehicle, it is possible to automatically change the output torque and the speed change depending on the magnitude of the resistance that the vehicle is subjected to while traveling.
  • the invention makes the engine and the starter operate in the economic speed region, that is, the engine works in the range of the very small pollution discharge speed, and avoids the engine discharging a large amount of exhaust gas during the idle speed and high speed operation, thereby reducing the exhaust gas. Emissions are conducive to protecting the environment;
  • the invention can utilize the effect of internal speed difference to buffer and overload protection, which is beneficial to prolonging the service life of the engine and the transmission system and the starter.
  • speed up which is beneficial to improve the driving performance of the vehicle;
  • the invention makes the input power uninterrupted, can ensure the vehicle has good acceleration and high average speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity.
  • the present invention is a composite twin-turbo torque converter and a continuously variable transmission for various ground vehicles, ships, railway locomotives, and machine tools.
  • FIG. 1 is a structural view of a first embodiment of the present invention
  • FIG. 2 is a structural view of a second embodiment of the present invention
  • the connection between two components in the drawing uses a thick solid line to indicate a fixed connection. The line indicates that the two elements can be rotated relative to each other.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • a composite twin-turbo torque converter includes an input shaft 1 , an output shaft 3 , a coupling gear pair 4 , an input gear pair 5 , an overrunning clutch 6 , and a twin-turbo torque converter 7 .
  • the output gear pair 8 is provided with a planetary gear 20, an input gear 21, an output carrier 22, a fixed gear 23, an input small ring gear 24, a coupling carrier 25, and an input between the input shaft 1 and the output shaft 3.
  • the input end 61 of the 6 is coupled to the fixed component
  • the output carrier 22 is coupled to the input large ring gear 26, and the input large ring gear 26 cooperates with the input small ring gear 24 and the coupled planet carrier 25 through the planetary gear 20 thereon, and the input is small.
  • the ring gear 24 is coupled to the output end 52 of the input gear pair 5, the coupling carrier 25 is coupled to the input gear 41 of the coupling gear pair 4, and the output gear 42 of the coupling gear pair 4 is coupled to the input carrier 29 through which the input carrier 29 is Planet gear 20 and input ring gear 27, output
  • the ring 28 cooperates, the output ring gear 28 is coupled to the output shaft 3, the input ring gear 27, the input gear 51 of the input gear pair 5, and the output 62 of the overrunning clutch 6 are coupled to the output 72 of the twin-turbo torque converter 7.
  • the input end 71 of the twin-turbo torque converter 7 is coupled to the output gear 82 of the output gear pair 8, the input gear 81 of the output gear set 8 and the input gear 21 are coupled to the input shaft 1.
  • the input small ring gear 24 and the input large ring gear 26 converge the power transmitted thereto by the planetary gears 20 coupled to the carrier 25 to the coupling carrier 25, and the coupling carrier 25 is transmitted to the input carrier 29 through the coupling gear pair 4.
  • the input ring gear 27, the input carrier 29, and the power transmitted thereto through the planetary gears 20 on the input carrier 29 are merged to the output ring gear 28.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the large ring gear 26 is input.
  • the input planet carrier 29 is decelerated and increased in torque.
  • the rotational speed of the connecting carrier 25 and the output ring gear 28 also increases, that is, When the rotational speed of the input small ring gear 24 and the input ring gear 27 changes, the rotational speeds of the coupled carrier 25, the output ring gear 28, and the output shaft 3 also change.
  • the input power is split into two paths via the input shaft 1, and the first path is transmitted to the twin-turbo torque converter 7 via the output gear pair 8, and the twin-turbo torque converter 7 is split into two paths, one way to
  • the input ring gear 27 is input to the input pinion ring 24 through the input gear pair 5; the second path is passed to the input gear 21, and the power is transmitted to the output carrier 22 through the planetary gears 20 on the output carrier 22.
  • the output carrier 22 is further transmitted to the input large ring gear 26, the input small ring gear 24, the input large ring gear 26 is connected to the coupled planet carrier 25 by the planetary gears 20 coupled to the carrier 25, and then coupled
  • the gear pair 4 is transmitted to the input carrier 29, the input ring gear 27, the input carrier 29 and the power transmitted thereto through the planetary gears 20 on the input carrier 29 are merged to the output ring gear 28 and then transmitted to the output shaft 3, Thereby, the power of the engine is externally outputted through the output shaft 3.
  • the twin-turbo torque converter 7 when the rotational speed of the input shaft 1 is constant, the torque on the coupled carrier 25, the output ring gear 28, and the output shaft 3 varies with the change of the rotational speed thereof, and the lower the rotational speed is transmitted to the coupled carrier 25 and the output teeth.
  • the torque on the ring 28 and the output shaft 3 is larger, and conversely, the smaller, in the process, the twin-turbo torque converter 7 also acts as a torque converter, thereby realizing the difference in the driving resistance of the present invention with the vehicle.
  • a compound twin-turbo torque converter that changes torque and speed.
  • the input power, the input rotational speed and the load of the engine are constant, that is, the rotational speed and torque of the input shaft 1 are constant, and before the vehicle starts, the rotational speed of the output shaft 3 is zero, and the input power of the engine passes through the input shaft 1 And transmitted to the input gear 21, and then the power is transmitted to the output carrier 22 through the planetary gears 20 on the output carrier 22, and the output carrier 22 is transferred to the input large ring gear 26, wherein there is no power or less at this time. Power flow into the input small ring gear 24.
  • the input ring gear 27 is input, and the input end 61 of the overrunning clutch 6 is coupled with the fixed component to restrict the steering, so that the steering of the input small ring gear 24 and the input ring gear 27 cannot be opposite to the input steering, and the rotational speed is zero.
  • the power transmitted to the input large ring gear 26 is transmitted to the coupled carrier 25 through the planetary gear 20 coupled to the carrier 25, and then transmitted to the input carrier 29 through the coupling gear pair 4.
  • the input carrier 29 then passes the power transmitted thereto through the planetary gears 20 on the input carrier 29 to the output ring gear 28, and then to the output shaft 3, and the torque transmitted to the output shaft 3 is transmitted to the transmission system through the transmission system.
  • the car starts and starts to accelerate, and the rotational speed of the output end 72 of the twin-turbo torque converter 7 is gradually increased, and the input small ring gear 24, input is connected thereto.
  • the rotational speed of the ring gear 27 also gradually increases, so that the torque of the coupling carrier 25, the output ring gear 28, and the output shaft 3 decreases as the number of revolutions increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a continuously variable transmission of a composite twin-turbo torque converter includes an input shaft 1, an output shaft 3, a twin-turbo torque converter 4, an input gear pair 5, an overrunning clutch 6, Coupling gear pair 7, input gear 8, output gear pair 9, between the input shaft 1 and the output shaft 3, a planetary gear 20, a fixed planet carrier 21, an input ring gear 22, an output ring gear 23, and a coupled planet carrier are disposed. 24.
  • the input end 41 of the torque converter 4 and the input gear 91 of the output gear pair 9 are coupled to the input shaft 1, and the input ring gear 22 cooperates with the fixed carrier 21 and the output ring gear 23 via the planetary gear 20 on the fixed carrier 21.
  • the fixed carrier 21 and the input end 61 of the overrunning clutch 6 are coupled to the fixed element, and the output ring gear 23 is coupled to the input gear 25.
  • the input gear 25 is coupled to the planet carrier 24 and the output large gear by the planetary gear 20 coupled to the carrier 24.
  • the ring 26 cooperates with the input gear 8 and the output large ring gear 26
  • the input planet carrier 31 is coupled
  • the input planet carrier 31 cooperates with the output gear 30 and the input pinion 32 through the planetary gear 20 thereon, and the input pinion 32, the output end 62 of the overrunning clutch 6, and the output gear of the coupling gear pair 7 72 is coupled to the output gear 52 of the input gear pair 5,
  • the input gear 71 of the coupling gear pair 7 is coupled to the coupling carrier 24, and the input gear 51 of the input gear pair 5 is coupled to the output 42 of the twin-turbo torque converter 4,
  • the output gear 30 is coupled to the input large ring gear 29, and the input large ring gear 29 cooperates with the input large gear 27 and the output carrier 28 through the planetary gear 20 on the output carrier 28, and the output of the input large gear 27 and the output gear pair 9
  • Gear 92 is coupled and output planet carrier 28 is coupled to output shaft 3.
  • the connecting carrier 24 and the input gear 25 converge the power transmitted thereto through the planetary gear 20 coupled to the carrier 24 to the output large ring gear 26, and the output large ring gear 26 is transmitted to the input carrier 31 through the input gear 8.
  • the input carrier 31 and the input pinion 32 converge the power transmitted thereto through the planetary gears 20 on the input carrier 31 to the output gear 30.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the rotational speed of the connecting carrier 24 and the input pinion 32 is zero, the input gear 25 and the input planet are input.
  • the frame 31 is reduced in speed, and when the rotational speed of the connecting carrier 24 and the input pinion 32 is continuously increased, the rotational speed of the output large ring gear 26 and the output gear 30 also increases, that is, when the planetary carrier is coupled 24.
  • the rotational speed of the input pinion 32 changes, the rotational speeds of the output large ring gear 26, the output gear 30, and the output shaft 3 also change.
  • the input power is divided into three paths via the input shaft 1, the first path is output to the input large gear 27 via the output gear pair 9, and the second path is transmitted to the input gear pair 5 via the twin-turbine torque converter 4, and the input is input.
  • the gear pair 5 is split into two paths, one for the input pinion 32, the other for the coupled gear pair 7, to the coupled planet carrier 24; the third for the input ring gear 22, and for the planet on the fixed planet carrier 21
  • the gear 20 transmits power to the output ring gear 23 and then to the output
  • the input gear 25, the connecting carrier 24, the input gear 25 and the planetary gear 20 coupled to the carrier 24 converge the power transmitted thereto to the output large ring gear 26, and then through the input gear 8, to the input carrier 31, the input
  • the carrier 31 and the input pinion 32 converge the power transmitted thereto through the planetary gears 20 on the input carrier 31 to the output gear 30, and the output gear 30 is transmitted to the input large ring gear 29, the input large gear 27, and the input large teeth.
  • the ring 29 converge
  • the twin-turbo torque converter 4 when the rotational speed of the input shaft 1 is constant, the torque on the output large ring gear 26, the output gear 30, and the output shaft 3 varies with the change of the rotational speed thereof, and the lower the rotational speed is transmitted to the output large ring gear 26 and the output.
  • the torque on the gear 30 and the output shaft 3 is larger, and conversely, the smaller, in the process, the twin-turbo torque converter 4 also acts as a torque converter, thereby realizing the difference in the driving resistance of the present invention with the vehicle.
  • a continuously variable transmission of a composite twin-turbo torque converter that changes torque and speed.
  • the input power, the input rotational speed and the load of the engine are constant, that is, the rotational speed and torque of the input shaft 1 are constant, and before the vehicle starts, the rotational speed of the output shaft 3 is zero, and the input power of the engine passes through the input shaft 1 Passing to the input ring gear 22 and transmitting power to the output ring gear 23 through the planet gears 20 on the fixed planet carrier 21, and then to the input gear 25, wherein no or less power flows into the coupled planet carrier at this time.
  • the input pinion 32, and the input end 61 of the overrunning clutch 6 is coupled with the fixed component to limit the steering, so that the steering of the connecting carrier 24 and the input pinion 32 cannot be opposite to the input steering, and the rotational speed is zero.
  • the power transmitted to the input gear 25 is transferred to the output large ring gear 26 through the planetary gear 20 coupled to the carrier 24, and then transmitted to the input carrier 31 through the input gear 8, and the input planet
  • the frame 31 is coupled to the output gear 30 via the planetary gears 20 thereon, and the output gear 30 is transmitted to the input large ring gear 29, the input large gear 27, and the input large ring gear 29 through the output.
  • the planetary gears 20 on the star frame 28 converge the power transmitted thereto to the output carrier 28, and the output carrier 28 is transferred to the output shaft 3, and the torque transmitted to the output shaft 3 is transmitted to the drive wheels via the transmission system.
  • the vehicle starts and starts to accelerate, and the rotational speed of the output end 42 of the twin-turbo torque converter 4 is also gradually increased, and the speed of the coupled carrier 24 and the input pinion 32 is associated with it. It also gradually increases, so that the torque of the output large ring gear 26, the output gear 30, and the output shaft 3 decreases as the number of revolutions increases.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • General Details Of Gearings (AREA)

Abstract

L'invention concerne un convertisseur de couple hydraulique à double turbine composite. Un porte-satellites de sortie (22) est relié à une grande couronne dentée d'entrée (26), une petite couronne dentée d'entrée (24) est reliée à une paire d'engrenages d'entrée (5), un porte-satellites de liaison (25) est relié à une paire d'engrenages de liaison, la paire d'engrenages de liaison (4) est reliée à un porte-satellites d'entrée (29), une couronne dentée de sortie (28) est reliée à un arbre de sortie (3), une couronne dentée d'entrée (27), la paire d'engrenages d'entrée (5), et un embrayage de dépassement (6) sont reliés à un convertisseur de couple hydraulique à double turbine (7), le convertisseur de couple hydraulique à double turbine (7) est relié à une paire d'engrenages de sortie (8), et la paire d'engrenages de sortie (8) et un engrenage d'entrée (21) sont reliés à un arbre d'entrée (1). En outre, l'invention concerne également une transmission variable en continu d'un convertisseur de couple hydraulique double turbine composite.
PCT/CN2016/070214 2015-01-16 2016-01-06 Convertisseur de couple hydraulique à double turbine composite et transmission variable en continu WO2016112805A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680004316.5A CN107407390A (zh) 2015-01-16 2016-01-06 一种复合型双涡轮液力变矩器以及无级变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510021320.XA CN104653743B (zh) 2015-01-16 2015-01-16 一种复合型双涡轮液力变矩器
CN201510021320.X 2015-01-16

Publications (1)

Publication Number Publication Date
WO2016112805A1 true WO2016112805A1 (fr) 2016-07-21

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PCT/CN2016/070214 WO2016112805A1 (fr) 2015-01-16 2016-01-06 Convertisseur de couple hydraulique à double turbine composite et transmission variable en continu

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CN (5) CN107269798A (fr)
HK (1) HK1211663A1 (fr)
WO (1) WO2016112805A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107269798A (zh) * 2015-01-16 2017-10-20 广州市志变制能科技有限责任公司 一种复合式限矩型水介质液力偶合器的无级变速器

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05263906A (ja) * 1990-12-13 1993-10-12 Fuji Heavy Ind Ltd 車両用無段変速機の圧力制御装置
KR20060009190A (ko) * 2004-07-21 2006-01-31 이종완 범위가 확장된 무단변속장치
CN102022512A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型双涡轮液力变矩器
WO2011093425A1 (fr) * 2010-01-28 2011-08-04 株式会社ユニバンス Dispositif de transmission de puissance
CN102287498A (zh) * 2011-08-05 2011-12-21 南京工程学院 一种行星齿轮无级变速器
CN102297255A (zh) * 2011-08-04 2011-12-28 湖南江麓容大车辆传动股份有限公司 自动变速器总成及自动变速型汽车
CN103939560A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型双涡轮液力变矩器以及无级变速器
CN104653743A (zh) * 2015-01-16 2015-05-27 吴志强 一种复合型双涡轮液力变矩器以及无级变速器

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3941058B2 (ja) * 2003-06-12 2007-07-04 本田技研工業株式会社 駆動装置
CN1928391A (zh) * 2006-10-04 2007-03-14 刘丙纯 行星齿轮变矩器

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05263906A (ja) * 1990-12-13 1993-10-12 Fuji Heavy Ind Ltd 車両用無段変速機の圧力制御装置
KR20060009190A (ko) * 2004-07-21 2006-01-31 이종완 범위가 확장된 무단변속장치
CN102022512A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型双涡轮液力变矩器
WO2011093425A1 (fr) * 2010-01-28 2011-08-04 株式会社ユニバンス Dispositif de transmission de puissance
CN102297255A (zh) * 2011-08-04 2011-12-28 湖南江麓容大车辆传动股份有限公司 自动变速器总成及自动变速型汽车
CN102287498A (zh) * 2011-08-05 2011-12-21 南京工程学院 一种行星齿轮无级变速器
CN103939560A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型双涡轮液力变矩器以及无级变速器
CN104653743A (zh) * 2015-01-16 2015-05-27 吴志强 一种复合型双涡轮液力变矩器以及无级变速器

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Publication number Publication date
CN107407390A (zh) 2017-11-28
CN107269795A (zh) 2017-10-20
HK1211663A1 (en) 2016-05-27
CN107269798A (zh) 2017-10-20
CN107299975A (zh) 2017-10-27
CN104653743B (zh) 2017-06-23
CN104653743A (zh) 2015-05-27

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