WO2016112801A1 - Convertisseur de couple hydraulique de roue de travail à éléments multiples composite et transmission à variation continue - Google Patents

Convertisseur de couple hydraulique de roue de travail à éléments multiples composite et transmission à variation continue Download PDF

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Publication number
WO2016112801A1
WO2016112801A1 PCT/CN2016/070210 CN2016070210W WO2016112801A1 WO 2016112801 A1 WO2016112801 A1 WO 2016112801A1 CN 2016070210 W CN2016070210 W CN 2016070210W WO 2016112801 A1 WO2016112801 A1 WO 2016112801A1
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Prior art keywords
input
gear
output
carrier
coupled
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PCT/CN2016/070210
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English (en)
Chinese (zh)
Inventor
吴志强
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吴志强
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Application filed by 吴志强 filed Critical 吴志强
Priority to CN201680004312.7A priority Critical patent/CN107208770A/zh
Publication of WO2016112801A1 publication Critical patent/WO2016112801A1/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
    • 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
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion

Definitions

  • the invention belongs to the field of torque converter and shifting, and more particularly to a composite multi-component working wheel hydraulic 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 multi-component working wheel hydraulic torque converter and a continuously variable transmission which are prolonged in service life, simple in structure, convenient in operation, low in cost, energy-saving and high-efficiency.
  • a compound multi-component working wheel hydraulic torque converter includes an input shaft (1), an output shaft (3), a multi-component working wheel hydraulic torque converter (4), an overrunning clutch (5), and an input gear pair ( 6), the output gear pair (7), between the input shaft (1) and the output shaft (3) is provided with a planetary gear (20), a fixed planet carrier (21), an input small ring gear (22), and an output.
  • the frame (21) and the output large ring gear (23) cooperate to work, and the fixed carrier (21) and the input end (51) of the overrunning clutch (5) are coupled with the fixed component, and the output large ring gear (23) and the input gear (25) ), the input gear (25) passes through the planet gear (20) on the input planet carrier (24) and the input planet (24)
  • the output ring gear (26) cooperates, the output ring gear (26) is coupled with the input pinion (27), and the input pinion (27) passes through the planet gear (20) and output on the output carrier (28).
  • the planet carrier (28) and the input large gear (29) work together, the output carrier (28) is coupled with the output shaft (3), the output gear (72) of the output gear pair (7) and the multi-component working wheel hydraulic torque
  • the input end (41) of the (4) is coupled, the output end (42) of the multi-component working wheel hydraulic torque converter (4) and the output end (52) of the overrunning clutch (5) and the input gear pair (6)
  • the input gear (61) is coupled, the output gear (62) of the input gear pair (6) is coupled to the input carrier (24), and the input carrier (24) is coupled to the input bull gear (29).
  • a continuously variable transmission of a compound multi-component working wheel hydraulic torque converter comprising an input shaft (1), an output shaft (3), an input gear pair (4), a coupling gear (5), and a coupling input gear pair (6) ), an overrunning clutch (7), a multi-component working wheel hydraulic torque converter (8), an output gear pair (9), and a planetary gear (20) between the input shaft (1) and the output shaft (3) ), input small ring gear (21), fixed ring gear (22), output planet carrier (23), coupling input planet carrier (24), coupling ring gear (25), output ring gear (26), input large ring gear (27), coupling input gear (28), coupling output planet carrier (29), input gear (30), input planet carrier (31), output gear (32), input small ring gear (21), input gear pair ( The input gear (41) of 4) and the input gear (91) of the output gear pair (9) are coupled to the input shaft (1), and the input small ring gear (21) passes through the planetary gear (20) on the output carrier (23).
  • the input end (71) of the device (7) is coupled to the fixed component, the output carrier (23) is coupled to the coupling ring gear (25), and the coupling ring gear (25) is coupled to the planetary gear on the input carrier (24) (20) ) and the input input planet carrier (24), output
  • the ring gear (26) cooperates, the output ring gear (26) is coupled with the coupling gear (5), the coupling gear (5) is coupled with the input large ring gear (27), and the input large ring gear (27) is coupled to the output carrier ( 29)
  • the upper planetary gear (20) cooperates with the coupling input gear (28), the coupled output carrier (29), the input gear (28), the input gear (61) that couples the input gear pair (6), and the overrunning clutch
  • the output end (72) of (7) is coupled to the output end (82) of the multi-component working wheel hydraulic torque converter (8), and the input end (81) and output of the multi-component working wheel
  • 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 multi-component working wheel hydraulic 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, and a thin solid line indicates The two elements can be rotated relative to each other.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • a composite multi-component working wheel hydraulic torque converter includes an input shaft 1 , an output shaft 3 , a multi-component working wheel hydraulic torque converter 4 , an overrunning clutch 5 , an input gear pair 6 ,
  • the output gear pair 7 is provided with a planetary gear 20, a fixed carrier 21, an input small ring gear 22, an output large ring gear 23, an input carrier 24, an input gear 25, and an output between the input shaft 1 and the output shaft 3.
  • the ring gear 26, the input pinion 27, the output carrier 28, the input bull gear 29, the input small gear 22 and the input gear 71 of the output gear pair 7 are coupled to the input shaft 1, and the input small ring gear 22 is fixed to the carrier 21
  • the planetary gear 20 cooperates with the fixed carrier 21 and the output large ring gear 23.
  • the fixed end of the carrier 21 and the overrunning clutch 5 are coupled to the fixed element, and the output large ring gear 23 is coupled to the input gear 25, and the input gear 25 is passed.
  • the planet gears 20 on the input carrier 24 cooperate with the input carrier 24 and the output ring gear 26, the output ring gear 26 is coupled to the input pinion 27, and the input pinion 27 passes through the planet gears 20 and the output planets on the output carrier 28.
  • the output carrier 28 is coupled to the output shaft 3, and the output gear 72 of the output gear pair 7 is coupled to the input 41 of the multi-element working wheel torque converter 4, the output 42 of the multi-component working wheel torque converter 4
  • the output end 52 of the overrunning clutch 5 and the input gear 61 of the input gear pair 6 are coupled, the output gear 62 of the input gear pair 6 is coupled to the input carrier 24, and the input carrier 24 is coupled to the input bull gear 29.
  • the input carrier 24 and the input gear 25 pass the power transmitted thereto through the planetary gear 20 on the input carrier 24 to the output ring gear 26, the output ring gear 26 is transmitted to the input pinion 27, the input pinion 27, and the input is large.
  • the gear 29 then converges the power delivered thereto through the planet gears 20 on the output carrier 28 to the output carrier 28.
  • the two power flows will vary according to the change of the rotational speed distribution between the two.
  • the rotational speed of the input carrier 24 and the input bull gear 29 is zero, the input gear 25 and the input are small.
  • the gear 27 is reduced in speed, and when the rotational speeds of the input carrier 24 and the input large gear 29 are continuously increased, the rotational speeds of the output ring gear 26 and the output carrier 28 also increase, that is, when the input carrier 24.
  • the rotational speed of the input bull gear 29 changes, the rotational speeds of the output ring gear 26, the output carrier 28, and the output shaft 3 also change.
  • the input power is split into two paths via the input shaft 1, and the first pass through the output gear pair 7 is transmitted to the multi-component working wheel torque converter 4, and then transmitted to the input carrier 24 via the input gear pair 6, and then transmitted to the input carrier 24
  • the input large gear 29; the other path is input to the small ring gear 22, and then the power is transmitted to the output large ring gear 23 through the planetary gear 20 on the fixed carrier 21, the output large ring gear 23 is transmitted to the input gear 25, and the input carrier 24.
  • the input gear 25 then passes the power transmitted thereto through the planetary gears 20 on the input carrier 24 to the output ring gear 26, and then to the input pinion 27, the input pinion 27, the input large gear 29, and the output planet.
  • the planetary gears 20 on the frame 28 confluent the power transmitted thereto to the output carrier 28 and then to the output shaft 3, thereby realizing the external output of the engine power through the output shaft 3.
  • the torque on the output ring gear 26, the output carrier 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 output ring gear 26 and the output planet.
  • the torque on the frame 28 and the output shaft 3 is larger, and conversely, the smaller, in the process, the multi-component working wheel torque converter 4 also acts as a torque converter, thereby realizing the driving resistance of the present invention with the vehicle.
  • a composite multi-component working wheel hydraulic torque converter that varies 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 It is transmitted to the input small ring gear 22, and then the power is transmitted to the output large ring gear 23 through the planetary gears 20 on the fixed carrier 21, and then transmitted to the input gear 25, wherein there is no power or relatively little power inflow at this time.
  • Input planet carrier 24, input large gear 29, and the input end 51 of the overrunning clutch 5 is coupled with the fixed component to limit the steering.
  • the steering of the input carrier 24 and the input bull gear 29 cannot be reversed from the input steering, and the rotational speed is zero. At this time, the input gear is transmitted to the input gear.
  • the power of 25 is transmitted to the output ring gear 26 through the planetary gears 20 on the input carrier 24, the output ring gear 26 is transmitted to the input pinion 27, and the input pinion 27 is passed through the planetary gears on the output carrier 28. 20 power is transmitted to the output planet carrier 28 and then to the output shaft 3.
  • the rotational speed of the output end 42 of the multi-component working wheel torque converter 4 is also gradually increased, and the rotational speeds of the input input carrier 24 and the input large gear 29 are also gradually increased, thereby causing the output ring gear 26 to be outputted.
  • the torque of the output carrier 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 multi-element working wheel hydraulic torque converter includes an input shaft 1, an output shaft 3, an input gear pair 4, a coupling gear 5, a coupling input gear pair 6, and a transcendental a clutch 7, a multi-component working wheel hydraulic torque converter 8, an output gear pair 9, a planetary gear 20, an input small ring gear 21, a fixed ring gear 22, and an output planet are disposed between the input shaft 1 and the output shaft 3.
  • the input end 81 of the torque converter 8 is coupled to the output gear 92 of the output gear pair 9, the output gear 62 of the input input gear pair 6 is coupled to the coupling input carrier 24, the coupled output carrier 29 is coupled to the input gear 30, and the input gear 30 is passed
  • the planetary gear 20 input to the carrier 31 cooperates with the input carrier 31 and the output gear 32.
  • the input carrier 31 is coupled to the output gear 42 of the input gear pair 4, and the output gear 32 is coupled to the output shaft 3.
  • the input input carrier 24 and the coupling ring gear 25 are connected to the output ring gear 26 by the planetary gears 20 coupled to the input carrier 24, and the output ring gear 26 is transmitted to the input large ring gear through the coupling gear 5.
  • the input large ring gear 27 the coupling input gear 28 converges the power transmitted thereto to the coupled output carrier 29 by the planetary gears 20 coupled to the output carrier 29.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the rotational speed of the input input carrier 24 and the coupled input gear 28 is zero, the ring gear 25 is coupled.
  • the input large ring gear 27 is used to reduce the speed and increase the torque
  • the rotational speed of the output ring gear 26 and the coupled output carrier 29 also increases.
  • the rotational speeds of the output ring gear 26, the coupled output carrier 29, and the output shaft 3 also change.
  • the input power is divided into three paths through the input shaft 1, and the first path is transmitted to the multi-component working wheel hydraulic torque converter 8 via the output gear pair 9, and the multi-component working wheel hydraulic torque converter 8 is divided into two paths.
  • One way is coupled to the input input carrier 24 via the coupled input gear pair 6 and the other to the coupled input gear 28; the second path is transmitted via the coupled input gear pair 4 To the input planet carrier 31; the third path is transmitted to the input small ring gear 21, the input small ring gear 21 is transmitted to the output carrier 23 through the planetary gears 20 on the output carrier 23, and then transmitted to the coupling ring gear 25,
  • the input input carrier 24 and the coupling ring gear 25 are connected to the output ring gear 26 by the planetary gears 20 coupled to the input carrier 24, and the output ring gear 26 is transmitted to the input large ring gear through the coupling gear 5.
  • the torque on the output ring gear 26, the coupled output carrier 29, and the output shaft 3 varies with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the output ring gear 26, the coupling
  • a continuously variable transmission of a compound multi-element working wheel torque converter that varies torque and speed while driving resistance.
  • 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 small ring gear 21, and then transmitting power to the output carrier 23 through the planetary gears 20 on the output carrier 23, and outputting the planet carrier 23 to the coupling ring gear 25, wherein there is no or less
  • the power flows into the input input carrier 24, the input input gear 28, and the input end 71 of the overrunning clutch 7 is coupled to the fixed element to limit the steering, so that the steering input carrier 26, the input input gear 28 can not be steered with the input In the opposite direction, the rotational speed is zero.
  • the power transmitted to the coupling ring gear 25 is transferred to the output ring gear 26 by the planetary gear 20 coupled to the input carrier 24, and the output ring gear 26 is passed again.
  • the coupling gear 5 is transmitted to the input large ring gear 27, and the input large ring gear 27 and the power transmitted thereto are coupled to the coupled output carrier 29 through the planetary gears 20 coupled to the output carrier 29.
  • the coupled output carrier 29 is transferred to the input gear 30.
  • the input gear 30, the input carrier 31, and the power transmitted thereto through the planetary gear 20 of the input carrier 31 are merged to the output gear 32, and the output gear 32 is transmitted to the output shaft. 3.

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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)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un convertisseur de couple hydraulique de roue de travail à éléments multiples composite. Une petite couronne dentée d'entrée (22) et une paire d'engrenages de sortie (7) sont reliées à un arbre d'entrée (1), une grande couronne dentée de sortie (23) est reliée à un engrenage d'entrée (25), une couronne dentée de sortie (26) est reliée à un pignon d'entrée (27), un porte-satellites de sortie (28) est relié à un arbre de sortie (3), la paire d'engrenages de sortie (7) est reliée à un convertisseur de couple hydraulique de roue de travail à éléments multiples (4), le convertisseur de couple hydraulique de roue de travail à éléments multiples (4) est relié à un embrayage à roue libre (5) et une paire d'engrenages d'entrée (6), la paire d'engrenages d'entrée (6) est reliée à un porte-satellites d'entrée (24), et le porte-satellites d'entrée (24) est relié à un grand engrenage d'entrée (29). En outre, l'invention concerne également une transmission à variation continue d'un convertisseur de couple hydraulique de roue de travail à éléments multiples composite.
PCT/CN2016/070210 2015-01-16 2016-01-06 Convertisseur de couple hydraulique de roue de travail à éléments multiples composite et transmission à variation continue WO2016112801A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680004312.7A CN107208770A (zh) 2015-01-16 2016-01-06 一种复合型多元件工作轮液力变矩器以及无级变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510021378.4A CN104712727B (zh) 2015-01-16 2015-01-16 一种复合型多元件工作轮液力变矩器以及无级变速器
CN201510021378.4 2015-01-16

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WO2016112801A1 true WO2016112801A1 (fr) 2016-07-21

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CN (4) CN104712727B (fr)
HK (3) HK1211660A1 (fr)
WO (1) WO2016112801A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104712727B (zh) * 2015-01-16 2016-03-16 吴志强 一种复合型多元件工作轮液力变矩器以及无级变速器

Citations (8)

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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
CN102022507A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型多元件工作轮液力变矩器
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
CN103939568A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型多元件工作轮液力变矩器以及无级变速器
CN104712727A (zh) * 2015-01-16 2015-06-17 吴志强 一种复合型多元件工作轮液力变矩器以及无级变速器

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GB1156049A (en) * 1965-11-01 1969-06-25 Inpower Works Ltd Improvements in or relating to Fluid Torque Transmitters.
DE19859458B4 (de) * 1997-12-23 2007-11-22 Luk Gs Verwaltungs Kg Getriebe
CN101598198B (zh) * 2008-06-06 2013-06-26 吴志强 一种复合型内锥输出行星锥式无级变速器
CN202091463U (zh) * 2011-05-16 2011-12-28 山推工程机械股份有限公司 一种新型液力变矩器
CN103939567B (zh) * 2014-05-07 2016-04-13 吴志强 一种具有综合式液力变矩器的无级变速器

Patent Citations (10)

* 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
CN102022507A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型多元件工作轮液力变矩器
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
CN103939568A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型多元件工作轮液力变矩器以及无级变速器
CN104712727A (zh) * 2015-01-16 2015-06-17 吴志强 一种复合型多元件工作轮液力变矩器以及无级变速器
CN105333091A (zh) * 2015-01-16 2016-02-17 吴志强 一种复合型多元件工作轮液力变矩器的无级变速器
CN105333087A (zh) * 2015-01-16 2016-02-17 吴志强 一种复合型多元件工作轮液力变矩器

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Publication number Publication date
HK1211660A1 (zh) 2016-05-27
CN104712727A (zh) 2015-06-17
CN105333087A (zh) 2016-02-17
CN104712727B (zh) 2016-03-16
HK1216337A1 (zh) 2016-11-04
CN105333091A (zh) 2016-02-17
HK1216338A1 (zh) 2016-11-04
CN107208770A (zh) 2017-09-26

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