WO2016112806A1 - Convertisseur de couple hydraulique composite ayant une soupape de débordement externe et transmission variable en continu - Google Patents

Convertisseur de couple hydraulique composite ayant une soupape de débordement externe et transmission variable en continu Download PDF

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Publication number
WO2016112806A1
WO2016112806A1 PCT/CN2016/070215 CN2016070215W WO2016112806A1 WO 2016112806 A1 WO2016112806 A1 WO 2016112806A1 CN 2016070215 W CN2016070215 W CN 2016070215W WO 2016112806 A1 WO2016112806 A1 WO 2016112806A1
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Prior art keywords
input
gear
output
carrier
coupled
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Application number
PCT/CN2016/070215
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English (en)
Chinese (zh)
Inventor
吴志强
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吴志强
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Filing date
Publication date
Application filed by 吴志强 filed Critical 吴志强
Priority to CN201680004299.5A priority Critical patent/CN107250614A/zh
Publication of WO2016112806A1 publication Critical patent/WO2016112806A1/fr

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H47/00Combinations of mechanical gearing with fluid clutches or fluid gearing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H47/00Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08Combinations 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H2702/00Combinations of two or more transmissions

Definitions

  • the invention belongs to the field of torque converter and shifting, and more particularly to a composite type external pressure-operated external torque converter for stepping vehicles, ships, railway locomotives and machine tools, and stepless transmission.
  • 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 type external relief hydraulic torque converter and a continuously variable transmission which have the advantages of short life, simple structure, convenient operation, low cost, energy saving and high efficiency.
  • Composite respirator external torque converter including input shaft (1), output shaft (3), relief valve external torque converter (4), overrunning clutch (5), input gear a pair (6) and an output gear pair (7), wherein the input shaft (1) and the output shaft (3) are provided with a planetary gear (20), a fixed carrier (21), an input pinion (22), Output large ring gear (23), output planet carrier (24), input ring gear (25), input gear (26), input planet carrier (27), input small ring gear (28), output ring gear (29),
  • the input pinion (22) and the input gear (71) of the output gear pair (7) are coupled to the input shaft (1), and the input pinion (22) is fixed to the fixed planet by the planet gear (20) on the fixed carrier (21).
  • 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 ring gear ( 25) Coupling, the input ring gear (25) cooperates with the output planet carrier (24) and the input gear (26) through the planetary gears (20) on the output carrier (24), and outputs the planet carrier (24) and the input small teeth.
  • Ring (28) is connected, input small ring gear (28) through the input planet carrier (27)
  • the gear (20) cooperates with the input carrier (27) and the output ring gear (29), and the input carrier (27) is coupled with the input gear (26) and the output gear (62) of the input gear pair (6), and the input gear is input.
  • the input gear (61) of the sub (6) and the output end (52) of the overrunning clutch (5) are coupled to the output end (42) of the external torque converter (4) of the relief valve, and the external valve of the overflow valve
  • the input end (41) of the torque converter (4) is coupled to the output gear (72) of the output gear pair (7), and the output ring gear (29) is coupled to the output shaft (3).
  • a continuously variable transmission of a composite relief valve external torque converter comprising an input shaft (1), an output shaft (3), an external hydraulic torque converter (4), and an overrunning clutch (5) ), input gear pair (6), coupled input gear pair (7), output gear pair (8), between the input shaft (1) and the output shaft (3), a planetary gear (20), an input gear (21), fixed planet carrier (22), output gear (23), coupled input planet carrier (24), coupling ring gear (25), output ring gear (26), input small ring gear (27), input large teeth Ring (28), coupled output planet carrier (29), input pinion (30), output planet carrier (31), input bull gear (32), input gear (21), input pinion (30), and output gear pair
  • the input gear (81) of (8) is coupled to the input shaft (1), and the input gear (21) is coupled to the fixed carrier (22) and the output gear (23) through the planetary gear (20) on the fixed carrier (22).
  • the output gear (23) is coupled to the input gear (71) of the input input gear pair (7), and the output gear (72) of the input input gear pair (7) is coupled to the coupled input carrier (24) to couple the input carrier (24) Planetary gears (20) and coupling teeth passing therethrough
  • the ring (25) and the output ring gear (26) work together to output the ring gear (26) and
  • the input large ring gear (28) is coupled, and the input large ring gear (28) cooperates with the input small ring gear (27) and the coupled output planet carrier (29) through the planetary gear (20) coupled to the output carrier (29).
  • the coupling ring gear (25), the input small ring gear (27), and the output end (52) of the overrunning clutch (5) are coupled to the output end (42) of the external torque converter (4) of the relief valve.
  • the input end (41) of the flow valve external torque converter (4) is coupled with the output gear (82) of the output gear pair (8), and is coupled to the input gear of the output carrier (29) and the input gear pair (6).
  • (61) coupled, the output gear (62) of the input gear pair (6) is coupled to the input bull gear (32), and the input large gear (32) passes through the planetary gear (20) on the output carrier (31) and the input pinion (30)
  • the output carrier (31) cooperates, and the output carrier (31) is coupled with 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 relief valve external 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 type relief valve external torque converter includes an input shaft 1, an output shaft 3, an overflow valve external torque converter 4, an overrunning clutch 5, and an input gear pair. 6.
  • the output gear pair 7 is provided with a planetary gear 20, a fixed carrier 21, an input pinion 22, an output large ring gear 23, an output carrier 24, and an input ring gear 25 between the input shaft 1 and the output shaft 3.
  • the input gear 26, the input carrier 27, the input small ring gear 28, the output ring gear 29, the input pinion 22 and the input gear 71 of the output gear pair 7 are coupled to the input shaft 1, and the input pinion 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 is coupled to the fixed component, and the output large ring gear 23 is coupled to the input ring gear 25, and the input ring gear is input. 25 cooperates with the output carrier 24 and the input gear 26 via the planetary gears 20 on the output carrier 24, the output carrier 24 is coupled to the input small ring gear 28, and the input small ring gear 28 is passed through the planetary gears 20 on the input carrier 27.
  • the input carrier 27 is coupled to the input gear 26 and the output gear 62 of the input gear pair 6, the input gear 61 of the input gear pair 6 and the output 52 of the overrunning clutch 5 and the output of the external torque converter 4 of the relief valve 42 is coupled, the input end 41 of the relief valve external torque converter 4 is coupled to the output gear 72 of the output gear pair 7, and the output ring gear 29 is coupled to the output shaft 3.
  • the input ring gear 25 and the input gear 26 converge the power transmitted thereto through the planetary gears 20 on the output carrier 24 to the output carrier 24, and the output carrier 24 is transmitted to the input small ring gear 28, the input carrier 27, and the input.
  • the small ring gear 28 then converges the power transmitted thereto through the planetary gears 20 on the input carrier 27 to the output ring gear 29.
  • 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 external torque converter 4 of the relief valve, and then transmitted to the input carrier 27 via the input gear pair 6, and then transmitted.
  • the input gear 26; the other pass through the input pinion 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 ring gear 25, and the input ring gear is input. 25.
  • the input gear 26 then converges the power transmitted thereto through the planetary gears 20 on the output carrier 24 to the output carrier 24, and then to the input small ring gear 28, the input carrier 27, the input small ring gear 28, and then The planetary gears 20 input to the carrier 27 converge the power transmitted thereto to the output ring gear 29 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 carrier 24, the output ring gear 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 carrier 24 and the output teeth.
  • the torque on the ring 29 and the output shaft 3 is larger, and conversely, the smaller, in the process, the external torque converter 4 of the relief valve also acts as a torque converter, thereby realizing the invention can travel with the vehicle.
  • a composite relief valve external torque converter that changes torque and speed with different 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 It is transmitted to the input pinion 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 ring gear 25, wherein there is no power or relatively little power inflow due to the current.
  • the input gear 26, the input carrier 27, and the input end 51 of the overrunning clutch 5 are coupled to the fixed element to restrict the steering, so that the steering of the input gear 26 and the input carrier 27 cannot be reversed from the input steering, and the rotational speed is zero.
  • the power transmitted to the input ring gear 25 is passed.
  • the planet gears 20 on the output planet carrier 24 transfer power to the output planet carrier 24, the output planet carrier 24 is passed to the input pinion 28, and the input small ring gear 28 is then powered by the planet gears 20 on the input carrier 27. It is transmitted to the output ring gear 29 and then to the output shaft 3.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a continuously variable transmission of a composite relief valve external torque converter includes an input shaft 1, an output shaft 3, an overflow valve external torque converter 4, and an overrunning clutch 5
  • the input gear pair 6, the input input gear pair 7, the output gear pair 8, the input shaft 1 and the output shaft 3 are provided with a planetary gear 20, an input gear 21, a fixed carrier 22, an output gear 23, and a coupling input.
  • the input pinion gear of the input pinion 30 and the output gear pair 8 is coupled to the input shaft 1.
  • the input gear 21 cooperates with the fixed carrier 22 and the output gear 23 through the planetary gear 20 on the fixed carrier 22, and the output gear 23 is coupled with
  • the input gear 71 of the input gear pair 7 is coupled, and the output gear 72 of the input input gear pair 7 is coupled to the coupling input carrier 24, and the planetary gear 20 coupled to the input carrier 24 is coupled with the coupling ring gear 25 and the output ring gear 26 through the planetary gear 20 thereon.
  • the ring gear 28 is coupled, and the input large ring gear 28 cooperates with the input small ring gear 27 and the coupled output carrier 29 through the planetary gear 20 coupled to the output carrier 29, the coupling ring gear 25, the input small ring gear 27 and the overrunning clutch
  • the output end 52 of the 5 is coupled to the output 42 of the relief valve external torque converter 4, and the input end 41 of the relief valve external torque converter 4 is coupled to the output gear 82 of the output gear pair 8 for coupling
  • the output carrier 29 is coupled to the input gear 61 of the input gear pair 6, the output gear 62 of the input gear pair 6 is coupled to the input bull gear 32, and the input bull gear 32 passes through the planetary gear 20 and the input pinion 30 on the output carrier 31,
  • the output carrier 31 cooperates, and the output carrier 31 is coupled to the output shaft 3.
  • the input input planet 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 planet carrier 24, and the output ring gear 26 is transmitted to the input large ring gear 28, and the input small teeth are input.
  • the ring 27, the input large ring gear 28, converges the power delivered thereto to the coupled output planet carrier 29 by the planet gears 20 coupled to the output carrier 29.
  • the input power is divided into three paths through the input shaft 1, and the first path is transmitted to the external torque converter 4 of the relief valve via the output gear pair 8, and the external torque converter 4 of the overflow valve is transmitted to the connection.
  • the coupling ring gear 25 is coupled to the output ring gear 26 by the planetary gears 20 coupled to the input carrier 24,
  • the output ring gear 26 is again transmitted to the input large ring gear 28, the input small ring gear 27, and the input large ring gear 28 is coupled to the power transmitted thereto by the planetary gears 20 coupled to the output carrier 29.
  • the planet carrier 29 is coupled to the output carrier 29 and then transmitted through the input gear pair 6 to the input bull gear 32.
  • the input pinion 30 and the input bull gear 32 converge the power transmitted thereto through the planet gears 20 on the output carrier 31.
  • the output carrier 31 is output, and the output carrier 31 is transmitted 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 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
  • the torque on the output planet carrier 29 and the output shaft 3 is larger, and conversely, the smaller, in the process, the relief valve external torque converter 4 also acts as a torque converter, thereby realizing the present invention.
  • a continuously variable transmission of a compound type external relief valve external torque converter that changes the torque and speed of the vehicle.
  • 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 gear 23 through the planetary gears 20 on the fixed carrier 22, and then transmitted to the coupled input carrier 24 through the coupled input gear pair 7, wherein there is no or less
  • the power flows into the coupling ring gear 25, the input small ring gear 27, and the input end 51 of the overrunning clutch 5 is coupled with the fixed element to restrict the steering, so that the steering ring 25 and the input small ring gear 27 cannot be turned with the input.
  • the rotational speed is zero.
  • the power transmitted to the input carrier carrier 24 is transferred to the output ring gear 26 through the planetary gear 20 thereon, and the output ring gear 26 is transmitted to the input.
  • the ring gear 28, the input large ring gear 28 is connected to the coupled output planet carrier 29 by the planetary gears 20 coupled to the output planet carrier 29, coupled to the output planet carrier 29 and then through the input teeth.
  • the sub 6 is transmitted to the input bull gear 32, the input pinion 30, the input bull gear 32 converges the power transmitted thereto through the planetary gear 20 on the output carrier 31 to the output carrier 31, and the output carrier 31 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)
  • Transmission Devices (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un convertisseur de couple hydraulique composite ayant une soupape de débordement externe. Un pignon d'entrée (22) et une paire d'engrenages de sortie (7) sont reliés à un arbre d'entrée (1), une grande couronne dentée de sortie (23) est reliée à une couronne dentée d'entrée (25), un porte-satellites de sortie (24) est relié à une petite couronne dentée d'entrée (28), un porte-satellites d'entrée (27) et un engrenage d'entrée (26) sont reliés à une paire d'engrenages d'entrée (6), la paire d'engrenages d'entrée (6) et un embrayage de dépassement (5) sont reliés à un convertisseur de couple hydraulique (4) ayant une soupape de débordement externe, le convertisseur de couple hydraulique (4) ayant la soupape de débordement externe est relié à la paire d'engrenages de sortie (7), et une couronne dentée de sortie (29) est reliée à un arbre de sortie (3). En outre, l'invention concerne également une transmission variable en continu d'un convertisseur de couple hydraulique composite ayant une soupape de débordement externe.
PCT/CN2016/070215 2015-01-16 2016-01-06 Convertisseur de couple hydraulique composite ayant une soupape de débordement externe et transmission variable en continu WO2016112806A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680004299.5A CN107250614A (zh) 2015-01-16 2016-01-06 一种复合型溢流阀外置式液力变矩器以及无级变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510021351.5A CN104653744B (zh) 2015-01-16 2015-01-16 一种复合型溢流阀外置式液力变矩器
CN2015100213515 2015-01-16

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WO2016112806A1 true WO2016112806A1 (fr) 2016-07-21

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CN (5) CN107218372A (fr)
HK (1) HK1211665A1 (fr)
WO (1) WO2016112806A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107218372A (zh) * 2015-01-16 2017-09-29 广州市志变制能科技有限责任公司 一种复合型阀控充液式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
CN102022509A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型溢流阀外置式液力变矩器
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
CN103939565A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型溢流阀外置式液力变矩器以及无级变速器
CN104653744A (zh) * 2015-01-16 2015-05-27 吴志强 一种复合型溢流阀外置式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
EP0321621B1 (fr) * 1987-12-23 1993-03-24 Honda Giken Kogyo Kabushiki Kaisha Transmission continue de vitesse pour véhicules automobiles
CN103161893B (zh) * 2008-06-06 2015-07-08 吴志强 一种复合外啮合行星齿轮机构的多档同时啮合变速器

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
CN102022509A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型溢流阀外置式液力变矩器
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
CN103939565A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型溢流阀外置式液力变矩器以及无级变速器
CN104653744A (zh) * 2015-01-16 2015-05-27 吴志强 一种复合型溢流阀外置式液力变矩器以及无级变速器

Also Published As

Publication number Publication date
HK1211665A1 (en) 2016-05-27
CN107166004A (zh) 2017-09-15
CN104653744B (zh) 2017-06-23
CN107218372A (zh) 2017-09-29
CN107314093A (zh) 2017-11-03
CN104653744A (zh) 2015-05-27
CN107250614A (zh) 2017-10-13

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