WO2017005182A1 - Coupleur façonné hydraulique composite, et démarreur - Google Patents

Coupleur façonné hydraulique composite, et démarreur Download PDF

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Publication number
WO2017005182A1
WO2017005182A1 PCT/CN2016/088746 CN2016088746W WO2017005182A1 WO 2017005182 A1 WO2017005182 A1 WO 2017005182A1 CN 2016088746 W CN2016088746 W CN 2016088746W WO 2017005182 A1 WO2017005182 A1 WO 2017005182A1
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WO
WIPO (PCT)
Prior art keywords
gear
input
output
coupled
coupling
Prior art date
Application number
PCT/CN2016/088746
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English (en)
Chinese (zh)
Inventor
吴志强
Original Assignee
吴志强
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 吴志强 filed Critical 吴志强
Priority to CN201680039010.3A priority Critical patent/CN107923507A/zh
Publication of WO2017005182A1 publication Critical patent/WO2017005182A1/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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • 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

Definitions

  • the invention belongs to the field of fluid couplings and starting, and more particularly to a composite hydraulic coupling and starter for various ground vehicles, ships, railway locomotives and machine tools.
  • the fluid coupling 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 hydraulic coupling and a starter which prolong the service life of the engine, has a simple structure, is convenient to operate, is low in cost, and is energy-saving and high-efficiency.
  • a composite hydraulic coupling and starter comprising an input shaft (1), a starter gear pair (3), a hydraulic profile coupling (4), a coupling frame (5), an output shaft (6), and an empty Gear shifting mechanism (7), coupling shaft (8), second one-way clutch (9), first one-way clutch (10), output gear pair (11), electromagnetic clutch (12), starting gear pair (13)
  • the overrunning clutch (14) is provided with a planetary gear (20), an input pinion (21), an output carrier (22), and an input large gear (23) between the input shaft (1) and the output shaft (6).
  • the coupling shaft (8) is coupled to the input end (71) of the neutral gear mechanism (7), the output gear (112) of the output gear pair (11), and the input end (121) of the electromagnetic clutch (12), the electromagnetic clutch ( 12)
  • the output gear (122) is coupled to the input gear (131) of the start gear pair (13), the output end (72) of the neutral gear mechanism (7) is coupled to the output shaft (6), and the coupling frame (5) is coupled to
  • the input carrier (29) is coupled, and the input planet carrier (29) cooperates with the fixed ring gear (27) and the output coupling gear (28) through the planetary gear (20) thereon, and the output coupling gear (28) and the input tooth
  • the ring (25) is coupled, and the input ring gear (25) cooperates with the fixed carrier (24) and the output gear (26) through the planetary gear (20) on the fixed carrier (24), and the output gear (26) and the first
  • the input end (91) of the two one-way clutch (9) is coupled, the output end (102) of the first one-way clutch (10)
  • a composite hydraulic profile coupling includes an input shaft (1), a hydraulic profile coupling (3), a one-way clutch (4), an output shaft (5), an output gear pair (6), and an input gear pair ( 7) an overrunning clutch (8) and a coupling gear pair (9), wherein the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input gear (21), and an output gear (22).
  • the elements that need to be coupled, and the elements that are separated by several other elements, can be connected to or through several other elements by means of a hollow or a coupling frame; when the coupled elements are gears or ring gears, Then, meshing or coupling; the gear ratio of each gear pair and the shifting mechanism is designed according to actual needs.
  • the hydraulic profile coupling can be replaced by a multi-element working wheel hydraulic torque converter.
  • the air-locking mechanism can select a clutch instead.
  • 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 enables the engine and the starter to operate in the region of the tempering speed, that is, the engine operates in a range of very small pollution discharge speeds, thereby avoiding the engine discharging a large amount of exhaust gas during idle speed and high speed operation, thereby reducing the number of exhaust gases.
  • the emission of exhaust gas is 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 drive train 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 vehicle speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity;
  • the invention reduces the transmission mechanism of the current starter machine, reduces the manufacturing cost, and only needs to face after the engine is started.
  • the motor is braked and separated to stop the drive.
  • the present invention is a composite hydraulic profile coupling and starter 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 diagram of a second embodiment of the present invention.
  • connection between the two elements is indicated by a thick solid line, and the thin solid line indicates that the two elements can be rotated relative to each other.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • a composite hydraulic profile coupling and starter includes an input shaft 1 , a starter gear pair 3 , a hydraulic profile coupling 4 , a coupling frame 5 , an output shaft 6 , and an idle gear mechanism 7.
  • the input shaft 1 is coupled to the input end 101 of the first one-way clutch 10, the output gear 132 of the starter gear set 13, and the input end 141 of the overrunning clutch 14, the output end 142 of the overrunning clutch 14 and the input pinion 21 and the starter gear pair
  • the output gear 32 of the starter gear pair 3 is coupled to the input gear 31 of the starter gear pair 3, and the input pinion 21 passes through the planetary gear 20 on the output carrier 22 and the output carrier 22, Input large gear 23 mutual Working together
  • the output carrier 22 is coupled to the coupling frame 5 and the input gear 111 of the output gear pair 11, the coupling shaft 8 and the input end 71 of the idle gear mechanism 7, the output gear pair 112 of the output gear pair 11, and the electromagnetic clutch 12
  • the input end 121 is coupled
  • the output gear 122 of the electromagnetic clutch 12 is coupled to the input gear 131 of the start gear pair 13
  • the output end 72 of the idle gear mechanism 7 is coupled to the output shaft 6, and
  • the coupling frame 5 is coupled to the input carrier 29 to input the planet The
  • the carrier 24 and the output gear 26 cooperate with each other, and the output gear 26 is coupled to the input end 91 of the second one-way clutch 9, the output end 102 of the first one-way clutch 10 and the output end 92 of the second one-way clutch 9 and the liquid
  • the input end 41 of the force-type coupling 4 is coupled, the output end 42 of the hydrodynamic coupling 4 is coupled to the input bull gear 23, the fixed planet carrier 24 is coupled to the fixed ring gear 27, and the fixed ring gear 27 is coupled to the fixed element.
  • the neutral shifting mechanism 7 is disengaged and the electromagnetic clutch 12 is engaged.
  • the input power of the starter is transmitted to the input pinion 21 through the starter gear pair 3, and the input pinion 21 is transmitted to the planetary gear 20 on the output carrier 22 to
  • the output carrier 22, the output carrier 22 is transmitted to the input shaft 1 through the output gear pair 11, the coupling shaft 8, the electromagnetic clutch 12, and the start gear pair 13, and then transmitted to the engine crankshaft, and the generated driving force is sufficient to overcome the engine starting resistance.
  • the idle gear mechanism 7 After the engine is started, the idle gear mechanism 7 is engaged, the electromagnetic clutch 12 is disengaged, and the input shaft 1 splits the power transmitted from the engine into two paths, one pass through the first one-way clutch 10 and the hydraulic profile coupling 4 to the input. Big
  • the gear 23 is passed through the overrunning clutch 14 to the input pinion 21, and the input pinion 21, the input bull gear 23, transmits the respective power to the respective output carrier 22 through the planetary gear 20 on the output carrier 22.
  • the output planet carrier 22 splits the power transmitted thereto into two paths, one through the output gear pair 11, the coupling shaft 8 and the air-gear mechanism 7 to the output shaft 6 of the present invention; the other path is transmitted to the output shaft 6 through the coupling frame 5
  • the input carrier 29 is input to the carrier 29 and transmitted to the output coupling gear 28 via the planetary gear 20 thereon.
  • the output coupling gear 28 is transmitted to the input ring gear 25, and the input ring gear 25 is passed through the planetary gear 20 on the fixed carrier 24.
  • the torque on the input bull gear 23, the output carrier 22, and the output shaft 6 varies with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the input large gear 23 and the output planet.
  • the torque on the frame 22 and the output shaft 6 is larger, and conversely, the smaller, thereby realizing the composite hydraulic coupling and the starter which can change the torque and speed according to the difference in the running resistance of the present invention.
  • the idle gear mechanism 7 When the invention is used, before the engine is started, the idle gear mechanism 7 is disengaged, the electromagnetic clutch 12 is engaged, and the engine speed is zero.
  • the starter When the starter is started, the input power of the starter is transmitted to the input pinion 21 through the starter gear pair 3, The input pinion 21 transmits power to the output carrier 22 through the planetary gears 20 on the output carrier 22, and the output carrier 22 is transmitted to the input shaft through the output gear pair 11, the coupling shaft 8, the electromagnetic clutch 12, and the start gear pair 13. 1, then transferred to the engine crankshaft, the generated starting power is enough to overcome the engine starting resistance, the engine starts.
  • the input power, input speed and load of the engine are set to be constant, that is, the speed and torque of the input shaft 1 are constant.
  • the idle gear mechanism 7 is engaged, the electromagnetic clutch 12 is separated, and the input shaft 1 is The power split to the engine is divided into two paths, one through the second one-way clutch 10 and the hydrodynamic coupling 4 to the coupled input bull gear 23, the other through the overrunning clutch 14 to the input pinion 21, the input pinion 21.
  • the input bull gear 23 converges the respective powers through the planet gears 20 on the output carrier 22 to the output carrier 22, and the output carrier 22 splits the power transmitted thereto into two paths, one through the output gear pair. 11.
  • the coupling shaft 8 and the idle gear mechanism 7 are transmitted to the output shaft 6 of the present invention; the other passage is transmitted through the coupling frame 5 to the input carrier 29, and the input carrier 29 is transmitted to the output coupling gear through the planetary gear 20 thereon. 28, the output coupling gear 28 is transmitted to the input ring gear 25, and the input ring gear 25 is transmitted to the output gear 26 through the planetary gear 20 on the fixed carrier 24, and the output gear 26 is output.
  • the second one-way clutch 9, the first one-way clutch 10, and the hydrodynamic coupling 4 are transmitted to the input bull gear 23, and the input pinion 21 and the input large gear 23 transmit the respective power to the output carrier 22.
  • the planetary gear 20 merges with the output carrier 22, and the output carrier 22 continuously repeats the shifting of the shifting between the respective components, wherein the output rotational speed of the hydrodynamic coupling 4 is continuously stepless as the running resistance changes. Shifting the ground so that the output rotational speed of the output carrier 22 is also constantly changing, and is transmitted to the output shaft 6 of the present invention through the output gear pair 11, the coupling shaft 8, and the neutral gear mechanism 7, so that the torque of the output shaft 6 is varied. As the speed increases, it decreases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a composite hydraulic profile coupling includes an input shaft 1, a hydraulic profile coupling 3, a one-way clutch 4, an output shaft 5, an output gear pair 6, an input gear pair 7, and an overrunning clutch.
  • Coupling gear pair 9 the input shaft 1 and the output shaft 5 are provided with a planetary gear 20, an input gear 21, an output gear 22, an input carrier 23, a fixed carrier 24, an input ring gear 25, a coupling output gear 26, an input large gear 27, and an output carrier 28.
  • the input pinion 29 is coupled to the input carrier 13 and the input end 81 of the overrunning clutch 8, the input end 81 of the overrunning clutch 8 is coupled to the input gear 61 of the output gear pair 6, and the output gear 62 of the output gear pair 6 is output.
  • the output 82 of the overrunning clutch 8 is coupled to the input end 31 of the hydrodynamic clutch 3 and the output 42 of the one-way clutch 4, the input 41 of the one-way clutch 4 and the input gear pair 7
  • the output gear 72 is coupled, the input gear 71 of the input gear pair 7 is coupled to the coupling output gear 26, the output 32 of the hydrodynamic coupling 3 is coupled to the input gear 21, and the input gear 21 is passed through the planetary gear 20 on the input carrier 23.
  • the output gear 22 and the input carrier 23 cooperate with each other.
  • the output gear 22 is coupled to the input gear 91 of the coupling gear pair 9.
  • the output gear 92 of the coupling gear pair 9 is coupled to the input ring gear 25 and the input bull gear 27, and the input ring gear 25 is input.
  • the planetary gear 20 on the fixed carrier 24 cooperates with the fixed carrier 24 and the coupled output gear 26, the fixed carrier 24 is fixed to the fixed component, and the input large gear 27 passes through the planetary gear 20 and the output on the output carrier 28.
  • the planet carrier 28 and the input pinion 29 cooperate with each other, and the output carrier 28 is coupled to the output shaft 5.
  • the input gear 21 and the input carrier 23 converge the transmission power to the respective output gears 22 through the planetary gears 20 on the input carrier 23. Since the output gear 22 is coupled to the hydrodynamic coupling 3, the rotational speed of the output gear 22 can be It constantly changes with the change in the rotational speed of the hydrodynamic coupling 3, so that the rotational speed of the output gear 22 also changes.
  • the input power is split into two paths through the input shaft 1, one way is transmitted to the input planet carrier 23, and the other path is split into two paths through the overrunning clutch 8, one way is transmitted to the hydraulic profile coupling 3, and then transmitted to the input gear 21, the other way It is transmitted to the input pinion 29 through the output gear pair 6, the input gear 21, the input carrier 23, and the planetary gear 20 transmitted to the respective power passing through the input carrier 23 is merged with the output gear 22, and the output gear 22 is passed through the coupling gear pair.
  • the coupling output gear 26 is transmitted to the input gear 21 through the input gear pair 7, the one-way clutch 4, the overrunning clutch 8, and the hydrodynamic coupling 3, that is, the input power of the input gear 21 is increased accordingly.
  • the input gear 21 and the input carrier 23 merge the planetary gears 20 transmitted to the respective powers through the input carrier 23 to the output gear 22, and the output gear 22 repeats the above process to continuously transmit the rotational speed to the input large gear 27.
  • the input bull gear 27 and the input pinion 29 converge the planetary gears 20 that are transmitted to the respective power through the output carrier 28 to the output carrier 28, and the output carrier 28 is transmitted to the output shaft 5 of the present invention.
  • the power of the engine is externally output through the output shaft 5.
  • the rotational speed input to the large gear 27 changes with the input power or running resistance of the vehicle, and the lower the resistance, the higher the rotational speed transmitted to the input bull gear 27 High, and vice versa, the lower the cross-section, so that the composite hydrodynamic coupling of the present invention can change speed with different input power or running resistance 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 5 is zero, and the input power of the engine passes through the input shaft 1 Diverted to Two ways, one way is transmitted to the input planet carrier 23, the other way is split into two paths through the overrunning clutch 8, one way is transmitted to the hydraulic profile coupling 3, and then to the input gear 21, and the other way is transmitted to the input through the output gear pair 6.
  • the pinion gear 29, the input gear 21, and the input carrier 23 converge the planetary gears 20 that are transmitted to the respective powers through the input carrier 23 to the output gear 22, and the output gears 22 are split into two paths by the coupling gear pair 9, one pass.
  • the input bull gear 27 and the input pinion 29 converge the planetary gear 20 transmitted to the respective power through the output carrier 28 to the output carrier 28, and the output carrier 28 is transmitted to the present invention.
  • the output shaft 5 is such that the power of the engine is externally output through the output shaft 5.
  • the vehicle starts to accelerate.
  • the resistance of the output shaft 5 decreases, the other is transmitted to the input.
  • the power of the ring gear 25 is increased accordingly, and the input ring gear 25 transmits power to the coupled output gear 26 through the planetary gears 20 on the fixed carrier 24, and the output gear 26 is coupled to the input gear pair 7 and the one-way clutch 4.
  • the overrunning clutch 8 and the hydraulically shaped coupling 3 are transmitted to the input gear 21, that is, the input power of the input gear 21 is increased, and the input gear 21 and the input carrier 23 transmit the respective powers to the input carrier 23.
  • the planetary gear 20 merges with the output gear 22, and the output gear 22 repeats the above process to continuously change the rotational speed transmitted to the input bull gear 27, and the input large gear 27 and the input pinion 29 transmit the respective power to the output carrier.
  • the planet gears 20 on 28 converge on the output planet carrier 28, and the output planet carrier 28 is transferred to the output shaft 5 of the present invention, and the torque transmitted to the output shaft 5 is transmitted through
  • the vehicle continues to accelerate, and the rotational speed of the output end 32 of the hydraulic profile coupling 3 is also gradually increased, and the rotational speed of the input gear 21 associated with it is also This is gradually increased, so that the rotational speeds on the output gear 22, the input bull gear 27, and the output shaft 5 are continuously increased.

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

Abstract

L'invention concerne un coupleur façonné hydraulique composite, et un démarreur présentant ledit coupleur façonné hydraulique composite ; un arbre d'entrée (1) est raccordé à un premier embrayage unidirectionnel (10), à une paire d'engrenages de démarrage (13), et à un embrayage à roue libre (14) ; l'embrayage à roue libre (14) est raccordé à un petit engrenage d'entrée (21) et à une paire d'engrenages de démarreur (3) ; un porte-satellites de sortie (22) est raccordé à un cadre de liaison (5) et à une paire d'engrenages de sortie (11) ; un arbre de liaison (8) est raccordé à un mécanisme de changement de vitesse nul (7), à la paire d'engrenages de sortie (11) et à un embrayage électromagnétique (12) ; l'embrayage électromagnétique (12) est raccordé à la paire d'engrenages de démarrage (13) ; le mécanisme de changement de vitesse nul (7) est raccordé à un arbre de sortie (6) ; le cadre de liaison (5) est raccordé à un porte-satellites d'entrée (29) ; un engrenage de liaison de sortie (28) est raccordé à une couronne d'entrée (25) ; un engrenage de sortie (26) est raccordé à un deuxième embrayage unidirectionnel (9) ; le premier embrayage unidirectionnel (10) est raccordé au deuxième embrayage unidirectionnel (9) et à un coupleur façonné hydraulique (4) ; le coupleur façonné hydraulique (4) est raccordé à un grand engrenage d'entrée (23).
PCT/CN2016/088746 2015-07-07 2016-07-06 Coupleur façonné hydraulique composite, et démarreur WO2017005182A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680039010.3A CN107923507A (zh) 2015-07-07 2016-07-06 一种复合式液力异型偶合器以及起动器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510389859.0A CN104976304A (zh) 2015-07-07 2015-07-07 一种复合式液力异型偶合器以及起动器
CN201510389859.0 2015-07-07

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WO2017005182A1 true WO2017005182A1 (fr) 2017-01-12

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CN (2) CN104976304A (fr)
HK (1) HK1211671A1 (fr)
WO (1) WO2017005182A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104976304A (zh) * 2015-07-07 2015-10-14 吴志强 一种复合式液力异型偶合器以及起动器

Citations (7)

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GB624858A (en) * 1942-01-09 1949-06-17 Borg Warner Improvements in or relating to variable-speed transmissions and control mechanisms therefor
DE19809464A1 (de) * 1998-03-06 1999-09-16 Voith Turbo Kg Anfahrvarianten für 6-Gang-Wandlerautomatgetriebe
WO2003016751A1 (fr) * 2001-08-17 2003-02-27 Korotkov Eduard Konstantinovic Transmission holonome universelle a variation infinie de couple
CN102358159A (zh) * 2011-08-05 2012-02-22 上海中科深江电动车辆有限公司 具有液力变矩器的混合驱动系统
CN104482161A (zh) * 2014-12-12 2015-04-01 吴志强 一种复合式液力异型偶合器以及起动器
CN104534053A (zh) * 2014-12-12 2015-04-22 吴志强 一种复合型液力传动器以及起动器
CN104976304A (zh) * 2015-07-07 2015-10-14 吴志强 一种复合式液力异型偶合器以及起动器

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DE19527754A1 (de) * 1994-08-30 1996-03-07 Steyr Daimler Puch Ag Hydrostatisch-mechanisches Leistungsverzweigungsgetriebe
CN102022514B (zh) * 2009-09-09 2014-05-07 吴志强 一种复合型轴流式液力变矩器
CN104295680A (zh) * 2009-09-09 2015-01-21 吴志强 一种紧凑型行星传动变速器
CN102312980B (zh) * 2010-07-07 2015-01-28 吴志强 一种复合型后置齿轮箱体式液力偶合器
US20120302386A1 (en) * 2011-05-25 2012-11-29 Caterpillar Inc. Triple hybrid transmission system
CN104633040A (zh) * 2014-12-12 2015-05-20 吴志强 一种复合型双腔液力偶合器以及起动器
CN106402323A (zh) * 2014-12-12 2017-02-15 吴志强 一种复合型叶轮式液力变矩器以及起动器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB624858A (en) * 1942-01-09 1949-06-17 Borg Warner Improvements in or relating to variable-speed transmissions and control mechanisms therefor
DE19809464A1 (de) * 1998-03-06 1999-09-16 Voith Turbo Kg Anfahrvarianten für 6-Gang-Wandlerautomatgetriebe
WO2003016751A1 (fr) * 2001-08-17 2003-02-27 Korotkov Eduard Konstantinovic Transmission holonome universelle a variation infinie de couple
CN102358159A (zh) * 2011-08-05 2012-02-22 上海中科深江电动车辆有限公司 具有液力变矩器的混合驱动系统
CN104482161A (zh) * 2014-12-12 2015-04-01 吴志强 一种复合式液力异型偶合器以及起动器
CN104534053A (zh) * 2014-12-12 2015-04-22 吴志强 一种复合型液力传动器以及起动器
CN104976304A (zh) * 2015-07-07 2015-10-14 吴志强 一种复合式液力异型偶合器以及起动器

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CN107923507A (zh) 2018-04-17
CN104976304A (zh) 2015-10-14

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