WO2020125329A1 - Transmission de puissance constante - Google Patents

Transmission de puissance constante Download PDF

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Publication number
WO2020125329A1
WO2020125329A1 PCT/CN2019/120542 CN2019120542W WO2020125329A1 WO 2020125329 A1 WO2020125329 A1 WO 2020125329A1 CN 2019120542 W CN2019120542 W CN 2019120542W WO 2020125329 A1 WO2020125329 A1 WO 2020125329A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
side plate
planetary
constant power
power transmission
Prior art date
Application number
PCT/CN2019/120542
Other languages
English (en)
Chinese (zh)
Inventor
潘国陶
Original Assignee
潘国陶
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
Priority claimed from CN201811546688.8A external-priority patent/CN109372970A/zh
Priority claimed from CN201822123763.1U external-priority patent/CN209164522U/zh
Application filed by 潘国陶 filed Critical 潘国陶
Publication of WO2020125329A1 publication Critical patent/WO2020125329A1/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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating

Definitions

  • the present invention relates to the field of transmission machinery, and more specifically, to a constant power transmission.
  • the invention number and the practical new model are 2018101117082 and 2018201977563 respectively.
  • the present invention is based on the principle of the previous application and is further optimized to form a new technical solution.
  • the object of the present invention is to provide a constant power transmission that can further simplify the structure or process and increase the volumetric efficiency.
  • a constant power transmission includes a differential gear train including a ring gear assembly, a sun gear assembly and a planet carrier assembly connected with a planetary gear mechanism, the planetary gear mechanism is provided with Two types of planetary gears, including transmission gears and sealed gears, the planet carrier assembly includes side plates, the side plates and the planetary gear mechanism combined with the ring gear assembly and the sun gear assembly form two high and low volume units, and the two volume units are connected Throttle channel.
  • the present invention has the following preferred or optional solutions:
  • the tooth height coefficients of the transmission gear and the sealing gear are different.
  • the side plate includes a front side plate, a floating side plate, and a rear side plate.
  • a planet wheel shaft is connected between the front side plate and the rear side plate, and the floating side plate is interposed on the planet wheel shaft.
  • a planetary shaft is connected between the front side plate and the rear side plate, and the planetary wheels are connected to the planetary shaft through an eccentric bushing.
  • the planet carrier assembly is provided with a packing block or a packing column.
  • a ferrule is connected between the front side plate and the rear side plate, and a heat sink is provided on the ferrule as needed.
  • the main advantage of the present invention is that it can improve the sealing performance of the transmission and reduce the throttle loss, thereby further improving the transmission efficiency.
  • FIG. 1 is a schematic cross-sectional view of a partial three-dimensional structure of an embodiment of the present invention
  • FIG. 2 is a schematic diagram of the auxiliary explanation of the present invention.
  • a constant power transmission includes a differential gear train.
  • the differential gear train includes an internal ring gear assembly, a sun gear assembly, and a planet carrier assembly connected with a planetary gear mechanism.
  • the planetary gear mechanism is provided with two types of planetary gears, including a transmission gear 20 With the sealing gear 19, the planet carrier assembly includes a side plate, the side plate and the planetary gear mechanism combined with the ring gear assembly and the sun gear assembly form two high- and low-pressure volume units, and a throttle channel is connected between the two volume units. Referring to FIG.
  • the inner ring gear assembly is the inner ring gear 21
  • the sun gear assembly is the sun gear 22 and the input shaft 23 connected or fixed thereto
  • the planet carrier assembly includes side plates
  • the side plates include a front side plate 11 and a floating side plate 12 and the rear side plate 17,
  • the planetary shaft 15 is connected between the front side plate 11 and the rear side plate 17,
  • the floating side plate 12 is axially movable on the planetary shaft 15, the floating side plate 12 and the front side plate 11
  • the gear is the inner ring gear 21, the sun gear 22, the transmission gear 20 and the sealing gear 19;
  • the ferrules 13 are connected between the rear side plates 17, and are fixed to each other by screws to form a planet carrier assembly.
  • the planet gear shaft 15 is also provided with screws to improve the connection strength.
  • the planetary gear mechanism is provided with two kinds of planetary gears, including a transmission gear 20 and a sealing gear 19.
  • the transmission gear 20 and the sealing gear 19 are sleeved on the planetary gear shaft 15 using an eccentric shaft sleeve 18, and the inner ring gear 21 and the sun gear are connected by a gear 22, the rear side plate 17 and the floating side plate 12 can be combined with the inner ring gear 21, the sun gear 22, the transmission gear 20, and the sealing gear 19 to construct two high and low volume units.
  • the transmission gear 20 and the sealing gear 19 can have multiple And the number is equal, and they are staggered with each other, so the high and low pressure volume units constructed in this way will also increase.
  • a throttle channel is connected between the two volume units.
  • the throttle channel communicates with the high-pressure volume unit.
  • a throttle valve can be set on the throttle channel to achieve constant power speed regulation.
  • the throttle channel is suitable for passing The side plate and the journal are led out to the housing to facilitate the setting of the throttle valve. Since internal leakage itself is also a throttling process, the throttling channel can also be a leakage channel between high and low pressure volume units, or artificially set a small channel on the side plate. In this case, it is not necessary to use a valve to adjust the speed.
  • the present invention is similar to a coupling with a speed regulation capability, and is applicable to a condition with relatively simple working conditions.
  • the present invention is basically similar to the structure of the previous application.
  • the main difference is that the sealing gear 19 is used to replace the role of the isolation block. Knowing the structure and scheme in the previous application in advance helps to better understand the present invention.
  • the side plate and the isolation block combine three gears: the ring gear 21, the sun gear 22 and the planetary gear to form a high and low pressure volume unit.
  • the sun gear 22 When the sun gear 22 is driven, the planet The wheel can rotate around its own center, or it can make rolling orbits with the tooth point as the fulcrum. The force arms of these two motion modes are different.
  • the amount of oil compressed by rotation is greater than the revolution, according to the pump
  • the differential gear train will tend to revolve and the output torque of the planet carrier assembly will be obtained. It is not enough to satisfy the pump effect.
  • the input end or output end must have a superimposed combined torque to have a torsion effect.
  • the high-pressure volume unit can only It is built on the right side of the planetary gear. At this time, the input torque, pump torque and motor torque are all in the same direction. After superposition, the planetary carrier assembly can get the same direction of the combined torque output. When the oil pressure is different, the combined torque is also different, so It can achieve torsion. If the high-pressure volume unit is built on the left side of the planetary gear, even if the pump effect is generated by the gear displacement, there is always no superimposed total torque output, which is invalid. The previously applied solution has been physically verified, and it is easy to understand the present invention based on the above. Referring to FIG.
  • the isolation block is removed in the present invention and the sealing gear 19 is used instead.
  • the sun gear 22 is driven clockwise, (pressure oil QA -Oil absorption QB)>0
  • the transmission gear 20 meets the pump effect and has a combined torque
  • the sealing gear 19 meets the motor effect
  • the torque generated by the motor effect depends on the effective displacement
  • ( The oil absorption QD-pressure oil QC) is very small, so the reverse torque generated by the motor effect due to self-interference is small.
  • the present invention has the following preferred or optional solutions:
  • the drive gear 20 and the seal gear 19 have different addendum coefficients. This is an ideal way to adjust the total displacement relationship. Increasing the pressure angle of the gear can increase the difference. If the gear is adjusted by displacement and other means, the displacement difference is adjusted to zero at the standard center distance, then the center distance of the transmission gear 20 is increased, and the center distance of the seal gear 19 is reduced (pressure oil QA) -Oil absorption QB)>0, (pressure oil QC-oil absorption QD)>0, this can also meet the pump effect, but this method needs to increase the backlash, and the gear is also easy to wear.
  • the side plate includes a front side plate 11, a floating side plate 12 and a rear side plate 17.
  • a planetary shaft 15 is connected between the front side plate 11 and the rear side plate 17.
  • the floating side plate 12 is inserted on the planetary shaft 15.
  • the floating side plate 12 mainly plays a role of end face compensation, and has been widely used in the field of high pressure to significantly improve the volumetric efficiency.
  • the sealing gear 19 has a toothed seal and end face compensation, its sealing effect will be superior to the isolation block solution.
  • the end face and the tooth gap can be eliminated by running-in or grinding. If metal self-healing agent is added to the oil during work, it can further eliminate the small gap and strengthen the contact characteristics. This is also the use of the sealing gear 19 instead of the isolation block in the present invention.
  • a plurality of floating side plates 12 can be provided, and multiple gear sets can be combined to form a series structure, which can increase the transmission capacity.
  • a planetary shaft 15 is connected between the front side plate 11 and the rear side plate 17, and the planetary gear is connected to the planetary shaft 15 through an eccentric bush 18.
  • FIG. 2 after the gear of the present invention is subjected to oil pressure, there will be 6 theoretical contact points a, b, c, d, e, f on the plane, but due to actual manufacturing or wear gaps, these 6 points Under rigid conditions, there can only be at most 5 contacts. Even if there are multiple planetary gears of the same type, the three points of each planetary gear cannot guarantee simultaneous contact. Although the same type of planetary gears can be improved by running in, but because The relative positions of the contact points are different, and the running-in of different planet wheels is also invalid.
  • the tooth-engaging portion is subjected to a large force.
  • it is necessary to achieve 6-point contact in practice.
  • the planetary gear shaft 15 can also be suspended to solve this problem, that is, the two ends of the planetary gear shaft 15 are connected to the side plates through the oil cylinder, but the oil cylinder has many disadvantages.
  • the planet carrier assembly is provided with a packing block or packing column 16.
  • a packing block or packing column 16 is connected between the side plates, and the purpose is to fill the gap between the two planet wheels to reduce oil compression loss and heat generation.
  • a centrifugal blade can be arranged on the side plate, and a channel is provided in the packing block or packing column 16. After introducing low-pressure cooling oil, it can be used for heat dissipation, or the cooling oil can be directly charged into the low-pressure volume unit to replace part of the hot oil.
  • a ferrule 13 is connected between the front side plate 11 and the rear side plate 17, and a heat sink is provided on the ferrule 13 as needed.
  • the ferrule 13 can make the planet carrier assembly play a role in strengthening the connection. Since the interior of the present invention is filled with metal components that are beneficial to heat dissipation, when applied to small and medium powers, the heat can be dissipated by itself, such as immersed in the oil pool, or further provided with fins on the ferrule 13 to dissipate heat by air cooling.
  • the main advantage of the present invention is that it can improve the sealing performance of the transmission and reduce the throttle loss, thereby further improving the transmission efficiency.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne une transmission de puissance constante, comprenant un train d'engrenages différentiels, le train d'engrenages différentiels comprenant un ensemble couronne de train planétaire interne, un ensemble roue solaire, et un ensemble porte-satellites relié à un mécanisme de train planétaire ; le mécanisme de train planétaire est pourvu de deux types de trains planétaires, comprenant un train de transmission (20) et un train d'étanchéité (19) ; l'ensemble porte-satellites comprend des plaques latérales ; les plaques latérales et le mécanisme de train planétaire se combinent avec l'ensemble couronne de train planétaire interne et l'ensemble roue solaire pour former une unité de volume élevé et une unité de faible volume ; et un canal d'étranglement est connecté entre les deux unités de volume. La présente transmission de puissance constante permet d'améliorer les performances d'étanchéité de la transmission et de réduire la perte d'étranglement, ce qui permet d'améliorer encore l'efficacité de transmission.
PCT/CN2019/120542 2018-12-18 2019-11-25 Transmission de puissance constante WO2020125329A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201811546688.8 2018-12-18
CN201822123763.1 2018-12-18
CN201811546688.8A CN109372970A (zh) 2018-12-18 2018-12-18 一种恒功率变速器
CN201822123763.1U CN209164522U (zh) 2018-12-18 2018-12-18 一种恒功率变速器

Publications (1)

Publication Number Publication Date
WO2020125329A1 true WO2020125329A1 (fr) 2020-06-25

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ID=71100680

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2019/120542 WO2020125329A1 (fr) 2018-12-18 2019-11-25 Transmission de puissance constante

Country Status (1)

Country Link
WO (1) WO2020125329A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2460098A1 (de) * 1974-12-19 1976-06-24 Gewerk Eisenhuette Westfalia Elektrischer kettenantrieb, insbesondere fuer hobelanlagen
DE3542184A1 (de) * 1985-11-29 1987-06-04 Konrad Heinrich Pro Langenbeck Selbstsperrendes planeten-differentialgetriebe
CN1266152A (zh) * 1999-09-15 2000-09-13 刘志国 行星液体阻尼无级变速器
CN103339409A (zh) * 2010-12-23 2013-10-02 玛格纳动力传动***股份及两合公司 传动单元
JP2015086951A (ja) * 2013-10-31 2015-05-07 株式会社ジェイテクト 歯車機構
CN108105359A (zh) * 2018-02-05 2018-06-01 潘国陶 一种无级变速器
CN109372970A (zh) * 2018-12-18 2019-02-22 潘国陶 一种恒功率变速器
CN209164522U (zh) * 2018-12-18 2019-07-26 潘国陶 一种恒功率变速器

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2460098A1 (de) * 1974-12-19 1976-06-24 Gewerk Eisenhuette Westfalia Elektrischer kettenantrieb, insbesondere fuer hobelanlagen
DE3542184A1 (de) * 1985-11-29 1987-06-04 Konrad Heinrich Pro Langenbeck Selbstsperrendes planeten-differentialgetriebe
CN1266152A (zh) * 1999-09-15 2000-09-13 刘志国 行星液体阻尼无级变速器
CN103339409A (zh) * 2010-12-23 2013-10-02 玛格纳动力传动***股份及两合公司 传动单元
JP2015086951A (ja) * 2013-10-31 2015-05-07 株式会社ジェイテクト 歯車機構
CN108105359A (zh) * 2018-02-05 2018-06-01 潘国陶 一种无级变速器
CN109372970A (zh) * 2018-12-18 2019-02-22 潘国陶 一种恒功率变速器
CN209164522U (zh) * 2018-12-18 2019-07-26 潘国陶 一种恒功率变速器

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