WO2024258312A1 - Boite de vitesses sans etage - Google Patents

Boite de vitesses sans etage Download PDF

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Publication number
WO2024258312A1
WO2024258312A1 PCT/RU2024/000185 RU2024000185W WO2024258312A1 WO 2024258312 A1 WO2024258312 A1 WO 2024258312A1 RU 2024000185 W RU2024000185 W RU 2024000185W WO 2024258312 A1 WO2024258312 A1 WO 2024258312A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
variator
continuously variable
variable transmission
coupled
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/RU2024/000185
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English (en)
Russian (ru)
Other versions
WO2024258312A8 (fr
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 RU2023115678A external-priority patent/RU2806843C1/ru
Application filed by Individual filed Critical Individual
Priority to CN202480007342.8A priority Critical patent/CN120569580A/zh
Priority to KR1020257028758A priority patent/KR20250164699A/ko
Priority to MX2025015029A priority patent/MX2025015029A/es
Priority to JP2025557565A priority patent/JP2026512432A/ja
Publication of WO2024258312A1 publication Critical patent/WO2024258312A1/fr
Publication of WO2024258312A8 publication Critical patent/WO2024258312A8/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuously variable friction gearing
    • F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuously variable friction gearing the toothed gearing 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
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/26—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members with members having orbital motion

Definitions

  • the invention relates to mechanical engineering, namely to drive devices with stepless change of speed and direction of rotation of the output shaft, and can be used in ground transport equipment.
  • a continuously variable transmission is known, disclosed in the Russian Federation patent for invention No. 2656941 (published on 07.06.2018, IPC F16H 15/50).
  • the continuously variable transmission comprises a friction variator and a simple three-link planetary mechanism consisting of a sun gear, an epicyclic wheel and a planet carrier with satellites.
  • the input and output shafts are installed in parallel, a toothed ring with a clutch for engaging the leading cylindrical gear, which is freely installed on the input shaft and meshed with the driven cylindrical wheel fixed to the epicyclic wheel housing.
  • a clutch for locking the planetary mechanism or stopping the epicyclic wheel is installed on the toothed ring of the tubular shaft of the housing.
  • the small friction wheel is mounted on the key of the input shaft, pressed against the large friction wheel of the driven shaft, which is connected to the sun gear by a bevel gear and a shaft.
  • the carrier is fixed on the output shaft.
  • the toothed crown of this shaft is located next to the toothed crowns of the tubular shaft of the epicyclic wheel housing and the continuously variable transmission housing.
  • a drive device is known, disclosed in the Russian Federation patent for invention No. 2748081 (published on 19.05.2021, IPC F16H 37/08).
  • the known drive device comprises a differential at the input, a planetary gear at the output, the carrier of which is made integral with the output shaft of the device, and a V-belt variator connected to the differential and the planetary gear via gears.
  • the revolutions of the differential axle shafts are changed by changing the gear ratio of the variator and are separately fed to the sun and ring gears of the planetary gear.
  • One of the flows is fed in the opposite direction of rotation.
  • the revolutions of the sun and ring gears are differentially dependent.
  • the continuously variable transmission Jatco JF015E is known - a prototype.
  • the well-known continuously variable transmission Jatco JF015E is characterized by a sequential arrangement of a torque converter, a package (gear block) of front and reverse gears, a variator and a two-stage reducer with a built-in interwheel differential.
  • the disadvantage of this variator box is the presence of a torque converter, a package (gear block) of front and reverse gears in the design, as well as a limited operational mileage of 200 ... 220 thousand kilometers. This is due to belt stretching, wear of the belt and working surfaces of the variator pulleys.
  • the Jatco JF015E variator box model is installed on passenger cars of Nissan, Mitsubishi, Chevrolet, Daewoo and other factories.
  • the technical problem underlying the present invention is to expand the range of V-belt continuously variable transmissions.
  • the technical result achieved by implementing the present invention consists in increasing the operating mileage of a V-belt continuously variable transmission.
  • the technical result is achieved by the present invention, which proposes a continuously variable transmission.
  • the proposed continuously variable transmission includes a primary shaft, a variator, which consists of a driving pulley and a driven pulley connected by a belt, a three-link planetary mechanism, which consists of a carrier with satellites, an epicycle and a sun gear, and an output shaft.
  • the proposed continuously variable transmission additionally includes a friction-tooth clutch, which is designed with the ability to connect and disconnect the primary shaft and the first gear connected to the first and second gear wheels, a toothed clutch, which is designed with the ability to connect and disconnect the driving pulley of the said variator and the second gear wheel, wherein the first gear wheel is connected to the carrier of the said planetary mechanism, wherein the epicycle of the said planetary mechanism is connected to the driven pulley of the said variator, and the satellites of the said planetary mechanism are connected to the sun gear, which is connected to the sequentially connected output shaft, the second gear wheel and the third gear wheel.
  • a friction-tooth clutch which is designed with the ability to connect and disconnect the primary shaft and the first gear connected to the first and second gear wheels
  • a toothed clutch which is designed with the ability to connect and disconnect the driving pulley of the said variator and the second gear wheel
  • the first gear wheel is connected to the carrier of the said planetary mechanism
  • the epicycle of the said planetary mechanism is connected to the
  • FIG. 1 shows the kinematic diagram of a continuously variable transmission
  • FIG. 2 shows the first diagram of the variator
  • FIG. 3 shows the second diagram of the variator
  • FIG. 4 shows the third variator diagram.
  • FIG. 1 shows the kinematic diagram of a continuously variable transmission.
  • the primary shaft 1 of the continuously variable transmission gearbox is connected with the friction-toothed clutch 2 and the first gear 3 located on the same axis.
  • the friction-toothed clutch is designed with the possibility of connecting and disconnecting the primary shaft 1 and the first gear 3.
  • the first gear 3 is engaged with the first gear wheel 4 and the second gear wheel 5.
  • the variator consists of a driving pulley 6 and a driven pulley 7, which are connected to each other by a belt 8.
  • the first gear wheel 4 is connected to the carrier 9 of the three-link planetary mechanism located on the same axis. Satellites 11 are mounted on the axes 10 of the carrier 9. Satellites 11 are engaged with the sun gear 12, which is connected to the sequentially connected output shaft 13, the second gear 14 and the third gear wheel 15.
  • the second gear wheel 5 is connected to the clutch 16, which is designed to connect and disconnect the second gear wheel 5 and the leading pulley 6 of the variator.
  • the driven pulley 7 of the variator is connected to the epicycle 17.
  • the epicycle 17 is engaged with the satellites 11.
  • the primary shaft 1 is connected to the crankshaft 18 of the internal combustion engine 19.
  • the third gear wheel 15 is connected to the drive wheels 20 via the interwheel differential 22.
  • the continuously variable transmission is assembled in housing 21.
  • the rotation speed of gear wheel 15, equal to the rotation speed of drive wheels 20, is determined by the formula: where ⁇ ] is the rotation frequency of the primary shaft 1, equal to the rotation frequency of the crankshaft 18, rpm;
  • the gear ratio of the planetary mechanism is determined by the following formula: where Zi2 is the number of teeth of the sun gear 12; zn ⁇ the number of teeth of the epicycle 17; is - gear ratio of the gear pair of the first pinion 3 and the first gear wheel 4.
  • the gear ratio of gear pairs 3 and 4 is determined by the following formula: where Z3 is the number of teeth of gear 3;
  • variable gear ratio of the variator is determined by the following formula: where ⁇ is the rotation speed of the leading pulley of the variator 6, rpm;
  • the box has the following operating modes: “Parking”, “Dynamic parking”, “Reverse”, “Neutral position”, “Forward movement”.
  • the gearbox operates as follows.
  • the rotation of the primary shaft 1 through the engaged friction-tooth clutch 2 and gear 3 simultaneously cause oppositely directed rotation of gear wheels 5 and 4.
  • the rotation of the second gear wheel 5 is perceived by the engaged clutch 16 and the leading pulley 6 of the variator, which through the belt 8 transmits rotation to the driven pulley of the variator 7.
  • the driven pulley 7 transmits rotation to the epicycle 17.
  • the rotation of the first gear wheel 4 is perceived by the planet carrier 9, which transmits diametrical rotation to the axes of the satellites 10 and the satellites 12.
  • the variator belt (Fig. 2) is in a certain middle position of its adjustment range, which is calculated based on the chain of gear ratios of the entire gearbox design.
  • the rotation speed of the output link of the gear wheel 15 has a zero value, which means that a torque converter is not required in this design of the gearbox.
  • the variator In the “Reverse” mode, the variator operates to accelerate (Fig. 3), the higher the rotation speed of the driven pulley 7, the more negative, relatively primary shaft 1, the speed of rotation of the output link of the gear wheel is 15.
  • a package (gear block) of front and reverse gears is not required.
  • the variator In the "Forward Movement” mode, the variator operates in deceleration (Fig. 4), the lower the rotation speed of the driven pulley 7, the higher, relative to the primary shaft 1, the rotation speed of the output link of the gear wheel 15.
  • a package (gear block) of the front and reverse gears is not required.
  • the friction-tooth clutch 2 is designed to disconnect the rotating primary shaft 1 from the gear 3 when the gearbox is operating in the "Parking" mode and to smoothly connect the rotating primary shaft 1 with the gear 3 when the gearbox is operating in the "Dynamic Parking” mode.
  • the clutch 16 is designed to protect the variator from overload when the gearbox is operating in the "Dynamic Parking" mode in the event that the following condition is not met:
  • M]5 MiU K
  • Mi is the torque on the primary shaft 1, equal to the torque of the internal combustion engine
  • Uk is the gear ratio of the box.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne des dispositifs d'actionnement avec un changement non étagé des tours minute et de la direction de rotation de l'arbre de sortie. Cette boîte de vitesses sans étage comprend un arbre primaire, un variateur, un mécanisme planétaire trois maillons et un arbre de sortie. Le variateur comprend une réa d'entraînement et une réa entraînée reliées par une courroie. La boîte de vitesses sans étage comprend en outre un embrayage à frottement-denté capable de coupler et découpler l'arbre primaire et un premier pignon connecté à des première et seconde roues dentées. La boîte de vitesses sans étage comprend également un embrayage denté pouvant coupler et découpler la réa d'entraînement du variateur et la seconde roue dentée. La première roue dentée est connectée au porte-satellite du mécanisme planétaire. L'épicycle du mécanisme planétaire est connecté à la réa entraînée du variateur, et les satellites du mécanisme planétaire sont connectés au pignon solaire qui est connecté à l'arbre de sortie, au second pignon et à la troisième roue dentée connectés en série. On simplifie ainsi la structure de la boîte de vitesses sans étages et on augmente sa fiabilité.
PCT/RU2024/000185 2023-06-15 2024-06-11 Boite de vitesses sans etage Ceased WO2024258312A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN202480007342.8A CN120569580A (zh) 2023-06-15 2024-06-11 无级变速箱
KR1020257028758A KR20250164699A (ko) 2023-06-15 2024-06-11 무단 변속기
MX2025015029A MX2025015029A (es) 2023-06-15 2024-06-11 Transmision continuamente variable
JP2025557565A JP2026512432A (ja) 2023-06-15 2024-06-11 無段変速機

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
RU2023115678A RU2806843C1 (ru) 2023-06-15 Бесступенчатая коробка передач
RU2023115678 2023-06-15

Publications (2)

Publication Number Publication Date
WO2024258312A1 true WO2024258312A1 (fr) 2024-12-19
WO2024258312A8 WO2024258312A8 (fr) 2025-10-23

Family

ID=93852782

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/RU2024/000185 Ceased WO2024258312A1 (fr) 2023-06-15 2024-06-11 Boite de vitesses sans etage

Country Status (5)

Country Link
JP (1) JP2026512432A (fr)
KR (1) KR20250164699A (fr)
CN (1) CN120569580A (fr)
MX (1) MX2025015029A (fr)
WO (1) WO2024258312A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004068932A (ja) * 2002-08-07 2004-03-04 Jatco Ltd パワースプリット型無段変速装置
WO2010125668A1 (fr) * 2009-04-30 2010-11-04 ジヤトコ株式会社 Dispositif de commande de transmission à variation continue basé sur une courroie, et procédé de commande afférent
RU2453749C1 (ru) * 2011-01-21 2012-06-20 Игорь Владимирович Леонов Устройство рекуперации энергии торможения
RU2748081C1 (ru) * 2020-10-19 2021-05-19 Александр Михайлович Рудник Устройство привода

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004068932A (ja) * 2002-08-07 2004-03-04 Jatco Ltd パワースプリット型無段変速装置
WO2010125668A1 (fr) * 2009-04-30 2010-11-04 ジヤトコ株式会社 Dispositif de commande de transmission à variation continue basé sur une courroie, et procédé de commande afférent
RU2453749C1 (ru) * 2011-01-21 2012-06-20 Игорь Владимирович Леонов Устройство рекуперации энергии торможения
RU2748081C1 (ru) * 2020-10-19 2021-05-19 Александр Михайлович Рудник Устройство привода

Also Published As

Publication number Publication date
MX2025015029A (es) 2026-02-03
JP2026512432A (ja) 2026-04-16
KR20250164699A (ko) 2025-11-25
CN120569580A (zh) 2025-08-29
WO2024258312A8 (fr) 2025-10-23

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