WO2016029719A1 - Mécanisme de changement de vitesse à chevauchement d'engrenages - Google Patents

Mécanisme de changement de vitesse à chevauchement d'engrenages Download PDF

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Publication number
WO2016029719A1
WO2016029719A1 PCT/CN2015/079228 CN2015079228W WO2016029719A1 WO 2016029719 A1 WO2016029719 A1 WO 2016029719A1 CN 2015079228 W CN2015079228 W CN 2015079228W WO 2016029719 A1 WO2016029719 A1 WO 2016029719A1
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WO
WIPO (PCT)
Prior art keywords
clutch
gear
driven
wheel
shifting
Prior art date
Application number
PCT/CN2015/079228
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English (en)
Chinese (zh)
Inventor
解利
梅天放
Original Assignee
解利
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 CN201410434004.0A external-priority patent/CN105370879B/zh
Priority claimed from CN201510014762.1A external-priority patent/CN104633017A/zh
Application filed by 解利 filed Critical 解利
Priority to CN201580000487.6A priority Critical patent/CN105793607B/zh
Publication of WO2016029719A1 publication Critical patent/WO2016029719A1/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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted

Definitions

  • the invention relates to a shifting device, in particular to a shifting device with overlapping gear positions, belonging to the technical field of mechanical transmission variable speed and twisting.
  • the transmission is a mechanism used to change the speed and torque from the engine. It can change the output shaft and input shaft ratio by fixed or split gear, also known as the gearbox. Transmissions typically include a shifting transmission and steering mechanism. Most of the transmission mechanisms are driven by ordinary gears, and some are driven by planetary gears.
  • the transmission is divided into manual and automatic.
  • the manual transmission is mainly composed of gears and shafts.
  • the variable speed torque is generated by different gear combinations.
  • the automatic transmission AT is composed of a hydraulic torque converter, planetary gears and hydraulic control system.
  • the force transmission and gear combination are used to achieve the variable speed torque.
  • the main functions of the transmission are as follows: changing the transmission ratio; enabling the car to reverse when the engine rotates in the same direction; using the neutral gear to interrupt the power transmission, enabling the engine to start and idle, facilitating transmission shifting or power output.
  • the automatic transmission AT is composed of a hydraulic torque converter, a planetary gear and a hydraulic operating system, and the variable speed torque is achieved by a combination of hydraulic transmission and gear combination.
  • the hydraulic torque converter is the most characteristic component of AT. It consists of components such as pump wheel, turbine and guide wheel, and directly inputs the engine power transmission torque and separation.
  • Commonly used transmissions are of the following types: hydraulic automatic transmissions, hydraulic transmission automatic transmissions, electric transmission automatic transmissions, stepped mechanical automatic transmissions, and stepless mechanical automatic transmissions.
  • the most common is the hydraulic automatic transmission.
  • the hydraulic automatic transmission is mainly composed of a hydraulically controlled gear shifting system, and mainly includes an automatic clutch and an automatic transmission. It can automatically perform shifting according to the opening of the throttle and the change of the speed of the vehicle.
  • the automatic transmissions commonly used in automobiles are classified into CVT continuously variable transmissions, AT automatic transmissions, DCT dual clutch transmissions, parallel shaft transmissions, and AMT type automatic transmissions.
  • CVT continuously variable transmissions AT automatic transmissions
  • DCT dual clutch transmissions DCT dual clutch transmissions
  • parallel shaft transmissions parallel shaft transmissions
  • AMT type automatic transmissions AMT type automatic transmissions.
  • AMT transmission shifting slow and smooth phase difference Such as AMT transmission shifting slow and smooth phase difference; CVT transmission load is small, rapid acceleration is easy to slip; DCT transmission cost is high in structure and complex, frequent shift failure rate is high, can not be single or double jump, dry clutch is easy to generate too much heat The friction of the wet clutch is not enough; the AT automatic transmission has a slow response to the speed change, and the structure is complicated and the fuel consumption is high.
  • the problem to be solved by the invention is how to make the gear shifting quality more comfortable, the shifting speed is faster, and the transmission speed is faster.
  • the dynamic torque is larger, the structure is simpler, the control is simpler, and the fuel economy is environmentally friendly.
  • the present invention provides a shifting device in which the gear positions are overlapped.
  • a gear shifting device with overlapping gears includes a power input shaft and a power output shaft.
  • the power input shaft is provided with a plurality of driving wheels, each of which has a corresponding gear position, and a plurality of driven wheels are correspondingly mounted on the power output shaft.
  • Each driven wheel corresponds to one gear position;
  • a shifting shaft is arranged in the power input shaft, and a piston is fixed at one end of the shifting shaft, and the outer side of the piston is a first hydraulic pressure chamber for controlling the shifting; each driving wheel is provided with a one-way clutch and a clutch, and the clutch can be The oil pressure control of the first oil pressure chamber is in a combined state, and the power input shaft is rotated by the working end of the clutch drive driving wheel, and the working end of the driving wheel meshes with the driven wheel on the power output shaft.
  • the one-way clutch is mounted on the power input shaft, the clutch is located outside the one-way clutch; the clutch oil chamber and the clutch piston are disposed in the driving wheel, and the clutch oil chamber can communicate with the first oil pressure chamber, the clutch piston It can be driven by oil pressure to put the clutch in the combined state.
  • a gear shifting device with overlapping gears includes a power input shaft and a power output shaft.
  • the power input shaft is provided with a plurality of driving wheels, each of which has a corresponding gear position, and a plurality of driven wheels are correspondingly mounted on the power output shaft.
  • Each of the driven wheels corresponds to one gear position, and a shifting shaft is disposed in the power output shaft, and a piston is fixed at one end of the shifting shaft, and the outer chamber of the piston is a third oil pressure chamber for controlling the shifting;
  • the driven wheel is provided with a one-way clutch and a clutch. The clutch can be controlled by the oil pressure of the third oil pressure chamber, and the driven wheel drives the power output shaft to rotate through the clutch.
  • the one-way clutch in the driven wheel is mounted on the power output shaft, the clutch is located outside the one-way clutch; the clutch oil chamber and the clutch piston are also disposed in the driven wheel, and the clutch oil chamber and the third oil pressure chamber are In communication, the clutch piston can be driven by oil pressure to bring the clutch into engagement.
  • a gear shifting device with overlapping gears includes a power input shaft and a power output shaft.
  • the power input shaft is provided with at least seven driving wheels, each of which has a corresponding gear position, and at least seven corresponding power output shafts are mounted on the power output shaft.
  • the driven wheel, each driven wheel corresponds to a gear position, and the power input shaft is provided with a first gear drive wheel, a second gear drive wheel, a third gear drive wheel, a fourth gear drive wheel, and a fifth gear drive wheel.
  • the sixth gear drive wheel and the seventh gear drive wheel, the power output shaft is provided with a first gear driven wheel, a second gear driven wheel, a third gear driven wheel, a fourth gear driven wheel, a fifth gear driven wheel, and a sixth gear.
  • a driven driven wheel and a seventh driven wheel each of which is provided with a clutch and an overrunning clutch outside the driving wheel
  • the clutch is controlled by the shifting oil pressure
  • the power output shaft drives the working end of the driven wheel through the clutch and the overrunning clutch to rotate
  • the working end of the moving wheel meshes with the driving wheel on the power input shaft, or the power input shaft drives the working end of the driving wheel through the clutch and the overrunning clutch, and the working end of the driving wheel meshes with the driven wheel on the power output shaft .
  • a clutch and an overrunning clutch are arranged outside each of the driven wheels, the clutch is controlled by the shifting oil pressure, and the power output shaft drives the working end of the driven wheel through the clutch and the overrunning clutch, and the working end of the driven wheel and the power input shaft a driving wheel engagement, wherein the first gear driven wheel and the first
  • the second-speed driven wheel is a common clutch type connection; the third-speed driven wheel and the fourth-speed driven wheel are a common overrunning clutch type connection; the fifth-speed driven wheel and the sixth-speed driven wheel respectively pass the clutch with the power output shaft
  • the shaft transmission connection is connected to the power output shaft through the overrunning clutch shaft.
  • each of the driving wheels is provided with a clutch and an overrunning clutch, the clutch is controlled by the shifting oil pressure, and the power input shaft drives the working end of the driving wheel through the clutch and the overrunning clutch, and the working end of the driving wheel and the power output shaft
  • the upper driven wheel is engaged, wherein the first gear drive wheel and the second gear drive wheel are co-clutch type connection; the third gear drive wheel and the fourth gear drive wheel are connected by a common overrunning clutch;
  • the gear drive wheel and the sixth gear drive wheel are respectively connected to the power input shaft through the clutch shaft, and the seventh gear driven wheel and the power input shaft are connected by the overrunning clutch shaft.
  • a shifting device with overlapping gears includes: a power input shaft, a power output shaft and a plurality of shifting units that are driven in parallel, wherein the power input shaft, the plurality of shifting units, and the power output shaft are sequentially driven in series;
  • the shifting unit includes a transmission, a clutch and an overrunning clutch, and the transmission includes a driving wheel and a driven wheel;
  • the transmission is driven in series with the clutch and the overrunning clutch in any order.
  • the transmission, the clutch and the overrunning clutch are serially driven in series.
  • the clutch, the transmission device and the overrunning clutch are serially driven in series.
  • the transmission device, the overrunning clutch and the clutch are sequentially driven in series.
  • the overrunning clutch, the transmission device and the clutch are serially driven in series.
  • the clutch, the overrunning clutch and the transmission are sequentially driven in series.
  • the overrunning clutch, the clutch and the transmission are sequentially driven in series.
  • the shifting unit further includes an engine brake clutch that controls engine braking in parallel with the overrunning clutch and/or the clutch.
  • the transmission is driven in series with the clutch.
  • the adjacent shifting units are driven by a common hub clutch device.
  • the common hub clutch device is disposed on the power input shaft or the power output shaft.
  • At least two adjacent clutches and/or said overrunning clutches are co-hubs.
  • the brake is further provided on the power output shaft or between the power output shaft and the differential.
  • the power input shaft and/or the power output section are arranged in parallel.
  • the power input shaft segment transmits torque in parallel with the power output shaft;
  • the PTO shaft segment is configured to transmit torque in parallel with the power input shaft.
  • the gear shifting device with overlapping gear positions provided by the invention has no gear interference when the working torque is transmitted, the interference friction between the gears is small, the gear positions can overlap, and the plurality of clutches can work at the same time to start at the start and upshifts. And the shifting is smooth and the transmission torque is increased at the same time.
  • the upshift is not required, the engaged low-speed clutch is not required to be separated.
  • the downshift is performed, the clutch is only disconnected one by one from the high-grade position to the low-range position, and the shifting procedure is simple and diverse; The shifting is smooth and fast, the output torque is large, the taxiing speed is fast, the shifting speed is fast, and the fuel economy is environmentally friendly.
  • FIG. 1 is a schematic overall structural view of a shifting device with overlapping gear positions according to the present invention
  • Figure 2 is a schematic structural view of a shifting unit of Embodiment 1 of the present invention.
  • Figure 3 is a schematic structural view of a shifting unit of Embodiment 2 of the present invention.
  • Figure 4 is a schematic structural view of a shifting unit of Embodiment 3 of the present invention.
  • Figure 5 is a schematic structural view of a shifting unit of Embodiment 4 of the present invention.
  • Figure 6 is a schematic structural view of a shifting unit of Embodiment 5 of the present invention.
  • Figure 7 is a schematic structural view of a shifting unit of Embodiment 6 of the present invention.
  • FIG. 8 to FIG. 10 are schematic diagrams showing the structure of a shifting unit for increasing an engine brake clutch according to Embodiment 7 of the present invention.
  • FIG. 12 are schematic diagrams showing the structure of a shifting unit for adding a high speed unit according to Embodiment 8 of the present invention.
  • Figure 13 is a schematic structural view of a shifting unit of an overrunning clutch common hub according to Embodiment 9 of the present invention.
  • Figure 14 is a schematic structural view of a shifting unit of a clutch common hub according to Embodiment 9 of the present invention.
  • FIG. 15 is a schematic structural view of a shifting unit of a common clutch of a clutch and an engine brake clutch according to Embodiment 9 of the present invention.
  • FIG. 16 is a schematic structural view of a shifting unit provided on a power input shaft of a common hub clutch device according to Embodiment 9 of the present invention.
  • FIG. 17 to FIG. 18 are schematic structural views of a shifting device in which gear positions of a plurality of shifting units of the present invention overlap;
  • 19-21 are schematic diagrams showing the overall structure of a shifting device in which a plurality of identical shifting unit positions overlap;
  • 22-23 are schematic diagrams showing the overall structure of a shifting device in which a plurality of different shifting unit positions overlap;
  • Figure 26 is a block diagram showing the structure of a shifting device in which the gear positions are overlapped in the eleventh embodiment of the present invention.
  • the present invention provides a gear shifting device with overlapping gear positions
  • the shifting device with overlapping gear positions includes: a power input shaft 1 , a power output shaft 3 , and a plurality of shifting units 2 connected in parallel, and a power input shaft 1
  • the plurality of shifting units 2 and the power output shafts 3 are sequentially driven in series;
  • the shifting unit 2 includes a transmission device 20, an overrunning clutch 23 and a clutch 24, and
  • the transmission device 20 includes a driving wheel 21 and a driven wheel 22; the driving wheel 21 and the driven wheel 22
  • the overrunning clutch 23 and the clutch 24 are driven in series in any order.
  • the shifting device in which the gear positions are overlapped by the present invention will be described in detail below.
  • the shifting device with overlapping gear positions provided by the present invention sets corresponding gears according to actual needs. Bits, each gear position corresponds to one shifting unit 2. As shown in FIG. 2 to FIG. 7, in the shifting unit 2 corresponding to each gear position of the present invention, the driving wheel 21 and the driven wheel 22 and the overrunning clutch 23 and the clutch 24 can be transmitted in various different sequences, with a plurality of separates below.
  • the embodiments (Embodiment 1 - Embodiment 12) respectively describe the schemes of the different sequential transmissions.
  • the driving wheel 21, the driven wheel 22, the clutch 24, and the overrunning clutch 23 are sequentially driven in series.
  • the driven wheel 22 is engaged with the clutch 24, and the clutch 24 is engaged with the overrunning clutch 23.
  • the power is sequentially transmitted from the power input shaft 1 to the driving wheel 21, and the driving wheel 21, the driven wheel 22, the clutch 24 and the overrunning clutch 23 are sequentially driven, and are transmitted from the overrunning clutch 23 to the power output shaft 3.
  • the clutch 24, the driving wheel 21, the driven wheel 22, and the overrunning clutch 23 are sequentially driven in series.
  • the clutch 24 is engaged with the driving wheel 21, and the driven wheel 22 is engaged with the overrunning clutch 23.
  • the power is sequentially transmitted from the power input shaft 1 to the clutch 24, and the driving wheel 21, the driven wheel 22 and the overrunning clutch 23 are sequentially driven, and the power is transmitted from the overrunning clutch 23 to the power output shaft 3.
  • the driving wheel 21, the driven wheel 22, the overrunning clutch 23, and the clutch 24 are sequentially driven in series.
  • the driven wheel 22 is engaged with the overrunning clutch 23, and the overrunning clutch 23 is engaged with the clutch 24.
  • the power is sequentially transmitted from the power input shaft 1 to the driving wheel 21, and the driving wheel 21, the driven wheel 22, the overrunning clutch 23 and the clutch 24 are sequentially driven, and are transmitted from the clutch 24 to the power output shaft 3.
  • the overrunning clutch 23, the driving wheel 21, the driven wheel 22, and the clutch 24 are sequentially driven in series.
  • the overrunning clutch 23 is engaged with the driving wheel 21, and the driven wheel 22 is engaged with the clutch 24.
  • the power is sequentially transmitted from the power input shaft 1 to the overrunning clutch 23, and the overrunning clutch 23, the driving wheel 21, the driven wheel 22, and the clutch 24 are sequentially driven in series, and are transmitted from the clutch 24 to the power output shaft 3.
  • the clutch 24, the overrunning clutch 23, the driving wheel 21, and the driven wheel 22 are sequentially driven in series.
  • the clutch 24 is engaged with the overrunning clutch 23, and the overrunning clutch 23 is engaged with the driving wheel 21.
  • the power is sequentially transmitted from the power input shaft 1 to the clutch 24, and the clutch 24, the overrunning clutch 23, the driving wheel 21 and the driven wheel 22 are sequentially driven in series, and are transmitted from the driven wheel 22 to the power output shaft 3.
  • the overrunning clutch 23, the clutch 24, the driving wheel 21, and the driven wheel 22 are sequentially driven in series.
  • the overrunning clutch 23 is engaged with the clutch 24, and the clutch 24 is engaged with the driving wheel 21.
  • the power is sequentially transmitted from the power input shaft 1 to the overrunning clutch 23, and the overrunning clutch 23, the clutch 24, the driving wheel 21 and the driven wheel 22 are sequentially driven in series, and are transmitted from the driven wheel 22 to the power output shaft 3.
  • the gear shifting device with overlapping gears provided by the present invention can set a corresponding engine brake clutch 25 in the corresponding shifting unit 2 according to actual needs.
  • the shifting unit 2 to which the engine brake clutch 25 is to be provided may be any one of the first to sixth embodiments.
  • the engine brake clutch 25 may be connected in parallel with the overrunning clutch 23 or in parallel with the overrunning clutch 23 and the clutch 24 in series.
  • the engine brake clutch 25 may be disposed on the side of the driving wheel 21 as needed, and may of course be disposed on the driven wheel 22 side.
  • an embodiment in which the engine brake clutch 25 of the present invention is provided will be exemplified by taking the shifting unit 2 of the first embodiment to the sixth embodiment as an example. As shown in FIG.
  • the shifting unit 2 in Embodiment 1 further includes an engine brake clutch 25 that controls the engine brake in parallel with the in-line clutch 23 and the clutch 24 in series.
  • the shifting unit 2 in Embodiment 3 further includes an engine brake clutch 25 that controls the engine brake in parallel with the overrunning clutch 23.
  • the shifting unit 2 in the second embodiment further includes an engine brake clutch 25 that is braked in parallel with the overrunning clutch 23.
  • the shifting unit 2 in other embodiments can still be provided with the corresponding engine brake clutch 25, and the functions of the above examples can also be realized, and the detailed description thereof will not be repeated here.
  • the engine brake clutch 25 may be omitted if the hybrid electric vehicle is driven by a drive motor to be converted into a generator to brake the vehicle.
  • the gear shifting device provided by the present invention further includes a high speed transmission unit 4 for transmitting power on the power input shaft 1 to the power output shaft 3.
  • the high speed transmission unit includes a driving wheel 21, a driven wheel 22, and a clutch 24; the driving wheel 21, the driven wheel 22, and the clutch 24 are serially driven in any order.
  • the clutch 24 is engaged with the driven wheel 22. The power is sequentially transmitted from the power input shaft 1 to the driving wheel 21, and the driving wheel 21, the driven wheel 22 and the clutch 24 are sequentially driven in series, and are transmitted from the clutch 24 to the power output shaft 3.
  • the present invention is not limited thereto, and the present invention can also be realized by the high speed transmission unit having the clutch 24 disposed on the power input shaft 1 as shown in FIG.
  • the specific transmission process is basically the same as the above scheme, and will not be repeated here.
  • the high-speed transmission unit is the highest gear, and the highest-grade clutch-shaft type can be installed without the overrunning clutch 23, which can effectively prevent the overrunning clutch from being worn.
  • the gear shifting device with overlapping gear positions provided by the invention can drive the adjacent shifting unit 2 between the adjacent shifting units 2 according to actual needs. It will of course be understood that the present invention is not limited thereto, and the clutch 24, the overrunning clutch 23, and the engine brake clutch 25 of the plurality of shifting units 2 may be driven by a common hub clutch device.
  • the common hub clutch device may be disposed on the power input shaft 1 or on the power output shaft 3.
  • the adjacent shifting unit 2 can be provided with a common hub clutch transmission according to actual needs, and the transmission volume can be reduced by providing a common hub clutch transmission.
  • the common hub clutch device includes a double-sided hub in which two clutches 24 or two overrunning clutches 23 are disposed.
  • a plurality of clutching devices may be included in the common hub clutching device, which may be the clutch 24, the overrunning clutch 23, and/or the engine brake clutch 25.
  • the common hub clutch device is disposed on the power output shaft 3, and the overrunning clutch 23 of the adjacent two transmission units is shared by the hub.
  • the common hub clutch device is disposed on the power output shaft 3, and the clutches 24 of the adjacent two transmission units are collectively disposed on the power output shaft 3.
  • the engine brake clutch 25 can also employ a common hub.
  • a clutch 24 of the adjacent two transmission units and an engine brake clutch 25 are disposed on the power output shaft 3 in common.
  • the common hub clutch device may also be disposed on the power input shaft 1. As shown in FIG. 16, the clutch 24 and the overrunning clutch 23 of the adjacent two transmission units are collectively disposed on the power input shaft 1. It should be noted that, in the shifting device provided by the present invention, the clutch 24, the overrunning clutch 23 or the engine brake clutch 25 of any two adjacent shifting units 2 in Embodiments 2 to 6 may be disposed at The power input shaft 1 or the power output shaft 3 has a common hub at the same time, and the implementation scheme is substantially similar to that of FIG. 13 to FIG. 16, and details are not described herein again. As shown in FIG.
  • a plurality of shifting units can be shared by a common hub clutch device, and the first clutch 24, the second clutch 24, the third clutch 24, and the fourth clutch 24 use a clutch common hub.
  • the form saves space for the shifting device relative to the solution of Figures 13-16.
  • a plurality of shifting units may be shared by a common hub clutch, a first clutch 24, a second clutch 24, a third clutch 24, and a fourth clutch.
  • the 24 is in the form of a clutch common hub, and the fifth clutch 24, the sixth clutch 24, the seventh clutch 24, and the eighth clutch 24 are in the form of a clutch common hub, the fifth gear overrunning clutch 23, the sixth gear overrunning clutch 23, The seventh gear overrunning clutch 23 and the eighth gear overrunning clutch 23 are in the form of an overrunning clutch common hub.
  • the gear shifting device adopts a plurality of shifting units 2 of the first to sixth gears, and the electronically controlled hydraulic clutches 24X and 24Y of the present embodiment are overlapped.
  • the shifting device further includes a control system portion including: a clutch control device A and an oil pump main oil pressure adjusting device C connected to the clutch control device, a first to third gear clutch hydraulic pressure adjusting device D, and a fourth gear
  • Oil pump B; oil pump main oil pressure adjusting device C communicates with first to third gear clutch hydraulic pressure adjusting device D, fourth gear to sixth gear clutch hydraulic pressure adjusting device E; first to third gear clutch oil Pressure sensing device F and first to third gear
  • the oil pressure adjusting device D is in communication;
  • the fourth to sixth gear clutch hydraulic pressure sensing device G is in communication with the fourth to sixth gear
  • the first to third gear clutch hydraulic pressure sensing device F is in communication with the first oil pressure chamber 27X.
  • the fourth to sixth gear clutch hydraulic pressure sensing device G is in communication with the second hydraulic pressure chamber 27Y, and the gear shifting device provided by the present invention further includes a throttle sensor H and a vehicle speed sensor I, a throttle sensor H and a vehicle speed.
  • the sensor I is connected to the clutch control device A, and the vehicle speed sensor I is connected to the power output shaft 3.
  • the clutch control device A comprehensively calculates the rear oil pump main oil pressure by the throttle signal detected by the throttle sensor H and the vehicle speed signal detected by the vehicle speed sensor I.
  • the adjusting device C, the first to third gear clutch hydraulic pressure adjusting device D, and the fourth to sixth gear clutch hydraulic pressure adjusting device E output control signals adjust the respective gear clutches.
  • the specific working process of the gear shifting device with this gear position is as follows:
  • the clutch control device A adjusts the main oil pressure by the oil pump main oil pressure adjusting device C, in preparation for the first to third gear clutch hydraulic pressure adjusting device D,
  • the fourth to sixth gear clutch hydraulic pressure adjusting device E is used, and the clutch control device A controls the first to third clutch hydraulic pressure adjusting devices D to supply lubricating oil pressure and control to the first to third clutches 24X and the gears.
  • the fourth to sixth gear clutch hydraulic pressure adjusting devices E supply lubricating oil pressure to the fourth to sixth clutches 24Y and the gears.
  • the clutch control device A adjusts the main oil pressure by the oil pump main oil pressure adjusting device C, and controls the first to third gear clutch hydraulic pressure adjusting device D to The first to third clutches 24X provide the creeping oil pressure, and the fourth to sixth clutch hydraulic pressure adjusting devices E are controlled to supply the lubricating oil pressure to the fourth to sixth clutches 24Y and the gears.
  • the clutch control device A adjusts the main oil pressure by the oil pump main oil pressure adjusting device C, and controls the first to third gear clutch hydraulic pressure adjusting device D to
  • the first to third clutches 24X provide the starting oil pressure, so that the first gear is brought into a fully engaged state from the sliding driving state, and the gearbox enters the first gear state, and the second gear and the third gear clutch are in the sliding friction driving state.
  • the clutch control device A also supplies lubricating oil pressure to the fourth to sixth clutches 24Y and the gears by controlling the fourth to sixth gear clutch hydraulic pressure adjusting devices E.
  • the second gear clutch When the shifting device with the gear position overlap provided by the present invention accelerates the upshift in the forward gear, the second gear clutch is in the fully engaged state in the sliding friction state, and enters the second gear working state, at which time the first gear clutch 24X is fully integrated.
  • the state is interrupted by the first gear of the overrunning clutch 23, and the third gear is in the sliding friction driving state.
  • the clutch control device A passes the fourth to sixth gear clutch hydraulic pressure adjusting device E.
  • the fourth to sixth clutch 24Y is provided with a sliding pressure to prepare for the fourth to sixth gear operation, the vehicle speed is gradually increased, and the first to third gear clutch hydraulic pressure adjusting device D controls the clutch engagement oil pressure.
  • the fourth to sixth gear clutch hydraulic pressure adjusting device E controls the fourth gear to the sixth gear clutch 24Y.
  • the engagement oil pressure is gradually increased, and the fourth clutch is brought into a fully engaged state from the sliding friction drive state.
  • the first gear, the second gear, and the third gear enter the overtaking state, and so on, the fifth gear and the sixth gear gradually enter the combined state from the sliding friction state.
  • the clutch control device A first adjusts the fourth to sixth gear clutch hydraulic pressure adjusting device E to make the fourth gear to the sixth gear correspondingly when the forward gear lift throttle is downshifted.
  • the first to third gear clutch hydraulic pressure adjusting device D is controlled so that the first gear to the third gear are at the corresponding gear positions.
  • the gear shifting device provided by the present invention is adjusted by the first to third gear clutch hydraulic pressure sensing device F, the fourth to sixth gear clutch hydraulic pressure sensing device G, and the throttle sensor H and the vehicle speed sensor I.
  • the first to third gear clutch hydraulic pressure adjusting device D and the fourth to sixth gear clutch hydraulic pressure adjusting device E control the gear shifting gears in which the gear positions overlap.
  • the above embodiment is an example of one of the preferred embodiments.
  • the shifting device in which the gears are overlapped in other embodiments can also be implemented by referring to the solution in the embodiment, and will not be further described herein.
  • the gear shifting device with overlapping gear positions sets corresponding gear positions according to actual needs, and each gear position corresponds to one shifting unit 2 .
  • Different gear positions have corresponding main-passenger wheel diameter ratios.
  • the drive wheel 21 and the driven wheel 22 are different in diameter and produce different gear positions.
  • the reverse gear can be controlled by the driving wheel 21 and the driven wheel 22 through the intermediate wheel plus clutch 24, or the driving wheel 21 and the driven wheel 22 can be connected by the chain plus clutch 24, or the power input shaft 1 and the power output shaft 3 can be installed with the planetary single.
  • the row control mode, or the hybrid electric drive mode is reversed by the motor control. As shown in Figs.
  • the shifting device in which the gears are overlapped by the present invention can be driven by the same shifting unit 2 of the first to sixth embodiments.
  • the shifting device in which the gear positions are overlapped by the present invention can of course be understood to be combined with the plurality of shifting units 2 driven by the various shifting units 2 of the first to sixth embodiments.
  • the shifting device with overlapping gear positions can be selected as the gear rotation or the belt rotation when the driving wheel 21 and the driven wheel 22 of the transmission are selected during the shifting transmission.
  • the belt transmission can also be selected.
  • the belt can be flexibly selected according to actual needs, such as toothed belts, flat belts, V-belts and shaped belts.
  • the gear shifting device with overlapping gear positions provided by the present invention realizes different gear torque outputs as needed, and a corresponding clutch 24 and an engine brake clutch 25 need to be provided in each gear position.
  • the clutch 24 engine brake clutch 25 can be a friction clutch, an embedded clutch, an air flexible clutch, an electromagnetic clutch, a magnetic powder clutch, a torque clutch (safety clutch), a centrifugal clutch, and the clutch control method includes: hydraulic control, pneumatic control, Mechanical control, electromagnetic control, automatic control.
  • the overrunning clutch 23 is also called an orienter, a one-way clutch or a one-way bearing. The overrunning clutch 23 transmits torque by the wedge action of the roller wedge.
  • the clutch 24 can be superimposed and engaged when switching between different gear positions, and the engaged low gears are not disconnected when the upshift is performed.
  • the clutch 24 as a hydraulic clutch as a preferred example.
  • the clutch 24 is a hydraulic clutch as a preferred example.
  • the gear clutches 24 are slidably engaged to assist in the working upshift.
  • the first clutch 24 is operative while the other gear clutch 24 is slidably engaged to assist the first gear.
  • the upshift is reached, the gear is shifted from the sliding engagement state of the clutch 24 to the combined state, and the gear is lower than the clutch 24 of the gear.
  • the clutch 24 is disconnected in order from high to low in downshifting.
  • the control of each clutch 24 is mainly controlled by the computer according to the engine load and the vehicle speed.
  • the torque from the power input shaft 1 is transmitted to the power output shaft through the current gear drive wheel 21, the driven wheel 22, the clutch 24 and the overrunning clutch 23 when which gear clutch 24 engages. 3 on.
  • the first hydraulic gear shifting unit is from the first gear clutch 24, the second gear clutch 24, the third gear clutch 24, the fourth gear clutch 24, and the fifth gear clutch 24,
  • the sixth gear clutch 24, the seventh gear clutch 24, the eighth gear clutch 24, and the ninth gear clutch 24 to the tenth gear clutch 24 are overlapped one by one to provide the clutch 24 to engage the oil pressure for upshifting, from high to low. Downshifting is achieved by sequentially disengaging the clutch 24 to engage the oil pressure.
  • one or more gears provide oil pressure at the same time to change the oil supply pressure to achieve the upshift and downshift. Because there is no gear interference, multiple gears can work at the same time.
  • the pressure is consistent, the low-speed wheel drive torque is greater than the high-end wheel drive torque first engagement work, and the high-end wheel drive torque is small for the friction engagement drive.
  • the driving torque of the car is gradually reduced, and the high-end position is gradually changed from the friction drive to the engagement drive.
  • the first gear engine brake clutch 25 and the second gear engine brake clutch 25 are mainly used to control the engine brake, and are installed in the required gear position according to actual needs. In order to extend the service life of the transmission, the highest gear of the transmission can be added without the overrunning clutch 23.
  • the power input shaft 1 is operatively engaged to drive the driving wheel 21 through the clutch 24, and the driving wheel 21 drives the driven wheel 22.
  • the driven wheel 22 drives the working end of the power output shaft 3 through the overrunning clutch 23 to rotate. Since there is no gear interference, multiple gears can work at the same time.
  • the clutch 24 on the power output shaft 3 can supply oil from the low gear to the high clutch 24 at the same time.
  • the oil supply pressure By adjusting the oil supply pressure to raise and lower the gear position, the oil pressure is gradually increased to the upshift process, and then the oil pressure is gradually reduced to the downshift process.
  • the lifting gear can also be realized by overlapping the oil supply mode from the low gear to the high clutch 24 and then shifting the oil from the high-grade to the low-speed clutch 24 step by step.
  • the shifting program of the invention is simple and smooth, and multiple shifting problems do not occur at the same time, and the shifting speed can be effectively improved.
  • the power input shaft 1 and/or the power output shaft 3 are driven in a segment drive manner.
  • Input segment drive drive the power input shaft 1 is divided into two sections and connected to the power output shaft 3 to transmit torque at both ends; using the output segment drive drive, the power output shaft 3 is divided into two sections and connected in parallel
  • the force input shaft 1 transmits torque at both ends.
  • the power input shaft 1 can be coupled in parallel to the power output shaft 3 to transmit torque; or the power output shaft 3 can be connected in parallel to the power input shaft 1 to transmit torque.
  • the gear Since there is no gear interference, the gear is upshifted during the upshift, without interrupting or slowing down the engine drive torque, the engaged low gear does not need to be disconnected, and only the high clutch to the low gear shifting unit 2 clutch 24 is cut off one by one. , can be any odd or even jump, from highest to lowest or from the lowest to the highest.
  • the plurality of different gear shifting unit 2 clutches 24 can simultaneously supply oil, and the gear position is adjusted by adjusting the oil supply pressure of the clutch 24, and the oil pressure of the clutch 24 of the different gear shifting unit 2 is gradually increased to the upshift process.
  • the oil pressure of the clutch 24 of the different gear shifting unit 2 is gradually lowered to the downshifting process, and one gear position engages the plurality of gear positions to assist in the driving of the gear.
  • These two shifting modes greatly improve the shifting smoothness, increase the shifting speed, and increase the transmission torque.
  • the structure can be used without a torque converter, without a double clutch, without a valve body, which greatly reduces the manufacturing cost. Since the engine brake clutch 25 can be used without the engine brake, the engine brake is completed by replacing the engine brake clutch 25 with the motor by the motor on the hybrid vehicle, and the recovery braking energy is further improved for the motor to drive the vehicle, saving Fuel. Electronically controlled engine braking can also be used for different mode controls, such as economic mode; snow mode and slope mode.
  • the shifting device power input shaft 1 provided with the gear positions of the present invention is provided with a plurality of driving wheels, each of which has a corresponding gear position, and the power output shaft 3 is correspondingly equipped with a plurality of driven wheels.
  • Each of the driven wheels corresponds to one gear position; in this embodiment, there are five forward gear positions, and the corresponding power input shaft 1 is equipped with five driving wheels, that is, the first gear driving wheel 21 and the second gear driving wheel 21
  • the power output shaft 3 is correspondingly equipped with five driven wheels, that is, the first gear driven wheel 22 and the second gear driven wheel 22,
  • the third driven wheel 22, the fourth driven wheel 22, and the fifth driven wheel 22 are provided.
  • a shift shaft 7 is disposed in the power input shaft 1, and a piston 26 is fixed to one end of the shift shaft 7, and the outer side of the piston 26 is a first oil pressure chamber 27 for controlling shifting.
  • each of the driving wheels is provided with an overrunning clutch 23 and a clutch 24, the clutch 24 is a hydraulically controlled friction plate type or a manual transmission synchronous type, and the overrunning clutch 23 is a wedge type one-way bearing. Overspeed clutch or one-way damper.
  • the overrunning clutch 23 is mounted on the power input shaft 1, the clutch 24 is located outside the overrunning clutch 23, and the power input shaft 1 drives the working end of the driving wheel to rotate by the clutch 24, and the working end of the driving wheel meshes with the driven wheel on the power output shaft 3.
  • the clutch wheel 241 and the clutch piston 242 are also disposed in the driving wheel.
  • the clutch oil chamber 241 can communicate with the first oil pressure chamber 27, and the clutch piston 242 can be driven by the oil pressure to bring the clutch 24 into a combined state, that is, the clutch 24 can be
  • the oil pressure control of the first oil pressure chamber 27 is in a combined state.
  • the power input shaft 1 is further provided with a reverse driving wheel 81.
  • the power output shaft 3 is correspondingly equipped with a reverse driven wheel 82.
  • a reverse intermediate gear 80 is provided between the reverse driving wheel 81 and the reverse driven wheel 82.
  • Intermediate gear 80 is mounted on the reverse shaft 85; the reverse drive pulley 81 is provided with a clutch 24 controlled by oil pressure, and a second hydraulic chamber 86 for controlling the reverse gear is disposed in the power input shaft 1, and the power input shaft 1 passes through The clutch 24 drives the reverse drive wheel 81 to rotate.
  • the power input shaft 1 is provided with an oil pump 9 for supplying oil to the first hydraulic chamber 27 and the second hydraulic chamber 86.
  • the oil pump 9 is a gear pump and is driven by the power input shaft 1.
  • the forward gear is engaged, the shift shaft 7 is moved to the left, the high pressure oil in the first oil pressure chamber 27 enters the clutch oil chamber 241 of the first gear drive wheel 21, and the clutch piston 242 is engaged with the clutch 24, that is, the clutch 24 is in a combined state, and the power of the power input shaft 1 is transmitted to the power output shaft 3 through the overrunning clutch 23, the clutch 24, the working end of the first speed drive wheel 21, and the first driven wheel 22 in the first speed drive wheel 21.
  • the first gear works; when the shifting shaft 7 continues to move to the corresponding position of the second gear drive wheel 21, the high pressure oil in the first oil pressure chamber 27 enters the clutch oil chamber of the second gear drive wheel 21 (ie, With the movement of the shifting shaft, the space of the first hydraulic pressure chamber changes accordingly, so that the clutch of the second-speed driving wheel 21 is in the combined state, the second gear works; and so on, the 5-speed shifting operation is realized.
  • the shifting of the shifting shaft 7 automatically determines the gear position according to the rotational speed of the power output shaft 3 and the driving load of the power input shaft 1, and is driven and controlled by a separate circuit. When the vehicle is upshifted, the clutches of each gear position in the gearbox are combined one by one.
  • the combined low-range clutch does not need to be separated, and the gears are separated one by one.
  • the downshifting the previously combined clutches are separated one by one from high to low, and when the clutch is upshifted, There is a procedure for separating the combined low-speed clutches.
  • the clutch is downshifted, it is only necessary to disconnect the clutch one by one from the high-end position to achieve the downshift.
  • the reverse intermediate gear 80 When the reverse gear R is engaged in use, the reverse intermediate gear 80 is combined with the reverse drive wheel 81 and the reverse driven gear 82, and the second oil pressure chamber 86 combines the clutch 24 in the reverse drive wheel 81 to make power input.
  • the power of the shaft 1 is transmitted to the power output shaft 3 through the clutch 24, the reverse drive wheel 81, the intermediate gear 17, and the reverse driven gear 16, so that the vehicle runs backward.
  • the shifting shaft is disposed in the power output shaft, the one-way clutch and the clutch are arranged in the driven wheel, the shifting shaft is arranged in the power output shaft, the piston is fixed at one end of the shifting shaft, and the outer chamber of the piston is used for control
  • the third oil pressure chamber is shifted; each of the driven wheels is provided with a one-way clutch and a clutch, and the clutch can be controlled by the oil pressure of the third oil pressure chamber, and the driven wheel drives the power output shaft to rotate through the clutch.
  • the one-way clutch in the driven wheel is mounted on the power output shaft, and the clutch is located outside the one-way clutch; the clutch oil chamber and the clutch piston are also disposed in the driven wheel, and the clutch oil chamber can communicate with the third oil pressure chamber, the clutch piston It can be driven by oil pressure to put the clutch in the combined state.
  • the shifting device with overlapping gear positions has a one-way clutch and a clutch in each driving wheel, and the power input shaft rotates through the working end of the driving wheel of the driving wheel, and the first oil pressure chamber moves with the shifting shaft.
  • the internal oil pressure controls the clutch combination of the corresponding gear position to realize the shifting.
  • the clutches need only be disconnected one by one from the high-end position to achieve downshifting.
  • the shifting gear of the invention has only one actuator and one clutch, the shifting program is simple and smooth, the shifting interference problem does not occur, and the shifting speed can be effectively improved.
  • the gear shifting device includes a power input shaft 1 and a power output shaft 3, and the power input shaft 1 is provided with at least seven driving wheels 21, each of which has a gear position and a gear position.
  • the power output shaft 3 is correspondingly equipped with at least seven driven wheels 22, and each of the driven wheels 22 corresponds to one gear position.
  • seven driving wheels 21 and seven driven wheels 22 are provided.
  • the power input shaft 1 is provided with a first gear drive wheel 21, a second gear drive wheel 21, a third gear drive wheel 21, a fourth gear drive wheel 21, a fifth gear drive wheel 21, a sixth gear drive wheel 21 and The seventh gear drive wheel 21.
  • the power output shaft 3 is provided with a first-speed driven wheel 22, a second-speed driven wheel 22, a third-speed driven wheel 22, a fourth-speed driven wheel 22, a fifth-speed driven wheel 22, a sixth-speed driven wheel 22, and a Seven-speed driven wheel 22.
  • a clutch 24 and an overrunning clutch 23 are disposed outside each of the driven wheels 22.
  • the clutch 24 is controlled by a shifting oil pressure, and the power output shaft 3 drives the working end of the driven wheel 22 through the clutch 24 and the overrunning clutch 23, and the working end of the driven wheel 22 Engaged with the driving wheel 21 on the power input shaft 1.
  • the gear shifting device provided by the present embodiment is provided with an overrunning clutch 23 and a clutch 24 on each of the driven wheel sides, and the clutch 24 is a hydraulically controlled friction plate clutch or a manual transmission synchronous clutch.
  • the clutch 23 is a wedge type one-way bearing, an overrunning clutch or a one-way damper.
  • the power output shaft 3 of the gear shifting device provided by the present embodiment is provided with a common hub clutch device, and the common clutch device is equipped with a first gear clutch 24 and a second gear clutch 24, and A first-speed engine brake clutch 25 is disposed between the first-speed clutch and the second-speed clutch, and the first-speed overrunning clutch 23 is connected to the first-speed clutch 24, and the first-speed overrunning clutch 23 is connected to the first-speed overrunning clutch 23, The second-speed clutch 24 is connected to the second-speed overrunning clutch 23, and the second-speed overrunning clutch 23 is connected to the second-speed driven wheel 22.
  • the power output shaft 3 is provided with a common hub clutch device.
  • the common clutch clutch device is equipped with a third gear overrunning clutch 23 and a fourth gear overrunning clutch 23, and the third gear overrunning clutch 23 is connected with the third gear clutch 24, and the third gear engine
  • the brake clutch 25 is connected in parallel with the third-speed overrunning clutch 23 and the third-speed clutch 24, it is connected to the third-speed driven wheel 22, the fourth-speed overrunning clutch 23 is connected to the fourth-speed clutch 24, and the fourth-speed clutch 24 is connected.
  • the fourth gear is driven wheel 22.
  • the fifth output clutch 24 is disposed on the power output shaft 3, the fifth speed overrunning clutch 23 is connected to the fifth speed clutch 24, and the fifth speed driven wheel 22 is connected to the fifth speed overrunning clutch 23.
  • a sixth gear clutch 24 is disposed on the power output shaft 3, a sixth gear overrunning clutch 23 is connected to the outside of the sixth gear clutch 24, and a sixth gear driven wheel 22 is connected to the outside of the sixth gear overrunning clutch 23.
  • the power output shaft 3 is provided with a seventh-speed overrunning clutch 23, and the seventh-speed overrunning clutch 23 is connected to the seventh-speed clutch 24, and the seventh-speed clutch 22 is connected to the seventh-speed driven wheel 22.
  • the driving torques of the low-speed driving wheel 21 and the driven wheel 22 are combined to work first, and the driving torques of the high-speed driving wheel 21 and the driven wheel 22 are small and friction-driven.
  • the high-end position transmits the torque, and although the low-range is combined, the over-running is performed by the overrunning clutch, and the torque is not transmitted.
  • the first gear engine brake 25 and the third gear engine brake 25 are mainly used to control the engine brake, and are installed in the required gear position according to actual needs. In order to extend the life of the gearbox, the highest gearbox is not equipped with an overrunning clutch.
  • Another type of gear superimposed multi-stage automatic transmission is provided with a clutch 24 and an overrunning clutch 23 outside each of the driving wheels 21, the clutch 24 is controlled by a shifting oil pressure, and the power input shaft 1 drives the driving wheel through the clutch 24 and the overrunning clutch 23.
  • the working end of 21 is rotated, and the working end of the driving wheel 21 meshes with the driven wheel 22 on the power output shaft 3.
  • the first gear drive wheel 21 and the second gear drive wheel 21 are connected in a common clutch manner;
  • the third gear drive wheel 21 and the fourth gear drive wheel 21 are connected by a common overrunning clutch;
  • the wheel 21 and the sixth gear drive wheel 21 are respectively coupled to the power input shaft 1 via a clutch shaft, and the seventh driven wheel 22 is coupled to the power input shaft 1 via the overrunning clutch 23.
  • the power input shaft or the power output shaft is driven in sections, and the power input shaft is segmented.
  • the power input shaft in the second embodiment is divided into two parallel sections.
  • the torque is transmitted at the power output shaft.
  • the power output shaft is segmented, and the power output shaft in the first embodiment is divided into two sections and connected in parallel to the power input shaft to transmit torque.
  • the gear shifting device provided by the present invention can be applied to automobile, motorcycle, electric vehicle, ship, military, engineering, mechanical, electric power, aviation, machine tool, power generation, industrial, agricultural, and other mechanical transmission shifting.
  • the invention relates to the technical field of gearbox and gearbox shifting and torsional transmission, and particularly relates to a gear-overlapping multi-stage automatic transmission.
  • the shifting device with overlapping gear positions of the invention has no gear interference when working to transmit torque, and the interference friction between the gears is small, the gear positions can be overlapped, and multiple clutches can work simultaneously to start and shift at the start and upshifts.
  • the gear shifting device with overlapping gear positions provides no gear interference when working to transmit torque, and the interference friction between the gears is small, and the gear positions can overlap.
  • multiple clutches can work at the same time to start and change.
  • the gear is stable and the transmission torque is increased.
  • the upshift is not required, the engaged low-speed clutch is not required to be separated.
  • the gear is downshifted, the clutch is only disconnected one by one from the high-grade position, and the shifting procedure is simple and diverse; the shifting is smooth and quick.
  • the output torque is large, the taxiing speed is fast, the shifting speed is fast, the fuel economy is environmentally friendly, and the industrial utility is available.

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

Abstract

L'invention porte sur un mécanisme de changement de vitesse à chevauchement d'engrenages, lequel mécanisme comprend un arbre d'entrée d'énergie (1), un arbre de sortie d'énergie (3) et de multiples unités de changement de vitesse à entraînement parallèle (2). L'arbre d'entrée d'énergie (1), les multiples unités de changement de vitesse (2) et l'arbre de sortie d'énergie (3) sont entraînés en tandem de façon séquentielle. L'unité de changement de vitesse (2) comprend une transmission (20), un embrayage (24) et un embrayage à roue libre (23). La transmission (20) comprend une roue motrice (21) et une roue entraînée (22). La transmission (20), l'embrayage à roue libre (23) et l'embrayage (24) sont entraînés en tandem selon n'importe quel ordre. Quand le mécanisme de changement de vitesse fonctionne de façon à transférer un couple, aucun des engrenages ne subit une interférence, le frottement d'interférence entre les engrenages est réduit et les engrenages peuvent se chevaucher. Lors du démarrage et de la montée en vitesse, une variété d'embrayages peuvent fonctionner simultanément de façon à rendre réguliers le démarrage et la montée en vitesse, et à accroître en même temps le couple de transfert. Lors de la montée en vitesse, l'embrayage de basse vitesse en prise n'a pas besoin d'être déconnecté. Lors de la rétrogradation, l'embrayage a seulement besoin d'être déconnecté à partir des engrenages hauts jusqu'aux engrenages bas un par un de façon à réaliser une rétrogradation. Le mécanisme présente un degré élevé de confort de changement de vitesse, une vitesse rapide, un grand couple de transmission, une structure simple, une commande simple, un coulissement rapide, une économie en carburant et une protection de l'environnement.
PCT/CN2015/079228 2014-08-29 2015-05-18 Mécanisme de changement de vitesse à chevauchement d'engrenages WO2016029719A1 (fr)

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Applications Claiming Priority (4)

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CN201410434004.0A CN105370879B (zh) 2014-08-29 2014-08-29 单离合多级自动变速器
CN201410434004.0 2014-08-29
CN201510014762.1 2015-01-13
CN201510014762.1A CN104633017A (zh) 2015-01-13 2015-01-13 一种档位叠加式多级自动变速器

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CN110345205A (zh) * 2019-07-11 2019-10-18 杭州萧山江南通用机械有限公司 一种多输出船用齿轮箱
CN111365436A (zh) * 2020-04-17 2020-07-03 丁红涛 动力开关自动变速箱
CN111412252A (zh) * 2020-01-23 2020-07-14 熵零技术逻辑工程院集团股份有限公司 一种传动机构
CN112984106A (zh) * 2020-04-02 2021-06-18 天津叠挡传动技术有限公司 挡位重叠的离合装置、变速装置、发电装置和电动汽车

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CN114235394B (zh) * 2021-12-23 2023-05-12 苏州英特模科技股份有限公司 一种变速加载机构和加载方法

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CN2448617Y (zh) * 2000-09-04 2001-09-19 郭永志 车辆电控自动变速器
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CN110345205B (zh) * 2019-07-11 2024-02-13 杭州萧山江南通用机械有限公司 一种多输出船用齿轮箱
CN111412252A (zh) * 2020-01-23 2020-07-14 熵零技术逻辑工程院集团股份有限公司 一种传动机构
CN112984106A (zh) * 2020-04-02 2021-06-18 天津叠挡传动技术有限公司 挡位重叠的离合装置、变速装置、发电装置和电动汽车
CN111365436A (zh) * 2020-04-17 2020-07-03 丁红涛 动力开关自动变速箱

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