WO2010094181A1 - Procédé de commande et dispositif de commande d'une transmission à variation continue - Google Patents

Procédé de commande et dispositif de commande d'une transmission à variation continue Download PDF

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Publication number
WO2010094181A1
WO2010094181A1 PCT/CN2009/070823 CN2009070823W WO2010094181A1 WO 2010094181 A1 WO2010094181 A1 WO 2010094181A1 CN 2009070823 W CN2009070823 W CN 2009070823W WO 2010094181 A1 WO2010094181 A1 WO 2010094181A1
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WO
WIPO (PCT)
Prior art keywords
transmission
transmission shaft
shaft
disk
continuously variable
Prior art date
Application number
PCT/CN2009/070823
Other languages
English (en)
Chinese (zh)
Inventor
吴希春
何帅
Original Assignee
Wu Xichun
He Shuai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wu Xichun, He Shuai filed Critical Wu Xichun
Publication of WO2010094181A1 publication Critical patent/WO2010094181A1/fr

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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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/067—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions mechanical actuating means
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable

Definitions

  • the present invention relates to a control method and control device for a continuously variable transmission, and more particularly to a fully mechanical continuously variable transmission intelligent control method and control device that can automatically change an optimum transmission ratio according to a required torque.
  • a continuously variable transmission system includes a drive plate, a driven plate, a V-belt, a hydraulic pump, and an electronic control unit.
  • the active disk and the driven disk are respectively composed of a movable disk and a fixed disk.
  • the movable plate and the fixed plate have a tapered surface, and their tapered faces form a V-shaped groove to cooperate with the V-shaped (metal) transmission belt.
  • the power output from the engine's driven shaft is first transmitted to the active disc of the continuously variable transmission, and then transmitted to the driven disc through the V-belt.
  • the control system composed of the hydraulic and electronic control unit controls the movable disc and the driven disc.
  • the disk moves axially, thereby changing the working radius of the active disk, the tapered surface of the driven disk and the V-shaped transmission belt, thereby changing the transmission ratio between the active disk and the driven disk.
  • the control system which is composed of a hydraulic system and an electronic control unit, controls the gear ratio, resulting in a high transmission cost, complicated structure, cumbersome manufacturing process, limited life and poor stability.
  • an object of the present invention is to provide a fully mechanical control method and control device for a continuously variable transmission, which can automatically detect a required torque and automatically change an optimal transmission ratio according to a required torque to solve the above problem. .
  • the fully mechanical intelligent control method of the present invention is characterized in that it comprises a control step using a control device comprising an elastic device capable of transmitting torque, the control step utilizing the elastic device
  • the elastic deformation memory changes the resistance of the continuously variable transmission to automatically adjust the output torque of the continuously variable transmission.
  • the control method is further characterized in that the continuously variable transmission includes a driven disc, the driven disc includes a fixed disc and a movable disc, and the fixed disc and the movable disc respectively have a V-shaped tapered surface, The fixed disk and the V-shaped tapered surface of the movable plate are opposite to each other to form a V-shaped groove, and the movable plate is movable relative to the fixed disk.
  • the control device further includes a threaded transmission device, a first transmission shaft and a second transmission shaft.
  • the control steps include: Step a, forming a linkage relationship between the first transmission shaft and the movable disc, so that the first transmission shaft can obtain power from the driven disc;
  • Step b setting the elastic device to transmit a predetermined torque
  • Step c when the resistance of the continuously variable transmission is not greater than the predetermined torque, the elastic device is used to directly transmit the power obtained by the first transmission shaft to the second transmission shaft;
  • Step d when the resistance of the continuously variable transmission exceeds the predetermined torque, the scroll spring is tightened, and the first transmission shaft and the second transmission shaft are relatively rotated in the first rotation direction, and simultaneously the first transmission The shaft and the second transmission shaft are relatively moved toward the first moving direction, so that the first transmission shaft drives the movable disc to reduce the distance between the movable disc and the fixed disc, thereby automatically searching for the driven disc.
  • An effective working radius thereby achieving an optimum gear ratio of the transmission, thereby adjusting the output torque required for the output of the continuously variable transmission.
  • control method is further characterized in that the control method further comprises a step in which the continuously variable transmission is connected to a power output shaft of an automobile engine, and the predetermined schedule of the elastic device is set according to individual requirements.
  • the torque causes the elastic device to adjust the output torque required for the output of the continuously variable transmission within a range of 20% to 80% of the maximum output torque of the engine.
  • the control method is further characterized in that the controlling step further comprises a step e, in which the elasticity is released from a process of reducing the resistance exceeding the predetermined moment to not exceeding the predetermined torque
  • the potential energy of the device rotates the first transmission shaft and the second transmission shaft relative to the second rotation direction, and simultaneously moves the first transmission shaft and the second transmission shaft relative to the second movement direction, thereby increasing the movable disc and fixing
  • the distance between the discs which in turn automatically finds the effective working radius of the driven disc, thereby achieving an optimum transmission ratio of the transmission, thereby adjusting the output torque required for the output of the continuously variable transmission.
  • the control method is further characterized in that, in the step d and the step e, the first transmission shaft and the second transmission shaft are relatively moved by means of a threaded transmission device.
  • a transmission adapted to the fully mechanical intelligent control device of the present invention includes a driven disk including a fixed disk and a movable disk, and the movable disk is movable relative to the fixed disk.
  • the control device includes An elastic device capable of transmitting torque; a threaded transmission; a first transmission shaft coupled to the movable plate and movable with the movable plate; and a second transmission shaft; wherein the elastic device Provided in a torque transmission path of the first transmission shaft and the second transmission shaft, the screw transmission device is respectively connected to the first transmission shaft and the second transmission shaft, so that the first transmission shaft and the second transmission shaft The relative movement is relatively straight while rotating relative to each other.
  • the control device is further characterized in that: the first end of the first transmission shaft is connected to the movable plate, and the elastic device is disposed on the second end of the first transmission shaft and the first end of the second transmission shaft In the torque transmission path, the thread transmitting device is respectively connected to the second end of the first transmission shaft and the first end of the second transmission shaft.
  • the control device is further characterized in that the threaded transmission comprises a second end of the first transmission shaft and a first end of the second transmission shaft connected in a threaded manner.
  • the control device is further characterized in that: the second end of the first transmission shaft is connected with a plurality of forks, the fork is inserted into a dial, and the dial is connected to the first end of the elastic device The second end of the elastic device is coupled to the second drive shaft.
  • the control device is further characterized in that: the second transmission shaft is formed with a seat body centered on the second transmission shaft, and the elastic device is received in the seat body, and the seat body is covered by a cover.
  • the dial has a sleeve portion extending from the center, the sleeve portion is connected to the first end of the elastic device through a central hole of the cover, and the first end of the second transmission shaft is from the sleeve portion Through the center hole.
  • the control device is further characterized in that the second end of the first transmission shaft has a threaded hole, and the first end of the second transmission has a screw portion, and the screw portion is screwed with the threaded hole to realize thread transmission.
  • the control device is further characterized in that the fork is radially offset from the axis of the first transmission shaft by a predetermined distance and evenly distributed, and the fork is formed integrally with the first transmission shaft.
  • the control device is further characterized in that the seat body and the second transmission shaft are formed integrally.
  • the control device is further characterized in that the elastic device is a spiral wrap spring, and a maximum circle of the wrap spring is fixed on the seat body, and a minimum ring of the wrap spring is fixed on the shaft Set of dials on the sleeve part.
  • the control device is further characterized in that: a plurality of radial grooves are formed in the seat body and the cover, and a centrifugal block is placed in the radial groove, and the centrifugal block can move freely along the radial groove, each A centrifugal block is located between the two turns of the scroll spring, and the curvature is slightly smaller than the curvature of the scroll spring to accommodate the area of contact with the scroll spring after the deformation of the scroll spring.
  • the control device of the transmission of the present invention can operate as follows:
  • the active disk of the transmission maintains the maximum working radius, and the working radius of the driven disk of the transmission is at a minimum to achieve the minimum transmission ratio, achieving the highest transmission efficiency, and the driver can I like to set the sensitivity value of the elastic device such as the scroll spring in advance, so that it can be arbitrarily adjusted between 20% and 80% of the maximum output torque of the engine.
  • the elastic device can accurately detect the change of the deformation force and change the deformation amount.
  • the resistance is reduced to less than the set value, the potential energy stored by the elastic device is released and released in the elastic device.
  • the screw drive rotates, the clearance between the movable plate and the fixed plate increases, and the working radius is reduced, thereby finding the most effective transmission ratio.
  • the transmission can intelligently identify the required torque, intelligently adjust the transmission ratio, control sensitive and fast, low cost, simple structure and manufacturing process, long life and strong stability.
  • Fig. 1 is an overall cross-sectional view showing a control device for a continuously variable transmission according to an embodiment of the present invention.
  • Figure 2 is a plan view showing the axial direction of the spiral spring in the embodiment shown in Figure 1.
  • Fig. 3 shows the scroll spring housing screw assembly 1 of the embodiment shown in Fig. 1, wherein (a) is an axial plan view and (b) is a half cross-sectional view.
  • Fig. 4 shows a fixed disk of the driven disk in the embodiment of Fig. 1, wherein (a) is an axial plan view and (b) is a half cross-sectional view.
  • Figure 5 shows the fork nut assembly of the embodiment of Figure 1, wherein (a) is an axial plan view and (b) is a half cross-sectional view.
  • Fig. 6 shows a scrolled spring dial with a bushing in the embodiment of Fig. 1, wherein (a) is an axial plan view and (b) is a half cross-sectional view.
  • Figure 7 shows the movable disk of the driven disk in the embodiment of Figure 1, wherein (a) is an axial plan view and (b) is a half cross-sectional view.
  • Figure 8 shows a cover gear assembly in accordance with an embodiment of the present invention, wherein (a) is an axial plan view and (b) is a half cross-sectional view.
  • Figure 9 is a state diagram of the case where the transmission ratio is the smallest and the transmission efficiency is the highest.
  • Fig. 10 is a view showing a state in which the transmission ratio is the largest and the torque is maximum.
  • Fig. 11 is a cross-sectional view showing the entirety of a control device for a continuously variable transmission according to an embodiment of the present invention.
  • Figure 12 is a developed view of an embodiment of a scroll spring.
  • Figure 13 shows a centrifugal friction block in an embodiment of Figure 1, wherein (a) is a longitudinal plan view and (b) is a schematic half-sectional view.
  • the following embodiment will substantially disclose a control device for a continuously variable transmission including a driven disk including a fixed disk and a movable disk, the movable disk being movable relative to the fixed disk
  • the control device comprises: a resilient device capable of transmitting torque; a threaded transmission device; a first transmission shaft coupled to the movable plate and operably coupled to the movable plate; and a second transmission shaft;
  • the elastic device is disposed in the torque transmission path of the first transmission shaft and the second transmission shaft, the thread transmission device is respectively connected to the first transmission shaft and the second transmission shaft, so that the first transmission shaft and The second drive shaft moves relatively linearly while rotating relative to each other.
  • the aforementioned elastic means may also be a coil spring.
  • the torque transmission path of the first transmission shaft (the driven shaft 43) and the second transmission shaft (the transmission shaft 100) includes a nut 42, a shift fork 41, a scroll spring dial 9, a scroll spring 2, and a scroll spring housing 102. It is obvious that there are many variations in the torque transmission path, for example, the torque transmission element can be increased or decreased.
  • the threaded transmission includes a nut 42 formed integrally with the driven shaft 43 and a screw 101 formed integrally with the drive shaft 100, the position of the nut 42 and the screw 100 being interchangeable. Further, the present invention has other modifications which can be made with reference to the following embodiments.
  • the control device of the present invention comprises a scroll spring housing screw assembly 1, a scroll spring 2, a cover 3, a fork nut assembly 4, a scroll spring dial 9 with a bushing, and a follower adjustable
  • the cone fixing plate 5 the driven adjustable cone disk movable plate 6, the bearings 7, 7' and the outer casings 8, 8'.
  • the fork nut assembly 4 includes a shift fork 41, a nut 42 and a driven shaft 43 with a spline 430 formed on the right end of the driven shaft 43, the nut 42 and the driven The left end of the shaft is connected, and the fork 41 is screwed
  • the female 42 is connected to the nut 42 by a predetermined distance from the radial direction.
  • the fork nut assembly is a single piece, but the invention is not limited thereto, and the fork 41 and the nut 42 are provided.
  • the driven shaft 43 with the splines 430 can be a separate member that is coupled together.
  • the scroll spring dial 9 includes a disk body 91 and a boss 90 projecting from the center of the disk body on one side of the disk body 91, and perforations 910 are formed at both ends of the disk body 91.
  • the shift fork 41 of the fork nut assembly 4 cooperates with the scroll spring dial 9, i.e., as shown in Fig. 1, the shift fork 41 is inserted into the through hole 910 of the disc body 91, thereby the shift nut assembly 4 and the scroll spring dial A simultaneous connection relationship between the disks 9 is formed.
  • the scroll spring housing screw assembly 1 includes a scroll spring housing 102, a screw 101 and a transmission shaft 100.
  • the screw 101 is coupled to the transmission shaft 100
  • the scroll spring housing 102 is coupled to the transmission shaft 100.
  • 102 is also centered on the transmission shaft 100.
  • the scroll spring housing screw assembly 1 is a single piece, but the invention is not limited thereto, the scroll spring housing 102, the screw 101, and the transmission shaft 100 Can be a separate component.
  • One end of the drive shaft 100 of the scroll spring housing screw assembly 1 (the left end in FIG. 3(b)) is connected to a speed reducer (not shown), and the screw 101 is screwed to the nut 42 of the fork nut assembly 4, which can be realized.
  • Threaded drive A plurality of pin holes 104 are formed in the scroll spring housing 102 of the scroll spring housing screw assembly 1, and the scroll spring is fixed at different pin hole positions by the pin, and the sensitivity value of the scroll spring can be adjusted to make the maximum output of the engine Adjust between 20% and 80% of the torque.
  • the fixed disk 5 and the moving disk 6 serve as the main components of the driven disk of the transmission.
  • the right side of the fixed disk 5 has a tapered surface 501, a guide shaft 502, and a spline 503.
  • the left side of the fixed disk 5 has a mounting shaft 504.
  • the mounting shaft 504 of the fixed disk 504 is rotatably coupled to the housing 8' via a bearing 7', i.e., the fixed disk 504 is rotatably supported by the housing 8'.
  • the left side of the moving plate 6 is formed with a tapered surface 601 and a guide hole 602, and the moving plate 6 is further formed with a connecting hole 603.
  • the connecting hole 603 and the guiding hole 602 are in communication, and the two are coaxial.
  • the tapered surface 501 of the fixed disk 5 and the tapered surface 601 of the moving disk 6 are opposed to each other to form a V-shaped groove 605 for accommodating a transmission belt (not shown).
  • the guide shaft 502 of the fixed disk 5 is inserted into the guide hole 602 of the moving plate 6, so that the moving plate 6 is axially movable along the guide shaft 502, and during the axial movement of the moving plate 6 along the guide shaft 502, the V-shaped groove 605 is changed.
  • the width or narrowing is such that the working radius of the belt at the driven disc end becomes smaller or larger, that is, the working radius of the driven disc of the transmission becomes smaller or larger. This is illustrated in Figures 9 and 10.
  • reference numeral 56 designates a pulley that is virtually formed by the V-groove of the driven disc
  • reference numeral 56' designates the virtual groove of the V-groove of the active disk end of the transmission.
  • Wheel similarly, the active disk also includes a fixed disk and a movable disk
  • the working radius of the pulleys 56, 56' becomes larger as the fixed disk and the movable disk move relative to each other or
  • FIG. 9 the distance between the movable disk 6 and the fixed disk 5 of the driven disk is the largest
  • FIG. 10 is the space between the movable disk 6 and the fixed disk 5 of the driven disk. The case of the smallest spacing.
  • the gear ratio of the transmission (the ratio of the angular velocities of the pulley 56' to the pulley 56) is the smallest
  • the transmission ratio of the transmission is the largest.
  • the driven shaft 43 passes through the center hole of the fixed disk 5, and the spline 430 on the shaft of the driven shaft 43 cooperates with the spline 503 in the center hole of the fixed disk 5. Thereby, a rotatable interlocking relationship is formed between the driven shaft 43 and the fixed disk 5.
  • the driven shaft 43 further has a threaded hole 431, the threaded hole 431 is aligned with the connecting hole 603 of the movable plate 6, and the screw 10 is connected to the threaded hole 431 through the connecting hole 603, so that the driven shaft 43 and the movable plate 6 are interposed therebetween.
  • a rotatable linkage relationship is also formed.
  • the scroll spring 2 has a first end 200 on the central axis and a second end 202 on the outermost ring.
  • the area of the cross section of the scroll spring 2 can be varied, as shown in FIG.
  • the width of the first end 200 of the scroll spring is greater than the width of the second end 202 of the scroll spring.
  • the first end 200 of the scroll spring 2 is coupled to the sleeve portion 90 of the scroll spring dial 9, and the second end 202 of the scroll spring 2 is coupled to the inner wall of the scroll spring housing 102.
  • the scroll spring housing 102 is covered by a cover 3.
  • the boss portion 90 of the scroll spring dial 9 is connected to the scroll spring 2 through the center hole of the cover 3.
  • the drive shaft 100 of the scroll spring housing screw assembly 1 is rotatably supported by the housing 7 of the transmission via a bearing 7.
  • the transmission of the driven disc of the transmission is from the driven shaft 43, the nut 42, the fork 41, the scroll spring dial 9, the scroll spring 2, the scroll spring
  • the outer casing 102 and the transmission shaft 100 are sequentially transmitted.
  • the scroll spring 2 functions as a flexible connection between the driven shaft 43 and the transmission shaft 100.
  • the driven shaft 43 transmits the power directly to the transmission shaft 100 through the scroll spring 2, and is driven.
  • the shaft 43 and the transmission shaft 100 rotate at the same speed.
  • the transmission shaft 100 in operation may decelerate or stop rotating.
  • the rotation speed of the driven shaft 43 may be greater than the transmission shaft 100.
  • the rotational speed therefore, the scroll spring 2 is deformed, for example, by crimping. Since the driven shaft 43 and the transmission shaft 100 are connected by a screw transmission formed by the nut 42 and a screw 101, when the driven shaft 43 and the transmission shaft 100 are relatively rotated, the driven shaft 43 and the transmission shaft 100 are simultaneously Will move relatively.
  • the driven shaft 43 is moved upward as shown in FIG.
  • the pitch becomes smaller, even if the working radius of the virtual pulley 56 shown in Figs. 9 and 10 becomes larger, so that the transmission ratio of the transmission becomes larger, thereby making the follower
  • the shaft 43 outputs a larger torque.
  • the scroll spring 2 stops deforming, and the scroll spring stores the elastic potential energy, that is, the change in the resistance received by the transmission shaft 100, if subsequently, The transmission shaft 100 is subjected to a decrease in resistance.
  • the scroll spring 2 releases the stored elastic potential energy, the rotation speed of the transmission shaft 100 becomes large, and a relative transmission in the opposite direction occurs between the transmission shaft 100 and the driven shaft 43 as before. Due to the screw transmission formed by the nut 43 and the screw 101, the transmission shaft 100 and the driven shaft 43 are relatively moved. As shown in FIG. 1, the moving direction is downward to increase the between the fixed disk 5 and the moving plate 6. The pitch of the transmission increases the transmission ratio of the transmission, and this adjustment continues until the scroll spring 2 returns to its original state, that is, a state in which a predetermined torque is transmitted. From the foregoing description, it can be understood that the transmission of the present invention memorizes the change in resistance by the scroll spring, thereby achieving automatic adjustment of the output torque or the gear ratio.
  • a plurality of sets of long grooves 15 are respectively formed in the opposite end faces of the spiral spring case 12 and the cover 3, and the long groove 15 of the spiral spring case 102 and the long groove 15 of the cover 3 are opposed to each other.
  • the long groove 15 extends in the radial direction of the scroll spring housing 102 or the cover 3, the friction block 12 can move freely in the long groove 15, the friction block 12, the long groove 15
  • the number can vary according to demand.
  • the friction block 12 has an arc portion 120 at an intermediate portion, the arc of the arc portion 120 being slightly smaller than the arc of the initial state of the scroll spring 2, after the friction block 12 is received between the scroll spring housing 102 and the cover 3, In contact with the side of the scroll spring 2 in the initial state, when the friction block 12 moves radially under the action of centrifugal force (for example, when the transmission mounted on the vehicle is at a speed higher than 50% of the maximum vehicle speed) Applying a certain anti-deformation force to the scroll spring 2 to increase the rigidity of the scroll spring 2 and improve the transmission efficiency.
  • the friction block 12 can be placed 1-10 according to the engine power, and the weight can be added according to the requirement ( Not shown).
  • Fig. 11 shows another embodiment of the control device of the present invention, which differs from the previous embodiment in that a gear 13 is added to the cover 3, and the gear 13 is directly coupled to the input gear of the reducer.
  • the foregoing embodiment also discloses a control method for a continuously variable transmission, the control method comprising a control step using a control device of the foregoing, and utilizing the elastic deformation of the elastic device 2 therein to memorize the continuously variable transmission
  • the change in resistance is to automatically adjust the output torque of the continuously variable transmission.
  • the control step includes the following steps:
  • Step a the driven shaft 43 and the movable plate 6 are coupled to each other such that the driven shaft 43 can obtain power from the driven plate 6;
  • Step b setting the elastic device 2 to transmit a predetermined torque
  • Step c when the resistance of the continuously variable transmission is not greater than the predetermined torque, the elastic device 2 is used The power obtained by the driven shaft 43 is directly transmitted to the transmission shaft 100;
  • Step d when the resistance of the continuously variable transmission exceeds the predetermined torque, the elastic device 2 is tightened, and the driven shaft 43 and the transmission shaft 100 are relatively rotated in the first rotational direction, and simultaneously the driven shaft 43 and the transmission shaft 100 are relatively moved in the first moving direction, so that the driven shaft 43 drives the movable disc to reduce the distance between the movable disc and the fixed disc, thereby automatically finding the effective of the driven disc.
  • the working radius is such that the optimum transmission ratio of the transmission is achieved, thereby adjusting the output torque required for the output of the continuously variable transmission.
  • the foregoing control method further includes a step of connecting the aforementioned continuously variable transmission to a power output shaft of an automobile engine, and the driver can set a predetermined torque of the elastic device according to individual requirements, so that the elastic device is in the engine
  • the output torque required to regulate the output of the continuously variable transmission is in the range of 20% to 80% of the maximum output torque.
  • the foregoing control method further includes a step e, in which the potential energy of the elastic device 2 is released during the process of reducing the resistance exceeding the predetermined moment to not more than the predetermined torque, so that the driven shaft 43 and The transmission shaft 100 is relatively rotated in the second rotation direction, and at the same time, the driven shaft 43 and the transmission shaft 100 are relatively moved in the second moving direction, thereby increasing the distance between the movable plate 6 and the fixed plate 5, thereby automatically searching for the transmission.
  • the effective working radius of the driven disc achieves the optimum gear ratio of the transmission, which in turn regulates the output torque required for the output of the continuously variable transmission.

Abstract

L'invention concerne un dispositif de commande d'une transmission à variation continue, cette transmission à variation continue comprenant un disque d'embrayage (5, 6), le disque d'embrayage (5, 6) comprenant un disque fixe (5) et un disque mobile (6), le disque mobile (6) pouvant se déplacer par rapport au disque fixe (5). Le dispositif de commande de la transmission à variation continue comprend un dispositif à ressort (2) pouvant transférer le moment ; un dispositif d'entraînement à vis (42, 101) ; un premier arbre de transmission (43), qui est raccordé au disque mobile (6), et qui peut être une liaison avec le disque mobile (6) ; et un deuxième arbre de transmission (100). Le dispositif à ressort (2) est mis en œuvre dans la trajectoire de transfert de moment du premier arbre de transmission (43) et du deuxième arbre de transmission (100), et le dispositif d'entraînement à vis (42, 101) est raccordé au premier arbre de transmission (43) et au deuxième arbre de transmission (100) respectivement. Le procédé de commande de cette transmission à variation continue fait appel à la déformation élastique du dispositif à ressort (2) pour se souvenir du changement de la force de résistance exercée par la transmission à variation continue, ajuste automatiquement le couple de sortie de la transmission à variation continue.
PCT/CN2009/070823 2009-02-18 2009-03-17 Procédé de commande et dispositif de commande d'une transmission à variation continue WO2010094181A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN200910046290A CN101806343A (zh) 2009-02-18 2009-02-18 机械式无级变速器智能控制方法及控制装置
CN200910046290.2 2009-02-18

Publications (1)

Publication Number Publication Date
WO2010094181A1 true WO2010094181A1 (fr) 2010-08-26

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PCT/CN2009/070823 WO2010094181A1 (fr) 2009-02-18 2009-03-17 Procédé de commande et dispositif de commande d'une transmission à variation continue

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WO (1) WO2010094181A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111658351B (zh) * 2020-05-28 2022-04-15 杭州电子科技大学 一种无极调节传动比的手动轮椅

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4075902A (en) * 1976-09-27 1978-02-28 Dana Corporation Variable speed pulley
CN2065263U (zh) * 1989-12-02 1990-11-07 马新平 适应摩托车阻力变化的无级变速装置
CN2081014U (zh) * 1990-05-22 1991-07-17 马新平 适应摩托车阻力变化的传动装置
FR2658892A1 (fr) * 1990-02-23 1991-08-30 Ibc Europ Sarl Poulie menee d'une transmission a vitesse variable.
EP0591872B1 (fr) * 1992-10-05 1996-05-01 PIAGGIO VEICOLI EUROPEI S.p.A. Transmission à variation continue de vitesse en particulier pour des véhicules à deux roues
CN2585780Y (zh) * 2002-12-11 2003-11-12 黄兆焕 一种机动车自动变速器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4075902A (en) * 1976-09-27 1978-02-28 Dana Corporation Variable speed pulley
CN2065263U (zh) * 1989-12-02 1990-11-07 马新平 适应摩托车阻力变化的无级变速装置
FR2658892A1 (fr) * 1990-02-23 1991-08-30 Ibc Europ Sarl Poulie menee d'une transmission a vitesse variable.
CN2081014U (zh) * 1990-05-22 1991-07-17 马新平 适应摩托车阻力变化的传动装置
EP0591872B1 (fr) * 1992-10-05 1996-05-01 PIAGGIO VEICOLI EUROPEI S.p.A. Transmission à variation continue de vitesse en particulier pour des véhicules à deux roues
CN2585780Y (zh) * 2002-12-11 2003-11-12 黄兆焕 一种机动车自动变速器

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