WO2002053945A1 - Transmission variable en continu toroidale - Google Patents

Transmission variable en continu toroidale Download PDF

Info

Publication number
WO2002053945A1
WO2002053945A1 PCT/JP2001/011258 JP0111258W WO02053945A1 WO 2002053945 A1 WO2002053945 A1 WO 2002053945A1 JP 0111258 W JP0111258 W JP 0111258W WO 02053945 A1 WO02053945 A1 WO 02053945A1
Authority
WO
WIPO (PCT)
Prior art keywords
disk
input
output
continuously variable
variable transmission
Prior art date
Application number
PCT/JP2001/011258
Other languages
English (en)
Japanese (ja)
Inventor
Yasuji Taketsuna
Shigenori Tamaki
Original Assignee
Toyota Jidosha Kabushiki Kaisha
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 Toyota Jidosha Kabushiki Kaisha filed Critical Toyota Jidosha Kabushiki Kaisha
Publication of WO2002053945A1 publication Critical patent/WO2002053945A1/fr

Links

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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
    • F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
    • F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
    • 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
    • F16H61/66—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 specially adapted for continuously variable gearings
    • F16H61/664—Friction gearings
    • F16H61/6649—Friction gearings characterised by the means for controlling the torque transmitting capability of the gearing

Definitions

  • the present invention relates to a toroidal type (or traction type) configured to sandwich a rolling element that transmits torque between an input disk and an output disk and transmit torque between the disks via the rolling element. ) Relates to a continuously variable transmission. Background technology
  • This type of continuously variable transmission has a configuration in which a disk-shaped roller (rolling element) is sandwiched between a pair of disks arranged to face each other.
  • An arcuate rolling surface centered on a point set between the opposing surfaces of the pair of disks is formed on a portion of the opposing surfaces of the pair of disks that is outside a predetermined radius.
  • This rolling surface is continuous in the circumferential direction of each disk. In this way, the rolling surfaces formed in a pair of disks and curved in the three-dimensional direction are toroidal surfaces, and between the rolling surfaces, the opening is rotatable. Is sandwiched between.
  • This roller is a disk having a cross section along the thickness direction of the outer peripheral portion in a plane including the rotation axis, which is an arc surface that matches the arc shape of the rolling surface of each disk. Therefore, when one disk is rotated, the roller rotates, and the other disk rotates accordingly. Then, by inclining the roller and adjusting the contact radius between the mouthpiece and one of the discs and the other disc, a gear ratio according to the ratio between the contact radii is set.
  • An example of such a toroidal-type continuously variable transmission is described in Japanese Patent Application Laid-Open No. 2000-5006767.
  • the toroidal-type continuously variable transmission described in this publication includes an input shaft and an output shaft arranged in parallel with each other.
  • Two input disks and two output disks are provided on the input shaft side.
  • the two input disks are arranged at a predetermined interval in the axial direction, and two output disks are arranged between the two input disks.
  • the two output disks are integrally formed with their rolling surfaces located on both sides in the axial direction. The rolling surface is provided on each of the opposing surfaces of the input disk and the output disk.
  • the input disk and the input shaft are configured to be relatively movable in the axial direction, and are configured to rotate integrally.
  • the other input disk and the input shaft are configured so as not to be relatively movable in the axial direction, and are configured to rotate integrally.
  • One input shaft is disposed in a cylinder, and a hydraulic chamber is formed in the cylinder.
  • the two output disks and the input shaft are configured to be rotatable relative to each other, and a chain drive for transmitting the torque of the two output shafts to the output shaft is provided. Rollers are provided between the input disk and the output disk, and the rollers are sandwiched by the rolling surfaces formed on each disk.
  • the torque of the input shaft is transmitted to the output disk via the input disk and the rollers, and the torque transmitted to the output disk is transmitted to the output shaft via the chain drive.
  • the torque transmission principle will be specifically described.
  • the surface pressure at the contact point between the roller and each rolling surface is high, and the shear resistance of the lubricating oil existing between the roller and each rolling surface is high.
  • the torque is transmitted by this, so-called traction transmission. That is,
  • the torque capacity between the input disk and the output disk changes according to the pressing force of each disk against the roller.
  • one input disk is moved in the axial direction by controlling the hydraulic pressure of a hydraulic chamber formed in a cylinder, and each of the input disks acts on a roller.
  • the clamping force of each disk acting on the roller is determined by conditions such as the hydraulic pressure in the hydraulic chamber, the pressure receiving area on the back surface of the input disk on which this hydraulic pressure acts, or the traction coefficient based on the characteristics of the lubricating oil Is determined by More specifically, the torque transmitted between the input disk and the output disk, and the pressing force of each disk acting on the roller are determined by, for example, Expressions (1) and (2).
  • T the transmission torque per roller
  • / the truncation coefficient
  • r the input. It represents the radius of the contact area between the roller and the rolling surface about the axis of the shaft (that is, the contact diameter)
  • F the pressing force of each disk acting on the roller
  • n one input disk.
  • the number of rollers between one output disk 0 indicates the angle between the axis of the input shaft and the axis of the roller (that is, the angle of inclination)
  • A indicates the hydraulic pressure.
  • R 1 represents the radius of the outer circumference of the input disk on which hydraulic pressure acts
  • rl represents the radius of the inner circumference of the input disk on which hydraulic pressure acts
  • P represents the hydraulic pressure.
  • R 1 represents the radius of the outer circumference of the input disk on which hydraulic pressure acts
  • rl represents the radius of the inner circumference of the input disk on which hydraulic pressure acts
  • P represents the hydraulic pressure.
  • the present invention has been made in view of the technical problem described above, and is a toroidal stepless type in which the torque capacity between the input disk and the output disk can be increased without increasing the outer diameter of the disk.
  • the purpose is to provide a transmission.
  • a feature of the present invention is that a pressing force generated by a plurality of hydraulic chambers is applied to any one of the disks to generate a clamping force for clamping a rolling element between the disk and another disk.
  • the present invention relates to an input disk and an output disk which are opposed to each other and are rotatably arranged on the same axis, and which are sandwiched between the input disk and the output disk, and A rolling element for transmitting torque between the input disk and the output disk; and a torque capacity between the input disk and the output disk according to a clamping force by which the input disk and the output disk sandwich the rolling element.
  • a variable toroidal type continuously variable transmission comprising a plurality of hydraulic chambers for separately applying a pressing force for pressing any one of the discs in a direction to sandwich the rolling element.
  • a plurality of hydraulic chambers for separately applying a pressing force for pressing any one of the disks means that a pressing force acts on any one disk from the plurality of hydraulic chambers.
  • Means multiple oils This does not mean that the number of discs on which the pressure from the pressure chamber acts is “only one”. Therefore, a continuously variable transmission provided with two or more disks on which a pressing force based on the hydraulic pressure of the plurality of hydraulic chambers is provided is also included in the present invention.
  • the holding force of the input disk and the output disk with respect to the rolling element in the axial direction is increased, and the torque capacity between the input disk and the output disk is increased.
  • the pressing force based on the hydraulic pressures of the plurality of hydraulic chambers acts on one disk in the axial direction, the pressing force, that is, the clamping force can be increased without increasing the outer diameter of the disk.
  • the present invention resides in that the operating force generated by the actuator is applied as a pressing force to any one of the disks via a booster mechanism. More specifically, the present invention relates to an input disk and an output disk that are opposed to each other on the same axis and that are rotatably arranged, and that the input disk and the output disk are sandwiched by the input disk and the output disk.
  • a toroidal-type continuously variable transmission provided with a hydraulic torque capacity control mechanism, wherein the torque capacity control mechanism doubles a pressure receiving member on which hydraulic pressure in a hydraulic chamber acts, and a pressing force acting on the pressure receiving member.
  • the input disk and the output disk by applying a force to the input disk and the output disk. It is characterized in that there.
  • the holding force of the input disk and the output disk with respect to the rolling elements is increased, and the torque capacity between the input disk and the output disk is increased.
  • the pressing force based on the hydraulic pressure is boosted by the booster mechanism, and the clamping force between the disks is increased. It is not necessary to increase the outer diameter of the pressure receiving member on which the hydraulic pressure acts.
  • FIG. 1 is a side view showing a torque capacity control mechanism applied to the toroidal-type continuously variable transmission according to the present invention.
  • FIG. 2 is a schematic sectional view showing the configuration of the toroidal-type continuously variable transmission according to the present invention.
  • Fig. 3 is a side view showing the piston of Fig. 1.
  • FIG. 4 is a side view showing another specific example of the torque capacity control mechanism applied to the toroidal-type continuously variable transmission shown in FIG.
  • Fig. 5 is a side view showing the output disk of Fig. 4. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1 is a partial cross-sectional view of the continuously variable transmission 1.
  • the whole of the continuously variable transmission 1 is housed in a hollow housing (not shown).
  • the continuously variable transmission 1 has an input shaft 2 and an output shaft 3, and the input shaft 2 and the output shaft 3 are arranged parallel to each other and horizontally.
  • the input shaft 2 is rotatably held by a bearing (not shown) or the like provided on the nozzle side and is immovable in the axial direction.
  • Power in other words, torque
  • a driving force source such as an engine
  • the torque of the output shaft 3 is configured to be transmitted to wheels (not shown) via a power transmission device (not shown).
  • the end plate 4 shown in Fig. 1 is fixed to the housing.
  • the output shaft 3 and the housing are rotatable relative to each other by a bearing 5 and other members (not shown) provided on the inner periphery of the end plate 4, and the output shaft 3 and the housing are arranged in the axial direction. It is configured to be unable to move relative to ⁇
  • a sprocket 6 is provided substantially at the center of the input shaft 2 in the axial direction.
  • the input shaft 2 and the sprocket 6 are configured to rotate integrally.
  • a sprocket is provided substantially at the center of the output shaft 3 in the axial direction.
  • a chain 38 is wound around the sprocket 6 and the sprocket 7.
  • the output shaft 3 and the sprocket 7 are connected so as to be relatively rotatable.
  • Input disks 8 and 9 are fixed to both sides of the sprocket 7 in the axial direction. That is, a pair of input disks 8 and 9 are arranged back to back. The pair of input disks 8, 9 and the sprocket 7 rotate integrally.
  • output discs 10 and 11 are provided at positions facing the pair of input discs 8 and 9 in the axial direction of the output shaft 3. That is, a pair of input disks 8 and 9 are arranged between a pair of output disks 10 and 11. In other words, the input disks 8 and 9 and the output disks 10 and 11 are arranged in series in the axial direction of the output shaft 3. The side surface of the output disk 11 opposite to the input disk 9 is in contact with a flange 39 provided on the output shaft 3.
  • the input disks 8 and 9 and the output disks 10 and 11 are formed with the opposing rolling surfaces 12 and 13 as full toroidal surfaces in the same manner as the disks in the conventional full toroidal type continuously variable transmission.
  • the disc has been burned.
  • the rolling surfaces 12 and 13 are formed annularly around the axis A1 of the output shaft 3.
  • Each of the rolling surfaces 12, 13 specifically has the following shape. That is, the cross-sectional shapes of the rolling surfaces 12 and 13 in a plane including the axis A 1 of the output shaft 3 are defined between the input disk 9 and the output disk 11 and between the input disk 8 and the output disk 10. It is configured to be a circular arc with a constant radius that curves around a point (not shown) separately set between the two.
  • each of the rolling surfaces 12 and 13 has a shape in which the middle between its innermost and outermost parts is most recessed (retracted). It has.
  • the distance from the moving surface 13 is the widest in the middle part between the innermost peripheral part and the outermost peripheral part.
  • a predetermined interval is provided in the circumferential direction around the axis A 1
  • a plurality of power rollers 14 are arranged.
  • a predetermined space is provided between the input disk 9 and the output disk 11, that is, between the rolling surface 12 and the rolling surface 13 in the circumferential direction around the axis A 1.
  • a plurality of rollers 15 are arranged.
  • These power rollers 14 and 15 are disk-shaped members, and each of the power rollers 14 and 15 is held rotatably about an axis B1. Further, in the plane including the axis A1, the power rollers 14 and 15 are held in a state where the angle between the axis A1 and the axis B1 is changed. Further, an actuator (not shown) for moving the power rollers 14 and 15 back and forth in a direction perpendicular to the axis A1 and the axis B1 is provided. Further, each of the pawl rollers 14 and 15 is formed on a curved surface whose outer peripheral cross-sectional shape matches the curvature of each rolling surface 12 and 13 in a plane including the axis B1. I have.
  • the outer peripheral surface of the power roller 14 comes into contact with the rolling surface 12 of the input disk 8 and the rolling surface 13 of the output disk 10. I have. Further, the outer peripheral surface of the power outlet 15 is in contact with the rolling surface 12 of the input disk 9 and the rolling surface 13 of the output disk 11. Therefore, when the power rollers 14 and 15 are moved back and forth perpendicularly to the axis B 1 by the actuating mechanism, the side slip force acting on the contact portion between the rolling surfaces 12 and 13 and the power rollers 14 and 15 is obtained.
  • an annular drum 16 is mounted on the outer periphery of the output shaft 3 and between the end plate 4 and the output disk 10.
  • a flange portion 3A is formed on the outer periphery of the output shaft 3, and the side of the drum 16 opposite to the output disk 10 contacts the flange portion 3A, so that the drum 16 is moved in the axial direction. Specifically, movement in a direction away from the output disk 10 is restricted.
  • an annular concave portion 17 centering on the axis A 1 is formed on the side surface of the drum 16 on the side of the output disk 10. In this concave portion 17, a disk-shaped disc spring 18 is arranged.
  • annular plate 19 is attached between the drum 16 and the output disk 10 on the outer periphery of the output shaft 3.
  • a step 34 is formed between the drum 16 and the output disk 10 on the outer periphery of the output shaft 3.
  • the plate 19 is restricted from moving in the axial direction toward the drum 16 side.
  • An annular concave portion 24 is formed on the side surface of the output disk 10 on the drum 16 side, and a plate 19 is disposed in the concave portion 24.
  • annular side surface 24B facing the concave portion 24 and orthogonal to the axis A1 is formed.
  • three holes 20 are formed at predetermined intervals on a circumference centered on the axis A1. Each hole 20 penetrates the plate 19 in the axial direction. The end face of the plate 19 and the end face of the drum 16 are in contact with each other.
  • annular recess 21 having a larger outer diameter than the recess 17 is formed at a position closer to the plate 19 than the recess 17 in the drum 16.
  • An annular piston 22 is arranged in the recess 21.
  • three protruding portions 23 are formed on the same circumference at predetermined intervals on the side surface of the piston 22 on the output disk 10 side.
  • the axial length of each protrusion 23 is set to be longer than the axial thickness of the plate 19.
  • Each protruding portion 23 is formed in a cylindrical shape.
  • the tip surface of each projection 23 is in contact with the side surface 24 B of the output disk 10. Further, each protrusion 23 is inserted into each hole 20 of plate 19.
  • each protrusion 23 centered on the axis A 1 is set to be smaller than the outer diameter of the plate 19. Furthermore, a pressure receiving surface 22 A orthogonal to the axis A 1 is formed on the back surface of the piston 22 on the concave portion 17 side. The area of the pressure receiving surface 22 A is larger than the sum of the areas of the tips of the protrusions 23 that are in contact with the output disk 10.
  • the piston 22, the output shaft 3, the drum 16, and the plate 19 are configured to be relatively movable in the axial direction.
  • This piston 2 The disc 2 is pressed in the axial direction toward the output disc 10 by the elastic force of the disc spring 18.
  • a hydraulic chamber 25 is formed by the outer peripheral surface of the output shaft 3 configured as described above, and a space (mainly, the recess 17) surrounded by the drum 16 and the piston 22.
  • a 0 ring 26 is provided between the outer circumference of the output shaft 3 and the inner circumference of the drum 16, and a 0 ring is provided between the inner circumference of the recess 21 of the drum 16 and the outer circumference of the piston 22.
  • a ring 27 is provided, and an O-ring 28 is provided between the outer circumference of the output shaft 3 and the inner circumference of the piston 22.
  • the hydraulic chamber 25 is liquid-tightly sealed by these o-rings 26, 27, 28.
  • a hydraulic chamber 29 is formed by a space surrounded by the outer periphery of the output shaft 3, the side surface of the plate 19, and the inner wall surface of the concave portion 24 of the output disk 10.
  • a ring 30 is provided between the inner circumference of the output disk 10 and the outer circumference of the output shaft 3, and a 0 ring 3 is provided between the inner circumference of the plate 19 and the outer circumference of the output shaft 3.
  • a 0 ring 32 is provided between the outer circumference of the plate 19 and the inner circumference of the recess 24 of the output disk 10. The outer circumference of each projection 23 and each hole are provided.
  • a 0 ring 33 is provided between the inner circumference of 20.
  • the hydraulic chamber 29 is liquid-tightly sealed by the O-rings 30, 31, 32, and 33.
  • An oil passage 35 is formed at the center of the output shaft 3 along the axial direction. This oil passage 35 is connected to the discharge side of an oil pump (not shown) via a solenoid valve (not shown). This oil pump is driven by the aforementioned driving power source. Further, oil passages 36 and 37 communicating with the oil passage 35 are formed. The oil passage 36 communicates with the hydraulic chamber 25, and the oil passage 37 communicates with the hydraulic chamber 29.
  • An electronic control unit (not shown) for controlling the driving force source, the actuator, the electromagnetic valve, and the like is provided.
  • This electronic control unit Various signals are input to the device, and based on these signals and data stored in the electronic control unit, the driving force source and the electromagnetic valve are controlled in the event of an accident.
  • the power rollers 14 and 15 are moved in a direction parallel to the rotation plane, and the side slip generated at the contact portion between the power rollers 14 and 15 and the disks 8, 9, 10, 11 accordingly.
  • the power rollers 14, 15 are tilted by the force. By tilting, each of the roller rollers 14 and 15 returns to the position before being moved by the actuator. Thus, the radius of the contact portion between the power rollers 14, 15 and the rolling surfaces 12, 13 is changed, and the speed ratio of the continuously variable transmission 1 is controlled.
  • the solenoid valves are controlled in accordance with the torque transmitted to the input disks 8 and 9, and the hydraulic pressure in the hydraulic chambers 25 and 29 is controlled.
  • the hydraulic pressure in the hydraulic chamber 29 acts on a part of the side surface 24B, specifically, on the pressure receiving surface 24A excluding the area where each protrusion 23 contacts, and the output disk 10 is moved to the input disk 8 side.
  • a pressing force is generated to push the output shaft 3 in the axial direction toward the output shaft 3.
  • the piston 22 is pressed in the axial direction of the output shaft 3 toward the output disk 10 by the pressing force of the countersunk spring 18 and the oil pressure of the hydraulic chamber 25.
  • the output disk 10 is input from the protrusion 23 to the input disk.
  • a pressing force is generated in the direction of pressing in the axial direction of the output shaft 3 toward the work 8 side.
  • the pressing force is transmitted to the input disks 8 and 9 via the power roller 14.
  • the power is transmitted from the input disk 9 to the power outlet 15.
  • the pressing force transmitted to the power roller 15 is transmitted to the output disk 11, the pressing force is received by the flange 39.
  • the movement of the output disk 11 away from the input disk 9 is restricted by the flange 39.
  • the power rollers 14 and 15 are sandwiched in the axial direction by the input disks 8 and 9 and the output disks 10 and 11 so that the contact pressure between the rolling surfaces 12 and 13 is increased. And the input discs 8, 9 and the output discs 10, 11, 1 and the power rollers 14, 11, due to the shearing resistance of the lubricating oil existing between each of the power rollers 14, 15 and each of the rolling surfaces 12, 13. Transmission of torque is performed between the motor and the motor. The torque transmitted to the output disks 10, 11 is transmitted to the wheels via the output shaft 3.
  • F 3 F 1 + F 2... Equation (5)
  • P represents the hydraulic pressure of the hydraulic chambers 25 and 29, and A 1 is the hydraulic pressure of the hydraulic chamber 25 in a plane orthogonal to the axis A1.
  • A2 represents the area of the pressure receiving surface 22A on which A acts, and A2 represents the entire area of the side surface 24B of the output disk 10, and A3 represents the area of the tip of one protrusion 23 Represents the area, n 1 represents the number of protrusions 23, R 2 represents the radius of the outer periphery of the side surface 24 B, r 2 represents the radius of the inner periphery of the side surface 24 R, and R 3 represents the pressure receiving pressure R 3 represents the radius of the inner periphery of the pressure receiving surface 22 A, and r 4 represents the radius of the projection 23.
  • the hydraulic pressure in the hydraulic chambers 25 and 29 is controlled to the same pressure. Further, a pressing force acts on the piston 22 from the disc spring 18 as well, but in Expression (5), this pressing force is omitted
  • the pressing forces based on the hydraulic pressures of the two hydraulic chambers 25 and 29 are combined and act on the output disk 10.
  • the pressing force corresponding to the oil pressure acting on the two pressure receiving surfaces 22 A and 24 A arranged in the axial direction is output.
  • Acting on force disc 10. The areas of the pressure receiving surfaces 22 A and 24 A are larger than the area of the side surface of the output disk 10.
  • the torque capacity between the input disks 8, 9 and the output disks 10, 1 1 and the power rollers 14, 15 can be increased without increasing the area of the side surface 248 of the output disk 10, that is, without increasing the outer diameter of the output disk 10. Can be increased. Therefore, it is possible to suppress the continuously variable transmission 1 from increasing in size in the radial direction of the output shaft 3, and the in-vehicle performance of the continuously variable transmission 1 is improved.
  • roller 14, 14 corresponds to the rolling element of the present invention.
  • Drum 16 recesses 17, 21, 24, disc spring 18, hydraulic chambers 25, 29, piston 22, pressure receiving surface 22A, 24A, protrusion 23, side surface 24B, plate 19, hole 20, etc.
  • this is a so-called torque capacity control mechanism.
  • FIG. 4 is a cross-sectional view showing another specific example of the torque capacity control mechanism applied to the continuously variable transmission 1 of FIG.
  • a projection 40 is formed on the back surface of the output disk 10, that is, on the side surface opposite to the rolling surface 13.
  • the protruding portion 40 is formed in a ring shape centering on the axis A1.
  • An annular drum 41 is fixed to the outer periphery of the output shaft 3.
  • the so-called inner surface of the drum 41 and the back surface of the output disk 10 face each other.
  • the drum 41 has a cylindrical portion 42 extending in the axial direction toward the output disk 10.
  • the output disk 10 is arranged inside the cylindrical portion 42.
  • an annular concave portion 43 centering on the axis A 1 is formed on the surface of the drum 41 on the side of the output disk 10.
  • An annular piston 44 is arranged in the recess 43 so as to be movable in the axial direction.
  • the inner circumferential surface and outer cylindrical portion 54 of the bistone 44 and the inner circumferential wall and the outer O-rings 45, 46 are arranged between the peripheral wall.
  • the hydraulic chamber 47 is formed in a space surrounded by the wall surface of the concave portion 43 and the side surface of the biston 44, and the hydraulic chamber 47 is liquid-tightly sealed by the O-rings 45, 46.
  • An oil passage 48 is provided inside the output shaft 3 along the axial direction thereof.
  • the oil passage 48 is connected to the oil pump discharge side via a solenoid valve (not shown).
  • An oil passage 49 communicating with the hydraulic chamber 47 is formed in the drum 41, and the oil passage 47 and the oil passage 49 are connected by an oil passage 50.
  • the drum 41 has an annular holding surface 51 orthogonal to the axis A1.
  • a snap ring 52 is attached to the inner periphery of the cylindrical portion 42, and an annular disc spring 53 is provided in the cylindrical portion 42.
  • the outer peripheral end of the disc spring 53 is arranged between the holding surface 51 and the snap ring 52, and one side of the outer peripheral end of the disc spring 53 (the side opposite to the output disk 10).
  • the holding surface 51 contact with each other to form a contact portion C1.
  • the inner diameter of the disc spring 53 is set smaller than the outer diameter R 5 of the outer cylindrical portion 54 of the piston 44. That is, one side surface on the inner peripheral side of the disc spring 53 comes into contact with the end surface of the outer peripheral cylindrical portion 54 to form a contact portion D1.
  • a represents the distance between the contact part E1 and the contact part C1 in the radial direction
  • b represents the distance between the contact part D1 and the contact part C1 in the radial direction.
  • the pressing force input to the contact portion D1 is amplified by the principle of leverage with the contact portion C1 as a fulcrum, the contact portion D1 as a power point, and the contact portion E1 as an action point, and the output disc is amplified. It is transmitted to 10. That is, the thrust (pressing force) F4 acting on the piston 44 by the hydraulic pressure of the hydraulic chamber 47 is obtained by the equation (6), and the pressing force F5 transmitted from the disc spring 53 to the output disk 10 is given by the equation (7) Required by
  • Equation (7) P represents the hydraulic pressure of the hydraulic chamber 47, and A4 is the piston on which the hydraulic pressure of the hydraulic chamber 47 acts.
  • 44 represents the area of the pressure receiving surface 44 A
  • R5 represents the radius of the outer peripheral surface of the piston 44 (outer cylindrical portion 54)
  • r5 represents the radius of the inner peripheral surface of the piston 44
  • Hydraulic chamber 47, biston 44, pressure receiving surface 44A, outer cylindrical portion 5 4, the disc spring 53, the snap ring 52, the projection 40, the holding surface 51, and the like correspond to the torque capacity control mechanism of the present invention
  • the piston 44 and the outer peripheral cylindrical portion 54 correspond to the present invention.
  • Configurations such as a disc spring 53, a snap ring 52, a protrusion 40, and a holding surface 51 correspond to a pressure receiving member, and correspond to a booster mechanism of the present invention.
  • the continuously variable transmission 1 shown in Fig. 2 is a double-cavity type continuously variable transmission with a cavity that accommodates two power rollers 14 and 15,
  • the present invention can also be applied to a single-cavity continuously variable transmission provided with one. Further, the present invention can be applied to a half toroidal type continuously variable transmission.
  • the continuously variable transmission 1 shown in Fig. 2 the torque between the input shaft and the output shaft It is also possible to adopt a configuration in which the torque transmission is performed by a gear instead of the chain.
  • the pressing forces based on the hydraulic pressures of the plurality of hydraulic chambers are combined, and the combined pressing force acts on one disk in the axial direction, so that it is not necessary to increase the outer diameter of one disk. Therefore, it is possible to suppress an increase in the size of the disk in the radial direction of the axis, and the on-board performance of the toroidal type continuously variable transmission is improved.
  • the clamping force of the input disk and the output disk with respect to the rolling element is increased, and the torque capacity between the input disk and the output disk is increased.
  • the pressing force based on the hydraulic pressure is boosted by the booster mechanism and the clamping force between the disks is increased, it is not necessary to increase the outer diameter of the pressure receiving member on which the hydraulic pressure acts. Therefore, it is possible to suppress an increase in the size of the disk in the radial direction of the axis, and to improve the on-board performance of the toroidal-type continuously variable transmission.
  • This invention can be utilized in the field

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

L'invention concerne une transmission variable en continu toroïdale, qui comprend un disque d'entrée et un disque de sortie montés rotatifs et de façon opposée sur un même axe, un élément de roulement pris en sandwich entre le disque d'entrée et le disque de sortie et transmettant un couple entre le disque d'entrée et le disque de sortie, ainsi qu'un mécanisme de régulation de capacité de couple hydraulique qui sert à limiter une capacité de couple transmise entre le disque d'entrée et le disque de sortie en exerçant une force de maintien axial sur le disque d'entrée et le disque de sortie. Ce mécanisme de régulation de capacité de couple comporte en outre une pluralité de chambres de pression hydraulique (25, 29) et un piston (22) pour l'application séparée d'une force de pression axiale sur le disque de sortie (10).
PCT/JP2001/011258 2000-12-28 2001-12-21 Transmission variable en continu toroidale WO2002053945A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000402406A JP3555577B2 (ja) 2000-12-28 2000-12-28 トロイダル型無段変速機
JP2000-402406 2000-12-28

Publications (1)

Publication Number Publication Date
WO2002053945A1 true WO2002053945A1 (fr) 2002-07-11

Family

ID=18866707

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2001/011258 WO2002053945A1 (fr) 2000-12-28 2001-12-21 Transmission variable en continu toroidale

Country Status (2)

Country Link
JP (1) JP3555577B2 (fr)
WO (1) WO2002053945A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005045284A2 (fr) * 2003-11-05 2005-05-19 Daimlerchrysler Ag Engrenage toroidal a dispositif de pression hydraulique

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4696537B2 (ja) * 2004-11-18 2011-06-08 日本精工株式会社 トロイダル型無段変速機
JP5045805B2 (ja) * 2010-10-28 2012-10-10 日本精工株式会社 トロイダル型無段変速機
JP2012172685A (ja) * 2011-02-17 2012-09-10 Nsk Ltd トロイダル型無段変速機
JP6492906B2 (ja) * 2015-04-10 2019-04-03 日本精工株式会社 トロイダル型無段変速機

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62258254A (ja) * 1986-05-01 1987-11-10 Nissan Motor Co Ltd トロイダル型無段変速機
JPH03107602A (ja) * 1989-09-20 1991-05-08 Kiyohara Masako 流体制御装置用アクチエータ
US5180339A (en) * 1991-06-26 1993-01-19 Borg-Warner Automotive, Inc. Double acting secondary sheave servo for a continuously variable transmission
JPH10169738A (ja) * 1996-12-05 1998-06-26 Koyo Seiko Co Ltd トロイダル型無段変速機
US6030310A (en) * 1996-04-19 2000-02-29 Torotrak (Development) Limited Variator control system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62258254A (ja) * 1986-05-01 1987-11-10 Nissan Motor Co Ltd トロイダル型無段変速機
JPH03107602A (ja) * 1989-09-20 1991-05-08 Kiyohara Masako 流体制御装置用アクチエータ
US5180339A (en) * 1991-06-26 1993-01-19 Borg-Warner Automotive, Inc. Double acting secondary sheave servo for a continuously variable transmission
US6030310A (en) * 1996-04-19 2000-02-29 Torotrak (Development) Limited Variator control system
JPH10169738A (ja) * 1996-12-05 1998-06-26 Koyo Seiko Co Ltd トロイダル型無段変速機

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Clutch ooi to clutch ban", 15 January 1968, THE JAPAN SOCIETY OF MECANICAL ENGINEERS, XP002909435 *
"Doryoku dentatsu sochi", 20 November 1980, K.K. SANKAIDO, XP002909436 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005045284A2 (fr) * 2003-11-05 2005-05-19 Daimlerchrysler Ag Engrenage toroidal a dispositif de pression hydraulique
DE10352174A1 (de) * 2003-11-05 2005-06-09 Daimlerchrysler Ag Toroidgetriebe mit einer hydraulischen Anpressvorrichtung
WO2005045284A3 (fr) * 2003-11-05 2005-08-18 Daimler Chrysler Ag Engrenage toroidal a dispositif de pression hydraulique

Also Published As

Publication number Publication date
JP2002195365A (ja) 2002-07-10
JP3555577B2 (ja) 2004-08-18

Similar Documents

Publication Publication Date Title
US5056640A (en) Torque transmission device for a four-wheel drive vehicle
US6484858B1 (en) Friction clutch and automatic transmission of automobile using the same and non-stage transmission of automobile and power distribution device of automobile and power transmission device of motorcycle
JP2604422B2 (ja) トロイダル式無段変速機のローディングガム装置
WO2002053945A1 (fr) Transmission variable en continu toroidale
US7077780B2 (en) Toroidal type continuously variable transmission
WO2002053953A1 (fr) Transmission toroidale variable en continu
JP3688178B2 (ja) トロイダル型無段変速機
JP2001012573A (ja) トロイダル形無段変速装置
JP4106797B2 (ja) トロイダル形無段変速装置
JP4882965B2 (ja) トロイダル式無段変速機
JP3760697B2 (ja) トロイダル型無段変速機及び変速比無限大無段変速機
JP2000213564A (ja) カップリング
KR100796163B1 (ko) 차량의 전자 제어 식 액슬 모듈
JP4901304B2 (ja) デファレンシャル装置
EP0637705B1 (fr) Variateur continu de vitesse à rouleaux de traction
JP4809526B2 (ja) ベルト式無段変速機
WO2005078313A1 (fr) Transmission à variation continue
JPH10169738A (ja) トロイダル型無段変速機
JP2008082357A (ja) 無段変速装置
JP2004162851A (ja) トロイダル型無段変速機のローディング油圧制御方法
JP4826409B2 (ja) 無段変速装置
JP2002286125A (ja) 制動力制御方法
JP4899785B2 (ja) 無段変速装置
JP2005172065A (ja) トラクションドライブ式無段変速機
JP3244293B2 (ja) 四輪駆動車用駆動力伝達装置

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application