WO2012169057A1 - 無段変速機 - Google Patents
無段変速機 Download PDFInfo
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- WO2012169057A1 WO2012169057A1 PCT/JP2011/063347 JP2011063347W WO2012169057A1 WO 2012169057 A1 WO2012169057 A1 WO 2012169057A1 JP 2011063347 W JP2011063347 W JP 2011063347W WO 2012169057 A1 WO2012169057 A1 WO 2012169057A1
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- torque
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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
- 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
- F16H15/40—Gearings providing a continuous range of gear ratios in which two members co-operative by means of balls, or rollers of uniform effective diameter, not mounted on shafts
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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
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
- F16H15/50—Gearings providing a continuous range of gear ratios
- F16H15/52—Gearings providing a continuous range of gear ratios in which a member of uniform effective diameter mounted on a shaft may co-operate with different parts of another member
Definitions
- the present invention includes a plurality of rotating elements having a common rotating shaft, and a plurality of rolling members arranged radially with respect to the rotating shaft, and each rolling element sandwiched between two of the rotating elements.
- the present invention relates to a continuously variable transmission that continuously changes a gear ratio between input and output by tilting a member.
- the traction planetary gear mechanism includes a transmission shaft that serves as a rotation center, a plurality of rotational elements that can rotate relative to each other with the central axis of the transmission shaft as a first rotation central axis, and parallel to the first rotation central axis.
- a rolling member having a different second rotation center axis, a plurality of rolling members arranged radially around the first rotation center axis, a support shaft for rotating and supporting the rolling member, and a transmission shaft And a holding member that holds the rolling member via a protruding portion from the rolling member on the support shaft.
- each rolling member is sandwiched between the first rotating element and the second rotating element arranged to face each other, and each rolling member is arranged on the outer peripheral surface of the third rotating element,
- the gear ratio is changed steplessly by tilting the rolling member.
- Patent Document 1 discloses this type of continuously variable transmission.
- the continuously variable transmission of Patent Document 1 includes an iris plate that tilts a rolling member via a support shaft by its own rotation, a motor as a drive source that rotates the iris plate, and a support shaft that rotates by itself. And a support plate (holding member) that generates a skew in the rolling member, and a motor as a drive source different from the above that rotates the support plate.
- the iris plate has an arcuate iris groove into which the support shaft is inserted.
- the support plate includes a radial guide portion into which the support shaft is inserted. This continuously variable transmission applies a force from the iris groove to the support shaft by the rotation of the iris plate, thereby tilting the rolling member.
- Patent Document 2 includes, as an example of this type of continuously variable transmission, a cam that moves the sun roller (third rotating element) in the axial direction by its own rotation, and the rolling member is tilted by the movement of the sun roller. What is converted is disclosed.
- the continuously variable transmission is provided with a spline that rotates the carrier (holding member) in conjunction with the rotation of the cam.
- the continuously variable transmission of Patent Document 1 includes not only a motor for rotating the iris plate but also another motor for rotating the support plate. Therefore, this continuously variable transmission can reduce the shift energy of the iris plate, but may increase the size of the transmission by a plurality of motors.
- an object of the present invention is to provide a continuously variable transmission that can improve the disadvantages of the conventional example and can reduce the shift energy and suppress the enlargement of the physique.
- the present invention provides a first and a first relatively rotatable shaft having a transmission shaft as a fixed shaft serving as a rotation center and a common first rotation center shaft arranged opposite to each other on the transmission shaft.
- 2 rotation elements and a second rotation center axis parallel to the first rotation center axis, and a plurality of the rotation elements arranged radially about the first rotation center axis are arranged in the first and second rotation elements.
- a rolling member sandwiched between the rolling member and the second rotation center axis, the supporting shaft of the rolling member projecting at both ends from the rolling member, and the respective rolling members are disposed on the outer peripheral surface;
- a first guide portion that guides one projecting portion of each support shaft in the radial direction is formed.
- a throttle portion that holds one protrusion of the support shaft at the intersection, and is centered on the first rotation center axis with respect to the transmission shaft.
- a tilting element that moves the intersection in the radial direction by relative rotation; an actuator that rotates the tilting element relative to the transmission shaft; and a relative relationship between the first holding member and the tilting element.
- a torque transmission unit that generates a transmission torque according to the rotation speed between the first holding member and the tilting element.
- the torque transmission unit is set to a transmission torque larger than a product of a force from the support shaft to the first holding member according to an input torque and an action radius of the force.
- the transmission torque of the torque transmitting portion is transmitted to the first holding member by rotating the tilting element with the actuator, and the first holding member can be rotated. That is, according to this continuously variable transmission, it is not necessary to prepare a dedicated actuator for rotating the first holding member as in the prior art by providing the torque transmitting portion, and the tilting element can be rotated. The first holding member can also be rotated only by the actuator. Therefore, this continuously variable transmission can achieve both reduction of shift energy required for shifting and downsizing of the transmission.
- FIG. 1 is a partial sectional view showing the configuration of an embodiment of a continuously variable transmission according to the present invention.
- FIG. 2 is a view for explaining the first carrier and is a cross-sectional view taken along the line XX of FIG.
- FIG. 3 is a diagram illustrating the second carrier.
- FIG. 4 is a diagram illustrating the iris plate.
- FIG. 5 is a diagram for explaining the force generated by the input torque and the rotation direction of the iris plate at the time of deceleration-side shifting.
- FIG. 6 is a diagram illustrating an example of torque transmission characteristics of the torque transmission unit.
- FIG. 7 is a diagram illustrating the skew force at the time of deceleration-side shifting.
- FIG. 1 is a partial sectional view showing the configuration of an embodiment of a continuously variable transmission according to the present invention.
- FIG. 2 is a view for explaining the first carrier and is a cross-sectional view taken along the line XX of FIG.
- FIG. 3 is a diagram
- FIG. 8 is a diagram for explaining the force generated by the input torque and the direction of rotation of the iris plate at the time of speed increase side shifting.
- FIG. 9 is a diagram illustrating the skew force at the time of speed-up side shifting.
- FIG. 10 is a diagram illustrating an example of characteristics of the elastic member.
- Reference numeral 1 in FIG. 1 indicates a continuously variable transmission according to this embodiment.
- the continuously variable transmission mechanism that constitutes the main part of the continuously variable transmission 1 includes first to third rotating elements 10, 20, 30 that have a common first rotation center axis A 1 and are capable of relative rotation with each other.
- a plurality of rolling members 40 arranged radially about the first rotation center axis A1 and each having a second rotation center axis A2 parallel to the first rotation center axis A1 and a reference position described later.
- the shaft 50 as a transmission shaft disposed at the rotation center of the first to third rotating elements 10, 20, 30, and the first and second holding members 61 that hold the respective rolling members 40 in a tiltable manner. , 62, a so-called traction planetary gear mechanism.
- the continuously variable transmission 1 changes the speed ratio ⁇ between input and output by inclining the second rotation center axis A2 with respect to the first rotation center axis A1 and tilting the rolling member 40.
- the direction along the first rotation center axis A1 and the second rotation center axis A2 is referred to as an axial direction
- the direction around the first rotation center axis A1 is referred to as a circumferential direction.
- the direction orthogonal to the first rotation center axis A1 is referred to as a radial direction
- the inward side is referred to as a radial inner side
- the outward side is referred to as a radial outer side.
- Torque can be transmitted through the rolling members 40 between the first rotating element 10, the second rotating element 20, and the third rotating element 30.
- one of the first to third rotating elements 10, 20, 30 is used as a torque (power) input unit, and at least one of the remaining rotating elements is used. It can be used as a torque output section.
- the ratio of the rotational speed (the number of rotations) between any rotation element serving as an input unit and any rotation element serving as an output unit is the gear ratio ⁇ .
- the continuously variable transmission 1 is disposed on the power transmission path of the vehicle.
- the input part is connected with the power source side, such as an engine and a motor
- the output part is connected with the drive wheel side.
- the rotation operation of each rotation element when torque is input to the rotation element as the input unit is referred to as normal drive
- the rotation element as the output unit is in the direction opposite to that during normal drive.
- the rotating operation of each rotating element when torque is input is called reverse driving.
- the continuously variable transmission 1 is configured to roll with the first to third rotating elements 10, 20, 30 by pressing at least one of the first and second rotating elements 10, 20 against the rolling member 40.
- An appropriate tangential force (traction force) is generated between the member 40 and torque can be transmitted therebetween.
- the continuously variable transmission 1 tilts each rolling member 40 on a tilt plane including its own second rotation center axis A2 and first rotation center axis A1, and the first rotation element 10 By changing the ratio of the rotation speed (rotation speed) between the second rotation element 20 and the second rotation element 20, the ratio of the rotation speed (rotation speed) between the input and output is changed.
- the first and second rotating elements 10 and 20 function as a ring gear as a planetary gear mechanism.
- the third rotating element 30 functions as a sun roller of the traction planetary gear mechanism.
- the rolling member 40 functions as a ball-type pinion in the traction planetary gear mechanism, and the first and second holding members 61 and 62 function as carriers.
- the first and second rotating elements 10 and 20 are referred to as “first and second rotating members 10 and 20”, respectively.
- the third rotating element 30 is referred to as “sun roller 30”, and the rolling member 40 is referred to as “planetary ball 40”.
- the first and second holding members 61 and 62 are referred to as “first carrier 61” and “second carrier 62”, respectively.
- the second carrier 62 is a fixing element and is fixed to the shaft 50.
- the shaft 50 is fixed to a fixed portion of the continuously variable transmission 1 in a housing or a vehicle body (not shown), and is a columnar or cylindrical fixed shaft configured not to rotate relative to the fixed portion. To do.
- the first and second rotating members 10 and 20 are disk members (disks) or ring members (rings) whose center axes coincide with the first rotation center axis A1, and each planetary ball is opposed to each other in the axial direction. 40 is interposed. In this example, both are circular members.
- the first and second rotating members 10 and 20 have a contact surface that comes into contact with the outer peripheral curved surface on the radially outer side of each planetary ball 40 described in detail later.
- Each contact surface has, for example, a concave arc surface having a curvature equivalent to the curvature of the outer peripheral curved surface of the planetary ball 40, a concave arc surface having a curvature different from the curvature of the outer peripheral curved surface, a convex arc surface, or a flat surface. is doing.
- the first and second contact surfaces are formed such that the distance from the first rotation center axis A1 to the contact point with each planetary ball 40 is the same length in the state of a reference position described later.
- the contact angles ⁇ of the rotating members 10 and 20 with respect to the planetary balls 40 are the same.
- the contact angle ⁇ is an angle from the reference to the contact point with each planetary ball 40.
- the radial direction is used as a reference.
- the respective contact surfaces are in point contact or surface contact with the outer peripheral curved surface of the planetary ball 40. Further, each contact surface is radially inward with respect to the planetary ball 40 when an axial force (pressing force) is applied from the first and second rotating members 10 and 20 toward the planetary ball 40. And an oblique force (normal force) is applied.
- the first rotating member 10 acts as a torque input portion when the continuously variable transmission 1 is positively driven
- the second rotating member 20 acts as a torque output portion when the continuously variable transmission 1 is positively driven.
- an input shaft (not shown) is connected to the first rotating member 10
- an output shaft (not shown) is connected to the second rotating member 20.
- the input shaft and the output shaft can perform relative rotation in the circumferential direction with respect to the shaft 50.
- the continuously variable transmission 1 may use what is provided as an input shaft as an output shaft and what is provided as an output shaft as an input shaft.
- an axial force generator (not shown) for generating an axial force is provided.
- a torque cam can be considered as the axial force generating portion. Therefore, the axial force generator generates an axial force between the input shaft and the first rotating member 10 by engaging the engaging member on the input shaft side and the engaging member on the first rotating member 10 side. It is generated and rotational torque is transmitted, and these are rotated together.
- the axial force generated by the axial force generating portion is transmitted to the first rotating member 10 and the second rotating member 20, and these become the pressing force when pressing each planetary ball 40.
- the axial force generation unit may be provided between the output shaft and the second rotating member 20 in place of the first rotating member 10 side or together with the first rotating member 10 side.
- the sun roller 30 is disposed concentrically with the shaft 50 and performs relative rotation in the circumferential direction with respect to the shaft 50.
- radial bearings RB 1 and RB 2 are disposed between the sun roller 30 and the shaft 50.
- a plurality of planetary balls 40 are radially arranged at substantially equal intervals on the outer peripheral surface of the sun roller 30. Accordingly, the outer peripheral surface of the sun roller 30 becomes a rolling surface when the planetary ball 40 rotates.
- the sun roller 30 can roll (rotate) each planetary ball 40 by its own rotation, or can rotate along with the rolling operation (rotation) of each planetary ball 40.
- a locking member such as a snap ring is provided on the side surfaces of the radial bearings RB1 and RB2 so as not to move in the axial direction with respect to the shaft 50.
- the planetary ball 40 is a rolling member that rolls on the outer peripheral surface of the sun roller 30.
- the planetary ball 40 is preferably a perfect sphere, but it may have a spherical shape at least in the rolling direction, for example, a rugby ball having an elliptical cross section.
- the planetary ball 40 is rotatably supported by a support shaft 41 that passes through the center of the planetary ball 40.
- the planetary ball 40 can be rotated relative to the support shaft 41 with the second rotation center axis A2 as a rotation axis (that is, rotation) by a bearing disposed between the outer periphery of the support shaft 41. . Accordingly, the planetary ball 40 can roll on the outer peripheral surface of the sun roller 30 around the support shaft 41. Both ends of the support shaft 41 are projected from the planetary ball 40.
- the reference position of the support shaft 41 is a position where the second rotation center axis A2 is parallel to the first rotation center axis A1.
- the support shaft 41 is inclined from the reference position and from within the tilt plane including the rotation center axis (second rotation center axis A2) and the first rotation center axis A1 formed at the reference position. It can swing (tilt) with the planetary ball 40 between the positions. The tilt is performed with the center of the planetary ball 40 as a fulcrum in the tilt plane.
- the first and second carriers 61 and 62 are arranged to face each other on the shaft 50 and hold the support shaft 41 so as not to prevent the tilting operation of the planetary balls 40 arranged therebetween. .
- One of the protruding portions of the support shaft 41 protruding from the planetary ball 40 is held by the first carrier 61 and the other is held by the second carrier 62.
- the first and second carriers 61 and 62 are, for example, disk members having a central axis coinciding with the first rotation central axis A1.
- the continuously variable transmission 1 is provided with first and second guide portions 63 and 64 for guiding the support shaft 41 in the tilt direction when each planetary ball 40 tilts.
- the first and second guide portions 63 and 64 are provided on the first and second carriers 61 and 62, respectively.
- the first and second guide portions 63 and 64 are radial guide grooves and guide holes for guiding the support shaft 41 protruding from the planetary ball 40 in the tilt direction, and the first and second carriers. It forms for each planetary ball 40 in the part which each of 61 and 62 opposes (FIG. 2, 3). That is, all the first and second guide portions 63 and 64 are radially formed when viewed from the axial direction (for example, the direction of arrow A in FIG. 1).
- a first carrier 61 is disposed between each planetary ball 40 and an iris plate 70 described later.
- the first guide portion 63 of the first carrier 61 is used as a guide hole and penetrates the support shaft 41.
- the second guide portion 64 of one second carrier 62 may be either a guide groove or a guide hole.
- the first and second guide portions 63 and 64 have a width in the circumferential direction of the first and second carriers 61 and 62.
- the 1st and 2nd guide parts 63 and 64 expand the width of the planetary ball 40 by expanding the width thereof than the diameter of the support shaft 41 (the outer shape when a roller bearing or the like is interposed). The tilting movement is not disturbed.
- the first carrier 61 disposed near the iris plate 70 is attached so as to be rotatable relative to the shaft 50, while the second carrier disposed at a position farther from the iris plate 70 than the first carrier 61.
- the carrier 62 is fixed to the shaft 50.
- the first carrier 61 has a groove 65 formed on the inner peripheral side thereof.
- the number of the groove portions 65 is one, but a plurality of the groove portions 65 may be formed diagonally or radially about the first rotation center axis A1.
- a protrusion 51 is provided at a position corresponding to the groove 65.
- the first carrier 61 is attached to the shaft 50 in a state where the protruding portion 51 is inserted into the groove portion 65.
- the wall surface on the radially inner side of the groove portion 65 and the wall surface on the radially outer side of the protruding portion 51 are formed so as not to contact each other.
- a gap is formed between each wall surface in the circumferential direction of the groove portion 65 and each wall surface in the circumferential direction of the protruding portion 51.
- an elastic member 66 such as a string spring is disposed in each gap.
- the respective elastic members 66 are arranged so as to be able to expand and contract in the circumferential direction or substantially in the circumferential direction, and hold the first carrier 61 in a neutral position if no circumferential force is applied to the first carrier 61.
- the neutral position means that when the first and second guide portions 63 and 64 have the same shape in the width direction and the radial direction, when viewed in the axial direction, the first guide portion 63 and the second guide portion 64 Is a position where the gaps between the support shaft 41 and the respective wall surfaces in the width direction of the first guide portion 63 are even.
- the second carrier 62 cannot be relatively rotated in the circumferential direction or relatively moved in the axial direction with respect to the shaft 50 by fixing its inner peripheral surface side to the outer peripheral surface side of the shaft 50 by fitting or press-fitting. Like that.
- the second rotating member 20 has a lower rotation (deceleration) than the first rotating member 10 when the planetary ball 40 is tilted in one direction, and the first rotating member 10 is tilted in the other direction. (High speed). Therefore, in the continuously variable transmission 1, the rotation ratio (speed ratio ⁇ ) between the first rotating member 10 and the second rotating member 20 can be changed steplessly by changing the tilt angle. it can.
- the speed ratio ⁇ is increased ( ⁇ ⁇ 1), the upper planetary ball 40 in FIG.
- the continuously variable transmission 1 is provided with a transmission that changes its transmission ratio ⁇ . Since the gear ratio ⁇ changes with changes in the tilt angle of the planetary ball 40, a tilting device that tilts each planetary ball 40 is used as the speed change device.
- the transmission is provided with a disk-shaped iris plate (tilting element) 70.
- the iris plate 70 is attached to the shaft 50 via a radial bearing RB3 on the radially inner side, and can rotate relative to the shaft 50 about the first rotation center axis A1.
- an actuator as a drive source of the iris plate 70 is used.
- the motor MG shown in FIG. 4 is provided. The driving force of the motor MG is transmitted to the outer peripheral portion of the iris plate 70 via a power transmission unit such as a worm gear 71, for example.
- the iris plate 70 is outside the first carrier 61 (the side where the planetary balls 40 are not arranged in the axial direction) and outside the second carrier 62 (the side where the planetary balls 40 are not arranged in the axial direction). ), Disposed between the first carrier 61 and each planetary ball 40 or between the second carrier 62 and each planetary ball 40. Here, it is arranged outside the first carrier 61.
- the iris plate 70 is formed with a throttle portion 72 into which one protrusion of the support shaft 41 is inserted.
- the throttle portion 72 has a shape that shifts in the circumferential direction with respect to the radial direction from the radially inner side toward the radially outer side, and is referred to as a so-called throttle hole (iris hole) or throttle groove (iris groove). Is.
- iris hole throttle hole
- iris groove throttle groove
- the throttle hole is illustrated. Specifically, when it is assumed that the radial direction of the starting point of the radially inner end is the reference line L, the narrowed portion 72 moves away from the reference line L in the circumferential direction from the radially inner side toward the radially outer side. It is arcuate (FIG. 4).
- the throttle portion 72 has an intersection that intersects the first guide portion 63 when viewed in the axial direction, and holds one protrusion of the support shaft 41 at the intersection. The intersection moves in the radial direction as the iris plate 70 rotates.
- FIG. 4 shows the iris plate 70 viewed in the direction of arrow A in FIG.
- One protrusion of the support shaft 41 moves toward the center of the iris plate 70 along the diaphragm 72 when the iris plate 70 rotates in the clockwise direction in FIG.
- the respective protrusions of the support shaft 41 are inserted into the guide parts 63 and 64 of the first and second carriers 61 and 62, one protrusion inserted into the throttle part 72 has a diameter of Move inward direction.
- one of the protrusions moves to the outer peripheral side of the iris plate 70 along the diaphragm 72 when the iris plate 70 rotates counterclockwise in FIG. At this time, the one projecting portion moves outward in the radial direction by the action of the guide portions 63 and 64.
- the support shaft 41 can be moved in the radial direction by the guide portions 63 and 64 and the throttle portion 72. Therefore, the planetary ball 40 can be tilted as described above.
- the iris plate 70 when tilting in the deceleration direction, the iris plate 70 is rotated in the clockwise direction in FIG. 4, and when tilting in the speed increasing direction, the iris plate 70 is rotated in the counterclockwise direction in FIG. Rotate to
- the continuously variable transmission 1 is provided with a torque transmission unit 80 that rotates the first carrier 61 in conjunction with the rotation of the iris plate 70.
- the torque transmission unit 80 generates a transmission torque T according to the relative rotational speed V between the first carrier 61 and the iris plate 70.
- a rotational speed-sensitive coupling or fluid cup is used.
- a ring or the like may be used.
- the illustrated torque transmission unit 80 generates a transmission torque T as the iris plate 70 rotates, and transmits the transmission torque T to the first carrier 61, thereby rotating the first carrier 61.
- the first carrier 61 is rotated in the same circumferential direction as the iris plate 70.
- the torque transmission portion 80 is disposed between the first carrier 61 and the iris plate 70, but is preferably disposed so as not to protrude outward in the radial direction.
- the first carrier 61 and the iris plate 70 are disposed on the inner side in the radial direction than the support shafts 41.
- FIG. 5 is a view of the planetary ball 40 and the like viewed in the direction of arrow B in FIG. 1 and is a partial cross-sectional view taken along the second rotation center axis A2.
- spin moment a rotational moment centered on the center of gravity
- the planetary ball 40 is formed as shown in FIG. As shown in Fig. 5, the rotation axis shifts in the direction of the spin moment and tilts. In the skew state due to the rotational axis deviation, forces F3 and F4 corresponding to the tangential forces F1 and F2 act on the portions of the support shaft 41 located in the first and second guide portions 63 and 64. (Equations 1 and 2).
- the forces F3 and F4 can be said to be forces according to the input torque from the power source.
- the forces F3 and F4 are applied to the first and second guide portions 63 and 64 in the circumferential direction when the support shaft 41 is in contact with the wall surfaces of the first and second guide portions 63 and 64. It becomes.
- F3 (Lb1 / Lc1) * F1 (1)
- F4 (Lb2 / Lc2) * F2 (2)
- Lb1, Lb2, Lc1, and Lc2 represent distances when the planetary ball 40 is viewed in the direction of arrow B in FIG.
- “Lb1” is the distance from the center of gravity of the planetary ball 40 to one contact point (the contact point between the first rotating member 10 and the planetary ball 40).
- “Lb2” is the distance from the center of gravity of the planetary ball 40 to the other contact point (the contact point between the second rotating member 20 and the planetary ball 40).
- “Lc1” is the distance between the center of gravity of the planetary ball 40 and the point of action of the first guide portion 63 from the support shaft 41 (for example, the central portion of the support shaft 41 in the first guide portion 63).
- Lc2 is the distance between the center of gravity of the planetary ball 40 and the point of action of the second guide portion 64 from the support shaft 41 (for example, the central portion of the support shaft 41 in the second guide portion 64).
- a force F5 corresponding to the tangential force F1 (that is, the input torque of the power source) is applied to the portion of the support shaft 41 positioned in the throttle portion 72 (Equation 3).
- the force F ⁇ b> 5 becomes a pressing force in the circumferential direction with respect to the throttle portion 72 if the support shaft 41 is in contact with the wall surface of the throttle portion 72.
- “La” is the distance between the center of gravity of the planetary ball 40 and the operating point from the support shaft 41 in the throttle portion 72 (for example, the central portion of the support shaft 41 in the throttle portion 72).
- the torque transmission unit 80 is configured so that the absolute value of the transmission torque T is larger than the absolute value of the product Tc of the force F3 and the acting radius Rc (FIG. 2) of the force F3 shown in the following formula 4. Set the transfer characteristics.
- the action radius Rc changes according to the speed ratio ⁇ .
- the product Tc is the torque that acts on the first carrier 61 from the support shaft 41, and can be said to be the torque that acts on the first carrier 61 by the input torque from the power source.
- carrier torque Tc is referred to as “carrier torque Tc”.
- the carrier torque Tc Since the direction of the carrier torque Tc depends on the direction of the input torque from the power source, the carrier torque Tc is generated in the same direction regardless of whether the shift is on the deceleration side or on the acceleration side. In this example, it occurs in the same direction as the rotation direction of the iris plate 70 when shifting to the deceleration side.
- the direction of the transmission torque T of the torque transmission unit 80 is determined by the rotation direction of the iris plate 70. Therefore, the transmission torque T is generated in the same direction as the carrier torque Tc when shifting to the deceleration side, and is generated in the opposite direction to the carrier torque Tc when shifting to the acceleration side.
- the direction of the transmission torque T at the time of shifting to the deceleration side is referred to as a positive rotation direction
- the direction of the transmission torque T at the time of shifting to the speed increasing side is referred to as a negative rotation direction.
- the transmission torque T of the torque transmission unit 80 is set so that the absolute value of the transmission torque T is larger than the absolute value of the carrier torque Tc in all the input torques that can be assumed as actual traveling scenes. Thereby, this torque transmission part 80 can rotate the 1st carrier 61 with rotation of the iris plate 70, even if the input torque is the magnitude
- FIG. 6 shows an example of torque transmission characteristics of the torque transmission unit 80.
- the vertical axis represents the transmission torque T of the torque transmission unit 80
- the horizontal axis represents the relative rotational speed V of the iris plate 70 with respect to the first carrier 61.
- the torque transmission unit 80 has a transmission torque T of zero when the relative rotational speed V is zero.
- the right side of FIG. 6 shows the torque transmission characteristic at the time of forward rotation when changing the speed ratio ⁇ to the deceleration side
- the left side of FIG. 6 shows the time when the speed ratio ⁇ is changed to the speed increasing side. It is a torque transmission characteristic at the time of negative rotation.
- torque transmission characteristics are shown in which they are symmetrical.
- T1 and T2 in FIG. 6 indicate the transmission torque of the torque transmission unit 80 at the time of sudden acceleration and slow acceleration, respectively.
- Tc1 and Tc2 indicate carrier torques during sudden acceleration and slow acceleration, respectively.
- V1 and V2 indicate relative rotational speeds of the iris plate 70 with respect to the first carrier 61 at the time of sudden acceleration and slow acceleration, respectively. These are all during forward rotation.
- the negative rotation is represented by “ ⁇ T1”, “ ⁇ T2”, etc. in FIG.
- the transmission torque T in the same direction as the carrier torque Tc acts on the first carrier 61, and the first Since the carrier 61 is rotated in the same direction as the carrier torque Tc, the skew state of FIG. 5 can be easily created. This is because, in this case, as the first carrier 61 rotates, the drag from one wall surface in the width direction of the first guide portion 63 to the support shaft 41 decreases, and the skew state due to the spin moment on the wall surface This is because the generation of is difficult to be disturbed.
- a tangential force due to the resultant force Fa and force Fb acts on the surface of the planetary ball 40 in the skew state of FIG.
- the tangential force resulting from this resultant force is the rotational moment in the clockwise direction of the drawing in the upper planetary ball 40 in FIG. 1, and the radially inner side of the protrusions of the support shaft 41 on the first carrier 61 side and the iris plate 70 side
- the skew force toward the FIG. 7 shows the skew force Fs generated at the position of the distance Lc1 in the first carrier 61.
- the skew force Fs becomes a tilting force when shifting to the deceleration side.
- the first carrier 61 is also rotated in the same direction via the torque transmission unit 80 by rotating the iris plate 70 so as to shift to the deceleration side, and the skew state of FIG. Can be generated.
- the skew force Fs required for shifting to the deceleration side can be generated on the support shaft 41, and the planetary ball 40 can be tilted to the deceleration side.
- the required skew force (required skew force) Fs0 is determined from the viewpoint of the speed and efficiency of the tilting operation, and the necessary skew force. It is necessary to create a skew state (shift angle of the support shaft 41) required for generating Fs0.
- a gap CL (FIG. 2) in the direction is set.
- the clearance CL is set so that the relationship between the required skew amount and the maximum value Smax satisfies the following relational expression (5).
- the skew amount of the first guide portion 63 is the amount of movement of the support shaft 41 in the first guide portion 63 due to the occurrence of skew. For example, from the deviation angle of the support shaft 41 and the distance Lc1 described above. An approximate value can be estimated.
- the clearance CL between the second guide portion 64 and the support shaft 41 is also set to the same size.
- the iris plate 70 is rotated so that a force opposite to the force F3 or the force F5 is exerted.
- a transmission torque T opposite to the carrier torque Tc acts on the first carrier 61 through the torque transmission unit 80 as the iris plate 70 rotates.
- the absolute value of the transmission torque T is larger than the absolute value of the carrier torque Tc
- the first carrier 61 rotates in the direction opposite to the carrier torque Tc.
- the wall surface of the first guide portion 63 pushes the support shaft 41 in the direction opposite to the spin moment, so that the planetary ball 40 is in a skew state as shown in FIG. Is in the opposite skew state.
- the force Fa is a force that moves the upper planetary ball 40 in FIG. 1 in the counterclockwise direction of the drawing.
- the vector direction of the tangential force F2 on the output side is outward (the second carrier 62 side in FIG. 8) by the amount of the shift angle of the support shaft 41. Tilted.
- a part of the tangential force F2 is a force Fb that geometrically rotates the upper planetary ball 40 in FIG.
- FIG. 9 shows the skew force Fs generated at the position of the distance Lc1 in the first carrier 61.
- the skew force Fs becomes a tilting force when shifting to the speed increasing side.
- the first carrier 61 is also rotated in the same direction via the torque transmission unit 80 by rotating the iris plate 70 so as to shift to the speed increasing side, and is opposite to the speed reducing side.
- Generation of a skew state can be assisted.
- the skew force Fs required for shifting to the speed increasing side can be generated on the support shaft 41, and the planetary ball 40 can be tilted to the speed increasing side. It becomes possible.
- the elastic member 66 is disposed in each of the two gaps formed between the groove portion 65 of the first carrier 61 and the protruding portion 51 of the shaft 50. For this reason, a force due to the elastic force of the elastic member 66 also acts on the point of application of the force F3 in the first carrier 61. Therefore, especially during the shift to the speed increasing side, the force due to the elastic force hinders the rotation of the first carrier 61 until the planetary ball 40 is in the skew state of FIG. It may be difficult to rotate the first carrier 61 at 80. Therefore, in this continuously variable transmission 1, the characteristic (spring constant) of the elastic member 66 is set as shown in FIG.
- the elastic member 66 sets characteristics so that the torque transmission unit 80 can rotate the first carrier 61 even during slow acceleration when shifting to the speed increasing side. Specifically, since the torque transmission unit 80 at the time of slow acceleration generates the transmission torque T2, the load (T2 / Rsp) acting on the elastic member 66 at this time and the elastic member 66 in the gap are Based on the maximum displacement amount X0, the characteristics of the elastic member 66 are set so that the maximum displacement amount X0 is obtained with a load smaller than the load (T2 / Rsp) due to the transmission torque T2. “Rsp” is the working radius of the elastic member 66 (FIG. 2). As a result, in the continuously variable transmission 1, the first carrier 61 required for generating the skew state can be rotated by the transmission torque T of the torque transmission unit 80.
- the continuously variable transmission 1 includes the torque transmission unit 80 between the first carrier 61 and the iris plate 70, so that the continuously variable transmission 1 can move toward the deceleration side or the acceleration side even under various circumstances.
- a skew state of the planetary ball 40 suitable for shifting can be created.
- the first carrier 61 is rotated by the transmission torque T of the torque transmission unit 80 generated by the rotation of the iris plate 70. Therefore, in the continuously variable transmission 1, a dedicated drive source for rotating the first carrier 61 is unnecessary, and only a drive source (motor MG) for rotating the iris plate 70 is provided.
- the transmission can be made smaller than the conventional one that also has the motor for the first carrier 61, and the shift energy required for the shift can be reduced.
- the torque transmission unit 80 may be disposed in the original gap between the first carrier 61 and the iris plate 70, and even if the gap needs to be expanded, it is necessary to greatly expand the gap. Therefore, the torque transmission unit 80 can be arranged while suppressing an increase in the size of the transmission.
- the torque transmission part 80 of this illustration is set to the same torque transmission characteristic by positive rotation and negative rotation, you may set to the torque transmission characteristic different by positive rotation and negative rotation.
- the positive rotation transmission torque T in the same direction as the carrier torque Tc can be made smaller than that of the negative rotation.
Abstract
Description
本発明に係る無段変速機の実施例を図1から図10に基づいて説明する。
F4=(Lb2/Lc2)*F2 … (2)
10 第1回転部材(第1回転要素)
20 第2回転部材(第2回転要素)
30 サンローラ(第3回転要素)
40 遊星ボール(転動部材)
41 支持軸
50 シャフト(変速機軸)
51 突出部
61 第1キャリア(第1保持部材)
62 第2キャリア(第2保持部材)
63 第1ガイド部
64 第2ガイド部
65 溝部
66 弾性部材
70 アイリスプレート(傾転要素)
72 絞り部
80 トルク伝達部
MG モータ
Claims (2)
- 回転中心となる固定軸としての変速機軸と、
前記変速機軸上で対向させて配置した共通の第1回転中心軸を有する相対回転可能な第1及び第2の回転要素と、
前記第1回転中心軸と平行な第2回転中心軸を有し、該第1回転中心軸を中心にして放射状に複数配置して前記第1及び第2の回転要素に挟持させた転動部材と、
前記第2回転中心軸を有し、前記転動部材から両端を突出させた当該転動部材の支持軸と、
前記各転動部材を外周面上に配置し、前記変速機軸並びに前記第1及び第2の回転要素に対する相対回転が可能な第3回転要素と、
前記変速機軸に対して前記第1回転中心軸を中心とする相対回転ができるよう配置し、前記各支持軸の一方の突出部を径方向に案内する第1ガイド部の形成された第1保持部材と、
前記変速機軸に固定され、且つ、前記各支持軸の他方の突出部を径方向に案内する第2ガイド部の形成された第2保持部材と、
軸線方向に観たときに前記第1ガイド部と交差している交差点を有し、該交差点で前記支持軸の一方の突出部を保持する絞り部を備え、前記変速機軸に対して前記第1回転中心軸を中心に相対回転することで前記交差点を径方向に移動させる傾転要素と、
前記傾転要素を前記変速機軸に対して相対回転させるアクチュエータと、
前記第1保持部材と前記傾転要素との間の相対回転速度に応じた伝達トルクを当該第1保持部材と当該傾転要素との間に発生させるトルク伝達部と、
を備えたことを特徴とする無段変速機。 - 前記トルク伝達部は、入力トルクに応じた前記支持軸から前記第1保持部材への力と当該力の作用半径との積よりも大きい伝達トルクに設定したことを特徴とする請求項1記載の無段変速機。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/124,162 US20140200110A1 (en) | 2011-06-10 | 2011-06-10 | Continuously variable transmission |
CN201180071396.3A CN103582769B (zh) | 2011-06-10 | 2011-06-10 | 无级变速器 |
PCT/JP2011/063347 WO2012169057A1 (ja) | 2011-06-10 | 2011-06-10 | 無段変速機 |
JP2013519322A JP5601420B2 (ja) | 2011-06-10 | 2011-06-10 | 無段変速機 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2011/063347 WO2012169057A1 (ja) | 2011-06-10 | 2011-06-10 | 無段変速機 |
Publications (1)
Publication Number | Publication Date |
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WO2012169057A1 true WO2012169057A1 (ja) | 2012-12-13 |
Family
ID=47295659
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2011/063347 WO2012169057A1 (ja) | 2011-06-10 | 2011-06-10 | 無段変速機 |
Country Status (4)
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US (1) | US20140200110A1 (ja) |
JP (1) | JP5601420B2 (ja) |
CN (1) | CN103582769B (ja) |
WO (1) | WO2012169057A1 (ja) |
Cited By (1)
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---|---|---|---|---|
JP2015227689A (ja) * | 2014-05-30 | 2015-12-17 | トヨタ自動車株式会社 | 無段変速機 |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150038285A1 (en) * | 2012-02-24 | 2015-02-05 | Toyota Jidosha Kabushiki Kaisha | Continuously variable transmission |
US11021144B2 (en) * | 2018-09-20 | 2021-06-01 | Dana Automotive Systems Group, Llc | Slip detection and mitigation for an electric drive powertrain having a high ratio traction drive transmission |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS5235481U (ja) * | 1975-09-04 | 1977-03-12 |
Family Cites Families (9)
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JPS4929168U (ja) * | 1972-06-15 | 1974-03-13 | ||
JPS5756028B2 (ja) * | 1972-07-06 | 1982-11-27 | ||
US7166052B2 (en) * | 2003-08-11 | 2007-01-23 | Fallbrook Technologies Inc. | Continuously variable planetary gear set |
US20070155567A1 (en) * | 2005-11-22 | 2007-07-05 | Fallbrook Technologies Inc. | Continuously variable transmission |
EP1811202A1 (en) * | 2005-12-30 | 2007-07-25 | Fallbrook Technologies, Inc. | A continuously variable gear transmission |
CN103438207B (zh) * | 2007-02-16 | 2016-08-31 | 福博科技术公司 | 无限变速式无级变速器、无级变速器及其方法、组件、子组件和部件 |
JP5591686B2 (ja) * | 2007-04-24 | 2014-09-17 | フォールブルック インテレクチュアル プロパティー カンパニー エルエルシー | 電気牽引駆動装置 |
EP2171312B1 (en) * | 2007-07-05 | 2013-08-21 | Fallbrook Intellectual Property Company LLC | Method of controlling a continuously variable transmission |
JP5500118B2 (ja) * | 2011-04-18 | 2014-05-21 | トヨタ自動車株式会社 | 無段変速機 |
-
2011
- 2011-06-10 US US14/124,162 patent/US20140200110A1/en not_active Abandoned
- 2011-06-10 WO PCT/JP2011/063347 patent/WO2012169057A1/ja active Application Filing
- 2011-06-10 CN CN201180071396.3A patent/CN103582769B/zh not_active Expired - Fee Related
- 2011-06-10 JP JP2013519322A patent/JP5601420B2/ja not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS5235481U (ja) * | 1975-09-04 | 1977-03-12 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015227689A (ja) * | 2014-05-30 | 2015-12-17 | トヨタ自動車株式会社 | 無段変速機 |
Also Published As
Publication number | Publication date |
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CN103582769A (zh) | 2014-02-12 |
US20140200110A1 (en) | 2014-07-17 |
JPWO2012169057A1 (ja) | 2015-02-23 |
CN103582769B (zh) | 2016-05-11 |
JP5601420B2 (ja) | 2014-10-08 |
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