JP2011202701A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission capable of appropriately changing a transmission gear ratio.SOLUTION: The continuously variable transmission includes: a first rotation element 3 and a second rotation element 4; a third rotation element 5 brought into contact with and held between the first rotation element 3 and the second rotation element 4 at a position shifted from a gravity center; a fourth rotation element 6 disposed in contact with the third rotation element 5, relatively rotatable around a rotation center of a first rotation axis X1, and relatively movable in a direction of the first rotation axis X1; and a tilting part 9. The tilting part 9 further includes: a first tilting part 12 tilting the third rotation element 5 on one side; and a second tilting part 13 tilting the third rotation element 5 on a side opposite to one side, by using a force in the direction of the first rotation axis X1, which acts from the third rotation element 5 to the fourth rotation element 6, while the third rotation element 5 is rotated.

Description

  The present invention relates to a continuously variable transmission.

  As a conventional transmission of a so-called traction drive system, for example, Patent Document 1 discloses that a plurality of balls for transmitting power from a driving member to a driven member are 3 for each of the driving member, the driven member, and the support member. A transmission provided in point friction contact is disclosed. In this transmission, for example, one end of a rotating shaft of a ball supported by a pivot support is pulled by a spring or a string to tilt the rotating shaft of the ball, thereby changing a gear ratio.

JP-T-2001-521109

  Incidentally, in the transmission described in Patent Document 1 as described above, for example, for further improvement, it has been desired that the gear ratio is appropriately changed by a configuration different from the above.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a continuously variable transmission capable of appropriately changing a gear ratio.

  To achieve the above object, a continuously variable transmission according to the present invention includes a first rotating element and a second rotating element that face each other in a direction along a first rotation axis and are capable of relative rotation about the first rotation axis. The rotating element and the second rotating axis different from the first rotating axis can be rotated as a rotation center, and the first rotating element and the second rotating element are held in contact with each other at a position deviated from the center of gravity. A third rotating element capable of transmitting torque between the one rotating element and the second rotating element; and the third rotating element closer to the first rotating axis with respect to a direction orthogonal to the first rotating axis. , Provided in contact with the third rotating element, capable of relative rotation with respect to the first rotating element and the second rotating element about the first rotating axis and in a direction along the first rotating axis. A fourth rotational element movable relative to the third rotational element; A tilting part capable of tilting the rolling element, the tilting part having a first tilting part tilting the third rotating element to one side and a state in which the third rotating element is rotated. A second tilt that tilts the third rotating element to the opposite side from the one side by using a force in a direction along the first rotating axis that acts on the fourth rotating element from the third rotating element. It has a rolling part.

  Further, in the continuously variable transmission, the first tilting portion applies a pressing force for tilting the one rotation side to a support shaft that rotatably supports the third rotating element, and the second tilting portion. Can convert the force in the direction along the first rotation axis into a force that tilts to the opposite side and acts on the support shaft.

  Further, in the continuously variable transmission, the first tilting portion applies a pressing force that tilts the support shaft to the one side by an operation in which the aperture blade narrows the aperture opening formed in the aperture fixing ring member. Can be.

  In the continuously variable transmission, the second tilting portion has a proximal end portion fixed to one end portion of the support shaft and a distal end portion in a direction along the first rotation axis of the fourth rotating element. An arm portion that can come into contact with one end portion can be provided.

  In the continuously variable transmission, the fourth rotating element has a curved surface portion formed in a curved shape at the one end portion, and the arm portion contacts the curved surface portion at the tip portion. Thus, a rolling element capable of rolling can be provided.

  In the continuously variable transmission according to the present invention, the first tilting part tilts the third rotating element to one side, and the second tilting part acts on the fourth rotating element from the third rotating element. Since the third rotating element is tilted to the side opposite to the one side using the force in the direction along the direction, there is an effect that the gear ratio can be appropriately changed.

FIG. 1 is a schematic cross-sectional view of a continuously variable transmission according to an embodiment. FIG. 2 is a diagram illustrating an example of a relationship between a ball tilt angle and a gear ratio in the continuously variable transmission according to the embodiment. FIG. 3 is a view taken in the direction of the arrow L1 shown in FIG. 4 is a view taken in the direction of arrow L1 shown in FIG.

  Embodiments of a continuously variable transmission according to the present invention will be described below in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily replaced by those skilled in the art or those that are substantially the same.

[Embodiment]
FIG. 1 is a schematic cross-sectional view of a continuously variable transmission according to an embodiment. FIG. 2 is a diagram illustrating an example of a relationship between a ball tilt angle and a gear ratio in the continuously variable transmission according to the embodiment. 4 is a view taken in the direction of arrow L1 shown in FIG.

  A continuously variable transmission 1 according to this embodiment shown in FIG. 1 is mounted on a vehicle and transmits power (torque) generated by a power source such as an internal combustion engine to drive wheels of the vehicle. The continuously variable transmission 1 is a so-called traction drive type continuously variable transmission capable of transmitting power between the rotating elements by a fluid such as traction oil (transmitted oil) interposed between the rotating elements in contact with each other. The continuously variable transmission 1 uses a resistance force (a traction force, a shearing force of a traction oil film) generated when shearing traction oil interposed between contact surfaces of one rotating element and the other rotating element to generate power (torque). ).

  The continuously variable transmission 1 according to the present embodiment includes a shaft member 2 formed in a cylindrical shape or a columnar shape, and a plurality of rotating elements are assembled on the outer peripheral side of the shaft member 2. In the continuously variable transmission 1, the central axis of the shaft member 2 forms a rotation axis X1 as a first rotation axis.

  In the following description, unless otherwise specified, the direction along the rotational axis X1 of the continuously variable transmission 1 is referred to as the axial direction, and the direction orthogonal to the rotational axis X1, that is, the direction orthogonal to the axial direction is the diameter. The direction around the rotation axis X1 is referred to as the circumferential direction. Further, in the radial direction, the rotation axis X1 side is referred to as a radial inner side, and the opposite side is referred to as a radial outer side. Further, the continuously variable transmission 1 is configured to be substantially symmetric with respect to the rotation axis X1 as a central axis. Therefore, FIG. 1 illustrates only one side with the rotation axis X1 as a central axis. Unless otherwise noted, only one side will be described with the rotation axis X1 as the central axis, and the description on the other side will be omitted as much as possible.

  The continuously variable transmission 1 is a so-called ball planetary continuously variable transmission, and includes a first ring 3 as a first rotating element, a second ring 4 as a second rotating element, and a plurality of rotating elements, A planetary ball 5 as a three rotation element, a sun roller 6 as a fourth rotation element, and a carrier 7 as a fifth rotation element are provided. The continuously variable transmission 1 further includes a pressing portion 8 and a tilting portion 9.

  The first ring 3, the second ring 4, the sun roller 6, and the carrier 7 are assembled on the outer peripheral side of the shaft member 2, are arranged coaxially with each other about the rotation axis X 1, and are relatively rotatable with respect to each other. The planetary ball 5 can rotate (spin) about a rotation axis X2 as a second rotation axis different from the rotation axis X1. The planetary ball 5 is sandwiched between the first ring 3 and the second ring 4 with respect to the axial direction of the rotation axis X1 and is disposed in contact with the outer peripheral surface 6a of the sun roller 6 provided radially inside. The The planetary ball 5 is supported by the carrier 7, and as described below, if the carrier 7 is not to be fixed, the planetary ball 5 rotates with the carrier 7 and rotates around the rotation axis X1 (revolution). ) Can also be performed.

  In the continuously variable transmission 1, the pressing portion 8 presses at least one of the first ring 3 and the second ring 4 against the planetary ball 5, whereby the first ring 3, the second ring 4, the sun roller 6, and the carrier 7 An appropriate traction force (friction force) is generated between the planetary balls 5 and torque can be transmitted therebetween. Further, the continuously variable transmission 1 changes the gear ratio between input and output steplessly by operating the tilting portion 9 to tilt the rotation axis X2 with respect to the rotation axis X1 and tilting the planetary ball 5. be able to.

  In the continuously variable transmission 1, one of the first ring 3, the second ring 4, the sun roller 6, and the carrier 7 rotates in the circumferential direction about the rotation axis X <b> 1 with respect to the member such as the shaft member 2. The remaining portion can be rotated in the circumferential direction around the rotation axis X1. In the continuously variable transmission 1, torque is transmitted through the planetary ball 5 between the first ring 3, the second ring 4, the sun roller 6, and the carrier 7. For example, in the continuously variable transmission 1, one of the first ring 3, the second ring 4, the sun roller 6, and the carrier 7 serves as a torque (power) input member, and at least one of the remaining members serves as a torque output member. It becomes. In this continuously variable transmission 1, the ratio of the rotational speed (the number of rotations) between any rotating element serving as an input member and any rotating element serving as an output member is the gear ratio. In the following description, the continuously variable transmission 1 will be described by exemplifying a case where the first ring 3 is an input member, the second ring 4 is an output member, and the carrier 7 is a fixing target.

  In the continuously variable transmission 1, the rotation operation of each rotation element when torque is input to the rotation element as the input member is referred to as normal drive, and the rotation element as the output member is opposite to that during normal drive. The rotating operation of each rotating element when the direction torque is input is called reverse driving. For example, the continuously variable transmission 1 is positively driven when torque is input to the rotating element forming the input member from the power source side and rotating the rotating element, such as during acceleration of the vehicle. The reverse drive occurs when torque in the direction opposite to that in the forward drive is input to the rotary element that forms the output member from the drive wheel side, such as during deceleration, to rotate the rotary element.

  Specifically, both the first ring 3 and the second ring 4 have an annular plate shape with the rotation axis X1 as the center, and are disposed opposite to each other with respect to the axial direction of the rotation axis X1. The The first ring 3 and the second ring 4 are provided on the radially outer side of the shaft member 2, the sun roller 6, the planetary ball 5, and the like. The first ring 3 and the second ring 4 can be rotated relative to each other about the rotation axis X1. The first ring 3 and the second ring 4 are provided so as to sandwich the planetary ball 5 with respect to the axial direction of the rotation axis X1, and the planetary ball 5 is arranged according to a predetermined pressing force generated by the pressing portion 8. Can be pinched.

  Here, the first ring 3 is an input member, and for example, power (torque) generated by a power source is input via the input drum member 10 having a cylindrical shape centered on the rotation axis X1. The second ring 4 is an output member. For example, the motive power input to the first ring 3 through the output drum member 11 having a cylindrical shape centered on the rotation axis X1 and the like is shifted to the driving wheel side. Output toward. Here, the first ring 3, the second ring 4 and the output drum member 11 are arranged so as to be accommodated inside the input drum member 10.

  In the first ring 3 and the second ring 4, the contact surfaces 3 a and 4 a are in contact with the outer surface (outer peripheral curved surface) 5 a of each planetary ball 5 so that torque can be transmitted. The first ring 3 and the second ring 4 are in contact with the planetary ball 5 through the contact surfaces 3a and 4a at positions shifted from the center of gravity of the planetary ball 5 (offset positions). The contact surfaces 3a and 4a are provided on the side surfaces of the first ring 3 and the second ring 4 on the planetary ball 5 side, respectively. Here, the contact surface 3a and the contact surface 4a have the same distance L from the rotation axis X1 to the contact portion with the planetary ball 5 in a state where the rotation axis X2 is positioned parallel to the rotation axis X1. Further, the contact angle θ with respect to the planetary ball 5 is formed to be equal. Here, the contact angle θ is a reference line passing through the center of the planetary ball 5 and parallel to the radial direction, a line passing through the contact portion between the contact surfaces 3a, 4a and the outer surface 5a and the center of the planetary ball 5 (contact). It is an angle formed by the normal of the contact surface between the surfaces 3a, 4a and the outer surface 5a. The contact surfaces 3a and 4a are subjected to a radially inward and oblique force on the planetary ball 5 when an axial force is applied from the first ring 3 and the second ring 4 to the planetary ball 5. It is formed to join.

  The planetary ball 5 corresponds to a ball-type pinion in a so-called traction planetary gear mechanism, and can rotate around the rotation axis X2. The planetary ball 5 here is a sphere that can rotate around the rotation axis X2. A plurality of planetary balls 5 are provided radially along the circumferential direction of the rotation axis X1. Here, the planetary ball 5 is described as a sphere, however, for example, the planetary ball 5 may have a spherical shape at least in the rolling direction, for example, a rugby ball having an elliptical cross section. Each planetary ball 5 is rotatably supported by a support shaft 51 provided so as to penetrate the center. Each planetary ball 5 is rotatable around each support shaft 51. In each planetary ball 5, the center axis of each support shaft 51 forms a rotation axis X2.

  Each planetary ball 5 contacts the first ring 3 and the second ring 4 at a position shifted from the center of gravity as described above. Each planetary ball 5 is a transmission member capable of transmitting torque between the first ring 3 and the second ring 4. Here, each planetary ball 5 is also a rolling member that can roll on an outer peripheral surface 6a of a sun roller 6 described later. That is, each planetary ball 5 is in contact with the contact surfaces 3 a and 4 a that are the inner peripheral portions of the first ring 3 and the second ring 4 and also with the outer peripheral surface 6 a that is the outer peripheral portion of the sun roller 6. However, the rotation axis X2 can be rotated as the center of rotation.

  The sun roller 6 has a cylindrical shape centered on the rotation axis X1, and is closer to the rotation axis X1 than each planetary ball 5 in the direction orthogonal to the rotation axis X1, that is, the planetary ball 5 is in the radial direction. It is provided in contact with the planetary ball 5 on the inner side. The sun roller 6 is rotatably supported on the shaft member 2 on the inner peripheral surface side via a bearing or the like. The sun roller 6 can rotate relative to the first ring 3 and the second ring 4 with the rotation axis X1 as the rotation center. In the sun roller 6, the outer peripheral surface 6 a forms a rolling surface of the planetary ball 5. A plurality of planetary balls 5 are radially arranged on the outer peripheral surface 6a of the sun roller 6 at substantially equal intervals. The sun roller 6 can roll (rotate) each planetary ball 5 by its own rotation, or it can rotate along with the rolling (rotational) movement of each planetary ball 5.

  The carrier 7 supports the support shaft 51 of each planetary ball 5. In other words, the carrier 7 supports each planetary ball 5 via the support shaft 51 so as to be rotatable (spinning) around the rotation axis X <b> 2. The carrier 7 can rotate relative to the first ring 3, the second ring 4, and the sun roller 6 about the rotation axis X 1 as a rotation center. The carrier 7 includes a pair of disk members 71 and 72 having a disk shape with the rotation axis X1 as the center. The disk members 71 and 72 are provided so as to face each other with the planetary balls 5 and the sun rollers 6 sandwiched in the axial direction of the rotation axis X1. Here, in the carrier 7, the disk member 71 is provided on the first ring 3 side on the one axial side, and the disk member 72 is provided on the second ring 4 side on the other axial side. In the disk member 71 and the disk member 72, for example, a plurality of linear grooves (not shown) along the radial direction are formed corresponding to the support shafts 51 of the planetary balls 5. In the carrier 7, the axial end portions of the support shafts 51 are inserted into the groove portions of the disc member 71 and the disc member 72, and the disc member 71 connects one end portion of each support shaft 51 to the disc member 72. Supports the other end of each support shaft 51. Here, as described above, the carrier 7 is basically a fixed object.

  The pressing unit 8 applies a pressing force to the contact portion between the rotating elements. The pressing unit 8 presses the first ring 3 and the second ring 4 against each planetary ball 5 to generate a pressing force (clamping pressure) between the first ring 3 and the second ring 4 and each planetary ball 5. . The pressing portion 8 transmits torque to the contact portion between the rotating elements, that is, the contact portion between the contact surfaces 3a and 4a of the first ring 3 and the second ring 4 and the outer surface 5a of each planetary ball 5 by this pressing force. Appropriate traction force (friction force) is generated. Here, the pressing portion 8 exemplifies a configuration including the torque cam mechanisms 81 and 82, but is not limited to this, and a hydraulic pressure mechanism or an atmospheric pressure that generates a pressing force by using the pressure of liquid or gas. A pressing mechanism may be used.

  The torque cam mechanism 81 is provided between the first ring 3 and the annular plate-shaped annular end surface portion 10a of the input drum member 10 with respect to the axial direction of the rotational axis X1, and the torque cam mechanism 82 is disposed on the rotational axis X1. It is provided between the second ring 4 and the output drum member 11 with respect to the axial direction. When the torque cam mechanism 81 transmits torque between the first ring 3 and the input drum member 10, the first ring 3 and the input drum member 10 are relatively displaced according to the magnitude of the transmitted torque, Along with this relative displacement, a thrust toward each planetary ball 5 along the axial direction is generated with respect to the first ring 3 by the action of the cam surface and the cam member. Since the torque cam mechanism 82 has substantially the same configuration and operation as the torque cam mechanism 81, the description thereof is omitted here. As a result, the pressing unit 8 moves the first ring 3 and the planetary balls 5 and the second ring 4 and the planetary balls 5 relatively close to each other and presses them in accordance with the magnitude of the transmitted torque. A pressing force can be generated. As a result, the continuously variable transmission 1 has a transmission torque capacity corresponding to the pressing force generated by the pressing portion 8, and the planets between the first ring 3 and the second ring 4 according to the transmission torque capacity. Power (torque) can be transmitted to each other via the balls 5.

  Further, the pressing force by the pressing portion 8 is caused by the action according to the shape and positional relationship between the contact surfaces 3a and 4a of the first ring 3 and the second ring 4 and the outer surface 5a of each planetary ball 5. It is also transmitted to Sun Roller 6 via. As a result, the continuously variable transmission 1 generates an appropriate traction force (frictional force) also between each planetary ball 5 and the sun roller 6, and a mutual power ( Torque) can be transmitted.

  The tilting unit 9 tilts the rotation axis X2 to tilt the planetary ball 5 to thereby steplessly change the gear ratio in the continuously variable transmission 1, that is, the rotation speed ratio between the first ring 3 and the second ring 4. It can be changed to The tilting portion 9 tilts in a state where the rotation axis X2 of the planetary ball 5 is located in a plane including the rotation axis X1 and is parallel to the rotation axis X1 in that plane and is tilted from the parallel state. It is comprised so that it can be made to. The tilting part 9 tilts the support shaft 51 by applying a tilting force to the support shaft 51, that is, a tilting force, and thereby tilts the tilt angle of the rotation axis X2 with respect to the rotation axis X1. The rolling angle φ is changed, and the planetary ball 5 is tilted together with the support shaft 51. A specific configuration of the tilting portion 9 will be described in detail later.

  In the continuously variable transmission 1 configured as described above, for example, when torque is transmitted to the first ring 3, the pressing portion 8 rotates with the first ring 3, and the first ring 3, each planetary ball 5, During this time, a traction force (friction force) is generated between each planetary ball 5 and the second ring 4 and between each planetary ball 5 and the sun roller 6, and each planetary ball 5, the second ring 4, and the sun roller 6 are Start spinning. The continuously variable transmission 1 is configured such that the tilting portion 9 tilts each planetary ball 5 so that the contact radius r1 between the first ring 3 and each planetary ball 5, the second ring 4 and each planetary ball 5 By changing the ratio with the contact radius r2, the speed ratio, which is the rotational speed ratio between the input side and the output side, can be changed steplessly.

Here, the contact radii r1 and r2 (see FIG. 1) are the planets at the contact points where the contact surfaces 3a and 4a of the first ring 3 and the second ring 4 are in contact with the outer surface 5a of the planetary ball 5, respectively. This corresponds to the rotation radius of the ball 5, that is, the distance from the rotation axis X2 to the contact point. The contact radii r1 and r2 can be expressed by the following formulas (1) and (2), for example, using the planetary ball radius rb, the contact angle θ, and the tilt angle φ, respectively.

r1 = rb · sin [(π / 2) − (θ + φ)] = rb · cos (θ + φ) (1)

r2 = rb · sin [(π / 2) − (θ−φ)] = rb · cos (θ−φ) (2)

For example, the continuously variable transmission 1 has a contact radius when the rotation axis X2 is set parallel to the rotation axis X1, as illustrated by the rotation axis X2 ′ in FIG. 1, that is, when the tilt angle φ = 0. Since r1 and the contact radius r2 are substantially equal, the first ring 3 and the second ring 4 rotate at the same rotational speed, and thus the transmission ratio is 1. On the other hand, in the continuously variable transmission 1, when the tilting portion 9 operates and the rotation axis X2 is tilted with respect to the rotation axis X1 as illustrated in FIG. 1, the contact radius r1 relatively increases and the contact radius increases. r2 is relatively decreased, and the gear ratio is changed accordingly. In this case, the rotation speed of the first ring 3 is relatively increased, and the rotation speed of the second ring 4 is relatively reduced. In this way, in the continuously variable transmission 1, for example, as illustrated in FIG. 2, the gear ratio is continuously changed according to the tilt angle φ of the rotation axis X <b> 2 that is the center of rotation of the planetary ball 5. The speed ratio γ can be expressed by the following formula (3) using, for example, the rotational speed ω1 of the first ring 3, the rotational speed ω2 of the second ring 4, the contact angle θ, and the tilt angle φ.

γ = ω1 / ω2 = cos (θ + φ) / cos (θ−φ) (3)

  By the way, in the continuously variable transmission 1 of the present embodiment, as shown in FIG. 1, the tilting part 9 capable of tilting the planetary ball 5 has a throttle mechanism 12 and a second tilting part as a first tilting part. The transmission mechanism 13 is included, and the aperture ratio 12 and the transmission mechanism 13 appropriately change the gear ratio. The aperture mechanism 12 tilts the planetary ball 5 to one side. On the other hand, the transmission mechanism 13 uses the thrust force that is the axial force of the rotation axis X1 that acts on the sun roller 6 from the planetary ball 5 in a state in which the planetary ball 5 is rotated, so that the planetary ball 5 is opposite to the one side. It is intended to tilt.

  The sun roller 6 included in the continuously variable transmission 1 of the present embodiment is configured to be relatively movable in the axial direction of the rotation axis X1 with respect to a rotating element such as the planetary ball 5. The sun roller 6 is supported so that the inner peripheral surface side can be relatively rotated with respect to the shaft member 2 and can be relatively moved in the axial direction via a bearing or the like.

  Here, FIGS. 3 and 4 are L1 arrow views shown in FIG. 1, and are schematic diagrams when an eccentric load moment is generated in the planetary ball 5. Here, for example, FIG. 3 represents the forward drive, and FIG. 4 represents the reverse drive. For example, when the first ring 3 starts to rotate, the continuously variable transmission 1 has a tangential traction force (friction) in the same direction as the rotation direction of the first ring 3 at the contact portion of the planetary ball 5 with the first ring 3. Force) acts. At this time, the position of the contact portion of the planetary ball 5 with the first ring 3 is shifted from the center of gravity of the planetary ball 5 on the outer surface 5 a of the planetary ball 5. As a result, the traction force acting on the contact portion of the planetary ball 5 with the first ring 3 becomes an eccentric load on the planetary ball 5, and therefore when this traction force acts, the rotational moment centered on the center of gravity. (Hereinafter referred to as “eccentric load moment”) occurs in the planetary ball 5.

  Further, during the operation of the continuously variable transmission 1 (during power transmission), as shown in FIGS. 3 and 4, the contact portion of the planetary ball 5 with the first ring 3 and the contact portion of the second ring 4. On the other hand, traction force (friction force) in the opposite direction is constantly generated. For example, in the case of forward rotation with the first ring 3 as the input side and the second ring 4 as the output side, at the contact portion with the first ring 3, the tangential direction is the same as the rotation direction of the first ring 3. In the contact portion with the second ring 4, the traction force is a tangential direction opposite to the rotation direction of the second ring 4. As a result, an eccentric load moment about the center of gravity is generated in the planetary ball 5 due to the difference in direction of the traction force.

  Here, the continuously variable transmission 1 is provided with a gap (clearance) between members that are operated during the tilting operation, for example, in order to facilitate the tilting operation of the planetary ball 5. For example, the continuously variable transmission 1 has a gap between the support shaft 51 and the disk members 71 and 72 of the carrier 7 described above. As a result, when the eccentric load moment is generated, the planetary ball 5 is inclined in the direction of the eccentric load moment by an amount corresponding to the gap. That is, the direction of the eccentric load moment is not along the plane including the rotation axis line X1 and the rotation axis line X2 described above, so that the eccentric load moment acts to cause parallelism between the rotation axis line X1 and the rotation axis line X2. The state collapses and the rotation axis X2 deviates from the plane described above. Therefore, a skew occurs between the sun roller 6 and the planetary ball 5.

  As a result, the continuously variable transmission 1 has a thrust force corresponding to the eccentric load moment of the planetary ball 5, that is, a shift between the speed vector of the sun roller 6 and the speed vector of the planetary ball 5 as shown in FIGS. 3 and 4. A thrust force in the axial direction according to the above acts on the sun roller 6 from the planetary ball 5. At this time, the thrust force at the time of forward driving shown in FIG. 3 and the thrust force at the time of reverse driving shown in FIG. 4 act in opposite directions along the axial direction of the rotation axis X1. In the continuously variable transmission 1 of the present embodiment, the thrust force during forward driving shown in FIG. 3 acts from the second ring 4 side to the first ring 3 side, and the thrust force during reverse driving shown in FIG. It acts on the second ring 4 side from the first ring 3 side. The transmission mechanism 13 of this embodiment uses this thrust force to tilt the planetary ball 5 to the other side opposite to the tilting mechanism 12.

  Specifically, the aperture mechanism 12 tilts the planetary ball 5 to one side, here, clockwise in FIG. The aperture mechanism 12 tilts each planetary ball 5 to one side by applying a pressing force to each support shaft 51. The pressing force that the diaphragm mechanism 12 acts on each support shaft 51 is a pressing force that tilts the planetary ball 5 to one side. The aperture mechanism 12 here applies a pressing force simultaneously to the plurality of support shafts 51 to simultaneously tilt the plurality of planetary balls 5 to one side.

  The diaphragm mechanism 12 includes a diaphragm fixed ring member 12a, a diaphragm opening 12b, and diaphragm blades 12c. The diaphragm mechanism 12 applies a pressing force to each support shaft 51 by the diaphragm blades 12c narrowing the diaphragm opening 12b formed in the diaphragm fixed ring member 12a.

  The diaphragm fixed ring member 12a is shaped like an annular plate centering on the rotation axis X1. The diaphragm fixed ring member 12a is provided in the vicinity of the end on one side of each support shaft 51, here the end on the first ring 3 side, with respect to the axial direction of the rotation axis X1. The aperture ring member 12a is provided on the opposite side of each planetary ball 5 with the disc member 71 interposed therebetween with respect to the axial direction of the rotation axis X1. That is, each planetary ball 5, the diaphragm fixed ring member 12a, and the disk member 71 are sandwiched between each planetary ball 5 and the diaphragm fixed ring member 12a with respect to the axial direction of the rotation axis X1. They are arranged in such a positional relationship. The diaphragm fixed ring member 12 a is provided to be fixed to the shaft member 2.

  The aperture opening 12b is an aperture that penetrates the aperture fixing ring member 12a in the axial direction of the rotation axis X1. The diaphragm opening 12b is a circular opening centered on the rotation axis X1. The aperture opening 12b is inserted with an axial end on one side of each support shaft 51, that is, an axial end on the first ring 3 side.

  The diaphragm blades 12c are for opening and closing the diaphragm opening 12b, and a plurality of diaphragm blades are provided. Each diaphragm blade 12c is supported, for example, by a diaphragm fixed ring member 12a so as to be swingable about a swing shaft. For example, the rotatory power generated by a diaphragm driving device such as a motor (not shown) is converted into swing power by a link mechanism or the like and transmitted to the diaphragm blade 12c. The diaphragm blades 12c are oscillated to one side and transmitted into the diaphragm opening 12b when the oscillating power is transmitted, so that the diaphragm opening 12b is narrowed, that is, the diaphragm opening 12b is relatively small. be able to. Each diaphragm blade 12c is oscillated to the other side when the oscillating power is transmitted and retracted from the diaphragm opening 12b, so that the diaphragm opening 12b is opened, that is, the diaphragm opening 12b is relatively large. be able to.

  Therefore, for example, the diaphragm mechanism 12 is driven by the diaphragm drive device under the control of an electronic control unit (ECU), and the diaphragm blades 12c operate to narrow the diaphragm opening 12b by the generated power, so that each diaphragm blade 12c is operated. It can contact | abut to the axial direction edge part by the side of the 1st ring 3 of each support shaft 51, and can push this axial direction edge part toward the side which approaches the rotating shaft X1. The aperture mechanism 12 applies a pressing force directed toward the axis approaching the rotation axis X1 to the axial end of each support shaft 51, so that the radial position of the end on the one axial side of each support shaft 51 The radial position of the end portion on the other side in the axial direction can be shifted, and accordingly, each planetary ball 5 can be tilted to one side, here the clockwise side in FIG. The tilt angle φ can be changed. The tilt angle φ of the tilt of each planetary ball 5 toward one side, in other words, the gear ratio, is determined according to the amount of advance of the aperture blade 12c into the aperture opening 12b.

  The transmission mechanism 13 uses the thrust force acting on the sun roller 6 to tilt the planetary ball 5 to the other side, here, counterclockwise in FIG. The transmission mechanism 13 transmits each thrust force to each support shaft 51 to tilt each planetary ball 5 to the other side. Furthermore, the transmission mechanism 13 converts the axial thrust force of the rotation axis X1 acting on the sun roller 6 into a tilting force, and causes the tilting force to act on each support shaft 51. The tilting force that the transmission mechanism 13 acts on each support shaft 51 is a force that tilts the planetary ball 5 to the other side.

  The transmission mechanism 13 includes an arm portion 13a. The transmission mechanism 13 converts the thrust force acting on the sun roller 6 to the tilting force by the arm portion 13 a and acts on each support shaft 51.

  The arm portion 13 a is a linear member provided on each support shaft 51. The arm portion 13 a has a proximal end portion fixed to one end portion of the support shaft 51 and a distal end portion capable of contacting the axial end portion 61 of the sun roller 6. Here, the axial end 61 is the end of the sun roller 6 on the first ring 3 side (right side in the figure). That is, here, the arm portion 13 a is provided on the first ring 3 side (right side in the figure) of the sun roller 6, and the base end portion is fixed to the axial end portion of each support shaft 51 on the first ring 3 side. The arm portion 13 a extends from the axial end portion side of the support shaft 51 on the first ring 3 side toward the axial end portion 61 side of the sun roller 6.

  Therefore, for example, as shown in FIG. 1, in the transmission mechanism 13, the thrust force from the planetary ball 5 to the sun roller 6 acts on the first ring 3 side during the positive drive, and the sun roller 6 is in one axial direction, that is, the first roller When moved to the 1 ring 3 side, the distal end portion of each arm portion 13 a comes into contact with the axial end portion 61 of the sun roller 6. In the transmission mechanism 13, the tip of each arm portion 13 a and the axial end portion 61 of the sun roller 6 come into contact with each other, so that the thrust force of the sun roller 6 passes through each arm portion 13 a to the first ring of each support shaft 51. It is transmitted as a tilting force to the axial end on the third side. That is, the transmission mechanism 13 can convert the thrust force acting on the sun roller 6 into a tilting force, and can apply the tilting force to each support shaft 51. In the transmission mechanism 13, each arm portion 13 a comes into contact with the axial end portion 61 of the sun roller 6, and each arm portion 13 a is pushed by the thrust force acting on the sun roller 6. A tilting force can be applied to the shaft 51 to push up the axial end of each support shaft 51 on the first ring 3 side toward the side away from the rotation axis X1.

  The transmission mechanism 13 uses the thrust force acting on the sun roller 6 in this way to apply a tilting force toward the side away from the rotation axis X1 to the axial end of each support shaft 51 on the first ring 3 side. Let As a result, the transmission mechanism 13 moves to the side where the diaphragm blades 12c open the diaphragm opening 12b, so that the radial position of the end portion on the one axial side of each support shaft 51 and the end on the other axial side. Accordingly, each planetary ball 5 can be tilted to the other side, in this case, counterclockwise in FIG. 1, and the tilt angle φ can be adjusted accordingly. Can be changed.

  Further, since the transmission mechanism 13 is configured as described above, when each planetary ball 5 tilts to one side as the diaphragm blades 12c move to the side narrowing the diaphragm opening 12b, With this tilting operation, the arm portion 13a can push the sun roller 6 toward the second ring 4 side. That is, in this case, the transmission mechanism 13 also functions as a conversion unit that converts a pressing force that tilts the planetary ball 5 into a force that presses the sun roller 6 toward the other side in the axial direction of the rotation axis X1. In the transmission mechanism 13, a part of the pressing force applied from the aperture mechanism 12 to the support shaft 51 is used to move the sun roller 6 to the other side in the axial direction at the contact portion between the distal end portion of the arm portion 13 a and the axial end portion 61 of the sun roller 6. It can act as a pushing force to the side. In this case, regardless of the magnitude and direction of the thrust force acting on the sun roller 6, the transmission mechanism 13 causes the sun roller 6 to move to the other side in the axial direction of the rotation axis X1, that is, the first It can be moved by pushing to the 2 ring 4 side.

  In the continuously variable transmission 1, a thrust force from the planetary ball 5 to the sun roller 6 acts on the second ring 4 side during reverse driving, and the sun roller 6 moves to the other axial side, that is, the second ring 4 side. Then, a stopper (not shown) comes into contact with the axial end portion 62 of the sun roller 6 at a predetermined position, so that the axial movement of the sun roller 6 is restricted. The axial end 62 is the end of the sun roller 6 on the second ring 4 side (left side in the figure). In this case, the transmission mechanism 13 is in a state where the contact between each arm portion 13a and the end portion 61 in the axial direction of the sun roller 6 is released. In this case, in the continuously variable transmission 1, each planetary ball 5 does not tilt to the other side, and therefore, no shifting is performed as the planetary ball 5 tilts to the other side.

  Here, the sun roller 6 has a curved surface portion 63 formed in a curved surface at an axial end portion 61 that is one end portion in the axial direction of the rotation axis X1. The curved surface portion 63 has a curved shape so that the central portion of the wall surface of the axial end portion 61 protrudes toward the arm portion 13a along the axial direction of the rotation axis X1. The arm portion 13a is provided with a roller 13b as a rolling element capable of rolling while contacting the curved surface portion 63 at the tip portion. As a result, in the transmission mechanism 13, when the sun roller 6 pushes the arm portion 13a to one side in the axial direction of the rotation axis X1, or as the planetary ball 5 tilts, the arm portion 13a pushes the sun roller 6 in the axial direction of the rotation axis X1. When the roller 13b is guided by the curved surface portion 63 when being pushed to the other side, the sliding resistance between the distal end portion of the arm portion 13a and the axial end portion 61 can be reduced. That is, the transmission mechanism 13 rotates while the roller 13b contacts the curved surface portion 63 when the axial end portion 61 pushes the tip end portion of the arm portion 13a or when the tip end portion of the arm portion 13a pushes the axial end portion 61. By moving, the sliding resistance between the distal end portion of the arm portion 13a and the axial end portion 61 can be reduced, and the sun roller 6 smoothly moves the arm portion 13a or the arm portion 13a smoothly and efficiently the sun roller 6. Can be pressed.

  The continuously variable transmission 1 configured as described above uses the throttle mechanism 12 for tilting the planetary ball 5 to one side and the thrust force acting on the sun roller 6 to tilt the planetary ball 5 to the other side. By operating the transmission mechanism 13, the gear ratio can be changed steplessly.

  The continuously variable transmission 1 does not include, for example, a pivot support for supporting and tilting the planetary ball 5 or a spring or string assembled to the planetary ball 5 by the operation of the throttle mechanism 12 and the transmission mechanism 13. The gear ratio can be changed. As a result, the continuously variable transmission 1 compares the number of planetary balls 5 that can be provided relative to the outer peripheral surface 6a of the sun roller 6 having the same outer diameter as compared with the case where the pivot support is provided. Can be much more. As a result, the continuously variable transmission 1 can relatively reduce the surface pressure acting on each planetary ball 5 when transmitting torque via the plurality of planetary balls 5, and thus durability is improved. Can be improved. In other words, the continuously variable transmission 1 can suppress an increase in the size of the device when the same number of planetary balls 5 are provided as compared with the case where the pivot support is provided. That is, the continuously variable transmission 1 can achieve both suppression of the increase in size of the device and improvement in durability. Furthermore, the continuously variable transmission 1 can achieve both suppression of an increase in the size of the device and an increase in allowable torque capacity.

  Further, the continuously variable transmission 1 uses the thrust force that the transmission mechanism 13 acts on the sun roller 6 to tilt each planetary ball 5 to the other side, so that, for example, the diaphragm blades 12c open the diaphragm opening 12b. Accordingly, it is not necessary to provide an elastic body such as a return spring because each planetary ball 5 is pushed back and tilted to the other side in accordance with the movement to the moving side. For this reason, the continuously variable transmission 1 can suppress an increase in the size of the device.

  Further, since the continuously variable transmission 1 can change the gear ratio by the operation of the throttle mechanism 12 and the transmission mechanism 13, for example, the carrier 7 is used to tilt each planetary ball 5 together with each support shaft 51. It is not necessary to relatively displace (rotate) the pair of disk members 71 and 72 constituting the. Therefore, the carrier 7 can be configured to have a bowl shape as a whole by connecting the disk member 71 and the disk member 72 with a plurality of connecting shafts (not shown). Thereby, the continuously variable transmission 1 can increase the rigidity of the carrier 7 that supports the support shaft 51. For example, even when a large load is applied, the rotation axis X2 of the planetary ball 5 is prevented from being displaced. As a result, the power transmission efficiency can be prevented from deteriorating due to the deviation in the rotation axis X2.

  In the continuously variable transmission 1, a thrust force acts on the sun roller 6 from each planetary ball 5, and the sun roller 6 moves in the axial direction of the rotation axis X 1, whereby the sun roller 6 contacts the planetary ball 5. The position can be changed. At this time, if the continuously variable transmission 1 is in the positive drive, the tilt angle φ is changed, that is, the speed ratio is changed, so that the arm portion 13a and the axial end portion 61 are changed. The axial contact position is also changed, and the axial position of the sun roller 6 is also changed. As a result, the continuously variable transmission 1 can change the contact position of the sun roller 6 with each planetary ball 5 in accordance with the tilt angle φ, in other words, the gear ratio in the forward drive. Wear can be suppressed, and thus durability can be improved.

  In the continuously variable transmission 1, the direction of the thrust force acting on the sun roller 6 is reversed between when the driving state is the normal driving state and when the driving state is the reverse driving state, and the moving direction of the sun roller 6 is reversed. . For this reason, the continuously variable transmission 1 has the same tilt angle φ, that is, the same gear ratio, each in the sun roller 6 in the forward drive state and in the reverse drive state. The contact position with the planetary ball 5 can be changed. As a result, the continuously variable transmission 1 can prevent the contact position of the sun roller 6 with each planetary ball 5 from being uniquely determined according to the tilt angle φ, that is, according to the gear ratio. In this respect, the durability can be further improved.

  According to the continuously variable transmission 1 according to the embodiment described above, the first ring 3 and the second ring 4 that face each other in the direction along the rotation axis X1 and are relatively rotatable around the rotation axis X1. The first ring 3 and the second ring 4 can be rotated about a rotation axis X2 different from the rotation axis X1 and are held in contact with the first ring 3 and the second ring 4 at positions shifted from the center of gravity. A planetary ball 5 capable of transmitting torque between the planetary ball 5 and the planetary ball 5 on the side of the rotation axis X1 with respect to the direction orthogonal to the rotation axis X1. A sun roller 6 that can rotate relative to the second ring 4 about the rotation axis X1 and can move relative to the direction along the rotation axis X1 and a tilting portion 9 that can tilt the planetary ball 5 are provided. The tilting part 9 is A throttle mechanism 12 for tilting the star ball 5 to one side and the planetary ball 5 using the force in the direction along the rotation axis X1 acting on the sun roller 6 from the planetary ball 5 while the planetary ball 5 is rotated. It has a transmission mechanism 13 that tilts to the opposite side to the one side. Therefore, the continuously variable transmission 1 can appropriately change the gear ratio by the operation of the aperture mechanism 12 and the transmission mechanism 13.

  The continuously variable transmission according to the above-described embodiment of the present invention is not limited to the above-described embodiment, and various modifications can be made within the scope described in the claims.

  In the above description, the first tilting portion has been described as being the diaphragm mechanism 12, but this is not restrictive, and any force may be applied to the support shaft to tilt the third rotating element to one side. That's fine.

  As described above, the continuously variable transmission according to the present invention is suitable for application to various continuously variable transmissions used in vehicles and the like.

1 continuously variable transmission 2 shaft member 3 first ring (first rotating element)
4 Second ring (second rotating element)
5 Planetary ball (third rotating element)
6 Sun Roller (4th rotating element)
7 Carrier 8 Pressing part 9 Tilt part 12 Drawing mechanism (first tilt part)
12a Diaphragm fixed ring member 12b Diaphragm opening 12c Diaphragm blade 13 Transmission mechanism (second tilting part)
13a Arm part 13b Roller (rolling element)
51 Support shafts 61, 62 Axial end 63 Curved surface X1 Rotation axis (first rotation axis)
X2 axis of rotation (second axis of rotation)

Claims (5)

A first rotation element and a second rotation element that face each other in a direction along the first rotation axis and are relatively rotatable with the first rotation axis as a rotation center;
The first rotation element can be rotated around a second rotation axis different from the first rotation axis, and is held in contact with and sandwiched between the first rotation element and the second rotation element at a position deviating from the center of gravity. A third rotating element capable of transmitting torque to and from the second rotating element;
The first rotation element and the second rotation element are provided in contact with the third rotation element on the first rotation axis side from the third rotation element with respect to a direction orthogonal to the first rotation axis. A fourth rotation element that is relatively rotatable about the first rotation axis as a rotation center and relatively movable in a direction along the first rotation axis;
A tilting part capable of tilting the third rotating element;
The tilting part acts on the fourth rotating element from the third rotating element in a state in which the first rotating part tilts the third rotating element to one side and the third rotating element rotates. A second tilting portion that tilts the third rotating element to the opposite side to the one side by using a force in a direction along the first rotation axis;
Continuously variable transmission. The first tilting portion causes a pressing force to tilt to the one side to a support shaft that rotatably supports the third rotating element,
The second tilting portion converts a force in a direction along the first rotation axis into a force tilting to the opposite side and acts on the support shaft.
The continuously variable transmission according to claim 1. The first tilting portion applies a pressing force for tilting the support shaft to the one side by an operation in which the diaphragm blades narrow the diaphragm opening formed in the diaphragm fixed ring member.
The continuously variable transmission according to claim 2. The second tilting portion has a proximal end portion fixed to one end portion of the support shaft, and a distal end portion capable of coming into contact with one end portion in the direction along the first rotation axis of the fourth rotating element. Having an arm part,
The continuously variable transmission according to claim 2 or claim 3. The fourth rotating element has a curved surface formed in a curved shape at the one end,
The arm part is provided at the tip part with a rolling element capable of rolling in contact with the curved surface part.
The continuously variable transmission according to claim 4.

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