JP2015140831A - One-way clutch and crank-type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a side face of a cage from being bitten by an outer peripheral portion of an end face of a roller biased in the axial direction by an axial spring.SOLUTION: As a frictional force acting on a first end face 25a of a roller 25, and frictional force acting on a second end face 25b of the roller 25 are agreed with each other, inclination due to unbalance of the frictional forces of the first and second end faces 25a, 25b is suppressed in moving the roller 25 from a datum point to an engage point, abrasion of the first and second end faces 25a, 25b of the inclined roller 25 due to contact with a first side face 36a and a second side face 36c of an inner ring 36 is prevented, and engagement responsiveness of a one-way clutch 21 can be improved by smoothly engaging the roller 25 with an outer peripheral face 23a of an inner member 23 and an inner peripheral face 22a of an outer member 22.

Description

  In the present invention, a plurality of rollers held in a cage disposed between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member are urged in the circumferential direction by an engagement spring, and the inner member and the outer member are moved in one direction. The present invention relates to a one-way clutch that transmits a driving force by engaging the roller between the outer peripheral surface and the inner peripheral surface by relative rotation, and a crank type continuously variable transmission including the one-way clutch.

  The engagement spring that urges the roller of the one-way clutch in the circumferential direction is composed of a coil spring, and the cage that holds the roller is provided with a protruding portion that restricts the axial displacement of the coil spring, thereby stabilizing the posture of the coil spring. Patent Document 1 below discloses that the roller is prevented from being caught between the inner ring and the outer ring in a tilted state.

Japanese Patent No. 3903157

  By the way, when a leaf spring is used as an engagement spring that urges the roller in the circumferential direction, the structure of Patent Document 1 that requires a coil spring cannot be adopted, so the first end face of the roller is attached to the axial spring. It is conceivable to prevent the tilt by pressing the second end surface of the roller against the side surface of the cage by biasing in the axial direction.

  However, even if an axial spring is provided to prevent the roller from tilting, if the roller tilts slightly while moving from the damping point to the daytime point, the outer peripheral portion of the second end surface of the roller will be caught on the side surface of the cage. As a result, the roller may tilt at the daytime point, preventing smooth engagement of the one-way clutch, or the outer peripheral portion of the second end surface of the roller may rub against the side surface of the cage and cause wear.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to prevent the outer peripheral portion of the end surface of the roller urged in the axial direction by an axial spring from being caught in the side surface of the cage.

  In order to achieve the above object, according to the first aspect of the present invention, a plurality of rollers held in a cage disposed between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member are circumferentially engaged with an engagement spring. The roller is energized to transmit the driving force by engaging the roller between the outer peripheral surface and the inner peripheral surface by relative rotation in one direction of the inner member and the outer member, and the cage is connected to the roller of the roller. A first side surface and a second side surface opposed to the first end surface and the second end surface, respectively, and an axial spring provided on the first side surface biases the first end surface in the axial direction so that the second end surface is A one-way clutch that regulates the posture of the roller by abutting against a side surface, wherein a frictional force that acts on the first end surface is matched with a frictional force that acts on the second end surface. The one-way clutch is proposed, characterized in that.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, an urging member is supported on the first side surface so as to be axially movable, and the urging member is supported by the axial spring. A biasing portion that urges in the axial direction toward one end surface and that the second end surface abuts on the second side surface is formed, and a roller abutting surface of the urging member and a roller abutting surface of the convex portion Are made to have the same shape and are coaxially opposed on both sides in the axial direction of the roller, so that the frictional force acting between the first end surface and the biasing member acts between the second end surface and the convex portion. A one-way clutch characterized by matching the frictional force is proposed.

  According to the invention described in claim 3, in addition to the structure of claim 2, the roller is a standby position immediately before the roller is engaged between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member. A one-way clutch is proposed in which the outer peripheral portion of the roller contact surface of the urging member and the convex portion is inside the outer peripheral portion of the first and second end surfaces when at the tom point. .

  According to a fourth aspect of the present invention, there is provided a crank type continuously variable transmission including the one-way clutch according to any one of the first to third aspects, wherein the inner member of the one-way clutch is The power transmission unit that shifts the rotation of the input shaft connected to the drive source and transmits the rotation to the output shaft is fixed to the outer periphery of the output shaft, and the power transmission unit has an eccentric amount from the axis of the input shaft. An input side fulcrum that is variable and rotates together with the input shaft, an output side fulcrum provided on the outer member of the one-way clutch, and a connecting rod that connects the input side fulcrum and the output side fulcrum. A crank type continuously variable transmission is proposed.

  The eccentric disk 18 of the embodiment corresponds to the input side fulcrum of the present invention, the pin 19c of the embodiment corresponds to the output side fulcrum of the present invention, and the engine E of the embodiment serves as the drive source of the present invention. Correspondingly, the first contact surface P1 of the embodiment corresponds to the roller contact surface of the biasing member of the present invention, and the second contact surface P2 of the embodiment is the roller contact surface of the convex portion of the present invention. Corresponding to

  According to the configuration of claim 1, the one-way clutch urges a plurality of rollers held in a cage disposed between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member in the circumferential direction by the engagement spring, The roller is engaged between the outer peripheral surface and the inner peripheral surface by relative rotation in one direction of the outer member to transmit the driving force. The cage includes a first side surface and a second side surface opposed to the first end surface and the second end surface of the roller, respectively, and an axial spring provided on the first side surface biases the first end surface in the axial direction so that the second end surface is The posture of the roller is regulated by contacting the two side surfaces.

  Since the frictional force acting on the first end surface of the roller is matched with the frictional force acting on the second end surface of the roller, the first and second end surfaces are moved when the roller moves from the daytime point toward the engagement point. The frictional force of the roller is prevented from being tilted, and the outer peripheral portions of the first and second end surfaces of the tilted roller are prevented from coming into contact with the first side surface and the second side surface of the cage and worn. The engagement response of the one-way clutch can be enhanced by smoothly engaging between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member.

  According to the second aspect of the present invention, the biasing member is supported on the first side surface so as to be movable in the axial direction, the biasing member is biased in the axial direction toward the first end surface by the axial spring, and the second side surface is supported. Forming a convex portion with which the second end surface abuts, the roller abutting surface of the urging member and the roller abutting surface of the convex portion having the same shape, and being coaxially opposed on both sides in the axial direction of the roller, Since the frictional force acting between the first end face and the biasing member is matched with the frictional force acting between the second end face and the convex portion, the biasing function of the roller and the frictional force adjusting function on the biasing member In addition, the frictional forces of the first and second end faces of the roller can be balanced accurately.

  According to the third aspect of the invention, when the roller is at the daytime point, the outer peripheral portion of the roller contact surface of the urging member and the convex portion is inside the outer peripheral portion of the first and second end surfaces. The outer peripheral portions of the first and second end surfaces are attached when the roller moves from the datum point, which is a standby position immediately before being engaged between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member, toward the engagement point. It is possible to more reliably prevent the roller from being tilted by being caught on the roller contact surface of the biasing member or the roller contact surface of the convex portion.

  According to the fourth aspect of the present invention, the inner member of the one-way clutch is fixed to the outer periphery of the output shaft of the power transmission unit that shifts the rotation of the input shaft connected to the drive source and transmits it to the output shaft. The transmission unit has a variable amount of eccentricity from the axis of the input shaft and connects the input fulcrum that rotates with the input shaft, the output fulcrum provided on the outer member of the one-way clutch, the input fulcrum and the output fulcrum Therefore, when the input shaft rotates and the connecting rod reciprocates, the one-way clutch is intermittently engaged and the output shaft rotates intermittently to transmit the driving force. At this time, since the one-way clutch repeatedly engages and disengages at short time intervals, the effects of the inventions of claims 1 to 4 are more effectively exhibited and the performance of the power transmission unit is improved.

The skeleton figure of the power transmission device for vehicles. FIG. 2 is a detailed view of part 2 of FIG. 1. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2 (OD state). FIG. 3 is a cross-sectional view taken along line 3-3 in FIG. 2 (GN state). The action explanatory view in OD state. The operation explanatory view in the GN state. The disassembled perspective view of a one-way clutch. The partial perspective view of the inner ring | wheel of an angular ball bearing. FIG. 9 is an enlarged view of a portion 9 in FIG. FIG. 10 is an enlarged view of 10 parts in FIG. 9. FIG. 11 is a sectional view taken along line 11-11 in FIG. 9; FIG. 12 is a sectional view taken along line 12-12 of FIG. 10;

  Hereinafter, embodiments of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 to 3, the vehicle power transmission device for transmitting the driving force of the engine E to the drive wheels W, W via the left and right axles 10, 10 is a crank type continuously variable transmission T and a differential. Gear D is provided. The continuously variable transmission T of the present embodiment is obtained by superimposing a plurality (four in the embodiment) of power transmission units U having the same structure in the axial direction, and these power transmission units U are parallel. Are provided with a common input shaft 11 and a common output shaft 12, and the rotation of the input shaft 11 is decelerated or increased and transmitted to the output shaft 12.

  Next, the structure of the continuously variable transmission T will be described with reference to FIGS.

  First, the structure of one power transmission unit U will be described as a representative. The input shaft 11 connected to the engine E and rotates passes through the hollow rotating shaft 14a of the speed change actuator 14 such as an electric motor so as to be relatively rotatable. The rotor 14b of the speed change actuator 14 is fixed to the rotating shaft 14a, and the stator 14c is fixed to the casing. The rotation shaft 14 a of the speed change actuator 14 can rotate at the same speed as the input shaft 11 and can rotate relative to the input shaft 11 at a different speed.

  A first pinion 15 is fixed to the input shaft 11 passing through the rotation shaft 14 a of the speed change actuator 14, and a crank-shaped carrier 16 is connected to the rotation shaft 14 a of the speed change actuator 14 so as to straddle the first pinion 15. The Two second pinions 17, 17 having the same diameter as the first pinion 15 are supported via pinion pins 16 a, 16 a at positions forming an equilateral triangle in cooperation with the first pinion 15, respectively. The first pinion 15 and the second pinions 17, 17 mesh with a ring gear 18 a formed eccentrically inside a disc-shaped eccentric disk 18. A ring portion 19 b provided at one end of the rod portion 19 a of the connecting rod 19 is fitted to the outer peripheral surface of the eccentric disk 18 via a ball bearing 20 so as to be relatively rotatable.

  A one-way clutch 21 provided on the outer periphery of the output shaft 12 is arranged inside the outer member 22 with a ring-shaped outer member 22 pivotally supported by a rod portion 19a of a connecting rod 19 via a pin 19c. 12, and an inner member 23 fixed to 12 and rollers 25 arranged in a wedge-shaped space formed between the outer member 22 and the inner member 23 and urged by engagement springs 24. The specific structure of the one-way clutch 21 will be described in detail later.

  As is clear from FIG. 2, the four power transmission units U... Share the crank-shaped carrier 16, but the phase of the eccentric disk 18 supported by the carrier 16 via the second pinions 17 and 17 is the same. Each power transmission unit U differs by 90 °. For example, in FIG. 2, the eccentric disk 18 of the leftmost power transmission unit U is displaced upward in the figure with respect to the input shaft 11, and the eccentric disk 18 of the third power transmission unit U from the left is relative to the input shaft 11. The eccentric discs 18 and 18 of the second and fourth power transmission units U and U from the left are located in the middle in the vertical direction.

  Next, the structure of the one-way clutch 21 will be described with reference to FIGS. 3 to 6, the one-way clutch 21 is schematically shown, and the actual structure is shown in FIGS.

  The one-way clutch 21 according to the present embodiment basically includes twelve rollers 25 between a circular inner peripheral surface 22a of an annular outer member 22 and an outer peripheral surface 23a bent in a wave shape of a cylindrical inner member 23. The connecting rod 19 is connected to the projecting portions 22b, 22b provided on the outer periphery of the outer member 22 via the pins 19c and the clips 40, 40, and the output shaft 12 is connected to the inner peripheral portion of the inner member 23. Are coupled so that they cannot rotate relative to each other.

  The one-way clutch 21 includes a cage 31 for supporting the engagement springs 24 that urge the rollers 25 in the circumferential direction. The cage 31 includes a pair of inner rings 36 and 36 of angular ball bearings 34 and 34, which will be described later, and twelve spring support rods 33 that are arranged at equal intervals in the circumferential direction and connect the pair of inner rings 36 and 36 to each other. The pair of inner rings 36 are arranged on both sides in the axial direction of the twelve rollers 25. The twelve spring support rods 33 are arranged between the twelve rollers 25. The cage 31 is coupled to the inner member 23 in a relatively non-rotatable manner by press-fitting the inner circumferential portions of the inner rings 36, 36 into the outer circumferential surface 23 a of the inner member 23.

  The engagement spring 24 is formed by bending a single elastic plate with an S-shaped cross section, one end of which is fixed to the spring support rod 33 of the cage 31 by welding or the like, and the other end is in contact with the roller 25 to be elastic. A deformable biasing portion 24a is formed.

  An annular ring spring 39 is disposed in an annular groove 22c formed in the inner peripheral surface 22a of the outer member 22, and this ring spring 39 abuts on the peripheral surface of the roller 25, so as to contact the outer peripheral surface 23a of the inner member 23. Energize towards.

  One angular ball bearing 34 is disposed between the two adjacent one-way clutches 21 and 21, and the outer ball members 22 and 22 and the inner member 23 can be rotated relative to each other while maintaining the concentric state. Connected to. The angular ball bearing 34 has a plurality of balls 37 arranged between two outer rings 35, 35 and one inner ring 36. The two outer rings 35, 35 are formed by two axially adjacent outer members 22, 22. The inner ring 36 is formed as a separate member and is press-fitted into the outer peripheral surface 23 a of the inner member 23. That is, one angular ball bearing 34 supports the two outer rings 35, 35 with a common ball 37, so that the two outer members 22, 22 of the two adjacent one-way clutches 21, 21 are supported in a relatively rotatable manner. Is done.

  The two angular ball bearings 34, 34 (see FIG. 9) located at both ends in the axial direction of the four one-way clutches 21 arranged side by side have only one inner ring 36 and one outer ring 35. Abut.

  As shown in FIGS. 7, 8, 10, and 12, a pair of angular ball bearings 34, 34 are disposed on both axial sides of each one-way clutch 21, and formed on an inner ring 36 of one angular ball bearing 34. The first side surface 36a and the second side surface 36b formed on the inner ring 36 of the other angular ball bearing 34 face each other. Flat first end face 25a and second end face 25b are formed at both ends in the axial direction of the roller 25. The first end face 25a of the roller 25 faces the first side face 36a of the inner ring 36, and the second end face of the roller 25. 25 b faces the second side surface 36 b of the inner ring 36.

  Twelve recesses 36d are formed at equal intervals in the circumferential direction on the first side surface 36a of the inner ring 36 of one angular ball bearing 34, and are fitted in these recesses 36d in a slidable manner in the axial direction. The disk-shaped urging members 26 are urged toward the first end face 25a of the roller 25 by an axial spring 38 made of a coil spring housed in the recess 36d. Twelve convex portions 36c are formed at equal intervals in the circumferential direction on the second side surface 36b of the inner ring 36 of the other angular ball bearing 34, and these convex portions 36c are formed on the second end surface of the roller 25. It protrudes toward 25b.

  The elastic force of the axial spring 38 presses the first end face 25a of the roller 25 through the biasing member 26 and presses the second end face 25b of the roller 25 against the convex portion 36c, thereby preventing the inclination of the roller 25. The posture is stabilized.

  As shown in FIG. 12, the roller 25 is movable relative to the outer member 22 and the inner member 23 in the circumferential direction, and the roller 25 is positioned at the position of the roller 25 so that the inner peripheral surface 22 a of the outer member 22 and the inner member 22 A position (engage point) that engages in a wedge-shaped space formed between the outer peripheral surfaces 23a of 23, and transmits a driving force, and a standby position (date point) immediately before the roller 25 engages in the wedge-shaped space; There is a position (damping point) where the roller 25 is pushed back in the reverse direction from the engagement point to the maximum in the reverse direction at the moment when the one-way clutch 21 is disengaged.

  The outer diameter D1 of the urging member 26 and the outer diameter D1 of the circular convex portion 36c are set to be smaller than the outer diameter D of the roller 25, and the center O1 of the circular urging member 26 and the circular convex portion 36c. The center O1 coincides with the center of the roller 25 at the daytime point.

  The first contact surface P1 where the biasing member 26 contacts the first end surface 25a of the roller 25 and the second contact surface P2 where the convex portion 36c contacts the second end surface 25b of the roller 25 are the diameter of the roller 25. It has the same diameter D1 smaller than D, and shares the center O1 with the roller 25 at the daytime point.

  Next, the operation of the embodiment of the present invention having the above configuration will be described.

  First, the operation of one power transmission unit U of the continuously variable transmission T will be described. When the rotation shaft 14 a of the speed change actuator 14 is rotated relative to the input shaft 11, the carrier 16 rotates about the axis L <b> 1 of the input shaft 11. At this time, the center O of the carrier 16, that is, the center of the equilateral triangle formed by the first pinion 15 and the two second pinions 17, 17 rotates around the axis L 1 of the input shaft 11.

  3 and 5 show a state in which the center O of the carrier 16 is on the opposite side of the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). The amount of eccentricity is maximized, and the gear ratio of the continuously variable transmission T is in a minimum OD (overdrive) state. 4 and 6 show a state in which the center O of the carrier 16 is on the same side as the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). At this time, the eccentric disk 18 with respect to the input shaft 11 The amount of eccentricity becomes zero, and the transmission ratio of the continuously variable transmission T becomes an infinite GN (geared neutral) state.

  In the OD state shown in FIG. 5, when the input shaft 11 is rotated by the engine E and the rotation shaft 14 a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotation shaft 14 a, the carrier 16, With the one pinion 15, the two second pinions 17 and 17, and the eccentric disk 18 being integrated, the pinion 15 rotates eccentrically around the input shaft 11 (see arrow A). While rotating from FIG. 5A through FIG. 5B to the state of FIG. 5C, the ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the outer member 22 pivotally supported by a pin 19c at the tip of the rod portion 19a in the counterclockwise direction (see arrow B). 5A and 5C show both ends of rotation of the outer member 22 in the arrow B direction.

  When the outer member 22 rotates in the arrow B direction in this way, the rollers 25... Bite into the wedge-shaped space between the outer member 22 and the inner member 23 of the one-way clutch 21, and the rotation of the outer member 22 passes through the inner member 23. Therefore, the output shaft 12 rotates counterclockwise (see arrow C).

  When the input shaft 11 and the first pinion 15 further rotate, the eccentric disk 18 in which the ring gear 18a is engaged with the first pinion 15 and the second pinion 17, 17 rotates eccentrically in the counterclockwise direction (see arrow A). While rotating from the state shown in FIG. 5C to the state shown in FIG. 5A, the ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the outer member 22 pivotally supported by a pin 19c at the tip of the rod portion 19a in the clockwise direction (see arrow B ′). FIG. 5C and FIG. 5A show both ends of the rotation of the outer member 22 in the arrow B ′ direction.

  When the outer member 22 rotates in the direction of the arrow B ′ in this way, the rollers 25 are pushed out from the wedge-shaped space between the outer member 22 and the inner member 23 while compressing the engagement springs 24, thereby the outer member. 22 slips with respect to the inner member 23 and the output shaft 12 does not rotate.

  As described above, when the outer member 22 reciprocates, the output shaft 12 rotates counterclockwise (see arrow C) only when the rotation direction of the outer member 22 is counterclockwise (see arrow B). The shaft 12 rotates intermittently.

  FIG. 6 shows the operation when the continuously variable transmission T is operated in the GN state. At this time, since the position of the input shaft 11 coincides with the center of the eccentric disk 18, the eccentric amount of the eccentric disk 18 with respect to the input shaft 11 becomes zero. In this state, when the input shaft 11 is rotated by the engine E and the rotating shaft 14a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotating shaft 14a, the carrier 16, the first pinion 15, 2 In a state where the second pinions 17 and 17 and the eccentric disk 18 are integrated, the input pin 11 is rotated eccentrically in the counterclockwise direction (see arrow A). However, since the eccentric amount of the eccentric disk 18 is zero, the stroke of the reciprocating motion of the connecting rod 19 is also zero, and the output shaft 12 does not rotate.

  Accordingly, if the speed change actuator 14 is driven and the position of the carrier 16 is set between the OD state of FIG. 3 and the GN state of FIG. 4, operation at an arbitrary speed ratio between the infinite speed ratio and the minimum speed ratio is performed. Is possible.

  In the continuously variable transmission T, the phases of the eccentric disks 18 of the four power transmission units U arranged in parallel are shifted by 90 ° from each other, so that the four power transmission units U are alternately driven. By transmitting, that is, any one of the four one-way clutches 21 is always in an engaged state, the output shaft 12 can be continuously rotated.

  Next, the tilt preventing action of the roller 25 of the one-way clutch 21 will be described.

  At the moment when the one-way clutch 21 is disengaged, the roller 25 at the engagement point is pushed back to the damping point while compressing the engagement spring 24 beyond the daytime point, and then the elastic force of the compressed engagement spring 24 causes the day. Return to the tom point and wait for the next engagement of the one-way clutch 21.

  When the roller 25 moves from the damping point to the daytime point, the first contact surface P1 of the biasing member 26 biased by the axial spring 38 contacts the first end surface 25a of the roller 25, and the roller 25 Since the two end surfaces 25b are in contact with the second contact surface P2 of the second side surface 36b of the inner ring 36, the inclination of the roller 25 is suppressed by the guide action of the first contact surface P1 and the second contact surface P2.

  At this time, if the frictional force acting on the first end surface 25a and the second end surface 25b of the roller 25 is unbalanced, the roller 25 may be inclined, but according to the present embodiment, The first contact surface P1 of the biasing member 26 that contacts the first end surface 25a and the second contact surface P2 of the convex portion 36c that contacts the second end surface 25b have the same shape, and the first contact surface P1. Since the second contact surface P2 is symmetrically disposed on both axial sides of the roller 25, the frictional forces acting on the first end surface 25a and the second end surface 25b of the roller 25 have the same magnitude. As a result, the inclination of the roller 25 at the daytime point is prevented, the roller 25 moves from the daytime point to the engagement point in a correct posture, and the one-way clutch 21 can be smoothly engaged.

  If the roller 25 is tilted, the outer peripheral portion of the first end surface 25a or the second end surface 25b may be engaged with the first side surface 36a or the second side surface 36b to promote wear, but the tilt of the roller 25 is prevented. This suppresses the wear. In particular, when the roller 25 is at the daytime point, the first end surface 25a and the second end surface 25b of the roller 25 are formed on the first contact surface P1 of the biasing member 26 having a smaller diameter and the first end surface 25c of the convex portion 36c. 2 Since the contact surface P2 contacts, the outer peripheral portion of the first end surface 25a or the second end surface 25b is reliably prevented from being engaged with the first side surface 36a or the second side surface 36b, and the wear is more effectively suppressed. Is done.

  Further, the one-way clutches 21 of the crank type continuously variable transmission T are required to have high engagement responsiveness in order to repeat engagement and disengagement at short time intervals. By providing this continuously variable transmission T, the effect is more effectively exhibited.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, the use of the one-way clutch of the present invention is not limited to the continuously variable transmission T of the embodiment. However, since the one-way clutch 21 of the continuously variable transmission T according to the embodiment repeats engagement and disengagement at short time intervals, the effect is more effectively exhibited by applying the present invention to the one-way clutch 21. .

  In the embodiment, the angular ball bearing 34 is used as a part of the cage 31 to simplify the structure of the cage 31 and reduce the number of parts. However, the cage 31 is formed of a member separate from the angular ball bearing 34. can do.

11 Input shaft 12 Output shaft 18 Eccentric disc (input side fulcrum)
19 Connecting rod 19c Pin (Output side fulcrum)
21 One-way clutch 22 Outer member 22a Inner peripheral surface 23 Inner member 23a Outer peripheral surface 24 Engage spring 25 Roller 25a First end surface 25b Second end surface 26 Energizing member 31 Cage 36a First side surface 36b Second side surface 36c Convex portion 38 Axial spring E Engine (drive source)
P1 first contact surface (roller contact surface of biasing member)
P2 Second contact surface (roller contact surface of convex part)
U Power transmission unit

Claims (4)

A plurality of rollers (25) held in a cage (31) disposed between the outer peripheral surface (23a) of the inner member (23) and the inner peripheral surface (22a) of the outer member (22) are circumferentially engaged by an engagement spring (24). The roller (25) is engaged between the outer peripheral surface (23a) and the inner peripheral surface (22a) by relative rotation in one direction of the inner member (23) and the outer member (22). As well as transmitting the driving force,
The cage (31) includes a first side surface (36a) and a second side surface (36b) facing the first end surface (25a) and the second end surface (25b) of the roller (25), respectively. An axial spring (38) provided on 36a) urges the first end face (25a) in the axial direction to bring the second end face (25b) into contact with the second side face (36b), thereby the roller ( 25) a one-way clutch that regulates the posture of
The one-way clutch characterized in that a frictional force acting on the first end face (25a) and a frictional force acting on the second end face (25b) are made to coincide.   An urging member (26) is supported on the first side surface (36a) so as to be axially movable, and the urging member (26) is axially directed toward the first end surface (25a) by the axial spring (38). And a convex portion (36c) against which the second end surface (25b) abuts is formed on the second side surface (36b), and the roller abutting surface (P1) of the urging member (26) and the The roller contact surface (P2) of the convex portion (36c) has the same shape and is coaxially opposed on both sides in the axial direction of the roller (25), so that the first end surface (25a) and the biasing member 2. The one-way clutch according to claim 1, wherein a frictional force acting between the second end surface and the convex portion is made to coincide with each other. .   When the roller (25) is at a daytime point that is a standby position immediately before being engaged between the outer peripheral surface (23a) of the inner member (23) and the inner peripheral surface (22a) of the outer member (22), The outer peripheral portions of the roller contact surfaces (P1, P2) of the urging member (26) and the convex portion (36c) are inside the outer peripheral portions of the first and second end surfaces (25a, 25b). The one-way clutch according to claim 2, wherein the one-way clutch is characterized. A crank type continuously variable transmission comprising the one-way clutch (21) according to any one of claims 1 to 3,
The inner member (23) of the one-way clutch (21) is a power transmission unit (U) for shifting the rotation of the input shaft (11) connected to the drive source (E) and transmitting it to the output shaft (12). Fixed to the outer periphery of the output shaft (12);
The power transmission unit (U) includes an input side fulcrum (18) that is variable in eccentricity from the axis of the input shaft (11) and rotates together with the input shaft (11), and the one-way clutch (21). A crank type comprising an output side fulcrum (19c) provided on the outer member (22), and a connecting rod (19) connecting the input side fulcrum (18) and the output side fulcrum (19c). Continuously variable transmission.

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