JP2014228109A - One-way clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure the total length while preventing interfering of an engage spring for biasing a roller of a one-way clutch with another member.SOLUTION: As an engage spring 24 of a one-way clutch 21 configured by curving an elastic plate material, includes: a fixed end portion 24a; a fixed end portion-side straight portion 24c; an inner curved portion 24d; a biased end portion-side straight portion 24e; an outer curved portion 24f; and a biased end portion 24b, the engage spring 24 having the long total length is disposed without interfering with another member, in a space limited between an outer member 22 and an inner member 12, stress generated on the engage spring 24 can be reduced, and durability can be improved. Further as a radius of curvature of the outer curved portion 24f is smaller than a radius of curvature of the inner curved portion 24d, the inner curved portion 24d is deformed first, so that a load is dispersed in a long distance from the inner curved portion 24d to the biased end portion 24b, and durability of the engage spring 24 can be further improved.

Description

  In the present invention, a plurality of rollers arranged between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member are urged in the circumferential direction by an engagement spring, and a plurality of rollers are rotated by relative rotation of the outer member and the inner member in a predetermined direction. The present invention relates to a one-way clutch that transmits a driving force by interposing a roller between the inner peripheral surface and the outer peripheral surface.

  A plurality of sprags are slidably disposed between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member, and an intermediate portion of an engagement spring formed by bending an elastic plate is fixed to the connecting portion of the cage. A one-way clutch in which both end portions of a spring are brought into contact with two adjacent sprags is known from Patent Document 1 below.

Japanese Patent Laid-Open No. 9-42329

  By the way, the sprag described in the above-mentioned Patent Document 1 is engaged when the one-way clutch is engaged when it swings in one direction, and the one-way clutch is disengaged when it swings in the other direction. The amount of deformation of the spring is relatively small.

  However, in a one-way clutch that uses a roller instead of a sprag, the roller largely moves in the circumferential direction of the outer member and the inner member between the engaged state and the disengaged state. It will be larger than if it were. Therefore, when the roller is urged by an engagement spring formed by bending a plate material having elasticity, a large amount of stress is generated in the engagement spring due to a large amount of movement of the roller, and there is a concern that the durability of the roller may be reduced.

  In order to reduce the stress generated in the engagement spring, it is effective to lengthen the entire length of the engagement spring (the total length of the elastic plate before bending), but in a limited space between the outer member and the inner member It becomes difficult to arrange a long engagement spring, and the engagement spring may interfere with other members and cannot generate a stable urging force.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to ensure the entire length while avoiding interference with other members of an engagement spring that biases a roller of a one-way clutch.

  In order to achieve the above object, according to the invention described in claim 1, an annular outer member, an inner member disposed coaxially within the outer member, an inner peripheral surface of the outer member, and the A plurality of rollers disposed between outer peripheral surfaces of the inner member, a cage fixed to the outer member or the inner member, and a plurality of engagements supported by the cage and biasing the plurality of rollers in the circumferential direction A one-way clutch that transmits a driving force by engaging the plurality of rollers between the inner peripheral surface and the outer peripheral surface by relative rotation of the outer member and the inner member in a predetermined direction. The cage includes a pair of annular members juxtaposed in the axial direction and a plurality of spring support members that connect the pair of annular members in the axial direction. The engagement spring is formed by bending an elastic plate, and is bent in a direction opposite to a fixed end portion fixed to the spring support member at a radially outer side than a moving locus of the roller and a surface of the roller. And a biasing end portion that comes into contact with the surface of the roller radially outward from the movement locus, a fixed end portion linear portion that extends linearly inward from the fixed end portion, and the fixed end portion straight line. An inner curved portion that curves convexly inwardly from the inner portion, an urging end side linear portion that extends linearly outward from the inner curved portion, and a radial direction from the urging end portion linear portion A one-way clutch characterized by comprising an outer curved portion that is convexly curved toward the outside and is connected to the biasing end portion, wherein a radius of curvature of the outer curved portion is smaller than a radius of curvature of the inner curved portion. Proposed.

  According to the second aspect of the present invention, in addition to the configuration of the first aspect, the fixed end portion is curved in a U-shape and is fitted to the spring support member of the cage from the biasing end portion side. A one-way clutch characterized by being fixed in this manner is proposed.

  According to the invention described in claim 3, in addition to the configuration of claim 1 or claim 2, a recess is formed in the outer peripheral surface of the inner member, and the inner curved portion is fitted in the recess. A one-way clutch is proposed.

  According to the invention described in claim 4, in addition to the configuration of claim 3, a convex portion is formed on the inner peripheral portion of the annular member of the cage, and the convex portion is engaged with the concave portion of the inner member. A one-way clutch characterized by the above is proposed.

  The output shaft 12 of the embodiment corresponds to the inner member of the present invention, and the swing link 22 of the embodiment corresponds to the outer member of the present invention.

  According to the configuration of claim 1, when the outer member and the inner member are relatively rotated in one direction, the roller biased by the engagement spring is engaged between the outer member and the inner member, and the one-way clutch is engaged, and the outer member When the inner member rotates relative to the other direction, the roller is pushed out between the outer member and the inner member while compressing the engagement spring, and the one-way clutch is disengaged.

  An engagement spring configured by bending an elastic plate material includes a fixed end side linear portion linearly extending radially inward from a fixed end portion fixed to a spring support member of the cage, and a fixed end side linear portion. From the inner curved portion, the urging end side linear portion extending linearly outward from the inner curved portion, and from the urging end side linear portion toward the radially outer side. And an outer curved portion that is convexly curved and a biasing end portion that is connected to the outer curved portion and contacts the surface of the roller, so that it interferes with other members in a space limited between the outer member and the inner member. In addition, an engagement spring having a large overall length can be arranged to reduce the stress generated in the engagement spring and enhance durability. Moreover, since the radius of curvature of the outer curved portion is smaller than the radius of curvature of the inner curved portion, the inner curved portion having a larger curvature radius first deforms when the biasing end receives a reaction force from the roller, and the inner curved portion, It is possible to increase the durability of the engagement spring by dispersing the load over a long distance of the urging end portion side straight portion, the outer curved portion, and the urging end portion.

  According to the second aspect of the present invention, the fixed end portion is curved in a U-shape and is fitted and fixed to the spring support member of the cage from the biasing end portion side, so that the biasing end portion of the engagement spring is Even when the reaction force is received from the roller, the reaction force acts in a direction in which the fixed end portion of the engagement spring is pressed against the spring support member, so that the fixed end portion of the engagement spring can be reliably prevented from falling off.

  Further, according to the configuration of the third aspect, since the concave portion is formed on the outer peripheral surface of the inner member and the inner curved portion is fitted into the concave portion, the engagement spring disposed in the limited space between the outer member and the inner member The length can be further extended, and the stress generated in the engagement spring can be further reduced to enhance the durability.

  Further, according to the configuration of the fourth aspect, since the convex portion is formed on the inner peripheral portion of the annular member of the cage and the convex portion is engaged with the concave portion of the inner member, the concave portion into which the inner curved portion of the engagement spring is fitted is formed. Utilizing this, the cage can be fixed to the inner member in a non-rotatable manner.

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 perspective view of a cage and an engagement spring. 9 is an enlarged view of 9 parts in FIG. FIG. 10 is a sectional view taken along line 10-10 in FIG. 9; FIG. 11 is an enlarged view of part 11 of FIG. 10.

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

  As shown in FIG. 1, 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 includes a crank type continuously variable transmission T and a differential gear D. Prepare.

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

  As shown in FIGS. 2 and 3, the continuously variable transmission T of the present embodiment is obtained by superimposing a plurality of (four in the embodiment) transmission units U having the same structure in the axial direction. These transmission units U are provided with a common input shaft 11 and a common output shaft 12 arranged in parallel, and the rotation of the input shaft 11 is decelerated or increased and transmitted to the output shaft 12.

  Hereinafter, the structure of one 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.

  The four 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 90 ° at each transmission unit U. Is different.

  The one-way clutch 21 provided on the outer periphery of the output shaft 12 has an inner peripheral portion of the swing link 22 pivotally supported on the rod portion 19a of the connecting rod 19 via a pin 19c as an outer member, and the outer peripheral portion of the output shaft 12 The inner member is provided with a plurality of rollers 25 urged by engagement springs 24 in a wedge-shaped space formed between the outer member and the inner member.

  As is apparent from FIG. 2, the four transmission units U... Share the crank-shaped carrier 16, but the phases of the eccentric discs 18 supported by the carrier 16 via the second pinions 17 and 17 are respectively. The transmission unit U is different by 90 °. For example, in FIG. 2, the eccentric disk 18 of the leftmost transmission unit U is displaced upward in the figure with respect to the input shaft 11, and the eccentric disk 18 of the third transmission unit U from the left is illustrated with respect to the input shaft 11. The eccentric disks 18 and 18 of the second and fourth transmission units U and U from the left are positioned 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 between a circular inner peripheral surface 22a of an annular swing link 22 and an outer peripheral surface 12a bent in a wave shape of the cylindrical output shaft 12. .., And the connecting rod 19 is connected to the projecting portions 22 b and 22 b provided on the outer periphery of the swing link 22 via the pins 19 c and the clips 40 and 40.

  The one-way clutch 21 includes a cage 31 for supporting the engagement springs 24 that urge the rollers 25. The cage 31 is composed of a pair of annular members 32, 32 made of an annular plate material, and twelve spring support members 33, which are arranged at equal intervals in the circumferential direction and connect the pair of annular portions 32, 32 to each other. The pair of annular members 32 are disposed on both sides in the axial direction of the twelve rollers 25, and the twelve spring support members 33 are disposed between the twelve rollers 25. Twelve recesses 32a... Recessed outward in the radial direction are formed at the inner peripheral portion of one annular member 32 at intervals of 30 °, and the inner peripheral portions of both annular members 32 protrude radially inward. Four convex portions 32b are formed at intervals of 90 °.

  As shown in detail in FIG. 11, the engagement spring 24 is configured by bending one rectangular elastic plate material so as to have a constant cross section. At one end of the engagement spring 24, a spring support of the cage 31 is provided on the outer side in the radial direction from the movement locus 42 of the concentric roller 25 located between the inner peripheral surface 22 a of the swing link 22 and the outer peripheral surface 12 a of the output shaft 12. A fixed end portion 24 a fixed to the member 33 is formed, and the other end of the engagement spring 24 is curved in an arc shape in a direction opposite to the curved direction of the surface of the roller 25, and the movement locus 42 of the roller 25 is Further, a biasing end portion 24b that is in contact with the surface of the roller 25 on the radially outer side is formed. The fixed end 24a has a U-shaped cross section, and is fixed by being pressed into the spring support member 33 having a rectangular cross section from the biasing end 24b side.

  The engagement spring 24 has a fixed end side linear portion 24c extending substantially linearly inward in the radial direction from the fixed end portion 24a, and is directed radially inward from the fixed end side linear portion 24c radially inward of the movement locus 42. An inner curved portion 24d that curves in a convex manner, and an urging end side straight portion 24e that extends linearly outward from the inner curved portion 24d in the radial direction. The fixed end portion straight portion 24c, the inner curved portion 24d, and the biasing end portion straight portion 24e are formed in a J-shape or U-shape as a whole, and the inner curved portion 24d is a recess formed on the surface of the output shaft 12. 12b is fitted through a slight gap. Further, the intermediate portion of the fixed end portion side straight portion 24c is slightly curved in a direction approaching the biasing end portion side straight portion 24e so as not to contact the roller 25 adjacent thereto.

  Further, the engagement spring 24 includes an outer curved portion 24f that is curved radially outward from the biasing end portion side straight portion 24e and is connected to the biasing end portion 24b on the radially outer side of the movement locus 42. The urging end side straight portion 24e and the outer curved portion 24f are formed in a J shape as a whole, and the outer curved portion 24f and the urging end portion 24b are formed in an S shape as a whole. Furthermore, the outer curved portion 24f, the biasing end portion side straight portion 24e, the inner curved portion 24d, and the fixed end portion straight portion 24c are formed in an S shape as a whole. The curvature radius of the outer curved portion 24f is smaller than the curvature radius of the inner curved portion 24d.

  Further, as shown in detail in FIG. 9, a pair of angular ball bearings 34, 34 located on both sides in the axial direction of the rollers 25 are disposed between the swing link 22 and the output shaft 12. The swing link 22 and the output shaft 12 are connected by the bearings 34 and 34 so as to be relatively rotatable while maintaining a concentric state. The angular ball bearing 34 has a plurality of balls 37 disposed between an outer ring 35 and an inner ring 36. The outer ring 35 is integrally formed at the axial end of the swing link 22, and the inner ring 36 is formed of a separate member. And fixed to the outer periphery of the output shaft 12.

  The angular ball bearings 34 are of a double row and a single row, and the two angular ball bearings 34, 34 located at both axial ends of the four one-way clutches 21 are a single row, The other three angular ball bearings 34 are shared by the two adjacent one-way clutches 21 and 21, so that they form a double row.

  An axial spring 38 is disposed between one angular ball bearing 34 and one annular member 32 of the cage 31, and a plurality of protrusions 38 a projecting from the inner periphery of the axial spring 38 are formed on the annular member 32. Passing between the inner peripheral recesses 32a (see FIG. 7), it elastically contacts the end face of the rollers 25. An annular ring spring 39 is disposed in an annular groove 22c formed on the inner peripheral surface of the swing link 22, and this ring spring 39 abuts on the peripheral surface of the rollers 25 to contact the outer peripheral surface 12a of the output shaft 12. Energize towards.

  Both ends of the output shaft 12 are rotatably supported by a transmission case via a pair of ball bearings 41, 41, and four one-way clutches 21 between the inner races 41a, 41a of the ball bearings 41, 41 ... Is placed.

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

  First, the operation of one 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 ratio of the continuously variable transmission T is in the 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 is minimized and the ratio of the continuously variable transmission T is in the 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 swing link 22 pivotally supported by the pin 19c at the tip of the rod portion 19a in the counterclockwise direction (see arrow B). 5A and 5C show both ends of the rotation of the swing link 22 in the arrow B direction.

  When the swing link 22 rotates in the direction of arrow B in this way, the rollers 25... Engage with the wedge-shaped space between the swing link 22 of the one-way clutch 21 and the output shaft 12, and the rotation of the swing link 22 rotates the output shaft. 12, 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 swing link 22 pivotally supported by the pin 19c at the tip of the rod portion 19a in the clockwise direction (see arrow B '). 5C and 5A show both ends of the rotation of the swing link 22 in the direction of the arrow B ′.

  When the swing link 22 rotates in the direction of the arrow B ′ in this way, the roller 25 is pushed out from the wedge-shaped space between the swing link 22 and the output shaft 12 while compressing the spring 24. The dynamic link 22 slips and the output shaft 12 does not rotate.

  As described above, when the swing link 22 reciprocates, the output shaft 12 rotates counterclockwise (see arrow C) only when the swing link 22 rotates counterclockwise (see arrow B). The output 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.

  Therefore, 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 ratio between the zero ratio and the predetermined ratio becomes possible.

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

  Next, the operation of the one-way clutch 21 will be described.

  FIG. 11 shows the roller 25 and the engagement spring 24 in the DP (Datum Point) state, the engagement state, and the damping state of the one-way clutch 21. The DP state indicates a state immediately before the one-way clutch 21 is engaged, and the roller 25 contacts the wedge-shaped space between the inner peripheral surface 22a of the swing link 22 and the outer peripheral surface 12a of the output shaft 12 without being bitten. ing. When the swing link 22 rotates relative to the output shaft 12 in the direction of arrow P from the DP state, the roller 25 is driven by the urging force received from the engagement spring 24 and the frictional force received from the swing link 22 and the output shaft 12. The one-way clutch 21 is engaged by moving in the P direction and engaging in a wedge-shaped space between the inner peripheral surface 22 a of the swing link 22 and the outer peripheral surface 12 a of the output shaft 12.

  When the swing link 22 rotates relative to the output shaft 12 in the arrow Q direction from the engaged state, the roller 25 resists the biasing force received from the engagement spring 24 by the frictional force received from the swing link 22 and the output shaft 12. And move in the direction of the arrow Q, and disengage from the wedge-shaped space between the inner peripheral surface 22a of the swing link 22 and the outer peripheral surface 12a of the output shaft 12, thereby releasing the engagement. This state is called a damping state. The roller 25 rotates in the direction of the arrow Q while compressing the urging end portions 24b of the engagement spring 24. The roller 25 is the inner peripheral surface 22a of the swing link 22 or the outer periphery of the output shaft 12. Separate from the surface 12a. Thereafter, the roller 25 is urged by the engagement spring 24 and quickly returns to the DP state.

  When the roller 25 is pushed out of the wedge-shaped space between the inner peripheral surface 22a of the swing link 22 and the outer peripheral surface 12a of the output shaft 12 in the process of shifting from the engaged state to the damping state, the axial spring 38 moves in the axial direction. Since the end face of the urged roller 25 is pressed against the annular member 32 of the cage 31, the behavior of the roller 25 can be stabilized by the frictional force. Further, when the roller 25 is pushed out from the wedge-shaped space between the inner peripheral surface 22a of the swing link 22 and the outer peripheral surface 12a of the output shaft 12, the roller 25 is subjected to an inner periphery of the swing link 22 positioned radially outward by centrifugal force. Although it is pressed against the surface, it can be suppressed by the elastic force of the ring spring 39 inward in the radial direction.

  As described above, the engagement spring 24 of the present embodiment includes the fixed end portion 24a, the fixed end portion-side straight portion 24c, the inner curved portion 24d, the biasing end portion-side straight portion 24e, and the outer curved portion that are continuously curved. Since it has 24f and urging | biasing end part 24b, the engagement spring 24 with a full length is arrange | positioned without interfering with other members in the narrow space between the rocking | fluctuation link 22 and the output shaft 12, and the stress which generate | occur | produces in the engagement spring 24 is reduced. And durability can be improved.

  Further, since the radius of curvature of the outer curved portion 24f is smaller than the radius of curvature of the inner curved portion 24d, the inner curved portion 24d having a larger curvature radius is deformed first when the biasing end portion 24b receives a reaction force from the roller 25. The durability of the engagement spring 24 can be increased by dispersing the load over a long distance of the inner curved portion 24d, the biasing end portion linear portion 24e, the outer curved portion 24f, and the biasing end portion 24b. Moreover, since the inner curved portion 24d has a large radius of curvature, the stress generated during deformation can be minimized.

  In particular, the spring support member 33 of the cage 31 and the fixed end portion 24a of the engagement spring 24 fixed to the cage 31 are positioned radially outside the movement locus 42 of the roller 25, that is, avoiding interference with the roller 25. Since the spring support member 33 and the fixed end portion 24a are arranged in a compact manner, the length of the fixed end portion side linear portion 24c extending radially inward from the spring support member 33 and the fixed end portion linear portion 24c is ensured to the maximum. The total length can be increased.

  Further, since the concave portion 12b is formed on the outer peripheral surface 12a of the output shaft 12 and the inner curved portion 24d of the engagement spring 24 is fitted into the concave portion 12b, it is disposed in a limited space between the swing link 22 and the output shaft 12. The length of the engagement spring 24 can be extended to the maximum, and the stress generated in the engagement spring 24 can be further reduced to enhance the durability. When the reaction force from the roller 25 is transmitted to the inner curved portion 24d, the inner curved portion 24d is prevented from coming into contact with the inner surface of the concave portion 12b of the output shaft 12 because the radius of curvature is deformed. The

  Further, the fixed end portion 24a of the engagement spring 24 is curved in a U-shape and is fitted and fixed to the spring support member 33 of the cage 31 from the biasing end portion 24b side, so that the biasing end portion 24b of the engagement spring 24 is fixed. Even if the reaction force is received from the roller 25, the reaction force acts in a direction in which the fixed end portion 24a of the engagement spring 24 is pressed against the spring support member 33, so that the fixed end portion 24a of the engagement spring 24 falls off. It can be surely prevented.

  The urging end 24 b of the engagement spring 24 abuts the roller 25 at a position radially outward from the movement locus 42 of the roller 25, so that the roller 25 that is urged radially outward by centrifugal force is moved toward the engagement spring 24. It is possible to stabilize the behavior of the roller 25 by urging radially inward with the elastic force.

  Further, since the roller 25 contacts the urging end 24b of the engagement spring 24 while rotating, if the contact area is large, the urging end 24b is not wound around the roller 25, and the urging end 24b causes the roller 25 to move. There is a possibility that the energizing direction is shifted. However, according to the present embodiment, the urging end 24b is curved in the direction opposite to the curve direction of the surface of the roller 25. Therefore, the urging end 24b and the roller 25 are brought into line contact to minimize the contact area. To the limit.

  Further, since the convex portions 32b are formed on the inner peripheral portion of the annular member 32 of the cage 31 and the convex portions 32b are engaged with the concave portions 12b of the output shaft 12, the inner curved portions 24d of the engagement spring 24 are formed. The cage 31 can be fixed to the inner member 22 in a non-rotatable manner by using the recessed portions 12b to be fitted.

  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, and can be applied to any use.

  In the embodiment, the cage 31 is fixed to the output shaft 12 side, but it can be fixed to the swing link 22 side.

  Further, the fixed-end-side straight portion 24c and the biasing-end-side straight portion 24e of the engagement spring 24 do not have to be geometric straight lines, and may have a larger radius of curvature than the inner curved portion 24d or the outer curved portion 24f. .

12 Output shaft (inner member)
12a Outer peripheral surface 12b Recess 22 Swing link (outer member)
22a Inner peripheral surface 24 Engagement spring 24a Fixed end 24b Energizing end 24c Fixed end-side linear portion 24d Inner curved portion 24e Energized end-side linear portion 24f Outer curved portion 25 Roller 31 Cage 32 Annular member 32b Protruding portion 33 Spring support member 42 Trajectory

Claims (4)

An annular outer member (22), an inner member (12) disposed coaxially within the outer member (22), an inner peripheral surface (22a) of the outer member (22), and the inner member (12) A plurality of rollers (25) disposed between the outer peripheral surfaces (12a) of the outer surface, a cage (31) fixed to the outer member (22) or the inner member (12), and the cage (31). A plurality of engagement springs (24) for urging the plurality of rollers (25) in the circumferential direction, and the plurality of the plurality of rollers (25) by relative rotation in a predetermined direction of the outer member (22) and the inner member (12). A one-way clutch that transmits the driving force by engaging the roller (25) between the inner peripheral surface (22a) and the outer peripheral surface (12a),
The cage (31) includes a pair of annular members (32) juxtaposed in the axial direction, and a plurality of spring support members (33) that connect the pair of annular members (32) in the axial direction,
The engagement spring (24) is formed by bending an elastic plate, and is fixed to the spring support member (33) at a radially outer side than the movement locus (42) of the roller (25) ( 24a), a biasing end (24b) that curves in the opposite direction with respect to the surface of the roller (25) and contacts the surface of the roller (25) radially outward from the movement locus (42), A fixed end side linear portion (24c) linearly extending radially inward from the fixed end portion (24a), and an inner curve that curves convexly from the fixed end side linear portion (24c) toward the radially inner side. Portion (24d), urging end side linear portion (24e) linearly extending radially outward from the inner curved portion (24d), and radially outward from the urging end portion linear portion (24e) Curved toward the convex end (2 With outwardly curved portion to be connected to b) and (24f), the radius of curvature of the outer curved portion (24f) is a one-way clutch, characterized in that less than the radius of curvature of the inner curved portion (24d).   The fixed end portion (24a) is curved in a U-shape and is fitted and fixed to the spring support member (33) of the cage (31) from the biasing end portion (24b) side. The one-way clutch according to claim 1.   The recessed part (12b) was formed in the outer peripheral surface of the said inner member (12), and the said inner side curved part (24d) was fitted to the said recessed part (12b), The Claim 1 or Claim 2 characterized by the above-mentioned. One-way clutch.   A convex portion (32b) is formed on the inner peripheral portion of the annular member (32) of the cage (31), and the convex portion (32b) is engaged with the concave portion (12b) of the inner member (12). The one-way clutch according to claim 3.

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