JP5352493B2 - One way clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To allow smooth engagement and disengagement, by controlling properly a lubrication state of a roller of a one-way clutch. <P>SOLUTION: A contact area when the roller 42 is meshed in between an inner circumferential face of an outer member 43 and an outer circumferential face of an inner member 41 is reduced by a level corresponding to a groove 70c, to enhance contact face pressure, since the groove 70c is formed in the inner member 41 contacting with the roller 42 located in a meshing start position, and an oil film on a contact face is broken therein to mesh smoothly the roller 42. A groove width decreases and the contact area increases in the position where the roller 42 is meshed strongly to eliminate a slipping space, because the axial-directional groove width of the roller 42 is reduced toward a meshing direction of the roller 42, and the contact face pressure is thereby prevented from increasing excessively to secure durability. The roller 42 is prevented from being caught to allow the smooth disengagement, since a circumferential face of the roller 42 is lubricated by a lubricating oil reserved in the groove 70c, when the roller 42 is rotated at the time of disengaging the one-way clutch. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  According to the present invention, a plurality of rollers disposed in an annular space formed between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member are biased in one circumferential direction by a spring, and the outer member and the inner member The present invention relates to a one-way clutch that transmits a driving force by engaging the roller between an inner peripheral surface of the outer member and an outer peripheral surface of the inner member by relative rotation of the member in a predetermined direction.

  In such a one-way clutch, in order to supply lubricating oil to a plurality of rollers disposed in a space between the outer member and the inner member, a spiral lubricating oil groove that opens on a facing surface where the outer member or the inner member and the end bearing rotate relative to each other is provided. Is known from Japanese Patent Application Laid-Open Publication No. 2004-228688.

Japanese Patent No. 3761596

  By the way, in order to ensure the durability of the one-way clutch, it is essential to supply lubricating oil to the contact surfaces of the outer member and the inner member and the roller. If the amount of lubricating oil present on the contact surface is excessive at the moment when the one-way clutch is engaged with the surface, the roller may slip, making smooth engagement difficult.

  The present invention has been made in view of the above circumstances, and an object thereof is to enable smooth engagement and disengagement by appropriately controlling the lubrication state of a roller of a one-way clutch.

  To achieve the above object, according to the first aspect of the present invention, a plurality of rollers arranged in an annular space formed between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member are springs. The roller is urged in one direction in the circumferential direction, and the outer member and the inner member are rotated relative to each other in a predetermined direction so that the roller is engaged between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member. In the one-way clutch that transmits the driving force, at least one of the outer member and the inner member that are in contact with the roller at the engagement start position is reduced in the axial width of the roller toward the roller engagement direction. A one-way clutch characterized by forming a groove is proposed.

  The first spring 59 of the embodiment corresponds to the spring of the present invention.

  According to the configuration of claim 1, since the plurality of rollers arranged in the annular space formed between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member are biased in the circumferential direction by the spring, By the relative rotation of the outer member and the inner member in a predetermined direction, the roller can be engaged between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member to transmit the driving force. Since the groove is formed in the outer member or the inner member that the roller at the meshing start position comes into contact with, the contact area when the roller is engaged between the inner peripheral surface of the outer member and the outer peripheral surface of the inner member is equal to the groove. By reducing the contact surface pressure, the oil film on the contact surface can be cut to enable smooth engagement of the roller. In addition, since the groove width in the axial direction of the roller decreases toward the roller engagement direction, the groove width decreases and the contact area increases at a position where there is no risk of the roller being strongly engaged and slipping. It is possible to prevent an excessive increase in the durability and ensure the durability. Also, if the roller rotates when the one-way clutch is disengaged, the circumferential surface of the roller is lubricated by the lubricating oil accumulated in the groove, so that the roller can be prevented from being caught and the engagement can be smoothly disengaged. it can.

The longitudinal cross-sectional view of a continuously variable transmission. [First Embodiment] FIG. 2 is a view taken along line 2-2 in FIG. 1 (neutral position). [First Embodiment] FIG. 3 is a sectional view taken along line 3-3 in FIG. 2 (neutral position). [First Embodiment] FIG. 4-4 is an arrow view (neutral position) in FIG. 3. [First Embodiment] 5A-5A line, 5B-5B line and 5C-5C line view of FIG. 3 (neutral position). [First Embodiment] The figure (UD position) corresponding to the said FIG. [First Embodiment] FIG. 7 is a view on arrow 7-7 in FIG. 6 (UD position). [First Embodiment] The figure which shows the eccentric state of the four eccentric discs in a UD position. [First Embodiment] The figure (OD position) corresponding to the said FIG. [First Embodiment] FIG. 10 is a view taken along line 10-10 in FIG. 9 (OD position). [First Embodiment] The figure which shows the eccentric state of four eccentric discs in OD position. [First Embodiment] The disassembled perspective view of a transmission unit. [First Embodiment] Explanatory drawing of the drive reaction force which a control shaft receives. [First Embodiment] Explanatory drawing of the shift control of a continuously variable transmission by a control valve. [First Embodiment] Explanatory drawing of the shift control from the start of an engine to a stop. [First Embodiment] FIG. 16 is a sectional view taken along line 16-16 in FIG. 2; [First Embodiment] FIG. 17 is a cross-sectional view taken along line 17-17 in FIG. [First Embodiment] 18 is an enlarged view of a portion 18 in FIG. [First Embodiment] FIG. 19 is a cross-sectional view taken along line 19-19 of FIG. [First Embodiment] FIG. 20 is a sectional view taken along line 20-20 in FIG. [First Embodiment] FIG. 21 is a sectional view taken along line 21-21 in FIG. [First Embodiment] FIG. 22 is a cross-sectional view taken along line 22-22 in FIG. 19. [First Embodiment] The disassembled perspective view of an inner member and a cam member. [First Embodiment] FIG. 24 is a sectional view taken along line 24-24 in FIG. 18. [First Embodiment] The exploded perspective view of a pivot arm. [First Embodiment] Action | operation explanatory drawing of the pivot arm at the time of engagement and the time of non-engagement. [First Embodiment] Action | operation explanatory drawing of an engagement control means. [First Embodiment] Action | operation explanatory drawing of a 2nd spring. [First Embodiment]

  Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 to 5 and 12, the continuously variable transmission T that transmits the driving force of the engine E to the left and right drive wheels W and W is connected in series and coaxially to the crankshaft 11 of the engine E. An input shaft 12 and an output shaft 13 arranged in parallel with the input shaft 12 are provided. The output shaft 13 is connected to the left and right axles 14 and 14 via a differential gear D, and one axle 14 penetrates the inside of the output shaft 13 in a relatively rotatable manner.

  The input shaft 12 and the output shaft 13 are connected by four sets of transmission units 15 that have the same structure and are overlapped in the direction of the axis L of the input shaft 12. The input shaft 12 formed in a crank shape has two journals 17 and 17 that are positioned at both ends and supported by ball bearings 16 and 16, and four journals that are arranged 90 ° out of phase with each other. The crank pins 18 are constituted by five crank webs 19 that integrally connect the journals 17, 17 and the crank pins 18.

  The control shaft 20 slides in the direction of the axis L through the centers of the two journals 17 and 17 of the input shaft 12 and the through holes 19a formed in the five crank webs 19 (see FIGS. 2 and 12). A hydraulic cylinder 22 is connected to one end of the control shaft 20 via a coupling 21 that transmits a thrust force in the direction of the axis L and does not transmit torque.

The hydraulic cylinder 22 is partitioned on both sides of the piston rod 23 disposed on the axis L, a piston 24 fixed to the piston rod 23, a cylinder 25 in which the piston 24 is slidably fitted, and a piston 24. First and second oil chambers 26 and 27 and a return spring 28 that urges the piston 24 in one direction are provided. The oil passage 29 that connects the first and second oil chambers 26 and 27 to each other has a position that allows only the flow of hydraulic oil from the first oil chamber 26 to the second oil chamber 27, and the first and second oil chambers 27 and 27. It consists of a solenoid valve that can select a position that prevents the flow of hydraulic oil between the oil chambers 26 and 27 and a position that only allows the flow of hydraulic oil from the second oil chamber 27 to the first oil chamber 26. Next, the structure of the transmission units 15 will be described with reference to FIGS. 1 to 5 and FIG. 12. Since the four sets of transmission units 15 have the same structure except that their phases are shifted from each other by 90 ° (see FIGS. 2 and 5), one structure will be described as a representative.

  The transmission unit 15 includes a shallow cup-shaped eccentric disc 31 having a pin hole 31a rotatably supported on the outer periphery of the crank pin 18 of the input shaft 12. The eccentric amount ε of the pin hole 31a with respect to the center O of the eccentric disk 31 is equal to the eccentric amount ε of the crank pin 18 with respect to the axis L of the input shaft (see FIGS. 4 and 8). Therefore, when the eccentric disk 31 is in a predetermined positional relationship with the crank pin 18 of the input shaft 12, the center O of the eccentric disk 31 coincides with the axis L of the input shaft 12. When the eccentric disk 31 swings around the crank pin 18, an arc-shaped long hole 31b centered on the pin hole 31a is formed on the bottom surface of the eccentric disk 31 in order to avoid interference with the control shaft 20.

  A support shaft 33 extending in a direction orthogonal to the crank pin 18 is rotatably supported by a pair of brackets 32, 32 provided on one side surface of the crank web 19 facing the bottom surface of the shallow cup-shaped eccentric disc 31. A pinion 34 and a bevel gear 35 which are coaxially coupled to the support shaft 33 are provided. The pinion 34 meshes with a rack 36 (see FIGS. 4 and 12) formed on the surface of the control shaft 20 in the direction of the axis L, and the bevel gear 35 is formed in an arc shape around the pin hole 31a on the bottom surface of the eccentric disk 31. Meshed with the sector gear 37.

  On the outer peripheral surface of the eccentric disc 31, the inner peripheral surface of one end of the pull side connecting rod 39 and the push side connecting rod 40 is supported via ball bearings 38, 38, respectively. One-way clutches 44, 44 each having an inner member 41, a plurality of rollers 42, and an outer member 43 are supported on the outer periphery of the output shaft 13, and are pulled by a convex portion 43 a provided on the upper portion of one outer member 43. The other end of the side connecting rod 39 is connected via a pin 45, and the other end of the push side connecting rod 40 is connected via a pin 45 to a convex portion 43 b provided at the lower portion of the other outer member 43.

  Next, the shifting operation of the continuously variable transmission T having the above-described configuration will be described.

  When the input shaft 12 connected to the crankshaft 11 of the engine E rotates, the four eccentric disks 31 supported by the four crankpins 18 of the input shaft 12 with the pin holes 31a are integrated with the input shaft 12. Rotate to. 2 to 4, the eccentricity of the eccentric discs 31 is zero, and the center O of the eccentric discs 31 coincides with the axis L of the input shaft 12 at the neutral position shown in FIGS. Yes. Accordingly, the four pull-side connecting rods 39 and the four push-side connecting rods 40 supported on the outer peripheral surface of the eccentric disc 31 through the ball bearings 38 do not reciprocate, and the pull-side connecting rods are not reciprocated. Also, the output shaft 13 connected to the 39... And the push side connecting rod 40 through the one-way clutch 44 does not rotate.

  From this state, as shown in FIG. 6, when the piston rod 23 of the hydraulic cylinder 22 moves slightly in the right direction in the drawing (UD position), the control shaft 20 connected to the piston rod 23 via the coupling 21 is moved. The rack 36 formed on the surface moves in the direction of the axis L and rotates the pinion 34 of each transmission unit 15 around the support shaft 33. As a result, the eccentric disc 31 in which the sector gear 37 is meshed with the bevel gear 35 rotating integrally with the pinion 34 swings around the crank pin 18 of the input shaft 12, and as shown in FIG. Is eccentric from the axis L of the input shaft 12 by the amount of eccentricity ε1.

  As a result, the pull-side connecting rod 39 and the push-side connecting rod 40 supported on the outer peripheral surface of the eccentric disc 31 via ball bearings 38 and 38 reciprocate with a stroke twice the eccentric amount ε1. In FIG. 7, when the pull-side connecting rod 39 is pulled to the right side in the drawing, the rollers 42 are engaged between the inner member 41 and the outer member 43 and the one-way clutch 44 is engaged, and the pull-side connecting rod 39 is shown in FIG. When pushed to the middle left, the rollers 42 slip and the one-way clutch 44 is disengaged.

  When the push side connecting rod 40 is pushed to the left in the figure, the rollers 42 are engaged between the inner member 41 and the outer member 43 and the one-way clutch 44 is engaged, so that the push side connecting rod 40 is on the right side in the figure. When pulled, the rollers 42 slip and the one-way clutch 44 is disengaged. Thus, when the pull-side connecting rod 39 and the push-side connecting rod 40 are reciprocated by the eccentric disc 31 as the input shaft 12 rotates, the pull-side connecting rod 39 is pulled and the push-side connecting rod 40 is pushed. Accordingly, the output shaft 13 rotates intermittently.

  As is apparent from FIG. 8, the four eccentric disks 31 of the four sets of transmission units 15 are out of phase with each other by 90 °, so that the four sets of transmission units 15 are rotated during the rotation of the input shaft 12. Any one of the sets always transmits the driving force, so that the output shaft 13 rotates continuously. The rotation of the output shaft 13 is transmitted to the left and right drive wheels W and W via the differential gear D and the left and right axles 14 and 14. At this time, since the eccentric amount ε1 of the eccentric discs 31 is small, the pull side connecting rods 39 and the push side connecting rods 40 reciprocate with a small stroke, and the output shaft 13 does not rotate with a large torque and a small rotational speed. The step transmission T is in the UD position (maximum gear ratio state).

  As shown in FIG. 9, when the piston rod 23 of the hydraulic cylinder 22 further moves to the right in the drawing beyond the UD position, the OD position (minimum speed ratio state) is reached, and the eccentric disc 31 is moved to the crank pin 18 of the input shaft 12. As shown in FIG. 10, the center O of the eccentric disk 31 is eccentric from the axis L of the input shaft 12 by an eccentric amount ε2 that is larger than the eccentric amount ε1 at the UD position.

  As a result, the pull-side connecting rod 39 and the push-side connecting rod 40 supported on the outer peripheral surface of the eccentric disc 31 via ball bearings 38 and 38 reciprocate with a stroke twice the eccentric amount ε2, The pull-side connecting rod 39 and the push-side connecting rod 40 reciprocate with a larger stroke than in the UD position, and the output shaft 13 rotates at a small torque and a large rotational speed so that the transmission gear ratio of the continuously variable transmission T becomes OD. Become.

  As described above, the position of the control shaft 20 is continuously controlled by the hydraulic cylinder 22 so that the transmission ratio of the continuously variable transmission T can be set to the neutral position and the OD position without requiring a special actuator such as an electric motor. Stepless control can be performed between them, and the number of parts and cost can be reduced. In addition, the eccentric discs 31 are swingably supported by the crank pins 18 of the input shaft 12, so that the eccentric discs 31 can be firmly supported to ensure stable transmission performance and durability performance.

  By the way, the hydraulic cylinder 22 of the present embodiment does not require a special drive source such as a hydraulic pump or an electric motor, and operates by a reaction force that the control shaft 20 receives from the eccentric discs 31. Hereinafter, the operation of the hydraulic cylinder 22 will be described.

  As shown in FIG. 13, when the one-way clutch 44 is engaged and the pull-side connecting rod 39 transmits a driving force, the pull-side connecting rod 39 receives a reaction torque from the one-way clutch 44 to the eccentric disc 31. Act. Similarly, when the one-way clutch 44 is engaged and the push-side connecting rod 40 transmits driving force, reaction torque is applied to the eccentric disc 31 by the driving reaction force received by the push-side connecting rod 40 from the one-way clutch 44. These two reaction torques are both sinusoidal and out of phase with each other by approximately 180 °. The control shaft 20 is moved from the eccentric disk 31 via the sector gear 37, bevel gear 35, pinion 34 and rack 36 in the direction of the axis L. It acts to push and pull in both directions.

  When the thrust forces of the control shaft 20 due to the two reaction torques received by the four eccentric disks 31 are all superimposed, a waveform with 90 ° as one cycle is obtained, and in each cycle of 90 °, the control shaft 20 is pushed and pulled in the direction in which the gear ratio is changed to the OD side and the direction in which the gear ratio is changed to the UD side.

  FIG. 14 shows a control method of the gear ratio of the continuously variable transmission T by the control valve 30. In the figure, the hold area is the area where the transmission ratio is held, the UD side shift area is the area where the transmission ratio is downshifted from the OD side to the UD side, and the OD side shift area is upshifted from the UD side to the OD side. It is an area.

  In the hold region, the communication between the first and second oil chambers 26 and 27 is blocked by turning off both the pair of solenoids 46 and 47 that operate the control valve 30. As a result, the hydraulic cylinder 22 is locked, the control shaft 20 is locked so as not to move, and the gear ratio is held.

  In the UD side shift region, by turning on one solenoid 46, the first and second oil chambers 26 and 27 are communicated with each other via one check valve. As a result, during the period in which the control shaft 20 is biased to the UD side, the hydraulic oil pushed out from the first oil chamber 26 passes through the control valve 30 and flows into the second oil chamber 27 on the opposite side, and the control is performed. Since the hydraulic cylinder 22 is locked during the period in which the shaft 20 is biased toward the OD side, the control shaft 20 moves intermittently toward the UD side.

  In the OD side shift region, the first and second oil chambers 26 and 27 are communicated with each other via the other check valve by turning on the other solenoid 47. As a result, during a period in which the control shaft 20 is urged to the OD side, the hydraulic oil pushed out from the second oil chamber 27 passes through the control valve 30 and flows into the first oil chamber 26 on the opposite side, and is controlled. Since the hydraulic cylinder 22 is locked during the period in which the shaft 20 is biased toward the UD side, the control shaft 20 moves intermittently toward the OD side.

  As described above, according to the present embodiment, the speed change ratio can be changed by operating the control shaft 20 by the driving reaction force received from the eccentric discs 31. It becomes unnecessary and the number of parts and cost can be reduced.

  By the way, when the gear ratio of the continuously variable transmission T is infinite and the eccentric amount of the eccentric discs 31 is zero, the pull side connecting rod 39 and the push side connecting rod 40 stop without reciprocating. ing. Therefore, the control shaft 20 is not pushed or pulled in the direction of the axis L, and the vehicle cannot be started because the gear ratio cannot be shifted from an infinite state to a finite state. .

  Further, when the continuously variable transmission T reduces the engine speed when the vehicle is traveling at a finite speed ratio, the one-way clutch 44 is disengaged and the pull side connecting rod 39 and the push side connecting rod 40. There is a problem that the driving force is not transmitted, and the speed change by the reaction force becomes impossible and the speed ratio cannot be returned to infinity via UD.

  Therefore, in the present embodiment, the above problem is solved by the following method. As shown in FIG. 15, since the weight distribution is set so that the gravity center position G of each eccentric disk 31 is eccentric from the center O by a distance ε3, the eccentric disk 31 is eccentric in a state where the gear ratio is infinite. Even when the center O of the disk 31 rotates in line with the axis L, a moment is generated that causes the eccentric disk 31 to swing by the centrifugal force acting on the gravity center position G.

  Further, since the eccentric disk 31 has a predetermined moment of inertia, when the rotational speed of the input shaft 12 increases, that is, when the angular acceleration of the input shaft 12 increases, the moment that urges the eccentric disk 31 toward the rotational direction delay side is increased. When the rotational speed of the input shaft 12 decreases, that is, when the angular acceleration of the input shaft 12 decreases, a moment is generated that biases the eccentric disk 31 toward the forward side in the rotational direction.

  Now, when the engine E is started at time t1 in FIG. 15, the speed ratio of the continuously variable transmission T is infinite and no driving force is transmitted, and the eccentricity of the eccentric discs 31 is zero. The pull side connecting rods 39 and the push side connecting rods 40 are not subjected to a driving reaction force for shifting. At this time, the load for urging the control shaft 20 includes the elastic force (UD side) of the return spring 28 of the hydraulic cylinder 22, the centrifugal force (OD side) acting on the eccentric center of gravity G of the eccentric disc 31, and the eccentric. The inertial force (according to acceleration / deceleration of the rotation of the disk 31) (OD side during acceleration, UD side during deceleration).

  The return spring 28 is arranged so as to bias the control shaft 20 toward the UD side, and in the event that an oil passage 29 connecting the first and second oil chambers 26 and 27 is lost, By urging the control shaft 20 to the UD side by the return spring 28, the vehicle speed can be reduced to ensure safety.

  Even if the solenoid 47 is turned on at time t1 to change the gear ratio from infinity to the OD side, the load acting on the eccentric disc 31 at that time is only the elastic force of the return spring 28 toward the UD side. The gear ratio is held in an infinite state without changing. When the sum of the centrifugal force and the inertial force exceeds the elastic force of the return spring 28 at time t2 due to the subsequent acceleration of the engine E, the transmission ratio starts to change from infinity to the OD side and starts to change from the input shaft 12 to the output shaft. Transmission of the driving force to 13 is started, and the OD position is reached at time t3.

  When the solenoid 46 is turned on at time t4 to change the gear ratio to the UD side, the pull-side connecting rod 39 and the push-side connecting rod 40 have already received a periodic driving reaction force due to transmission of the driving force. The gear ratio changes from the OD toward the UD side by the driving reaction force. During a cruise from time t5 to time t6, both solenoids 46 and 47 are turned off and the transmission ratio is held.

  When the solenoid 46 is turned on to reduce the engine speed at time t7 and decelerate the vehicle and further change the gear ratio to the UD side, the load that biases the eccentric disc 31 to the UD side is The elastic force and the inertial force accompanying the deceleration of the rotation of the eccentric disk 31, and the load that urges the eccentric disk 31 to the OD side is a centrifugal force that acts on the gravity center position G of the eccentric disk 31. At time t7, the shift to the UD side starts when the sum of the elastic force of the return spring 28, which is the urging force to the UD side, and the centrifugal force, which is the urging force to the OD side, exceeds the centrifugal force. Even after the engine E is stopped at time t8, the shift toward the UD side is continued by the resilient force of the return spring 28, and the neutral position is reached at time t9 to complete the shift.

  Note that when the engine E is started at time t1, the speed of the foot shaft (vehicle speed) has already exceeded zero because the vehicle of the present embodiment is a hybrid vehicle and the drive wheels W connected to the engine E , W is traveling by driving a drive wheel different from W.

  Next, the structure of the one-way clutch 44 will be described in detail with reference to FIGS. Since the eight one-way clutches 44 provided in the continuously variable transmission T have the same structure, one of them will be described as a representative.

  As shown in FIGS. 16 to 28, the one-way clutch 44 includes nine rollers 42... Between the outer member 43 and the inner member 41, and each roller 42 swings on the inner member 41 via the pivot arm 51. It is pivoted as possible. That is, the pivot arm 51 includes two metal holders 52 and 52 having a mirror-symmetrical shape, and two first and second couplings made of synthetic resin that integrally couple the two holders 52 and 52. Members 53 and 54. Each holder 52 includes a U-shaped roller support portion 52a and an arm portion 52b extending in a direction orthogonal to the center of the roller support portion 52a, and supports the roller 42 in the center of the roller support portion 52a. A shaft hole 52c is formed, and a long hole 52d for pivotally supporting the pivot arm 51 on the inner member 41 is formed at the tip of the arm portion 52b. The long hole 52d is formed such that the major axis “a” of the arm portion 52b in the longitudinal direction is larger than the minor axis “b” in the direction orthogonal to the arm part 52b (see FIG. 25).

  The first and second connecting members 53 and 54 are molded in a state where both ends of the roller support portion 52a of one holder 52 and both ends of the roller support portion 52a of the other holder 52 are opposed to each other. Thus, one contact portion is covered by the first connecting member 53 and integrally connected, and the other contact portion is covered by the second connecting member 54 and integrally connected. The first connecting member 53 is formed with a stopper 53 a that abuts the outer peripheral surface of the inner member 41 and restricts the pivot end of the pivot arm 51 in the non-engagement direction.

  The roller support portion 52a of the holder 52 is inclined toward the radially outer side on one side in the circumferential direction of the inner member 41, and is inclined toward the radially inner side on the other side in the circumferential direction of the inner member 41. Can be prevented from interfering with each other even if the roller support portions 52a of the holders 52 are arranged close to each other.

  A pair of bushes 58, 58 are fitted to both ends of a fulcrum pin 57 that passes through the inner member 41 and is prevented from coming off by the circlip 56, and these bushes 58, 58 are elongated holes 52 d, 52 d of the pivot arm 51. To fit. The diameter b of the bushes 58, 58 is the same as the short diameter b of the long holes 52d, 52d. Therefore, the pivot arm 51 moves in the radial direction of the one-way clutch 44 by the difference between the long diameter a and the short diameter b of the long holes 52d, 52d. Is possible.

  One end of a first spring 59, 59 made of a torsion spring wound around the outer periphery of the bushes 58, 58 at both ends of the fulcrum pin 57 is connected to the outer peripheral surface of the output shaft 13 integrally connecting the eight inner members 41. The other end is locked in locking holes 52e, 52e formed in the arm portions 52b, 52b of the pivot arm 51. Due to the resilient force of the first springs 59, 59, the pivot arm 51 is urged in the engaging direction, that is, the direction in which the roller 42 is engaged with the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41.

  A second compression spring is formed between the spring seats 61 and 61 fitted to the outer surfaces of the bushes 58 and 58 and the spring seats 52f and 52f formed by cutting and raising the arm portions 52b and 52b of the pivot arm 51. Springs 62, 62 are arranged. Due to the elastic force of the second springs 62, 62, the pivot arm 51 is urged radially outward within the range of play between the long holes 52d, 52d and the bushes 58, 58, and is in a disengaged state. 42 contacts the inner peripheral surface of the outer member 43 and is separated from the outer peripheral surface of the inner member 41.

  A roller shaft 64 passes through bushes 63 and 63 fitted in a pair of shaft holes 52c and 52c of the pivot arm 51 and is prevented from being removed by a circlip 65. Sliding bearings 66 and 66 are provided on the outer periphery of the roller shaft 64. The roller 42 is rotatably supported. Nine rollers 42 of each one-way clutch 44 are grouped in three to form three groups, and two adjacent groups face each other rather than the interval between the three rollers 42 of each group. The interval between the individual rollers 42 and 42 is set larger. Three plate-like support members 67 are radially outward from the outer peripheral surface of the output shaft 13 and the outer peripheral surfaces of the eight inner members 41 so as to partition the three groups arranged at intervals of 120 °. To extend.

  Outer races 68a and 68a of a pair of roller bearings 68 and 68 are press-fitted into both ends in the axial direction on the inner peripheral surface of the outer member 43, and three pieces are inserted into the inner races 68b and 68b of the roller bearings 68 and 68. The radially outer ends of the support members 67 are joined. Thereby, both can be assembled | attached so that relative rotation is possible, making the center of the outer member 43 and the inner member 41 correspond with sufficient precision.

  The nine pivot arms 51 are connected to each other by nine tension coil springs 69 arranged in the circumferential direction so that the nine rollers 42 move in the circumferential direction in the same phase. The tension coil springs 69 that connect the pivot arms 51 of different groups are formed longer than the other tension coil springs 69 and are disposed so as to penetrate through the openings 67a formed in the support members 67. .

  As apparent from FIG. 22, as the pivot arm 51 swings, the roller 42 moves in an annular gap between the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41 in the circumferential direction. Can be divided into three. The engagement position in FIG. 22A is a position where the roller 42 has moved most in the rotation direction of the outer member 43 (the clockwise direction in FIG. 22A). In this state, the roller 42 has an inner circumference of the outer member 43. The one-way clutch 44 is engaged by engaging with the outer peripheral surface of the surface and the inner member 41 with the contact A1 and the contact B1, and the driving force is transmitted from the outer member 43 to the inner member 41 (FIG. 26B). reference).

  The disengaged position in FIG. 22C is a position where the roller 42 has moved in the direction opposite to the rotation direction of the outer member 43 (counterclockwise in FIG. 22C), and the first connection is made at the moving end. The stopper 53a of the member 53 contacts the outer peripheral surface of the inner member 41 (see FIG. 26A). In this state, the roller 42 has a gap between the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41, but the pivot arm 51 is biased radially outward by the second springs 62 and 62. The roller 42 contacts the inner peripheral surface of the outer member 43 at the contact A3 and is slightly separated from the outer peripheral surface of the inner member 41, and the one-way clutch 44 is disengaged from the outer member 43 to the inner member 41. Transmission of the driving force is interrupted.

  The engagement start position in FIG. 22B is an intermediate position between the engagement position and the non-engagement position, and a first spring 59 that urges the pivot arm 51 to swing rightward in the drawing. With the elastic force of 59, the roller 42 comes into contact with the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41 at the contact A2 and the contact B2, but is not engaged, the roller 42 is engaged and the one-way clutch 44 is engaged. It will be in a state of preparation for matching. When the outer member 43 rotates relative to the clockwise direction in the drawing from this engagement start position, the roller 42 moves to the right in the drawing by the frictional force acting on the contact point A2, and the roller 42 moves between the inner peripheral surface of the outer member 43 and the inner member. The one-way clutch 44 is engaged with the outer peripheral surface of the member 41.

  As apparent from FIGS. 22 and 23, a cam member 70, which is a member different from the inner member 41, is fixed to the contact surface of the nine rollers 42 on the outer peripheral surface of the inner member 41 by press-fitting. That is, a notch 41a having a triangular cross section is formed on the outer peripheral surface of the inner member 41 corresponding to each roller 42, and a press-fit hole 41b is formed on the surface of the notch 41a on the engagement direction side of the roller 42. . On the other hand, the cam member 70 shaped to fit into the notch 41a is formed with a press-fit projection 70a having the same shape as the press-fit hole 41b, and a pressing surface 70b is provided at the end of the roller 42 in the disengagement direction. It is formed. Then, the cam member 70 is positioned in the notch 41a of the inner member 41, a load is applied to the pressing surface 70b, and the press-fitting protrusion 70a is press-fitted into the press-fitting hole 41b of the notch 41a of the inner member 41. The cam member 70 can be integrated.

  When the roller 42 is in the engagement start position, the cam surface of the cam member 70 corresponding to the contact B2 has a bottom extending in the axial direction of the roller 42 through the contact B, and the engagement direction of the roller 42 relative to the bottom. An isosceles triangular groove 70c having a vertex at a position shifted to is formed. Therefore, the width and the depth of the groove 70c are the largest at the central portion in the axial direction of the cam member 70, and become smaller from the both sides in the axial direction.

  Thus, by applying a press-fitting load to the pressing surface 70b when the cam member 70 is press-fitted, the cam surface of the cam member 70 (the surface that forms a wedge-shaped space in cooperation with the inner peripheral surface of the outer member 43) is damaged. There is no fear. Further, the shape of the cam surface of the cam member 70 is required to have high processing accuracy. However, if a total of nine cam surfaces and grooves are processed into the inner member 41 which is a relatively large member, the processing accuracy is reduced. In addition to being difficult to maintain, there is a problem of increased processing costs. On the other hand, by machining the cam surface and the groove 70c into the cam member 70 which is a relatively small member and press-fitting it into the inner member 41, the machining cost can be reduced while increasing the machining accuracy.

  As apparent from FIGS. 16 and 24, the engagement restricting means 71 for switching the eight one-way clutches 44 from the engageable state to the non-engageable state is movable in the axial direction on the outer periphery of the left axle 14. And a driven member 72 fitted non-rotatably and a drive member 73 fitted on the outer periphery of the driven member 72 so as not to move in the axial direction and rotatable. A pin implanted on the outer peripheral surface of the driven member 72 74 engages with a cam groove 73 a formed in the drive member 73. Therefore, when the drive gear 76 meshed with the driven gear 75 provided on the driven member 72 is driven to reciprocate by the motor 77, the pin 74 is guided to the cam groove 73a along with the rotation of the drive member 73, whereby the driven member 72 is driven. Reciprocates in the axial direction.

  A plate 79 that abuts the end surface of the driven member 72 via a thrust bearing 78 is urged toward the driven member 72 by a coil spring 80 that is contracted between the end surface of the output shaft 13 and thereby the driven member 72. Following the movement of 72 in the axial direction, the plate 79 moves in the axial direction. Nine control shafts 81 are slidably fitted in guide holes 41c (see FIGS. 18 and 24) formed in the eight inner members 41, and one end of these control shafts 81 is a plate. 79. Each control shaft 81 is formed with two circular cross-section movement restricting portions 81a and 81a and two semicircular cross-section notches 81b and 81b for one one-way clutch 44. Accordingly, a total of 16 movement restricting portions 81a ... and a total of 16 notches 81b ... are formed on one control shaft 81.

  Next, the operation of the one-way clutch 44 having the above configuration will be described. Note that the operation of the eight one-way clutches 44 is substantially the same except that the timing of engagement and disengagement is different, so the operation of the one one-way clutch 44 will be described.

  As shown in FIG. 22, in a state where the non-engaged one-way clutch 44 waits for engagement, as shown in FIG. 22 (B), the roller 42 is held in the vicinity of the meshing start position, and the outer member is connected at the contact A2. 43 is in contact with the inner peripheral surface of the inner member 41 and is in contact with the outer peripheral surface of the inner member 41 at the contact point B2.

  From this state, as shown by an arrow in FIG. 22 (A), when the outer member 43 rotates in the clockwise direction in the figure, the roller 42 urged rightward in the figure by the first springs 59, 59 (not shown). The roller 42 is driven in the right direction in the figure by the frictional force acting between the outer member 43 and the roller 42 in the space formed between the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41. The one-way clutch 44 is engaged at B1 and the driving force is transmitted from the outer member 43 to the inner member 41.

  In addition, when the outer member 43 rotates counterclockwise in the drawing as indicated by an arrow in FIG. 22C from the engaged state described above, the roller 42 is illustrated by the frictional force acting between the outer member 43 and the outer member 43. It moves in the left direction in the figure against the elastic force of the first springs 59, 59 and contacts the inner peripheral surface of the outer member 43 at the contact A3, but is separated from the outer peripheral surface of the inner member 41, thereby The clutch 44 is disengaged, and transmission of the driving force from the outer member 43 to the inner member 41 is interrupted.

  Now, when the roller 42 shifts from the meshing start position of FIG. 22B to the engagement position of FIG. 22A, if excessive oil is present at the contact B2 between the roller 42 and the cam member 70 of the inner member 41. There is a problem that the roller 42 slips and it becomes difficult to bite between the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41. Therefore, in this embodiment, the oil film of the contact B2 is quickly cut by the groove 70c of the cam member 70 to improve the engagement response of the one-way clutch 44.

  That is, in FIG. 22, when the roller 42 shifts from the meshing start position to the engagement position, the groove 70c exists at the position of the contact B2, so the contact area of the contact B2 is reduced by the amount of the groove 70c. By increasing the pressure, the oil film is cut, and slippage of the roller 42 is suppressed to facilitate engagement between the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41, thereby improving the engagement response of the one-way clutch 44. Can be increased.

  As the engagement of the one-way clutch 44 progresses and the possibility that the roller 42 slips decreases, the contact between the roller 42 and the cam member 70 moves from the bottom side to the apex side of the groove 70c of the isosceles triangle of the cam member 70. Therefore, the contact area between the roller 42 and the cam member 70 gradually increases and the contact surface pressure gradually decreases, and wear of the cam member 70 can be minimized.

  On the contrary, when the one-way clutch 44 is disengaged, the roller 42 is driven by the inner peripheral surface of the outer member 43 and rotates while passing over the groove 70c of the cam member 70. Therefore, the oil accumulated in the groove 70c is used. The outer peripheral surface of the roller 42 is lubricated, and the durability of the roller 42 that contacts the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41 can be ensured.

  By the way, the one-way clutch 44 of the present embodiment is used in the continuously variable transmission T and repeats engagement and disengagement at intervals of several hundred to several thousand times per minute. Sex is required. In the present embodiment, various techniques are employed to improve the engagement response of the one-way clutch 44.

  First, in order to improve the engagement response of the one-way clutch 44, it is necessary to maintain the position of the roller 42 at the time of non-engagement in the vicinity of the engagement start position in FIG. The reason is that if the roller 42 is in the vicinity of the meshing start position, the outer member 43 is rotated in the direction of the arrow in FIG. This is because the surface and the outer peripheral surface of the inner member 41 can be immediately bitten. However, when the one-way clutch 44 is in the non-engaged state, if the degree of freedom is too high in the position of the roller 42, the roller 42 is moved to the outer member 43 when the outer member 43 rotates in the direction of the arrow in FIG. The inner peripheral surface of the inner member 41 and the outer peripheral surface of the inner member 41 cannot be immediately bitten, and the engagement responsiveness decreases.

  Therefore, in the present embodiment, the roller 42 is pivotally supported on the radially outer end of the pivot arm 51 pivotally supported on the inner member 41 by the fulcrum pin 57 on the inner member 41, and the pivot arm 51 is moved to the first end. Since the springs 59 and 59 are urged in the engagement direction, the movable region of the roller 42 is restricted on the swinging locus of the pivot arm 51 to restrict the degree of freedom of the position, so that the vicinity of the meshing start position is obtained. keeping.

  Further, when the one-way clutch 44 is engaged, the roller 42 is moved from the meshing start position to the engagement position by the frictional force acting between the inner circumferential surface of the outer member 43, so that the roller 42 is moved to the inner circumferential surface of the outer member 43. It must be in contact with the surface. In order to satisfy this requirement, in this embodiment, the long holes 52d and 52d at the radially inner end of the pivot arm 51 are supported by the fulcrum pin 57 so as to be movable in the radial direction, and the pivot arm 51 is supported by the second springs 62 and 62. The roller 42 is reliably brought into contact with the inner peripheral surface of the outer member 43 from the non-engagement position to the meshing start position, and the roller 42 is reliably secured by the frictional force received from the outer member 43. Are engaged with the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41.

  At this time, the first springs 59 and 59 do not urge the roller 42 directly, and urge the roller 42 via the pivot arm 51, so that the degree of freedom of the position where the first springs 59 and 59 are provided is increased. The first springs 59, 59 can be prevented from coming into direct contact with the roller 42, and the durability against wear can be enhanced.

  When the one-way clutch 44 is in the engaged state, the nine rollers 42 are engaged between the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41. And the coaxial property of the inner member 41 is maintained. However, when the one-way clutch 44 is in the disengaged state, a gap is generated between the rollers 42 and the outer peripheral surface of the inner member 41 (see FIG. 22C). In addition, the coaxiality of the inner member 41 is not ensured, and the roller 42 cannot be properly held at the meshing start position, and the engagement response may be lowered.

  However, since the inner races 68b and 68b of the roller bearings 68 and 68 provided on the inner peripheral surface of the outer member 43 are coupled to the tips of the three support members 67 extending radially outward from the inner member 41, The coaxiality of the outer member 43 and the inner member 41 can be forcibly ensured and the engagement responsiveness of the one-way clutch 44 can be enhanced.

  At this time, if the three supporting members 67 are extended radially outward from the inner member 41, the supporting members 67 may interfere with any of the nine rollers 42, and layout may become difficult. However, in the present embodiment, the nine rollers 42 are separated into three groups of three, and the support members 67 are arranged in the gaps between adjacent groups, so that the above-mentioned problem of layout is solved. Can do.

  Further, when the one-way clutch 44 repeats engagement and disengagement, the nine rollers 42 move in the engagement direction and the disengagement direction all at once, but the movement of the rollers 42 varies. This will cause a decrease in response.

  However, in this embodiment, since the adjacent ones of the nine pivot arms 51 are connected by the tension coil springs 69, the nine pivot arms 51 are aligned in the same phase and moved in the circumferential direction. By making it easy, the engagement responsiveness of the one-way clutch 44 can be improved.

  Further, when the engaged one-way clutch 44 (see FIG. 26 (B)) is disengaged, the frictional force received from the outer member 43 engaged with the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41. It is pushed out in the disengagement direction, but its moving end is restricted by the stopper 53 a of the first connecting member 53 of the pivot arm 51 coming into contact with the outer peripheral surface of the inner member 41. At this time, if the stopper 53a strongly repels the outer peripheral surface of the inner member 41, the pivot arm 51 swings in the engaging direction, and the roller 42 collides with the inner peripheral surface of the outer member 43 to repel it. By repeating, it becomes difficult for the roller 42 to converge to the meshing start position, which may cause a decrease in engagement response.

  However, according to the present embodiment, the stopper 53a of the first connecting member 53 is made of a synthetic resin having a low coefficient of restitution, so that it strongly repels when the stopper 53a collides with the outer peripheral surface of the inner member 41. This makes it possible to improve the engagement responsiveness of the one-way clutch 44 by quickly converging the roller 42 in the vicinity of the meshing start position. In addition, since the swinging end of the pivot arm 51 in the disengagement direction of the pivot arm 51 is regulated by the stopper 53a, the position of the pivot arm 51 is prevented from greatly deviating from the meshing start position, and the engagement responsiveness of the one-way clutch 44 is further enhanced. be able to.

As shown in FIG. 28A, when the pivot arm 51 is in the engagement start position, the direction of the pivot arm 51 is shifted from the radial direction around the output shaft 13 to the engagement direction (clockwise). When the pivot arm 51 swings in the disengagement direction (counterclockwise) from the engagement start position and the direction of the pivot arm 51 coincides with the radial direction centering on the output shaft 13 (maximum compression position), the pivot arm Since the position of the fulcrum pin 57 of 51 is shifted in the radial direction from the position of the output shaft 13, the movement locus of the roller 42 does not match the shape of the inner peripheral surface of the outer member 43. Therefore, while the pivot arm 51 swings from the meshing start position toward the maximum compression position, the length of the pivot arm 51 is shortened and the second springs 62 and 62 are compressed, and the first compression position is reached at the maximum compression position. 2 The spring force of the springs 62 and 62 is maximized.
In FIG. 28B, the horizontal axis represents the pivot angle of the pivot arm 51, and the vertical axis represents the length of the pivot arm 51 or the elastic force of the second springs 62, 62. Is swung in the disengagement direction from the mesh start position, the resilience of the second springs 62, 62 increases to the maximum compression position where the length of the pivot arm 51 is minimized, and when the maximum compression position is exceeded, It can be seen that the resilience of the two springs 62, 62 starts to decrease.

  The pivot arm 51 is urged in the engaging direction by a substantially constant elastic force by the first springs 59, 59, but the pivot arm 51 is added to the second spring in addition to the urging force by the first springs 59, 59. The biasing force by the springs 62 and 62 is received.

  That is, the rotation direction of the outer member 43 is reversed from the state where the one-way clutch 44 is engaged and the roller 42 is engaged with the inner peripheral surface of the outer member 43 and the outer peripheral surface of the inner member 41. When the state shifts to the disengaged state, the roller 42 is pushed in the disengagement direction by the frictional force received from the outer member 43, and the pivot arm 51 swings in the disengagement direction via the meshing start position. At this time, since the pivot arm 51 is gradually compressed and the second springs 62 and 62 are compressed, the load that resists the swinging of the pivot arm 51 in the disengagement direction gradually increases. The swing speed in the disengagement direction is effectively attenuated.

  The load that resists the swinging of the pivot arm 51 in the disengagement direction gradually decreases after reaching the maximum in the maximum compression position, but the pivot arm 51 generates a load that is greater than the second springs 62, 62. Since the first springs 59 and 59 are biased in the engaging direction, the pivot arm 51 is swung in the disengaging direction, that is, until the stopper 53a of the first connecting member 53 collides with the outer peripheral surface of the inner member 41. Continue to slow down. Therefore, the reciprocation of the pivot arm 51 is achieved by sufficiently reducing the speed at which the stopper 53a of the first connecting member 53 collides with the outer peripheral surface of the inner member 41 and minimizing the rebound of the pivot arm 51 in the engaging direction. It is possible to improve the engagement response of the one-way clutch 44 by suppressing the vibration.

  Further, when the pivot arm 51 swings in the engagement direction after the stopper 53a collides with the outer peripheral surface of the inner member 41 and bounces back, the load of the second springs 62, 62 resisting the swing is applied by the pivot arm 51. Since it continues to increase until the maximum compression position is reached, the moving speed of the pivot arm 51 in the disengagement direction is decelerated and the reciprocating vibration is more effectively suppressed.

  When the stopper 53a of the first connecting member 53 collides with the outer peripheral surface of the inner member 41, the first connecting member 53 is made of synthetic resin having a low coefficient of restitution, so that the repelling speed of the pivot arm 51 is effectively increased. Can be reduced. In addition, since the first connecting member 53 including the stopper 53a also serves as a member for integrally connecting the pair of holders 52, 52, it can contribute to the reduction in the number of parts.

  By the way, the continuously variable transmission T according to the present embodiment does not have a function of establishing the reverse gear, so that when it is used for driving the front wheels as the main drive wheels, for example, the secondary drive A rear wheel which is a wheel is driven by an in-hole motor or the like. Therefore, the reverse of the vehicle is performed by driving the rear wheels in reverse with a motor.

  The relative rotation of the outer member 43 and the inner member 41 when such a hybrid vehicle slides backward when starting on an uphill slope or when the rear wheel is driven by a motor. Is the same as that during forward traveling by the engine E, and the one-way clutch 44 is engaged. As a result, the driving force is reversely transmitted from the wheel through the inner member 41 to the outer member 43, and the outer member 43 rotates in the reverse direction. However, the outer member 43 has a structure that can be reciprocally swung only within a predetermined angle range, and is not structured to be able to rotate over 360 °, and thus is damaged by the reversely transmitted driving force. there is a possibility. In order to prevent this, the engagement restricting means 71 may forcibly prohibit the engagement of the one-way clutch 44.

  As shown in FIG. 27A, when the notches 81b and 81b of the control shaft 81 of the engagement restricting means 71 are opposed to the pivot arm 51 of the one-way clutch 44, the pivot arm 51 interferes with the control shaft 81. Therefore, the one-way clutch 44 can be engaged and disengaged.

  When the motor 77 of the engagement restricting means 71 is driven from this state and the driving member 73 is rotated via the driving gear 76 and the driven gear 75, the pin 74 of the driven member 72 supported so as to be axially movable and non-rotatable. Is guided by the cam groove 73a of the drive member 73, the driven member 72 moves in the axial direction toward the left side in the figure as shown in FIG. As a result, the plate 79 pressed against the driven member 72 via the thrust bearing 78 by the elastic force of the coil spring 80 moves to the left in the figure following the driven member 72, and the driven member 72 is coupled. Nine control shafts 81 also move leftward in the figure.

  When each control shaft 81 moves to the left in the figure, instead of the notches 81b and 81b facing the pivot arm 51, the movement restricting portions 81a and 81a having a circular cross section abut against the pivot arm 51, and the pivot arm By restricting the swing of 51 in the engaging direction, it stops before the engagement start position. Thus, since the nine control shafts 81 can be simultaneously driven by the common engagement restricting means 71, the engagement state of the eight one-way clutches 44 is synchronized by one motor 77. It can be controlled all at once. Thus, the engagement of the one-way clutch 44... Can be prohibited and the vehicle can be moved backward.

  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 44 of the present invention is not limited to the continuously variable transmission T of the embodiment.

  In the embodiment, the groove 70c is formed on the inner member 41 side, but the groove 70c can be formed on the outer member 43 side.

  In the embodiment, the groove 70 c is formed in the cam member 70, but the groove 70 c may be formed directly in the inner member 41.

  Although the one-way clutch 44 of the embodiment includes the pivot arm 51, the present invention can be applied to the one-way clutch 44 that does not have the pivot arm 51.

41 Inner member 42 Roller 43 Outer member 59 First spring (spring)
70c groove

Claims (1)

A plurality of rollers (42) arranged in an annular space formed between the inner peripheral surface of the outer member (43) and the outer peripheral surface of the inner member (41) are biased in the circumferential direction by a spring (59). Then, due to the relative rotation of the outer member (43) and the inner member (41) in a predetermined direction, the roller (42) is moved to the inner peripheral surface of the outer member (43) and the outer peripheral surface of the inner member (41). In the one-way clutch that transmits the driving force by biting between
At least one of the outer member (43) and the inner member (41) with which the roller (42) at the meshing start position comes into contact, the shaft of the roller (42) toward the meshing direction of the roller (42) A one-way clutch characterized in that a groove (70c) having a reduced width in the direction is formed.

Images