JP2018162814A - Two-way clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a two-way clutch which is reduced in size and achieved in power saving.SOLUTION: A two-way clutch comprises: a first member connected to an input shaft, and having a prescribed first face; a second member connected to an output shaft, and having a second face opposing the first face in an axial line direction; a first engagement piece interposed between the first face and the second face, and transmitting torque in a forward direction from the first member to the second member; a second engagement piece for transmitting torque in a reverse direction from the first member to the second member; a spring for energizing the first engagement piece and the second engagement piece to the axial line direction in which the first engagement piece and the second engagement piece are engaged with each other; and a cam mechanism for converting the torque of the input shaft to a force in the axial direction, and making the first engagement piece and the second engagement piece non-engageable with each other by elastically deforming the space.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a two-way clutch that transmits or interrupts torque between an input shaft and an output shaft.

  As a two-way clutch that transmits or interrupts torque between an input shaft and an output shaft, techniques disclosed in Patent Document 1 and Patent Document 2 are known. The two-way clutch disclosed in Patent Document 1 or Patent Document 2 includes a first member coupled to the input shaft, a second member coupled to the output shaft and opposed to the first member in the axial direction, and a first member. A first engagement element and a second engagement element which are interposed between the second member and engage the first member and the second member; and a drive device which restricts the operation of the first engagement element and the second engagement element. It is equipped with. The drive device includes a solenoid that converts electric energy into mechanical motion using electromagnetic force, and a switching mechanism that switches whether the first engagement element and the second engagement element are engaged by the mechanical movement of the solenoid. .

Japanese Patent No. 5145019 International Publication No. 2015/001642

  However, since the conventional technology includes the solenoid, there are problems that the two-way clutch is enlarged and the power consumption of the solenoid is generated.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a two-way clutch that achieves miniaturization and power saving.

  In order to achieve this object, the two-way clutch of the present invention switches between transmission and interruption of torque between the input shaft and the output shaft. The first member coupled to the input shaft has a predetermined first surface, and the second member coupled to the output shaft has a second surface facing the first surface in the axial direction. A first engagement element interposed between the first surface and the second surface engages the first member and the second member, and transmits torque in the forward rotation direction from the first member to the second member. A second engagement element interposed between the first surface and the second surface engages the first member and the second member, and transmits torque in the reverse direction from the first member to the second member. The spring biases the first engagement element and the second engagement element in the axial direction in which the first engagement element and the second engagement element are engaged. The cam mechanism converts the torque of the input shaft into an axial force, and elastically deforms the spring to make the first engagement element and the second engagement element impossible to engage.

  According to the two-way clutch of the first aspect, the first engagement element and the second engagement element are biased by the spring in the axial direction in which the first engagement element and the second engagement element are engaged. By converting the torque of the input shaft into axial force by the cam mechanism, the spring is elastically deformed so that the first engagement element and the second engagement element cannot be engaged. As a result, the solenoid can be dispensed with. Therefore, the two-way clutch can be reduced in size and power can be saved as much as the solenoid can be omitted.

  According to the two-way clutch of the second aspect, the cam mechanism includes the first cam, the second cam, and the third cam. The first cam is disposed so as to be movable with respect to the input shaft in the axial direction relative to the first engagement element and rotates integrally with the input shaft. The second cam is disposed so as to be movable relative to the input shaft and the first cam in the axial direction with respect to the second engagement element, and rotates integrally with the input shaft. The third cam is disposed so as to be rotatable about the axis and immovable in the axial direction while facing the first cam and the second cam in the axial direction.

  Thus, when the input shaft rotates and the first cam and the second cam rotate, the third cam rotates via the first ball or the second ball. The first ball interposed between the third cam and the first cam increases the axial distance between the third cam and the first cam by the relative rotation with the third cam in the reverse rotation direction of the first cam. 1 Engagement element is disabled. The second ball interposed between the third cam and the second cam increases the axial distance between the third cam and the second cam by relative rotation with the third cam in the forward rotation direction of the second cam. The second engagement element is disabled. Therefore, in addition to the effect of the first aspect, the rotary motion is converted into the axial motion by the cam mechanism, the torque of the input shaft in the forward rotation direction is transmitted to the output shaft through the first engagement element, and the second engagement element. The torque of the input shaft in the reverse direction can be transmitted to the output shaft via the.

  According to the two-way clutch of the third aspect, the engaging portion is provided on the third cam. The mass body moves in a direction away from the engaging portion by centrifugal force while rotating integrally with the third cam by friction with the engaging portion. The elastic body urges the mass body in a direction approaching the engaging portion. Therefore, when the third cam has a low rotation speed, the mass body and the elastic body cause the first cam to rotate. The inertial mass of 3 cams can be increased. Therefore, in addition to the effect of claim 2, when the rotation speed of the third cam is low, the cam mechanism is operated by generating the relative rotation between the first cam and the second cam and the third cam necessary for the operation of the cam mechanism. In addition, it is possible to reduce friction when the rotation speed of the third cam is high.

  According to the two-way clutch of the fourth aspect, the friction material imparts a frictional force against the fixed element to the third cam, so that the relative relationship between the first cam, the second cam, and the third cam necessary for the operation of the cam mechanism. Rotation can be generated. Therefore, in addition to the effect of the second or third aspect, the cam mechanism can be easily operated when the rotational speed of the input shaft is low.

  According to the two-way clutch of the fifth aspect, since the braking mechanism applies a frictional force in the rotational direction to the mass body, in addition to the effect of the third aspect, the friction when the rotation speed of the third cam is high is reduced. However, the cam mechanism can be more easily operated when the rotation speed of the third cam is low.

  According to the two-way clutch of the sixth aspect, the cam mechanism is axially arranged so that the first engagement element and the second engagement element are disengaged when the rotation direction of the first cam is switched from the reverse rotation direction to the normal rotation direction. The amount of movement is set. Therefore, in addition to the effect of any one of claims 2 to 5, it is possible to prevent the first engagement element and the second engagement element from engaging at the same time.

  According to the two-way clutch of the seventh aspect, the cam mechanism moves in the axial direction so that the first engagement element and the second engagement element are engaged when the rotation direction of the first cam is switched from the reverse rotation direction to the normal rotation direction. The amount is set. Therefore, in addition to the effect of any one of claims 2 to 6, the first member and the second member can be quickly synchronized.

It is sectional drawing of the two-way clutch in one embodiment of this invention. It is sectional drawing of the two-way clutch in the II-II line of FIG. (A) is sectional drawing of the two-way clutch in the IIIa-IIIa line | wire of FIG. 1, (b) is a front view of a 1st engagement element, (c) is a side view of a 1st engagement element. (A) is a schematic diagram of a 3rd cam, (b) is a schematic diagram of another 3rd cam. It is sectional drawing of the two-way clutch in the VV line | wire of FIG. (A) is a schematic diagram of the two-way clutch in which the forward rotation direction torque is input to the input shaft, and (b) is a schematic diagram of the two-way clutch in which the reverse rotation direction torque is input to the input shaft.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. First, the two-way clutch 10 according to the first embodiment of the present invention will be described with reference to FIG. FIG. 1 is a cross-sectional view of a two-way clutch 10 according to an embodiment of the present invention. The two-way clutch 10 is mounted on a vehicle in the present embodiment.

  As shown in FIG. 1, the two-way clutch 10 is a device for transmitting or blocking torque between the input shaft 11 and the output shaft 12 arranged on the same axis O. The two-way clutch 10 includes a first member 20 coupled to the input shaft 11, a second member 30 coupled to the output shaft 12, and a first engagement element that engages the first member 20 and the second member 30. 40 and the second engaging element 50, springs 43 and 53 for urging the first engaging element 40 and the second engaging element 50 in the direction in which the first member 20 and the second member 30 are engaged, and the springs 43 and 53, respectively. And a cam mechanism 60 that releases the engagement of the first engagement element 40 and the second engagement element 50 against the elastic force.

  The first member 20 will be described with reference to FIG. 2 is a cross-sectional view of the two-way clutch 10 taken along the line II-II in FIG. The first member 20 is a substantially annular member that is coupled to the input shaft 11 and whose inner periphery is rotatably supported by the output shaft 12 by a bearing 13. The first surface 21 of the first member 20 is a flat surface orthogonal to the axis O. A cylindrical portion 22 extending in the direction of the axis O is coupled to the first member 20 on the outer periphery of the first surface 21.

  In the first member 20, annular grooves 23 and 26 having different diameters are formed on the first surface 21. The first surface 21 has a plurality (eight in this embodiment) of first recesses 24 formed on the groove 23 and a plurality (eight in this embodiment) of second recesses 27 formed on the groove 26. Has been. The diameter of the groove 26 is smaller than the diameter of the groove 23. In the first member 20, a through hole 25 penetrating the first member 20 in the thickness direction (axis O direction) is formed on the groove 23 in the first recess 24, and the first member 20 is formed in the thickness direction. A through hole 28 is formed on the groove 26 in the second recess 27.

  The first concave portion 24 is a portion into which a main body portion 41 (described later) of the first engagement element 40 that is swingably supported by the second member 30 enters. The second concave portion 27 is a portion into which a main body portion 51 (described later) of the second engaging member 50 that is swingably supported by the second member 30 enters. The first recess 24 and the second recess 27 have openings that are substantially rectangular when viewed from the front, and are formed on the circumferences of the grooves 23 and 26 at substantially equal intervals. The radial widths of the first recess 24 and the second recess 27 are slightly larger than the widths of the main body 41 of the first engagement element 40 and the main body 51 of the second engagement element 50. Accordingly, the main body portions 41 and 51 can enter the first recess portion 24 and the second recess portion 27.

  The groove 23 is a part for accommodating the ring member 44 (see FIG. 1) so as to be movable in the circumferential direction and the axis O direction, and the groove 26 is capable of moving the ring member 54 (see FIG. 1) in the circumferential direction and the axis O direction. It is a part to accommodate. Each of the grooves 23 and 26 has a rectangular cross section in a cross section including the axis O. The through holes 25 and 28 are portions into which the pins 45 and 55 (see FIG. 1) are slidably fitted. The pins 45 and 55 transmit the force of the cam mechanism 60 to the ring members 44 and 54. The ring members 44 and 54 restrict the swinging of the first engagement element 40 and the second engagement element 50.

  The second member 30 will be described with reference to FIG. FIG. 3A is a cross-sectional view of the two-way clutch 10 taken along line IIIa-IIIa in FIG. The second member 30 is a substantially annular member that is coupled to the output shaft 12 by a spline. The second member 30 is disposed inside the cylindrical portion 22 (see FIG. 1). The movement of the second member 30 in the direction of the axis O relative to the first member 20 is restricted by the restriction member 14 (see FIG. 1) fixed to the cylindrical portion 22. The second surface 31 of the second member 30 is a flat surface orthogonal to the axis O. The second surface 31 faces the first surface 21 of the first member 20 in the axis O direction.

  The second surface 31 has a plurality of (eight in the present embodiment) first accommodating portions 32 formed at positions corresponding to the first recesses 24 of the first surface 21 (see FIG. 2). A plurality of (eight in the present embodiment) second accommodating portions 36 are formed at positions corresponding to the second concave portions 27 of the surface 21. The first engaging element 40 is accommodated in the first accommodating part 32, and the second engaging element 50 is accommodated in the second accommodating part 36.

  The first engaging element 40 and the second engaging element 50 will be described with reference to FIGS. 3B and 3C. FIG. 3B is a front view of the first engagement element 40, and FIG. 3C is a side view of the first engagement element 40. The first engagement element 40 and the second engagement element 50 are configured in the same manner except that the circumferential direction arranged on the second member 30 is different. Therefore, each part of the 1st engagement element 40 is demonstrated and description of each part of the 2nd engagement element 50 is abbreviate | omitted.

  The first engagement element 40 is a plate-like body that is substantially T-shaped when viewed from the front, and protrudes from the both side edges of the end portion of the main body 41 and the main body 41 formed in a substantially rectangular shape when viewed from the front. And a substantially rod-shaped arm portion 42 provided. The first engagement element 40 and the second engagement element 50 transmit torque in different directions.

  Returning to FIG. The first housing portion 32 includes a main body housing portion 33 that is a shallow depression in which the main body portion 41 of the first engagement element 40 is accommodated, and an arm housing portion 34 that is a shallow depression in which the arm portion 42 is accommodated. . The arm accommodating portion 34 is connected to the main body accommodating portion 33. The first accommodating portion 32 is arranged with the arm accommodating portion 34 facing inward and outward in the radial direction in a state where the main body accommodating portions 33 are arranged in the circumferential direction.

  In the first housing portion 32, a spring housing portion 35, which is a depression deeper than the main body housing portion 33, is connected to the main body housing portion 33 on the side opposite to the arm housing portion 34. A spring 43 (see FIG. 1) is accommodated in the spring accommodating portion 35. The circumferential length obtained by adding the spring accommodating portion 35 to the main body accommodating portion 33 is that the main body portion 41 of the first engaging element 40 is accommodated in the main body accommodating portion 33 and the spring accommodating portion 35. It is slightly longer than the length of the portion 41. As for the 1st accommodating part 32 adjacent to the circumference direction, the arm accommodating part 34 and the spring accommodating part 35 face each other. In the present embodiment, the spring 43 is a torsion coil spring, but is not limited thereto. It is naturally possible to use a compression coil spring or the like instead of the torsion coil spring.

  The second housing portion 36 includes a main body housing portion 37 that is a shallow depression in which the main body portion 51 of the second engagement element 50 is accommodated, and an arm housing portion 38 that is a shallow depression in which the arm portion 52 is accommodated. . The arm accommodating portion 38 is connected to the main body accommodating portion 37. The second accommodating portion 36 is arranged with the arm accommodating portions 38 facing inward and outward in the radial direction in a state where the main body accommodating portions 37 are arranged in the circumferential direction.

  In the second housing portion 36, a spring housing portion 39, which is a depression deeper than the main body housing portion 37, is connected to the main body housing portion 37 on the side opposite to the arm housing portion 38. A spring 53 (see FIG. 1) is accommodated in the spring accommodating portion 39. In the present embodiment, the spring 53 is a torsion coil spring. The circumferential length of the spring accommodating portion 39 added to the main body accommodating portion 37 is that the main body 51 of the second engaging member 50 is accommodated in the main body accommodating portion 37 and the spring accommodating portion 39. It is slightly longer than the length of the part 51. As for the 2nd accommodating part 36 adjacent to the circumferential direction, the arm accommodating part 38 and the spring accommodating part 39 face each other. The 2nd accommodating part 36 and the 1st accommodating part 32 are arrange | positioned by making the direction of the circumferential direction mutually differ.

  As shown in FIG. 1, the first engaging element 40 and the spring 43 are accommodated in the first accommodating part 32 of the second member 30, and the second engaging element 50 and the spring 53 are accommodated in the second accommodating part 36. On the other hand, the ring members 44 and 54 are accommodated in the grooves 23 and 26 of the first member 20, respectively. The second member 30 is assembled to the first member 20 such that the second surface 31 of the second member 30 faces the first surface 21 of the first member 20.

  When the first engagement element 40 comes to the position of the first recess 24 due to the relative rotation of the first member 20 and the second member 30, the two-way clutch 10 is moved to the arm of the first engagement element 40 by the elastic force of the spring 43. The main body 41 swings about the part 42 as an axis, and the end of the main body 41 enters the first recess 24. Similarly, when the second engagement element 50 comes to the position of the second recess 27, the main body part 51 swings around the arm part 52 of the second engagement element 50 by the elastic force of the spring 53, and the main body part 51. The end portion enters the second recess 27.

  On the other hand, when a cam mechanism 60 (see FIG. 1), which will be described later, pushes the pins 45 and 55 fitted in the through holes 25 and 28 toward the first concave portion 24 and the second concave portion 27, the cam mechanism 60 is accommodated in the grooves 23 and 26. The ring members 44 and 54 are pushed into the first recess 24 and the second recess 27. The ring members 44 and 54 pushed into the first recess 24 and the second recess 27 prevent the first engagement element 40 and the second engagement element 50 from entering the first recess 24 and the second recess 27.

  Next, the cam mechanism 60 (see FIG. 1) will be described. The cam mechanism 60 is a mechanism that restricts the operations of the first engagement element 40 and the second engagement element 50. The cam mechanism 60 includes a first cam 61 disposed in the axis O direction with respect to the first engagement element 40, a second cam 63 disposed in the axis O direction with respect to the second engagement element 50, the first cam 61, and the second cam 61. And a third cam 65 facing the cam 63. A plurality of first balls 68 are interposed between the first cam 61 and the third cam 65, and a plurality of second balls 69 are interposed between the second cam 63 and the third cam 65.

  The first cam 61 is an annular member disposed so as to surround the input shaft 11 on the opposite side of the second member 30 across the first member 20. The first cam 61 rotates integrally with the cylindrical portion 22 by the engagement of the cylindrical portion 22 and the spline formed in the first cam 61, and is movable in the direction of the axis O with respect to the cylindrical portion 22. Arranged inside. The first cam 61 is formed with a cam groove 62 that opens to the opposite side of the first member 20. The cam grooves 62 are, for example, triangular grooves extending in the radial direction, and a plurality of cam grooves 62 are provided at intervals in the circumferential direction.

  The second cam 63 is an annular member disposed on the opposite side of the second member 30 across the first member 20 and on the inner side (axis O side) of the first cam 61. The second cam 63 surrounds the input shaft 11. The second cam 63 rotates integrally with the input shaft 11 by engagement of the splines formed on the input shaft 11 and the second cam 63, and is movable with respect to the input shaft 11 in the axis O direction. Arranged outside. The second cam 63 is movable in the axis O direction with respect to the first cam 61. The second cam 63 is formed with a cam groove 64 that opens to the opposite side of the first member 20. The cam grooves 64 are, for example, triangular grooves extending in the radial direction, and a plurality of cam grooves 64 are provided at intervals in the circumferential direction.

  The third cam 65 is an annular member that faces the first cam 61 and the second cam 63. The third cam 65 surrounds the input shaft 11. The third cam 65 is disposed inside the cylindrical portion 22 so as to be rotatable with respect to the input shaft 11 and the cylindrical portion 22. The movement of the third cam 65 in the direction of the axis O toward the opposite side of the first member 20 is restricted by an annular bearing 70 fixed to the cylindrical portion 22. The third cam 65 is formed with cam grooves 66 and 67 that open to the first member 20 side. The cam groove 66 is provided at a position facing the cam groove 62 of the first cam 61, and the cam groove 67 is provided at a position facing the cam groove 64 of the second cam 63. The cam grooves 66 and 67 are, for example, triangular grooves extending in the radial direction.

  The first cam 61, the second cam 63, and the third cam 65 are provided with a phase difference in the rotational direction. The first cam 61, the second cam 63, and the third cam 65 can rotate relative to each other while receiving the reaction force of the first ball 68 and the second ball 69 by the amount of the phase difference. When the first ball 68 or the second ball 69 is engaged with the first cam 61 or the second cam 63 and the third cam 65 by the relative rotation of the first cam 61 and the second cam 63 and the third cam 65, The first cam 61 or the second cam 63 and the third cam 65 rotate integrally. Since the third cam 65 is restricted from moving in the direction of the axis O, if there is a rotational difference between the first cam 61, the second cam 63, and the third cam 65, the first cam 61 or the second cam 63 is moved to the axis. Move in the O direction (second member 30 side).

  FIG. 4A is a schematic diagram (cam diagram) of the third cam 65. In FIG. 4A, the cam grooves 66 and 67 of the third cam 65 are shown on the left and right with the rotation angle around the axis O being aligned. An arrow F shown in FIG. 4A indicates the rotation direction (forward rotation direction) of the input shaft 11 (see FIG. 1) (the same applies to FIG. 4B).

  As shown in FIG. 4A, the direction of inclination of the cam groove 66 in the rotational direction is opposite to the direction of inclination of the cam groove 67 in the rotational direction. Due to the relative rotation of the second cam 63 (see FIG. 1) and the third cam 65 (in the direction of arrow F), the second ball 69 moves along the inclination of the cam groove 67 on the first member 20 side in the axis O direction (FIG. 4). When approaching (a) right side), the second ball 69 pushes the cam groove 64 (see FIG. 1) in the direction of the axis O, and the second cam 63 moves in the direction of the axis O so as to move away from the third cam 65. When the second cam 63 rotates, the first cam 61 also rotates. However, since the cam groove 66 is inclined in the opposite direction to the cam groove 67, the first ball 68 is moved to the first cam 61 (see FIG. 1). ) Is not moved in the direction of the axis O.

  Thereby, as shown in FIG. 1, the second cam 63 pushes the pin 55 fitted in the through hole 28 toward the second recess 27, and pushes the ring member 54 accommodated in the groove 26 into the second recess 27. The ring member 54 pushed into the second recess 27 prevents the second engaging element 50 from entering the second recess 27.

  On the contrary, as shown in FIG. 4 (a), the relative rotation of the first cam 61 (see FIG. 1) and the third cam 65 (counter arrow F direction) causes the cam groove 66 to follow the inclination. When the first ball 68 approaches the first member 20 side (right side in FIG. 4A) in the axis O direction, the first ball 68 pushes the cam groove 62 (see FIG. 1) in the axis O direction, and the first cam 61 Moves in the direction of the axis O so as to move away from the third cam 65. When the first cam 61 rotates, the second cam 63 also rotates. However, since the cam groove 67 is inclined in the opposite direction to the cam groove 66, the second ball 69 is in contact with the second cam 63 (see FIG. 1). ) Is not moved in the direction of the axis O.

  Thereby, as shown in FIG. 1, the first cam 61 pushes the pin 45 fitted in the through hole 25 toward the first recess 24, and pushes the ring member 44 accommodated in the groove 23 into the first recess 24. The ring member 44 pushed into the first recess 24 prevents the first engagement element 40 from entering the first recess 24.

  4A is a position where the first cam 61 and the second cam 63 do not push the pins 45 and 55 toward the first member 20 (the positions of the bottoms of the cam grooves 66 and 67). Are set to have the same rotation angle. That is, when the cam mechanism 60 switches the rotation direction of the first cam 61 from the reverse rotation direction (counter arrow F direction) to the normal rotation direction (arrow F direction), the first engagement element 40 and the second engagement element 50 are engaged with each other. The amount of movement in the axial direction is set in. After the first engagement element 40 and the second engagement element 50 are engaged with the first recess 24 and the second recess 27, respectively, the engagement of the second engagement element 50 is released, so that the first cam 61, the second cam 63 and the third engagement element are disengaged. By relative rotation with the cam 65, the first engagement element 40 or the second engagement element 50 can be easily engaged with the first recess 24 or the second recess 27 (play can be reduced). Therefore, the first member 20 and the third member 30 can be quickly synchronized.

  As shown in FIG. 1, the third cam 65 is provided with an engaging portion 71 on the surface opposite to the surface on which the cam groove 66 is formed. In the present embodiment, the engaging portion 71 is a cylindrical portion that protrudes in the direction of the axis O from the radial center of the third cam 65, and the engaging portion 71 is coupled to the third cam 65.

  FIG. 5 is a sectional view of the two-way clutch 10 taken along the line V-V in FIG. As shown in FIG. 5, the third cam 65 has a mass body 72 attached to the engaging portion 71. The mass bodies 72 are members for increasing the inertial mass of the third cam 65, and each is formed in a substantially sector shape when viewed from the direction of the axis O. A plurality of mass bodies 72 (two in the present embodiment) are arranged around the engaging portion 71 at intervals in the circumferential direction. In the mass body 72, the contact surface 73 comes into contact with the outer periphery of the engaging portion 71. An elastic body 75 is wound around a circumferentially extending groove 74 formed on the outer periphery of the mass body 72. The groove 74 restricts the movement of the elastic body 75 in the axis O direction. In the present embodiment, the elastic body 75 is formed in an annular shape by hooking hooks provided at both ends of the tension coil spring.

  The braking mechanism 80 (see FIG. 1) includes a friction material 82 fixed to the case 81. The friction material 82 contacts the end surface of the mass body 72 in the direction of the axis O, and restricts the rotation of the mass body 72. The mass body 72 is biased by the elastic body 75 in a direction approaching the engaging portion 71 (inside in the radial direction), and the contact surface 73 is pressed against the engaging portion 71. Therefore, when the third cam 65 and the engaging portion 71 are stationary or when the rotation speed of the third cam 65 and the engaging portion 71 is low, the third cam 65 and the engaging portion 71 are not connected to the first cam 61 or the first cam 61. A braking force can be applied to the third cam 65 so as not to rotate together with the two cams 63. Since the inertial mass of the third cam 65 can be increased by the mass body 72, when the first cam 61 and the second cam 63 rotate relative to each other by the phase difference, the first ball 68 or the second ball 69 is moved to the first cam. 61 or the second cam 63 and the third cam 65 can be easily engaged.

  On the other hand, the first ball 68 or the second ball 69 is engaged with the first cam 61 or the second cam 63 and the third cam 65, and the first cam 61 or the second cam 63 and the third cam 65 are integrated. When the rotation speed of the third cam 65 and the engaging portion 71 increases, the center of gravity of the mass body 72 moves away from the engaging portion 71 by the centrifugal force against the elastic force of the elastic body 75 (radial direction). To the outside). When the frictional force between the contact surface 73 of the mass body 72 and the engaging portion 71 becomes small, the engaging portion 71 slides with respect to the mass body 72. Thereby, the moment of inertia of the third cam 65 that rotates integrally with the first cam 61 or the second cam 63 can be reduced, so that loss due to friction can be reduced.

  Next, the operation of the two-way clutch 10 will be described with reference to FIG. FIG. 6A is a schematic diagram of the two-way clutch 10 in which torque in the forward rotation direction (arrow F direction) is input to the input shaft 11. FIG. 6B is a schematic diagram of the two-way clutch 10 in which torque in the reverse rotation direction (arrow R direction) is input to the input shaft 11.

  As shown in FIG. 6A, the first engaging element 40 and the second engaging element 50 are urged toward the first member 20 by springs 43 and 53, respectively. The first ball 68 between the cam groove 62 of the first cam 61 and the cam groove 66 of the third cam 65 that rotates integrally with the input shaft 11 rotates in the forward rotation direction (arrow F direction), thereby forming the cam groove. The first cam 61 moves away from the first member 20 by engaging with 62 and 66. On the other hand, since the cam groove 64 of the second cam 63 is out of phase with the cam groove 62 of the first cam 61, the reaction force of the second ball 69 between the third cam 65 and the second cam 63 causes The two cams 63 approach the first member 20.

  The second cam 63 pushes the pin 55 toward the first member 20 against the elastic force of the spring 53, and the ring member 54 pushed by the pin 55 causes the main body 51 of the second engagement element 50 to move to the second member. It accommodates in the 30 2nd accommodating part 36. Since the second engagement element 50 cannot swing into the second recess 27, torque transmission by the second engagement element 50 is interrupted.

  On the other hand, the first engagement element 40 biased by the spring 43 swings and enters the first recess 24. Therefore, torque in the forward rotation direction (arrow F direction) is transmitted from the first member 20 to the second member 30 by the first engagement element 40.

  From this state, when the rotation of the input shaft 11 is slowed down or the output shaft 12 is rotated fast, and the rotational speed of the second member 30 is higher than the rotational speeds of the first cam 61 and the second cam 63, the first engagement element. Since the main body 41 of 40 cannot engage with the first recess 24, torque transmission is interrupted.

  As shown in FIG. 6B, the second ball 69 between the cam groove 64 of the second cam 63 and the cam groove 67 of the third cam 65 that rotates integrally with the input shaft 11 moves in the reverse direction (arrow R). , The second cam 63 moves away from the first member 20. On the other hand, since the cam groove 62 of the first cam 61 is out of phase with the cam groove 64 of the second cam 63, the reaction force of the first ball 68 between the third cam 65 and the first cam 61 causes One cam 61 approaches the first member 20.

  The first cam 61 pushes the pin 45 toward the first member 20 against the elastic force of the spring 43, and the ring member 44 pushed by the pin 45 causes the main body portion 41 of the first engagement element 40 to move to the second member. It accommodates in the 30 1st accommodating part 32. FIG. Since the first engagement element 40 cannot swing into the first recess 24, torque transmission by the first engagement element 40 is interrupted.

  On the other hand, the second engagement element 50 biased by the spring 53 swings and enters the second recess 27. Therefore, torque in the reverse rotation direction (arrow R direction) is transmitted from the first member 20 to the second member 30 by the second engagement element 50.

  From this state, when the rotation of the input shaft 11 slows down or the output shaft 12 rotates faster, and the rotational speed of the second member 30 becomes higher than the rotational speeds of the first cam 61 and the second cam 63, the second engagement element. Since the 50 main body portions 51 cannot be engaged with the second recesses 27, torque transmission is interrupted.

  As described above, since the two-way clutch 10 disables the engagement of the first engagement element 40 and the second engagement element 50 by the cam mechanism 60, a device such as a solenoid that converts electric energy into mechanical motion can be eliminated. The two-way clutch 10 can be reduced in size and power can be saved as much as a device such as a solenoid can be dispensed with.

  The cam mechanism 60 including the first cam 61, the second cam 63, and the third cam 65 is disposed on the same axis O as the first member 20 and the second member 30. Therefore, the size of the two-way clutch 10 can be prevented from expanding in the radial direction. In addition, since the first cam 61 and the second cam 63 are provided, torque in the forward direction and the reverse direction can be transmitted between the input shaft 11 and the output shaft 12.

  The elastic body 75 disposed on the third cam 65 urges the mass body 72 in a direction approaching the engaging portion 71. Therefore, when the rotation speed of the third cam 65 is low, the rotation speed of the third cam 65 is low. The inertial mass of the third cam 65 can be increased by the mass body 72 and the elastic body 75 as compared to when it is high. Therefore, the cam mechanism 60 can be easily operated (engaged) when the rotation speed of the third cam 65 is low, and friction when the rotation speed of the third cam 65 is high can be reduced.

  The third cam 65 is given a frictional force in the rotational direction via the mass body 72 by the friction material 82 fixed to the case 81, and a braking action is generated. Therefore, when the rotational speeds of the input shaft 11, the first cam 61, and the second cam 63 are low, the first cam 61, the second cam 63, and the third cam 65 required for the operation of the cam mechanism 60 are caused by the braking action. Can be easily generated.

  On the other hand, when the rotation speed of the third cam 65 increases and the center of gravity of the mass body 72 moves in a direction away from the engagement portion 71 due to centrifugal force (outside in the radial direction), the engagement portion 71 moves relative to the mass body 72. Since the sliding state occurs, the braking action by the friction material 82 is reduced. Therefore, the cam mechanism 60 can be easily operated when the rotational speed of the input shaft 11 is low, and friction when the rotational speed of the input shaft 11 is high can be reduced.

  The present invention has been described above based on the embodiments. However, the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed. For example, the numbers of the first engagement elements 40 and the second engagement elements 50 are examples and can be set as appropriate.

  In the above embodiment, the first engagement element 40 that transmits the torque in the forward rotation direction of the input shaft 11 is arranged on the outer peripheral side of the second member 30, and the second engagement element that transmits the torque in the reverse rotation direction of the input shaft 11. Although the case where 50 is arrange | positioned to the inner peripheral side of the 2nd member 30 was demonstrated, it is not necessarily restricted to this. On the contrary, it is naturally possible to arrange the first engaging element 40 on the inner peripheral side and the second engaging element 50 on the outer peripheral side.

  In the above-described embodiment, the case where the first engagement element 40 and the second engagement element 50 are pressed in the direction of the axis O via the ring members 44 and 54 has been described, but the present invention is not necessarily limited thereto. By omitting the ring members 44 and 54 and changing the tip shapes of the pins 45 and 55 and the shapes of the first and second engagement elements 40 and 50, the first engagement element 40 and the first engagement element 40 and the second engagement element 50 are interposed via the pins 45 and 55. It is naturally possible to press the two engaging elements 50 in the direction of the axis O.

  In the above embodiment, the first cam 61 and the second cam 63 do not push the pins 45 and 55 to the first member 20 side (the positions of the bottoms of the cam grooves 66 and 67) so that the rotation angle is the same. Although the case where the cam grooves 66 and 67 of the three cams 65 are set has been described, the present invention is not necessarily limited thereto. Of course, it is possible to set the cam grooves 66 and 67 as shown in FIG.

  FIG. 4B is a schematic diagram of another third cam 85. In FIG. 4B, the cam grooves 66 and 67 of the third cam 85 are shown on the left and right with the rotation angle around the axis O being aligned. The third cam 85 is configured so that the positions at which the first cam 61 and the second cam 63 push the pins 45 and 55 toward the first member 20 (the positions of the tops of the cam grooves 66 and 67) have the same rotation angle. Grooves 66 and 67 are set.

  That is, the first engagement element 40 and the second engagement element 50 are disengaged when the rotation direction of the first cam 61 is switched from the reverse rotation direction (counter arrow F direction) to the normal rotation direction (arrow F direction). A movement amount in the axial direction of the first cam 61 and the second cam 63 with respect to the three cams 85 is set. After the first engagement element 40 and the second engagement element 50 are disengaged from the first recess 24 and the second recess 27, the first engagement element 40 meshes with the first recess 24, so that the first cam 61 and the second cam 63 By the relative rotation with the third cam 85, the first engaging element 40 and the second engaging element 50 can be made difficult to engage with the first recess 24 and the second recess 27 (the play can be increased). Therefore, the first engaging element 40 and the second engaging element 50 can be prevented from being engaged at the same time.

  In the above embodiment, the case where the mass body 72 and the elastic body 75 are disposed on the third cam 65 and the friction material 82 fixed to the case 81 is brought into contact with the mass body 72 has been described. It is not a thing. It is naturally possible to omit both the mass body 72, the elastic body 75, and the friction material 82. Of course, any one of the mass body 72, the elastic body 75, and the friction material 82 may be omitted. When the mass body 72 and the elastic body 75 are omitted, it is naturally possible to obtain a braking action by bringing the friction material 82 fixed to the case 81 into contact with the third cam 65.

  In the above-described embodiment, the case where the first engaging element 40 and the second engaging element 50 have the same shape has been described, but the present invention is not necessarily limited thereto. Of course, the first engagement element 40 and the second engagement element 50 may be configured to have different lengths, widths, and thicknesses.

  In the above embodiment, the case 81 has been described as an example of a fixing element to which the friction material 82 is fixed. However, the present invention is not necessarily limited to this. The fixing element can be appropriately set in addition to the case 81 as long as it is a member that does not rotate integrally with the third cams 65 and 85.

DESCRIPTION OF SYMBOLS 10 Two-way clutch 11 Input shaft 12 Output shaft 20 1st member 21 1st surface 30 2nd member 31 2nd surface 40 1st engagement element 43 Spring 50 2nd engagement element 53 Spring 60 Cam mechanism 61 1st cam 63 2nd Cam 65, 85 Third cam 68 First ball 69 Second ball 71 Engaging portion 72 Mass body 75 Elastic body 80 Braking mechanism 81 Case (fixing element)
82 Friction material O Axis

Claims (7)

A two-way clutch that switches between transmission and interruption of torque between the input shaft and the output shaft,
A first member coupled to the input shaft and having a predetermined first surface;
A second member having a second surface coupled to the output shaft and facing the first surface in the axial direction;
A first member that is interposed between the first surface and the second surface and engages the first member and the second member to transmit torque in the forward rotation direction from the first member to the second member; An engagement element;
A second engagement that is interposed between the first surface and the second surface and engages the first member and the second member to transmit torque in the reverse direction from the first member to the second member. With Kazuko,
Springs for urging the first and second engagement elements in the axial direction with which the first and second engagement elements engage; and
A two-way clutch comprising: a cam mechanism that converts torque of the input shaft into axial force and elastically deforms the spring so that the first engagement element and the second engagement element cannot be engaged. The cam mechanism is disposed so as to be movable with respect to the input shaft in the axial direction with respect to the first engagement element, and rotates together with the input shaft.
A second cam that is arranged so as to be movable with respect to the input shaft and the first cam in the axial direction with respect to the second engagement element and rotates integrally with the input shaft;
A third cam disposed so as to be rotatable about the axis and immovable in the axial direction while facing the first cam and the second cam in the axial direction;
The third cam and the first cam are interposed between the third cam and the first cam by the relative rotation of the third cam and the first cam in the reverse rotation direction of the first cam. A first ball that widens an axial interval to disengage the first engagement element;
The third cam is interposed between the third cam and the second cam, and the third cam and the second cam are rotated by relative rotation between the third cam and the second cam in the forward rotation direction of the second cam. The two-way clutch according to claim 1, further comprising: a second ball that widens the interval in the axial direction and makes the second engagement element unengageable. An engagement portion provided on the third cam;
A mass body that rotates integrally with the third cam by friction with the engagement portion and moves away from the engagement portion by centrifugal force;
The two-way clutch according to any one of claims 2 to 4, further comprising: an elastic body that urges the mass body in a direction approaching the engagement portion.   4. The two-way clutch according to claim 2, further comprising a friction material that applies a frictional force to the fixed element to the third cam. 5.   The two-way clutch according to claim 3, further comprising a braking mechanism that applies a frictional force in a rotational direction to the mass body.   The cam mechanism has an axial movement amount so as to disengage the first engagement element and the second engagement element when the rotation direction of the first cam is switched from the reverse rotation direction to the normal rotation direction. The two-way clutch according to any one of claims 2 to 5.   The axial movement amount of the cam mechanism is set so that the first engagement element and the second engagement element are engaged when the rotation direction of the first cam is switched from the reverse rotation direction to the normal rotation direction. The two-way clutch according to any one of 2 to 5.

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