JP2020045926A - Rotation transmission device - Google Patents

Abstract

To prevent dragging torque caused by contact of a roller incorporated into a space between an inner member and an outer ring member with a cylindrical surface of the outer ring member when the inner member rotates at high speed in an idling state.SOLUTION: A rotation transmission device includes: a first split retainer 11 having a first pillar part 13 facing a roller 3 at one side in a circumferential direction; a second split retainer 12 having a second pillar part 15 facing the roller 3 at the other side in the circumferential direction; a retainer moving mechanism 30 which moves the first split retainer 11 and the second slit retainer 12 between a neutral position and an engagement position; and a pocket width change mechanism 50 which switches a state of the device between a roller sandwiching state and a roller sandwiching release state in conjunction with operation of the retainer moving mechanism 30.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a rotation transmission device corresponding to high-speed rotation.

  As a rotation transmission device that switches between a fastened state in which rotation is transmitted from an inner member to an outer ring member and an idling state in which transmission of rotation from the inner member to the outer ring member is interrupted, for example, a rotation transmission device described in Patent Document 1 is known. Have been.

  The rotation transmission device described in Patent Literature 1 includes an inner member, an outer ring member provided so as to surround an outer periphery of the inner member, and an inner periphery of the outer ring member radially opposed to the outer periphery of the inner member. And a plurality of cam surfaces formed on the outer periphery of the inner member so as to form a wedge space gradually narrowing from the center in the circumferential direction toward both ends in the circumferential direction between the cylindrical surface and the cylindrical surface. , And one roller incorporated between the cylindrical surface and each cam surface, and a retainer for holding the roller.

  A plurality of pockets penetrating in the radial direction are formed in the retainer at intervals in the circumferential direction, and a roller is accommodated in each pocket. The retainer is provided between the neutral position for holding the roller accommodated in each pocket at the center of the cam surface and the engagement position for engaging the roller between the cylindrical surface and the cam surface. And is supported so as to be movable in the circumferential direction.

  Further, the rotation transmitting device includes an armature detented by a retainer, a rotor detented by an outer ring member, an electromagnet which moves the armature in an axial direction by energization to attract the rotor, and a retainer for the inner member. And a neutral spring for elastically retaining the circumferential position of the spring.

  In the rotation transmission device of Patent Document 1, the roller is not engaged between the cylindrical surface and the cam surface because the retainer is held at the neutral position by the neutral spring in a state where the power supply to the electromagnet is stopped. In this case, the idle state occurs in which the transmission of rotation between the inner member and the outer ring member is interrupted.

  On the other hand, when the electromagnet is energized, the armature is attracted to the rotor, and in this state, when the inner member rotates with respect to the outer ring member, the armature and the rotor rotate together, and the retainer, which is prevented from rotating by the armature, moves to the inner member. In the circumferential direction, the retainer moves from the neutral position to the engagement position, and the roller engages between the cylindrical surface and the cam surface. That is, the rotation transmitting device is in a fastened state in which rotation is transmitted between the inner member and the outer ring member.

JP 2005-90678 A

  The inventor of the present application has considered using the rotation transmission device of Patent Document 1 in an application in which the inner member rotates at a high speed. When the inner member rotates at a high speed in the idling state, the inner member and the outer ring are rotated. It has been found that there is a problem that the roller incorporated between the members comes into contact with the cylindrical surface of the outer ring member and drag torque is generated.

  That is, when the inner member rotates in the idling state, the roller incorporated between the inner member and the outer ring member moves together with the inner member. Here, when the inner member rotates at a high speed, a large centrifugal force acts on the roller that rotates together with the inner member, and the centrifugal force may cause the roller to contact the inner peripheral cylindrical surface of the outer ring member. When the roller comes into contact with the cylindrical surface of the outer ring member due to centrifugal force, a drag torque (rotational resistance of the inner member) is generated due to friction between the roller and the cylindrical surface of the outer ring member, resulting in a large energy loss during idling. Turned out to be a problem. Further, when the roller comes into contact with the cylindrical surface of the outer race member due to centrifugal force, there is a problem that the roller is worn and the cylindrical surface of the outer race member is worn. Further, when the roller comes into contact with the cylindrical surface of the outer ring member due to centrifugal force, the roller and the retainer move in the circumferential direction with respect to the inner member due to the frictional resistance of the roller with respect to the cylindrical surface of the outer ring member, and the roller misengages. There is also a risk of doing so.

  The problem to be solved by the present invention is that when the inner member rotates at a high speed in the idling state, a drag torque caused by a roller incorporated between the inner member and the outer ring member coming into contact with the cylindrical surface of the outer ring member is reduced. It is to prevent.

In order to solve the above problems, the present invention provides a rotation transmission device having the following configuration.
An inner member,
An outer ring member provided so as to surround the outer periphery of the inner member, and rotatably supported with respect to the inner member;
A cylindrical surface formed on the inner periphery of the outer ring member so as to radially oppose the outer periphery of the inner member,
A plurality of cam surfaces formed on the outer periphery of the inner member so as to form a wedge space gradually narrowing from the center in the circumferential direction to both ends in the circumferential direction between the cylindrical surface and the cylindrical surface,
Rollers incorporated one by one between the cylindrical surface and each of the cam surfaces,
A first split retainer having a first pillar portion facing one side of the roller in the circumferential direction;
A second split retainer having a second column portion facing the other side of the roller in the circumferential direction;
A neutral position for holding the roller at the center of the cam surface at the first column portion and the second column portion, and pressing the roller in the circumferential direction at the first column portion or the second column portion, Retainer that moves the first split retainer and the second split retainer in the circumferential direction with respect to the inner member between an engagement position where the first split retainer and the second split retainer are engaged between the cylindrical surface and the cam surface. A moving mechanism;
In conjunction with the operation of the retainer moving mechanism, the width of a pocket defined by a surface of the first column portion facing the roller and a surface of the second column portion facing the roller is reduced to reduce the width of the first column. A roller clamping state in which the roller is clamped by the portion and the second column, and a roller clamping release state in which the width of the pocket is increased to release the clamping of the roller by the first column and the second column. A pocket width changing mechanism that relatively displaces the first split cage and the second split cage in the circumferential direction so as to switch;
A rotation transmission device comprising:

  With this configuration, when the cage moving mechanism moves the first split cage and the second split cage from the engagement position to the neutral position, the first split cage and the second split cage are moved in conjunction with the operation. When the cage is relatively displaced in the circumferential direction, the first pillar portion of the first split cage and the second pillar portion of the second split cage pinch the roller, thereby preventing the roller from moving in the radial direction. Therefore, when the inner member rotates at a high speed in the idling state, the roller incorporated between the inner member and the outer ring member is prevented from contacting the inner peripheral cylindrical surface of the outer ring member due to centrifugal force, and the roller is rotated. Drag torque due to contact with the cylindrical surface of the outer ring member can be prevented. Further, when the inner member rotates at a high speed in the idling state, the roller incorporated between the inner member and the outer ring member comes into contact with the cylindrical surface of the outer ring member. It is also possible to prevent engagement.

  When the first pillar portion and the second pillar portion sandwich the roller, the first pillar portion and the second pillar portion are radially outside a virtual circle passing through a center position of the roller. In contact with the outer circumference, such that the circumferential interval between the contact point of the first pillar portion with the roller and the contact point of the second pillar portion with the roller is smaller than the diameter of the roller, It is preferable to form the first pillar and the second pillar.

  With this configuration, when the roller is sandwiched between the first pillar portion and the second pillar portion, the circumferential interval between the first pillar portion and the second pillar portion radially outside the imaginary circle passing through the center of the roller is increased. Since the diameter is smaller than the diameter of the roller, it is possible to reliably prevent the roller from moving radially outward.

  The opposing surface of the first pillar portion to the roller and the opposing surface of the second pillar portion to the roller have a central opposing portion that faces in the circumferential direction across the center position of the roller, and a portion outside the central opposing portion. It is preferable that the outer diameter side opposing portion is formed so as to be connected to the radial side and project in the circumferential direction.

  With such a configuration, the rigidity of the first pillar portion and the second pillar portion is secured at the center facing portion of the first pillar portion and the second pillar portion, while the outer diameter side facing portion of the first pillar portion and the second pillar portion. Thus, it is possible to effectively prevent the rollers from moving outward in the radial direction.

The cage moving mechanism,
An armature that is prevented from rotating by the first split cage or the second split cage;
A rotor that is prevented from rotating by the outer ring member and is disposed to face the armature in the axial direction;
An electromagnet that moves the armature in the axial direction by energization and attracts the rotor to the rotor;
A neutral spring for elastically holding a circumferential position of the first divided cage or the second divided cage with respect to the inner member;
Can be employed.

The pocket width change mechanism,
A motion conversion mechanism that converts axial movement of the armature by energization of the electromagnet into relative displacement in the circumferential direction of the first split cage and the second split cage in a direction in which the width of the pocket increases;
It is possible to employ a structure in which the first split cage and the second split cage are formed of an elastic member that urges the pocket in a direction in which the width of the pocket is reduced.

  With this configuration, when the armature is attracted to the rotor by energization of the electromagnet, the axial movement of the armature is converted by the motion conversion mechanism into a relative displacement in the circumferential direction of the first split cage and the second split cage, The width of the pocket expands. On the other hand, when the energization of the electromagnet is stopped, the first split cage and the second split cage are relatively displaced in the circumferential direction by the urging force of the elastic member, and the width of the pocket is reduced.

  The armature may be connected to the first split cage or the second split cage so as to move integrally in the axial direction. In this case, as the motion conversion mechanism, an axial facing surface provided on each of the split cages so as to face in the axial direction between the first split cage and the second split cage, A first inclined groove formed on a surface of the first split cage that faces the second split cage in the axial direction so as to extend in the circumferential direction; and an axially opposed face of the second split cage to the first split cage. A ball cam mechanism including a second inclined groove formed on the surface so as to extend in the circumferential direction and a ball incorporated between the first inclined groove and the second inclined groove can be employed.

  The rotation transmission device according to the present invention is configured such that when the cage moving mechanism moves the first split cage and the second split cage from the engagement position to the neutral position, the first split cage and the first split cage are moved in conjunction with the operation. As the second split cage is relatively displaced in the circumferential direction, the first pillar of the first split cage and the second pillar of the second split cage sandwich the roller, thereby preventing the roller from moving in the radial direction. I do. Therefore, when the inner member rotates at a high speed in the idling state, the roller incorporated between the inner member and the outer ring member is prevented from contacting the inner peripheral cylindrical surface of the outer ring member due to centrifugal force, and the roller is rotated. Drag torque due to contact with the cylindrical surface of the outer ring member can be prevented.

Sectional view showing a rotation transmission device according to an embodiment of the present invention. 1. Enlarged view of the vicinity of the first split cage and the second split cage of FIG. Sectional view along the line III-III in FIG. The figure which expands and shows a part of FIG. FIG. 2 is a sectional view taken along the line VV in FIG. 2. 5A is a cross-sectional view taken along the line VI-VI in FIG. 5, and FIG. 5B is a view in which the ball shown in FIG. Sectional view showing a state in which the cage is relatively displaced in the circumferential direction. Sectional view along the line VII-VII in FIG. The figure which shows the state which energized the electromagnet shown in FIG. 2 and made the armature adsorb | suck to a rotor. Sectional view along the line IX-IX in FIG. FIG. 9 is a sectional view showing a state where the first split cage and the second split cage shown in FIG. 9 have been moved from the neutral position to the engagement position. Sectional view along the line XI-XI in FIG.

  FIG. 1 shows a rotation transmission device according to an embodiment of the present invention. The rotation transmitting device includes an inner member, an outer ring member 2 provided to surround an outer periphery of the inner member 1, and a plurality of rotation transmission devices incorporated between the outer periphery of the inner member 1 and the inner periphery of the outer ring member 2. And a retainer 4 for holding these rollers 3. The input shaft 5 is connected to the inner member 1, and the output shaft 6 is connected to the outer ring member 2. The input shaft 5 and the output shaft 6 are coaxially arranged.

  The inner member 1 is prevented from rotating around the input shaft 5 so as to rotate integrally with the input shaft 5 to which rotation is input from the outside. In the figure, the inner member 1 and the input shaft 5 are formed as a seamless and integral member, but they may be serrated and fitted as separate members.

  The output shaft 6 is stopped by the outer ring member 2 so as to rotate integrally with the outer ring member 2. In the drawing, the outer race member 2 and the output shaft 6 are formed as a seamless and integral member, but they may be serrated and fitted as separate members. A rolling bearing 7 that supports the outer ring member 2 so as to be able to rotate relative to the inner member 1 is incorporated between the outer ring member 2 and the inner member 1.

  As shown in FIGS. 2 and 3, a cylindrical surface 8 is formed on the inner periphery of the outer ring member 2 so as to radially oppose the outer periphery of the inner member 1. A plurality of cam surfaces 9 are formed on the outer periphery of the inner member 1 so as to face the inner diameter side of the cylindrical surface 8. The rollers 3 are incorporated one by one between the cylindrical surface 8 and each cam surface 9. The intervals between the circumferentially adjacent rollers 3 are all equal. The roller 3 is a columnar steel solid member.

  As shown in FIG. 4, the cam surface 9 is formed such that a wedge space is formed between the cam surface 9 and the cylindrical surface 8 so as to form a wedge space gradually narrowing from the circumferential center of the cam surface 9 toward both ends in the circumferential direction. This is a surface formed on the outer periphery of the member 1. That is, the radial distance between the cam surface 9 and the cylindrical surface 8 gradually decreases from the center of the cam surface 9 in one circumferential direction, and from the center of the cam surface 9 to the other circumferential direction. Are also getting smaller. If a plane having a straight section perpendicular to the axis is adopted as such a cam surface 9, machining of the cam surface 9 is easy, and the cam surface 9 can be formed with high dimensional accuracy.

  As shown in FIG. 2, the cage 4 includes a first divided cage 11 and a second divided cage 12. The first split retainer 11 includes a plurality of first pillars 13 arranged at intervals in the circumferential direction, and an annular first flange 14 connecting the ends of the first pillars 13 to each other. Have. The number of the first pillar portions 13 is the same as the number of the rollers 3. Similarly, the second split cage 12 also includes a plurality of second pillar portions 15 arranged at intervals in the circumferential direction, and an annular second flange portion connecting the ends of the second pillar portions 15 to each other. 16. The number of the second pillar portions 15 is the same as the number of the rollers 3.

  As shown in FIG. 4, the first pillar 13 faces one side (left side in the figure) of the roller 3 in the circumferential direction, and the second pillar 15 faces the other side of the roller 3 in the circumferential direction. (The right side in the figure). Here, the facing surface 17 of the first pillar portion 13 facing the roller 3 and the facing surface 18 of the second pillar portion 15 facing the roller 3 define pockets for accommodating the roller 3, and one roller 3 is provided in each pocket. Is housed. The first split cage 11 and the second split cage 12 are supported so as to be relatively displaceable in the circumferential direction. With the relative displacement, the opposing surface 17 of the first pillar 13 to the roller 3 and the second pillar 15 The circumferential distance (width of the pocket) between the roller 3 and the opposing surface 18 is changed.

  A facing surface 17 of the first pillar portion 13 facing the roller 3 and a facing surface 18 of the second pillar portion 15 facing the roller 3 are opposed to a central facing portion 19 that faces circumferentially across the center position of the roller 3 and a center facing portion. An outer diameter side opposing portion 20 is connected to the outer diameter side of the portion 19. The outer diameter side facing portion 20 is a surface protruding in the circumferential direction with respect to the center facing portion 19. The outer diameter side opposing portion 20 and the center opposing portion 19 form a concave pocket surface that is bent along the cylindrical surface of the roller 3.

  When the outer diameter side facing portion 20 of the first pillar portion 13 and the outer diameter side facing portion 20 of the second pillar portion 15 hold the roller 3 between the first pillar portion 13 and the second pillar portion 15, It comes into contact with the outer periphery of the roller 3 on the radial outside of the virtual circle C passing through the center position. Here, the contact point of the outer diameter side facing portion 20 of the first pillar portion 13 with the roller 3 and the contact point of the outer diameter side facing portion 20 of the second pillar portion 15 with the roller 3 pass through the center position of the roller 3. The roller 3 is located on the outer diameter side of ロ ー ラ or more (more preferably 以上 or more) of the diameter of the roller 3 with respect to the virtual circle C. The circumferential distance between the contact point of the outer diameter side facing portion 20 of the first pillar portion 13 with the roller 3 and the contact point of the outer diameter side facing portion 20 of the second pillar portion 15 with the roller 3 is equal to that of the roller 3. Smaller than the diameter of.

  A surface 21 of the first column 13 opposite to the surface 17 facing the roller 3 and a surface 22 of the second column 15 opposite to the surface 18 facing the roller 3 are circumferentially opposed. An elastic member is provided between a surface 21 of the first column 13 opposite to the surface 17 facing the roller 3 and a surface 22 of the second column 15 opposite to the surface 18 facing the roller 3. 23 are incorporated. The elastic member 23 is assembled in a state of being compressed in the circumferential direction, and the first member 13 is moved in the direction of decreasing the distance between the facing surface 17 of the first column portion 13 facing the roller 3 and the facing surface 18 of the second column portion 15 facing the roller 3. The split cage 11 and the second split cage 12 are urged. That is, the elastic member 23 urges the first split cage 11 and the second split cage 12 in a direction in which the width of the pocket accommodating the roller 3 is reduced by the elastic restoring force. As the elastic member 23, an elastomer or a metal spring can be employed.

  As shown in FIG. 2, the first flange portion 14 and the second flange portion 16 face each other in the axial direction in a direction in which the second flange portion 16 is located closer to the roller 3 than the first flange portion 14. Are located. The second flange portion 16 is provided with a plurality of axial through holes 24 through which the first column portion 13 is inserted, at intervals in the circumferential direction.

  The inner circumference of the first flange portion 14 and the inner circumference of the second flange portion 16 are supported by a cylindrical surface 25 provided on the outer circumference of the inner member 1 so as to be slidable in the circumferential direction. The tip of the first pillar 13 and the tip of the second pillar 15 are also slidably supported in the circumferential direction on the outer cylindrical surface of the washer 26 attached to the inner member 1. As shown in FIG. 4, the first split cage 11 and the second split cage 12 have a neutral position where the first pillar 13 and the second pillar 15 hold the roller 3 at the center of the cam surface 9. As shown in FIG. 10, the first pillar portion 13 or the second pillar portion 15 (the second pillar portion 15 in the figure) pushes the roller 3 in the circumferential direction, so that the roller 3 engages between the cylindrical surface 8 and the cam surface 9. It is movable in the circumferential direction with respect to the inner member 1 between the engaging position to be inserted.

  This rotation transmission device moves the first split cage 11 and the second split cage 12 in the circumferential direction with respect to the inner member 1 between a neutral position shown in FIG. 4 and an engagement position shown in FIG. It has a retainer moving mechanism 30 for moving.

  As shown in FIG. 1, the cage moving mechanism 30 includes an armature 31 that is prevented from rotating by the second divided cage 12, a rotor 32 that is arranged to face the armature 31 in the axial direction, and an armature 31 that is energized. The electromagnet 33 includes an electromagnet 33 that is moved in the axial direction and is attracted to the rotor 32, and a neutral spring 34 that elastically retains the circumferential position of the first split retainer 11 with respect to the inner member 1.

  As shown in FIG. 2, the armature 31 has an annular disk portion 35 and a cylindrical portion 36 integrally formed so as to extend in the axial direction from the outer periphery of the disk portion 35. The inner periphery of the disk portion 35 is slidably supported in the circumferential and axial directions by the outer periphery of a support ring 37 mounted on the outer periphery of the input shaft 5. Into the cylindrical portion 36, a cylindrical portion 38 integrally formed so as to extend in the axial direction from the outer periphery of the second flange portion 16 is press-fitted. It is connected to the second split cage 12 so as to move integrally in the axial direction.

  As shown in FIG. 1, the rotor 32 is press-fitted and fixed to the inner periphery of the end of the outer race member 2, so that the rotor 32 is prevented from rotating around the outer race member 2. The rotor 32 is arranged between opposing surfaces of the armature 31 and the electromagnet 33 in the axial direction. On the surface of the rotor 32 facing the armature 31, a plurality of elongated holes 39 that penetrate the rotor 32 in the axial direction and are elongated in the circumferential direction are formed at intervals in the circumferential direction. A rolling bearing 40 that rotatably supports the input shaft 5 is incorporated in the inner periphery of the rotor 32. The armature 31 and the rotor 32 are both formed of a metal having ferromagnetism.

  The electromagnet 33 is arranged to face the armature 31 in the axial direction so as to attract the armature 31 in the axial direction. The electromagnet 33 has a solenoid coil 41 and a field core 42 around which the solenoid coil 41 is wound. The field core 42 is fixed to a stationary member 44 having a hole 43 through which the input shaft 5 passes. The electromagnet 33 forms a magnetic path passing through the field core 42, the rotor 32, and the armature 31 by energizing the solenoid coil 41, and attracts the armature 31 to the rotor 32.

  As shown in FIG. 7, the neutral spring 34 includes a C-shaped annular portion 45 formed by winding a steel wire into a C shape, and a pair of extending portions 46 extending radially outward from both ends of the C-shaped annular portion 45. Consists of The C-shaped annular portion 45 is fitted into a circular spring accommodating recess 47 formed on the axial end surface of the inner member 1. The pair of extending portions 46 are inserted into radial grooves 48 formed on the axial end surface of the inner member 1 so as to penetrate radially outward from the spring accommodating recess 47.

  The extending portion 46 of the neutral spring 34 projects from the radially outer end of the radial groove 48, and the projecting portion of the extending portion 46 from the radial groove 48 is formed on the inner periphery of the first split retainer 11. It is inserted into the formed retainer groove 49. The radial groove 48 and the retainer groove 49 are formed to have the same circumferential width.

  The extension portion 46 of the neutral spring 34 is in contact with the inner surface of the radial groove 48 and the inner surface of the retainer groove 49, respectively, and the first split retainer 11 is neutralized by a circumferential force acting on the contact portion. Elastic holding in position. That is, when the first split retainer 11 is relatively rotated with respect to the inner member 1 and is moved in the circumferential direction from the neutral position shown in FIG. 7, the position of the radial groove 48 is held and retained as shown in FIG. Since the position of the container groove 49 is shifted in the circumferential direction, the C-shaped annular portion 45 is elastically deformed in the direction in which the interval between the pair of extending portions 46 is reduced, and the pair of extending portions 46 of the neutral spring 34 is elastically deformed by the elastic restoring force. The inner surface of the radial groove 48 and the inner surface of the retainer groove 49 are pressed, and a force in the direction of returning the first split retainer 11 to the neutral position is applied by the pressing. When the first split cage 11 moves to the neutral position, the first split cage 11 and the second split cage 12 are urged by the elastic member 23 in the direction in which the width of the pocket is reduced. The retainer 12 also moves to the neutral position.

  In addition, the rotation transmission device interlocks with the operation of the retainer moving mechanism 30 to reduce the width of the pocket for accommodating the roller 3 as shown in FIG. 9 and a roller holding state in which the width of the pocket is widened to release the holding of the roller 3 by the first pillar portion 13 and the second pillar portion 15 as shown in FIG. There is a pocket width changing mechanism 50 that relatively displaces the one-piece holder 11 and the second holder 12 in the circumferential direction. In this embodiment, as shown in FIG. 2, the pocket width changing mechanism 50 converts the movement of the armature 31 in the axial direction into the relative displacement of the first divided cage 11 and the second divided cage 12 in the circumferential direction. It comprises a mechanism 51 and an elastic member 23 (see FIG. 3).

  As shown in FIG. 2, the motion converting mechanism 51 is attached to the first flange portion 14 and the second flange portion 16 so as to oppose each other in the axial direction between the first split cage 11 and the second split cage 12. A first inclined groove 52 formed so as to extend in the circumferential direction on an axially opposed surface provided on the axially opposed surface of the first flange portion 14 with respect to the second flange portion 16; It comprises a second inclined groove 53 formed on the surface facing the first flange portion 14 in the axial direction so as to extend in the circumferential direction, and a ball 54 incorporated between the first inclined groove 52 and the second inclined groove 53. It is a ball cam mechanism. The first flange portion 14 is supported by a thrust bearing 55 so as to restrict axial movement away from the second flange portion 16.

  As shown in FIGS. 5 and 6A and 6B, the first inclined groove 52 is inclined such that the depth in the axial direction becomes gradually shallower in the circumferential direction from the deepest portion 56 in the deepest direction. The second inclined groove 53 also has a groove bottom inclined such that the depth in the axial direction becomes gradually shallower from the deepest portion 57 in the axial direction toward the other direction in the circumferential direction. ing. The ball 54 is arranged between the deepest portion 56 and the deepest portion 57 along the circumferential direction.

  The motion conversion mechanism 51 is configured such that when the second flange portion 16 moves in the axial direction toward the first flange portion 14, the ball 54 rolls toward the deepest portions 56, 57 of the inclined grooves 52, 53. The first divided cage 11 and the second divided cage 12 rotate relative to each other, and the width of the pocket for accommodating the roller 3 is widened by the relative rotation. As shown in FIG. The unit 15 operates to release the nipping of the roller 3. That is, the motion conversion mechanism 51 causes the axial movement of the armature 31 due to the energization of the electromagnet 33 to move the armature 31 in the circumferential direction of the first divided cage 11 and the second divided cage 12 in the direction in which the width of the pocket accommodating the roller 3 increases. Convert to relative displacement.

  The armature 31 shown in FIG. 2 is urged by the elastic member 23 (see FIG. 3) in a direction away from the rotor 32. That is, the elastic member 23 shown in FIG. 3 urges the first split retainer 11 and the second split retainer 12 in a direction to reduce the width of the pocket accommodating the roller 3, and the urging force of the elastic member 23 is The motion converting mechanism 51 shown in FIGS. 5 and 6A and 6B is converted into a force in the direction of increasing the axial distance between the first split cage 11 and the second split cage 12, and the second split holding. As shown in FIG. 2, since the vessel 12 is connected to the armature 31 so as to move integrally in the axial direction, the armature 31 is eventually urged away from the rotor 32 by the force of the elastic member 23. It has been done.

  An operation example of the rotation transmitting device will be described.

  As shown in FIG. 1, in a state in which the energization of the electromagnet 33 is stopped, the first split cage 11 and the second split cage 12 include the neutral spring 34 (see FIG. 5) and the elastic member 23 (FIG. 3). (See FIG. 2) is held at the neutral position. At this time, as shown in FIG. 4, the roller 3 is held at the center of the cam surface 9 by the first column portion 13 and the second column portion 15, and does not engage between the cylindrical surface 8 and the cam surface 9. Therefore, the rotation transmitting device is in an idling state in which transmission of rotation between the inner member 1 and the outer ring member 2 is interrupted.

  By the way, when the inner member 1 rotates in the idling state, the roller 3 incorporated between the inner member 1 and the outer ring member 2 moves together with the inner member 1. Here, when the inner member 1 rotates at a high speed, a large centrifugal force acts on the roller 3 rotating together with the inner member 1, and the centrifugal force causes the roller 3 to contact the inner peripheral cylindrical surface 8 of the outer ring member 2. The possibility arises. When the roller 3 comes into contact with the cylindrical surface 8 of the outer ring member 2 by centrifugal force, a drag torque (rotational resistance of the inner member 1) is generated by friction between the roller 3 and the cylindrical surface 8 of the outer ring member 2, There is a problem that energy loss during idling increases. Further, when the roller 3 comes into contact with the cylindrical surface 8 of the outer ring member 2 due to centrifugal force, there is a problem that the roller 3 and the cylindrical surface 8 of the outer ring member 2 are worn. Further, when the roller 3 comes into contact with the cylindrical surface 8 of the outer ring member 2 by centrifugal force, the roller 3 and the retainer 4 move in the circumferential direction with respect to the inner member 1 due to frictional resistance of the roller 3 against the cylindrical surface 8 of the outer ring member 2. And the roller 3 may be erroneously engaged.

  Therefore, in the rotation transmitting device of this embodiment, the first roller 3 is disposed between the inner member 1 and the outer ring member 2 to prevent the roller 3 from contacting the cylindrical surface 8 of the outer ring member 2 due to centrifugal force. When the split cage 11 and the second split cage 12 are at the neutral position, the roller 3 is held between the first pillar 13 of the first split cage 11 and the second pillar 15 of the second split cage 12. The roller 3 is prevented from moving in the radial direction.

  That is, when the energization to the electromagnet 33 shown in FIG. 1 is stopped and the armature 31 separates from the rotor 32, as shown in FIG. 4, the first split cage 11 and the second split cage 12 The biasing force causes the pockets to relatively displace in the direction in which the width of the pockets is narrowed, so that the first column portion 13 and the second column portion 15 sandwich the roller 3, thereby preventing the roller 3 from moving in the radial direction.

  On the other hand, when the electromagnet 33 is energized, the armature 31 is attracted to the rotor 32 as shown in FIG. 8, and when the inner member 1 rotates with respect to the outer ring member 2 in this state, the armature 31 rotates together with the rotor 32. , The second split cage 12 stopped by the armature 31 moves in the circumferential direction with respect to the inner member 1, so that the second split cage 12 and the second split cage 12 via the motion conversion mechanism 51. Is moved from the neutral position to the engagement position, and the roller 3 is engaged between the cylindrical surface 8 and the cam surface 9 as shown in FIG. That is, the rotation transmission device is in a fastened state in which rotation is transmitted between the inner member 1 and the outer ring member 2.

  Here, when the armature 31 is attracted to the rotor 32 by the energization of the electromagnet 33, the axial movement of the armature 31 is caused by the movement conversion mechanism 51 to move the armature 31 relative to the circumferential direction of the first split cage 11 and the second split cage 12. The displacement is converted to a displacement, and the width of the pocket accommodating the roller 3 is widened. Therefore, the pinching of the roller 3 by the first column portion 13 and the second column portion 15 is released, and the roller 3 is moved between the cylindrical surface 8 and the cam surface 9. Bite smoothly between.

  As described above, this rotation transmission device is interlocked with the operation when the cage moving mechanism 30 moves the first divided cage 11 and the second divided cage 12 from the engagement position to the neutral position. When the first split cage 11 and the second split cage 12 are relatively displaced in the circumferential direction, the first pillar 13 of the first split cage 11 and the second pillar 15 of the second split cage 12 are moved. The roller 3 is pinched to prevent the roller 3 from moving in the radial direction. Therefore, when the inner member 1 rotates at a high speed in the idling state, the roller 3 incorporated between the inner member 1 and the outer ring member 2 contacts the inner peripheral cylindrical surface 8 of the outer ring member 2 due to centrifugal force. Is prevented, and drag torque due to the contact of the roller 3 with the cylindrical surface 8 of the outer race member 2 can be prevented. Further, when the inner member 1 rotates at a high speed in the idling state, the roller 3 incorporated between the inner member 1 and the outer ring member 2 comes into contact with the cylindrical surface 8 of the outer ring member 2 so that the roller 3 and the outer ring member 2 and the roller 3 can be prevented from being erroneously engaged.

  In addition, as shown in FIG. 4, when the roller 3 is sandwiched between the first pillar portion 13 and the second pillar portion 15, the rotation transmitting device is positioned radially outside the virtual circle C passing through the center position of the roller 3. And the first column portion 13 and the second column portion 15 are in contact with the outer periphery of the roller 3, and between the contact point of the first column portion 13 with the roller 3 and the contact point of the second column portion 15 with the roller 3. Is smaller than the diameter of the roller 3, it is possible to reliably prevent the roller 3 from moving radially outward due to centrifugal force and coming into contact with the cylindrical surface 8 of the outer ring member 2. Has become.

  As shown in FIG. 4, when the roller 3 is sandwiched between the first pillar portion 13 and the second pillar portion 15, the rotation transmitting device is configured such that the roller 3 is larger than the virtual circle C passing through the center position of the roller 3. The first pillar portion 13 and the second pillar portion 15 contact the outer periphery of the roller 3 at a position on the outer diameter side of １ ／ or more of the diameter of the roller 3, so that the roller 3 moves radially outward, and the roller 3 When received by the first pillar portion 13 and the second pillar portion 15, the magnitude of the circumferential component of the force acting on the first pillar portion 13 and the second pillar portion 15 from the roller 3 is suppressed. Therefore, when the inner member 1 rotates at a high speed, it is possible to prevent the circumferential interval between the first pillar portion 13 and the second pillar portion 15 from being expanded by the centrifugal force acting on the roller 3.

  In addition, as shown in FIG. 4, the rotation transmitting device is configured such that the opposing surface 17 of the first column portion 13 facing the roller 3 and the opposing surface 18 of the second column portion 15 facing the roller 3 Since it is composed of the center opposing portion 19 which is sandwiched and opposes in the circumferential direction, and the outer diameter side opposing portion 20 formed so as to protrude in the circumferential direction, the center opposing portion of the first column portion 13 and the second column portion 15 is formed. 19, the roller 3 is moved outward in the radial direction by the outer diameter side facing portion 20 of the first column portion 13 and the second column portion 15 while securing the rigidity of the first column portion 13 and the second column portion 15. It is possible to prevent it effectively.

  In the above-described embodiment, a motion conversion mechanism that converts the axial movement of the armature 31 due to the energization of the electromagnet 33 into the circumferential relative displacement of the first split cage 11 and the second split cage 12 in the direction in which the width of the pocket increases. Although the ball cam mechanism is adopted as 51, another type of motion conversion mechanism 51 may be adopted.

  In the above embodiment, the neutral spring 34 that elastically holds the circumferential position of the first split retainer 11 with respect to the inner member 1 is employed. A retainer that elastically retains the circumferential position of the retainer 12 may be employed. Further, as the neutral spring 34, a spring that elastically holds the circumferential positions of the first split cage 11 and the second split cage 12 with respect to the inner member 1 may be employed.

  The embodiments disclosed this time are to be considered in all respects as illustrative and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

DESCRIPTION OF SYMBOLS 1 Inner member 2 Outer ring member 3 Roller 8 Cylindrical surface 9 Cam surface 11 First split cage 12 Second split cage 13 First column 15 Second column 17, 18 Opposing surface 19 Center opposing portion 20 Outer diameter side Opposing portion 23 Elastic member 30 Cage moving mechanism 31 Armature 32 Rotor 33 Electromagnet 34 Neutral spring 50 Pocket width changing mechanism 51 Motion converting mechanism 52 First inclined groove 53 Second inclined groove 54 Ball C Virtual circle

Claims (4)

An inner member (1),
An outer ring member (2) provided so as to surround the outer periphery of the inner member (1), and supported to be rotatable relative to the inner member (1);
A cylindrical surface (8) formed on the inner periphery of the outer ring member (2) so as to radially oppose the outer periphery of the inner member (1);
A plurality of cam surfaces (9) formed on the outer periphery of the inner member (1) so as to form a wedge space gradually narrowing from the center in the circumferential direction toward both ends in the circumferential direction between the cam surface (9) and the cylindrical surface (8). )When,
A roller (3) incorporated one by one between the cylindrical surface (8) and each of the cam surfaces (9);
A first split cage (11) having a first pillar (13) facing one side of the roller (3) in the circumferential direction;
A second split cage (12) having a second pillar (15) facing the other side in the circumferential direction with respect to the roller (3);
A neutral position where the roller (3) is held at the center of the cam surface (9) by the first column portion (13) and the second column portion (15); The roller (3) is pushed and moved in the circumferential direction by the two pillars (15), so that the roller (3) is engaged between the cylindrical surface (8) and the cam surface (9). A cage moving mechanism (30) for circumferentially moving the first divided cage (11) and the second divided cage (12) with respect to the inner member (1);
In conjunction with the operation of the cage moving mechanism (30), a surface (17) of the first column (13) facing the roller (3) and the roller (3) of the second column (15). A roller sandwiching state in which the width of a pocket defined by an opposing surface (18) is narrowed to sandwich the roller (3) between the first pillar portion (13) and the second pillar portion (15); The first split retainer (11) is switched so as to switch between a roller pinching release state in which the width of the roller (3) is released by the first column portion (13) and the second column portion (15). ) And a pocket width changing mechanism (50) for relatively displacing the second split cage (12) in the circumferential direction;
A rotation transmission device comprising:   When the roller (3) is sandwiched between the first pillar portion (13) and the second pillar portion (15), the roller (3) is located radially outside the virtual circle (C) passing through the center position of the roller (3). The first pillar portion (13) and the second pillar portion (15) are in contact with the outer periphery of the roller (3), and the contact point of the first pillar portion (13) with the roller (3) is different from the contact point. The first column portion (13) and the first column portion (13) are so arranged that a circumferential distance between a contact point of the second column portion (15) with the roller (3) is smaller than a diameter of the roller (3). 2. The rotation transmitting device according to claim 1, wherein two pillars are formed.   The surface (17) of the first column portion (13) facing the roller (3) and the surface (18) of the second column portion (15) facing the roller (3) are formed by the roller (3). A central opposing portion (19) facing the circumferential direction across the center position, and an outer diameter side opposing portion (20) connected to the outer diameter side of the center opposing portion (19) and formed to protrude in the circumferential direction. The rotation transmitting device according to claim 1, wherein the rotation transmitting device is configured. The cage moving mechanism (30) includes:
An armature (31) that is prevented from rotating by the first split cage (11) or the second split cage (12);
A rotor (32) which is prevented from rotating by the outer ring member (2) and is arranged to face the armature (31) in the axial direction;
An electromagnet (33) for causing the armature (31) to move in the axial direction by energization and attracting the rotor (32);
A neutral spring (34) for elastically holding a circumferential position of the first divided cage (11) or the second divided cage (12) with respect to the inner member (1),
The pocket width changing mechanism (50) includes:
The movement of the armature (31) in the axial direction caused by the energization of the electromagnet (33) is caused by changing the circumferential direction of the first split cage (11) and the second split cage (12) in the direction in which the width of the pocket increases. A motion conversion mechanism (51) for converting into a relative displacement;
An elastic member (23) for urging the first split cage (11) and the second split cage (12) in a direction in which the width of the pocket is reduced;
The armature (31) is connected to the first split cage (11) or the second split cage (12) so as to move integrally in the axial direction,
The motion conversion mechanism (51) is provided in each of the split cages so as to be axially opposed to each other between the first split cage (11) and the second split cage (12). An opposing surface, a first inclined groove (52) formed so as to extend in a circumferential direction on an axially opposing surface of the first split cage (11) with respect to the second split cage (12); A second inclined groove (53) formed to extend in the circumferential direction on a surface of the split cage (12) facing the first split cage (11) in the axial direction; the first inclined groove (52); The rotation transmission device according to any one of claims 1 to 3, wherein the rotation transmission device is a ball cam mechanism including a ball (54) incorporated between the second inclined grooves (53).

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