JP2016065592A - Latch mechanism and drive force transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a latch mechanism which can control noise at operation, and a drive force transmission device having the latch mechanism.SOLUTION: A latch mechanism 10 comprises: a piston ring 5 having a plurality of axial protrusions 51 in which locked parts 510 are formed at their tips; locking protrusions 19 which lock the piston ring 5; an armature 4 which presses the piston ring 5; an elastic member 7 which energizes the piston ring 5 to a direction opposite to a pressing direction by the armature 4; a yoke 30 which opposes the piston ring 5 in a radial direction; and an O-ring 8 which is arranged between the yoke 30 and the piston ring 5. In the piston ring 5, a first state that the locked parts 510 are locked to the locking protrusions 19 and a second state that the locked parts 510 are located between a pair of the adjacent locking protrusions 19 are switched with respect to each other accompanied by the advance/retreat movement of the armature 4, and in the piston ring 5, its axial movement is constrained by the slide resistance of the O-ring 8.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a latch mechanism and a driving force transmission device including the latch mechanism.

  2. Description of the Related Art Conventionally, a driving force transmission device that is used in, for example, a driving force transmission system of a vehicle and can intermittently transmit driving force between rotating members is known (for example, see Patent Document 1).

  A clutch device described in Patent Document 1 is used in a transmission of a vehicle, and includes a first friction disk that is spline-engaged with an outer peripheral surface of a shaft-shaped clutch hub, and a second frictional member that is spline-engaged with a cylindrical clutch drum. The friction disk, the electric motor for generating power for pressing the first friction disk and the second friction disk, and the first friction disk and the second friction in a state where the current supply to the electric motor is cut off. Locking means for maintaining the pressing force against the disc. The power of the electric motor is decelerated by the speed reduction mechanism and converted into linear motion by the cam mechanism, and the lock means is operated.

  In Example 2 (see FIG. 11) of Patent Document 1, a first inner cylinder having a switching slope and a shallow groove and a deep groove as positioning grooves are alternately arranged in the circumferential direction as locking means. And a second inner cylinder having a moving pin, and the moving pin of the second inner cylinder is moved between the shallow groove and the deep groove of the outer cylinder by the switching slope of the first inner cylinder. It is described that a cylindrical latch mechanism that can be switched between a locked state in which a moving pin is held in a shallow groove and an unlocked state in which the moving pin is held in a deep groove by moving is used.

  On the axial end surfaces of the first inner cylinder and the outer cylinder, inclined surfaces that are inclined with respect to the respective circumferential directions are formed, and the moving pin of the second inner cylinder slides on these inclined surfaces. Move between shallow and deep grooves. When the moving pin moves to the shallow groove, the second inner cylinder presses the first friction disk and the second friction disk, and when the moving pin moves to the deep groove, the second inner cylinder Release the friction disk with the friction disc.

International Publication WO2005 / 106272

  In the driving force transmission device described in Patent Document 1, when the moving pin moves from a shallow groove to a deep groove, noise (collision sound) is generated by colliding with the bottom of the deep groove. There is a risk of giving.

  Therefore, an object of the present invention is to provide a latch mechanism that can suppress noise during operation, and a driving force transmission device that includes the latch mechanism.

  In order to achieve the above object, the present invention has a cylindrical base portion and a plurality of axial protrusions that protrude in the axial direction from the base portion, and a to-be-locked portion is formed on the distal end surface of the axial protrusion. A locking member, a plurality of locking projections that lock the locked portion, and a direction in which the base portion separates from the locking projection in contact with the distal end surface of the axial protrusion A pressing member that presses the locked member, a biasing member that biases the locked member in a direction opposite to the pressing direction by the pressing member, a facing member that faces the locked member in a radial direction, and the facing member And a sliding contact member disposed between the locking member and the locking member, wherein the pressing member and the locking projection are inclined with respect to a circumferential direction of the locked member and A contact surface that contacts the tip surface, and the locked member is moved forward and backward by the pressing member; A first state in which the leading end surface slides and rotates on the locking projection and the contact surface of the pressing member, and the locked portion is locked by the locking projection; and the locked portion Is switched between a second state positioned between a pair of the locking protrusions adjacent to each other in the circumferential direction, and the locked member is latched with its axial movement braked by the sliding resistance of the sliding contact member Provide mechanism.

  Further, the present invention includes a first rotating member and a second rotating member that are arranged to be relatively rotatable on the same axis as the latch mechanism, and the first rotating member and the second rotating member are operated by the operation of the latch mechanism. Is a driving force transmission device connected so as to be able to transmit driving force, and is connected to the second rotating member so as to be axially movable and relatively non-rotatable, and is formed in the first rotating member. A meshing member having a second meshing portion that meshes with the second rotating member, and the meshing member is moved in the axial direction with respect to the second rotating member by the latched member of the latch mechanism. Provided is a driving force transmission device in which the first rotating member and the second rotating member are coupled by meshing with the meshing portion.

  According to the present invention, noise during operation can be suppressed.

It is sectional drawing of the driving force transmission apparatus provided with the latch mechanism which concerns on the 1st Embodiment of this invention, and its periphery part. It is a principal part enlarged view of FIG. It is a perspective view which shows an armature. It is a perspective view which shows a some latching protrusion and its peripheral part. (A) is the top view which looked at the piston ring from the some latching protrusion side along the rotating shaft, (b) is a perspective view which shows a part of piston ring. (A) to (d) show that the locked portion of the piston ring is locked by the locking protrusion from the non-locked state (second state) where the locked portion of the piston ring is not locked by the locking protrusion. It is a schematic diagram which shows operation | movement of the latch mechanism at the time of switching to the latched state (1st state). In (a) to (d), the locked portion of the piston ring is not locked to the locking protrusion from the locked state (first state) where the locked portion of the piston ring is locked to the locking protrusion. It is a schematic diagram which shows operation | movement of the latch mechanism at the time of switching to a non-locking state (2nd state). It is sectional drawing which shows the latch mechanism which concerns on the 2nd Embodiment of this invention. (A) And (b) is sectional drawing which shows the latch mechanism based on the 3rd Embodiment of this invention. (A) And (b) is sectional drawing which shows the latch mechanism based on the 4th Embodiment of this invention. It is sectional drawing which shows the latch mechanism which concerns on the 5th Embodiment of this invention, and its peripheral part. (A) And (b) is sectional drawing which shows the latch mechanism based on the 6th Embodiment of this invention.

[First Embodiment]
FIG. 1 is a cross-sectional view of a driving force transmission device including a latch mechanism according to a first embodiment of the present invention and a peripheral portion thereof. FIG. 2 is an enlarged view of a main part of FIG. This driving force transmission device 1 is used for transmitting intermittently the driving force of a driving source such as an engine of a vehicle, for example. Here, the latch mechanism refers to a mechanism in which a target member that moves forward and backward in a direction in which the pressing force is applied is positioned at a plurality of locations by intermittently applying the pressing force from one direction.

  The driving force transmission device 1 is connected to a first rotating member 11 and a second rotating member 12 that are coaxially arranged so as to be relatively rotatable, and are axially movable and relatively non-rotatable with respect to the second rotating member 12. The engagement member 2, the electromagnetic coil 3 that generates a magnetic force when energized, and a latch mechanism 10 that operates when the electromagnetic coil 3 is energized. The first rotating member 11 and the second rotating member 12 are activated by the operation of the latch mechanism 10. Are coupled so as to transmit the driving force. The first rotating member 11 and the second rotating member 12 share a rotation axis O and are rotatably supported by the housing 100.

  The housing 100 includes a first housing member 101 and a second housing member 102, and the first housing member 101 and the second housing member 102 are mutually connected by a plurality of bolts 103 (only one bolt 103 is shown in FIG. 1). It is fixed to. The inside of the housing 100 is filled with lubricating oil (not shown) for reducing sliding resistance between the constituent members at a predetermined ratio. In the following description, a direction parallel to the rotation axis O may be referred to as an axial direction, and a circumferential direction around the rotation axis O may be simply referred to as a circumferential direction.

  The first rotating member 11 is rotatably supported by a ball bearing 13 disposed between the first rotating member 11 and the first housing member 101. The first rotating member 11 includes a shaft portion 111 supported by the ball bearing 13, a projecting portion 112 formed by projecting radially outward from the end portion of the shaft portion 111, and an outer diameter end portion of the projecting portion 112. A cylindrical portion 113 extending toward the second rotating member 12 along the rotation axis O, and a gear flange portion 114 as a first meshing portion formed to protrude further radially outward from the distal end portion of the cylindrical portion 113. It has one. A plurality of gear teeth 115 are formed in the gear flange portion 114 along the circumferential direction.

  The second rotating member 12 has a cylindrical shape in which an insertion hole 120 through which the shaft 14 inserted from the opening 102 a formed in the second housing member 102 is inserted, and the inner surface of the insertion hole 120 has the shaft 14. An inner peripheral spline fitting portion 12a that is spline fitted to the outer peripheral spline fitting portion 14a is formed. The second rotating member 12 and the shaft 14 are not relatively rotatable by the spline fitting of the inner peripheral spline fitting portion 12a and the outer peripheral spline fitting portion 14a, and relative movement in the axial direction is restricted by the snap ring 15. ing. A seal member 16 seals between the outer peripheral surface of the shaft 14 and the inner surface of the opening 102 a of the second housing member 102.

  The second rotating member 12 is supported at one end in the axial direction by a ball bearing 17 disposed inside the cylindrical portion 113 of the first rotating member 11, and the other end in the axial direction is between the second housing member 102. Are supported by ball bearings 18 arranged on the surface. The ball bearings 17 and 18 are fitted to the outer peripheral surface of the second rotating member 12, and extend in parallel to the rotation axis O between the ball bearing 17 and the ball bearing 18 on the outer peripheral surface of the second rotating member 12. An outer peripheral spline fitting portion 12b made of a plurality of protrusions is formed. A latch mechanism 10 is disposed between the outer peripheral surface of the second rotating member 12 and the inner surface of the housing 100.

  The latch mechanism 10 includes an armature 4 as a pressing member that moves in the axial direction by the magnetic force of the electromagnetic coil 3, a piston ring 5 as a locked member that is externally fitted to the second rotating member 12, and a second housing member 102. A plurality of formed locking projections 19, a rolling bearing 6 disposed between the meshing member 2 and the piston ring 5, and elasticity as an urging member that elastically presses the meshing member 2 toward the piston ring 5. The member 7, the yoke 30 as a facing member facing the piston ring 5 in the radial direction, the disc spring 301 as the biasing member for biasing the armature 4 in the direction away from the yoke 30, the yoke 30 and the piston ring 5 And an O-ring 8 as a sliding contact member having elasticity that is compressed in the radial direction of the piston ring 5.

  The piston ring 5 is disposed between the armature 4 and the plurality of locking projections 19 and the rolling bearing 6, and the pressing force by the elastic member 7 is engaged with the engagement member 2 through the rolling bearing 6 to the plurality of locking projections 19. As an urging force in the axial direction. The armature 4 presses the piston ring 5 against the rolling bearing 6 against the pressing force of the elastic member 7. That is, the elastic member 7 biases the piston ring 5 in the direction opposite to the pressing direction by the armature 4.

  The locking protrusion 19 is formed as a protrusion that protrudes toward the piston ring 5 from the facing surface of the second housing member 102 that faces the armature 4 in the axial direction. In the present embodiment, the plurality of locking projections 19 are integrally provided on the second housing member 102, but the plurality of locking projections 19 may be separate from the second housing member 102.

  In the present embodiment, the rolling bearing 6 is a needle thrust roller bearing. The elastic member 7 is configured by facing a pair of disc springs 71 and 72, and is disposed at a position on the first rotating member 11 side of the meshing member 2. The disc spring 71 is in contact with the axial end surface of the meshing member 2, and the disc spring 72 is in contact with the axial end surface of the inner ring 171 of the ball bearing 17 including the inner ring 171, the outer ring 172, and a plurality of spherical rolling elements 173. Yes.

  The meshing member 2 includes a cylindrical portion 21 having an inner peripheral spline fitting portion 21a that is spline-fitted to the outer peripheral spline fitting portion 12b of the second rotating member 12, and an end portion of the cylindrical portion 21 on the first rotating member 11 side. It integrally has a gear flange portion 22 as a second meshing portion formed to project outward in the radial direction. The meshing member 2 is connected to the second rotating member 12 so as to be axially movable and relatively non-rotatable. When the meshing member 2 moves to the first rotating member 11 side, the gear flange portion 22 moves to the gear flange of the first rotating member 11. It is configured to mesh with the portion 114.

  A plurality of gear teeth 23 are formed in the gear flange portion 22 along the circumferential direction, and the plurality of gear teeth 23 mesh with the plurality of gear teeth 115 of the gear flange portion 114. In FIG. 1, a state where the gear flange portion 22 of the meshing member 2 is not meshed with the gear flange portion 114 of the first rotational member 11 is shown above the rotational axis O and is below the rotational axis O. The gear flange portion 22 of the meshing member 2 is meshed with the gear flange portion 114 of the first rotating member 11 (connected state).

  The piston ring 5 responds to the axial movement of the armature 4, and causes the meshing member 2 to move along the rotational axis O in the axial direction so that the gear flange portion 22 of the meshing member 2 meshes with the gear flange portion 114 of the first rotating member 11. Press. That is, the meshing member 2 moves in the axial direction with respect to the second rotating member 12 by the piston ring 5, and the gear flange portion 22 meshes with the gear flange portion 114 of the first rotating member 11. The two-rotating member 12 is connected. The operation when the piston ring 5 presses the meshing member 2 will be described later.

  The electromagnetic coil 3 is formed by winding a winding 32 through which a current supplied from a controller (not shown) flows around a bobbin 31 made of resin. The electromagnetic coil 3 is held by an annular yoke 30 made of a ferromagnetic material such as iron, and the yoke 30 is supported by the second housing member 102. The yoke 30 has a plurality of holes 300a into which the cylindrical pins 300 arranged so as to be parallel to the rotation axis O are fitted, and one end of the pin 300 is inserted into the hole 300a. . The second housing member 102 is formed with a plurality of holes 102b into which the other ends of the pins 300 are fitted.

  FIG. 3 is a perspective view showing the armature 4. The armature 4 includes an annular plate-like main body portion 40 having a through hole 4a through which the second rotating member 12 is inserted at the center, and a pressing protrusion 41 protruding inward from the inner peripheral surface of the main body portion 40. It has one. The main body 40 is disposed to face the electromagnetic coil 3 and the yoke 30 in the axial direction, and has a plurality of pin insertion holes 4b (four in the present embodiment) through which a plurality of pins 300 (shown in FIG. 1) are inserted. ). A facing surface 40a of the main body 40 facing the electromagnetic coil 3 and the yoke 30 is formed as a flat surface orthogonal to the axial direction.

  The pressing protrusion 41 has a trapezoidal shape when viewed from the inside of the through-hole 4 a and has a contact surface 41 a that contacts the piston ring 5 when the electromagnetic coil 3 is energized. The contact surface 41a is an inclined surface inclined with respect to the circumferential direction of the piston ring 5, and an angle formed between the end surface 41b corresponding to the lower base of the trapezoid and the contact surface 41a is an acute angle. In the present embodiment, six pressing protrusions 41 are formed at equal intervals in the circumferential direction.

  As shown in FIG. 1, the armature 4 is elastically pressed in a direction away from the yoke 30 by a disc spring 301 disposed between the main body 40 and the yoke 30. When the electromagnetic coil 3 is not energized, the armature 4 abuts against the receiving portion 102c of the second housing member 102 by the pressing force of the disc spring 301. When the electromagnetic coil 3 is energized, the armature 4 is attracted to the yoke 30 by the magnetic force. Thus, the facing surface 40 a comes into contact with the yoke 30.

  Further, the armature 4 is restricted from rotating with respect to the second housing member 102 and the yoke 30 by a plurality of pins 300 inserted through the pin insertion holes 4b, and is movable in the axial direction with respect to the electromagnetic coil 3 and is not relatively rotatable. The armature 4 is guided by a plurality of pins 300 between a retracted position in contact with the receiving portion 102 c of the second housing member 102 and an advanced position in which the opposing surface 40 a of the main body 40 contacts the yoke 30. Move back and forth in the axial direction. The disc spring 301 urges the armature 4 from the forward movement position toward the backward movement position. In FIG. 1, the armature 4 is in the retracted position above the rotation axis O, and the armature 4 is in the forward position below the rotation axis O.

  FIG. 4 is a perspective view showing the plurality of locking protrusions 19 provided on the second housing member 102 and the peripheral portion thereof.

  The second housing member 102 is formed with a through hole 102d through which the second rotating member 12 is inserted, and the plurality of locking projections 19 bulge inward from the inner peripheral surface of the through hole 102d, and the rotation axis O Along the piston ring 5 side. The plurality of locking protrusions 19 are provided at equal intervals along the circumferential direction of the through hole 102 d, and the number thereof is the same as the number of pressing protrusions 41 of the armature 4.

  Similarly to the contact surface 41 a of the pressing protrusion 41 of the armature 4, the locking protrusion 19 has a contact surface 19 a that contacts a distal end surface 51 a of an axial protrusion 51 of the piston ring 5 described later. It is formed as an inclined surface inclined with respect to. The locking projection 19 has a flat first side surface 19b and a second side surface 19c perpendicular to the circumferential direction of the piston ring 5, and a contact surface between the first side surface 19b and the second side surface 19c. 19a is formed. The angle formed between the first side surface 19b and the contact surface 19a is an acute angle, and the angle formed between the second side surface 19c and the contact surface 19a is an obtuse angle.

  5A and 5B show the piston ring 5. FIG. 5A is a plan view of the piston ring 5 viewed from the side of the plurality of locking projections 19 along the rotation axis O, and FIG. 5B is a perspective view showing a part of the piston ring 5. FIG. FIG.

  The piston ring 5 has a cylindrical base portion 50 through which the second rotating member 12 is inserted, and a plurality of axial protrusions 51 that protrude from the base portion 50 in the axial direction. In the present embodiment, the cross-sectional shape of the base 50 in the cross section along the rotation axis O is a rectangular shape, and twelve axial protrusions 51 are provided at equal intervals integrally with the base 50. A locked portion 510 is formed on the distal end surface 51 a that is the axial end surface of each axial protrusion 51. More specifically, the tip surface 51 a of the axial protrusion 51 includes a first inclined surface 510 a that is inclined with respect to the circumferential direction of the piston ring 5, and a first inclined surface 510 a that is similarly inclined with respect to the circumferential direction of the piston ring 5. The first inclined surface 510 a and the second inclined surface 510 b are arranged in the circumferential direction of the piston ring 5, including the second inclined surface 510 b inclined in the same direction.

  A step surface 510c parallel to the rotation axis O is formed between the first inclined surface 510a and the second inclined surface 510b. Further, the axial protrusion 51 has a flat first side surface 51b and a second side surface 51c orthogonal to the circumferential direction of the piston ring 5, and the first side surface 51b is formed continuously with the first inclined surface 510a. The second side surface 51c is formed continuously with the second inclined surface 510b.

  The first inclined surface 510a and the second inclined surface 510b in the circumferential direction of the piston ring 5 are formed such that the width of the first inclined surface 510a is wider than the width of the second inclined surface 510b. The locked portion 510 is formed by a first inclined surface 510a and a step surface 510c, and is configured as a recess having a triangular shape when viewed from the outer peripheral side of the piston ring 5. The axial end face 50a of the base 50 between two axially adjacent protrusions 51 adjacent in the circumferential direction is a flat surface orthogonal to the axial direction, and the axial protrusion 51 is perpendicular to the axial end face 50a. Is erected. The bearing 6 faces the surface of the base 50 opposite to the axial end surface 50a. The outer peripheral surface 50b of the base 50 is parallel to the axial direction of the piston ring 5 over the entire surface, and no step is formed.

  The locked portion 510 of the piston ring 5 is locked by the locking protrusion 19. More specifically, the movement and rotation of the piston ring 5 in the axial direction are locked when the contact surface 19a of the locking protrusion 19 comes into surface contact with the first inclined surface 510a of the distal end surface 51a of the locked portion 510. It is regulated by the protrusion 19. In a state where the locked portion 510 of the piston ring 5 is locked by the locking protrusion 19, the gear flange portion 22 of the meshing member 2 meshes with the gear flange portion 114 of the first rotating member 11, and the first rotating member 11 and the second rotating member 11 are engaged. The rotating member 12 is connected to be able to transmit a driving force.

  Further, when the electromagnetic coil 3 is excited, the contact surface 41 a of the pressing protrusion 41 of the armature 4 contacts the tip surface 51 a of the axial protrusion 51. More specifically, the abutting surface 41a of the pressing protrusion 41 abuts on a part of the outer peripheral side of the front end surface 51a in the radial direction of the piston ring 5, and a part of the inner peripheral side of the front end surface 51a The contact surface 19a of the protrusion 19 contacts.

  When the electromagnetic coil 3 is excited, the armature 4 presses the piston ring 5 in the direction in which the base portion 50 is separated from the locking projection 19 by the contact between the contact surface 41 a and the distal end surface 51 a of the axial projection 51. To do.

  As shown in FIG. 2, the yoke 30 faces the base 50 of the piston ring 5 in the radial direction. More specifically, the piston ring 5 is disposed inside the yoke 30, and the inner peripheral surface 30 b of the yoke 30 and the outer peripheral surface 50 b of the base portion 50 face each other in the radial direction of the piston ring 5.

  The O-ring 8 is held by the yoke 30 and slides on the outer peripheral surface 50b of the base 50 when the piston ring 5 moves in the axial direction. An annular groove 30a is formed on the inner peripheral surface 30b of the yoke 30 over the entire circumference, and the O-ring 8 is held in the groove 30a. The O-ring 8 is made of an elastic body that is compressed in the radial direction of the piston ring 5. In the present embodiment, the O-ring 8 is an annular rubber molded body made of, for example, nitrile rubber, styrene rubber, silicon rubber, or fluorine rubber. The surface of the O-ring 8 is pressed against the outer peripheral surface 50b of the base 50 with a restoring force accompanying compression.

(Operation of the latch mechanism 10)
6 (a) to 6 (d), the locked portion 510 of the piston ring 5 is moved from the unlocked state (second state) where the locked portion 510 of the piston ring 5 is not locked to the locking projection 19. It is a schematic diagram which shows operation | movement of the latch mechanism 10 at the time of switching to the latching state (1st state) latched by the latching protrusion 19. FIG. 6A to 6D, for ease of explanation and clarification, the circumferential direction of the piston ring 5 and the armature 4 is shown as a straight line extending in the vertical direction of the drawing. The outline of one locking projection 19 is shown by a two-dot chain line. Further, the pressing protrusion 41 of the armature 4 is illustrated by a broken line.

  In the present embodiment, when the piston ring 5 moves to the left in the drawing, the gear flange portion 22 of the meshing member 2 meshes with the gear flange portion 114 of the first rotating member 11, and the piston ring 5 moves to the right in the drawing. At this time, the gear flange portion 22 of the meshing member 2 is detached from the gear flange portion 114 of the first rotating member 11. Hereinafter, the direction toward the left side of the drawing is referred to as the meshing direction, and the direction toward the right side of the drawing is referred to as the separation direction.

  As the armature 4 moves forward and backward, the piston ring 5 rotates while the front end surface 51 a of the locked portion 510 slides on the locking protrusion 19 and the contact surfaces 19 a and 41 a of the armature 4. When the locked portion 510 of the piston ring 5 is not locked to the locking protrusion 19, the locked portion 510 is positioned between a pair of locking protrusions 19 adjacent in the circumferential direction.

  In the non-locking state, as shown in FIG. 6A, the contact surface 41 a of the pressing protrusion 41 in the armature 4 contacts the first inclined surface 510 a of the piston ring 5 by the pressing force of the elastic member 7. As described above, since the first inclined surface 510a of the piston ring 5 and the contact surface 41a of the armature 4 are inclined with respect to the circumferential direction of the piston ring 5, the contact surface 41a of the armature 4 is The piston ring 5 generates a rotational force with the rotation axis O as the rotation axis by contacting the first inclined surface 510a, but the rotation of the piston ring 5 is caused by the first side surface 51b of the axial protrusion 51 being locked. It is regulated by contacting the first side surface 19 b of the protrusion 19.

  6B shows a state in which the electromagnetic coil 3 is energized from the non-locking state shown in FIG. 6A, the armature 4 moves to the yoke 30 side, and the piston ring 5 moves together with the armature 4 in the axial direction. The state where the entire first side surface 51b of the axial projection 51 is displaced in the meshing direction with respect to the first side surface 19b of the locking projection 19 is shown. In this state, since the rotation restriction of the piston ring 5 due to the contact between the first side surface 51b of the axial protrusion 51 and the first side surface 19b of the locking protrusion 19 is released, the piston ring 5 rotates, and FIG. ), The front end surface 51a (first inclined surface 510a) of the locked portion 510 slides on the contact surface 41a of the armature 4. Also, with this rotation, the piston ring 5 moves in the disengagement direction.

  The rotation of the piston ring 5 is restricted by the stepped surface 510 c of the axial projection 51 coming into contact with the end surface 41 b of the pressing projection 41 of the armature 4. At this time, the first inclined surface 510 a of the axial protrusion 51 faces the contact surface 19 a of the locking protrusion 19. When the energization of the electromagnetic coil 3 is interrupted and the armature 4 moves in the disengagement direction, the front end surface 51a (first inclined surface 510a) of the locked portion 510 slides on the contact surface 19a of the locking protrusion 19. Then, as shown in FIG. 6D, the step surface 510 c of the axial projection 51 comes into contact with the first side surface 19 b at the distal end portion of the locking projection 19.

  As a result, the locked portion 510 of the piston ring 5 is locked with the locking protrusion 19, and the plurality of gear teeth 23 of the gear flange portion 22 of the meshing member 2 are connected to the gear flange portion 114 of the first rotating member 11. The first rotating member 11 and the second rotating member 12 are coupled so as to be able to transmit driving force.

  7A to 7D, the locked portion 510 of the piston ring 5 is moved from the locked state (first state) where the locked portion 510 of the piston ring 5 is locked to the locking protrusion 19. It is a schematic diagram which shows operation | movement of the latch mechanism 10 at the time of switching to the non-locking state (2nd state) which is not latched by the latching protrusion 19. FIG.

  7A shows a state in which the electromagnetic coil 3 is energized from the locked state shown in FIG. 6D and the armature 4 moves in the meshing direction, and the contact surface 41a of the armature 4 is the contact surface of the locking projection 19. The state displaced to the meshing direction rather than 19a is shown in figure. In this state, the rotation restriction of the piston ring 5 due to the contact between the step surface 510c of the axial protrusion 51 and the first side face 19b of the locking protrusion 19 is released, and as shown in FIG. The front end surface 51a (second inclined surface 510b) of 510 slides on the contact surface 41a of the armature 4 and the contact surface 19a of the locking projection 19 by the pressing force of the elastic member 7, and the piston ring 5 rotates.

  When the front end surface 51a (second inclined surface 510b) of the locked portion 510 slides on the contact surface 19a to the end of the locking projection 19 on the second side surface 19c side, as shown in FIG. The contact state between the tip surface 51 a and the contact surface 19 a is released, and the piston ring 5 moves in the axial direction by the pressing force of the elastic member 7. Then, as shown in FIG. 7D, the first inclined surface 510a of the piston ring 5 comes into contact with the contact surface 41a of the pressing protrusion 41 in the armature 4, and the latch mechanism 10 enters the second state.

  The movement of the piston ring 5 at this time is a linear movement that does not involve rotation, and the piston ring 5 abuts against the pressing protrusion 41 of the armature 4 under the pressing force of the elastic member 7. Thereby, when the moving speed of the piston ring 5 when the piston ring 5 abuts against the pressing protrusion 41 is high, a collision sound can be generated. However, in the present embodiment, the axial movement of the piston ring 5 is the O-ring 8. This collision resistance is suppressed by the sliding resistance. That is, the axial movement speed of the piston ring 5 is reduced by the frictional force generated when the surface of the O-ring 8 is in sliding contact with the outer peripheral surface 50b of the base 50 of the piston ring 5, and the collision noise is suppressed.

  In the second state, the latch mechanism 10 can be configured such that the base 50 of the piston ring 5 abuts against the locking protrusion 19. In this case, a collision sound may be generated when the axial end surface 50a of the base portion 50 abuts against the tip end of the locking projection 19, and this collision sound is caused by the movement of the piston ring 5 in the axial direction when the O-ring 8 slides. Suppressed by braking by dynamic resistance.

(Operation and effect of the first embodiment)
According to the first embodiment described above, the following operations and effects can be obtained.

(1) When the latch mechanism 10 is switched from the first state to the second state, the piston ring 5 is braked by the O-ring 8 in its axial movement, so that the collision noise is suppressed. Thereby, it becomes possible to suppress noise during operation of the driving force transmission device 1.

(2) Since the O-ring 8 made of an annular rubber molded body is used as a sliding contact member for braking the piston ring 5, for example, the latch mechanism 10 and the driving force transmission device 1 are compared with the case where a spring is used. The configuration can be simplified. Further, since the surface of the O-ring 8 directly contacts and slides on the outer peripheral surface 50b of the base 50 as the sliding surface of the piston ring 5, the configuration of the latch mechanism 10 and the driving force transmission device 1 is further simplified. It becomes possible.

[Second Embodiment]
FIG. 8 is a sectional view showing a latch mechanism 10A according to the second embodiment of the present invention. In the latch mechanism 10 according to the first embodiment, the O-ring 8 is held by the yoke 30, but in this embodiment, the O-ring 8 is held by the piston ring 5A. In FIG. 8, the same components as those described in the first embodiment are denoted by the same reference numerals, and redundant description thereof is omitted.

  The piston ring 5A integrally includes a cylindrical base 50 and a plurality of axial protrusions 51, and an annular groove 50c is formed on the outer peripheral surface 50b of the base 50 over the entire circumference. An O-ring 8 is held in the concave groove 50c. The O-ring 8 is compressed in the radial direction of the piston ring 5 </ b> A between the piston ring 5 </ b> A and the yoke 30, and the surface thereof is in contact with the inner peripheral surface 30 b of the yoke 30.

  The operation of the latch mechanism 10A is the same as that described with reference to FIGS. 6 and 7 in the first embodiment, and the piston ring 5A is moved when the latch mechanism 10A is switched from the first state to the second state. The axial movement is alleviated by the frictional force generated when the surface of the O-ring 8 comes into sliding contact with the inner peripheral surface 30b of the yoke 30, and the collision noise is suppressed. In other words, the same operation and effect as the first embodiment can be obtained also by the second embodiment.

[Third Embodiment]
FIGS. 9A and 9B are cross-sectional views showing a latch mechanism 10B according to the third embodiment of the present invention. In the latch mechanism 10 according to the first embodiment, the outer peripheral surface 50b of the base 50 in the piston ring 5 is parallel to the axial direction of the piston ring 5, but the piston ring 5B in the present embodiment has its base 50 Is different from the piston ring 5 according to the first embodiment. The operation of the latch mechanism 10B according to the present embodiment is the same as that described with reference to FIGS. 6 and 7 in the first embodiment.

  FIG. 9A shows a first state in which the locked portion 510 of the piston ring 5B is locked to the locking protrusion 19, and FIG. 9B shows that the locked portion 510 of the piston ring 5B is adjacent. The 2nd state located between a pair of matching protrusion 19 is shown. 9 (a) and 9 (b), components that are the same as those described in the first embodiment are given the same reference numerals, and redundant descriptions thereof are omitted.

In the piston ring 5B according to the present embodiment, the sliding contact surface that is in sliding contact with the O-ring 8 on the outer peripheral surface 50b of the base 50 includes two sliding contact portions having different diameters. More specifically, the base portion 50 of the piston ring 5B has a stepped cylindrical shape, and the outer peripheral surface 50b thereof has a first sliding contact portion 50b ₁ that contacts the O-ring 8 in the first state of the latch mechanism 10B, and a latch. A second sliding contact portion 50b ₂ that contacts the O-ring 8 in the second state of the mechanism 10B, and a tapered portion 50b ₃ formed between the first sliding contact portion 50b ₁ and the second sliding contact portion 50b ₂ are provided. Contains. The first sliding contact portion 50b ₁ is formed in the engaged portion 510 side of the second sliding contact portion 50b _2.

Here, the "sliding surface" of the outer peripheral surface 50b of the base 50, refers to the sliding contact area to the O-ring 8 with the axial movement of the piston rings 5B, in this region, the tapered portion 50b ₃ whole and includes at least a part of each of the first sliding contact portion 50b ₁ and the second sliding contact portion 50b ₂ is.

The outer diameter of the base 50 in the first sliding contact portion 50b ₁ is formed smaller than the outer diameter of the base 50 in the second sliding contact portion 50b ₂ . The outer diameter of the base portion 50 in the taper portion 50b ₃ is gradually increased from the first sliding contact portion 50b ₁ side toward the second sliding contact portion 50b ₂ side. Incidentally, the outer peripheral surface 50b of the base 50 is parallel to the axial direction of the first sliding contact portion 50b ₁ and the second sliding contact portion piston ring 5B in 50b _2.

The O-ring 8 contacts the first sliding contact portion 50b ₁ when contacting the second sliding contact portion 50b ₂ based on the step between the first sliding contact portion 50b ₁ and the second sliding contact portion 50b ₂ . It is compressed more than usual. Thus, the base portion 50 is a surface pressure applied from the O-ring 8 in the second sliding contact portion 50b _2, the base 50 is higher than the surface pressure applied from the O-ring 8 in the first sliding contact portion 50b _1. This difference in surface pressure, O-ring 8 acts as a difference in braking force when braking the axial movement of the piston rings 5B, the piston ring. 5B, O-ring 8 slides a second sliding contact portion 50b ₂ when subjected to a large braking force than when the O-ring 8 slides on the first sliding contact portion 50b _1.

As described above, the first sliding contact portion 50b _1, since it is formed in the engaged portion 510 side of the second sliding contact portion 50b _2, the latch mechanism 10B moves from the first state to the second state when the base 50 of the piston ring 5B, first, in the first sliding contact portion 50b ₁ in sliding contact with the O-ring 8, then the diameter of the O-ring 8 is piston rings 5B by the tapered portion 50b ₃ slides over O-ring 8 It is compressed in a direction, which sliding contact with the O-ring 8 in the subsequent further second sliding contact portion 50b _2. Thereby, when the latch mechanism 10B shifts from the first state to the second state, the braking force of the piston ring 5B by the O-ring 8 increases stepwise.

According to the present embodiment, since a relatively large braking force is generated immediately before the piston ring 5B hits the pressing projection 41 of the armature 4, the collision sound is suppressed while suppressing a decrease in the moving speed in the axial direction of the piston ring 5B. Can be suppressed. That is, if in the case where the entire outer peripheral surface 50b of the base 50 were formed in the same diameter as the second sliding contact portion 50b _2, the axis of the piston ring 5B when the latch mechanism 10B moves from the first state to the second state causes decreased responsiveness decreases the moving speed of the direction is large, and if the case where the entire outer peripheral surface 50b of the base 50 were formed in the same diameter as the first sliding contact portion 50b ₁ is control by the O-ring 8 Although the power does not sufficiently act and a collision sound is generated, in the present embodiment, it is possible to achieve both responsiveness and quietness by suppressing the collision sound.

In the present embodiment, the case where the sliding surface of the outer peripheral surface 50b of the base 50 has two different sliding contact portion (first sliding contact portion 50b ₁ and the second sliding contact portion 50b ₂₎ diameters from each other Although described, this sliding contact surface may have three or more sliding contact portions. That is, the slidable contact surface on the outer peripheral surface 50b of the base 50 only needs to include at least two slidable contact portions having different diameters. However, it is desirable that the outer diameter of each sliding contact portion be formed so as to be farther away from the locked portion 510 in the axial direction.

[Fourth Embodiment]
FIGS. 10A and 10B are cross-sectional views showing a latch mechanism 10C according to the fourth embodiment of the present invention. In the second embodiment, the inner peripheral surface 30b of the yoke 30 facing the outer peripheral surface 50b of the base portion 50 of the piston ring 5A is formed as a surface parallel to the rotation axis O. However, in the present embodiment, the yoke The slidable contact surface slidably contacting the O-ring 8 on the inner peripheral surface 30b of the 30 includes two slidable contact portions having different diameters.

  FIG. 10A shows a first state in which the locked portion 510 of the piston ring 5A is locked by the locking protrusion 19, and FIG. 10B shows that the locked portion 510 of the piston ring 5A is adjacent. The 2nd state located between a pair of matching protrusion 19 is shown. 10 (a) and 10 (b), the same components as those described in the first and second embodiments are denoted by the same reference numerals, and redundant description thereof is omitted.

In this embodiment, the inner circumferential surface 30b of the yoke 30 is, the first sliding contact portion 30b ₁ in contact with the O-ring 8 in the first state of the latch mechanism 10C, the O-ring 8 in a second state of the latch mechanism 10C a second sliding contact portion 30b ₂ which contacts include first sliding contact portion 30b ₁ and a tapered portion 30b _3, which is formed between the second sliding contact portion 30b _2. The second sliding contact portion 30b ₂ is formed closer to the locked portion 510 than the first sliding contact portion 30b ₁ is.

Here, the “sliding contact surface” refers to a region of the inner peripheral surface 30b of the yoke 30 that is in sliding contact with the O-ring 8 as the piston ring 5A moves in the axial direction. In this region, the tapered portion 30b ₃ whole and include each at least a portion of the first sliding contact portion 30b ₁ and the second sliding contact portion 30b ₂ is.

The inner diameter of the yoke 30 in the first sliding contact portion 30b ₁ is formed larger than the inner diameter of the yoke 30 in the second sliding contact portion 30b _2. The inner diameter of the yoke 30 in the taper portion 30b ₃ is gradually reduced from the first sliding contact portion 30b ₁ side toward the second sliding contact portion 30b ₂ side. Incidentally, the inner circumferential surface 30b of the yoke 30 is parallel to the axial direction of the first sliding contact portion 30b ₁ and the second sliding contact portion piston ring 5A in 30b _2.

The O-ring 8 contacts the first sliding contact portion 30b ₁ when contacting the second sliding contact portion 30b ₂ based on the step between the first sliding contact portion 30b ₁ and the second sliding contact portion 30b ₂ . It is compressed more than usual. Thus, the surface pressure yoke 30 receives from the O-ring 8 in the second sliding contact portion 30b _2, the yoke 30 is higher than the surface pressure applied from the O-ring 8 in the first sliding contact portion 30b _1. This difference in surface pressure, O-ring 8 acts as a difference in braking force when braking the axial movement of the piston rings 5A, the piston ring. 5A, O-ring 8 slides a second sliding contact portion 30b ₂ when subjected to a large braking force than when the O-ring 8 slides on the first sliding contact portion 30b _1.

As described above, since the second sliding contact portion 30b ₂ is formed closer to the locked portion 510 than the first sliding contact portion 30b ₁ , the latch mechanism 10B shifts from the first state to the second state. when, O-ring 8 held by the piston rings 5A, first the first sliding contact portion 30b ₁ sliding contact with the yoke 30 in, then the radial direction of the piston rings 5A by O-ring 8 is in sliding contact with the tapered portion 30b ₃ compressed into, then further sliding contact with the yoke 30 in the second sliding contact portion 30b _2. Thereby, when the latch mechanism 10C shifts from the first state to the second state, the braking force of the piston ring 5A by the O-ring 8 increases stepwise.

  According to the present embodiment, the same operations and effects as the operations and effects described for the third embodiment can be obtained. That is, since a relatively large braking force is generated immediately before the piston ring 5A hits the pressing protrusion 41 of the armature 4, a collision sound can be suppressed while suppressing a decrease in the moving speed in the axial direction of the piston ring 5A.

In this embodiment, the case where the inner peripheral surface 30b of the yoke 30 sliding surface has two different sliding contact portion (first sliding contact portion 30b ₁ and the second sliding contact portion 30b ₂₎ diameters from each other However, this sliding contact surface may have three or more sliding contact portions. That is, the sliding contact surface on the inner peripheral surface 30b of the yoke 30 only needs to include at least two sliding contact portions having different diameters. However, it is desirable that the inner diameter of each sliding contact portion be formed so as to be farther away from the locked portion 510 in the axial direction.

[Fifth Embodiment]
FIG. 11 is a cross-sectional view showing a latch mechanism 10D and its peripheral part according to the fifth embodiment of the present invention. In FIG. 11, the same components as those described in the first embodiment are denoted by the same reference numerals, and redundant description thereof is omitted.

  In the first embodiment, the armature 4 is supported so as not to rotate relative to the housing 100 (second housing member 102), and the plurality of locking projections 19 are provided integrally with the second housing member 102. In the present embodiment, the armature 4D constituting the latch mechanism 10D is connected to the second rotating member 12D so as not to be relatively rotatable and to be relatively movable in the axial direction. The locking protrusion 121 is provided integrally with the second rotating member 12D. The configuration of the piston ring 5 itself in the latch mechanism 10D is the same as that of the first embodiment described with reference to FIG.

  FIG. 11 shows a state where the gear flange portion 22 of the meshing member 2 is not meshed with the gear flange portion 114 of the first rotational member 11 (disconnected state) above the rotational axis O, and below the rotational axis O. The gear flange portion 22 of the meshing member 2 is meshed with the gear flange portion 114 of the first rotating member 11 (connected state).

  The plurality of locking projections 121 are formed to protrude radially outward from the outer peripheral surface of the second rotating member 12D at a portion facing the inner peripheral surface 50d of the base 50 of the piston ring 5, and are formed at end portions in the axial direction. Is formed with an abutting surface 121 a that abuts against the tip end surface 51 a of the axial projection 51 of the piston ring 5. The contact surface 121a is inclined with respect to the circumferential direction of the piston ring 5 in the same manner as the contact surface 19a of the locking projection 19 in the first embodiment.

  The second rotating member 12D is formed with a plurality of protrusions 122 on the outer peripheral portion of the locking projection 121 for connecting the armature 4D to the second rotating member 12D so that the armature 4D is relatively unrotatable and relatively movable in the axial direction. Has been. The armature 4 </ b> D has a plurality of meshing teeth 42 that mesh with the protrusions 122 on the axial end surface 40 b opposite to the yoke 30, and the axial end surface 40 b abuts the projections 122 between the meshing teeth 42. It is possible to move in the axial direction between the retracted position and the advanced position where the opposing surface 40a of the yoke 30 contacts the yoke 30.

  An annular groove 12c is formed over the entire circumference of the second rotating member 12D facing the inner peripheral surface 50d of the base 50, and the O-ring 8 is held in the groove 12c. The O-ring 8 is compressed in the radial direction of the piston ring 5 by contact with the inner peripheral surface 50 d of the base 50. That is, in the present embodiment, the second rotating member 12D corresponds to the facing member of the present invention. The O-ring 8 brakes the axial movement of the piston ring 5 by a frictional force generated between the O-ring 8 and the inner peripheral surface 50d of the base 50.

  According to the present embodiment, the same operations and effects as those of the first embodiment can be obtained. Further, since the O-ring 8 is held in the recessed groove 12c of the second rotating member 12D disposed inside the piston ring 5, the O-ring 8 can be easily and reliably held.

[Sixth Embodiment]
12A and 12B are sectional views showing a latch mechanism 10E according to the sixth embodiment of the present invention. In the fifth embodiment, the inner peripheral surface 50d of the base 50 of the piston ring 5 is formed as a surface parallel to the rotation axis O. However, in the present embodiment, the piston ring 5E constituting the latch mechanism 10E is formed. The slidable contact surface slidably contacting the O-ring 8 on the inner peripheral surface 50d of the base 50 includes two slidable contact portions having different diameters.

  12A shows a first state in which the locked portion 510 of the piston ring 5E constituting the latch mechanism 10E is locked to the locking protrusion 121, and FIG. 12B shows the locked state of the piston ring 5E. A second state is shown in which the locking portion 510 is located between a pair of adjacent locking protrusions 121. 12 (a) and 12 (b), the same components as those described for the fifth embodiment are denoted by the same reference numerals, and redundant description thereof is omitted.

In this embodiment, the inner circumferential surface 50d of the base portion 50 of the piston ring. 5E, the first sliding contact portion 50d ₁ in contact with the O-ring 8 in a first state of the latch mechanism 10E, in a second state of the latch mechanism 10E a second sliding contact portion 50d ₂ in contact with the O-ring 8 includes a first sliding contact portion 50d ₁ and the tapered portion 50d ₃ formed between the second sliding contact portion 50d _2. The first sliding contact portion 50d ₁ is formed on the engaged portion 510 side of the second sliding contact portion 50d _2.

Here, the “sliding contact surface” refers to a region in the inner peripheral surface 50d of the base portion 50 that is in sliding contact with the O-ring 8 as the piston ring 5E moves in the axial direction. In this region, the tapered portion 50d ₃ whole and include each at least a portion of the first sliding contact portion 50d ₁ and the second sliding contact portion 50d ₂ is.

The inner diameter of the base portion 50 in the first sliding contact portion 50d ₁ is formed larger than the inner diameter of the base portion 50 in the second sliding contact portion 50d _2. The inner diameter of the base portion 50 in the taper portion 50d ₃ is gradually reduced in diameter from the first sliding contact portion 50d ₁ side to the second sliding contact portion 50d ₂ side. Incidentally, the inner circumferential surface 50d of the base 50 is parallel to the axial direction of the first sliding contact portion 50d ₁ and the second sliding contact portion piston ring 5E at 50d _2.

The O-ring 8 contacts the first sliding contact portion 50d ₁ when contacting the second sliding contact portion 50d ₂ based on the level difference between the first sliding contact portion 50d ₁ and the second sliding contact portion 50d ₂ . It is compressed more than usual. Thus, the surface pressure piston ring 5E receives an O-ring 8 in the second sliding contact portion 50d _2, the piston ring 5E is higher than the surface pressure applied from the O-ring 8 in the first sliding contact portion 50d _1. This difference in surface pressure, O-ring 8 acts as a difference in braking force when braking the axial movement of the piston ring 5E, the piston ring. 5E, O-ring 8 slides a second sliding contact portion 50d ₂ when subjected to a large braking force than when the O-ring 8 slides on the first sliding contact portion 50d _1.

The second sliding contact portion 50d _2, since it is formed at a position farther from the engaged portion 510 than the first sliding contact portion 50d _1, when the latch mechanism 10E transitions from a first state to a second state, O ring 8 is in contact firstly sliding the base 50 of the piston ring 5E in the first sliding contact portion 50d _1, then, O-ring 8 is compressed in the radial direction of the piston rings 5E by sliding contact with the tapered portion 50d _3, then further sliding contact to the base 50 in the second sliding contact portion 50d _2. Thereby, when the latch mechanism 10E shifts from the first state to the second state, the braking force of the piston ring 5E by the O-ring 8 increases stepwise.

  According to the present embodiment, operations and effects similar to those described with respect to the third and fourth embodiments can be obtained. That is, since a relatively large braking force is generated immediately before the piston ring 5E hits the pressing protrusion 41 of the armature 4D, it is possible to suppress a collision sound while suppressing a decrease in the moving speed in the axial direction of the piston ring 5E.

In the present embodiment, when the base portion sliding surface of the inner peripheral surface 50d of the 50 has two different sliding contact portion (first sliding contact portion 50d ₁ and the second sliding contact portion 50d ₂₎ diameters from each other However, this sliding contact surface may have three or more sliding contact portions. That is, the slidable contact surface on the inner peripheral surface 50d of the base portion 50 only needs to include at least two slidable contact portions having different diameters. However, it is desirable that the inner diameter of each sliding contact portion be formed so as to be smaller from the locked portion 510 in the axial direction.

(Appendix)
As mentioned above, although this invention was demonstrated based on the 1st thru | or 6th embodiment, embodiment described above does not limit the invention based on a claim. In addition, it should be noted that not all the combinations of features described in the embodiments are essential to the means for solving the problems of the invention.

  Further, the present invention can be appropriately modified and implemented without departing from the spirit of the present invention. For example, in the above-described embodiment, the case where the latch mechanisms 10, 10A to 10E are applied to the driving force transmission device 1 that transmits the driving force of a driving source such as an engine of a vehicle in an intermittent manner has been described. The use of 10, 10A to 10E is not limited, and can be applied to, for example, an electromagnetic brake that fixes a rotating member to a vehicle body. Furthermore, the present invention can be applied not only to the in-vehicle device but also to machine tools and various instruments.

  In the above embodiment, the case where the armatures 4 and 4D that move in the axial direction by the electromagnetic coil 3 are used as the pressing member is described. However, the pressing member is not limited to this, and an actuator such as a motor or a solenoid is used. What is necessary is just to be able to apply the pressing force generated by the above to the piston rings 5, 5A, 5B, 5E.

DESCRIPTION OF SYMBOLS 1 ... Driving force transmission device 10, 10A, 10B, 10C, 10D, 10E ... Latch mechanism, 100 ... Housing, 101 ... 1st housing member, 102 ... 2nd housing member, 102a ... Opening, 102b ... Hole part, 102c ... receiving part, 102d ... through hole, 103 ... bolt, 11 ... first rotating member, 111 ... shaft part, 112 ... projecting part, 113 ... cylindrical part, 114 ... gear flange part, 115 ... gear teeth, 12, 12D ... first 2-rotating member, 120 ... insertion hole, 121 ... locking projection, 121a ... abutting surface, 122 ... projection, 12a ... inner periphery spline fitting portion, 12b ... outer periphery spline fitting portion, 12c ... concave groove, 13 ... Ball bearing, 14 ... shaft, 14a ... outer spline fitting portion, 15 ... snap ring, 16 ... sealing member, 17, 18 ... ball bearing, 171 ... inner ring, 172 ... outer ring, 1 DESCRIPTION OF SYMBOLS 3 ... Rolling element, 19 ... Locking protrusion, 19a ... Contact surface, 19b ... 1st side surface, 19c ... 2nd side surface, 2 ... Meshing member, 21 ... Cylindrical part, 21a ... Inner peripheral spline fitting part, 22 ... Gear flange portion, 23 ... gear teeth, 3 ... electromagnetic coil, 30 ... yoke, 300 ... pin, 300a ... hole, 301 ... disc spring, 30a ... concave groove, 30b ... inner peripheral surface, 30b ₁ ... first sliding contact portion 30b ₂ ... 2nd sliding contact part, 30b ₃ ... Tapered part, 31 ... Bobbin, 32 ... Winding, 4, 4D ... Armature, 40 ... Body part, 40a ... Opposing surface, 40b ... Axial end face, 41 ... Pressing Projection, 41a ... abutting surface, 41b ... end face, 42 ... meshing tooth, 4a ... through hole, 4b ... pin insertion hole, 5, 5A, 5B, 5E ... piston ring, 50 ... base, 50a ... axial end face, 50b ... outer peripheral surface, 50b 1 _... first sliding contact portion, 50b ₂ The second sliding contact portion, 50b 3 _... taper portion, 50c ... groove, 50d ... inner peripheral surface, 50d 1 _... first sliding contact portion, 50d 2 _... second slidable contact portion, 50d 3 _... taper portion, 51 ... shaft Direction projection, 510... Locked portion, 510 a. First inclined surface, 510 b. Second inclined surface, 510 c. Step surface, 51 a ... End surface, 51 b ... First side surface, 51 c ... Second side surface, 6. , 7 ... Elastic member, 71, 72 ... Disc spring, 8 ... O-ring

Claims (8)

A locked member having a cylindrical base portion and a plurality of axial protrusions protruding in the axial direction from the base portion, and a locked portion formed on a distal end surface of the axial protrusion;
A plurality of locking projections for locking the locked portion;
A pressing member that contacts the distal end surface of the axial protrusion and presses the locked member in a direction in which the base portion is separated from the locking protrusion;
A biasing member that biases the locked member in a direction opposite to the pressing direction by the pressing member;
A facing member that faces the locked member in a radial direction;
A sliding contact member disposed between the opposing member and the locked member,
The pressing member and the locking projection have a contact surface that is inclined with respect to the circumferential direction of the locked member and contacts the tip surface of the axial projection,
The locked member rotates with the front end surface sliding on the locking protrusion and the contact surface of the pressing member as the pressing member moves forward and backward, and the locked portion is locked by the locking member. The first state locked to the protrusion and the second state where the locked portion is positioned between a pair of the locking protrusions adjacent in the circumferential direction are switched,
The axial movement of the locked member is braked by the sliding resistance of the sliding contact member,
Latch mechanism. The sliding contact member is held by the facing member,
The sliding contact surface of the locked member with the sliding contact member includes at least two sliding contact portions having different diameters.
The latch mechanism according to claim 1. The sliding surface includes a first sliding contact portion that contacts the sliding contact member in the first state, and a second sliding contact portion that contacts the sliding contact member in the second state,
The sliding contact member has elasticity that is compressed in the radial direction of the locked member, and is compressed to a greater extent than when it comes into contact with the first contact portion when in contact with the second sliding contact portion,
The first sliding contact portion is formed closer to the locked portion than the second sliding contact portion.
The latch mechanism according to claim 2. The sliding contact member is held by the locked member,
The sliding contact surface of the facing member with the sliding contact member includes at least two sliding contact portions having different diameters from each other.
The latch mechanism according to claim 1. The sliding surface includes a first sliding contact portion that contacts the sliding contact member in the first state, and a second sliding contact portion that contacts the sliding contact member in the second state,
The sliding contact member has elasticity that is compressed in the radial direction of the locked member, and is compressed to a greater extent than when it comes into contact with the first contact portion when in contact with the second sliding contact portion,
The second sliding contact portion is formed closer to the locked portion than the first sliding contact portion.
The latch mechanism according to claim 4. The sliding contact member is made of an elastic body, and the surface thereof is in sliding contact with the sliding contact surface.
The latch mechanism according to any one of claims 2 to 5. The sliding contact member is an annular rubber molded body,
The latch mechanism according to any one of claims 1 to 6. The latch mechanism according to any one of claims 1 to 7, and a first rotating member and a second rotating member that are coaxially arranged to be relatively rotatable, and the first rotating member is operated by the operation of the latch mechanism. And a driving force transmission device in which the second rotating member is coupled to transmit the driving force,
A meshing member having a second meshing portion that is coupled to the second rotating member so as to be axially movable and relatively non-rotatable and meshes with a first meshing portion formed on the first rotating member;
The meshing member moves in the axial direction with respect to the second rotating member by the locked member of the latch mechanism, and the second meshing portion meshes with the first meshing portion, whereby the first rotating member and A driving force transmission device coupled to the second rotating member.

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