JP2006300296A - Damper unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To diminish load caused by engagement between teeth of a pinion and teeth of a rack of a rotary damper upon relative movement in a non-buffering direction, in a damper unit including the rotary damper for buffering relative movement between a first member and a second member. <P>SOLUTION: In the damper unit, the first member includes a case body 2 having a rack body. The rotary damper is rotatably pivoted at an end portion of a sliding member which slides within the case body. When a slider 18 moves in the non-buffering direction, the rotary damper 38 is rotated in such a direction that the teeth of the pinion 43 and the teeth 14 of the rack 13 of the rotary damper 38 are disengaged from each other. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a shock absorber that cushions relative movement of a first member and a second member.

  2. Description of the Related Art Conventionally, a drawer device is known in which a drawer portion is slidable via a slide rail on a fixed rail provided in a storage case portion of the drawer device as this type of shock absorber (Patent Document 1). The drawer of this device is provided with a traveling body, and a highly viscous fluid is sealed in the traveling body, and a rotating cylinder is rotatably mounted. Further, the traveling body includes a movable cylinder that covers the rotary cylinder and a pinion that is arranged in parallel with the rotary cylinder so as to be rotatable integrally with the rotary cylinder. The movable cylinder is provided with a spring one-way clutch, one end of which is hooked to a pinion and the other end is free.

  And in the direction that the drawer is pulled out, the pinion is rotated by the rack provided on the fixed rail, but the rotation of the pinion is caused by the spring one-way clutch being unwound by the pinion, and the diameter is expanded to be in a slip state with the movable cylinder. The movable cylinder and the rotating cylinder do not rotate, and the pinion does not receive a resistance force due to the highly viscous fluid.

  On the other hand, in the direction in which the drawer is stored, the pinion is rotated by a rack provided on the fixed rail, and by this pinion, the spring one-way clutch winds the movable cylinder, and the rotational force of the pinion is transmitted to the movable cylinder and the rotating cylinder. Therefore, the pinion receives a resistance force due to the highly viscous fluid, and can apply a braking force to the traveling body only when traveling in the storage direction of the drawer portion.

In addition, there is known a device that guides a movable part of conventional furniture, for example, a drawer in a sliding manner with a drawer guide (Patent Document 2). This device is provided with a shock absorber. The shock absorber includes a carrier fixed to the drawer rail, a rotary damper supported by the carrier, a pinion attached to the shaft of the rotary damper, and a rack provided on the slider. The carrier is provided with a holder such as rubber that holds the rotary damper against rotation, plastic with high frictional properties, or claw teeth.
JP-A-4-28307 JP 2002-242978 A

  However, since the above-described drawer device uses a spring one-way clutch, there is a problem that the shock absorber itself becomes complicated and the cost is increased. In addition, the rotary damper with the spring one-way clutch is relatively large in structure and has a problem that the shock absorber cannot be reduced in size.

  In addition, in a known shock absorber that does not use a one-way clutch, a holding tool such as rubber and plastic having high friction is required, and an operation of placing the holding tool on the carrier is required, resulting in an increase in product cost. In addition, when claw teeth are placed on the carrier instead of rubber or plastic with high friction properties, it is rare that the claw teeth of the carrier and claw teeth of the rotary damper mesh completely from the beginning. There are many cases where the tooth tips of the teeth contact each other. In such a case, a time lag occurs in the occurrence of the buffering action until the nail teeth and the nail teeth mesh with each other. Furthermore, there is a problem that abnormal noise is generated when the nail teeth engage with each other.

  2. The shock absorber according to claim 1, wherein the shock absorber absorbs relative movement between the first member (fixed member) and the second member (moving body), and the first member includes a case body provided with a rack and the case. A sliding member that slides in the body together with the second member, and a rotary damper that is pivotally supported by the sliding member and has a pinion that meshes with the rack, and a rotation shaft of the pinion of the rotary damper; A straight line between the shafts connecting the rotation fulcrum of the sliding member is inclined in a direction opposite to a buffering direction of the sliding member with respect to a vertical line with respect to a tooth tip surface of the rack, and the sliding member is When the rotary damper is moved in an inclined direction in the case body, the rotary damper is rotated around the rotation fulcrum in a direction to disengage the mesh between the rack and the pinion. When the sliding member is moved to the side opposite to the side on which the straight line between the axes is inclined, the rotary damper moves the rack around the rotation fulcrum of the sliding member. And the pinion are rotated in a direction in which the pinion meshes with each other, so that the buffering action of the rotary damper is generated.

  According to the present invention, it is possible to cause the rotary damper to have a buffering action in a direction in which a desired buffering is desired, and to reduce or hardly cause the buffering action in a direction in which the buffering action is not desired.

  The shock absorber according to claim 2 includes a sliding friction member that slides the rotary damper with respect to the case body when the sliding member slides in the case body, and the sliding friction member and the case body When the sliding member is in one movement direction, the rotary damper rotates so that the rotary damper rotates about the rotation fulcrum in a direction to release the engagement between the pinion of the rotary damper and the rack. When power is applied and when the slider moves in the other moving direction, the turning force is applied so that the rotary damper pinion and the rack are rotated around the rotation fulcrum of the rotary damper. It is characterized by that. According to the present invention, the rotation in the meshing direction can be enhanced in the direction of releasing the meshing between the pinion and the rack according to the moving direction of the sliding member in the invention of the first aspect.

  The shock absorber according to claim 3, wherein the rack provided in the longitudinal direction in the case body has a meshing guide portion on which the rack teeth are not formed at an end portion where the straight line between the axes is inclined. The pinion teeth and the rack teeth mesh with the meshing guide portion of the rotary damper rotated in a direction in which the meshing between the pinion teeth of the rotary damper and the rack teeth is released. It is characterized by having guide means for rotating in the direction.

  According to the present invention, when the moving body moves away from the shock absorber and the pinion teeth of the rotary damper deviate from the position facing the front end of the rack teeth, the rotary damper is forcibly centered on its rotation fulcrum. The teeth can be forcibly rotated in the meshing direction between the teeth of the rack and the teeth of the rack, and when the rotary damper is moved in the buffering direction, the teeth of the pinion and the teeth of the rack can be reliably meshed from the beginning.

  The shock absorber according to claim 4 is configured to rotate the rotary damper around its rotation fulcrum in a direction to release the engagement between the pinion teeth of the rotary damper and the teeth of the rack at the buffer end position of the rotary damper. It is characterized by having means for moving.

  According to the present invention, when the rotary damper is moved from the buffering end position in the non-buffering direction, the teeth of the rotary damper pinion and the rack teeth can be prevented from meshing from the beginning.

  Hereinafter, the configuration of an embodiment of the shock absorber according to the present invention will be described with reference to FIGS. In each figure, the same reference numerals are assigned to the same parts.

  FIG. 1 is an exploded perspective view.

  2 to 5 are schematic plan views showing only one ridge provided on the back cover at various operating positions of the shock absorber by broken lines and with the back cover removed.

  Reference numeral 1 denotes the entire first member, which is a shock absorber for a moving body, for example, a sliding door, that is, a sliding door closer, and is a device that prevents the sliding door from being roughly closed or rebounded. This shock absorber is provided with a case body 2 having an elongated rectangular flat plate shape. A mounting recess 3 extends in the longitudinal direction on the upper surface side of the case body 2. Reference numeral 4 denotes a moving body, for example, a sliding door, a folding door, or a drawer, and an engagement pin 5 is attached thereto by a mounting plate 6. A guide slot 8 is formed in the bottom surface portion 7 that forms the bottom surface of the mounting recess 3. The guide slot 8 has a width slightly larger than the diameter of the engagement pin 5 so that the engagement pin 5 of the movable body 4 can be slidably engaged in the longitudinal direction. The guide slot 8 is provided from the center in the longitudinal direction of the bottom surface portion 7 to the front end in the longitudinal direction of the case body 2. That is, the guide slot 8 penetrates up and down to the front end of the case body 2 and communicates with the front end surface of the case body 2. Therefore, the guide slot 8 between the front end surface of the case body 2 and the mounting recess 3 is formed as a slot provided in the bottom surface portion 7 of the case body 2. A tapered guide surface 9 that is tapered toward the front end edge of the guide slot is formed at the opening edge of the front end of the guide slot 8. The tapered guide surface 9 functions as a guide surface that facilitates engagement of the engagement pin 5 of the movable body 4 with the guide slot 8.

  An elongated sliding groove 10 is provided on the bottom surface portion 7 of the mounting recess 3 of the case body 2. The sliding groove 10 includes a moving groove portion 11 that extends in the longitudinal direction of the mounting recess 3. The moving groove 11 is provided in parallel to the guide slot 8.

  Further, the front end of the moving groove 11 is continuously provided with a turning groove 12 that faces the width direction of the mounting recess 3. The turning groove 12 has a curved shape. The rotating groove 12 is formed across the one side edge of the case body 2 in the width direction from the moving groove 11.

  Further, a rack 13 is formed on the rear end side of the mounting recess 3 of the case body 2 so as to rise vertically from the bottom surface portion over a length of about 1/3 in the longitudinal direction of the case. The teeth 14 of the rack 13 are directed toward one side of the case body 2, that is, toward the right side wall, and the upper surface of the rack is formed flat. The front and rear end portions of the rack 13 are formed with occlusal guide portions with missing tooth rows. It is not always necessary to delete the teeth at the rear end, but it is advantageous to delete the teeth at the front end in order to make the rack teeth 14 start the engagement of the pinion well.

  A projecting portion 15 is provided continuously on one side edge of the front end portion of the mounting recess 3 of the case body 2, and an L-shaped fixing groove 16 is formed there. One of the L-shaped leg portions of the fixing groove 16 extends parallel to the longitudinal direction of the case and reaches the mounting recess 3.

  A brake plate 17 having a shape obtained by bending the end of an elongated rectangular flat plate into an L shape is fitted and fixed in the fixing groove 16. The length of the brake plate 17 in the longitudinal direction of the case is about ½ of the case length.

  The brake plate 17 is made of metal or the like and functions as a sliding contact member. Further, the brake plate 17 extends into the mounting recess 3 in parallel with the longitudinal direction of the case body 2 with the tip fixed to the fixing groove 16. The sliding contact surface of the brake plate 17 can be roughened so that the frictional resistance is increased. The brake plate 17 extends into the mounting recess 3 in a state of being separated from the case body side wall, and is slidably mounted in the mounting recess 3 of the case body 2 so as to be slidable in the longitudinal direction of the mounting recess. It extends into a slider 18 that forms a member. The slider 18 as a sliding member is guided by the right inner wall and the left inner wall of the mounting recess 3 in contact with the left side surface 19 and the right side wall 20 of the slider 18 so as to be slidable in the longitudinal direction of the case body 2. It is installed.

  The slider 18 is formed in a substantially flat plate shape, and includes a holding piece 23a and 23b protruding from the plate-like portion of the slider 18 to hold the constricted portion 22 at the front end portion of the tension spring 21 at the front end portion on the left side. A portion 23 is provided, and a guide wall 24 that guides the tension spring from the holding piece 23 a extends to the elevated platform portion 25 of the slider 18. The guide of the tension spring on the side of the holding piece 23 b is made by the inner wall forming the mounting recess 3 of the case body 2.

  Further, a low trapezoidal portion 26 is formed at the front end portion of the slider 18, and a short slot 27 that runs in the longitudinal direction of the slider 18 is formed at the center portion in the width direction of the slider 18. The slot 27 is a groove into which an engaging pin attached to the upper end surface of the moving body 4, for example, a sliding door is slidably inserted, and has a width slightly larger than the diameter of the engaging pin 5. With the slider 18 mounted in the mounting recess of the case body 2, the slot 27 communicates with the guide slot 8 of the case body 2 in the vertical direction. Further, a locking groove 28 is formed at the front end portion of the high platform portion 25 of the slider 18, and the platform portion 29 of the high platform portion 25 located on the front end side of the slider with respect to the locking groove 28 of the high platform portion 25 is rearward. It is curled to the left side in the width direction from the end side. An accommodation groove 30 in which the brake plate 17 extends is provided between the right side surface of the hill-like portion 25 of the slider 18 and the right side wall of the slider 18. For example, a short leg portion of a pressing member 30 formed by bending an elongated rectangular flat plate made of metal into an L shape is inserted into the locking groove 28, and the long leg portion is interposed between the side wall of the platform portion 29 and the brake plate 17. To place. A flat brake pad 32 made of a friction material or the like is attached to the surface of the pressing member 31 facing the brake plate 17 in order to increase the frictional force with the brake plate 17 when the slider 18 slides. .

  Further, a mounting groove 35 for mounting a mounting projection 34 of a brake pad 33 made of a friction material is formed on the right side wall 20 of the slider 18. Further, a short shaft 37 is erected on the right corner lower base portion 36 at the rear end portion of the slider 18. A sleeve bearing 41 having a bearing hole provided in an overhanging portion 40 of a casing 39 filled with silicone oil of the rotary damper 38 is attached to the short shaft 37.

  A pinion 43 is fixed to the rotary shaft 42 of the rotary damper 38. The teeth of the pinion 43 are rotatable about the short axis 37 so that the teeth of the pinion 43 can mesh with the teeth of the rack 13. The rotary range of the rotary damper 38 is restricted on the one hand by a stopper 44 projecting from the rear end of the slider and on the other hand at the rear end edge of the hill-like part 25.

  In the present invention, a straight line (interaxial straight line) connecting the rotating short axis 37 of the rotary damper 38 provided on the slider 18 and the rotating shaft 42 of the pinion is inclined with respect to a vertical line with respect to the tooth tip surface of the rack 13. . When the slider 18 is moved to the inclined side of the inter-axis straight line, that is, the front end side by the inclination of the inter-axis straight line, the rotary damper is such that the teeth of the pinion 43 of the rotary damper 38 are only in contact with the tips of the teeth of the rack 13. 38 rotates around the short shaft 37 in the direction opposite to the direction in which the rack 13 and the pinion 43 are engaged. Accordingly, the pinion 43 of the rotary damper 38 and the rack 13 are not engaged with each other in one of the relative movement directions of the case body 2 and the slider 18, so that the slider 18 is in a direction in which the straight line between the axes is inclined, that is, When moving to the front end side, there is no buffering action of the rotary damper 38.

  On the other hand, when the slider 18 is moved to the side opposite to the side where the straight line between the axes is inclined, that is, when the slider 18 is moved to the rear end side of the case body 2, the pinion 43 and the rack 13 of the rotary damper 38 are once. , The rotary damper 38 rotates about the short shaft 37 in the direction in which the rack 13 and the pinion 43 are engaged.

  Accordingly, in the other movement direction of the relative movement of the case body 2 and the slider 18, that is, the direction in which the slider 18 is moved to the rear end side of the case body 2, the pinion 43 of the rotary damper 38 and the rack 13 mesh with each other. Due to the buffering action of the damper 38, the relative movement between the slider 18 and the case body 2 can be buffered.

  Further, the rotary damper 38 is provided on the pinion 43 of the rotary damper 38 and the case body 2 on one side of the rack 13 provided in the longitudinal direction of the case body 2 (side where the straight line between the axes is inclined), that is, the front end side of the rack 13. A guide shaft 45 is provided on the surface of the rotary damper casing as means for rotating in the direction in which the rack 13 is engaged. A protrusion 47 is provided on the inner surface of the back cover 46 of the case body 2, and a taper surface inclined in the same direction as the rotation direction of the rotary damper 38 toward the rear end is formed at the rear end of the protrusion 47. Has been. The teeth 14 of the rack 13 are not formed at the position of the rack 13 facing the position of the protrusion 47 provided with the tapered surface.

  Therefore, when the slider 18 moves in one direction, that is, the front end direction of the case body, the guide shaft 45 is guided by the taper surface of the protrusion 47 formed on the back cover 46 that forms a part of the case body 2, and the pinion The rotary damper 38 is forcibly rotated about the short axis 37 in the direction in which the teeth of 43 and the teeth of the rack 13 mesh. Since no teeth are formed on the rack 13 at the position where it is forced to rotate, the pinion 43 of the rotary damper 38 and the teeth of the rack 13 do not contact each other.

  Therefore, when the slider 18 is moved in a direction opposite to the side of the inclination of the straight line between the axes, that is, when the slider 18 is moved in the rear end direction of the case body 2, the relative rotation between the slider 18 and the case body 2 is caused by the forced rotation. During movement, the pinion 43 of the rotary damper 38 and the teeth 14 of the rack 13 can be immediately meshed with each other, so that the relative movement between the slider 18 and the case body 2 can be reliably buffered.

  Further, a sliding friction shaft 49 protruding upward from a support portion 48 protruding laterally from the casing 39 of the rotary damper 38 is provided. The sliding friction shaft 49 is preferably provided on the rack 13 side with respect to a straight line in the longitudinal direction of the slider passing through the rotation fulcrum of the rotary damper 38. The sliding friction shaft 49 forms a sliding friction member that comes into sliding contact with the inner surface of the back cover 46 of the case body 2 while being in friction. The sliding friction shaft 49 may be elastic per se or may be in sliding contact with an elastic body. The sliding friction shaft 49 can be configured to protrude directly from the surface of the casing 39.

  As described above, when the slider 18 moves relative to the case body 2, the rotary damper moves with the movement of the slider 18, and the sliding friction shaft 49 provided on the rotary damper 38 and the inner surface of the back cover 46 of the case body 2. Friction occurs between them.

  Therefore, when the slider 18 is moved to the side of the inclination of the straight line between the axes, that is, the front end side of the case body 2, the rotary damper 38 causes the rack 13 and the pinion 43 to be centered around the short shaft 37 as a pivotal fulcrum. Is rotated in a direction opposite to the meshing direction, and can be moved while maintaining its position.

  On the other hand, when the slider 18 is moved in the direction of the inclination of the straight line between the axes, the friction between the sliding friction shaft 49 and the back cover 46 of the case body 2 causes the short shaft 37 that is the rotation fulcrum of the rotary damper 38 to be the center. The rack 13 and the pinion 43 are rotated in a direction opposite to the direction in which the rack 13 and the pinion 43 are engaged, and the rack 13 and the pinion 43 can move while maintaining the position.

  In an advantageous embodiment, the guide shaft 45 can also be used as a sliding friction shaft 49. In this case, it is preferable that the guide shaft 45 is configured to elastically press in the axial direction so that the elasticity can be adjusted and the frictional force by the guide shaft can be adjusted.

  A bearing hole 50 is formed in the low base portion 26 of the slider 18. The bearing hole 50 is provided near the rear end portion of the slot 27 in the axial direction of the slider, but is provided on the right side of the slot 27. A hook body 51 for pressing the brake plate 17 by the abutment of the engagement pin 5 of the moving body 4 is rotatably attached to the bearing hole 50 as a buffer member. The holding means for sliding with 2 members (engagement pin) is comprised.

  The hook body 51 is rotated by the contact of the engagement pin 5 of the moving body 4 and presses the brake plate 17 attached to the case body 2 via the pressing member 31 and the brake pad 32. At this time, the right side surface of the brake plate 17 abuts on a brake pad 33 attached to the inner surface of the right side wall 20 of the slider 18, and the brake plate 17 is sandwiched so that the slider 18 and the moving body are braked. The relative movement of the case body 2 is buffered.

  The hook body 51 has a low trapezoidal part 52 from the front end side to the right side of the rear end and a high base part 53 on the left side of the rear end. A short shaft 54 that is supported by the bearing hole 50 is provided on the back side of the low base portion 52.

  Further, on the back side of the front end portion of the low trapezoidal portion 52, an engaging convex portion 55 is slidably engaged with each of the moving groove portion 11 and the rotating groove portion 12 of the sliding groove 10 of the case body 2. Yes. The engaging convex portion 55 has a longitudinal dimension that is slidably fitted into the moving groove portion, and has a width dimension that is pivotally fitted to the rotating groove portion of the sliding groove 10. ing. Accordingly, both side edges of the engaging convex portion 55 are formed in an arc shape along the rotating groove portion of the sliding groove 10. Further, the engaging convex portion 55 is provided in the central portion in the width direction on the front end side of the hook body 51. A hill-like portion 53 having a holding recessed portion 56 is formed from the left end side rear edge portion of the hill-like portion 52 of the hook body 51. A cam bulging portion 57 that bulges from the right end portion of the holding concave portion 56 toward the right side continues. The cam bulging portion 57 has the engaging pin 5 of the moving body 4 in the holding recess 56 in a state where the short shaft 54 of the hook body 51 is rotatably mounted in the bearing hole 50 of the low platform portion 52 of the slider 18. When it is pushed and moved toward the rear end side, the left side surface of the leg portion of the pressing member 31 is pressed. Therefore, the brake pad 32 attached to the right side surface of the pressing member 31 is pressed against the left side surface of the brake plate 17. At that time, the brake plate 17 is sandwiched between the brake pad 33 attached to the inner surface of the right side wall 20 of the slider, a clamping force is applied from both sides, and a braking force for braking the movement of the slider 18 is applied. As a result, a buffering action for braking the movement of the moving body occurs.

  In addition, an attachment recess 58 for fixing the constricted portion of the rear end portion of the tension spring 21 is formed in the left corner portion of the rear end portion of the case body 2.

  Further, attachment holes 60 and 61 for attaching the cushioning member to the fixing member, for example, the rail end attached to the door frame, are formed in the front end portion and the rear end portion of the case body 2.

  FIG. 6 is a perspective view when the shock absorber of the present invention is applied to a sliding door. In the figure, the upper guide rail 65 of the pair of guide rails is configured in two stages, the shock absorber 1 of the present invention is attached to one end in the upper guide rail, and the sliding door 4 as a moving body is interposed via the support shaft 66. It is supported by a four-wheel carriage 67 that travels in the lower guide rail. The engaging pin 5 is attached to an extension 68 extending in the direction opposite to the shock absorber 1 side in the width direction of the sliding door of the base of the four-wheel carriage. Even if the sliding door 4 is vigorously driven in the guide rail 65 in the direction of closing the sliding door, that is, in the direction of the shock absorber 1 by the four-wheel carriage 67, the sliding pin 4 has the engaging pin 5 of the sliding door 4 in the case body of the shock absorber 1. 2 progresses into the buffer and receives a buffering action, preventing rebound.

  The case where the shock absorber shown in FIGS. 1 to 5 is applied to a sliding door as a sliding door closer as shown in FIG. 6 will be described.

  First, the operation position of the shock absorber in a state where the sliding door 4 is closed in the direction of the shock absorber 1 is shown in FIG. 2, and the operation position during the opening operation from the state where the sliding door 4 is closed is shown in FIG.

  FIG. 4 shows an operation position in which the shock absorber is waiting for the engaging pin 5 of the sliding door 4, and FIG. 5 buffers the movement of the sliding door 4 in the closing operation direction by holding the engaging pin 5 of the sliding door 4. The operation position during the movement is shown.

  When the shock absorber 1 is used as a sliding door closer, even when the sliding door 4 is closed and closed vigorously, the door frame is shocked and does not rebound, so that no gap is generated between the sliding door 4 and the door frame. There is a need to. Therefore, it is necessary to complete the gradual closing operation from the vicinity of the closing operation end of the sliding door 4 toward the closing operation of the sliding door.

  When the sliding door 4 is closed, the engaging pin 5 attached to the upper end surface of the sliding door 4 moves toward the shock absorber 1 side.

  Before the engagement pin 5 contacts the holding recess 56 of the hook body 51, the shock absorber 1 is in the operating position shown in FIG. In this operating position, the brake plate 17 fitted and fixed in the fixing groove 16 of the slider 18 as a sliding member is not pressed by the brake pad 32 attached to the pressing member 31 inserted in the locking groove 28. . Therefore, although the brake plate 17 is positioned between the brake pad 33 attached to the right side wall 20 of the slider 18 and the brake pad 32 attached to the pressing member 31, the brake plate 17 is not subjected to the pressing force by the pressing member 31.

  Further, since the engaging convex portion 55 formed on the low base portion 52 of the hook body 51 pivotally supported by the slider 18 is located in the rotating groove portion 12 of the sliding groove 10, the slider 18 is moved by the tension spring 21. Even if it is urged toward the rear end direction of the case body 2, the slider 18 cannot move in the longitudinal direction. Further, the rotary damper 38 rotatably mounted with the short shaft 37 of the right corner platform 36 at the rear end of the slider 18 as a rotation fulcrum is positioned immediately before the teeth of the pinion 43 mesh with the teeth of the rack 13. is doing.

  However, the sliding door 4 is moved, and the engaging pin 5 on the sliding door is inserted into the guide slot 8 and the slot 27 of the slider 18 through the case body 2 taper guide surface 9, respectively. The inside of the hook body 51 is guided by sliding, and is in contact with and inserted into the rear end side protruding portion of the holding recessed portion 56 of the hook body 51. The engagement pin 5 abuts against the rear end side protruding portion 56 of the holding recessed portion 56 of the hook body 51, and the hook body 51 is pressed to the rear end side by the contact force. As a result, the hook body 51 rotates about the minor axis 54 counterclockwise. Then, the engaging pin 5 is fitted and held in the holding recessed portion 56 of the hook body 51. At that time, the hook body 51 rotates around the short shaft 54 fitted in the bearing hole 50 of the slider while the engaging convex portion 55 of the hook body is guided by the rotating groove portion 12 of the sliding groove 10 of the case body 2. After that, the engaging convex portion 55 of the hook body 51 moves to the moving groove portion 11 of the sliding groove 10 of the case body 2.

  As a result, the engagement between the engagement convex portion 55 and the rotation groove portion 12 is released, and each of the hook body 51, the engagement pin 5 and the slider 18 is caused by the tensile force of the tension spring 21 as shown in FIG. It moves toward the rear end of the case body 2. At this time, the teeth of the pinion 43 of the rotary damper 38 and the teeth of the rack 13 provided in the case body 2 are rotatably attached to the right corner platform 36 at the rear end of the slider 18 via the short shaft 37. Engage. Accordingly, as the hook body 51, the engagement pin 5 and the slider 18 move, the pinion 43 of the rotary damper 38 rotates with respect to the rack 13, and the rear end edge of the slider 18 becomes the case body as shown in FIG. The hook body 51 and the engaging pin 5 and thus the sliding door 4 are moved to a predetermined closed position together with the slider 18 until they contact the rear end of the second mounting recess 3.

  Here, the closing speed of the sliding door 4 is relatively slow, and the contact force of the engaging pin 5 of the sliding door 4 to the holding recessed portion 56 of the hook body 51 is smaller than the tensile force of the tension spring 21 and the rotary damper 38. When a buffering action is applied to the rack 13 and is smaller than the resultant force of the rotational resistance force of the rotary damper 38 against the pinion 43, the meshing resistance force of the rack 13 and the pinion 43, and the tensile force of the tension spring 21, the holding recess portion of the hook body 51 The engaging pin 5 is entrained on the front end side surface 56, and only the buffering action by the rotary damper 38 and the rack 13 is received, so that the engaging pin 5 and the sliding door 4 reliably move to a predetermined position.

  On the other hand, the closing speed of the sliding door 4 is relatively fast, and the contact force of the engagement pin 5 of the sliding door 4 to the holding recess 67 of the hook body 51 on the rear end side is larger than the tensile force of the tension spring 21. In this case, when the buffering action of the rotary damper 38 occurs, and the rotational resistance force of the rotary damper 38 by the pinion 43 and the meshing resistance force of the pinion 43 and the rack 13 and the resultant force of the tension spring are larger than the resultant force of the tension spring, the hook body 51 An inner surface of one leg portion of the pressing member 31 is pressed by the cam raised portion 57 to press the brake plate 17 through the brake pad 32 attached to the pressing member 31 and to be attached to the right side wall 20 of the slider 18. The brake plate 17 is sandwiched with the brake pad 33 and the brake plate 17 is tightened.

  Therefore, the brake pad 32 attached to the pressing member 31 and the brake pad 33 attached to the right side wall 20 of the slider 18 squeeze the brake plate 17 as the hook body 51, the engagement pin 5, and the slider 18 move. The sliding contact is received, the braking force is received, and the buffering action by the rotary damper 38 and the rack 13 is received, so that the movement of the engagement pin 5 to the rear end side of the case body 2 is buffered.

  Next, the case where the sliding door 4 is opened from the state where the opening is closed by the sliding door 4 will be described.

  In this case, the sliding door 4 is opened from the operation position shown in FIG. 2, and the tension spring 21 is extended by moving the engagement pin 5 of the sliding door 4 to the front end side of the shock absorber 1.

  At the same time, when the engagement pin 5 moves toward the front end side of the case body 2 of the shock absorber 1, the engagement pin 3 presses the front end side of the holding recessed portion 56 of the hook body 51 so that the hook body 51 rotates clockwise. Rotate.

  As a result, the pressing of the brake plate 17 via the pressing member 31 by the cam raised portion 57 of the hook body 51 is released by the clockwise rotation of the hook body 51. Therefore, the sliding door can be opened in a state where the buffering action by pressing the pressing member 31 against the brake plate 17 is released.

  In this state, when the sliding door 4 is further opened, the front end side of the holding recessed portion 56 of the hook body 51 is pressed by the engaging pin 5 on the sliding door 4, and the engaging convex portion 55 of the hook body 51 becomes the case body 2. The sliding groove 10 is guided from the moving groove portion 11 to the rotating groove portion 12.

  As a result, as shown in FIG. 4, the hook body 51 rotates clockwise to change to a standby position and posture for waiting for the engagement pin 5, and the engagement pin 5 is engaged by the holding recessed portion 56 of the hook body 51. The combined holding is released, and the engagement protrusion 55 of the hook body 51 is engaged with the rotation groove 12 of the sliding groove 10 of the case body 2 so that the tension spring is held in an extended state.

  Further, in the present invention, a rotary damper 38 is rotatably attached to a short shaft 37 erected on the right corner lower base portion 36 at the rear end portion of the slider 18. Therefore, when the slider 18 moves to the front end side of the case body 2, the rotation shaft 42 of the pinion of the rotary damper 38 and the rotation fulcrum attached to the short shaft 37 of the slider 18 of the rotary damper 38 are connected. The axis-to-axis straight line is inclined toward the front end of the case body 2 with respect to a vertical line with respect to the tooth surface of the rack 13 of the case body 2. Therefore, when the slider 18 is moved in the front end direction of the case body, the rotary fulcrum of the rotary damper 38 receives a force parallel to the moving direction of the slider 18, so that the rotary damper 38 is centered on the rotary fulcrum. 14 and the pinion 43 are rotated in a direction to disengage the teeth.

  As a result of the rotation of the rotary damper 38, the teeth of the pinion 42 and the teeth 14 of the rack 13 are disengaged as shown in FIG. 3, so that when the sliding door 4 is opened, the pinion 43 and the rack 13 by the rotary damper 38 are disengaged. The sliding action based on the meshing does not occur and the sliding door can be opened smoothly.

  Further, in the present invention, in order to assist the rotation of the rotary damper 38, a sliding friction shaft 49 that elastically slides and contacts the inner surface of the back cover 46 of the case body 2 is provided in the casing 39 of the rotary damper 38. The sliding shaft 49 elastically frictionally contacts the inner surface of the back cover 46 of the case body 2. When the slider 18 moves in the direction toward the front end of the case body 2 due to this frictional force, a force is generated that causes the rotary damper 38 to rotate counterclockwise around its rotation fulcrum. This frictional force is for eliminating the engagement between the teeth of the rotary damper 38 and the teeth of the rack so that the rotary damper does not generate a braking force against the movement of the slider 18 and has almost no effect as a braking force for the opening operation. Is selected as follows. Therefore, the teeth of the pinion 43 of the rotary damper 38 can be reliably disengaged from the teeth 14 of the rack 13. Therefore, when the engagement pin 5 of the sliding door 4 opens the sliding door, the rotary damper 38 does not become a braking load, so the load during the opening operation of the sliding door 4 can be reduced.

  Further, in the present invention, the rack 13 provided in the longitudinal direction of the case body 2 has a meshing guide portion in which the teeth 14 of the rack 13 are not formed at the front end portion, and the teeth of the pinion 43 of the rotary damper and the rack are provided in this guide portion. The rotary damper 38 rotated in the direction in which the meshing with the 13 teeth is released is provided with a guiding means for rotating in the direction in which the teeth of the pinion 43 and the teeth of the rack 13 are meshed. In the above embodiment, as the guide means, when the slider 18 moves to the position of the rack tooth missing portion in the non-buffering direction, the rotary damper casing 39 is provided on the protrusion 47 having a taper provided on the inner surface of the back cover 46 of the case body 2. The rotary damper 38 is rotated to a rotation position where the guide shaft 45 provided on the guide shaft 45 is guided and the pinion teeth 43 and the rack teeth can mesh with each other.

  Therefore, in the present invention, when the slider 18 moves in the buffering direction, the teeth of the pinion 43 of the rotary damper 38 and the teeth of the rack 13 can immediately mesh with each other from the beginning of the buffering operation.

  Further, in the present invention, a means for releasing the engagement between the pinion teeth of the rotary damper and the teeth of the rack may be provided at the buffer end position. In another embodiment of the present invention, the rotary damper 38 is rotated by a guide shaft 45 protruding from the casing 39 of the rotary damper 38 and a protrusion 59 having a taper guide surface provided on the back cover 46 of the case body. Since it is configured to rotate in the direction of disengagement of the teeth of the pinion 43 and the teeth 14 of the rack 13 around the fulcrum, that is, in the counterclockwise direction, the slider 18 is started from the beginning of moving the sliding door 2 in the opening direction. The load caused by the engagement between the teeth of the pinion 43 of the rotary damper 38 and the teeth of the rack 13 can be eliminated.

  In the above-described embodiment, when the sliding door is closed, braking force is applied to the brake plate 17 fixed to the case body 2 with the slider 18 and the brake pad through the pressing member by the rotation of the hook body 51. It is also possible to slide the slider 18 by pressing with the body 51 itself.

  Further, the pressing member may not have a brake pad, and the pressing member may be directly pressed against the brake plate or the case body. Further, the slider may not have a brake pad, and the brake plate may be tightened by sandwiching the slider 18 and the pressing member directly in a sandwich shape.

  Further, instead of the brake plate 17, the hook body 51 can directly or indirectly act on the case body itself.

  Instead of applying a tensile force to the slider 18 by the tension spring 21, a pressure spring can be provided between the slider 18 and the inner wall of the case so that the slider 18 can be moved by the applied pressure.

  In addition, as a means for applying a frictional force between the rotary damper 38 and the inner wall of the case body 2, a projecting portion that projects directly from the casing 39 of the rotary damper 38 can be used instead of the sliding friction shaft 49. In addition, sliding friction can be generated by the pad attached to the casing 39 or the casing itself. In addition, the rotary damper 38 can also be used as a guide shaft 45 provided to guide the pinion 43 in the direction in which the teeth of the rack 13 and the teeth of the rack 13 are engaged or in the opposite direction. In that case, it is desirable to make elastic contact with the inner wall of the case body 2. Therefore, the frictional force applying means is made of an elastic material, or at least a part thereof is made of an elastic member.

  As described above, according to the present invention, when the sliding door 4 is opened, the engaging pin 5 of the sliding door 4 presses the front end side of the holding recessed portion 56 of the hook body 51, so that the hook body 51 rotates clockwise, Since the pressing force against the brake plate by the pressing member 31 by the cam raised portion of the hook body 51 does not act, the braking force does not act on the movement of the slider 18.

  Further, a rotary damper 38 is attached to the rear end portion of the slider 18 so as to be rotatable about its rotation fulcrum, and an inter-axis straight line connecting the rotation fulcrum and the rotation shaft 42 of the pinion 43 of the rotary damper 38 is formed. Since the rack 13 is inclined in a non-buffering direction with respect to the vertical line with respect to the tooth tip surface, when the engagement pin 5 of the sliding door 4 is moved in the opening direction of the sliding door 4, the slider 18 is also moved together with it. Accordingly, a force in the moving direction of the slider 18 acts on the rotation fulcrum of the rotary damper 38 attached to the slider 18 so as to be able to rotate, whereby the teeth of the pinion 43 of the rotary damper 38 and the teeth of the rack 13 are engaged. Rotation force is generated to rotate the rotary damper 38 in a direction in which the rotary damper 38 is rotated in a direction in which the rotary shaft 38 is detached, that is, in a direction in which the inclination angle of the straight line between the axes with respect to the tooth surface of the rack 13 decreases. Is released.

  Therefore, in the opening operation of the sliding door 4, since the braking action due to the engagement between the teeth of the rotary damper 38 and the teeth of the rack 13 does not occur, the opening movement force that opens the sliding door 4 in the sliding door opening direction can be reduced during the opening operation of the sliding door 2, The sliding door 4 can be opened lightly.

  Next, a second embodiment of the present invention will be described with reference to FIGS. 7 and 8, a third embodiment with reference to FIGS. 9 and 10, and a fourth embodiment with reference to FIGS. In each of the drawings showing these embodiments, parts having the same or similar functions as those shown in FIGS. 1 to 6 are denoted by the same reference numerals. Therefore, the detailed description about the structure and effect | action is abbreviate | omitted.

  First, FIGS. 7 and 8 are schematic plan views in which the back cover of the shock absorber is removed. However, only the protrusions formed on the inner surface of the back cover are additionally illustrated in corresponding portions.

  Major differences between the second embodiment of FIGS. 7 and 8 and the first embodiment are as follows.

    (1) In the first embodiment, the rotary damper 38 is pivotally attached to the slider 18 as a sliding member. In the second embodiment, the sliding member is a hook body 51. A rotary damper 38 is rotatably attached to 51.

    (2) In the second embodiment, the buffering action is caused only by braking based on the braking force of the rotary damper 38 itself and the engagement between the pinion 43 of the rotary damper 38 and the teeth 14 of the rack 13, whereas in the first embodiment. Then, the brake plate 17 is attached to the case body, the slider 18 that slides in the attachment recess 3 of the case body 2 is provided, the pressing member 30 that cooperates with the slider 18, the brake pads 32, 33, and the like. A braking force generated by clamping the brake plate 17 in a sandwich shape by the pressing member 30 and the brake pads 32 and 33 is added.

    (3) In the second embodiment, the constricted portion 22 on the front end side of the tension spring 21 is locked to the tension spring narrow portion 23 of the hook body 51 so that the hook body 51 is buffered by the tension spring 21, that is, on the rear end side. In contrast, in the first embodiment, the front end side of the tension spring is fixed to the front end side of the slider 18, and the slider 18 is biased by the tension spring 21 in the buffer direction.

    (4) In the second embodiment, the guide shaft 45 of the rotary damper 38 is disengaged from the inner surface of the rear end 46 of the case lid 2, and the teeth of the pinion 43 of the rotary damper 38 disengage from the teeth of the rack 13. In order to guide in the direction, a ridge 70 having a taper is provided. Accordingly, the rotary damper 38 is rotated counterclockwise about the rotation shaft 37, and the teeth of the pinion 43 and the teeth of the rack 13 are engaged from the beginning when the rotary damper 38 starts to move in the non-buffering direction. Therefore, it is possible to reduce the load when the hook body 51 moves in the non-buffering direction.

          The movement of the hook body 51 at the buffer end position is stopped by the contact of the casing 39 of the rotary damper 38 with the stopper base 69 formed at the rear end of the mounting recess 3 of the case body 2. ing. Further, the rack teeth 14 are omitted from the portion of the rack 13 facing the protrusion 70 at the buffer end position to facilitate the rotation of the rotary damper 38.

  Also in the second embodiment, a straight line (straight axis) connecting the short shaft 37 of the rotary damper 38 and the rotation shaft 42 of the pinion 43 is in a non-buffering direction with respect to a vertical line with respect to the tooth tip surface of the rack 13. Inclined.

  Therefore, when the hook body 51 is moved in the non-buffering direction, that is, in the front end direction of the case body 2, a force parallel to the movement direction in the front end direction of the hook body acts on the rotation fulcrum of the rotary damper 38. In other words, a force is generated to rotate the rotary damper 38 counterclockwise about the short axis 37 in the direction to release the engagement between the teeth of the pinion 43 and the teeth of the rack 13, and the teeth of the pinion 43 and the rack 13 are There is no meshing with the teeth.

  On the other hand, when the rotary damper 38 moves in the buffering direction, the tension spring 21 causes a force to rotate clockwise around the rotating short shaft 37 by the tension spring 21, and the buffering action of the rotary damper 38. Thus, a buffering action based on the meshing resistance force between the teeth of the rotary damper 38 and the teeth 14 of the rack 13 occurs.

  FIG. 7 shows a standby state in which the hook body 51 is waiting for the engaging pin 5 of the moving body 4. In this case, the engaging convex portion 55 of the hook body 51 is located in the rotating groove portion 12 of the sliding groove 10. From this state, the hook body 51 is rotated by the contact of the engaging pin 5 of the moving body 4, and the engaging pin 5 of the moving body 4 enters the holding recess portion of the hook body 51 and engages with the hook body 51. The convex portion 55 moves from the rotating groove portion 12 to the moving groove portion 11, and the hook body 51 moves in the buffer direction by the tensile force of the tension spring 21.

  Then, the pinion 43 of the rotary damper 38 rotatably attached to the short shaft 37 on the hook body 51 is started to move in the buffering direction by the protrusion 47 provided inside the back cover 46 of the case body 2. The tooth of the pinion 43 is engaged with the tooth of the rack 13 from the beginning of the movement because it is located at the missing portion of the tooth of the hour rack 13. At that time, the shaft can be rotated to the short shaft 37 by the frictional force between the sliding friction shaft 49 attached to the rotary damper casing 39 and the inner surface of the back cover 46 of the case body 2 and the buffering direction force applied to the hook body. A rotating force is generated to rotate the supported rotary damper 38 in the clockwise direction, and the teeth of the pinion 43 and the teeth 14 of the rack 13 are engaged with each other, and the hook body 51 and the engagement held by the holding recess 56 of the hook body are engaged. The pin 5 moves while being buffered in the buffer direction. When the pinion 43 reaches the missing tooth portion of the rack 13 at the buffer end position, the rotary damper 38 is guided by the taper surface of the ridge 70 provided on the inner surface of the back cover 46, and the rotary damper 38 is rotated. The damper 38 is rotated counterclockwise about the short axis 37. As a result, the rotary damper 38 reaches a rotational position where the teeth of the pinion 43 do not mesh with the teeth of the rack 13 at the buffer end position.

  FIG. 8 shows the state of the buffer end position of the shock absorber. When the hook body 51 and the engaging pin 5 start moving from the buffer end position toward the front end of the case body 2 against the tensile force of the tension spring 21, the hook body 51 and the engaging pin 5 are pivotable to the short shaft 37 of the hook body 51. The supported rotary damper 38 has a frictional contact force between the sliding friction shaft 49 attached to the rotary damper casing 39 and sliding while elastically contacting it, and the back cover 46, and the movement of the movable body 4 and the engagement pin 5. The force causes a force to rotate the rotary damper 38 counterclockwise about the short axis 37, so that the pinion 43 teeth of the rotary damper 38 and the teeth of the rack 13 are not moved during the movement in the non-buffering direction. It will not be engaged. Therefore, when the moving body 4 moves in the non-buffering direction, the moving body 4 only needs to move against the tensile force of the tension spring 21 without being subjected to the braking action by the rotary damper 38 or the rack 13. Move power can be reduced.

  Next, a third embodiment will be described with reference to FIGS. 9 and 10 are schematic plan views showing the shock absorber with the back cover removed. However, only the protrusions formed on the back cover are shown in the corresponding portions. FIG. 9 shows the state of the engaging pin at the standby position, and FIG. 10 shows the state of the buffer end position.

  The differences between the third embodiment and the second embodiment of FIGS. 7 and 8 are as follows.

    (1) The holding entrainment body 71 is used as the sliding member, and the rotary damper 38 is rotatably attached to the low base portion 72 of the holding entrainment body 71, and the permanent magnet 74 is attached to the front end portion of the high base portion 73. Is provided to attract and hold the engaging pin 5 made of a magnetic member.

    (2) In the second embodiment shown in FIGS. 7 and 8, the tension spring 21 is provided to forcibly bring the hook body 51 to the buffer end position. However, the third embodiment shown in FIGS. Then, no forced connection means is provided. Therefore, neither the moving groove portion 11 nor the rotating groove portion 12 of the sliding groove portion 10 of the hook body is present.

    (3) The entrainment holder 71 is slidably guided by the left and right side walls of the mounting recess 3 of the case body.

    (4) In the third embodiment, the engagement pin standby position of the entrainment holding body 71 is the front end wall of the mounting recess 3 of the case body 2, and the entrainment end position is a force applied from the moving body 4 via the engagement pin 5. When the force applied from the engagement pin 5 is large or the position determined by the buffering force of the rotary damper 38 and the meshing resistance force between the teeth of the pinion 43 of the rotary damper 38 and the teeth of the rack 13 is large, it depends on the final position of the rotary damper 38. Take a determined position.

          At the final position of the rotary damper 38, the entrainment holding body 71 is in contact with the front end wall of the stopper portion 75 protruding from the right rear end portion of the mounting recess 3 of the case body 2.

  As is apparent from the above, in the third embodiment, since there is no tension force of the tension spring 21 that goes against the buffering force of the rotary damper 38 of the moving body 4, the rotary damper 38 is used in the second embodiment. When the same rotary damper is used, the buffering effect is increased.

  Furthermore, in the third embodiment, when the movable body 4 is moved in the non-buffering direction, the teeth of the pinion 43 of the rotary damper 38 and the teeth of the rack 13 do not mesh with each other, and the tension spring 21 does not exist. Therefore, the moving force of the moving body in the non-buffering direction can be reduced.

  As described above, the permanent magnet 74 is disposed in the holding entrainment body 71, the engaging pin 5 is a permanent magnet, and a magnetic body such as an iron material can be used in place of the permanent magnet 74 provided in the holding entrainment body 71. Of course, both may be permanent magnets. As the permanent magnet, a magnet made of a ferromagnetic material such as a ferrite magnet can be used.

  In addition, it is preferable that the attracting force is improved by flattening both attracting surfaces of the engaging pin 5 and the permanent magnet 74. When the rotary damper 38 is moved in the non-buffering direction, the pinion 43 and the teeth of the rack 13 are not meshed with each other so that the holding entrainment body 71 and the rotary damper 38 are moved as a sliding load. Since it is only necessary that the engaging pin 5 can be taken to the standby position, a very strong magnet is not necessary.

  Next, a fourth embodiment will be described with reference to FIGS.

  FIG. 11 and FIG. 12 are both schematic plan views with the back cover of the shock absorber removed. However, only the protrusions formed on the back cover are shown in the corresponding portions. The difference of this embodiment from the third embodiment is as follows.

    (1) An elastic member such as plastic or rubber metal is used for the holding portion that entrains the engaging pin 5 of the holding entraining body 71 as a sliding member, and a bag hole 76 is formed in a portion facing the engaging pin 5. Although the narrow protrusion 77 at the entrance of the bag hole is narrower than the diameter of the engagement pin, the engagement pin 5 is narrowed by its moving force in the buffering direction. The projecting portion is expanded to enter the bag hole. In this embodiment, the inlet portion of the bag hole is tapered toward the inside in order to facilitate the introduction of the engagement pin 5.

    (2) Adjacent to the bag hole 76, slots 78 are formed on the left and right sides to facilitate the elastic expansion of the narrowed portion of the bag hole at the front end of the holding entraining body 71.

  Unlike the circular shape, the engagement pin 5 has a triangular cross section with rounded corners, a bag hole with a triangular cross section, and one apex of both triangles facing the buffer direction. By providing a narrow protrusion on the bottom of the square, the engagement pin 5 can easily enter and be held in the bag hole.

  The holding force due to the elasticity of the constriction is selected to such an extent that the holding entrainment body 71 can be taken to the standby position by the engagement pin 5.

  Other operations of the shock absorber in the buffering direction and the non-buffering direction are the same as those in the third embodiment.

It is a disassembled perspective view of 1st Example of the buffering device of this invention. It is the plane top view in the buffering operation end operation position which removed the back cover of the buffer device of the Example of Drawing 1, and was seen from the back side. FIG. 2 is a schematic plan view of the shock absorber shown in FIG. 1 at an operating position during movement in a non-buffer direction. FIG. 2 is a schematic plan view showing an engaging pin standby posture operation position of a moving body to be buffered in the shock absorber shown in FIG. 1. FIG. 2 is a schematic plan view showing an operation position during a buffering operation of a moving motion of a moving body of the shock absorber shown in FIG. 1. 1 is a schematic perspective view of a device to which a shock absorber according to the present invention is applied. It is a plane schematic diagram of the standby state of 2nd Embodiment of the buffering device of this invention. It is a plane schematic diagram of the state of the buffer end position of the shock absorber of the second embodiment shown in FIG. It is a plane schematic diagram of the waiting state of a 3rd embodiment of the buffering device of the present invention. FIG. 10 is a schematic plan view showing a state of a buffer end position of the shock absorber according to the third embodiment shown in FIG. 9. It is a schematic plan view of a standby state of a fourth embodiment of the shock absorber according to the present invention. FIG. 12 is a schematic plan view showing a state of a buffer end position of the shock absorber according to the fourth embodiment shown in FIG. 11.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Buffer body 2 Case body 3 Mounting recessed part 4 Moving body 5 Engagement pin 6 Mounting plate 7 Bottom face part 8 Guide slot 9 Tapered guide part 10 Sliding groove 11 Moving groove part 12 Turning groove part 13 Rack 14 Rack tooth 15 Protrusion Part 16 Fixed groove 17 Brake plate 18 Slider 19 Slider left side 20 Slider right side wall 21 Tension spring 22 Tension spring constriction part 23 Tension spring holding part 24 Guide wall 25 High platform part 26 Low platform part 27 Slot 28 Locking groove 29 30-shaped portion 30 receiving groove 31 pressing member 32 brake pad 33 brake pad 34 mounting protrusion 35 mounting groove 36 right corner lower base portion 37 short shaft 38 rotary damper 39 rotary damper casing 40 overhanging portion 41 sleeve bearing 42 rotating shaft 43 pinion 44 Stopper 45 Guide shaft 46 Back cover 47 Projection 48 Support portion 49 Sliding friction shaft 50 Bearing hole 51 Hook body 52 Low base portion 53 High base portion 54 Short shaft 55 Engaging convex portion 56 Holding concave portion 57 Cam raised portion 58 Mounting concave portion 60 Mounting hole 61 Mounting hole 65 Upper guide rail 66 Support shaft 67 Four-wheel carriage 68 Extension part 69 Stopper base part 70 Projection 71 Holding body 72 Low base part 73 High base part 74 Permanent magnet 75 Stopper base part 76 Bag hole 77 Constriction 78 Slot

Claims (4)

  In the shock absorber that buffers relative movement between the first member and the second member, the first member includes a case body provided with a rack, a sliding member that slides in the case body together with the second member, and the sliding member. A rotary damper having a pinion pivotally supported by the moving member and meshing with the rack, and an inter-axis straight line connecting a rotation axis of the pinion of the rotary damper and a rotation fulcrum of the sliding member is It is inclined toward the direction opposite to the buffering direction of the sliding member with respect to the vertical line with respect to the tooth tip surface of the rack, and the sliding member is moved in the direction of the inclined side in the case body. The rotary damper is configured to rotate in a direction to disengage the engagement between the rack and the pinion teeth around the rotation fulcrum.   When the sliding member slides in the case body, the rotary damper includes a sliding friction member that elastically slides with respect to the case body, and friction generated between the sliding friction member and the case body When the sliding member is in one moving direction, the rotational force that causes the rotary damper to rotate about its rotation fulcrum in a direction to release the meshing between the pinion of the rotary damper and the teeth of the rack. When the sliding member moves in the other moving direction, a turning force is applied to rotate about the rotation fulcrum of the rotary damper in the direction in which the pinion of the rotary damper and the teeth of the rack are engaged with each other. The shock absorber according to claim 1, wherein the shock absorber is configured as described above.   The rack provided in the longitudinal direction in the case body has a meshing guide portion in which the rack teeth are not formed at an end portion on the side where the straight line between the axes is inclined. Guide means for rotating the rotary damper rotated in a direction in which the engagement between the pinion teeth of the rotary damper and the teeth of the rack is released in a direction in which the teeth of the pinion and the teeth of the rack are engaged. The shock absorber according to claim 1, wherein the shock absorber is provided.   Means for rotating the rotary damper about its rotation fulcrum in a direction to disengage the engagement between the pin of the rotary damper and the tooth of the rack at the buffer end position of the rotary damper; The shock absorber according to any one of claims 1 to 3.

Images