JP2015094463A - Vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an axial force member type vibration damping device, which attains high practical utility and versatility, whose manufacturing cost and weight are reduced, which facilitates the adjustment of a spring constant, and enables the maximum value of damping force to be limited.SOLUTION: A damping device 1 is configured to be extendable and contractible, and makes damping force to vibration of a building act as axial force along an extending and contracting direction. The damping device comprises: a sliding mechanism 9 having a convex sliding part 7 and a concave sliding part 8 and forming a tubular outer peripheral surface 9a, the convex sliding part 7 provided integrally with a first joint part 5 on a one end side in the extending and contracting direction, which is a connection portion to the building, the concave sliding part 8 fitted to the convex sliding part 7 and reciprocating in a direction along the extending and contracting direction; and a biasing wire 10 provided along the outer peripheral surface 9a and biasing the sliding mechanism 9. The sliding parts 7, 8 have two kinds of sliding surfaces of central siding surfaces 35, 45 and outer sliding surfaces 34, 44, which have shapes of increasing dimensions in directions, in which the sliding parts of the sliding mechanism face each other, with increase in displacement from a neutral position in a sliding direction.

Description

  The present invention relates to a vibration damping device that suppresses vibration of a structure.

  Conventionally, there is a viscous damping device such as an oil damper as one of the categories of vibration damping devices (hereinafter also simply referred to as “damping devices”) that suppress vibrations of structures. In a viscous damping device, generally, the damping force is proportional to the speed of vibration (natural vibration) of a structure. Therefore, according to the viscous damping device, it is difficult to obtain a sufficient damping force as the vibration period of the structure is long. For this reason, the damping device is applied to a long-period structure having a relatively long vibration cycle. In order to obtain a desired damping force, there is a problem that the size of the device or the performance of the device needs to be improved.

  Another class of damping device is a friction type damping device. In the friction type damping device, generally, the magnitude of the frictional force acting as the damping force is constant regardless of the displacement caused by the vibration of the structure. For this reason, according to the friction-type damping device, when the vibration amplitude is relatively small, the function of the device is not sufficiently exhibited due to the sticking of the sliding surfaces (sliding surfaces) that generate the frictional force. When the amplitude of vibration is relatively large, there is a problem that the equivalent viscous damping coefficient decreases as the amplitude increases. Here, the equivalent viscous damping coefficient is obtained by converting the damping performance of the damping device into the viscous damping coefficient of the viscous damping device, and is a numerical value that serves as an index of the damping performance of the damping device alone.

  As described above, based on the problems of each type of damping device, the damping effect continues even if the natural vibration mode of the structure becomes longer, and the equivalent viscous damping coefficient decreases as the amplitude increases. A non-attenuating device is ideal. Here, attention is focused on a friction type damping device having a relatively simple mechanism for generating damping force. According to the friction type damping device, the effect of the damping on the damping effect due to the long period of the natural vibration mode of the structure is relatively small, so the magnitude of the frictional force changes with the displacement due to the vibration of the structure. By doing so, it is considered that the problem depending on the amplitude as described above is solved, and an ideal attenuation device can be obtained.

  Therefore, as a vibration damping device, there has been proposed a displacement proportional friction force type vibration damping device in which a frictional force as a damping force is increased in proportion to an increase in operating displacement of the damping device (Patent Document 1, Non-Patent Document 1). -3)). Such a damping device includes a sliding body mechanism having at least a pair of sliding bodies provided so as to be reciprocally slidable in a predetermined direction in a state of facing each other, and a sliding body in a direction in which the sliding bodies face each other (a direction in which they are pressed against each other). Biasing means for biasing the mechanism.

  The sliding body mechanism has a sliding surface of a predetermined shape in each sliding body, so that the sliding bodies face each other in proportion to the displacement of the sliding bodies in the reciprocating sliding direction, that is, the increment of the operating displacement. The size (assembly height) is increased. In contrast to such a sliding body mechanism, the biasing means has a predetermined spring constant in the direction in which the assembly height of the sliding body mechanism increases or decreases, and the displacement due to relative sliding of the pair of sliding bodies increases. An increasing compressive force in the pressing direction is applied to the sliding body mechanism.

  The displacement proportional friction force type damping device having such a configuration acts on the sliding surface of the sliding body mechanism by the interaction between the increase in the assembly height of the sliding body mechanism and the biasing force (pressing force) by the biasing means. The compressive force to be increased increases in proportion to the increase in operating displacement, and the principle of Coulomb friction is used to generate a frictional force or damping force that increases in proportion to the increase in operating displacement.

Japanese Patent No. 5286487

Takuro Katayama, Toshitaka Yamao: "Study on sliding damping device that generates frictional force proportional to the absolute value of displacement", Proceedings of Japan Society of Civil Engineers A Vol.66 No.4, pp.783-798, December 2010 Takuro Katayama, Koji Higashi: “Trial manufacture and loading test of leaf spring used for vibration damping device with displacement proportional frictional force”, Summary of 67th Annual Conference of Japan Society of Civil Engineers (CD-ROM), pp.831-832, September 2012 Takuro Katayama, Koji Higashi: “Reciprocating loading test of vibration damping device with displacement proportional frictional force”, Summary of 68th Annual Conference of Japan Society of Civil Engineers (CD-ROM), pp.233-234, September 2013

  The displacement proportional frictional force type damping device described above constitutes an urging means using a substantially U-shaped leaf spring (U-shaped leaf spring). According to Non-Patent Document 2, a spring steel material such as SUP10 is used as the material of the U-shaped leaf spring in order to improve the performance of the device. The U-shaped leaf spring is composed of a round bar-like material made of spring steel, and includes a rough forming process by forging and cutting, a heat treatment process such as quenching and tempering, and a forming process to a predetermined dimension by cutting. It is manufactured by going through in order.

  When a U-shaped leaf spring made of spring steel is used in this way, the manufacturing process is complicated, and the manufacturing cost of the U-shaped leaf spring in the damping device increases. Further, since the U-shaped leaf spring made of spring steel is heavier than other metal materials or the like, when the U-shaped leaf spring made of spring steel is used, the weight of the damping device is increased. Specifically, according to a trial calculation, the manufacturing cost and weight of a U-shaped leaf spring made of spring steel account for about 50% and about 10% of that of the entire damping device, respectively. For these reasons, in order to reduce the manufacturing cost of the damping device and to reduce the weight, it is desirable to develop an economical configuration that replaces the U-shaped leaf spring as the biasing means.

  In the U-shaped leaf spring, the spring constant can be set by various factors such as the material, the plate thickness, the radius of curvature of the bent portion, and the length of the straight portion. However, according to the U-shaped leaf spring made of a spring steel material, the manufacturing process is complicated as described above. Therefore, it is not easy to adjust the spring constant by each of the above elements in the manufacturing process. Therefore, it is desirable to develop a biasing means that can easily adjust the spring constant.

  Furthermore, since the damping force of the displacement proportional friction type damping device increases in proportion to the increment of the operating displacement, the operating displacement increases during a large earthquake such as a large-scale oceanic plate boundary earthquake. As a result, the damping force becomes excessively large. In order to cope with such an excessive damping force, it may be difficult to design the strength of the mounting portion of the damping device on the structure side. In particular, when the damping device is attached to an existing structure, securing the strength at the attachment portion on the structure side becomes a problem. Therefore, the displacement proportional friction force type damping device is desired to have a function capable of limiting the magnitude of the damping force regardless of an increase in the operating displacement.

  The present invention has been made in view of the above circumstances, and has a simple structure and efficiently absorbs vibration energy from a small amplitude to a large amplitude without depending on the length of vibration of the structure. High practicality and versatility, reduction in manufacturing cost and weight reduction, easy adjustment of spring constant, and damping according to operating displacement An object of the present invention is to provide a vibration damping device capable of limiting the maximum value of force.

  The vibration damping device according to the present invention is configured to be extendable and contractible in a predetermined direction, and is a vibration damping device that suppresses vibration of a structure by causing a damping force against vibration of the structure to act as an axial force along the expansion and contraction direction. A first sliding portion provided integrally with a connecting portion with respect to the structure on one end side in the expansion / contraction direction, and the first sliding portion in a state facing the first sliding portion A sliding mechanism having a second sliding portion provided so as to be reciprocally slidable in a direction along the expansion / contraction direction, and forming a cylindrical outer peripheral surface with the expansion / contraction direction as a cylinder axis direction; An urging means provided along the outer peripheral surface, for urging the sliding mechanism in a direction in which the first sliding portion and the second sliding portion are pressed against each other; The sliding portions of the first sliding portion and the second sliding portion are slid on the other side to slide. The sliding portions of the sliding mechanism face each other as the amount of displacement increases in one of the reciprocating sliding directions from the neutral position in the range of relative reciprocating sliding with respect to The amount of displacement in the other direction of the reciprocating sliding direction from the neutral position with respect to the first sliding surface having a shape that increases the size of the direction and the sliding part of the other party sliding And a second sliding surface having a shape that increases the size of the sliding mechanism in the opposing direction.

  In the vibration damping device according to one aspect of the present invention, one of the first sliding portion and the second sliding portion is opposed to the sliding portion of the other party that slides. The side surface portion has a protruding portion that extends along the reciprocating sliding direction and protrudes toward the opposing side and has a convex shape in the reciprocating sliding direction, and includes the first sliding portion and the second sliding portion. The other sliding portion of the moving portions has a groove portion that is formed in the surface portion on the opposite side along the reciprocating sliding direction and that is open on the facing side and has a concave shape when viewed in the reciprocating sliding direction. The first sliding portion and the second sliding portion have a base end surface of the projecting portion and an end surface on the opening side of the groove portion of the first sliding surface and the second sliding surface, respectively. Either one of the sliding surfaces, the end surface on the protruding side of the protrusion and the bottom surface of the groove, the first sliding surface and the second And the other of the sliding surfaces of the sliding surface.

  Further, in the vibration damping device according to one aspect of the present invention, the sliding mechanism includes the first sliding portion and the first sliding portion corresponding to the first sliding portion at a plurality of equiangular ranges around the axis of the axial force. Two sliding portions, and in the state where these sliding portions are in the neutral position, the side opposite to the side facing the first sliding portion of the plurality of second sliding portions. This surface forms a cylindrical outer peripheral surface.

  Moreover, in the vibration damping device according to one aspect of the present invention, the sliding mechanism includes the first sliding portion and the second sliding corresponding thereto at four locations around the axis of the axial force. A cylindrical portion by a surface opposite to the first sliding portion of the four second sliding portions in a state where these sliding portions are in the neutral position. The outer peripheral surface of the shape is made.

  In the vibration damping device according to one aspect of the present invention, the biasing means is a cord-like member wound around the outer peripheral surface of the sliding mechanism.

  In the vibration damping device according to one aspect of the present invention, the cord-like member is a superelastic alloy wire.

  The vibration damping device according to an aspect of the present invention includes a cylinder member that has a cylindrical outer shape with the expansion and contraction direction as a cylinder axis direction, and surrounds the sliding mechanism and the biasing unit. It is filled with a viscous fluid.

  According to the present invention, vibration energy can be efficiently absorbed from a small amplitude to a large amplitude without depending on the length of vibration of the structure with a simple structure, and is highly practical and versatile. The manufacturing cost can be reduced and the weight can be reduced, the spring constant can be easily adjusted, and the maximum value of the damping force can be limited according to the operating displacement.

1 is a perspective view showing an appearance of a vibration damping device according to a first embodiment of the present invention. 1 is a longitudinal sectional view of a vibration damping device according to a first embodiment of the present invention. It is a cross-sectional view of the vibration damping device according to the first embodiment of the present invention. It is a perspective view which shows the sliding mechanism of the vibration damping apparatus which concerns on 1st Embodiment of this invention. It is a perspective view which shows the sliding mechanism and urging | biasing means of the vibration damping apparatus which concern on 1st Embodiment of this invention. It is a disassembled perspective view which shows the structure of the 1st sliding part of the vibration damping apparatus which concerns on 1st Embodiment of this invention. It is a disassembled perspective view which shows the structure of the sliding mechanism of the vibration damping apparatus which concerns on 1st Embodiment of this invention. It is a perspective view which shows the sliding body mechanism of the vibration damping apparatus which concerns on 1st Embodiment of this invention. It is a perspective view which shows the sliding body mechanism of the vibration damping apparatus which concerns on 1st Embodiment of this invention. It is a perspective view which shows the sliding body mechanism of the vibration damping apparatus which concerns on 1st Embodiment of this invention. It is a perspective view which shows an example of the sliding surface of the vibration damping apparatus which concerns on 1st Embodiment of this invention. It is a figure which shows the component of the vibration damping device which concerns on 1st Embodiment of this invention. It is a figure which shows the component of the vibration damping device which concerns on 1st Embodiment of this invention. It is a figure which shows the component of the vibration damping device which concerns on 1st Embodiment of this invention. It is a figure which shows the component of the vibration damping device which concerns on 1st Embodiment of this invention. It is a longitudinal section showing the expansion state of the vibration damping device concerning a 1st embodiment of the present invention. It is a cross-sectional view which shows the expansion | extension state of the vibration damping apparatus which concerns on 1st Embodiment of this invention. It is a longitudinal cross-sectional view which shows the shortened state of the vibration damping apparatus which concerns on 1st Embodiment of this invention. It is a cross-sectional view showing a shortened state of the vibration damping device according to the first embodiment of the present invention. It is explanatory drawing about the dynamic characteristic of the vibration damping device which concerns on 1st Embodiment of this invention. It is explanatory drawing about the dynamic characteristic of the vibration damping device which concerns on 1st Embodiment of this invention. It is a figure which shows an example of the stress degree-strain curve of the superelastic alloy wire with which the vibration damping apparatus which concerns on 1st Embodiment of this invention is provided. It is a figure which shows the calculation model which idealized the relationship between the stress degree and distortion | strain of the superelastic alloy wire with which the vibration damping apparatus which concerns on 1st Embodiment of this invention is provided. It is a figure which shows an example of the relationship between the operation displacement and damping force in the vibration damping device which concerns on 1st Embodiment of this invention. It is a figure which shows an example of the relationship between the operation displacement and damping force in the vibration damping device which concerns on 1st Embodiment of this invention. It is a figure which shows an example of the trial calculation result of the yield working displacement in the vibration damping device which concerns on 1st Embodiment of this invention. It is a cross-sectional view of the vibration damping device according to the second embodiment of the present invention. It is a longitudinal cross-sectional view of the vibration damping device which concerns on 2nd Embodiment of this invention. It is a longitudinal cross-sectional view which shows the modification of the vibration damping device which concerns on 2nd Embodiment of this invention. It is a figure which shows an example of the result of the operation test by the Example of this invention.

  The present invention relates to a sliding type (friction type) vibration damping device that contributes to passive vibration control of a structure, and a relative displacement amount (sliding amount) of at least a pair of sliding portions that are relatively slidable. The mechanical characteristic in which the frictional force as the damping force increases with the increase in the frequency is to be realized with a simple configuration. The present invention provides a cylindrical outer peripheral surface in which a sliding mechanism including at least a pair of sliding portions is used as an axial force in a configuration in which a damping force against vibration of a structure acts as an axial force. In addition, the urging means that presses and urges the sliding mechanism to generate a frictional force in the sliding mechanism is provided along the outer peripheral surface of the sliding mechanism, thereby reducing cost. It is intended to reduce the weight of the device and facilitate adjustment of the spring constant of the biasing means. Embodiments of the present invention will be described below.

[First Embodiment]
A first embodiment of the present invention will be described. A vibration damping device (hereinafter simply referred to as “damping device”) 1 according to the present embodiment is installed on a predetermined structure to suppress vibration of the structure. The damping device 1 is configured to be extendable and contractible in a predetermined direction, and suppresses the vibration of the structure by causing the damping force against the vibration of the structure to act as an axial force along the expansion and contraction direction.

  As shown in FIG. 1, the damping device 1 includes an intermediate cylindrical portion 2 having a substantially cylindrical outer shape and a cylindrical axis direction (center axis direction) of the intermediate cylindrical portion 2 as a portion having an overall schematic shape. A first shaft portion 3 and a second shaft portion 4 that protrude from both sides of the intermediate tube portion 2 are provided. That is, the damping device 1 as a whole has a mode in which a diameter-enlarged portion is formed by the intermediate cylindrical portion 2 in an intermediate portion of the shaft-shaped portion having the first shaft portion 3 and the second shaft portion 4 as both end portions. .

  The attenuation device 1 is configured to be extendable / contractable with the axial direction along which the first shaft portion 3 and the second shaft portion 4 are aligned as the expansion / contraction direction. That is, the damping device 1 sets the axial direction along which the first shaft portion 3 and the second shaft portion 4 are aligned as the direction of the axial force acting as a damping force on the structure. The damping device 1 has a first joint portion 5 provided at a distal end portion of the first shaft portion 3 at both ends in the axial direction (stretching direction, hereinafter referred to as “device axial direction”) as a connecting portion to a structure. And a second joint portion 6 provided at the distal end portion of the second shaft portion 4. Each of the first joint portion 5 and the second joint portion 6 has an annular or cylindrical connecting portion at the end of the shaft portion, and this connecting portion is connected to a predetermined mounting portion provided on the structure side. As a result, the damping device 1 is connected to the structure.

  The damping device 1 includes a central axial force transmission portion, which is an integral structural portion including the first joint portion 5, and a second joint portion 6 as a structural portion that expands and contracts the damping device 1 by relatively reciprocating sliding. It has two axial force transmission parts with the outer side axial force transmission part which is an integral structural part. These two axial force transmission parts have mutual sliding parts in the intermediate cylinder part 2 part. The damping device 1 expands and contracts by changing the distance in the device axial direction between the first joint portion 5 and the second joint portion 6 by relative sliding of the central axial force transmission portion and the outer axial force transmission portion. . Details of the central axial force transmission unit and the outer axial force transmission unit will be described later.

  As shown in FIG. 2 to FIG. 7, the damping device 1 has a convex sliding portion 7 and a concave sliding portion 8 as parts constituting the intermediate cylindrical portion 2, and the axial direction of the device (the horizontal direction in FIG. 2 ( A sliding mechanism 9 having a cylindrical outer peripheral surface with the cylinder axis direction as indicated by an arrow A1) and a biasing wire 10 for applying a predetermined biasing force to the sliding mechanism 9 are provided. 2 is a cross-sectional view in the direction of arrow Y in FIG. 3, and FIG. 3 is a cross-sectional view in the direction of arrow X in FIG. The damping device 1 is a sliding type damping device, and the convex sliding portion 7 and the concave sliding portion 8 slide relative to each other in the sliding mechanism 9 that receives the biasing force by the biasing wire 10. The generated frictional force is a damping force, and the frictional force increases in proportion to the absolute value of the relative displacement between the sliding portions.

  The convex sliding portion 7 and the concave sliding portion 8 are a pair of sliding portions provided so as to be relatively reciprocally slidable in a state of facing each other. The damping device 1 of the present embodiment includes a total of four combinations of the convex sliding portion 7 and the concave sliding portion 8 with the pair of convex sliding portion 7 and the concave sliding portion 8 as one set. The convex sliding part 7 and the concave sliding part 8 are made of a metal such as stainless steel, for example. However, the material constituting the convex sliding portion 7 and the concave sliding portion 8 is not particularly limited as long as sufficient strength can be obtained as a member constituting the attenuation device 1. For example, a polymer material such as plastic Etc.

  The convex sliding part 7 will be described. The convex sliding portion 7 corresponds to a first sliding portion provided integrally with the first joint portion 5 that is a connecting portion to a structure on one end side in the apparatus axial direction. Specifically, it is as follows.

  The damping device 1 has a central rod 11 provided in a state of penetrating the intermediate cylindrical portion 2 along the position of its central axis. The central rod 11 is a rod-shaped member having a circular cross-sectional shape, and is provided so as to be movable relative to the intermediate cylinder portion 2 along the axial direction thereof. The central rod 11 moves relative to the intermediate cylinder part 2 to change the amount of protrusion from the intermediate cylinder part 2. A first joint portion 5 is provided at an end portion on one side (right side in FIG. 2) in the axial direction of the central rod 11 protruding from the intermediate cylinder portion 2. That is, the first shaft portion 3 is configured by a protruding portion from the intermediate cylinder portion 2 on one side in the axial direction of the central rod 11.

  The first joint portion 5 is constituted by a joint member 12 attached to one end of the central rod 11. The joint member 12 includes an axial or columnar shaft portion 12a and an annular or cylindrical connecting portion 12b provided on one end side of the shaft portion 12a. At the end of the shaft portion 12a opposite to the connecting portion 12b side, a female screw portion 12c extending in the axial direction of the shaft portion 12a is formed so as to open to the end portion of the shaft portion 12a. The joint member 12 is fixed to the end portion of the central rod 11 by receiving a threaded insertion of a male screw portion 11a provided as a reduced diameter portion at the end portion of the central rod 11 in the female screw portion 12c. As described above, the first joint portion 5 is provided at one end side, and the convex sliding portion 7 is provided at an intermediate portion of the central rod 11 provided so as to be relatively movable in the axial direction with respect to the intermediate cylinder portion 2.

  The convex sliding portion 7 is configured by fixing the convex sliding body 30 to a rectangular parallelepiped sliding body supporting portion 13 provided at a substantially central portion of the central rod 11. The sliding body support portion 13 is configured by fixing a support member 14 having a rectangular parallelepiped outer shape to a substantially central portion of the central rod 11 (see FIG. 6).

  The support member 14 is a rectangular parallelepiped member having a square cross-sectional shape, and has a through hole 14a located at the center of the cross-section. The through hole 14 a is a hole having a circular cross section that is aligned with the center of the cross sectional shape of the support member 14 and opens at both end faces 14 b in the longitudinal direction of the support member 14. The support member 14 is fixed to a substantially central portion of the central rod 11 with the central rod 11 passing through the through hole 14a. The central rod 11 and the support member 14 are fixed to each other by shrink fitting or welding using the through hole 14a, for example. The four rectangular side surfaces of the support member 14 serve as a support surface 13 a to which the convex slide body 30 is fixed in the slide body support portion 13.

  The convex sliding body 30 is a member having a substantially rectangular plate-like outer shape as a whole, and has a flat bottom surface 31 on one plate surface side and a protrusion 32 on the other plate surface side, The surface shape is a convex shape. The protrusion 32 is a protrusion that protrudes in a rectangular shape in cross section, and is provided along the longitudinal direction of the convex sliding body 30 at the center in the short direction of the plate surface of the convex sliding body 30. . The protrusion 32 is formed over the entire length of the convex sliding body 30.

  The convex slide body 30 has a shape and dimensions of the bottom surface 31 substantially the same as the shape and dimensions of the support surface 13a of the slide body support portion 13 (side surface of the support material 14). The convex slide body 30 has a support member 14 that constitutes the slide body support portion 13 in a state where the longitudinal direction of the protrusion 32 is aligned with the apparatus axial direction and the bottom surface 31 is aligned with the support surface 13 a of the slide body support portion 13. Fixed to. The convex slide body 30 is fixed to the support member 14 by, for example, bolt fastening or welding with a stripper bolt or the like. In the present embodiment, the dimension in the short direction of the convex sliding body 30 is slightly smaller than the dimension in the short direction of the supporting surface 13a, and in each supporting surface 13a to which the convex sliding body 30 is fixed, The edges on both sides in the short direction are exposed along the long side of the support surface 13a (see FIGS. 3 and 7).

  As described above, the convex slide body 30 is fixed to the slide body support portion 13, so that the four support portions of the slide body support portion 13 around the axis of the central rod 11 are provided at the substantially central portion in the axial direction of the central rod 11. Convex-type sliding portions 7 are provided at four positions corresponding to the surface 13a. That is, the four convex sliding parts 7 have two straight lines in which the projecting direction of the projecting part 32 passes through the axial center position of the central rod 11 when viewed in the apparatus axial direction (viewed in the axial direction of the central rod 11). It is provided so that it may become the direction of the outside which meets. The four convex sliding parts 7 have the same shape, dimensions, etc., and are arranged around the axis of the central rod 11 so as to be vertically symmetric and laterally symmetric as viewed in the apparatus axial direction (see FIG. 3). . The convex sliding part 7 has a longitudinal direction along which the projecting part 32 of the convex sliding body 30 extends, that is, the apparatus axial direction as a relative sliding direction with respect to the concave sliding part 8. As described above, the convex sliding portion 7 protrudes on the side facing the concave sliding portion 8 along the reciprocal sliding direction on the surface facing the concave sliding portion 8 of the counterpart to slide. The projection 32 has a convex shape in the direction of reciprocating sliding.

  The central rod 11, and the support member 14 and the convex sliding body 30 constituting the convex sliding portion 7 form an integral structure by being fixed between the members. That is, each of these members constitutes a portion that moves integrally with the relative movement of the central rod 11 with respect to the intermediate tube portion 2. The part which makes this integral structure is equivalent to the central axial force transmission part which is an integral structural part in which the 1st coupling part 5 is provided as mentioned above. That is, the central axial force transmission portion constitutes a first joint portion 5, a central rod 11 provided with the first joint portion 5 on one end side, and a convex sliding portion 7 provided at an intermediate portion of the central rod 11. It is a structural part including the support member 14 and the convex slide body 30 and these members are integrally formed by bolt fastening or the like.

  As described above, the convex sliding portion 7 is integrally provided with the central rod 11 at the substantially central portion of the central rod 11 in which the first joint portion 5 is provided on one end side in the axial direction. It is provided integrally with the first joint portion 5 which is one connecting portion to the structure of the device 1. In the present embodiment, the convex sliding portion 7 is configured by fixing the convex sliding body 30 to the support member 14 fixed to the central rod 11, but the central rod 11 and the support member 14 are configured. May be an integral member, or the support member 14 and the convex sliding body 30 may be an integral member.

  The concave sliding portion 8 will be described. The concave slide portion 8 is a second slide provided so as to be reciprocally slidable in a direction along the device axial direction relative to the convex slide portion 7 in a state of facing the convex slide portion 7. It corresponds to the part. The concave sliding portion 8 is constituted by a concave sliding body 40 that is a member constituting the intermediate cylinder portion 2.

  The concave slide body 40 is a member having a substantially rectangular plate-like outer shape as a whole, and a partial shape of a cylindrical outer peripheral surface is formed on one plate surface side opposite to the side facing the convex slide body 30. The outer curved surface 41 is formed, and the groove portion 42 is provided on the other plate surface side which is the side facing the convex sliding body 30, and the cross-sectional shape is a concave shape. The outer curved surface 41 is formed as a quarter cylindrical surface having a predetermined radius. The outer curved surface 41 is a surface of the concave slide body 40 opposite to the side facing the convex slide body 30. The groove portion 42 is a groove-like portion that is recessed in a rectangular shape in cross section, and is provided along the longitudinal direction of the concave slide body 40 in the center portion in the short direction of the plate surface of the concave slide body 40. The groove portion 42 is formed over the entire length of the concave slide body 40. The groove portion 42 is a portion into which the protrusion 32 of the convex sliding body 30 is fitted.

  As described above, the concave slide body 40 having the outer curved surface 41 and the groove portion 42 is provided in a state of being fitted to the convex slide bodies 30 constituting the four convex slide portions 7 in the intermediate cylinder portion 2. The concave sliding portion 8 is configured. That is, the concave slide body 40 is provided corresponding to each convex slide body 30 constituting the four convex slide parts 7, and the four concave slide parts 8 are provided around the axis of the central rod 11. . Accordingly, the four concave sliding portions 8 are arranged so as to be vertically symmetric and laterally symmetric as viewed in the apparatus axial direction, as with the convex sliding portion 7 (see FIG. 3). The concave sliding portion 8 has a longitudinal direction along which the groove portion 42 of the concave sliding body 40 extends as a relative sliding direction with respect to the convex sliding portion 7. As described above, the concave sliding portion 8 opens on the side facing the convex sliding portion 7 along the reciprocating sliding direction and on the side facing the convex sliding portion 7. It has the groove part 42 which makes a concave shape by the moving direction view.

  In addition, the four concave slide bodies 40 arranged around the axis of the central rod 11 are used as end faces on both long sides in the substantially rectangular plate-like outer shape, that is, around the axis of the central rod 11, that is, the sliding mechanism 9. It has the mating surface 43 with respect to the concave slide body 40 adjacent to the circumferential direction. The mating surface 43 is a surface that forms a boundary between the concave slide bodies 40 that are adjacent to each other in the circumferential direction of the sliding mechanism 9, and the radial direction in the circumference centered on the axial center position of the central rod 11 as viewed in the apparatus axial direction. That is, it is formed as a slope (plane) along the radial direction of the sliding mechanism 9 (hereinafter referred to as “device radial direction”). The four concave slide bodies 40 are in a state in which the mating surfaces 43 are in contact with each other between the concave slide bodies 40 adjacent to each other in the circumferential direction of the slide mechanism 9 in a neutral state in the damping device 1 described later. The four concave slide bodies 40 constitute a cylindrical portion with the mating surfaces 43 in contact with each other. However, a slight gap may be provided between the mating surfaces 43 in the neutral state.

  The concave slide body 40 has a dimension larger than the dimension in the same direction of the convex slide body 30 as a longitudinal dimension along the apparatus axial direction. The convex slide body 30 slides with respect to the concave slide body 40 within a range of dimensions in the longitudinal direction of the concave slide body 40 that is a relative sliding direction. The convex slide body 30 and the concave slide body 40 are provided so as to be relatively slidable in a state where the protrusion 32 and the groove 42 are fitted to each other.

  As described above, the sliding mechanism 9 has the convex sliding portion 7 constituted by the convex sliding body 30 and the like, and the concave sliding portion 8 constituted by the concave sliding body 40. The sliding mechanism 9 is positioned in a state where the four convex sliding bodies 30 are fitted into the cylindrical portion constituted by the four concave sliding bodies 40 corresponding to the concave sliding bodies 40. And a configuration in which the central rod 11 integral with the convex sliding body 30 is penetrated at the coaxial center position.

  The four convex sliding bodies 30 are provided so as to be slidable relative to the cylindrical portion constituted by the four concave sliding bodies 40 in the apparatus axial direction. That is, the convex sliding part 7 and the concave sliding part 8 make the device axial direction a relative sliding direction. Further, the four concave slide bodies 40 are maintained in the fitted state with respect to the convex slide body 30 from the state in which the concave slide bodies 40 adjacent to each other in the circumferential direction of the slide mechanism 9 are brought into contact with each other. In order to widen the gap between the mating surfaces 43, it is provided so as to be movable within a predetermined range so as to approach and move away from the convex slide body 30 along two device radial directions orthogonal to each other when viewed in the device axial direction. It is done. That is, the four concave slide bodies 40 are radially extended from the neutral state along the vertical and horizontal directions in the apparatus axial view shown in FIG. 3 in accordance with the relative sliding operation with the convex slide body 30. Move to spread.

  The sliding mechanism 9 forms a cylindrical outer peripheral surface with the apparatus axial direction as the cylindrical axis direction by the outer curved surfaces 41 of the four concave sliding bodies 40. That is, the sliding mechanism 9 has a quarter cylinder with a predetermined radius in a state in which the four concave sliding bodies 40 are in contact with each other with the concave sliding bodies 40 adjacent to each other in the circumferential direction of the sliding mechanism 9. By connecting four outer curved surfaces 41 that are surfaces in the circumferential direction of the sliding mechanism 9, an outer peripheral surface 9 a that is a cylindrical surface having a predetermined radius is formed. Each outer curved surface 41 forms an angle range of 90 ° with respect to the outer circumferential surface 9a having a circumferential shape when viewed in the apparatus axial direction.

  Further, in the sliding mechanism 9, there are gaps 9 b at positions outside the four corners of the support member 14 as viewed in the apparatus axial direction, that is, at positions inside the boundary portions of the adjacent concave slide bodies 40 (FIG. 3). reference). The gap 9b includes the exposed portions along the long sides on both sides in the short direction of the support surface 13a as described above, the side surfaces that are the end surfaces on both sides in the short direction of the convex slide body 30, and the groove portions of the concave slide body 40. 42 is a space formed by the end portions along the long sides on both sides in the short direction on the side where 42 is provided, and has a substantially square shape when viewed in the apparatus axial direction. The gap 9b may be closed by partially extending the convex slide body 30 or the concave slide body 40 with respect to the cross-sectional view shape, or attaching a member such as a metal fitting to each slide body.

  As described above, the sliding mechanism 9 of the present embodiment has four locations around the axis of the axial force, that is, four locations around the central axis of the sliding mechanism 9 (around the axis of the central rod 11). With the convex sliding part 7 and the concave sliding part 8 corresponding to the convex sliding part 7 and the corresponding concave sliding part 8 in an equiangular range around the axis of the axial force, the four concave sliding parts are in a state where these sliding parts are in neutral positions. The outer curved surface 41 of the moving part 8 forms a cylindrical (columnar) outer peripheral surface 9a. The state in which these sliding portions are in the neutral position with respect to the convex sliding portion 7 and the concave sliding portion 8 will be described later.

  Next, the biasing wire 10 will be described. The urging wire 10 is a cord-like member that functions as urging means for applying a predetermined urging force to the sliding mechanism 9. In this embodiment, the urging wire 10 is a superelastic alloy wire having a wire diameter of about 0.5 mm and a circular wire shape (cross-sectional shape). In the drawing, the wire diameter is exaggerated for easy understanding of the urging wire 10. Examples of superelastic alloys include nickel / titanium (Ni—Ti) alloys, Cu—Zn alloys, Ni—Al alloys, Ni—Ti—Co alloys, and the like.

  The material of the urging wire 10 is not limited to a superelastic alloy, and for example, piano steel wire, carbon fiber, chemical fiber, or the like can be used. The wire diameter of the urging wire 10 is not limited to about 0.5 mm, and may be appropriately selected according to the manufacturing range of the wire wire diameter, the cost, the performance of the attenuation device 1, and the like. Further, the element wire shape of the urging wire 10 is not limited to a circle, but may be a polygonal shape such as a rectangle or an elliptical shape, or a tape-like shape. Further, the urging wire 10 may be one in which a plurality of strands are assembled or twisted together.

  The urging wire 10 is provided along the outer peripheral surface 9a by being wound around the outer peripheral surface 9a of the sliding mechanism 9 which is a cylindrical surface. The urging wire 10 is provided in a state wound around the outer peripheral surface 9a of the sliding mechanism 9, that is, around the four concave sliding bodies 40 (see FIG. 5). The urging wire 10 is fixed to the sliding mechanism 9 by fastening both ends to the sliding mechanism 9 with bolts or the like while being wound around the sliding mechanism 9. In this embodiment, one continuous energizing wire 10 is wound at substantially equal intervals in the apparatus axial direction.

  The urging wire 10 wound around the sliding mechanism 9 is preferably a single continuous wire, but the urging wire 10 may be wound into a plurality of pieces. Further, a plurality of the urging wires 10 may be wound on the outer peripheral surface 9 a of the sliding mechanism 9 in a stacked manner. Further, the wire diameter of the urging wire 10, the density of the winding, the fixing method to the sliding mechanism 9, etc. are not particularly limited, and are appropriately adjusted and selected so as to obtain a desired urging force with respect to the sliding mechanism 9. Is done. Further, the urging wire 10 may be wound with an initial tension applied to the sliding mechanism 9.

  The urging wire 10 is wound around the sliding mechanism 9, and the combination of the four sets of the convex sliding portion 7 and the concave sliding portion 8 is directed from the radially outer side to the inner side of the sliding mechanism 9. Energize. That is, the biasing wire 10 is a direction in which the convex sliding portion 7 and the concave sliding portion 8 that reciprocate relatively slide in a state in which the damping device 1 is installed on the structure are pressed against each other. A biasing force (hereinafter referred to as “sliding portion pressing direction”) is applied to the sliding mechanism 9. In this way, the urging wire 10 functions as an urging unit that urges the sliding mechanism 9 in the sliding portion pressing direction. The urging wire 10 slides the compressive force in the sliding portion pressing direction, which increases as the displacement (displacement amount) increases due to the relative sliding of the convex sliding portion 7 and the concave sliding portion 8. Act on the mechanism 9.

  The damping device 1 having the above-described configuration is obtained by relative sliding of the convex sliding portion 7 and the concave sliding portion 8 (the convex sliding body 30 and the concave sliding body 40) constituting the sliding mechanism 9. By changing (increasing) the radial dimension of the sliding mechanism 9 against the urging force of the urging wire 10, the urging force in the sliding portion pressing direction from the urging wire 10 is received. The damping device 1 is slid as the displacement (actuation displacement) due to relative sliding of the convex sliding portion 7 and the concave sliding portion 8 (the convex sliding body 30 and the concave sliding body 40) increases. By increasing the radial dimension of the moving mechanism 9, the biasing force in the sliding portion pressing direction received from the biasing wire 10 is increased.

  Thereby, in the damping device 1, the frictional force generated between the convex sliding part 7 and the concave sliding part 8 (the convex sliding body 30 and the concave sliding body 40) acting as a damping force is accompanied by an increase in the operating displacement. Configured to increase proportionally. A change in the radial dimension of the sliding mechanism 9 due to a change in the operating displacement is allowed by expansion and contraction due to elastic deformation of the urging wire 10.

  Below, the detail of the sliding mechanism 9 is demonstrated using FIGS. 6-10. In the detailed description of the sliding mechanism 9, for convenience, as shown in FIGS. 8 to 10, a combination of a pair (a pair) of the convex sliding body 30 and the concave sliding body 40 is referred to as a sliding body mechanism 50. The sliding body mechanism 50 will be described by paying attention as appropriate. Further, as shown in FIGS. 8 to 10, the sliding body mechanism 50 has a concave sliding body 40 side as a lower side and a convex sliding body 30 side among a pair of sliding bodies in a fitted state. Upper side. Accordingly, in the sliding body mechanism 50 shown in FIGS. 8 to 10, the convex sliding body 30 and the concave sliding body 40 slide in a state in which they face each other in the vertical direction. The facing direction of the convex sliding body 30 and the concave sliding body 40 coincides with the apparatus radial direction at a predetermined position in the circumferential direction of the sliding mechanism 9. Further, in the configuration in which the convex slide body 30 slides with respect to the concave slide body 40 within the range of the longitudinal dimension of the concave slide body 40, the convex slide body 30 is relative to the concave slide body 40. A reciprocating sliding direction (sliding direction) is defined as an operating direction, and one of the operating directions in which the convex sliding body 30 is directed toward the first joint portion 5 is defined as a front side, and the second joint portion on the opposite side. The other direction toward the 6 side is the rear. The operation direction corresponds to the apparatus axial direction (see arrow A1 in FIG. 2).

  The convex slide body 30 and the concave slide body 40 have a neutral position within a relatively reciprocal sliding range, and the displacement due to the relative sliding from the neutral position corresponds to the operation displacement. That is, the convex slide body 30 slides back and forth by sliding forward and backward with respect to the concave slide body 40 with the neutral position as a reference (displacement = 0), thereby changing the operating displacement.

  Each of the convex sliding body 30 and the concave sliding body 40 has two types of sliding surfaces formed as inclined surfaces whose inclinations are opposite to each other with respect to the relative sliding direction. The moving surfaces face each other and are assembled in a contactable state. Further, the convex sliding body 30 and the concave sliding body 40 are in contact with only one type of sliding surface of the two types of sliding surfaces in a state where the convex sliding body 30 is positioned forward of the neutral position. However, in the state where the convex sliding body 30 is located behind the neutral position, only the other type of sliding surface of the two types of sliding surfaces is in contact.

  The sliding surfaces that come into contact with each other in a state in which the convex slide body 30 is positioned forward of the neutral position are projected with the displacement due to the forward slide from the neutral position of the convex slide body 30. It is formed as an inclined surface having an upward slope toward the front so as to raise 30. Further, the sliding surfaces that come into contact with each other in a state where the convex sliding body 30 is located rearward of the neutral position are convex with the displacement due to the backward sliding from the neutral position of the convex sliding body 30. In order to raise the sliding body 30, it is formed as an inclined surface having an upward slope toward the rear.

  The sliding body mechanism 50 configured by assembling the convex sliding body 30 and the concave sliding body 40 has the sliding bodies facing each other in proportion to the absolute value of the operating displacement due to the inclination of the sliding surface of each sliding body. (In the example shown in FIGS. 8 to 10, the vertical dimension, hereinafter referred to as “slider mechanism height”) is increased. The urging wire 10 wound around the sliding mechanism 9 uses the increase in the height of the sliding body mechanism as the operating displacement increases, and the outer side of the sliding mechanism 9 constituted by the four sets of sliding body mechanisms 50. Compressive force is applied. The damping device 1 uses a compressive force acting on the sliding mechanism 9 as the height of the sliding body mechanism increases to generate a frictional force having a characteristic that increases in proportion to the absolute value of the operating displacement. It is generated on the sliding surfaces of the sliding body 30 and the concave sliding body 40. Note that the height of the sliding body mechanism is a dimension from the position of the bottom surface 31 of the convex sliding body 30 to the lower end position of the outer curved surface 41 of the concave sliding body 40 in the vertical direction when viewed in the apparatus axial direction.

  The sliding body mechanism 50 has a concavo-convex portion on the surface portion of the convex sliding body 30 and the concave sliding body 40 on the side facing the counterpart, and the convex sliding body 30 and the concave sliding body are formed by the concavo-convex portion. 40 is slidably fitted. As described above, the sliding body mechanism 50 has the protrusions 32 formed on the convex sliding body 30 side and the groove portions 42 formed on the concave sliding body 40 side, as described above.

  In the convex slide body 30 having the protrusion 32, two outer sliding surfaces 34 that are base end surfaces of the protrusion 32 and a central sliding surface 35 that is an end surface of the protrusion 32 on the protruding side are formed. The The two outer sliding surfaces 34 are surfaces from which a rectangular protrusion 32 protrudes in a cross section, and are formed so as to be located on the same plane. Further, between the two outer sliding surfaces 34 and the central sliding surface 35, protruding side surfaces 36 are formed which face opposite sides in the width direction of the protruding portion 32 and are parallel to each other.

  In the concave slide body 40 having the groove portion 42, two outer sliding surfaces 44 that are end surfaces on the opening side of the groove portion 42 and a central sliding surface 45 that is the bottom surface of the groove portion 42 are formed. The two outer sliding surfaces 34 are surfaces in which rectangular grooves 42 in the cross section are recessed, and are formed so as to be located on the same plane. Further, between the two outer sliding surfaces 44 and the central sliding surface 45, groove side surfaces 46 that are opposed to each other in the width direction of the outer sliding surface 44 and are parallel to each other are formed.

  The protrusion 32 and the groove 42 are secured to each other so as not to shift in the width direction of the groove 42 while ensuring the relative slidability between the convex slide 30 and the concave slide 40 in a state of fitting with each other. , Having width dimensions of approximately the same size. That is, the dimension between the protrusion side surfaces 36 that form the protrusion 32 and the dimension between the groove side surfaces 46 that form the groove 42 are substantially the same. In addition, the protrusion height of the protrusion 32 and the depth of the groove part 42 are substantially the same.

  As described above, in the configuration in which the convex sliding body 30 and the concave sliding body 40 are slidably fitted to each other by the protrusion 32 and the groove 42, the convex sliding body 30 and the concave sliding body 40 are respectively described above. Thus, it has two types of sliding surfaces. Of the two types of sliding surfaces, one type of sliding surface contacts each other in a state where the convex sliding body 30 is positioned forward of the concave sliding body 40 with respect to the neutral position. Similarly, one of the two types of sliding surfaces causes the convex sliding body 30 to rise with the displacement due to the forward sliding from the neutral position of the convex sliding body 30. In addition, the slope has an upward slope toward the front.

  Also, the other type of sliding surface of the two types of sliding surfaces of the convex sliding body 30 and the concave sliding body 40 is such that the convex sliding body 30 is neutral with respect to the concave sliding body 40. They are in contact with each other in a state of being located behind the position. Similarly, of the two types of sliding surfaces, the other type of sliding surface raises the convex sliding body 30 in accordance with the displacement caused by the backward sliding from the neutral position of the convex sliding body 30. In addition, the slope has an upward slope toward the rear.

  In the following, the former sliding surface (the one type of sliding surface) will be referred to as “front sliding surface”, and the latter sliding surface (the other type of sliding surface) will be referred to as “rear sliding surface. " In the damping device 1 of the present embodiment, the direction indicated by the arrow B1 (the right direction in FIG. 2) in FIGS. 8 to 10 is the front, and the direction indicated by the arrow B2 (the left direction in FIG. 2) is the rear. is there.

  In the convex slide body 30 of the slide body mechanism 50 shown in FIG. 8, the central slide surface 35 is used as the front slide surface. Similarly, in the convex sliding body 30, the two outer sliding surfaces 34 are used as rear sliding surfaces. Accordingly, the central sliding surface 35 as the front sliding surface is formed as an inclined surface that faces the lower side (concave slide body 40 side) and rises forward over the entire longitudinal direction of the convex slide body 30. The Further, the outer sliding surface 34 as the rear sliding surface is formed as a slope that faces downward and rises rearward over the entire longitudinal direction of the convex sliding body 30.

  In the concave slide body 40 of the slide body mechanism 50 shown in FIG. 8, the center slide surface 45 is used as the front slide surface. Similarly, in the concave slide body 40, the two outer slide surfaces 44 are used as the rear slide surfaces. Accordingly, the central sliding surface 45 as the front sliding surface is formed as an inclined surface that faces the upper side (the convex sliding body 30 side) and rises forward over the entire longitudinal direction of the concave sliding body 40. . Further, the outer sliding surface 44 as the rear sliding surface is formed as an inclined surface that faces upward and rises rearward over the entire longitudinal direction of the concave slide body 40. Thus, each of the convex sliding body 30 and the concave sliding body 40 has one front sliding surface and two rear sliding surfaces.

  As described above, the convex sliding body 30 and the concave sliding body 40 constituting the sliding body mechanism 50 have the central sliding surfaces 35 and 45 as the front sliding surfaces and the outer sliding surfaces 34 and 44 as the rear. The sliding surface. In the present embodiment, the gradients (inclinations) of the central sliding surfaces 35 and 45 that are the front sliding surfaces and the outer sliding surfaces 34 and 44 that are the rear sliding surfaces are equal to each other. However, the magnitudes of the gradients of the front sliding surface and the rear sliding surface may be different from each other.

  Further, in the sliding mechanism 9 having four sets of the sliding body mechanisms 50, the concave sliding body 30 is related to the position of the convex sliding body 30 in the longitudinal direction (sliding direction) shorter than the concave sliding body 40 with respect to the concave sliding body 40. The position of the center of the moving body 40 in the longitudinal direction, that is, the position where the convex slide body 30 matches the position of the center of the longitudinal direction with the center position of the concave slide body 40 in the longitudinal direction is the neutral position. The state in which the convex slide body 30 is located in a neutral position with respect to the concave slide body 40 is a neutral state in the damping device 1, and the convex slide part 7 and the concave slide part 8 are in a neutral position. Corresponds to a state (neutral state). Regarding the relative movement of the convex slide body 30 with respect to the concave slide body 40, in each of the forward movement process from the neutral state and the backward movement process from the neutral state, the front sliding surface and the rear sliding surface are provided. Due to the gradient of the sliding surface, the height of the sliding body mechanism increases proportionally as the operating displacement increases.

  Therefore, when the convex sliding body 30 is moved forward from the neutral state, only the front sliding surfaces of the convex sliding body 30 and the concave sliding body 40, that is, only the central sliding surfaces 35 and 45 are in contact with each other. Further, when the convex slide body 30 is moved backward from the neutral state, only the rear slide surfaces of the convex slide body 30 and the concave slide body 40, that is, only the two outer slide surfaces 34 and 44 are in contact with each other. To do. In the neutral state, the front sliding surfaces and the rear sliding surfaces of the convex slide body 30 and the concave slide body 40 are in contact with each other.

  Thus, the central sliding surfaces 35 and 45 as the sliding surfaces for the front function as sliding surfaces in a state where the convex sliding body 30 is positioned forward of the concave sliding body 40 with respect to the neutral position. This is a sliding surface dedicated to the front. In addition, the outer sliding surfaces 34 and 44 as the sliding surfaces for the rear are dedicated to the rear functioning as the sliding surfaces when the convex sliding body 30 is positioned behind the neutral sliding position with respect to the concave sliding body 40. This is a sliding surface.

  For example, in a neutral state, a slight gap is provided between the front sliding surfaces of the convex slide body 30 and the concave slide body 40 and between the rear slide surfaces, and neither surface comes into contact with each other. You may do it. That is, a range in which the front sliding surfaces and the rear sliding surfaces do not contact each other may be provided as a predetermined moving range (sliding range) from the neutral state to the front and rear of the convex sliding body 30. Thereby, in a predetermined sliding range where no sliding surfaces come into contact with each other, it is possible to prevent the frictional force generated when the sliding surfaces come into contact with each other, that is, the damping force by the damping device 1 from being generated.

  As described above, the sliding bodies of the convex sliding body 30 and the concave sliding body 40 constituting the sliding body mechanism 50 have the front sliding surface and the rear sliding surface. That is, each of the sliding portions of the convex sliding portion 7 constituted by the convex sliding body 30 and the concave sliding portion 8 constituted by the concave sliding body 40 has a sliding surface for the front and a sliding surface for the rear. And have.

  In the present embodiment, the forward sliding surface of each of the convex sliding part 7 and the concave sliding part 8 is from a neutral position in the range of reciprocal sliding relative to the sliding part of the other party sliding. As the amount of displacement in one of the sliding directions (forward) increases, the dimension in the direction in which the sliding portions of the sliding mechanism 9 face each other (sliding portion pressing direction) is increased. It functions as a first sliding surface having a simple shape. That is, in the present embodiment, the central sliding surfaces 35 and 45 that are the sliding surfaces for the front function as first sliding surfaces, respectively.

  Here, the dimension of the sliding mechanism 9 in the pressing direction of the sliding portion (hereinafter referred to as “sliding mechanism radial dimension”) is the sliding body mechanism 50 located on the opposite side in the apparatus radial direction in the sliding mechanism 9. The dimension is in the direction along the opposite direction, and roughly corresponds to the diameter or radius of the sliding mechanism 9. The radial dimension of the sliding mechanism corresponds to the height of the sliding mechanism when focusing on one set of the sliding mechanism 50.

  Further, in this embodiment, the rear sliding surfaces of the convex sliding portion 7 and the concave sliding portion 8 are included in the sliding direction from the neutral position with respect to the sliding portion of the other party sliding. As the amount of displacement in the other direction (backward) increases, it functions as a second sliding surface having a shape that increases the radial dimension of the sliding mechanism. That is, in the present embodiment, the outer sliding surfaces 34 and 44, which are rear sliding surfaces, function as second sliding surfaces, respectively.

  However, in this embodiment, when the moving direction (one of the operating directions) that increases the radial dimension of the sliding mechanism for the first sliding surface is the rear, the second sliding surface The moving direction (the other of the operating directions) that increases the radial dimension of the sliding mechanism is the front. In this case, the rear sliding surface functions as the first sliding surface, and the front sliding surface functions as the second sliding surface. That is, the first sliding surface and the second sliding surface are sliding surfaces in which the moving direction of the sliding body from the neutral position that increases the radial dimension of the sliding mechanism is different from each other in the operation direction.

  Therefore, in the configuration in which the front sliding surface and the rear sliding surface are formed in each of the convex sliding portion 7 and the concave sliding portion 8, the central sliding surfaces 35 and 45, which are the front sliding surfaces, The inclination of the outer sliding surfaces 34 and 44, which are the sliding surfaces for the rear, is opposite to that shown in the figure, so that the outer sliding surfaces 34 and 44 become the sliding surfaces for the front, and the central sliding surface 35, 45 is a sliding surface for the rear. In other words, the convex sliding part 7 and the concave sliding part 8 have the central sliding surfaces 35 and 45 as either one of the front sliding surface and the rear sliding surface, and the outer sliding surface. The surfaces 34 and 44 are configured to be either one of the front sliding surface and the rear sliding surface.

  As described above, the sliding surface for the front and the sliding surface for the rear included in each sliding portion of the convex sliding portion 7 and the concave sliding portion 8 are present at a common position in the reciprocating sliding direction. Become. That is, in the damping device 1 of the present embodiment, the sliding surface for the front and the sliding surface for the rear included in each sliding portion are located at a common position in the sliding direction between the sliding portions in each sliding portion. Exists. This is because, for example, in the case of the convex sliding body 30 constituting the convex sliding portion 7, the central sliding surface 35 that is the front sliding surface and the outer sliding surface 34 that is the rear sliding surface. It is equivalent to being provided at the same position in the operation direction (direction to reciprocate), in other words, the central sliding surface 35 and the outer sliding surface 34 are provided in a form aligned in the width direction of each sliding surface. To do. In this respect, the positional relationship between the sliding surfaces of the central sliding surface 45 and the outer sliding surface 44 of the concave sliding body 40 constituting the concave sliding portion 8 is the same as that of the convex sliding body 30.

  In the attenuation device 1 having the above configuration, the following operation is obtained. In the following description, the operation displacement that is the relative displacement in the operation direction of the convex slide body 30 and the concave slide body 40 is u, and the gradient (inclination) of the front slide surface and the rear slide surface is i. To do. Further, regarding the operation displacement u, a forward displacement is a positive value, and a backward displacement is a negative value.

  FIG. 8 shows the sliding body mechanism 50 in the neutral state. The operating displacement u in this neutral state is set to zero. Further, the height of the sliding body mechanism in the neutral state is assumed to be h. In the neutral state shown in FIG. 8, as described above, the front sliding surfaces (center sliding surfaces 35 and 45) and the rear sliding surfaces (outer sliding surfaces 34 and 44) are in contact with each other.

  FIG. 9 shows a state in which the convex slide body 30 is positioned ahead of the neutral position with respect to the concave slide body 40 (a state during forward movement). Here, the forward displacement u (> 0) from the neutral position of the convex sliding body 30 occurs. In the forward movement state, the central sliding surfaces 35 and 45 that are the forward sliding surfaces are in contact with each other, and the outer sliding surfaces 34 and 44 that are the rear sliding surfaces are not in contact with each other.

In the state at the time of forward movement shown in FIG. 9, when an operation displacement u occurs, the height of the sliding body mechanism changes (increases) to h + v due to the gradient i of the central sliding surfaces 35 and 45. Here, v is the amount of change (increase) in the height of the sliding body mechanism caused by the displacement from the neutral position of the convex sliding body 30 and is expressed by the following equation (1).
v = i | u | (1)

  FIG. 10 shows a state in which the convex slide body 30 is located behind the neutral position with respect to the concave slide body 40 (a state during backward movement). Here, an operation displacement u (<0) backward from the neutral position of the convex sliding body 30 occurs. In the state of rearward movement, the outer sliding surfaces 34 and 44 that are the rear sliding surfaces are in contact with each other, and the central sliding surfaces 35 and 45 that are the front sliding surfaces are not in contact with each other. When an operation displacement u occurs in the state of backward movement, the sliding mechanism mechanism height changes to h + v because of the gradient i of the outer sliding surfaces 34 and 44. Here, v is represented by the above formula (1).

  As represented by Expression (1), the amount of change v of the sliding body mechanism height is proportional to the value (absolute value) of the operating displacement u. The damping device 1 generates a compressive force in the sliding portion pressing direction that increases in proportion to the operating displacement by utilizing the characteristic that the height of the sliding body mechanism increases in proportion to the operating displacement. In other words, in the damping device 1, the height of the sliding body mechanism increases in proportion to the operating displacement, so that the sliding mechanism 9 moves in the direction of pressing the sliding portion from the concave sliding body 40 positioned on the outer peripheral side. A force against the urging force acts, and as a reaction force, a compressive force in the sliding portion pressing direction acts on the sliding body mechanism 50, that is, the sliding mechanism 9.

  Further, in the damping device 1, the convex slide body 30 and the concave slide body 40 are fitted to each other by the protrusion 32 and the groove portion 42, and the width of the protrusion of the protrusion 32 and the groove portion 42 as described above. The groove is formed so that the width dimension thereof is substantially the same. With such a configuration, the gap in the width direction generated between the protrusion 32 and the groove 42 in a state where the protrusion 32 and the groove 42 are fitted to each other is eliminated as much as possible, and the convex slide body 30 and the concave slide body 40 are removed. Slides without rattling in the width direction.

  Further, in the convex slide body 30 and the concave slide body 40 that slide relative to each other regardless of whether the convex slide body 30 moves forward or backward, the transverse direction (width direction) perpendicular to the operation direction is used. There is no eccentricity. That is, as the sliding body mechanism 50, the convex and concave sliding bodies are engaged with each other in a direction perpendicular to the operation direction, and therefore, the relative displacement of the sliding body mechanism 50 is equal to the direction of the operation displacement u and the height of the sliding body mechanism. Limited to direction. Further, the sliding surface of the convex sliding body 30 can come into contact with the entire sliding surface of the concave sliding body 40.

  Further, the sliding surfaces of the convex sliding body 30 and the concave sliding body 40 are subjected to heat treatment or nitriding treatment, or embedded with a solid lubricant in order to improve wear characteristics. Here, an example in which a solid lubricant is embedded in the sliding surface of the convex sliding body 30 is shown in FIG.

  In the example shown in FIG. 11, a lubricant embedded portion 38 in which a solid lubricant is embedded is provided on the outer sliding surface 34 and the central sliding surface 35 which are sliding surfaces of the convex sliding body 30. A plurality of lubricant embedded portions 38 are provided in a predetermined arrangement by embedding a predetermined solid lubricant in a plurality of holes formed in a predetermined array. As the solid lubricant constituting the lubricant embedding part 38, for example, graphite or fluororesin is used.

  As described above, the sliding mechanism 9 that forms the cylindrical outer peripheral surface 9a with the apparatus axis direction as the cylinder axis direction, and the urging wire 10 that is provided in a state of being wound around the outer peripheral surface 9a of the sliding mechanism 9 As shown in FIGS. 1 and 2, the damping device 1 including the above includes an end support plate 16 and an intermediate support plate 17 which are a pair of support plates as members constituting the intermediate cylinder portion 2. As shown in FIGS. 1, 2, 12, and 13, each of the end support plate 16 and the intermediate support plate 17 is a member having a substantially disk-like outer shape as a whole, and the cylinder of the intermediate tube portion 2. The end face portions on both sides in the axial direction are configured. The end support plate 16 is provided on the side where the first joint portion 5 is located (the right side in FIG. 2) with respect to the intermediate tube portion 2, and the intermediate portion support plate 17 is the second joint with respect to the intermediate tube portion 2. It is provided on the side where the portion 6 is located (left side in FIG. 2). 12 is a view in the apparatus axial direction showing a plate surface portion inside (left side in FIG. 2) of the end support plate 16, and FIG. 13 is an outside view of the intermediate support plate 17 (left side in FIG. 2). It is a figure of the apparatus axial direction view which shows the plate | board surface part.

  The end support plate 16 and the intermediate support plate 17 have substantially the same size and shape. The end portion support plate 16 and the intermediate portion support plate 17 are opposed to each other on the plate surface side, and the center rod 11 is slidably passed through the center portion in the axial direction, and the sliding mechanism 9 is provided between them. The center rod 11 and the sliding mechanism 9 are supported in the sandwiched state. The end support plate 16 and the intermediate support plate 17 are provided in a state of being concentrically arranged with the central rod 11 and the sliding mechanism 9.

  As shown in FIGS. 1, 2, 12, and 13, the end support plate 16 and the intermediate support plate 17 have through holes 16 a and 17 a that allow the central rod 11 to pass therethrough at the center. The through holes 16 a and 17 a have the same hole diameter as the outer diameter of the central rod 11. The end portion support plate 16 and the intermediate portion support plate 17 are formed on a surface portion facing each other, that is, on an inner surface portion of the intermediate tube portion 2, and a protruding portion 16 b that protrudes in a square tube shape around the holes of the through holes 16 a and 17 a. 17b. That is, the end support plate 16 and the intermediate support plate 17 are provided in a state where the protrusions 16b and 17b face each other.

  A bearing 18 that supports the central rod 11 is provided at a portion of the through holes 16a and 17a on the side of the protrusions 16b and 17b in the drilling direction. The bearing 18 is a cylindrical member made of, for example, a copper-based alloy. The bearing 18 is interposed between the inner peripheral surface of the protrusions 16b and 17b and the outer peripheral surface of the central rod 11, and the central rod 11 is slidable in the axial direction at the end support plate 16 and the intermediate support plate 17. To support. In addition, the enlarged diameter part 16c which expands the hole diameter of through-holes 16a and 17a partially as a part by which the bearing 18 is engage | inserted in the part by the side of the projection parts 16b and 17b (inner surface part side) of the through-holes 16a and 17a. , 17c are formed.

  The end support plate 16 and the intermediate support plate 17 support the central rod 11 with the central rod 11 passing through the central portion thereof, and are configured by the support member 14 and the convex sliding body 30 in the sliding mechanism 9. The sliding mechanism 9 is supported in such a manner as to sandwich the concave sliding portion 8 including the convex sliding portion 7, that is, the concave sliding body 40 from both sides in the apparatus axial direction. That is, the end support plate 16 and the intermediate support plate 17 are configured so as to block the cylindrical space formed by the four concave slide bodies 40 where the convex slide portion 7 is located from both sides in the cylinder axis direction. Provided. For this reason, on both sides in the sliding direction of the convex sliding portion 7, end surface portions on both sides in the sliding direction of the convex sliding portion 7 and the inner surface portion of the concave sliding portion 8 (surface portion on the groove 42 side). ) And the inner surface portion of the end portion support plate 16 or the intermediate portion support plate 17 are formed (see FIG. 2). The cavities 19a and 19b are space portions that allow relative sliding between the convex sliding portion 7 and the concave sliding portion 8.

  The end support plate 16 and the intermediate support plate 17 support the central rod 11 in a state of passing through the through holes 16a and 17a, and are provided integrally with the central rod 11 at four locations around the axis of the central rod 11. A concave slide body 40 that moves in four directions as viewed in the apparatus axial direction is movably supported with respect to the convex slide portion 7 thus formed. The end support plate 16 and the intermediate support plate 17 are inner surface portions facing each other and are supported by sandwiching the concave slide body 40 at portions around the protrusions 16b and 17b. That is, on the inner surface portions of the end portion support plate 16 and the intermediate portion support plate 17, the portions on the outer side (radially outer side) than the protrusion portions 16 b and 17 b become the support surface portions 16 d and 17 d of the concave slide body 40. Specifically, the end support plate 16 and the intermediate support plate 17 support the concave slide body 40 via the retainer 20.

  The retainer 20 is provided so as to penetrate the protrusions 16b and 17b and cover the support surface portions 16d and 17d in the inner surface portions of the end support plate 16 and the intermediate support plate 17, respectively. In the present embodiment, the retainer 20 is provided so as to cover the entire support surface portions 16d and 17d in accordance with the shape and dimensions of the support surface portions 16d and 17d. Therefore, as shown in FIG. 14, the retainer 20 has a circular outer shape having the same diameter as the support surface portions 16 d and 17 d when viewed in the apparatus axial direction, and is substantially along the outer shape of the protrusions 16 b and 17 b at the center portion. It has a square-shaped opening 20a. The retainer 20 is made of an elastic material such as sponge or rubber.

  In contrast to the support surface portions 16d and 17d of the end support plate 16 and the intermediate support plate 17 on which the retainer 20 is provided in this way, the concave slide body 40 serves as a support surface for the support surface portions 16d and 17d on both sides in the longitudinal direction. It has an end sliding surface 47 which is an end surface. The end sliding surface 47 is a surface perpendicular to the apparatus axial direction. The concave slide body 40 is supported in a state where the end slide surface 47 is in contact with or substantially in contact with the plate surface inside the retainer 20 (opposite the support plate side). That is, the retainer 20 is provided in a state of being sandwiched between the support surface portions 16 d and 17 d and the end sliding surface 47.

  Thus, the retainer 20 provided on the support surface portions 16d and 17d of the end support plate 16 and the intermediate support plate 17 forms a slide surface portion by the end slide surface 47 of the concave slide body 40. That is, the concave slide body 40 is fixed in position in the height direction of the slide body mechanism in the four slide body mechanisms 50 in the slide mechanism 9 with relative reciprocal sliding in relation to the convex slide body 30. It moves away from the convex sliding body 30 along the direction of increasing the sliding body mechanism height, that is, along the apparatus radial direction (in FIG. 3, up, down, left and right directions) orthogonal to each other. In the movement along the apparatus radial direction of the concave slide body 40 with respect to the convex slide body 30 (hereinafter also referred to as “radial movement”), the concave slide body 40 has an end sliding surface 47 on the inside of the retainer 20. Along the board.

  As described above, the end support plate 16 that supports the concave slide body 40 via the retainer 20 and the support surface portions 16d and 17d of the intermediate support plate 17 end at least within the moving range of the concave slide body 40 in the apparatus radial direction. The sliding surface 47 has a dimension (outer diameter dimension) that can maintain a state in which the sliding surface 47 is in contact or substantially in contact with the entire surface. Therefore, the outer diameters of the support surface portions 16d and 17d are larger than the outer diameter of the sliding mechanism 9. At least in the neutral state of the sliding mechanism 9, the end sliding surface 47 is formed on the outer edge portion of the plate surface inside the retainer 20. There is an annular exposed portion that is not in contact and serves as a movement allowance for the concave slide body 40.

  In this way, the retainer 20 constituting the sliding portion for the radial movement of the concave slide body 40 contacts the end sliding surface 47 of the concave slide body 40 to move the concave slide body 40 in the radial direction. Accordingly, a rotating roller 21 is provided. As shown in FIGS. 2 and 14, the roller 21 is a cylindrical member and rotates in a direction perpendicular to the radial movement direction of each concave slide body 40 in the retainer 20 as viewed in the apparatus axial direction. It is supported rotatably as an axial direction. In the present embodiment, the direction along each side of the square opening 20a of the retainer 20 is the direction of the rotation axis of the roller 21 provided for the concave slide body 40 corresponding to the side. FIG. 14 is a view showing the retainer 20 as viewed in the apparatus axial direction.

  As shown in FIG. 14, the roller 21 is provided in a portion of the retainer 20 where the end sliding surface 47 of the concave slide body 40 comes into contact or substantially in contact, that is, a portion around the opening 20 a. The roller 21 is provided in a state of being supported in a roller support hole 20 b provided in the retainer 20. The roller support hole 20b is formed as a rectangular opening having a size that allows the roller 21 to freely rotate. The roller 21 is provided in a state of being exposed at least on the inner plate surface side of the retainer 20. As the roller 21, a roller whose outer diameter is the same as or larger than the plate thickness of the retainer 20 is used.

  As shown in FIG. 14, in the present embodiment, for each concave slide body 40, two rollers 21 on both sides in a direction perpendicular to the apparatus radial direction as viewed in the apparatus axial direction, and the two rollers 21. A total of four rollers 21 including two rollers 21 adjacent to each other in the rotation axis direction are disposed therebetween. Therefore, in the configuration having the four concave slide bodies 40, the retainer 20 as a whole is provided with 16 rollers 21 in total.

  As described above, the retainer 20 is provided with the rollers 21 corresponding to the concave slide bodies 40, and the concave slide body 40 is provided with respect to each of the end support plate 16 and the intermediate support plate 17. 20 and a roller 21. The concave slide body 40 moves in the apparatus radial direction with the end slide surface 47 in contact with the roller 21. The roller 21 rotates with the radial movement of the concave slide body 40, thereby smoothing the movement of the concave slide body 40. That is, the roller 21 supports the concave slide body 40 so as to be freely movable with respect to the radial movement of the concave slide body 40 on the end support plate 16 side and the intermediate support plate 17 side. Moreover, the roller 21 supports the concave slide body 40 so that the damping force by the sliding mechanism 9 is transmitted to the end support plate 16 and the intermediate support plate 17 in the operation direction.

  The retainer 20 is preferably composed of a soft viscoelastic body or the like or a thin plate that can be easily deformed so that the position of the roller 21 during the movement of the concave slide body 40 can be easily restored. Further, the retainer 20 and the roller 21 may be made of a sliding material such as various plastic materials. Further, the retainer 20 and the roller 21 may be integrated as a single sliding plate. Examples of the material for integrating the retainer 20 and the roller 21 include a synthetic resin such as a fluororesin, a copper-based alloy containing a solid lubricant such as high-strength brass and graphite, and a composite material of a metal and a synthetic resin. Available.

  Moreover, the damping device 1 has a plurality of outer rods 22 provided outside the sliding mechanism 9 around which the urging wire 10 is wound as a member constituting the intermediate cylinder portion 2. The outer rod 22 is a rod-shaped member having a circular cross section, and is provided in a state of being laid between the end support plate 16 and the intermediate support plate 17. In the present embodiment, eight outer rods 22 are provided at equal intervals (equal angular intervals) along the circumferential direction of the sliding mechanism 9, that is, along the circumference centered on the central rod 11 when viewed in the apparatus axial direction. (See FIG. 3). Specifically, with respect to the circumferential direction of the sliding mechanism 9, four of the eight outer rods 22 are arranged at angular positions corresponding to the radial movement positions of the concave sliding bodies 40, and the remaining four. The book is arranged at the angular position of the boundary portion between the concave slide bodies 40 adjacent to each other.

  The outer rod 22 is provided between the end support plate 16 and the intermediate support plate 17 in a state of being sandwiched between flange portions 16e and 17e provided at the peripheral portions of the support plates 16 and 17. . The flange portions 16e and 17e are portions formed on the outer peripheral portion of the end support plate 16 and the intermediate support plate 17 on the side opposite to the side from which the protrusions 16b and 17b project in the plate thickness direction, and are relatively thick. Is a thin bowl-shaped part.

  The outer rod 22 is fixed by bolts 23 in a state of being sandwiched between flange portions 16e and 17e of the end support plate 16 and the intermediate support plate 17 from both sides in the apparatus axial direction (see FIG. 1). The bolt 23 is screwed along the axial direction of the outer rod 22 from the outer sides of the end support plate 16 and the intermediate support plate 17 via the flange portions 16e and 17e. For this reason, the bolt holes 16f and 17f which penetrate the flange parts 16e and 17e are provided in the flange parts 16e and 17e in the position corresponding to the arrangement position of the outer rod 22. Each outer rod 22 is formed with a bolt hole 22a that is a female screw portion so as to open to both end sides thereof. That is, the bolt 23 passes through the flange portions 16e and 17e from the outside of each of the end support plate 16 and the intermediate support plate 17 and is screwed into the bolt hole 22a of the outer rod 22, so that the end support plate 16 and The outer rod 22 is fixed between the intermediate portion support plate 17 and the intermediate portion support plate 17.

  The outer rod 22 is wound with the urging wire 10 so as not to interfere with the movement of the concave slide body 40 in the radial direction, that is, not to interfere with the concave slide body 40 moving along the apparatus radial direction. A clearance 24 is provided between the sliding mechanism 9 and the outer peripheral surface 9a. In other words, the gap 24 is a space portion that allows the radial movement of the concave sliding portion 8 (concave sliding body 40) accompanying the relative sliding of the convex sliding portion 7 and the concave sliding portion 8. Become. In the present embodiment, the outer rod 22 has outer peripheral surfaces 16g, 17g at both ends thereof forming support surface portions 16d, 17d on which the retainer 20 of the end support plate 16 and the intermediate support plate 17 is provided (see FIG. 12 and FIG. 12). The gap 24 is formed between the sliding mechanism 9 and the sliding mechanism 9.

  Thus, the plurality of outer rods 22 arranged around the sliding mechanism 9 has a function of transmitting a damping force generated in the sliding mechanism 9. Further, the outer rod 22 has a function of increasing the overall rigidity of the intermediate cylinder portion 2 and a function of protecting the urging wire 10 wound around the outer peripheral surface 9a of the sliding mechanism 9 from the outside. Note that the material, diameter, number, arrangement interval, and the like of the outer rod 22 are appropriately determined based on the viewpoint of efficiently transmitting the damping force generated by the damping device 1 to the structure.

  Moreover, the damping device 1 of this embodiment has the connection material 25 as a member which comprises the 2nd axial part 4 in which the 2nd coupling part 6 is provided in a front-end | tip part. As shown in FIGS. 2 and 15, the connecting member 25 is a substantially shaft-like member as a whole, and is located outside the intermediate support plate 17 (on the side facing the end support plate 16 at a concentric position with respect to the apparatus axial direction. And the second shaft portion 4 is formed. FIG. 15 is a view showing the connecting member 25 as viewed in the apparatus axial direction.

  The connecting member 25 includes a shaft portion 25a that is a portion having a substantially columnar outer shape, and a flange portion 25b provided at one end of the shaft portion 25a in the axial direction. A screw hole 25c as an internal thread portion for fixing the joint member 26 constituting the second joint portion 6 is axially provided at an end portion on the other side in the axial direction of the shaft portion 25a (the side opposite to the flange portion 25b side). Is formed so as to open at the end of the shaft portion 25a.

  The joint member 26 has a shaft-shaped or columnar shaft portion 26a and an annular or cylindrical connecting portion 26b provided on one end side of the shaft portion 26a. A male screw portion 26c is provided at the end of the shaft portion 26a opposite to the connecting portion 26b side. The joint member 26 is fixed to the connecting member 25 by screwing the male screw portion 26 c into the screw hole 25 c of the connecting member 25.

  The flange portion 25b of the connecting member 25 is a disk-shaped enlarged diameter portion in which the axial direction of the shaft portion 25a is the plate thickness direction, that is, a bowl-shaped portion. The flange portion 25b is provided with a screw hole 25d for fixing the connecting member 25 to the intermediate portion support plate 17 so as to penetrate the flange portion 25b in the plate thickness direction. In the present embodiment, the screw holes 25d are provided at eight locations at equal intervals (equal angular intervals) along the circumferential direction of the flange portion 25b as viewed in the apparatus axial direction (see FIG. 15). On the other hand, in the intermediate portion support plate 17, screw holes 17j as female screw portions are provided at eight positions corresponding to the arrangement of the screw holes 25d so as to open to the outer plate surface portion. Then, a bolt (not shown) passes through the screw hole 25d of the flange portion 25b and is screwed into the screw hole 17j on the intermediate support plate 17 side, whereby the connecting member 25 is fixed to the outside of the intermediate support plate 17. The connecting member 25 is provided so that the shaft center of the shaft portion 25 a coincides with the shaft center of the intermediate cylinder portion 2.

  Further, in the connecting member 25, an insertion hole 25e having a circular cross section is provided along the axial direction of the shaft portion 25a. The insertion hole 25e is formed from the shaft portion 25a to the flange portion 25b and opens to the flange portion 25b side. The insertion hole 25e is a hole having substantially the same diameter as the through hole 17a so as to be continuous with the through hole 17a provided at the center of the intermediate support plate 17 in a state where the connecting member 25 is fixed to the intermediate support plate 17. It is provided as.

  The connecting member 25 receives the end portion of the central rod 11 protruding from the intermediate support plate 17 to the outside of the intermediate cylinder portion 2 through the insertion hole 25e. That is, the end of the center rod 11 opposite to the side where the first joint portion 5 is provided is inserted into the insertion hole 25e, and the amount of insertion is relative to the intermediate tube portion 2 along the axial direction of the center rod 11. Changes with movement. As described above, the insertion hole 25 e of the connecting member 25 is a hole that receives the end of the central rod 11 and allows relative movement with respect to the intermediate cylindrical portion 2 in the direction along the axial direction of the central rod 11.

  In the damping device 1 of the present embodiment having the above-described configuration, the end support plate 16, the intermediate support plate 17, the retainer 20, the roller 21, the outer rod 22, and the connecting member 25 are fixed between the members. As a result, an integrated structure is formed. That is, each of these members constitutes a portion that moves integrally with the relative movement of the central rod 11 with respect to the intermediate tube portion 2. The portion that forms this integral structure corresponds to the outer axial force transmission portion that is an integral structural portion in which the second joint portion 6 is provided as described above. That is, the outer axial force transmission part includes the end support plate 16 and the intermediate support plate 17, the retainer 20 provided on each support plate 16, 17, the roller 21 supported by the retainer 20, and the support plates 16 and 17. It is a structural part that includes a plurality of outer rods 22 laid between them and a connecting member 25 that is fixed to the intermediate support plate 17, and these members are integrally configured by bolt fastening or the like.

  As described above, the damping device 1 has the central axial force transmission portion and the outer axial force transmission portion as the portion that relatively reciprocates along the device axial direction. Then, the concave slide body 40 constituting the concave slide portion 8 is relative to the central axial force transmitting portion in the apparatus axial direction while being fitted to the convex slide body 30 constituting the convex slide portion 7. The outer axial force transmission portion is slidably provided so as to be relatively slidable in the apparatus radial direction while being sandwiched between the end support plate 16 and the intermediate support plate 17. That is, the concave slide body 40 is pressed and urged from the outside by the urging wire 10, and the center axial force transmission portion and the outer axial force transmission portion are moved in the center along the relative reciprocal sliding along the device axial direction. While moving in the axial direction of the device together with the outer axial force transmitting portion, the axial force transmitting portion is independent of the outer axial force transmitting portion according to the gradient of the front sliding surface and the rear sliding surface (separately (As body) move in the device radial direction.

  By such relative sliding of the central axial force transmission portion and the outer axial force transmission portion along the device axial direction, the distance between the first joint portion 5 and the second joint portion 6 in the device axial direction changes. To do. A change in the distance between the first joint portion 5 and the second joint portion 6 corresponds to expansion and contraction of the attenuation device 1. The central axial force transmission portion and the outer axial force transmission portion have a convex sliding portion 7 and a concave sliding portion 8 that constitute the sliding mechanism 9, respectively, as sliding portions with respect to the counterpart in relative sliding. Thus, the frictional force generated in the sliding mechanism 9 serving as the sliding portion of the central axial force transmission portion and the outer axial force transmission portion becomes a damping force as an axial force by the damping device 1. The relative sliding along the device axial direction between the central axial force transmitting portion and the outer axial force transmitting portion is the device axial direction of the convex sliding portion 7 as the sliding portion on the central axial force transmitting portion side. Are allowed by the cavities 19a, 19b existing on both sides of the. As described above, the damping device 1 is configured to be extendable and contractible in the device axial direction, and causes the damping force against the vibration of the structure to act as an axial force along the extending and contracting direction.

  Below, an effect | action, a characteristic, etc. of the attenuation device 1 of this embodiment provided with the above structures are demonstrated. In the following description, the distance between the first joint portion 5 and the second joint portion 6 in the device axial direction in the damping device 1, more specifically, the annular shape of the joint members 12 and 26 constituting each joint portion. The distance between the center positions of the connecting portions 12b and 26b is defined as the axial length of the attenuation device 1, and the axial length in the neutral state of the attenuation device 1 is defined as b (see dimension b in FIG. 2). Further, the side length of the square cross-sectional shape of the support member 14 which is a member that supports the convex slide body 30 is a, the diameter (wire diameter) of the urging wire 10 is d, and the slide becomes a cylindrical surface. Let r be the radius of the outer peripheral surface 9a of the mechanism 9 (see FIG. 3). 2 and 3 each show a neutral state of the attenuation device 1.

  As shown in FIG. 3, in the neutral state of the damping device 1, the diameter of the sliding mechanism 9 is 2r = a + 2h, and the biasing forces are located on the opposite sides via the axial center position of the sliding mechanism 9 in the device radial direction. The dimension between the axial center positions of the wire 10 is 2r + (d / 2) · 2 = 2r + d. In addition, h is the sliding body mechanism height in a neutral state. The diameter of the sliding mechanism 9 is the apparatus axial direction with respect to the apparatus radial direction (hereinafter referred to as “sliding body moving radial direction”) which is the radial movement direction of the concave slide body 40 in the apparatus radial direction. In FIG. 3 showing a view, it is a dimension between the end portions of the outer curved surface 41 in the vertical direction or the horizontal direction between the concave slide bodies 40 arranged to face each other in the vertical and horizontal directions.

  A tensile damping force D that pulls the damping device 1 in the axial direction of the device acts on both ends of the damping device 1 in the neutral state, so that the axial length of the damping device 1 is an operation displacement u from b in the neutral state in the natural state. And b + u. FIG. 16 shows a state in which the axial length is extended to b + u (hereinafter referred to as “axial length extended state”). Note that the operating displacement u in the direction in which the damping device 1 extends is positive (u> 0). That is, the axial length extension state of the attenuation device 1 corresponds to the above-described forward movement state. FIG. 16 is a longitudinal sectional view at the same sectional position as the sectional position of the sectional view shown in FIG.

  As shown in FIG. 16, when the axial length of the damping device 1 increases from b in the neutral state to b + u in the axial length extended state, the central axial force transmission portion and the outer axial force transmission portion are in the direction of the operating displacement. The volume of the cavity 19a on the first joint portion 5 side (the right side in FIG. 16) decreases with respect to the convex sliding portion 7 and is on the opposite side. The volume of the cavity 19b on the second joint portion 6 side (left side in FIG. 16) increases. Moreover, since the sliding body mechanism height of each sliding body mechanism 50 increases, the clearance gap 24 between the outer rods 22 around the sliding mechanism 9 becomes narrow.

  FIG. 17 is a cross-sectional view (transverse cross-sectional view) as viewed in the apparatus axial direction in a state where the axial length is extended to b + u by the tensile damping force D (axial length extended state). 17 is a cross-sectional view of the same cross-sectional position as the cross-sectional position of the cross-sectional view shown in FIG. As shown in FIG. 17, in the axially elongated state, only the central sliding surfaces 35 and 45, which are the sliding surfaces for the front of the convex sliding body 30 and the concave sliding body 40, are in contact with each other. Some outer sliding surfaces 34 and 44 do not contact each other. Further, the height of the sliding mechanism of each sliding body mechanism 50 increases from h in the neutral state to h + v. Further, the diameter of the sliding mechanism 9 in the sliding body moving radial direction increases from 2r in the neutral state to 2r + 2v.

  Further, a gap δ is generated in a tangential direction with respect to the circumferential direction of the sliding mechanism 9 at the boundary between the concave sliding bodies 40 adjacent to each other in the circumferential direction of the sliding mechanism 9, that is, between the mating surfaces 43. Since the outer curved surface 41 of the concave slide body 40 is a ¼ cylindrical surface having a radius r, the gap δ is determined by ignoring the elastic deformation of the concave slide body 40, the convex slide body 30, the support member 14, and the central rod 11. It is represented by the following formula (2).

  A compression damping force D that compresses the damping device 1 in the axial direction of the device acts on both ends of the damping device 1 in the neutral state, so that the axial length of the damping device 1 is equal to the operating displacement u from b in the neutral state. Decreases to b + u (u <0). FIG. 18 shows a state where the axial length is reduced to b + u (hereinafter referred to as “axial length shortening state”). The operating displacement u in the direction in which the damping device 1 is shortened is negative (u> 0). That is, the axial length shortened state of the attenuation device 1 corresponds to the above-described state during backward movement. FIG. 18 is a longitudinal sectional view at the same sectional position as FIG.

  As shown in FIG. 18, the axial length of the damping device 1 is reduced from b in the neutral state to b + u in the shortened axial length state, so that the central axial force transmission portion and the outer axial force transmission portion are in the direction of the operating displacement. In addition, the volume of the cavity 19b on the second joint portion 6 side (left side in FIG. 18) decreases with respect to the convex sliding portion 7 and is on the opposite side. The volume of the cavity 19a on the first joint portion 5 side (the right side in FIG. 18) increases. Moreover, since the sliding body mechanism height of each sliding body mechanism 50 increases, the clearance gap 24 between the outer rods 22 around the sliding mechanism 9 becomes narrow.

  FIG. 19 is a cross-sectional view (transverse cross-sectional view) as viewed in the apparatus axial direction in a state where the axial length is reduced to b + u (u <0) by the compression damping force D (axial length shortened state). FIG. 19 is a cross-sectional view of the same cross-sectional position as FIG. As shown in FIG. 19, in the shortened axial length state, only the outer sliding surfaces 34 and 44 that are the rear sliding surfaces of the convex sliding body 30 and the concave sliding body 40 are in contact with each other, Some central sliding surfaces 35 and 45 do not contact each other. As in the case of the axial length extension state, the sliding mechanism height of each sliding body mechanism 50 increases to h + v, and the diameter of the sliding mechanism 9 in the sliding body moving radial direction increases to 2r + 2v. At the boundary between the concave slide bodies 40 adjacent to each other in the circumferential direction of the mechanism 9, a gap δ represented by the formula (2) is generated in the tangential direction with respect to the circumferential direction of the sliding mechanism 9.

  Next, the relationship between the compression force V acting on the pair of sliding body mechanisms 50 and the tension T generated on the urging wire 10 will be described with reference to FIG. In FIG. 20, attention is focused on the combination of the convex sliding body 30 and the concave sliding body 40 located on the lower side (sliding body mechanism 50). In FIG. 20, a part of the configuration and hatching representing a cross section are omitted for convenience.

  FIG. 20 (a) shows the position where the compression force is applied when the operating displacement u is a positive value (u> 0) and the front sliding surfaces are in contact with each other, that is, when the shaft length is extended (when moving forward). Show. Actually, the compressive force acting on the convex sliding body 30 is a distributed force, but here, the compressive force is expressed by one (one vector) corresponding to one central sliding surface 35 which is a front sliding surface. Think of it as concentration V. The increase in the height of the sliding mechanism is v, and the tension is T. When the friction of the contact portion between the urging wire 10 and the concave slide body 40 and the influence of the winding angle of the urging wire 10 are ignored, the relationship between the compression force V and the tension T is expressed by the following equation (3).

The degree of stress of the urging wire 10 is expressed by the following equation (4).
σ = σ ₀ + σ _u (4)
Here, σ ₀ is an initial stress generated by the initial tension, and σ _u is a stress generated by the operating displacement u and the increase v of the sliding mechanism height. Assuming that the stress of the urging wire 10 is uniform in the length direction of the urging wire 10, the elongation Δs per circumference of the urging wire 10 caused by the operating displacement u is expressed by the following equation (5). .

The circumferential length s ₀ of the urging wire 10 in the neutral state is expressed by the following equation (6).
s ₀ = 2π (r + (d / 2)) (6)
From the equations (5) and (6), the stress degree σ _u is expressed by the following equation (7).

  In Equation (7), E is the Young's modulus of the urging wire 10. When the sectional area and the number of windings of the urging wire 10 are respectively A and n, the total tension ΣT of the urging wire 10 is expressed by the following equation (8).

  Substituting equation (8) into equation (3) yields equation (9) below.

  FIG. 20B shows the position where the compression force is applied when the operating displacement u is a negative value (u <0) and the sliding surfaces for back contact with each other, that is, when the axial length is shortened (backward movement). Show. Actually, the compressive force acting on the convex sliding body 30 is a distributed force, but here, it is expressed by two (two vectors) corresponding to the two outer sliding surfaces 34 which are the rear sliding surfaces. ) I think that it works by dividing into concentration power V / 2. Also in the case shown in FIG. 20B, the compressive force V is expressed by Expression (9).

FIG. 21 shows forces acting on the convex slide body 30 and the concave slide body 40 in the axial length extended state (the state of u> 0) shown in FIGS. 16 and 17. FIGS. 21A and 21B show cases where the operating speed du / dt is positive (du / dt> 0) and negative (du / dt <0), respectively. The compressive force V is the compressive force V acting on the convex slide body 30 shown in FIG. The force H acting on the convex sliding body 30 is a reaction force received from the support material 14. The reaction force H is transmitted to the central rod 11 via the support member 14 and becomes a part of the damping force D. Since the damping device 1 includes four sets of sliding body mechanisms 50, the damping force D is expressed by the following equation (10).
D = 4H (10)

  It is considered that the frictional force F acts on the central sliding surface 35 that is the front sliding surface of the convex sliding body 30 in parallel with the sliding surface, and the drag P acts on the sliding surface perpendicularly. Similarly, the frictional force F and the drag force P also act on the central sliding surface 45 that is the front sliding surface of the concave slide body 40. The force of the urging wire 10 acts on the portion of the concave slide body 40 that contacts the urging wire 10. In FIG. 21, the force generated by these urging wires 10 acting on the concave slide body 40 is expressed as “wire acting force”.

  Since the concave slide body 40 is supported by the roller 21 in the operation direction on both sides in the longitudinal direction, when the operation speed du / dt is positive (du / dt> 0), that is, in a state of moving forward, As shown in FIG. 21A, a reaction force H acts on the roller 21 (21a) portion on the first joint portion 5 side (right side in the drawing). The reaction force H is transmitted to the connecting member 25 via the end support plate 16, the outer rod 22, and the intermediate support plate 17 and becomes a part of the damping force D. On the other hand, when the operation speed du / dt is negative (du / dt <0), that is, in a state of moving backward, as shown in FIG. 21B, the second joint portion 6 side (left side in the figure) The reaction force H acts on the roller 21 (21b) portion. The reaction force H is transmitted to the connecting member 25 via the intermediate support plate 17 and becomes a part of the damping force D. The relationship between the damping force D and the reaction force H is expressed by equation (10).

The relationship between the frictional force F and the normal force P acting on the central sliding surfaces 35 and 45 that are the forward sliding surfaces of the convex sliding body 30 and the concave sliding body 40 is expressed by the following equation (11) from the law of Coulomb friction. expressed.
F = μP (11)
Here, μ is a dynamic friction coefficient of the sliding surface.

  When the operation speed du / dt in FIG. 21A is positive (du / dt> 0), the balance of the force of the convex sliding body 30 in the direction of the reaction force H and the direction of the compression force V is expressed by the following equation (12 ).

  In Expression (12), j is an angle formed by the direction of the reaction force H (operation direction) and the sliding surface. When the equations (9), (10), (11), and (12) are solved for the damping force D, the following equation (13) is obtained.

  In the equation (13), λ is a motion resistance coefficient defined by the following equation (14). In addition, u dot in Formula (14) represents operating speed du / dt.

  When the operation speed du / dt in FIG. 21B is negative (du / dt <0), the balance of the force of the convex sliding body 30 in the direction of the reaction force H and the direction of the compression force V is expressed by the following equation (15 ).

  When Expression (9), Expression (10), Expression (11), and Expression (15) are solved for the damping force D, Expression (13) is obtained. However, the motion resistance coefficient λ is represented by the following equation (16).

  When the direction of the tensile damping force D shown in FIG. 16 is defined as positive (D> 0), when the operating displacement u is positive and the operating speed du / dt is negative, the direction of the damping force D is the direction shown in FIG. And the damping force D is negative (D <0). Therefore, as shown in Expression (16), when the operation displacement u is positive and the operation speed du / dt is negative, the motion resistance coefficient λ is negative. The gradient i is set smaller than the dynamic friction coefficient μ.

  As shown in FIGS. 18 and 19, also when the convex sliding body 30 and the concave sliding body 40 are in contact with each other on the outer sliding surfaces 34 and 44, which are rear sliding surfaces, the damping force D is expressed by the equation (13). It is represented by However, the motion resistance coefficient λ is given by the following equation (17).

FIG. 22 is an example of a stress-strain curve of a nickel-titanium superelastic alloy wire as the urging wire 10. In the graph shown in FIG. 22, the horizontal axis represents elongation as strain (Strain (%)), and the vertical axis represents tensile force (Tensile force (kgf)). The diameter of the biasing wire 10 d = 0.475 mm, cross-sectional area A = 0.177 mm ^2, Young's modulus is E = 40700N / mm ^2. The temperature is t = 20 ° C.

  In FIG. 22, a path O → Y → Z → S indicates a stress / strain load path (loading path) that increases the tensile force applied to the urging wire 10, and a path S → T → R → O indicates The unloading path | route which reduces the tension | tensile_strength which acts on the force wire 10 is shown. The origin O represents the stress / strain of the urging wire 10 before the load (the load is zero), and the point S is a return start point at which unloading is started. Usually, the path OY is called an elastic region, and the path YS is called a superelastic region (or pseudoelastic region).

In the load path Y → S, a martensitic transformation occurs in the crystal of the material of the biasing wire 10 and a section where the stress becomes constant appears. The stress in the constant stress section and the end point (S side) of the section are called the yield stress σ _y and the transformation end point Z, respectively. Point Y is called the yield point, but the yield point Y is not clear in the figure. In the unloading path S → T → R, reverse transformation of the crystal occurs, and the strain generated in the loading path Y → S is recovered. In the unloading path R → O, the elasticity is restored, and when there is no load, the stress / strain returns to the state before the load. For convenience of explanation, points T and R on the unloading route STRO are called a return intermediate point and an elastic recovery point, respectively.

If the stress / strain at the start of return is in the straight line portion of the path OY, the unloading path coincides with the straight line portion of the path OY. When the strain ε _s at the start of return (at the return start point S) exceeds the strain ε _z at the transformation end point Z as shown in the graph of FIG. 22, the unloading route R → O is changed to the loading route O → Y. Different. When the strain ε _s at the start of return does not exceed the strain ε _z of the transformation end point Z, that is, when the return start point S is located on the loading path YZ, the elastic recovery point R is on the loading path O → Y. Yes, it can be considered that the unloading route R → O partially overlaps the loading route O → Y. Further, it may be considered that the partial overlap between the unloading route R → O and the loading route O → Y is maintained at the time of repeated loading and unloading several hundred times at the time of the earthquake. The above is the origin return characteristics of the stress and strain of the superelastic alloy wire. In practice, if the maximum strain is less than 4%, it is expected that the strain returns to the origin with repeated loading and unloading.

FIG. 23 is a calculation model in which the relationship between the stress degree σ (N / mm ² ) and the strain ε (%) of the nickel-titanium superelastic alloy wire as the urging wire 10 is idealized. In the graph shown in FIG. 23, the origin O, the yield point Y, the return start point S, the return intermediate point T, the elastic recovery point R, and the transformation end point Z correspond to the points with the same symbols in FIG. However, in the example shown in FIG. 23, it is assumed that the magnitude of the strain ε _s at the return start point S is smaller than the magnitude of the strain ε _z at the transformation end point Z.

As shown in FIG. 23, if the strain is equal to or less than the yield strain (strain at the yield point Y) ε _y , the stress degree σ and the strain ε are on the path OY representing the direct proportionality regardless of the load and unloading. . The slope of the path OY is a Young's modulus E. When the strain exceeds the yield strain ε _y , martensitic transformation occurs, and the stress degree σ and the strain ε pass on the path YS. When unloading is performed in a range where the strain ε does not exceed the strain ε _z at the transformation end point Z, the strain ε reaches the elastic recovery point R via the path STR, and the urging wire 10 recovers elasticity. When unloading is further performed, the stress degree σ and the strain ε of the urging wire 10 return to the origin O through the route RO. The route TS is parallel to the route OY, and the route TR is parallel to the route YS.

The relationship between the operating displacement u of the damping device 1 and the damping force D will be described using the calculation model shown in FIG. When energized wire 10 actuated displacement of the damping device 1 upon reaching the yield point Y (the yield actuation displacement) and u _y, the relationship of the yield stress of sigma _y and the yield actuation displacement u _y of the biasing wire 10 is above It represents with following Formula (18) from Formula (7).

In equation (18), the yield actuation displacement u _y is positive. Substituting equation (18) into equation (13), the damping force D, the operating displacement u, and the initial stress degree σ ₀ are the resultant tension of the biasing wire 10 (nAσ _y ), the yield operating displacement u _y , and the yield stress degree, respectively. When dimensionless with σ _y , the relationship between the damping force D and the actuation displacement u in the following equation (19) is obtained.

FIG. 24 is an example of the relationship between the operating displacement and the damping force expressed by Equation (19). As shown in the graph of FIG. 24, if the operating displacement u is smaller than the yielding operating displacement u _y , that is, if the absolute value of u / u _y is smaller than 1, the damping is proportional to the increment of the operating displacement (Displacement). It is confirmed that the Damping force increases.

When the operating displacement u exceeds the yield operating displacement u _y and the operating speed is positive, the stress degree σ and strain ε of the biasing wire 10 are on the path YZ in the calculation model of FIG. The stress degree σ becomes the yield stress degree σ _y . Therefore, equation (18) is established regardless of the magnitude of the operating displacement u. Therefore, the relationship between the operating displacement and the damping force is expressed by the following equation (20).

If the operating displacements of the return start point S and the return intermediate point T are u _s and u _t , respectively, the slope of the path TS in the calculation model of FIG. 23 is equal to the slope of the path OY. Only when the operating displacement is positive and the operating speed is negative, the relationship between the operating displacement and the damping force is expressed by the following equation (21).

The recovery stress of the biasing wire 10 elastic recovery point R and sigma _r, when the operating displacement of the time and u _r, the following equation from the equation (18) (22) holds.

  When the operating displacement is positive and the operating speed is negative, and the stress degree σ and strain ε of the urging wire 10 are on the path RT in the calculation model of FIG. 23, the equation (22) holds regardless of the operating displacement. The relationship between the operating displacement and the damping force is expressed by the following equation (23).

  When the operating displacement is positive and the operating speed is negative, and the stress degree σ and strain ε of the urging wire 10 are on the path OR in the calculation model of FIG. 23, the above equation (19) is established. The relationship of the damping force is expressed by the following equation (24).

FIG. 25 shows an example of a result of trial calculation of the relationship between the operation displacement and the damping force when the operation displacement u exceeds the yield operation displacement u _y using Equations (19) to (24). A point O, a point Y, a point S, a point T, and a point R in FIG. 25 respectively correspond to the points with the same sign in the calculation model of FIG.

As can be confirmed from the graph of FIG. 25, in the region where the operating displacement u exceeds the yielding operating displacement u _y , that is, the region where the absolute value of u / u _y exceeds 1, the damping force is a substantially constant value. . Thus, according to the damping device 1, the damping force can be limited in the region of the operating displacement exceeding the yield operating displacement u _y by utilizing the stress and strain recovery characteristics of the urging wire 10.

FIG. 26 is a trial calculation of the yield actuation displacement u _y shown by the equation (18) using the radius of curvature of the outer curved surface 41 of the concave slide body 40, that is, the radius r of the sliding mechanism 9 and the gradient i of the sliding surface as parameters. An example of the results is shown. FIG. 26 shows graphs when the gradient is i = 0.01, i = 0.02, and i = 0.03.

From the graph of FIG. 26, it is confirmed that the yield operation displacement u _y can be set in the range of about 100 to 600 mm by adjusting the radius r and the gradient i of the sliding mechanism 9. From FIG. 22 and FIG. 26, if two times the yield actuation displacement _{u y} and limit operating displacement, it is possible to limit operating displacement range of about 200 to 1000 mm. Accordingly, it is considered that the damping device 1 is effective as a countermeasure against seismic motion of structures such as multi-span bridges and long-span bridges where large displacement is expected.

  Then, the dimension and material of each member which comprise the damping device 1 of this embodiment are demonstrated. It is preferable that one of the convex slide body 30 and the concave slide body 40 is made of a hard material and the other is made of a soft material. Here, as the hard material, for example, carbon steel such as S45C, stainless steel such as SUS304, nitride steel such as SACM645 can be used. Further, it is desirable that the sliding surface of the hard material is improved in wear characteristics by heat treatment or nitriding treatment. As the soft material, for example, high-strength brass such as CAC304, fluorine resin, or the like can be used. Further, as the soft material, bronze-based material containing graphite or the like as a solid lubricant, high-strength brass or fluorine resin in which graphite or fluorine resin or the like is embedded as a solid lubricant like the lubricant embedded portion 38 shown in FIG. Or a synthetic resin containing silicon may be used. In order to increase the wear of the soft material more than that of the hard material and prevent seizure of the sliding surface, the soft material and the hard material need only have a significant difference in the amount of wear. Therefore, the convex slide body 30 and the concave slide body As the material of 40, other materials may be used regardless of the above. Regardless of the material of the convex sliding body 30 and the concave sliding body 40, the surface of the central sliding surface 35 and the surface of the central sliding surface 45 that are in sliding contact with each other are combined with a hard material and a soft material so that they slide on each other. The surface of the outer sliding surface 34 in contact with the surface of the outer sliding surface 44 may be a combination of a hard material and a soft material. Specifically, a stainless steel plate or the like may be used as a hard material, and a fluororesin plate or a copper-based alloy containing a solid lubricant may be used as a soft material to adhere to the sliding surfaces.

  The center rod 11, the support member 14, the end support plate 16, the intermediate support plate 17, and the connecting member 25 can be made of carbon steel such as S45C, for example. When reducing the weight of these members, for example, a composite material such as an aluminum alloy, a magnesium alloy, a carbon fiber reinforced resin, or the like can be used as the material of these members.

  Further, the support material 14 to which the convex slide body 30 is fixed is formed by using the elastic deformation of the support material 14 by forming the support material 14 with a viscoelastic material such as natural rubber, polyurethane rubber, or silicon rubber. The support member 14 may be a part of the urging means. In this case, the damping device 1 includes the sliding body support portion 13 constituted by the support material 14 that supports the convex sliding body 30 in addition to the urging wire 10 provided along the outer peripheral surface 9a of the sliding mechanism 9. The urging means (second urging means) for urging the sliding mechanism 9 in the sliding portion pressing direction is provided. According to such a configuration, it is possible to deal with a wider range of spring constants with respect to the configuration for applying the urging force to the sliding mechanism 9.

  As the urging wire 10, a nickel / titanium superelastic alloy wire can be used. As the superelastic alloy wire, a material having a return characteristic as shown in FIG. 23 is desirable, but if it has an origin return characteristic, the return path is not limited to the path STRO shown in FIG. Elastic alloy wires can also be used. When the use of the urging wire 10 is limited to the elastic region, a piano steel wire, carbon fiber, chemical fiber, or the like can be used as the urging wire 10.

  As the roller 21, a high chromium steel material or the like can be used. When the roller 21 and the retainer 20 are integrated to form a sliding plate, a bronze sliding material or a fluororesin in which a solid lubricant is dispersed can be used. As the retainer 20, silicon-based or fluorine-based sponge rubber or the like can be used. When pressure acts on the retainer 20, the retainer 20 is preferably configured as a thin plate structure using spring steel or synthetic resin, or as a sliding plate integrated with the roller 21.

  According to the damping device 1 according to the present embodiment described above, the vibration energy can be efficiently absorbed from a small amplitude to a large amplitude with a simple structure and without depending on the length of the vibration period of the structure. It is possible to obtain high practicality and versatility, reduce manufacturing costs and reduce weight, easily adjust the spring constant, and maximize the damping force according to the operating displacement. The value can be limited.

  For example, when a skyscraper is targeted as a structure, it responds to different types of vibration, such as vibration with relatively small amplitude, such as vibration due to wind, and vibration with relatively large amplitude, such as long-period ground motion. There is a need. In such a case, according to the damping device 1 of the present embodiment, it is possible to deal with a wide range of vibrations from a small amplitude to a large amplitude. Therefore, one type of damping device can be used without using a different damping device for each type of vibration. It becomes easy to cope with vibrations of different types with the damping device.

  According to the damping device 1 of the present embodiment, the damping force increases in proportion to the absolute value of the displacement, that is, the equivalent viscous damping coefficient does not decrease even if the amplitude increases, and the natural vibration mode of the structure is long. It is possible to realize a configuration in which the equivalent viscous damping coefficient does not decrease even when the period is changed. In the damping device 1 of the present embodiment, the convex sliding portion 7 and the concave sliding portion 8 that are two types of sliding portions mesh with each other on the uneven surface, and only the front sliding surfaces are forward when moving forward. The two sliding surfaces are in close contact with each other when moving backward. When relative displacement occurs in the assembled convex slide body 30 and concave slide body 40, the height of the slide body mechanism changes due to the gradient of the sliding surface.

  The biasing wire 10 wound around the outer periphery of the sliding mechanism 9 including four sets of the sliding body mechanisms 50 including the convex sliding body 30 and the concave sliding body 40 has a change in the height of the sliding body mechanism. A compressive force proportional to is applied to the sliding surface. A friction force proportional to the product of the compression force and the friction coefficient of the sliding surface is generated on the sliding surface. Therefore, the vibration of the structure can be attenuated by mounting the damping device 1 of the present embodiment on the structure body. Moreover, according to the damping device 1 incorporating the sliding body mechanism 50, a displacement proportional friction force type damping device can be easily realized.

  Moreover, since the damping device 1 of this embodiment is an axial force member type damping device, higher versatility can be obtained. Specifically, the attenuation device 1 can be easily applied to the support of pipes of general houses and various plants by setting axial dimensions and the like. In particular, since the piping of the plant is more complicated than a general structure, the damping device 1 of the present embodiment is preferably used. Further, the damping device 1 can be attached to the structure by connecting the first joint portion 5 and the second joint portion 6 at both ends in the axial direction to a predetermined mounting portion on the structure side. It can be easily applied to structures. The damping device 1 configured as an axial force member type damping device can be applied to various structures such as steel buildings and concrete buildings, wooden buildings, seismic isolation bridges, and the like, and has high versatility.

  Further, the damping device 1 of the present embodiment has a configuration for biasing the sliding mechanism 9, and a biasing wire 10 wound around the outer periphery of the sliding mechanism 9 forming the cylindrical outer peripheral surface 9a. Since, for example, a super elastic alloy wire can be used as the urging wire 10, for example, a ready-made member can be easily adopted, so that manufacturing costs can be reduced. Further, by adopting a biasing wire 10 that is a cord-like member as a configuration for biasing the sliding mechanism 9, the weight ratio of the configuration for biasing the sliding mechanism 9 in the damping device 1 is reduced. This makes it possible to reduce the weight of the attenuation device 1.

  Further, according to the urging wire 10, the spring constant of the urging wire 10 can be adjusted by each element such as the number of turns, the diameter (wire diameter), and the material. For this reason, the spring constant about the structure for giving urging | biasing force to the sliding mechanism 9 can be adjusted easily, and it can respond to a wide range spring constant.

  Further, according to the damping device 1 of the present embodiment, since the damping force becomes a substantially constant value in the region of the operating displacement where the operating displacement exceeds the yielding operating displacement (see FIG. 25), the biasing wire 10 By utilizing the origin return characteristics of stress and strain, the maximum value of the damping force can be limited according to the operating displacement. This makes it possible to design the strength of the mounting part of the damping device on the structure side, even when preparing for a relatively large displacement (large amplitude) assuming a large earthquake such as a large-scale oceanic plate boundary earthquake. This difficulty can be avoided. Therefore, the damping device 1 according to the present embodiment can be easily applied to an existing structure in which it is relatively difficult to secure the strength at the attachment portion on the structure side, and can cope with a large amplitude. .

  In the damping device 1 of the present embodiment, the sliding surface of the sliding mechanism 9 (of the sliding body mechanism 50) has a predetermined inclination at the fitting portion formed by the concave and convex shapes of the convex sliding body 30 and the concave sliding body 40. However, the present invention is not limited to this. The shape of the sliding surface of the sliding mechanism 9 is a shape that increases the height of the sliding body mechanism as the amount of displacement forward or backward from the neutral position with respect to the sliding portion of the other party that slides increases. If there is, it will not be specifically limited.

  Therefore, the sliding surface of the sliding mechanism 9 is not formed in a fitting portion with an uneven shape as in the present embodiment, for example, but one (a pair) of sliding for the front and the rear. The surfaces may be in contact with each other, or may be curved surfaces that are curved in at least one of the operation direction and the width direction. However, as in the present embodiment, the sliding surface is formed by the fitting-shaped portion formed by the protrusion 32 of the convex sliding body 30 and the groove 42 of the concave sliding body 40, so that the operating direction in the sliding body mechanism 50. The occurrence of eccentricity in the transverse direction (width direction) perpendicular to each other can be prevented, and the sliding surfaces of the sliding bodies can be brought into contact with each other over almost the entire length of each sliding body. Thereby, while being able to implement | achieve a simple structure easily, high stability can be easily acquired about the operation | movement by the relative sliding of sliding bodies.

  Moreover, the uneven | corrugated shape in the sliding body mechanism 50 may be reverse in the mutually opposing direction (up and down). In other words, the sliding portion that constitutes the central axial force transmission portion integrally with the central rod 11 or the like is a concave sliding portion, and a convex that operates separately from the central axial force transmission portion and the outer axial force transmission portion. The structure which a type | mold sliding part fits may be sufficient.

  Further, since the sliding surface of the sliding mechanism 9 is a slope having a predetermined gradient as in the present embodiment, the mechanical analysis is facilitated, and the high practicality and versatility of the damping device 1 are easily achieved. Can be obtained. The sliding surface of the sliding mechanism 9 is coated with a lubricant or the like to reduce the difference between the dynamic friction coefficient and the static friction coefficient, or an oxide film or oil to prevent adhesion between metals or corrosion. A film or the like may be formed.

  Further, the damping device 1 of the present embodiment is configured to include four sets of sliding body mechanisms 50 including the convex sliding body 30 and the concave sliding body 40 around the axis. However, the present invention is not limited to this configuration. The structure provided with 5 or more sets of sliding body mechanisms 50 may be sufficient. Here, for example, when the sliding mechanism 9 is configured by only one set of the sliding body mechanism 50, the surface of the convex sliding body 30 and the concave sliding body 40 on the opposite side to the opposite side is integrated. A typical cylindrical outer peripheral surface (cylindrical surface) is formed. That is, the sliding mechanism 9 is not limited to the number of combinations of the sliding fitting portions due to the concave and convex shapes of the convex sliding portion 7 and the concave sliding portion 8, but the assembly of the convex sliding body 30 and the concave sliding body 40. As the outer peripheral surface of the structure, any structure may be used as long as it forms a cylindrical outer peripheral surface in which the sliding direction (operation direction) between the sliding portions is the cylindrical axis direction.

  In addition, the four sets (four places) of the sliding body mechanisms 50 included in the sliding mechanism 9 according to the present embodiment are provided in an equiangular range of 90 ° (at equiangular intervals) around the axis of the axial force. However, the present invention is not limited to such a configuration, and each sliding body mechanism 50 may be provided so as to occupy different angular ranges around the axial force axis (at unequal angular intervals). That is, in the configuration in which the sliding body mechanisms 50 are provided at a plurality of locations around the axis of the axial force, the angle ranges (angular intervals between the sliding body mechanisms 50) occupied by the respective sliding body mechanisms 50 may be different from each other. Specifically, for example, in a configuration including four sets of sliding body mechanisms 50 as in the present embodiment, two of the four sets of sliding body mechanisms 50 each occupy an angle range of 45 °, and the remaining A mode in which the two sets of sliding body mechanisms 50 are provided so as to occupy an angle range of 135 ° can be mentioned. However, according to the configuration in which the plurality of sliding body mechanisms 50 are provided in an equiangular range around the axis of the axial force as in the present embodiment, the sliding bodies constituting each sliding portion can be a common component. Therefore, the types of parts can be reduced and the management of parts can be facilitated. Further, the frictional force and the like obtained in each sliding portion can be made uniform around the axis of the axial force, that is, in the circumferential direction of the sliding mechanism 9.

  In the damping device 1 of the present embodiment, the urging wire 10 wound around the outer peripheral surface 9a of the sliding mechanism 9 is provided as an urging means for applying a predetermined urging force to the sliding mechanism 9. However, the present invention is not limited to this. The urging means may be of any configuration provided along the outer peripheral surface 9 a of the sliding mechanism 9, for example, a plurality of annular wires, or a sheet-like shape wound around the outer peripheral surface 9 a of the sliding mechanism 9. It may be a member, an annular or tubular member fitted around the sliding mechanism 9, a member having a cylindrical space into which the sliding mechanism 9 is inserted, and the like. In other words, the urging means may be configured to be provided so as to surround the sliding mechanism 9 from the outer peripheral surface 9a side. However, by adopting a cord-like member such as the urging wire 10 wound around the sliding mechanism 9 as the urging means, the spring constant can be easily adjusted as described above. It is possible to effectively reduce the weight of the damping device 1 in terms of the weight of the biasing means. For the purpose of protecting the urging wire 10, the urging wire 10 and the outer peripheral surface 9a or the outer rod 22, the urging wire 10 and the outer peripheral surface 9a are surrounded by a viscoelastic body such as polyurethane rubber or silicon rubber. You may do it. At that time, the surrounding viscoelastic body may be used as a part of the urging means, or a part of the reaction force of the roller 21 may be shared by the surrounding viscoelastic body.

  Furthermore, as the urging wire 10, it is preferable to employ a superelastic alloy wire made of a superelastic alloy such as a nickel / titanium alloy. As a result, for the strain deformation of the urging wire 10 accompanying the dimensional change in the sliding body moving radial direction due to the relative sliding of the convex sliding body 30 and the concave sliding body 40, the range in which the deformation is completely recovered is widened. Therefore, it is possible to deal with a wide range of damping force.

  Further, the outer peripheral surface of the sliding mechanism 9 is not limited to a cylindrical shape such as the outer peripheral surface 9a of the present embodiment. For example, the cross-sectional shape is a polygonal rectangular tube shape such as a square shape or a hexagonal shape, The outer peripheral surface may be a wide cylindrical shape such as an elliptical cylindrical shape. However, by adopting a cylindrical shape as in the present embodiment as the outer peripheral surface shape of the sliding mechanism 9, it is possible to reduce the burden on the urging wire 10 due to the sliding operation of the sliding mechanism 9, Since the urging force by the urging wire 10 can be transmitted in a balanced manner in the circumferential direction of the sliding mechanism 9, the frictional force as the damping force by the damping device 1 can be obtained efficiently.

[Second Embodiment]
A second embodiment of the present invention will be described. In addition, about the content which overlaps with 1st Embodiment, description is abbreviate | omitted suitably using the same code | symbol.

  As shown in FIGS. 27 and 28, the damping device 71 of the present embodiment is a cylindrical member instead of the plurality of outer rods 22 as a configuration provided around the sliding mechanism 9 in the intermediate cylindrical portion 2. A cylinder 80 is provided. In the intermediate cylinder portion 2, the cylinder 80 is filled with a viscous fluid 85 such as lubricating oil. With such a configuration, the damping device 71 of the present embodiment is configured as a composite damping device that uses a frictional force and a viscous force as a damping force.

  The cylinder 80 is a cylindrical cylinder member that is open at both ends in the cylinder axis direction. The cylinder 80 has a cylindrical outer shape with the apparatus axis direction as the cylinder axis direction, and surrounds the sliding mechanism 9 and the urging wire 10 wound around the sliding mechanism 9. Similarly to the outer rod 22 in the case of the first embodiment, the cylinder 80 is provided such that a gap 84 is formed between the outer peripheral surface 9a of the sliding mechanism 9 around which the urging wire 10 is wound. That is, the cylinder 80 surrounds the urging wire 10 with the gap 84 sandwiched between the outer peripheral surface 9 a of the sliding mechanism 9.

  Like the outer rod 22, the cylinder 80 has bolt holes 16 f and 17 f in a state of being sandwiched between the flange portions 16 e and 17 e of the end support plate 16 and the intermediate support plate 17 from both sides in the apparatus axial direction. It is fixed with bolts. For this reason, a plurality of bolt holes 80a, which are female screw portions, are formed at both ends of the cylinder 80 at a predetermined interval in the circumferential direction. In the configuration in which the cylinder 80 is provided instead of the outer rod 22 as described above, the outer axial force transmission portion that slides relative to the central axial force transmission portion including the central rod 11 and the convex sliding body 30 is provided at the end. It includes a part support plate 16 and an intermediate part support plate 17, a cylinder 80, and a connecting member 25 fixed to the end support plate 16.

  The cylinder 80 can be made of carbon steel such as S45C, for example. In the case of reducing the weight of the cylinder 80, a composite material such as an aluminum alloy, a magnesium alloy, or a carbon fiber reinforced resin can be used as the material of the cylinder 80, for example.

  An annular seal member 72 is provided at a contact portion between the end support plate 16 and the intermediate support plate 17 at both ends of the cylinder 80. The sealing material 72 is externally fitted to the end support plate 16 and the intermediate support plate 17 at portions that form the outer peripheral surfaces 16g and 17g (see FIGS. 12 and 13), which are reduced diameter step portions with respect to the flange portions 16e and 17e. The space between the inner peripheral surface 80b of the cylinder 80 and the outer peripheral surfaces 16g and 17g of the end support plate 16 and the intermediate support plate 17 is sealed.

  An annular sealing material 73 is provided at a contact portion between the central rod 11 and the end support plate 16 and a contact portion between the central rod 11 and the intermediate support plate 17. The sealing material 73 is fitted on the central rod 11 and seals between the inner peripheral surfaces of the through holes 16 a and 17 a of the end support plate 16 and the intermediate support plate 17 and the outer peripheral surface of the central rod 11. The sealing material 73 is held by a disk-shaped cap 74 provided outside the central rod 11 in the axial direction. The cap 74 is provided in a state of being fitted into circular recesses 16h and 17h provided on the outer plate surface portions of the end support plate 16 and the intermediate support plate 17.

  Thus, in the damping device 71 of the present embodiment, the space in the intermediate cylinder portion 2 including the gap 84 is a sealed space by the sealing materials 72 and 73. This sealed space is filled with the viscous fluid 85. Specifically, in the intermediate tube portion 2, the space surrounded by the central axial force transmission portion and the outer axial force transmission portion is mainly used as a space 84 on the outer peripheral side of the sliding mechanism 9 and the inside of the sliding mechanism 9. There are cavities 19a and 19b on both sides in the sliding direction of the convex sliding portion 7 in FIG. 2, and these spaces are sealed with sealing materials 72 and 73, and the viscous fluid 85 is filled in these spaces. Thus, in the damping device 71, the cylinder 80 is filled with the viscous fluid 85.

  The gap 84 outside the sliding mechanism 9 is closed with a soft viscoelastic material such as urethane rubber or silicone rubber, so that the viscous fluid 85 filled in the cavities 19a and 19b in the sliding mechanism 9 slides. Intrusion into the gap 84 side outside the mechanism 9 may be restricted. Alternatively, a soft viscoelastic material or the like that closes the gap 84 may be used as a part of the urging means, or a part of the reaction force of the roller 21 may be shared by the soft viscoelastic material or the like that closes the gap 84. good.

  In the damping device 71 of the present embodiment having the above-described configuration, the convex sliding portion 7 including the support member 14 and the convex sliding body 30 functions as a piston in the cylinder 80. Along with the relative displacement of the central axial force transmission portion and the outer axial force transmission portion, the viscous fluid 85 in the cavities 19a and 19b in the sliding mechanism 9 causes the support material 14 to move in the sliding mechanism 9 as viewed in the apparatus axial direction. It flows so as to go back and forth between the cavities 19a and 19b through the gaps 9b existing at the four corners and the gaps between the sliding surfaces of the convex slide body 30 and the concave slide body 40 that are not in contact with each other. The gap 9b in the sliding mechanism 9 becomes a passage for the viscous fluid 85 along the apparatus axial direction.

  By such movement of the viscous fluid 85, fluid force such as viscous force or dynamic pressure acts on the central axial force transmission portion and the outer axial force transmission portion. Further, since the gap between the sliding surfaces changes with the operation displacement of the central axial force transmission portion and the outer axial force transmission portion, the viscous fluid 85 flows out of the clearance between the sliding surfaces and flows into the clearance. The fluid force is also generated. The damping device 71 uses these fluid forces as damping forces (axial forces). As the viscous fluid 85, mineral oil, silicone oil, fluorine oil, oil obtained by adding graphite, molybdenum disulfide, or the like to these oils to improve sliding performance can be used.

(Modification)
A modification of the second embodiment of the present invention will be described. In the damping device 71A of this modification, the viscosity travels between the cavities 19a, 19b on both sides of the convex sliding portion 7 in the sliding mechanism 9 with relative displacement of the central axial force transmission portion and the outer axial force transmission portion. The fluid 85 is configured to come and go through the outside of the intermediate cylinder portion 2. That is, in the above-described configuration, the cavity is formed inside the intermediate cylinder portion 2 (inside the sliding mechanism 9) through the gap 9b in the sliding mechanism 9 and the gap between the sliding surfaces of the convex sliding body 30 and the concave sliding body 40. While the viscous fluid 85 moves back and forth between 19a and 19b, in this modification, a passage for the viscous fluid 85 is provided outside the intermediate cylinder portion 2, and the viscous fluid 85 is passed through the cavity 19a via the outside of the intermediate cylinder portion 2. , 19b is adopted.

  Specifically, in the damping device 71A of this embodiment, the gap 9b is closed by, for example, embedding a predetermined sealing material in the gap 9b in the sliding mechanism 9. As shown in FIG. 29, in the damping device 71A, the flow path hole 16i that communicates with the cavities 19a and 19b and opens to the outside of the intermediate cylindrical portion 2 in each of the end support plate 16 and the intermediate support plate 17. , 17i are provided. The channel holes 16i and 17i are holes that penetrate the support plates 16 and 17 in the thickness direction (left and right direction in FIG. 29).

  In addition, an external passage 90 for the viscous fluid 85 is provided outside the intermediate cylinder portion 2. One end side of the external passage 90 is connected to the end support plate 16 from the outside of the intermediate cylinder portion 2 so as to communicate with the flow path hole 16 i of the end support plate 16. The other end side of the external passage 90 is connected to the intermediate portion support plate 17 from the outside of the intermediate cylinder portion 2 so as to communicate with the flow path hole 17 i of the intermediate portion support plate 17. As described above, the flow path holes 16 i and 17 i of the end support plate 16 and the intermediate support plate 17 and the external passage 90 allow the cavities 19 a and 19 b in the sliding mechanism 9 to be mutually connected via the outside of the intermediate cylinder portion 2. It becomes a state of communication.

  The external passage 90 may be provided with a control valve 92 that changes the passage area of the external passage 90. The flow rate of the viscous fluid 85 passing through the external passage 90 is controlled by the control valve 92.

  In the damping device 1 according to the first embodiment, the frictional force as the damping force increases in proportion to the increment of the operating displacement. On the other hand, in the damping devices 71 and 71A according to the second embodiment, the fluid force as the damping force increases as the sliding speed of the central axial force transmission unit and the outer axial force transmission unit increases. For this reason, the phases of the frictional force and the fluid force are shifted from each other by 90 °. According to the damping devices 71 and 71A according to the present embodiment, both frictional force and fluid force can be used as the damping force.

  As described above, in the damping devices 71 and 71A configured as the composite damping device using the frictional force and the fluid force (viscous force and dynamic pressure) as the damping force, sliding is performed by the viscous fluid 85 filled in the cylinder 80. In the case where the surface can be lubricated, for example, a configuration in which the solid lubricant is provided on the sliding surface such as the lubricant buried portion 38 shown in FIG. 11 can be omitted.

  According to the damping devices 71 and 71A of the present embodiment having the above-described configuration, the damping force due to the fluid force generated by the viscous fluid 85 is added to the damping force due to the frictional force generated by the sliding mechanism 9. Can be obtained. That is, according to the damping devices 71 and 71A, a hybrid damper in which a function as a viscous damping device that obtains an action of viscous damping using the viscosity of the viscous fluid 85 is added to the function as a friction damping device. The damping force based on both functions can be obtained. For this reason, it becomes possible to greatly improve the damping force acting as an axial force. Further, by filling the cylinder 80 with a viscous fluid 85 such as lubricating oil, the durability of the sliding surface can be improved, and the reliability of the apparatus can be improved.

  Further, of the damping devices 71 and 71A of the present embodiment, as shown in FIGS. 27 and 28, according to the damping device 71 configured to flow the viscous fluid 85 inside the intermediate cylinder portion 2, the device configuration is simplified. The number of parts can be reduced and the cost can be reduced. In addition, since a pipe for the viscous fluid 85 or the like is not provided outside the intermediate cylinder portion 2, a simple outer shape can be realized, which facilitates installation with respect to the structure, and the overall apparatus. The range of application can be widened in terms of shape and exterior structure, and high versatility can be obtained.

  On the other hand, as shown in FIG. 29, according to the damping device 71 </ b> A configured to flow the viscous fluid 85 outside the intermediate cylindrical portion 2, the passage area of the viscous fluid 85 can be easily ensured. The flow of the fluid 85 can be made smooth, and a favorable sliding operation can be obtained. Further, by providing the control valve 92 in the external passage 90, the magnitude of the fluid force can be controlled. Thereby, since it becomes possible to adjust the magnitude | size of the damping force as the whole attenuation | damping apparatus 71A, an application range can be expanded from the surface of the magnitude | size of damping force, and high versatility can be acquired.

  Examples of the present invention will be described below. In this example, an operation test was performed with the configuration of the attenuation device 1 of the first embodiment. In order to verify the relationship between the damping force and the operating displacement of the damping device 1, a low-speed reciprocating loading test was performed with the minimum amplitude, the maximum amplitude, and the amplitude increase amount set to 5 mm, 35 mm, and 5 mm, respectively.

  FIG. 30 is a comparison between the test value (Test), which is the result of the test of this example, and the calculated value (Theory) according to Equation (13). In the graph shown in FIG. 30, the test value is indicated by a solid line, and the calculated value is indicated by a broken line.

  As can be seen from the graph of FIG. 30, in this example, the test values and the calculated values showed a good correspondence. The graph shown in FIG. 30 is a test result in a range where the operating displacement does not exceed the yield operating displacement, but since the test value and the calculated value show a good correspondence, even when the operating displacement exceeds the yield operating displacement It is considered that the relationship between the operating displacement and the damping force as shown in FIG. 25 is obtained. The specifications of the apparatus used for the operation test in this example are as follows.

  The maximum amplitude is 35 mm, the maximum damping force is 800 N, the shaft length b is 540 mm, the mass is about 40 kg, the sliding surface gradient i is 1%, and the sliding surface dynamic friction coefficient μ is 0.14 to 0.16.

  The convex sliding body 30 is made of high-strength brass (CAC304), and a graphite-based solid lubricant is embedded in the sliding surface of the convex sliding body 30 (see FIG. 11, the lubricant embedding portion 38). ). Of the sliding surfaces, one central sliding surface 35 has a size of 28 mm × 100 mm, and two outer sliding surfaces 34 on both sides in the width direction have a size of 25 mm × 100 mm.

  The concave slide body 40 is made of carbon steel (S50C). Of the sliding surfaces, the central sliding surface 45 of one central surface has a size of 28 mm × 170 mm, and two outer sliding surfaces on both sides in the width direction. The dimension of 44 is 14 mm × 170 mm, and any sliding surface is not quenched. The radius of curvature of the outer curved surface 41 of the concave slide body 40 is 65 mm.

  The support member 14 is made of carbon steel (S50C) and has dimensions of 60 mm × 60 mm × 100 mm. The central rod 11 is made of carbon steel (S45C) and has a φ (diameter) of 30 mm. The roller 21 is made of bearing steel (SUJ2) and has a size of φ10 mm × 10 mm. One side of one concave slide body 40 was supported by four rollers 21.

  The outer rod 22 is made of carbon steel (S45C) and has a diameter of 14 mm. The end support plate 16 is made of carbon steel (S50C) and has a size of φ180 mm × 50 mm. The intermediate support plate 17 is made of carbon steel (S50C) and has a size of φ180 mm × 50 mm. The connecting member 25 is made of carbon steel (S50C) and has a size of φ44 mm × φ105 mm × 100 mm.

  As the urging wire 10, a nickel-titanium alloy superelastic alloy wire manufactured by NEC TOKIN Corporation was used. The wire diameter of the superelastic alloy wire was 0.475 mm, and the winding pitch was 6 mm (number of turns 28.3 / 170 mm). The retainer 20 is made of fluorine sponge rubber and has a size of φ150 mm × 10 mm.

  As described in the above embodiments, the present invention aims to develop a damping device that can efficiently absorb vibration energy from a small amplitude to a large amplitude regardless of the natural period of the structure. The present invention proposes an axial force member type sliding damping device in which a frictional force as a force increases in proportion to an absolute value of displacement. According to the sliding device according to the present invention, the damping force is proportional to the displacement and the damping force does not depend on the natural period of the structure, and is small for a wide variety of structures. Absorption of vibration energy from amplitude to large amplitude can be performed efficiently.

1. Damping device (vibration damping device)
5 1st joint part (connection part)
7 Convex sliding part (first sliding part)
8 Recessed sliding part (second sliding part)
9 Sliding mechanism 9a Outer peripheral surface 10 Biasing wire (Biasing means, cord-like member)
30 Convex sliding body 32 Protruding portion 34 Outer sliding surface (second sliding surface)
35 Central sliding surface (first sliding surface)
40 concave sliding body 41 outer curved surface 42 groove 44 outer sliding surface (second sliding surface)
45 Central sliding surface (first sliding surface)
50 Sliding body mechanism 71 Damping device (vibration damping device)
71A damping device (vibration damping device)
80 Cylinder (Cylinder member)
85 Viscous fluid

Claims (7)

A vibration damping device configured to extend and contract in a predetermined direction, and to suppress the vibration of the structure by acting the damping force against the vibration of the structure as an axial force along the expansion and contraction direction,
A first sliding portion provided integrally with a connecting portion to the structure on one end side in the expansion and contraction direction, and relative to the first sliding portion in a state facing the first sliding portion A sliding mechanism having a second sliding portion provided so as to be reciprocally slidable in a direction along the expansion / contraction direction, and forming a cylindrical outer peripheral surface having the expansion / contraction direction as a cylinder axis direction,
An urging means provided along the outer peripheral surface, for urging the sliding mechanism in a direction in which the first sliding portion and the second sliding portion are pressed against each other; ,
Each sliding part of the first sliding part and the second sliding part is
As the amount of displacement in one direction of the reciprocating sliding direction increases from the neutral position in the range of the reciprocating sliding relative to the sliding part of the counterpart to slide, the sliding mechanism A first sliding surface having a shape that increases a dimension in a direction in which the sliding parts face each other;
As the amount of displacement in the other direction of the reciprocating sliding direction increases from the neutral position with respect to the sliding part of the other party that slides, the dimension of the sliding mechanism in the opposite direction increases. A second sliding surface having a shape to allow
Vibration damping device. One sliding portion of the first sliding portion and the second sliding portion is:
On the surface portion on the side facing the sliding portion of the other party that slides, along the reciprocating sliding direction, protrudes to the facing side, and has a protruding portion that has a convex shape in the direction of reciprocating sliding,
The other sliding part of the first sliding part and the second sliding part is:
On the surface portion on the opposite side, along the direction of reciprocating sliding and opening on the facing side, and having a groove portion that has a concave shape in the direction of reciprocating sliding,
The first sliding portion and the second sliding portion are:
The base end surface of the projecting portion and the end surface on the opening side of the groove portion are either one of the first sliding surface and the second sliding surface,
The projecting side end surface of the protrusion and the bottom surface of the groove are the other sliding surface of the first sliding surface and the second sliding surface,
The vibration damping device according to claim 1. The sliding mechanism includes the first sliding portion and the second sliding portion corresponding to the first sliding portion at a plurality of equiangular ranges around the axis of the axial force. In the state of the neutral position, a cylindrical outer peripheral surface is formed by a surface opposite to the side facing the first sliding portion of the plurality of second sliding portions.
The vibration damping device according to claim 1 or 2. The sliding mechanism has the first sliding portion and the second sliding portion corresponding to the first sliding portion at four locations around the axis of the axial force, and these sliding portions are in the neutral position. In the state in which a cylindrical outer peripheral surface is formed by a surface opposite to the side facing the first sliding portion of the four second sliding portions.
The vibration damping device according to claim 1 or 2. The urging means is a cord-like member wound around the outer peripheral surface of the sliding mechanism.
The vibration damping device according to any one of claims 1 to 4. The cord-like member is a superelastic alloy wire,
The vibration damping device according to claim 5. A cylindrical member having a cylindrical axial direction as the expansion / contraction direction, and a cylinder member surrounding the sliding mechanism and the urging means,
The cylinder member is filled with a viscous fluid,
The vibration attenuating device according to any one of claims 1 to 6.