JP2006250329A - Vibration absorbing device and anti-seismic rack using it - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration absorbing device and an anti-seismic rack using it capable of exerting a large damping force while the configuration remains simple and compact. <P>SOLUTION: The arrangement according to the invention is configured with guiding/supporting means 12 and 15 to guide and support a weight 12 reciprocatively, a position holding means 15 to hold the weight with resilient balancing in any position on the way of reciprocation due to the guiding/supporting means 12 and 15, pinching means 16 and 17 to pinch part 13 of the weight (including a member provided rigidly with the weight) in the directions intersecting the reciprocating motions, and a pressurizing means 18 to act a resilient force on the pinching means 16 and 17. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a vibration absorber and a seismic rack using the same.

Electronic devices such as communication devices are required to have earthquake resistance so that the devices are not destroyed by an earthquake. As a seismic measure for a conventional electronic equipment housing rack, there is a method in which the entire rack is slidable to form a pedestal portion and separated from floor vibration (see, for example, Patent Document 1).
This method has the following worrisome attributes: (B) Since the entire mass of the rack on which the electronic device is mounted is applied to the seismic device, the slide device is required to be strong and expensive. (B) In order to install the rack in a slidable manner, a space is required around it and a lot of installation space is required. (C) Since it is configured to be attached to the rack base, it requires extensive work to remove the wiring and move the rack in order to attach to the existing equipment. Have difficulty. (D) It is necessary to take measures such as moving to a region where seismic waves are avoided with respect to the natural frequency of seismic devices equipped with racks.

As another example of earthquake resistance measures, there is a method of mounting an electronic device unit in a rack via a spring or the like to separate the electronic device from vibration (see, for example, Patent Document 2).
This method has the following worrisome attributes: (E) A space is required between the rack and the electronic device in order to secure the movement amount of the electronic device unit, and the space utilization efficiency is low. (F) It is difficult to add to existing equipment. (G) It is necessary to take measures such as moving to the area where the seismic waves are avoided with respect to the natural frequency of the electronic equipment mounted via springs.

On the other hand, a vibration absorber that attenuates vibration of an object by adding a vibration system having a damping force to the object to be controlled has been proposed in fields other than electronic equipment (see, for example, Patent Document 3).
By adding to the object to be damped, the preceding example according to the proposal can attenuate the vibration when the object is free vibrating, and if the object is forcedly vibrating, the object of the object against the vibration can be attenuated. Response magnification can be lowered.

  In this case, when the natural frequency of the dynamic vibration absorber is matched with the natural frequency of the object to be damped, the effect is greatest, and the damping force of the dynamic vibration absorber has an optimum value that maximizes the effect. In the previous case, considering this point, the natural frequency and damping force of the dynamic vibration absorber can be adjusted. In addition, the frictional force is used as the damping force, and an expensive damper is not used, so that it is relatively inexpensive. However, the precedent case has the following characteristics of concern:

  (H) When applied to earthquake resistance measures for electronic equipment, it is generally necessary to withstand a forced excitation force with a maximum acceleration of 0.5 to 1.0 G in an earthquake resistance test standard that assumes a seismic wave. Requires a frictional force of several hundred N to act on the mass. In the structure of the preceding case, it is difficult to apply a sufficiently large damping force to the mass point because a frictional force is applied to the rotating shaft of the pendulum. (Ii) When a friction force having a constant magnitude is used as the damping force, the damping effect is less than that of the damper. (Nu) It does not have a shape that can be mounted on a rack for mounting electronic equipment without wasting space.

JP 2001-349373 A JP 2002-16375 A JP-A-11-287285

  In the prior art, there are characteristics to be concerned that have been pointed out in the above (a) to (nu), and there is a problem that it is difficult to obtain a large damping force with a compact configuration.

  The present invention has been made to solve the above-described problems, and an object thereof is to provide a vibration absorber capable of obtaining a large damping force with a simple and compact configuration, and an earthquake-resistant rack using the vibration absorber.

  A vibration absorber according to the present invention and an earthquake-resistant rack using the vibration absorber include a guide support unit that guides and supports a weight so that the weight can reciprocate, and an elastic force applied to the weight at an arbitrary fixed position in the reciprocating direction by the guide support unit. Position holding means for holding the balance, clamping means for sandwiching a part of the weight from a direction crossing the reciprocating direction, and pressing means for applying an elastic force to the clamping means.

  According to the present invention, it is possible to provide a vibration absorber that can obtain a large damping force with a simple and compact configuration, and an earthquake-resistant rack using the vibration absorber.

Embodiment 1 FIG.
1 and 2 show the internal structure of the vibration absorber according to the first embodiment. 1A is a plan view of the vibration absorber with the top cover 22 removed, FIG. 1B is a sectional view taken along the line X1-X1 of FIG. 1A, and FIG. 2 is an exploded perspective view of the vibration absorber. The frame 11 having a rectangular frame shape is closed at the top and bottom of the frame by the bottom lid 23 and the top lid 22 to form an internal space. The internal structure of the vibration absorber is housed in this internal space. In FIG. 1A, the characters “front”, “rear”, “left”, and “right” attached to the arrows indicate directions determined for convenience of explanation. In addition, the back side penetrating the paper surface is “lower” and the near side is “up”.

  The weight 12 having a rectangular plate shape in the frame 11 is formed with protrusions 12a at the ends in the front-rear direction and at the center in the left-right direction, and these protrusions 12a have through holes 12b in the left-right direction. Is formed. A guide shaft 20 is slidably inserted in these through holes 12b so as to be reciprocally movable in the left-right direction. Both ends of the guide shaft 20 are fixed to the frame 11. Further, the extensible spring 15 is mounted on the guide shaft 20 between the protrusion 12a and the left and right frames 11, respectively. Here, the guide shaft 20 is an example of a guide support unit that guides and supports the weight 12 so as to be capable of reciprocating in the left-right direction.

  Further, the springs 15 that are stretched opposite to each other with the protrusion 12a interposed therebetween have the same elastic force, and in the center of the frame 11 in the left-right direction, in balance with the elastic force that the spring has, at a fixed position. Is maintained. That is, the weight 12 is positioned and held in the frame 11 by the spring 15, and the pair of springs 15 arranged to face each other are position holding means for holding the weight 12 in a fixed position. In the present embodiment, two guide shafts 20 are provided through holes formed in the weight 12 and used as a guide when the weight 12 repels the spring 15 and slides left and right. The structure of may be sufficient.

  The upper surface of the weight 12 is formed with a protruding portion 13 which is long in the left-right direction, or is fixed. The protruding portion 13 is sandwiched between a fixed plate 16 and a movable plate 17 slidable in the front-rear direction. It is out. The fixing plate 16 is a U-shaped plate, and its left and right end portions are bent downward, and the bent flat portion is brought into contact with the side surface of the frame 11 to be fastened by fastening means 14 including bolts and nuts. It is fixed. The movable plate 17 is bent downward at the front and left and right ends, and covers the front side of the weight 12 with the left and right ends slidably fitted to the frame 11.

  An extensible spring 18 is interposed between the bent portion at the front end of the movable plate 17 and the frame 11 to urge the movable plate 17 rearward. The movement of the movable plate 17 due to the elasticity of the spring 18 is prevented by the movable plate 17 coming into contact with the protrusion 13.

The fixed plate 16 and the movable plate 17 constitute sandwiching means for sandwiching a part of the weight 12 (projection 13) from the front-rear direction intersecting the reciprocating direction (left-right direction). The spring 18 constitutes a pressurizing unit that applies an elastic force to the movable plate 17 that is a clamping unit.
In this manner, the spring 18 pushes the movable plate 17 backward, and a frictional force is generated between the weight 12, the fixed plate 16, and the movable plate 17.

  In the first embodiment, the frictional force is generated at two positions on both sides of the protrusion 13 in the front-rear direction, so that the total reaction force of the spring 18 and between the weight 12 and the front and rear plates (the fixed plate 16 and the movable plate 17). Twice the product of the friction coefficient. In general, since a rack on which an electronic device is mounted is the weakest with respect to left-right vibration, the present embodiment is designed to exhibit a damping effect with respect to left-right vibration.

In order to exert the effect in the front-rear direction, the vibration absorber shown in FIG. Moreover, the effect is the same even if this apparatus is attached to the front and back.
According to the vibration damping device of the first embodiment, a shape with reduced thickness (vertical direction in the figure) can be realized, and therefore, when mounted on a rack, there is little influence on the rack mounting amount. Further, since the fixed plate 16 and the movable plate 17 are arranged along the load direction (front-rear direction) of the spring 18 that generates the frictional force, it is easy to ensure the strength of the fixed plate 16 and the movable plate 17, and strong friction. Can generate power. Further, since the generated frictional force acts directly on the weight 12, it is easy to obtain a large damping force.

Embodiment 2. FIG.
3 and 4 show an example of the second embodiment. FIG. 3B is a cross-sectional view taken along the line X2-X2 in FIG. The present embodiment is different from the first embodiment in that the clamping means and a part of the weight (including a member integrated with the weight) sandwiched between the clamping means and the weighting means are multistage (plural). . 3 and 4, members having the same functions as those in FIGS. 1 and 2 described above are denoted by the same reference numerals and description thereof is omitted.

  This is an example in which the protrusion 13 is improved. Similar to the protrusion 13 in the weight 12 in FIG. 1 described above, a protrusion 31 is integrally or fixedly provided on the upper surface of the weight 12. The protruding pieces 32 and 33 have a convex shape when viewed from the longitudinal direction, and the longitudinal direction of the protruding pieces 32 and 33 is adjusted to the left and right in a rectangular hole 12c formed on the upper surface of the weight 12, as shown in FIG. It is stored side by side in the direction. The lower steps 32 a and 33 a are accommodated in the rectangular hole 12 c, and the protrusions 32 b and 33 b protrude above the upper surface of the weight 12.

  The protruding pieces 32 and 33 are inserted in a skewered manner in the front-rear direction by a shaft 36, and both end portions of the shaft 36 are fixed to the weight 12. Since the dimension in the front-rear direction in which the projecting pieces 32, 33 are combined is slightly smaller than the dimension in the front-rear direction of the rectangular hole 12c, the projecting pieces 32, 33 can slide in the front-rear direction using the shaft 36 as a guide. The protrusions 32 and 33 are restricted by the rectangular hole 12c in the left-right direction and cannot move and are fixed to the weight 12. The vertical direction is also restricted by the shaft 36 and cannot be moved. In other words, these members move integrally with the weight 12 with respect to these directions, and thus are members integrated with the weight 12.

  As described above, the protrusions 32 and 33 that can be slid only in the front-rear direction in order to ensure contact with the plate, and the fixed plate 16, the movable plate 17, the plates 34 and 35, etc., are arranged in multiple stages as the plates sandwiching them. 3 stages). The plates 34 and 35 and the slidable protrusions 32 and 33 are effective even in two stages, and the effect increases as the number of stages increases.

  The reaction force of the spring 18 acts on the protrusion 31 via the movable plate 17 and the protrusions 32 and 33 and plates 34 and 35 that can slide back and forth. At this time, the frictional force is generated between the movable plate 17, the protrusions 32 and 33 slidable in the front-rear direction, the plates 34 and 35, and the protrusions 31. Is 6 times the product of the total reaction force of the spring 18 and the friction coefficient. Therefore, a large frictional force can be generated more efficiently than in the first embodiment, the reaction force of the spring 18 can be reduced, the size of the spring can be reduced, and the frame, the fixed plate, which supports the reaction force of the spring 18, Ensuring the strength of the movable plate is facilitated and the size can be reduced.

Embodiment 3 FIG.
5 and 6 show an example of the third embodiment. FIG. 5B is a cross-sectional view taken along line X3-X3 in FIG. In this example, on the basis of the structure described in the first embodiment or the second embodiment, a surface that sandwiches a part of the weight (including a member integrated with the weight) of the member constituting the clamping means. It is supposed to be composed of a slope 21.

  In the third embodiment, instead of the movable plate 17 in the example shown in FIGS. 1 to 4 in which the rear end face is linear in the left-right direction, as shown in FIG. The rear end face advances outwardly in the reciprocating direction (left and right) with a fixed position (intermediate position in the left and right direction) where the force is balanced by two springs 15 arranged opposite to each other on the guide shaft 20 Accordingly, the movable plate 170 having two slopes 21 in the shape of a mountain having a climbing slope is used. The base point coincides with the center of the flat columnar protrusion 13 provided on the upper surface of the weight 12 so as to protrude from the center position.

  When the weight 12 strokes (moves) in the left-right direction due to vibration, the protrusion 13 of the weight 12 presses the inclined surface 21 to push the movable plate 170 forward, and the spring 18 further compresses regardless of the left-right movement. Is done. As a result, the reaction force of the spring 18 increases and the frictional force between the protrusion 13 and the movable plate 170 or the fixed plate 16 increases. By setting the compression amount of the spring 18 at the position where the weight 12 is not in a stroke, that is, the position of the protrusion 13 including the base point, the friction amount having a magnitude proportional to the displacement amount of the weight 12 with respect to the vibration absorber. Can generate power.

  When this structure is used, the vibration damping ability is improved. FIG. 7 shows an example of calculating the effect by numerical analysis. FIG. 7 shows the response magnification A / Ast of the acceleration acting on the object to be controlled with respect to the forced acceleration. The characteristic without the anti-earthquake measures is the curve 60, the characteristic of the first embodiment is the curve 61, and the characteristic of the third embodiment is shown. A curve 62 and, as a reference, a characteristic of a vibration absorber using a damper is indicated by a curve 63. The maximum response magnification of about 19 times when no countermeasure is taken can be reduced to about 7.4 times according to the first embodiment and about 5.3 times according to the third embodiment. As is apparent from FIG. 7, in the third embodiment, a damping performance comparable to that of a vibration absorber using a damper can be obtained.

Embodiment 4 FIG.
8 and 9 show an example of the fourth embodiment. FIG. 8B is an X4-X4 cross-sectional view in FIG. The fourth embodiment is a combination of the second embodiment and the third embodiment. That is, a part of a weight (including a member integrated with the weight) and a sandwiching means sandwiching the weight are provided in multiple stages in a direction (front-rear direction) intersecting the reciprocating direction (left-right direction), Ascending slope as the surface of the member constituting the clamping means that sandwiches a part of the weight (including a member integrated with the weight) advances outward in the reciprocating direction with the fixed position as a base point It has a configuration that consists of a slope.

  8 and 9, a protrusion 31 is integrally or fixedly provided on the upper surface of the weight 12 in the same manner as in FIGS. The protrusions 32 and 330 have a convex shape when viewed from the longitudinal direction. As shown in FIG. 9, the longitudinal direction of the projection pieces 32 and 330 is adjusted to the left and right in the rectangular hole 12 d formed on the upper surface of the weight 12. It is stored side by side in the direction. The lower steps 32 a and 330 a are accommodated in the rectangular hole 12 d, and the protrusions 32 b and 330 b protrude above the upper surface of the weight 12.

  The projecting pieces 32 and 330 are inserted in a skewered manner in the front-rear direction by a shaft 360, and both end portions of the shaft 360 are fixed to the weight 12. Since the dimension in the front-rear direction in which the projecting pieces 32 and 330 are combined is slightly smaller than the dimension in the front-rear direction of the rectangular hole 12d, the projecting pieces 32 and 330 are slidable in the front-rear direction using the shaft 360 as a guide. The protrusions 32 and 330 are fixed to the weight 12 in the left-right direction, being restricted by the rectangular hole 12d and not being able to move. The vertical direction is also restricted by the shaft 360 and cannot be moved. In other words, these members move integrally with the weight 12 with respect to these directions, and thus are members integrated with the weight 12.

As described above, the fixed plate 16, the movable plate 170, the plates 34, 35 are sandwiched between the protrusion 31 and the protrusions 32, 330 slidable only in the front-rear direction to ensure contact with the plate. Etc. are provided in multiple stages (three stages).
Further, in the fourth embodiment, as in the third embodiment, a fixed position (right-and-left direction) in which force is balanced by two springs 15 in which the end surface in the front-rear direction of the movable plate 170 is disposed opposite to the guide shaft 20 is used. The two slopes 21 are mountain-shaped and have an upward slope as they go outward in the reciprocating direction (left and right) with the intermediate point at the center as the starting point. The base point coincides with the center of the semi-cylindrical portion 330c formed at an intermediate position in the left-right direction of the protruding portion 330b.

  When the weight 12 strokes (moves) in the left-right direction due to vibration, the semi-cylindrical portion 330c formed on the protrusion 330b of the weight 12 presses the inclined surface 21 to move the movable plate 170 forward regardless of the left-right movement. And the spring 18 is further compressed. As a result, the reaction force of the spring 18 acts on the projecting portion 31 via the movable plate 170 and the projecting piece 32 slidable back and forth and the plates 34 and 35.

  At this time, the frictional force is generated between the movable plate 170, the protrusions 32b and 330b slidable in the front-rear direction, the plates 34 and 35, and the protrusions 31. The friction force acting on 12 is six times the product of the total reaction force of the spring 18 and the friction coefficient. Therefore, the reaction force of the spring 18 can be reduced, the spring can be reduced in size, and the compression amount of the spring 18 can be made substantially zero at the position of the semi-cylindrical portion 330c including the base point as in the third embodiment. Thus, a frictional force having a magnitude proportional to the amount of displacement of the weight 12 with respect to the vibration absorber can be generated.

Embodiment 5. FIG.
10 and 11 show an example of the fifth embodiment. In the fifth embodiment, on the basis of the structure of the vibration absorber in the first embodiment, an auxiliary weight 140 is provided on the weight 12 by bolting so as to be added or removed. The frame 11 has a space for accommodating the auxiliary weight 140 in advance, and a screw hole for bolting the auxiliary weight is formed in the weight 12.

  A plurality of auxiliary weights 140 can be attached to the weight 12 in a stacked manner, and various loads can be obtained by combination. The natural frequency of the vibration absorber can be adjusted by increasing / decreasing the auxiliary weight 140, and the natural frequency of the vibration absorption unit can be adjusted to match the natural frequency of the vibration suppression target. As a result, it is possible to suppress vibrations to be controlled with different natural frequencies with the same vibration absorber, and to reduce the manufacturing cost of the vibration absorber. Moreover, after investigating the natural frequency of the vibration suppression target, a vibration absorbing device can be added quickly and the construction period can be shortened. Of course, such an auxiliary weight can be applied to the second to fourth embodiments described above and the embodiments described below.

Embodiment 6 FIG.
FIG. 12 shows an example of the sixth embodiment. In the sixth embodiment, the climbing slope of the slope 21 in the third embodiment (FIG. 5), the fourth embodiment (FIG. 8), etc. is variable. In the sixth embodiment, instead of the movable plate 170 in the third embodiment (FIG. 5), as shown in FIG. 12, a movable plate 1700 whose rear end face is parallel to the left-right direction is used.

  A rotating plate 41 having a rectangular plate shape is rotatable about a fulcrum shaft 42 provided on the movable plate 1700, and a free end side is fixed with a screw 43. The position of the fulcrum shaft 42 is in the vicinity of the protrusion 13 and in the vicinity of the rear end of the movable plate 1700. The position to be fixed by the screw 43 is variable at an arbitrary position on the movable plate 1700 and on the elongated hole 44 formed in an arc shape with the fulcrum shaft 42 as the center. That is, the free end side of the rotating plate 41 can be protruded rearward from the rear end face of the movable plate 1700.

  Two sets of the rotating plates 41 are arranged symmetrically with respect to a front-rear direction line passing through the center of the protrusion 13 as a target axis. Thereby, the slope 21 similar to the slope 21 shown in FIG. 5 can be obtained, and the slope is variable. By changing the position where the rotating plate 41 is fixed on the long hole 43, the angle of the inclined surface can be changed. Thereby, the magnitude of the frictional force generated according to the stroke (movement) of the weight 12 can be adjusted. The magnitude of the frictional force has an optimum value that maximizes the damping effect with respect to the mass of the object to be controlled and the mass of the weight.

  Therefore, by making the frictional force adjustable, it is possible to optimally suppress vibrations to be controlled with different masses and natural frequencies with the same vibration absorber, and to reduce the manufacturing cost of the vibration absorber. In addition, after investigating the mass and natural frequency of the vibration suppression target, a vibration absorber can be added quickly and the construction period can be shortened. It goes without saying that such a rotating plate mechanism can be appropriately applied to the embodiments described so far and the embodiments described below.

Embodiment 7 FIG.
FIG. 13 shows an example of the seventh embodiment. The present embodiment is a combination of the second embodiment, the fifth embodiment, and the sixth embodiment. That is, (1) a part of the weight (including a member integrated with the weight) and a clamping means for sandwiching the weight are provided in multiple stages, and (2) the weight allows the auxiliary weight to be attached and detached. ) Ascending slope as the surface of the member constituting the clamping means that sandwiches a part of the weight (including the member integrated with the weight) proceeds outward in the reciprocating direction with the fixed position as a base point The slope of the slope consisting of the slope becomes variable and adjustable.

  In FIG. 13, the protruding portion 31, the protruding pieces 32 and 33, the fixing plate 16, and the plates 34 and 35 that are part of the weight 12 are the same as those described in FIGS. 8 and 9 in the fourth embodiment. is there. Further, the configuration capable of adjusting the slope of the slope, such as the movable plate 1700, the rotating plate 41 having the slope 21, the fulcrum shaft 42, the screw 43, and the long hole 44, is the same as that of the sixth embodiment described with reference to FIG. is there. Further, the configuration of the auxiliary weight 140 and the bolt 50 is the same as that of the fifth embodiment described with reference to FIGS.

  The frictional force acting on the weight 12 can be dramatically increased by providing a plurality of clamping means for sandwiching a part of the weight 12 (projecting portion 31) or a member integrated with the weight 12 (projecting pieces 32, 33, etc.). Therefore, since the reaction force of the spring 18 can be reduced, the spring 18 can be reduced in size and the frame, fixed plate, and movable plate that support the reaction force of the spring 18 can be easily secured and reduced in size. it can.

  Moreover, the magnitude of the frictional force generated according to the stroke (movement) of the weight 12 can be adjusted by making the angle of the slope changeable, and the mass and the natural frequency are different by making the frictional force adjustable. Optimum damping can be performed with the same vibration damping device on the vibration damping object, and the manufacturing cost of the vibration damping device can be reduced.

Furthermore, it is possible to suppress vibrations to be controlled with different natural frequencies with the same vibration absorber, thereby reducing the manufacturing cost of the vibration absorber. Moreover, after investigating the natural frequency of the vibration suppression target, a vibration absorbing device can be added quickly and the construction period can be shortened.
By making the auxiliary weight attachable to and detachable from the weight, it is possible to control the vibration suppression target having different natural frequencies with the same vibration absorber, thereby reducing the manufacturing cost of the vibration absorber. Moreover, after investigating the natural frequency of the vibration suppression target, a vibration absorbing device can be added quickly and the construction period can be shortened.

Embodiment 8 FIG.
FIG. 14 shows an example of the eighth embodiment. In the present embodiment, all of the embodiments of the vibration absorber described so far or the external shape of the vibration absorber having an arbitrarily selected configuration is formed into a shape that can be mounted on a general-purpose 19-inch rack. The vibration absorber 55 may be any of the first to seventh embodiments, or may be an arbitrary combination thereof. In order to be able to fix the vibration absorbing device 50 with a screw when the vibration absorbing device 50 is attached to the rack, a mounting seat 51 is provided on the vibration absorbing device 50, and screw grooves 52 are provided on the left and right of the seat 51. The dimension W conforms to the JIS standard or EIA standard. By providing a mounting diameter portion that can be mounted on such a 19-inch rack, if the JIS standard or EIA standard 19-inch rack is used, it is possible to install a vibration absorber on the top of the rack without any special processing. Even in an existing rack, if there is a free space above the rack, the vibration absorber of the present invention can be easily installed.

Embodiment 9 FIG.
FIG. 15 shows an example of the ninth embodiment. FIG. 15A is a front view of a rack for mounting an electronic device, and FIG. 15B is a side view thereof. Various electronic devices 2 are mounted on each stage of the rack 1. The vibration absorber 3 proposed by the present invention is attached to the uppermost space of the rack 1. In the first to eighth embodiments described above, the vibration absorber 3 can obtain a large damping force with a simple and compact configuration, and thus can have an outer shape with a reduced thickness in the vertical direction. Such a thin vibration absorber If so, it does not affect the amount of equipment mounted on the rack.

1A is a plan view of the vibration absorber, and FIG. 1B is a cross-sectional view taken along the line X1-X1 of FIG. It is a disassembled perspective view of a vibration absorber. 3A is a plan view of the vibration absorber, and FIG. 3B is an X2-X2 cross-sectional view of FIG. It is a disassembled perspective view of the protrusion piece integrated in the weight. 5A is a plan view of the vibration absorber, and FIG. 5B is an X3-X3 cross-sectional view of FIG. 5A. It is a perspective view of the fixed plate and movable plate which clamp a projection part. It is a characteristic curve figure which shows the response magnification with respect to the forced acceleration of the acceleration which acts on a damping object. 8A is a plan view of the vibration absorber, and FIG. 8B is an X4-X4 cross-sectional view of FIG. 8A. It is a disassembled perspective view of the protrusion piece integrated in the weight. It is a top view of a vibration absorber. It is a disassembled perspective view of the weight which attached the auxiliary weight. It is a top view of a vibration absorber. It is a top view of a vibration absorber. FIG. 14A is a front view of the vibration absorber, and FIG. 14B is a bottom view of the vibration absorber. FIG. 15A is a front view of the rack, and FIG. 15B is a side view of the rack.

Explanation of symbols

  12 Weight, 13 Protrusion, 15 Spring, 16 Fixed plate, 17 Movable plate, 18 Spring, 20 Guide shaft.

Claims (7)

  A guide support means for guiding and supporting the weight so as to be able to reciprocate; a position holding means for holding the weight in a balance of elastic force at an arbitrary fixed position in the reciprocating direction by the guide support means; and a part of the weight A vibration absorbing device comprising: a holding means for holding the screw from a direction crossing the reciprocating direction; and a pressing means for applying an elastic force to the holding means.   2. The vibration absorber according to claim 1, wherein a part of the weight and a sandwiching means for sandwiching the part are provided in multiple stages in a direction intersecting the reciprocating direction.   The surface of the member constituting the clamping means that sandwiches a part of the weight is formed of an inclined surface having an upward slope as it proceeds outward in the reciprocating direction with the fixed position as a base point. The vibration absorber according to claim 1 or 2.   The vibration absorber according to any one of claims 1 to 3, wherein the weight is detachable from an auxiliary weight.   The vibration absorber according to any one of claims 2 to 4, wherein the slope of the slope is variable and adjustable.   The vibration absorber according to any one of claims 1 to 5, further comprising an attachment shape portion that can be mounted on a 19-inch rack conforming to JIS standard or EIA standard.   An earthquake-resistant rack comprising the vibration absorber according to any one of claims 1 to 6.

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