JP2006258260A - Vibration isolator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an anti-vibration device that can be easily designed and processed by using only one metal material.
An anti-vibration device includes two flanges 1 fastened to a structure and a place where the structure is installed, and a beam-shaped neck 4 that couples the two flanges 1. A film 3 is formed on the flange 1 by punching. Therefore, the vibration isolator can be configured with one material. In addition, it is possible to absorb vibration in the vertical direction and to design the vertical spring coefficient and the horizontal spring coefficient independently.
[Selection] Figure 1

Description

  The present invention relates to a technique for blocking vertical and horizontal vibrations and preventing structural vibrations, and more particularly, to a vibration isolator having a simple structure using only one material.

  A conventional vibration isolator is configured by combining a plurality of processed products in order to block both vertical and horizontal vibrations. As related techniques, JP 2000-337439 A, JP 9-14346 A, JP 2002-227898 A, JP 9-189341 A, JP 2004-169533 A, JP 2003 2003 A. There are inventions disclosed in JP-A-313883, JP-A-9-144810, JP-A-6-346628, and JP-A-2000-161430.

  An omnidirectional vibration isolation suspension system disclosed in Japanese Patent Application Laid-Open No. 2000-337439 includes a first vibration isolation device having a first elastic structure having a first end and a second end spaced apart from each other, and a compressive load. A second vibration isolation device having a second elastic structure configured to receive the first vibration isolation device and connected in series in the axial direction to the first vibration isolation device. The first elastic structure has a lateral stiffness corresponding to the movement of the first end relative to the second end, an axial stiffness supporting the object, and an elastic instability point corresponding to the axial load. Has one end that supports the object, axial stiffness, and zero axial stiffness at the elastic instability point corresponding to the compressive load.

  The invention disclosed in Japanese Patent Application Laid-Open No. 9-14346 is a seismic isolation device for absorbing displacement in different directions due to vibrations such as earthquakes, and a side surface between parallel upper and lower plates. A plurality of vibration absorbers made of a steel plate or the like on which a connection plate for vibration absorption consisting of a bent plate or a vertical plate is bent in a vertical direction via an elastic body such as a rubber plate. It consists of the structure which connected and shifted the direction of the vibration absorption connecting plate of a piece and a vibration absorber horizontally.

  Moreover, the vibration-isolating damper disclosed in Japanese Patent Application Laid-Open No. 2002-227898 uses a steel pipe as a damper main body, and cuts the intermediate portion between the base portions in a spiral shape, leaving the base portions at both ends in the axial direction. A spiral portion continuous with the base portion is formed in the portion.

  In the three-dimensional vibration absorber disclosed in Japanese Patent Laid-Open No. 9-189341, both ends of eight elastic bodies formed in a semi-elliptical shape are connected between two opposing fixing plates. Fix it. The middle part of the elastic body is arranged radially and at an equal pitch. The fixing plate is fixed to the installation surface during installation, and a supporting device is attached to the fixing plate.

  Further, in the seismic isolation bearing device disclosed in Japanese Patent Application Laid-Open No. 2004-169533, the base plate and upper plate of the seismic isolation bearing device that are coupled and fixed to the foundation of the structure and the structure supported on the foundation, respectively. Between the two spring plates for seismic isolation with a plurality of semicircular arcs, and by fixing both ends of the spring members to the upper and lower plates, it is integrated as a seismic isolation support device. It is configured to absorb the displacement caused by the load and to quake the shaking caused by the earthquake.

  Further, the invention disclosed in Japanese Patent Application Laid-Open No. 2003-313883 is a seismic isolation device that reduces shaking of a building, and a receiving hole portion having a concave surface equipped on the building side, and a support rod body having elastic characteristics, And the building is supported by the engagement between the support bar and the receiving hole.

  Further, a three-dimensional seismic isolation device for a structure disclosed in Japanese Patent Application Laid-Open No. 9-144810 has a rubber bearing mechanism that alleviates horizontal vibration by a seismic isolation action of laminated rubber bodies laminated in a vertical direction, and a vertical And a disc spring support mechanism that relieves vibration in the direction by the seismic isolation action of the disc spring laminate laminated in the vertical direction, so that no horizontal vibration force acts on the disc spring laminate in the disc spring support mechanism. A guide transmission mechanism and a load support member that supports α% (0 ≦ α <100) of the static load in the vertical direction are provided.

  Further, the three-dimensional seismic isolation device disclosed in Japanese Patent Laid-Open No. 6-346628 is composed of a pair of opposed flanges and a spring material installed between the flanges, and a protrusion is formed on the opposite flange side of one flange. Consists of a vertical seismic isolation device that protrudes and has a cylindrical engagement portion that protrudes on the other flange so as to surround the projection so as to be relatively movable in the vertical direction, and two horizontal seismic isolation devices made of laminated rubber The horizontal seismic isolation devices are arranged on both sides of the vertical seismic isolation device in the axial direction.

The three-dimensional seismic isolation device disclosed in Japanese Patent Application Laid-Open No. 2000-161430 includes a first member, a second member, a first frictional force generating means, a spring means, and a second frictional force generating means. The spring means is disposed between the upper end surface of the cylindrical portion of the first member and the lower surface of the disc portion of the second member. The first frictional force generating means includes a first sliding contact member attached to the upper structure and a second sliding contact member attached to the upper surface of the disk portion. The second frictional force generating means includes a third sliding contact member attached to the outer peripheral surface of the columnar portion of the first member, and a fourth sliding contact member attached to the inner peripheral surface of the cylindrical portion of the second member. Consists of.
JP 2000-337439 A Japanese Patent Laid-Open No. 9-14346 JP 2002-227898 A JP-A-9-189341 JP 2004-169533 A JP 2003-313883 A JP-A-9-144810 JP-A-6-346628 JP 2000-161430 A

  In the above-mentioned Patent Document 1, the strength design of each of ten or more parts is necessary to support one structure, and further, the dynamic design of the spring constant that combines them is necessary. There was a problem that processing took time and cost. In addition, since a coil spring is used, the problem of surging in the high frequency band is unavoidable.

  Further, in Patent Document 2, the vertical direction is a bent plate and an elastic body, the horizontal direction is an elastic body that absorbs vibration energy, and the horizontal direction borrows the force of the elastic body. There is a problem that the durability of the invention itself depends on the durability of the elastic body. Although the spring constant depends on the size of the elastic body, there is a problem that independent spring constant design cannot be performed because the vertical direction and the horizontal direction are coupled. In addition, since it is formed of a plurality of parts, there is a problem that it takes time and cost to design and process.

  Further, in Patent Document 3, it is necessary to process a metal in a spiral shape, which requires a great deal of cost for processing, and the design of the spring constant requires an empirical rule by a large number of experiments. was there.

  Further, in Patent Document 4 and Patent Document 5, since the spring constant is determined by the elasticity of a plurality of rings, a plurality of processes are necessary, and the design is difficult because the spring constants in the vertical direction and the horizontal direction are coupled. There was a problem.

  Further, in Patent Document 6, a lateral spring constant is determined by a method in which a large number of disc springs are stacked in the vertical direction, the support rod is supported by the rigidity of the disc springs, and the slip with the supporting structure is adjusted. ing. Therefore, there is a problem that the design of the horizontal spring constant determined by the amount of deflection with respect to the slip has to be determined empirically and is difficult to design.

  Further, in Patent Documents 7 and 8, since metal springs and anti-vibration rubber are used, it takes time and cost to design and process, and the durability of the invention itself depends on the durability of the rubber. There was a problem.

  Further, in Patent Document 9, since different types of spring mechanisms such as a spring and a frictional force generating means are combined, it is difficult to design and process, and the spring constant due to friction is non-linear and the vibration-proof design is very difficult. There was a problem that it was difficult.

  The present invention has been made to solve the above problems, and a first object thereof is to provide a vibration isolator that facilitates design processing by using only one metal material.

  The second object is to provide an anti-vibration device that is durable and can be easily designed independently of the spring constants in the vertical and horizontal directions.

  The present invention is an anti-vibration device for preventing vibration of a structure, and includes two flange portions fastened to the structure and the installation location of the structure, and a beam-shaped neck that couples the two flange portions. In other words, at least one of the two flange portions is pierced to form a film.

  Preferably, the beam-shaped neck has a shape with R at the base.

  Preferably, the membrane has a curved shape.

  Preferably, the beam-like neck has the same surface as the surface on which the film of the flange portion is formed.

  Preferably, the vibration isolator has a structure in which a plurality of spring structures including two flange portions and a beam-shaped neck are connected in series.

  Preferably, the vibration isolator is made of a vibration-damping material.

  Preferably, the vibration isolator further includes a damping material provided between the structure and the installation location.

  In the present invention, the vibration isolator is composed of two flange portions that are fastened to the structure and the installation place of the structure, and a beam-shaped neck that connects the two flange portions. An anti-vibration device can be configured.

  Since at least one of the two flange portions forms a film by scooping out, it can absorb vertical vibrations, and the spring coefficient in the vertical direction and the spring coefficient in the horizontal direction are designed independently. It becomes possible to do.

  Further, since the beam-shaped neck has a shape with an R at the base, the vertical spring coefficient can be changed, and the magnitude of the stress at the base of the beam-shaped neck can be adjusted.

  Further, since the film has a curved shape, it is possible to reduce the stress generated in the film due to the force in the vertical direction.

  In addition, since the beam-shaped neck has the same surface as the surface on which the film of the flange portion is formed, the stress concentrated on the base of the beam-shaped neck can be dispersed.

  Further, since the vibration isolator has a structure in which a plurality of spring structures including two flange portions and a beam-shaped neck are connected in series, even if each of the spring structures is stiff, a soft spring is configured. It becomes possible.

  Further, since the vibration isolator is made of a material having vibration damping properties, it is possible to reduce the increase in amplitude at the resonance frequency.

  In addition, since the vibration isolator further includes a damping material provided between the structure and the installation location, it is possible to reduce the increase in amplitude at the resonance frequency even when the spring is made of a material having no vibration damping property. It becomes.

(First embodiment)
FIG. 1 is a cross-sectional view of a vibration isolator according to a first embodiment of the present invention. This vibration isolator includes two flanges 1 and a beam-like neck 4 that connects the central portions of the two flanges 1. A bolt fastening portion 2 for coupling with a structure is provided in a peripheral portion of one flange 1, and the structure and the vibration isolator are rigidly coupled with the bolt.

  In addition, a bolt fastening portion 2 for coupling to the ground on which the structure is installed is provided in the peripheral portion of the other flange 1, and the vibration isolator and the ground are rigidly coupled by the bolt. The two flanges 1 or one of the flanges 1 is removed from the bolt fastening portion 2 toward the center, and a film 3 is formed.

  The central portions of the two flanges 1 are connected by a beam-like neck 4. This shape can be formed, for example, by cutting out a rod having the diameter of the flange 1 or by separately forming and welding the flange 1 and the neck 4.

  With this configuration, the vibration between the structure and the ground becomes the same as the vibration of the bolt fastening portion 2 of the upper and lower flanges 1, and a vertical or horizontal force corresponding to the vibration is generated on the flange 1. .

  Since the vertical force acts on the membrane 3 of the flange 1, a spring force determined by the thickness of the membrane 3 and the radius of the membrane 3 is generated. Further, since the bending force acts on the neck 4 by the force in the horizontal direction, a spring force determined by the cross-sectional secondary moment of the neck 4 and the length of the neck 4 is generated. Vibration transmitted from the ground to the structure or from the structure to the ground can be cut off at a resonance frequency or higher determined by both the springs and the weight of the structure.

  When the film 3 formed by punching the flange 1 is formed on one of the upper and lower flanges 1, the spring constant of the film 3 on the formed side becomes the spring constant in the vertical direction. When the upper and lower films 3 are formed, if the spring constant of the upper film 3 is k1 and the spring constant of the lower film 3 is k2, 2 is expressed as (k1 × k2) / (k1 + k2). A spring constant is obtained by connecting two springs in series.

  When the radius of the membrane 3 is a, the radius of the neck 3 is b, the longitudinal elastic modulus is E, the thickness of the membrane is h, and the constant of material mechanics calculated by the ratio of a and b is α, this vibration isolator The spring constant kz in the vertical direction due to the film 3 can be expressed by the following equation.

  Further, when the sectional moment of inertia of the neck 4 is I and the length of the neck 4 is 1, the horizontal spring constant kxy by the neck 4 of this vibration isolator can be expressed by the following equation.

  As described above, the spring constants in the vertical direction and the horizontal direction can be easily designed by independent dimensional design.

  FIG. 2 is a diagram illustrating an example where a structure is supported by using the vibration isolator according to the first embodiment of the present invention. One flange 1 of the vibration isolator 6 is coupled to the structure 5 via the bolt fastening portion 2, and the other flange 1 of the vibration isolator 6 is coupled to the ground via the bolt fastening portion 2. When the weight of the structure 5 is M, resonance of one degree of freedom occurs due to the spring constant K of the vibration isolator 6. The resonance frequency f0 can be expressed by the following equation.

  FIG. 3 is a diagram illustrating a vibration acceleration response of the structure 5 when the vibration isolating apparatus 6 according to the first embodiment of the present invention is used to prevent vibration. In FIG. 3, the thick line indicates the acceleration of the ground 7, and the thin line indicates the acceleration response of the structure 5. It can be seen that the resonance frequency f0 is 110 Hz, and the acceleration response of the structure 5 decreases at a frequency higher than that, and vibration isolation is possible at 200 Hz or higher.

  As described above, according to the vibration isolator in the present embodiment, the vibration isolator is constituted by the two flanges 1 and the beam-like neck 4 that connects the central portions of the two flanges 1, and at least one of the flanges 1 is formed. Since the film 3 is formed by punching the center portion, the film 3 can be made of a single metal material, and a vibration isolator can be manufactured at low cost.

  In addition, since the vibration of the vertical direction is absorbed by the spring action of the membrane 3 of the flange 1 and the vibration of the horizontal direction is absorbed by the spring action of the neck 4, the spring constant can be easily designed independently in the vertical direction and the horizontal direction. It became possible to do.

  In addition, it is possible to form a vibration isolator regardless of the size of the installation space.

(Second Embodiment)
FIG. 4 is a cross-sectional view of a vibration isolator according to the second embodiment of the present invention. This vibration isolator is obtained by adding R (8) to the base of the neck 4 in addition to the configuration of the vibration isolator described in the first embodiment. With this R, the magnitude of the spring constant kz can be changed, and the magnitude of the stress at the base of the neck 4 can be adjusted.

(Third embodiment)
FIG. 5 is a cross-sectional view of a vibration isolator according to the third embodiment of the present invention. In this vibration isolator, when the film 3 is formed around the upper and lower flanges 1, the film 3 is provided with a curve 9. This curve 9 can reduce the stress generated in the film 3 when a force is applied in the vertical direction, and it is possible to design a spring having high strength while having the same characteristics as the vibration isolator in the first embodiment. It becomes.

  FIG. 9 is a diagram showing a stress calculation result when a force in the vertical direction is applied to the vibration isolator according to the first embodiment of the present invention. As shown in FIG. 9B, stress is concentrated at the base portion of the neck 4, and the probability of breakage at this portion is very high. FIG. 9A shows a stress calculation model of the vibration isolator according to the first embodiment.

  FIG. 10 is a diagram illustrating a stress calculation result when a force in the vertical direction is applied to the vibration isolator according to the third embodiment of the present invention. As shown in FIG. 10 (b), the stress concentrated on the base of the neck 4 in the first embodiment is also seen in the portion of the curve 9 attached to the film 3 in the third embodiment. Thus, it can be seen that the stress is distributed as compared with the first embodiment, and the probability of fracture is lower than that of the first embodiment. FIG. 10A shows a stress calculation model of the vibration isolator according to the third embodiment.

(Fourth embodiment)
FIG. 6 is a sectional view of a vibration isolator according to the fourth embodiment of the present invention. In addition to the structure of the vibration isolator described in the third embodiment, this vibration isolator is also a part of the neck 4 when the upper and lower flanges 1 are formed to form the film 3. By the neck 10 of the neck 4, the stress generated between the neck 4 and the film 3 can be reduced.

  FIG. 11 is a diagram illustrating a stress calculation result when a vertical force is applied to the vibration isolator according to the fourth embodiment of the present invention. As shown in FIG. 11 (b), the stress concentrated on the base of the neck 4 in the first embodiment is also seen in the portion of the curve 9 attached to the film 3 in the fourth embodiment. Further, it can be seen that the level of stress generated in the film 3 is smaller than that in the third embodiment. Therefore, the probability of breakage is lower than that in the third embodiment. FIG. 11A shows a stress calculation model of the vibration isolator according to the fourth embodiment.

(Fifth embodiment)
FIG. 7 is a cross-sectional view of a vibration isolator according to the fifth embodiment of the present invention. In this vibration isolator, a plurality of springs described in the first to fourth embodiments are coupled in series. With such a configuration, even when one spring is stiff, a soft spring can be formed by combining a plurality of springs. Since each spring is stiff, the vibration isolator in the present embodiment has a configuration that is advantageous in terms of strength.

(Sixth embodiment)
The material of the vibration isolator described in the first to fifth embodiments may be anything. For example, when a vibration-damping material such as a damping alloy such as M2052 is used for the vibration isolator, the increase in amplitude at the resonance frequency can be reduced.

  FIG. 8 is a diagram illustrating an example of a method for supporting a structure when a material having vibration damping properties cannot be used for the vibration isolator. As shown in FIG. 8, for example, a damping material 11 such as non-brene is disposed between the structure 5 and the ground 7 in parallel with the vibration isolator 6. With this configuration, even when the vibration isolator is configured using a material having no vibration damping property, it is possible to reduce the increase in amplitude at the resonance frequency.

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

It is sectional drawing of the vibration isolator in the 1st Embodiment of this invention. It is a figure which shows an example of the place which supported the structure using the vibration isolator in the 1st Embodiment of this invention. It is a figure which shows the vibration acceleration response of the structure 5 at the time of anti-vibration using the anti-vibration apparatus 6 in the 1st Embodiment of this invention. It is sectional drawing of the vibration isolator in the 2nd Embodiment of this invention. It is sectional drawing of the vibration isolator in the 3rd Embodiment of this invention. It is sectional drawing of the vibration isolator in the 4th Embodiment of this invention. It is sectional drawing of the vibration isolator in the 5th Embodiment of this invention. It is a figure which shows an example of the method of supporting a structure, when the material which has damping property cannot be used for a vibration isolator. It is a figure which shows the stress calculation result at the time of applying the force of a perpendicular direction to the vibration isolator in the 1st Embodiment of this invention. It is a figure which shows the stress calculation result at the time of applying the force of the perpendicular direction to the vibration isolator in the 3rd Embodiment of this invention. It is a figure which shows the stress calculation result at the time of applying the force of a perpendicular direction to the vibration isolator in the 4th Embodiment of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Flange, 2 bolt fastening part, 3 film | membrane, 4 neck, 5 structure, 6 Vibration isolator, 7 Ground, 8 R, 9 Curve of film | membrane, 10 Neck turn, 11 Damping material.

Claims (7)

An anti-vibration device for preventing vibration of a structure,
Two flange portions fastened to each of the structure and an installation place of the structure;
A beam-like neck connecting the two flange portions,
A vibration isolator in which at least one of the two flange portions is formed by punching.   The anti-vibration device according to claim 1, wherein the beam-shaped neck has a shape with an R at the base.   The vibration isolator according to claim 1, wherein the film has a curved shape.   The anti-vibration device according to claim 1, wherein the beam-shaped neck has a same surface as a surface on which the film of the flange portion is formed.   The anti-vibration device according to claim 1, wherein the anti-vibration device has a structure in which a plurality of spring structures including the two flange portions and the beam-shaped neck are connected in series.   The anti-vibration device according to any one of claims 1 to 5, wherein the anti-vibration device is made of a vibration-damping material.   The vibration isolator according to any one of claims 1 to 5, further comprising an attenuation member provided between the structure and the installation location.

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