Vibration control devices for building structures

Abstract

To provide an improved vibration control apparatus for a building structure that exhibits an effective damping effect with a small number of installation bases.SOLUTION: A vibration control apparatus 10 in which four corners of a main mass 16 having a rectangular shape in a top view are supported by rubber mounts 14 is configured such that an additional mass 18 mounted below the main mass 16 in a mass member 12 is provided between the rubber mounts 14, 14 in a long side direction of the main mass 16; centers of gravity g1, g2 of the main mass 16 and the additional mass 18 are positioned on a vertical elastic main axis Z of a support spring system by the rubber mounts 14, 14, 14, 14; a length D1 between the rubber mounts 14, 14 in the short side direction of the main mass 16 is 0.15 to 0.45 time as long as a length D2 between the rubber mounts 14, 14 in the long side direction; a vertical spring constant of the rubber mount 14 is 3-40 times as large as the horizontal spring constant; and a gravity center position G of the mass member 12 is set between an upper limit position U of a horizontal elastic main shaft of the support spring system and a lower limit position E of the horizontal elastic main shaft of the rubber mount 14 alone.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a vibration damping device for architectural structures, which is installed in architectural structures such as hospitals and hotels to suppress vibrations caused by traffic vibrations, wind, etc. [Background technology]

[0002] In architectural structures such as houses, vibrations may occur due to the action of external forces such as traffic vibrations and wind as exciting forces. Therefore, the present applicant has proposed a vibration control device for architectural structures in Japanese Patent Laid-Open No. 2008-214886 (Patent Document 1) and other publications as one means for reducing such vibrations. The vibration control device in Patent Document 1 has a structure in which a mass member is elastically supported by rubber mounts, and when an external force such as traffic vibrations acts as an exciting force, the mass member vibrates in a substantially horizontal direction (translational movement), thereby reducing the exciting force. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2008-214886 Summary of the Invention [Problem to be solved by the invention]

[0004] In order to effectively achieve vibration control, vibration control devices for architectural structures require mass members with a mass that corresponds to the mass of the architectural structure. Therefore, in small architectural structures such as ordinary houses, the mass of the mass members required to sufficiently reduce the exciting force is relatively small, and the number of vibration control devices installed can be reduced. However, in large architectural structures such as apartment buildings, hospitals, and hotels, the mass of the mass members required to sufficiently reduce the exciting force is large, and therefore it has been necessary to install a large number of vibration control devices.

[0005] However, if a large number of vibration control devices are to be installed, the installation work takes time, which leads to problems such as the work becoming more complicated and the construction period becoming longer.

[0006] An object of the present invention is to provide a vibration damping device for building structures of an improved structure that can obtain an effective vibration damping effect with a relatively small number of units installed. [Means for solving the problem]

[0007] The inventor attempted to increase the mass of mass members to reduce the number of vibration control devices installed in architectural structures. However, increasing the mass of conventional mass members inevitably leads to larger mass members, making them difficult to install in narrow spaces such as ceilings. Furthermore, increasing the mass mass by increasing the specific gravity of the mass member results in increased costs due to changes in material. Therefore, the inventor considered using a conventional mass member as the main mass and adding an additional mass to the main mass to increase the overall mass of the mass member. However, it became clear that with a mass member with an additional mass, the displacement of the mass member is less likely to be a translational motion, i.e., a vibration in a substantially horizontal direction as in conventional mass members. Instead, rotational motion (oscillation), such as rolling, around a horizontal axis occurs, adversely affecting the vibration control effect. Thus, the inventor discovered that simply increasing the mass member's mass is difficult to achieve an efficient vibration control effect while satisfying requirements such as installation space. Based on this finding, the inventor developed the present invention.

[0008] The following describes preferred embodiments for understanding the present invention, but the embodiments described below are merely examples and may be appropriately combined with one another. Multiple components described in each embodiment may be recognized and employed independently to the greatest extent possible, and may also be appropriately combined with any of the components described in other embodiments. Accordingly, the present invention is not limited to the embodiments described below, and various other embodiments may be realized.

[0009] The first aspect is a vibration control device for an architectural structure, which comprises a main mass that is rectangular when viewed in the vertical direction, and four rubber mounts that are arranged below the four corners of the main mass and elastically connect the main mass to a base member, and an additional mass that is smaller in mass than the main mass is attached to the main mass by being superimposed below the main mass to form a mass member, and the additional mass is arranged between the rubber mounts in the long side direction of the main mass, and the centers of gravity of the main mass and the additional mass are both elastically connected to each other by a support spring system formed by the rubber mounts that extends in the vertical direction. The rubber mounts are positioned on the elastic main axis, the distance between the rubber mounts in the short side direction of the main mass is within a range of 0.15 to 0.45 times the distance between the rubber mounts in the long side direction of the main mass, the vertical spring constant of the rubber mount is within a range of 3 to 40 times the horizontal spring constant of the rubber mount, and the center of gravity of the mass member is set between the upper limit position of the elastic main axis extending horizontally in the support spring system formed by the rubber mount and the lower limit position of the elastic main axis extending horizontally in the rubber mount alone.

[0010] In a vibration control device for architectural structures constructed in accordance with this embodiment, the mass member is constructed by attaching an additional mass to a main mass, which improves vibration control performance and tuning freedom due to the increased mass, compared to when the mass member is constructed from the main mass alone.

[0011] By arranging the additional mass below the main mass and between the rubber mounts, it is possible to suppress the occurrence of rolling of the mass member due to the addition of the additional mass while suppressing the increase in size of the rubber mounts, compared to when the additional mass is added above the main mass.

[0012] The additional mass is placed below the main mass, making clever use of the space between the rubber mounts, and the additional mass can be provided without increasing not only the size of the mass member in plan view, but also the external size of the entire vibration damping device.

[0013] When adopting a main mass that is rectangular in plan view, in which rolling around the long axis of the main mass is likely to be a problem, the distance between the rubber mounts in the direction of the short side of the main mass is set to be within the range of 0.15 to 0.45 times the distance between the rubber mounts in the direction of the long side of the main mass, which is sufficiently large, so that rolling around the long axis of the mass extending in the direction of the long side of the main mass is also suppressed by the support position of the rubber mounts.

[0014] By making the vertical spring constant of the rubber mount sufficiently large relative to its horizontal spring constant, the rolling of the mass member around its horizontal axis is easily suppressed by the support spring stiffness of the rubber mount.Furthermore, by making the horizontal spring constant of the rubber mount small relative to its vertical spring constant, vibration damping by the horizontal translational movement of the mass member is effectively exerted.

[0015] By setting the vertical position of the center of gravity of the mass member between the upper limit position of the main elastic axis extending horizontally in the support spring system using the rubber mount and the lower limit position of the main elastic axis extending horizontally in the rubber mount alone, rolling of the mass member around the horizontal axis is reduced.

[0016] In a second aspect, in the vibration control device for an architectural structure described in the first aspect, the length of the side of the additional mass that is parallel to the long side of the main mass is equal to or greater than the length of the short side of the main mass.

[0017] According to a vibration control device for an architectural structure constructed in accordance with this aspect, the additional mass can be made larger in the direction of the long side of the main mass, thereby improving the vibration control effect of the additional mass.

[0018] Even if the additional mass is made larger in the long side direction of the main mass, the increase in inertia due to rolling around the long axis of the mass is suppressed, so the loss of vibration damping effect due to rolling can be reduced.

[0019] In a third aspect, in the vibration control device for architectural structures described in the first or second aspect, the rubber mount has a structure in which a plurality of rectangular plate members are stacked and spaced apart from each other in the vertical direction, and adjacent plate members in the vertical direction are connected to each other by connecting rubber, and opposite sides of the plate members are each provided with an inclined portion that slopes upward toward the outer periphery, and the connecting rubber is fixed to the inclined portion.

[0020] With a vibration control device for architectural structures constructed in accordance with this embodiment, the upper limit position of the horizontally extending main elastic axis changes depending on the circumferential orientation of the rubber mount, making it easier to set the center of gravity of the mass member below the upper limit position of the main elastic axis.

[0021] The fourth aspect is a vibration control device for architectural structures described in any one of the first to third aspects, wherein the length of the short side of the main mass is the same as the length of the side of the additional mass that is parallel to the short side of the main mass.

[0022] According to a vibration control device for architectural structures constructed in accordance with this aspect, the size of the additional mass in the short side direction can be maximized while preventing the additional mass from protruding outward from the main mass, thereby increasing the mass of the additional mass.

[0023] A fifth aspect is the vibration damping device for an architectural structure according to any one of the first to fourth aspects, wherein the main mass and the additional mass are formed from the same material.

[0024] A vibration control device for an architectural structure constructed according to this aspect prevents the additional mass from becoming excessively heavy relative to the main mass, making it easier to prevent abnormal vibration conditions caused by the provision of the additional mass. [Effects of the Invention]

[0025] According to the present invention, an effective vibration damping effect can be obtained with a relatively small number of vibration damping devices installed. [Brief explanation of the drawings]

[0026] [Figure 1] FIG. 1 is a front view showing a vibration damping device according to a first embodiment of the present invention; [Figure 2] Right side view of the vibration damping device shown in Figure 1 [Figure 3] A bottom view of the vibration damping device shown in Figure 1 [Figure 4] FIG. 2 is a diagram illustrating the setting of the center of gravity of the mass in the vibration damping device shown in FIG. 1. DETAILED DESCRIPTION OF THE INVENTION

[0027] Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

[0028] 1 to 3 show a vibration damping device 10 for architectural structures (hereinafter referred to as vibration damping device) constructed in accordance with the present invention. Vibration damping device 10 has a structure in which rubber mounts 14 are attached to mass members 12. In the following explanation, as a general rule, the up-down direction refers to the vertical height direction in FIG. 1, the front-rear direction refers to the up-down direction in FIG. 3 which is the direction of the short sides of main mass 16 (described later), and the left-right direction refers to the left-right direction in FIG. 3 which is the direction of the long sides of main mass 16.

[0029] The mass member 12 is configured to include a main mass 16. The main mass 16 is formed of a material with a high specific gravity, such as an iron-based metal. The main mass 16 is a rectangular parallelepiped, and is rectangular in shape with a short side direction (front-to-back direction) and a long side direction (left-to-right direction) when viewed in the vertical direction. In other words, the length dimension A1 of the short side of the main mass 16 is smaller than the length dimension A2 of the long side when viewed in the vertical direction.

[0030] An additional mass 18 is attached to the main mass 16. The additional mass 18 is a rectangular parallelepiped or cube and is attached by being superimposed on the underside of the main mass 16 to form the mass member 12. The means for fastening the additional mass 18 to the main mass 16 is not particularly limited, but it is preferably detachable from the main mass 16. For example, as in this embodiment, the additional mass 18 is bolted to the main mass 16. The additional mass 18 has a smaller mass than the main mass 16. The volume of the additional mass 18 is preferably smaller than the volume of the main mass 16. The additional mass 18 is preferably formed from the same material as the main mass 16, which allows the additional mass 18 to be lighter and smaller than the main mass 16. However, the main mass 16 and the additional mass 18 may be formed from different materials. For example, by forming the main mass 16 from a material with a higher specific gravity than the additional mass 18, it is possible to reduce the size of the main mass 16 while maintaining the mass of the main mass 16.

[0031] The length dimension B1 of the additional cell 18 in the direction of the short side of the main cell 16 is less than or equal to the length dimension A1 of the short side of the main cell 16 (B1≦A1), and preferably is approximately the same as the length dimension A1 of the short side of the main cell 16 (B1=A1). Also, the length dimension B2 of the additional cell 18 in the direction of the long side of the main cell 16 is greater than or equal to the length dimension A1 of the short side of the main cell 16 (B2≧A1).

[0032] The mass member 12 has a square portion of the main mass 16 elastically supported by four rubber mounts 14. While the rubber mounts 14 are not particularly limited in structure, in this embodiment, as shown in FIG. 1 , the rubber mounts 14 have a laminated structure in which multiple plate members 20 are stacked at predetermined intervals and elastically connected to each other by rubber elastic bodies 22. The plate members 20 are rectangular when viewed from the top-bottom, with rubber elastic bodies 22 fixed to both ends of the long sides. The rubber elastic bodies 22 are rectangular block-shaped, elongated along the short sides of the plate members 20, and are disposed between adjacent plate members 20 in the top-bottom direction. The rubber elastic bodies 22 are interconnected through through-holes (not shown) formed in the plate members 20 and also through the rubber coating covering the surface of the plate members 20, forming a single unit. For ease of viewing, the plate members covered with the rubber coating are designated by the reference numeral 20 in FIGS. 2 and 3 .

[0033] The opposite side portions (both end portions) in the long side direction of the plate member 20 to which the rubber elastic body 22 is fixed are inclined portions 23 that slope upward outward in the long side direction. This allows the rubber elastic body 22 to bear the shared support load of the mass member 12 as a compressive force, and also increases the difference in spring characteristics between the long side direction and the short side direction of the plate member 20. By adjusting the orientation of the rubber mounts 14, the resonance frequency of the mass-spring resonance system, which will be described later, can be adjusted with a greater degree of freedom.

[0034] As shown in Figure 3, the four rubber mounts 14, 14, 14, 14 are arranged at the four corners of the main mass 16, and the distance D1 between the rubber mounts 14, 14 in the direction of the short sides of the main mass 16 is within the range of 0.15 to 0.45 times the distance D2 between the rubber mounts 14, 14 in the direction of the long sides of the main mass 16. Note that the distances D1 and D2 between the rubber mounts 14, 14 referred to here refer to the distance between the attachment positions of each rubber mount 14 to the main mass 16.

[0035] The spring constant of the rubber mount 14 in the vertical direction is set to be larger than the spring constant in the horizontal direction, and the spring constant in the vertical direction is set within a range of 3 to 40 times the spring constant in the horizontal direction.

[0036] The additional masses 18 are positioned inward in the long side direction of the main mass 16 and spaced apart from each rubber mount 14, and are disposed between the rubber mounts 14, 14 on both sides in the long side direction. The length dimension B2 of the additional masses 18 in the long side direction is desirably set within a range of 0.5 to 0.9 times the distance D3 between the innermost ends of the rubber mounts 14, 14 in the long side direction, which makes it easier to ensure a large volume for the additional masses 18 while preventing interference between the additional masses 18 and the rubber mounts 14.

[0037] The vertical thickness dimension h of the additional mass 18 is smaller than the vertical height dimension H of the rubber mount 14 including the bracket 28 (described later). In this embodiment, the vertical thickness dimension h of the additional mass 18 is larger than the vertical thickness dimension of the main mass 16, but the main mass 16 may be thicker in the vertical direction, or the main mass 16 and the additional mass 18 may be the same thickness in the vertical direction.

[0038] The rubber mount 14 is interposed between the mass member 12 and the base member 30 by having the first attachment member 24 located at the upper end fixed to the mass member 12 via the bracket 28 and the second attachment member 26 located at the lower end fixed to the base member 30. In this way, the mass member 12 and the base member 30 are elastically connected to each other by the four rubber mounts 14, 14, 14, 14, and the vibration damping device 10, which constitutes a secondary vibration system (mass-spring resonance system), is mounted on the base member 30. The base member 30 may be part of the architectural structure, such as a ceiling beam, or it may be a separate member from the architectural structure that is attached to the architectural structure.

[0039] The orientation of each rubber mount 14 around the vertical central axis is set appropriately taking into consideration the position of the main elastic axis, the spring ratios in the front-rear and left-right directions, etc. In this embodiment, as shown in Fig. 3, the rubber mount 14 is arranged so that the long side direction of the plate member 20 in the rubber mount 14 is inclined with respect to both the front-rear and left-right directions, but for ease of viewing, Figs. 1 and 2 show the orientation of the rubber mount 14 as viewed from the short side direction and the long side direction of the plate member 20.

[0040] Because both ends of the plate member 20 of the rubber mount 14 in the long side direction are inclined portions 23, the vertical position of the main elastic axis extending horizontally of the support spring system made up of the four rubber mounts 14, 14, 14, 14 can be changed and set by adjusting the orientation of the rubber mounts 14. Specifically, for example, the vertical position of one main elastic axis extending horizontally changes so that the closer the long side of the rubber mount 14 approaches the horizontal direction, the higher it is located, and the closer the short side of the rubber mount 14 approaches the horizontal direction, the lower it is located. Therefore, by appropriately adjusting the orientation of each rubber mount 14, the vertical position of the main elastic axis extending horizontally can be adjusted.

[0041] In the secondary vibration system in which the mass member 12 is supported by rubber mounts 14, 14, 14, 14, the center of gravity g1 of the main mass 16 and the center of gravity g2 of the additional mass 18 that make up the mass member 12 are both located on the principal elastic axis Z that extends in the vertical direction of the support spring system made up of the rubber mounts 14, 14, 14, 14, as shown in Figures 1 and 2. Therefore, the center of gravity G of the mass member 12 is also located on the principal elastic axis Z.

[0042] When external forces acting on an architectural structure, such as traffic vibrations or wind pressure, are input as vibrations to the vibration damping device 10, the mass member 12 displaces relative to the base member 30 and ultimately the architectural structure, thereby reducing the vibration energy and providing a vibration suppression effect (vibration damping effect). The vibration damping effect is efficiently provided by translation, which is the horizontal displacement of the mass member 12. In the vibration damping device 10, the resonant frequency of the mass-spring system formed by the mass member 12 and rubber mounts 14, 14, 14, 14 is tuned to the frequency of the vibration in question, so that when the vibration is input, translation of the mass member 12 actively occurs in a resonant state, efficiently reducing the vibration energy.

[0043] The mass member 12 of the vibration damping device 10 is configured to include not only the main mass 16 but also an additional mass 18 attached to the main mass 16. The additional mass 18 is attached to the underside of the main mass 16 and is positioned by effectively utilizing the space between the rubber mounts 14, 14 along the long side of the main mass 16. This allows the additional mass 18 to increase the mass of the mass member 12 without increasing the size of the vibration damping device 10. This allows for a greater vibration damping effect to be achieved in vibration damping devices 10 for architectural structures where installation space is limited. Therefore, particularly in relatively large architectural structures such as hotels and apartment buildings, the desired vibration damping performance can be achieved with a smaller number of units installed, simplifying installation work and shortening the installation period.

[0044] 4, in the vibration damping device 10, the center of gravity G of the mass member 12 is set between the upper limit U of the main elastic axis extending horizontally in the support spring system formed by the four rubber mounts 14 and the lower limit E of the main elastic axis extending horizontally in each rubber mount 14. This makes it possible to effectively obtain vibration damping action through the horizontal translational movement of the mass member 12 while suppressing rolling of the mass member 12.

[0045] That is, when the vibration damping device 10 is mounted on the base member 30 as shown in Figure 4, the lateral vibration mode of the main mass 16 is considered to have a bottom-center rolling resonance mode a and a top-center rolling resonance mode b. Here, the rolling amplitude of the mass member 12 can be reduced by raising the vertical position of the lateral principal elastic axis of the support spring system and lowering the vertical position of the center of gravity G of the mass member 12. Preferably, the optimal translational mode is achieved by aligning the vertical positions of the lateral principal elastic axis of the support spring system and the center of gravity G.

[0046] However, because the rubber mounts 14 are anisotropic due to the inclined portions 23 of the plate member 20, the vertical position of the principal elastic axis of the support spring system changes depending on the orientation of the rubber mounts 14. Therefore, the center of gravity G of the mass member 12 is set below the principal elastic axis U at the uppermost position, with the highest principal elastic axis U in the support spring system as the reference point. This brings the center of gravity G of the mass member 12 closer to the principal elastic axis extending in the horizontal direction of the support spring system, ensuring the resonance magnification of the translational mode in the mass-spring system, and suppressing excessive deflection of the mass member 12 caused by bottom-center rolling a and the rolling center being far away from the center of gravity G of the mass member 12, while avoiding the need to increase the upper and lower springs by increasing the size of each rubber mount 14.

[0047] If the vertical position of the mass center of gravity G is set too low, the loss of amplitude or vibration control effect due to top-center rolling b will be significant. However, in a vibration model in which the main mass 16 is placed on a support spring system and the mass member 12 is supported from below by rubber mounts 14, the distance between the rolling center and the center of gravity G of the mass member 12 in top-center rolling b is smaller than the distance between the rolling center and the center of gravity G in bottom-center rolling a. Furthermore, in bottom-center rolling a, the upper end of the mass member 12, where the amplitude of the mass member 12 is greatest, is the free end, whereas in top-center rolling b, the lower end of the mass member 12, where the amplitude of the mass member 12 is greatest, is supported by the rubber mount 14, making amplitude control by the rubber mount 14 more effective.

[0048] Therefore, the lower limit position of the center of gravity G of the mass member 12 can be set lower than the height position L of the elastic main axis at the lowest position in the support spring system, thereby increasing the tuning range and facilitating tuning.

[0049] However, if the center of gravity G of the mass member 12 is located too far downward, the input force to each rubber mount 14 will be dominated by shear rather than compression or tension on the rubber elastic body 22. This could result in an increase in the amplitude of the mass member 12 or the need to increase the spring of the rubber mount 14. From this perspective, the set lower limit position of the center of gravity G of the mass member 12 can be set to the lower limit position E of the center of elasticity of the rubber mount 14 alone (the intersection of the vertical principal elastic axis and the horizontal principal elastic axis). Note that since the lower limit position E of the center of elasticity of the rubber mount 14 alone coincides with the lower limit position of the horizontal principal elastic axis of the rubber mount 14 alone, it can also be said that the set lower limit position of the center of gravity G of the mass member 12 is the lower limit position E of the horizontal principal elastic axis of the rubber mount 14 alone.

[0050] As can be seen from the technical reasons described above, in a vibration damping device 10 in which the center of gravity G of the mass member 12 is positioned between the upper limit U of the horizontally extending principal elastic axis of the support spring system and the lower limit E of the horizontally extending principal elastic axis of the rubber mount 14 alone, vibrations of the mass member 12 other than the translational mode in the vibration damping device 10 can be effectively suppressed, thereby reducing loss of vibration damping effect due to mass vibrations of such other modes. As a result, not only is it easier to adjust the mass of the mass member 12 using the additional mass 18, and thus easier to adjust the resonant frequency (vibration damping frequency), but it is also possible to further improve the vibration damping effect in the tuned frequency range.

[0051] Furthermore, the distance D1 between the rubber mounts 14, 14 in the short side direction of the main mass 16 is set within a range of 0.15 to 0.45 times the distance D2 between the rubber mounts 14, 14 in the long side direction of the main mass 16. As a result, the support position of the main mass 16 by the rubber mounts 14 is set at a position sufficiently far away from the rolling axis extending in the short side direction of the main mass 16 and the rolling axis extending in the long side direction of the main mass 16, making it possible to suppress rolling of the mass member 12.

[0052] Furthermore, the vertical spring constant of the rubber mount 14 is set to be greater than the horizontal spring constant, within a range of 3 to 40 times the horizontal spring constant. As a result, the rolling of the mass member 12 is suppressed by the vertical spring of the rubber mount 14, which is set to be relatively stiff, and the resonance magnification of the horizontal translation mode of the mass member 12 is ensured to be large by the horizontal spring of the rubber mount 14, which is set to be relatively soft.

[0053] While the above embodiment has been described with reference to Fig. 4 regarding the suppression of rolling about the major axis of the mass member 12 extending in the direction of the major sides of the main mass 16, the present invention can also be applied to the suppression of rolling about the minor axis of the mass member 12 extending in the direction of the minor sides of the main mass 16. That is, when viewed in the minor axis direction of the mass member 12 as shown in Fig. 1, rolling about the minor axis of the mass member 12 can be suppressed by setting the center of gravity G of the mass member 12 between the upper limit position (U) of the principal elastic axis of the support spring system and the lower limit position E of the principal elastic axis of the rubber mount 14 alone. Therefore, for example, when the vibration damping device 10 is tuned to damp vibrations in the major axis direction of the mass member 12, the increase in rolling displacement due to the addition of the additional mass 18 is suppressed, and the vibration of the mass member 12 is more likely to occur as translational motion, thereby enabling the desired vibration damping effect to be obtained stably and efficiently. Even in this configuration, rolling around the mass major axis can be suppressed by setting the distance between the rubber mounts in the mass minor axis direction and the spring ratio of the rubber mounts in the vertical and horizontal directions within specific ranges, thereby avoiding deterioration of vibration due to excessive rolling around the mass major axis.

[0054] Furthermore, the vibration damping device 10 according to the present invention is not limited to the input direction of vibration to be damped, and can be tuned to exert a vibration damping effect on vibrations input in any horizontal direction. Furthermore, the input direction of vibration to be damped, as tuned by the vibration damping device 10, does not necessarily have to coincide with the vibration direction in which the rolling suppression effect is exerted by setting the center of gravity position G of the mass member 12 in the vertical direction. For example, while the major vibration to be damped is directed in the major axis direction of the mass member 12, the direction in which the rolling suppression effect is exerted by setting the center of gravity position of the mass member 12 in the vertical direction can be set to the minor axis direction of the mass member 12 (as in the above embodiment), thereby suppressing deterioration of the vibration state due to excessive rolling around the major axis.Furthermore, by aligning the direction in which the rolling suppression effect is exerted by setting the center of gravity position G of the mass member 12 in the vertical direction with the major axis direction of the mass member 12, which is the major vibration input direction, it is possible to suppress rolling when the mass member 12 vibrates in the major axis direction, which is the damping direction, and thereby improve vibration damping efficiency.Furthermore, when performing two-way tuning so that the vibration damping effect is exerted in both the major axis direction and the minor axis direction of the mass member 12, the direction in which the rolling suppression effect is exerted by setting the center of gravity position G of the mass member 12 in the vertical direction can be set to at least one of the major axis direction and the minor axis direction of the mass member 12.

[0055] Although the embodiments of the present invention have been described in detail above, the present invention is not limited to those specific descriptions. For example, the rubber mount is not limited to a layered structure of multiple plate members 20 and rubber elastic bodies 22 as in the above-described embodiments, but may instead have a single-layer structure in which upper and lower mounting members 24, 26 are elastically connected by a single rubber elastic body. Furthermore, the plate member 20 does not have to have the inclined portion 23 and can be, for example, flat. Furthermore, the rubber mount 14 may have an overall cylindrical shape, for example, and is not necessarily limited to the overall rectangular prism shape of the above-described embodiments.

[0056] In the rubber mount 14 of the above-described embodiment, both ends of the long side of the plate member 20 are inclined portions 23, and thus the vertical position of the horizontally extending main elastic shaft of the support spring system can be changed by adjusting the circumferential orientation of the rubber mount 14. However, the present invention is not necessarily limited to a structure in which the vertical position of the horizontally extending main elastic shaft of the support spring system can be adjusted. Therefore, the horizontally extending main elastic shaft of the support spring system may have the same upper and lower limit positions. Similarly, the horizontally extending main elastic shaft of the rubber mount 14 alone may have the same upper and lower limit positions. Furthermore, the vertical position of the horizontally extending main elastic shaft of the support spring system can be changed by, for example, changing the inclination angle or inclination direction of the vertically extending main elastic shaft of the rubber mount 14. [Explanation of symbols]

[0057] 10 Vibration damping device (first embodiment) 12 Mass members 14 Rubber mount 16 Main Square 18 additional squares 20 Plate member 22 Rubber elastic body 23 Slope 24 First mounting member 26 Second mounting member 28 Bracket 30 Base member A1 Length of the short side of the main compartment A2 Length of the main square B1 Length dimension of additional cells in the direction of the short side of the main cell B2 Length dimension of additional cells along the long side of the main cell D1 Distance between rubber mounts along the short side of the main mass D2 Distance between rubber mounts along the long side of the main mass D3 Distance between the innermost ends of the rubber mounts along the long side of the main mass h Upper and lower thickness dimensions of additional mass H Rubber mount vertical height dimension g1 Center of gravity of main mass g2 Center of gravity of additional mass G Center of gravity of mass member Z: The principal elastic axis of the support spring system extending in the vertical direction U Upper limit position of the horizontally extending elastic axis of the support spring system L: Lower limit of the horizontal axis of the support spring system E Lower limit position of the main elastic axis of the rubber mount in the horizontal direction a. Ultimate Rolling b. Upper center rolling

Claims

1. A vibration control device for an architectural structure, comprising: a main mass having a rectangular shape when viewed in the vertical direction; and four rubber mounts disposed below the four corners of the main mass and elastically connecting the main mass to a base member, a mass member is formed by attaching an additional mass having a smaller mass than the main mass to the main mass and stacked below the main mass, the additional mass being disposed between the rubber mounts in the direction of the long sides of the main mass, and the centers of gravity of the main mass and the additional mass being both located on the main elastic axis extending in the vertical direction in the support spring system formed by the rubber mounts; the distance between the rubber mounts in the short side direction of the main mass is within a range of 0.15 to 0.45 times the distance between the rubber mounts in the long side direction of the main mass, The spring constant of the rubber mount in the vertical direction is set within a range of 3 to 40 times the spring constant of the rubber mount in the horizontal direction, A vibration control device for architectural structures in which the center of gravity of the mass member is set between the upper limit position of the main elastic axis extending horizontally in the support spring system using the rubber mount and the lower limit position of the main elastic axis extending horizontally in the rubber mount alone.

2. 2. The vibration damping device for an architectural structure according to claim 1, wherein the length of the side of the additional mass that is parallel to the long side of the main mass is equal to or greater than the length of the short side of the main mass.

3. The rubber mount has a structure in which a plurality of rectangular plate members are stacked and spaced apart from each other in the vertical direction, and the plate members adjacent to each other in the vertical direction are connected to each other by connecting rubber, 3. A vibration damping device for architectural structures according to claim 1, wherein opposite sides of said plate member are provided with inclined portions inclined upward toward the outer periphery, and said connecting rubber is fixed to said inclined portions.

4. 3. The vibration damping device for an architectural structure according to claim 1, wherein the length of a short side of said main mass is the same as the length of a side of said additional mass that is parallel to the short side of said main mass.

5. 3. The vibration damping device for an architectural structure according to claim 1, wherein the main mass and the additional mass are formed from the same material.

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