JP5062566B2 - Vibration reduction mechanism - Google Patents

Description

  The present invention relates to a vibration reduction mechanism suitable for application to a structure such as a building, and more particularly to a vibration reduction mechanism having a structure that obtains a vibration reduction effect by utilizing a rotational inertial mass effect caused by rocking of a weight.

In recent years, a method using a rotational inertial mass (inertia connection element) has attracted attention as a measure capable of exhibiting a large mass effect with a small mass, and various response reduction mechanisms using the method have been proposed. For example, in Patent Document 1, in a vertical seismic isolation device that increases the vertical vibration of a structure subject to seismic isolation, a mass that increases the inertial mass involved in the vertical vibration by interlocking with the vertical movement of the structure subject to seismic isolation. A vertical seismic isolation device with an additional mechanism has been proposed.
As a specific device for generating an inertial mass in this type of mechanism, a device using a ball screw and a flywheel (rotating weight) is generally used, and the vertical seismic isolation device disclosed in Patent Document 1 also has a predetermined mass. An inertial mass adding mechanism configured to rotate a disk having a ball screw type motion conversion mechanism is employed.
JP 2004-44748 A

Although the mechanism using the ball screw and the flywheel as described above can be made compact, it cannot cope with a large burden force in consideration of the burden of the ball screw.
That is, in such a mechanism, since all of the burden force acts on the ball screw, it is necessary to use it within the range where the ball screw does not buckle, etc., and the inertial mass obtained by that is about 1,000 tons in practice. However, it is difficult to increase the yield strength beyond that, and therefore it is difficult to apply to large-scale structures.
Therefore, there has been a demand for the development of an effective and appropriate mechanism capable of obtaining a huge rotational inertial mass effect without depending on the mechanical mechanism as described above.

  In view of the above circumstances, an object of the present invention is to provide a vibration reduction mechanism that can achieve high performance, high yield strength, and a large response reduction effect without using a mechanical mechanism, and can be applied to a large-scale structure. .

The present invention provides a weight body that is rocked between a lower structure and an upper structure, which are relatively vibrated in the horizontal direction, by being applied with a horizontal relative vibration generated between the lower structure and the upper structure. Is a vibration reduction mechanism configured to reduce the relative vibration by a rotational inertial mass effect due to locking of the weight body, and supports a lower portion of the weight body rotatably with respect to the lower structure, The lower center of rotation, which is the center of rotation, is set at the center of gravity of the weight body or a position near the center of gravity, and the upper part of the weight body is supported rotatably with respect to the upper structure, and the upper rotation, which is the center of rotation. The center is set at a position deviating upward from the lower rotation center.
In the present invention, the “lower part” of the weight body is substantially the “bottom part”, but the “upper part” of the weight body includes both the “top part” and the “side part”.

  In the present invention, a lower sliding surface and an upper sliding surface are formed at the lower and upper portions of the weight body, respectively, and the lower sliding surface and the upper sliding surface are slidable on the lower structure and the upper structure, respectively. A lower seat surface and an upper seat surface to be supported on each other, the lower slide surface and the lower seat surface are both formed into a curved surface centered on the lower rotation center, and the upper slide surface and the upper seat surface are both It is good to form in the curved surface centering on the said upper rotation center.

  In this case, the weight body is a wall body that forms a wall surface along the vibration direction of the relative vibration generated between the lower structure and the upper structure body and can be locked in the plane of the wall surface. The lower sliding surface formed in the lower portion of the lower seat and the lower seating surface supporting the lower sliding surface are formed as a convex arc surface and a concave arc surface centering on a horizontal axis passing through the lower rotation center and orthogonal to the wall surface. And forming the upper sliding surface formed on the upper portion of the wall body and the upper seating surface supporting the upper sliding surface through the upper rotation center and having a horizontal axis perpendicular to the wall surface as a center line. It may be formed as a surface and a concave arc surface.

  Alternatively, the weight body is a block body that can be locked in each horizontal direction, and the lower sliding surface formed at the lower portion of the block body and the lower seating surface that supports the lower sliding surface are centered on the lower rotation center. A convex spherical surface and a concave spherical surface, with the upper sliding surface formed on the block body and the upper seating surface supporting the upper sliding surface as the center point of the upper rotation center. It is also possible to form it as a spherical surface.

  Further, a sliding mechanism that rotatably supports the weight body may be interposed between the lower portion of the weight body and the lower structure body and between the upper portion of the weight body and the upper structure body. It is done.

  Further, the upper structure or the lower structure is supported while rotatably supporting the weight between the upper part of the weight and the upper structure or between the lower part of the weight and the lower structure. And an additional spring that operates between the jig and the upper structure or the lower structure in a horizontal relative vibration direction generated between the jig and the upper structure or the lower structure. It is also possible to intervene.

The vibration reduction mechanism of the present invention locks the weight body by following the interlayer deformation during the horizontal vibration of the structure, thereby making the weight function as a rotational inertia mass damper using the rotational inertial mass effect of the locking. A large mass of rotational inertial mass can be obtained by a small mass weight, and the effect of reducing the vibration at the cutoff frequency can be effectively exhibited by increasing the period of the structure, reducing the seismic motion input.
In particular, since the weight body can be formed of general construction materials such as reinforced concrete and steel, it can be manufactured and installed at a lower cost than conventional rotary inertia mass dampers with a mechanical screw mechanism using a ball screw and flywheel. However, since the stress treatment is easy, it can be applied to a large-scale structure without any trouble, and the weight body can be effectively used as a wall body or a storage object installed in the structure.
Moreover, the rotational inertial mass can be determined arbitrarily and widely only by setting the mass and dimensions of the weight, and the center-to-center distance between the upper and lower rotation centers. It is also possible to function as a TMD (tuned mass damper: dynamic vibration absorber) by setting the natural frequency by the inertia mass and the additional spring.

1 to 2 show a basic embodiment of the vibration reducing mechanism of the present invention. This is a structure in which a weight body 1 is installed in the form of a wall that can be locked between a column and a beam constituting a frame of a building, and the weight body 1 that is generated following an interlayer deformation of the frame during an earthquake. The effect of reducing the vibration is obtained by utilizing the rotational inertial mass effect due to the rocking.
In addition, since the following embodiments are basically vertically symmetric, the same reference numerals are given to the same constituent elements arranged symmetrically in the vertical direction, but the constituent elements related to the lower part are indicated by reference numerals as necessary. A subscript A is attached, and a component related to the upper part is attached with a subscript B to distinguish them from each other.
In the following description, the “lower part” of the weight body 1 is substantially the “bottom part”, but the “upper part” of the weight body 1 may include not only the “top part” but also the “side part” ( Details will be described later).

  The weight body 1 in the present embodiment is a reinforced concrete structure or steel frame structure or a composite structure wall appropriately combining them, and the lower part and the upper part thereof are interposed via jigs 2 (lower jig 2A and upper jig 2B), respectively. The upper and lower beams 3 (the lower beam 3A as the lower structure and the upper beam 3B as the upper structure) are supported so as to be rotatable, so that the in-plane surface of the wall formed by the weight 1 Are arranged so that they can be locked.

That is, as shown in FIGS. 1 to 2, a sliding surface 4 (lower sliding surface 4 </ b> A) having a convex arc surface is formed at the lower part of the weight body 1 and is fixed to the upper surface of the lower floor beam 3 </ b> A. The lower jig 2A is formed with a seat surface 5 (lower seat surface 5A) having a concave arc surface, and the weight 1 has the lower slide surface 4A slidably adhered to the lower seat surface 5A. In this state, it is supported by the lower floor beam 3A via the lower jig 2A, and the frictional resistance there is set to be sufficiently small, so that the weight 1 is smooth with respect to the lower jig 2A and the lower floor beam 3A. It is possible to rotate. The lower rotation center OA, which is the rotation center of the weight body 1 with respect to the lower jig 2A and the lower floor beam 3A, is set at the gravity center position of the weight body 1 or near the center of gravity, and the lower sliding surface 4A and the lower seat surface 5A. Each is formed as a circular arc surface (cylindrical surface) having a lower rotation radius R ₂ with a horizontal axis perpendicular to the weight body 1 passing through the lower rotation center OA as a center line.
Similarly, a sliding surface 4 (upper sliding surface 4B) having a convex arc surface is formed on the upper portion of the weight body 1 and a concave arc is formed on the upper jig 2B fixed to the lower surface of the upper floor beam 3B. The upper jig 2B is formed in a state in which a seat surface 5 (upper seat surface 5B) is formed, and the upper portion of the weight 1 also has the upper slide surface 4B slidably adhered to the upper seat surface 5B. And the frictional resistance there is set to be sufficiently small, so that the weight body 1 can be smoothly rotated with respect to the upper jig 2B and the upper floor beam 3B. The upper rotation center OB, which is the rotation center of the weight body 1 with respect to the upper jig 2B and the upper floor beam 3B, is set at a position that is displaced upward by the deviation dimension a from the lower rotation center OA. The upper sliding surface 4B and the upper seating surface 5B are both formed as circular arc surfaces (cylindrical surfaces) having an upper rotation radius R ₁ with the horizontal axis perpendicular to the weight body 1 passing through the upper rotation center OB. Yes.
The upper turning radius R ₁ and the lower turning radius R ₂ may be the same, but are not necessarily the same.

In the vibration reduction mechanism of the present embodiment having the above structure, when the frame is subjected to interlayer deformation during an earthquake as shown in FIG. 1B from the normal state (stationary state) shown in FIG. When the upper floor beam 3B has a horizontal displacement δ in the right direction with respect to the lower floor beam 3A as shown in the example, the upper portion of the weight 1 is horizontally directed from the upper floor beam 3B through the upper jig 2B. As a result, the weight body 1 is rotated by a small angle in the force application direction to cause locking, whereby a horizontal displacement occurs at the top of the weight body 1.
In this case, the rotation angle θ and the top horizontal displacement u of the weight body 1 are expressed by the following equation based on the horizontal displacement δ of the frame, the center-to-center displacement dimension a, and the upper rotation radius R ₁ .

From the above equation, it can be seen that when the center-to-center deviation dimension a is sufficiently small with respect to the upper turning radius R ₁ , the top horizontal displacement u of the weight body 1 is greatly enlarged with respect to the horizontal displacement δ of the frame. That is, the weight body 1 rotates greatly only by a slight horizontal displacement δ occurring in the frame, and the top horizontal displacement u becomes large.
As a result of such rotation, a large rotational inertial mass Ψ is generated in the weight body 1, and an excellent vibration reduction effect is obtained due to the rotational inertial mass effect thereby. That is, when the rotational inertia moment of the weight body 1 is Ip and the lower rotation center OA is the center of gravity of the weight body 1, the rotational inertia mass Ψ generated in the weight body 1 is as follows.

The rotational inertia mass Ψ is much larger than the actual mass of the weight body 1. For example, if the weight 1 is a reinforced concrete wall with a thickness of 0.5m, a width of 9m, and a height of 6m, its mass is only 65tons, but the center-to-center displacement dimension a = 0.5m The rotational inertial mass Ψ obtained by the rotation of the wall is 2,527 tons, which is several tens of times larger than the actual mass. Therefore, a large-scale building can be created with only one RC wall. It is possible to easily secure a large inertial mass exceeding 1,000 tons required for the target.
Note that if the value of the center-to-center deviation dimension a is too small, the influence of frictional resistance and accuracy error on rotation increases, so it is desirable that the value be 5% or more of the maximum dimension of the weight 1.
Further, the upper rotation center OB is slightly vertically displaced with the rotation of the weight body 1, but is a high-order minute term in the analysis, and the horizontal displacement δ is usually sufficiently smaller than the center-to-center deviation dimension a. Therefore, the rotation mechanism is not affected and can be ignored.

The basic effects obtained by the vibration reduction mechanism of the above embodiment are listed below.
(1) The above-described vibration reduction mechanism functions as a rotary inertia mass damper that uses the rotary inertia mass generated by the locking of the weight 1, and the rotary inertia mass damper is arranged in parallel with the structure spring (structural rigidity). Since this structure is a response reduction mechanism, it is possible to effectively exhibit the effect of reducing the period of the structure, reducing the input of ground motion, and reducing the vibration frequency at the cutoff frequency.
(2) Compared with a conventional rotary inertia mass damper with a mechanical mechanism using a ball screw and a flywheel, the inertial mass with respect to the weight 1 as a rotary weight is small, but a huge inertia exceeding 1,000 tons. The mass effect can be easily realized.
(3) The weight body 1 can be manufactured at low cost by using reinforced concrete, steel, or a combination thereof (however, the material is not limited thereto, and any material can be used as long as a desired mass can be obtained). The rotational inertial mass is determined by the setting of the mass and the dimension, and a huge inertial mass can be obtained only by satisfying the condition that it can rotate around both the lower rotational center OA and the upper rotational center OB. It can be manufactured and installed at a lower cost than the mechanical screw mechanism.
(4) Since the inertial mass is determined by the center-to-center displacement dimension a between the lower rotation center OA and the upper rotation center OB and the rotational inertia moment of the weight body 1, the value of the center-center displacement dimension a is adjusted. Thus, the inertial mass can be set arbitrarily and widely.
(5) The force between the weight 1 and the upper and lower beams 3 is transmitted between the arcuate sliding surface 4 and the seating surface 5, but the transmission area can be increased as required. Therefore, the stress per unit area is smaller than that of the conventional mechanical mechanism that processes all the burden force only with the cross-sectional area of the ball screw, and the stress processing is easy.
(6) It is possible to effectively use the walls and stored items installed in the building as the weight body 1, and in that case, prevent the reduction of the effective area by installing a special vibration control mechanism. Can do.

  The basic embodiment of the present invention has been described above, but other embodiments will be described below.

In the above embodiment, the upper and lower sides of the weight body 1 are both supported by the sliding support, and the sliding surface 4 formed on the weight body 1 slides in a state of being in direct contact with the seating surface 5 formed on the jig 2. Even with this, the friction coefficient can be set to a sufficiently small value, for example, μ = 0.04 or less, but an appropriate sliding mechanism is interposed between the weight body 1 and the jig 2 instead of the sliding bearing. It is also possible to do.
For example, a sliding mechanism 10 by roller support as shown in FIG. 3A is fixed to the weight body 1 and a rail on which it can roll is attached to the jig 2 (or conversely, the sliding mechanism 10 is mounted on the jig). 2), the friction coefficient can be further reduced compared to the case of simple sliding support, for example, μ = 0.006 or less. Is also possible.
Further, as shown in FIG. 3B, a sliding mechanism 13 called a linear guide having a configuration in which a slider 12 is smoothly slidably assembled to a guide rail 11 curved in an arc shape can be suitably employed. According to this, not only can μ be less than about 0.006, but the load capacity per unit can be reduced to about 1000 tons, and it can resist not only the compressive force but also the tensile force, thus preventing the lifting of the weight body 1. It is also possible to do.
Further, even in the case of using a sliding bearing, for example, if a commercially available product having a configuration in which the sliding member 15 is slid with respect to the sliding plate 14 as shown in FIG. 3C, μ = 0.013 or less and a load resistance of 2,000 tonf are used. This can be done.

  In addition, the setting of the friction coefficient μ in the sliding bearing and the sliding mechanism as exemplified above may be set so as to give an appropriate frictional resistance after setting the weight body 1 to be effectively locked, By doing so, it is possible to cause the sliding support and the sliding mechanism itself to function as a friction damper, and thereby it is possible to effectively attenuate the locking of the weight body 1.

In the above embodiment, the upper and lower sides of the weight body 1 are respectively supported by the upper and lower beams 3 via the jig 2, and the upper and lower sliding surfaces 4 of the weight body 1 and the seat surface 5 formed on the jig 2 are provided. In both cases, the circular arc surface (cylindrical surface) is used, but the upper and lower sides of the weight body 1 are both supported rotatably, and the weight body 1 is pressed by interlayer deformation (from the structure to the weight body 1). It is only necessary to generate a rocking force by transmitting a force via the seating surface 5 and the sliding surface 4, and the sliding surface 4 and the seating surface 5 are not necessarily limited to simple arc surfaces. For example, a modification as shown in FIG. 4 is conceivable.
4 (a) shows a flat top surface of the upper sliding surface 4B, FIG. 4 (b) shows the lower sliding surface 4A without the central portion, and FIG. 4 (c) shows the lower sliding surface. The tool 2A is divided into two parts. Further, as shown in (d), the most basic configuration is that the bearing surface 5 is directly formed on the beam 3 itself and the jig 2 is substantially omitted (however, the cross-sectional defect of the beam 3 due to the formation of the bearing surface 5). It is also possible to consider that the jig 2 and the beam 3 are integrally formed in advance.
4A to 4C only illustrate one of the upper part and the lower part of the weight body 1, it goes without saying that the other one not shown in the figure may be similarly modified. If necessary, various combinations are possible, for example, the upper part is shown in (a) and the lower part is shown in any of (b) to (d), and these can be combined with FIG. 3 (a). Of course, it is also possible to arbitrarily combine the sliding mechanism as exemplified in (c).

  Further, the wall body as the weight body 1 is not necessarily a simple flat plate shape, and the shape of the entire weight body 1 is arbitrary as long as a desired mass can be secured and the upper and lower surfaces can be rotatably supported. For example, there is no problem even if an opening used for a window, an entrance, or the like is formed at a desired position. In particular, the mass of the central portion of the weight body 1 does not contribute much in obtaining the rotational inertial mass effect, and the lower rotational center OA and the upper rotational center OB are merely virtual centers, and the rotational axis and pin are actually located at those positions. Since it is not necessary to provide a wall of the weight 1 as a wall surface in a building, it is not a problem to cut out the central part to form an opening for a window. On the contrary, it is reasonable from the viewpoint of obtaining a suitable mass distribution in the weight body 1 and gaining a rotational moment of inertia.

Further, in the above embodiment, the weight body 1 is assumed to be a wall body and only locking within the surface is assumed. However, the weight body 1 may be a three-dimensional block body that can be locked in each horizontal direction. This is possible and an example is shown in FIG.
5A, the weight body 1 is formed in a disk shape, and the upper and lower sides thereof are supported by a square disk-shaped jig 2, and the sliding surface 4 protrudes in a convex spherical shape above and below the weight body 1. Is formed with a concave spherical seating surface 5. In this case, the center points of the convex spherical surface as the upper and lower sliding surfaces 4 and the concave spherical surface as the upper and lower seating surfaces 5 that support them are the positions of the upper rotational center OB and the lower rotational center OA described in the above embodiment. As a matter of course, it is natural to ensure an appropriate center-to-center displacement dimension a between the upper rotation center OB and the lower rotation center OA.
According to this, it is possible to support the block body as the weight body 1 in a state in which locking in each horizontal direction is possible, thereby obtaining a rotational inertial mass effect in each horizontal direction, and in each direction. A vibration reduction effect can be obtained. A conventional general mechanical rotary inertia mass damper is effective only in one direction, and when it is effective in each direction, it is necessary to install a plurality of dampers corresponding to each direction. By adopting a structure that locks in each direction, it is possible to effectively obtain a damper effect in each direction with this single unit.

5 (b) and 5 (c) are modified examples thereof, FIG. 5 (b) shows the weight 1 having a square disk shape, and FIG. 5 (c) shows the top of the upper sliding surface 4 in FIG. 4 (a). It is flattened in the same manner as shown. Further, in FIG. 5 (d), the upper and lower sides of the weight body 1 are projected in a substantially truncated pyramid shape, and the sliding surface 4 and the seating surface 5 are formed by two-way cylindrical surfaces (two-way cone-shaped shape of a ridged building). This is also formed, and by this, locking in two horizontal directions is possible and the same effect can be obtained.
In any case, the block body as the weight body 1 does not need to be completely solid, and may have a hollow portion (cavity) inside as long as it has a desired mass, and in particular, a rotary inertia mass. Since it is reasonable to make the central part that does not contribute much to the effect as a hollow part, it is also conceivable to use the internal space effectively by making the block body into a hollow box shape. For example, the block body as the weight body 1 can be made to function as a chamber as a hollow box-shaped unit having a surrounding wall surface, a ceiling surface, and a floor surface.

In the above embodiment, the upper and lower jigs 2 are both fixed to the upper and lower beams 3, but it is also conceivable that either one of them can be displaced relative to the beam 3 via an additional spring and additional damping. An example in that case is shown in FIG.
FIG. 6A shows that the upper jig 2B is arranged so as to be displaceable in the length direction (= vibration direction = direction of force applied to the weight body 1) without being fixed to the upper floor beam 3B. An additional spring 21 and an additional damping 22 are interposed between both ends of 2B and the pillars 20 on both sides.
In this case, the rotary inertia mass damper constituted by the weight body 1 is arranged in series with the additional spring 21 and then arranged in parallel with the structure spring (structural rigidity). The vibration system including the rotational inertial mass and the additional spring 21 can function in the same manner as a TMD (tuned mass damper).
That is, in the case of the spring constant k ₀ of the additional spring 21, the rotational inertia mass Ψ of the weight body 1, and the vibration suppression target frequency f ₀ (vibration suppression target angular frequency ω ₀ ), the following relationship holds: Set each item as follows.

The above equation means that the natural frequency of the vibration system due to the rotational inertial mass Ψ by the weight body 1 and the additional spring 21 is tuned to the vibration suppression target frequency f _0. It is possible to significantly improve the resonance characteristics in terms of number and reduce the response. In particular, by setting the vibration suppression target frequency f ₀ as the natural primary frequency of the structure (building), it is possible to effectively reduce the response at the natural primary frequency of the structure during an earthquake.
FIG. 6 (b) shows a modified example in which a laminated rubber as the additional spring 21 and an oil damper as the additional damping 22 are interposed between the upper floor beam 3B and the upper jig 2B. In this case, the same effect can be obtained by the same tuning.
The additional damping 22 is not only installed in parallel to the additional spring 21 as described above, but may be installed between the weight body 1 and the upper jig 2B. By properly setting the coefficient of friction in the sliding bearing (or the above-described appropriate sliding mechanism) between the body 1 and the upper jig 2B so as to have a desired damping performance, it functions as an additional damping 22 itself. It is also possible.
Further, the same effect can be obtained by adopting the same configuration for the lower jig 2A in place of the upper jig 2B (that is, by making the configuration upside down in FIG. 6).

In each of the embodiments described above, the lower part (bottom part) and the upper part (top part) of the weight body 1 are rotatably supported and the weight body 1 is locked. The weight 1 may be locked by applying an interlayer deformation, and as long as it is not necessarily applied to the top of the weight 1, the side of the weight 1 as shown in FIG. It is also possible to apply force. That is, in the present invention, the “lower part” of the weight body substantially means the “bottom part”, but the “upper part” of the weight body means not only the “top part” but also the range including the “side part”. This means that the “upper part” of the weight body in the present invention includes both the “top part” and the “side part”.
That is, in the embodiment shown in FIG. 7, the upper sliding surface 4B is formed as a convex arc surface on both sides instead of the top of the weight 1, and the top of the weight 1 is formed flat, and the upper jig 2B is formed. Instead of fixing to the upper floor beam 3B, it is fixed to the middle part of the pillars 20 on both sides, and the tip of the upper jig 2B is slidably brought into contact with the upper sliding surface 4B. Thereby, the interlayer deformation is transmitted to the weight body 1 via the column 20 and the upper jig 2B, and the side portion of the weight body 1 is applied, and this also locks the weight body 1 as in the above embodiment. And the same effect can be obtained.
However, in this case, as in the above-described embodiment, the upper rotation center OB is shifted upward from the lower rotation center OA, and at least the upper rotation center is used to effectively lock the weight body 1. Since it is necessary to apply a force in the horizontal direction above the position of the OB, the installation position of the upper jig 2B (that is, the position of the side part for applying the weight 1) needs to be set within such a range. There is.
In this case, the upper seat surface 5B at the tip of the upper jig 2B is slidably brought into contact with the side portion of the weight body 1 so that a force is applied. Although it is sufficient that the surface 5B is a flat surface, the upper seat surface 5B may be supported as a concave arc surface in a state of being in close contact with the upper sliding surface 4B in the same manner as in the above embodiment.
In any case, it is preferable to stiffen the column 20 by providing an intermediate beam 23 behind the fixed position of the upper jig 2B because the force applied to the weight body 1 is made through the column 20.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to the said embodiment, Of course, it is set as the structure which can be rock | rocked so that the weight body 1 may function as a rotation inertia mass damper. It goes without saying that appropriate design modifications and applications are possible including various combinations of the above embodiments.

It is a schematic block diagram which shows the vibration reduction mechanism which is one Embodiment of this invention. It is a figure which shows the jig | tool which supports the wall body as a weight body, and its upper and lower sides similarly. It is a figure which shows other embodiment of this invention, and shows the example of the suitable sliding mechanism for supporting a weight body. It is a figure which shows the modification of a sliding surface and a jig | tool similarly. It is a figure which shows the example of the block body as a weight body same as the above. It is a figure which shows the example in the case of installing a jig | tool through an additional spring similarly. It is a figure which shows the structural example in the case of applying force to the side part of a weight body similarly.

Explanation of symbols

OA Lower rotation center OB Upper rotation center 1 Weight 2 Jig 2A Lower jig 2B Upper jig 3 Beam 3A Lower floor beam (lower structure)
3B Upper floor beam (superstructure)
4 sliding surface 4A lower sliding surface 4B upper sliding surface 5 seating surface 5A lower seating surface 5B upper seating surface 10 sliding mechanism 11 guide rail 12 slider 13 sliding mechanism 14 sliding plate 15 sliding material 20 pillar 21 additional spring 22 additional damping 23 intermediate beam

Claims (6)

Between the lower structure and the upper structure that vibrate relative to each other in the horizontal direction, a weight body that is rocked by being applied by the horizontal relative vibration generated between the lower structure and the upper structure is installed. A vibration reduction mechanism configured to reduce the relative vibration by a rotational inertial mass effect due to locking of the weight,
The lower part of the weight body is rotatably supported with respect to the lower structure, and the lower rotation center, which is the center of rotation, is set at the center of gravity position of the weight body or near the center of gravity.
The upper part of the weight body is rotatably supported with respect to the upper structure, and the upper center of rotation that is the center of rotation is set at a position that deviates upward from the lower center of rotation. Vibration reduction mechanism. The vibration reduction mechanism according to claim 1,
A lower seat that forms a lower sliding surface and an upper sliding surface at a lower portion and an upper portion of the weight, respectively, and that slidably supports the lower sliding surface and the upper sliding surface on the lower structure and the upper structure, respectively. Surface and upper bearing surface,
Both the lower sliding surface and the lower seating surface are formed into a curved surface centered on the lower rotation center,
The vibration reducing mechanism characterized in that both the upper sliding surface and the upper seating surface are formed into curved surfaces centering on the upper rotation center. The vibration reduction mechanism according to claim 2,
The weight body is a wall body that forms a wall surface along a vibration direction of relative vibration generated between the lower structure body and the upper structure body and can be locked in a plane of the wall surface,
The lower sliding surface formed at the lower portion of the wall body and the lower seating surface supporting the lower sliding surface are formed as a convex arc surface and a concave with a horizontal axis passing through the lower rotation center and perpendicular to the wall surface as a center line. Formed as a circular arc surface,
The upper sliding surface formed on the upper portion of the wall body and the upper seating surface supporting the upper sliding surface are formed with a convex arc surface and a concave centered on a horizontal axis passing through the upper rotation center and perpendicular to the wall surface. A vibration reduction mechanism formed as an arc surface. The vibration reduction mechanism according to claim 2,
The weight body is a block body that can be locked in each horizontal direction,
Forming the lower sliding surface formed at the lower part of the block body and the lower seating surface supporting the lower sliding surface as a convex spherical surface and a concave spherical surface centered on the lower rotation center,
The upper sliding surface formed on the block body and the upper seating surface supporting the upper sliding surface are formed as a convex spherical surface and a concave spherical surface centered on the upper rotation center. Vibration reduction mechanism. The vibration reduction mechanism according to any one of claims 1 to 4,
A sliding mechanism for rotatably supporting the weight body is interposed between the lower portion of the weight body and the lower structure body and between the upper portion of the weight body and the upper structure body. Vibration reduction mechanism. The vibration reduction mechanism according to any one of claims 1 to 5,
With respect to the upper structure or the lower structure while rotatably supporting the weight body between the upper portion of the weight body and the upper structure or between the lower portion of the weight body and the lower structure. And a jig that is relatively displaceable in the horizontal direction, and an additional spring that is operated between the jig and the upper structure or the lower structure according to the horizontal relative vibration direction generated therebetween. A vibration reduction mechanism characterized by being worn.

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