JP2009293693A - Vibration control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact and high-performance vibration control device which keeps invariably a constant frequency even when large-amplitude occurs due to long-term oscillation by merging a pendulum principle and a rolling principle. <P>SOLUTION: The vibration control device is equipped with a rolling element 20 and a support 30 for supporting the rolling element 20 in a rolling motion enable manner. The support 30 is formed in a curved cross-sectional surface depressed downward in relation to a horizontal surface and includes a supporting surface 40 on which the rolling element 20 rolls. In the supporting surface 40, a curvature radius of a curved line for defining the curved cross-sectional surface gradually shortens as the lowermost portion of a central portion of the supporting surface moves away toward both-side directions of the supporting surface. Besides, the supporting surface 40 is formed so that the center of the curvature radius gradually descends on the vertical line passing the lowermost portion. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention comprises a rolling element and a support that supports the rolling element so as to be able to roll, and is structured by rolling of the rolling element with respect to the support in a state of being installed in a structure. The present invention relates to a vibration damping device that suppresses shaking of an object. In particular, the present invention relates to a vibration damping device that suppresses a relatively slow vibration of about 1 Hz or less when an earthquake occurs or a strong wind, such as a slender structure represented by a suspended bridge or a high-rise building. Especially for slender civil engineering structures such as main towers of suspension bridge type long bridges and high-rise buildings, it is possible to suppress vibrations from slow vibrations of about 1 Hz or less to several hertz in the event of an earthquake or strong wind. The present invention relates to a vibration device.

  Conventionally, various damping devices have been studied as a countermeasure against wind fluctuations and earthquakes for structures such as the main tower of a suspension bridge type long bridge and high-rise buildings. As these vibration damping devices, for example, as shown in FIG. 18 (a), a sloshing damper using a sloshing damping action of liquid using a water tank, and as shown in FIG. Although not shown, a tuned mass damper having a weight placed on a laminated rubber is known.

  Furthermore, a rolling vibration damping device (TRMD) that rolls a rolling element within a circular inner peripheral surface is known as a vibration damping device applied to a gate-type structural facility installed on a road. As an advancement of this type of rolling vibration damping device, the present inventors have already proposed, for example, a tuned cradle vibration damping device described in Patent Document 1 below. Here, the tuning is to match the natural frequency of the structure and that of the rolling element. By bringing this tuning together with the vibration of the structure, vibration energy can be absorbed.

  However, in the above-described conventional technology, particularly in the case of a sloshing damper, a pendulum type, and a tuned mass damper, the mechanical structure of the apparatus becomes complicated, the entire apparatus becomes large, and the desired damping performance is obtained. There is a problem in that it is necessary to frequently perform maintenance and inspection in order to make it work, and it is not easy to keep it in an always operable state.

  In addition, all of the conventional techniques described above are configured with a countermeasure for resonance of a relatively short period of the structure in mind, and no countermeasure for resonance due to long-period vibration with a long period has been taken. For this reason, long-period vibrations that sway once every few seconds, which are known to be the main causes of damage to high-rise building elevators due to the Tokachi-oki earthquake, the Niigata Chuetsu-oki earthquake, and the Noto Peninsula-oki earthquake, continue for several minutes. There is a problem that it is not possible to substantially cope with a situation in which a building has a large amplitude due to resonance.

  Focusing on these problems, the inventors of the present application further simplified the configuration and facilitated maintenance inspection as described in Patent Document 2 below, particularly for low-order vibration (for example, 1 Hz or less). We have proposed a tuned cradle type vibration control device that can be tuned. This is because, when the support swings in a direction intersecting with the extending direction of the central axis of the arc-shaped support surface, two swings supported at two points on the arc-shaped support surface of the support via two rolling rollers. The rotor is oscillated in synchronism, and the two rolling rollers are oscillated in synchronism to absorb the vibration energy of the support.

  However, the inventor of the present application has advanced research on this tuned cradle type vibration damping device, and since the arc-shaped support surface of the vibration damping device has an arc shape with a constant curvature radius, It has been found that the vibration period changes. That is, in general, the pendulum swings at a substantially constant period if it is a minute vibration, but if the vibration becomes large, the period changes according to the magnitude, and as a result, there is a possibility that the damping performance may be lowered. It turned out to be. The same can be said for the tuned cradle type vibration damping device described in Patent Document 1.

  Focusing on such problems, the inventors of the present application have further studied the device corresponding to the long-period vibration, and as a result, as described in Patent Document 3 below, for the vibration having a large amplitude. We have also proposed a tuned cradle type vibration control device that can fully exhibit the vibration control performance. This has a support surface having a concave curved support surface, two swingers positioned on both outer sides in the width direction of the support body, and supports each rollable on the support surface along the support surface. And two rolling rollers that have both ends rotatably coupled to the two rockers and support the rockers, and the concave curved surfaces of the two support surfaces are at the bottom. The radius of curvature decreases as the distance from the distance increases.

Japanese Patent No. 3696724 JP 2005-83499 A JP 2007-24261 A

However, even in the conventional tuned cradle type vibration damping device described in Patent Document 3 as described above, the following problems to be improved have been clarified by the subsequent earnest research by the present inventors. That is, the two rolling rollers that roll on the support surface as a concave curved surface in the support and the two rockers that are rotatably coupled to these are essential components, and the number of parts is large and the cost is high. There was a risk of an increase. Subsequent research has revealed that it is possible to omit the oscillator and give the rolling roller considerable weight.

  In addition, by changing the concave curved surface of the support surface so that the radius of curvature decreases as it moves away from the lowermost part, it is possible to always maintain a constant cycle even if the deflection angle of the rolling roller increases. If it is the shape of such a concave curved surface, in order to obtain the minimum required rolling distance, it is necessary to ensure a sufficient height in the vertical (vertical) direction. Therefore, it has been difficult to make the entire apparatus more compact.

  The present invention has been made by paying attention to the problems of the prior art as described above, and by combining the principle of the pendulum and the rolling principle, a constant vibration is maintained even when a large amplitude is generated by long-term vibration. Providing a high-performance vibration control device with extremely high commercial value that can maintain the number, and can not only reduce the cost and reduce the cost, but also make the entire device more compact. The purpose is to do.

The gist of the present invention for achieving the above-described object resides in the inventions of the following items.
First, the present invention described in claim 1
It is provided with a rolling element (20, 120, 220) and a support (30, 130, 230) that supports the rolling element (20, 120, 220) so that it can roll, and is installed in a structure. In the vibration damping device (10, 110, 210) for suppressing the shaking of the structure by rolling of the rolling element (20, 120, 220) with respect to the support (30, 130, 230)
The support (30, 130, 230) is formed in a curved cross section that is recessed downward with respect to a horizontal plane, and the support surface (40, 140,) for rolling the rolling element (20, 120, 220). 240)
As the support surface (40, 140, 240) moves away from the lowermost part of the center in both directions, the curvature radius of the curved line defining the curved cross section gradually decreases, and the center of the curvature radius is the lowermost part. The vibration control device (10, 110, 210) is characterized in that it is set in a shape that gradually descends on a vertical line passing through.

The present invention according to claim 2
The support body (30, 130, 230) has the support surface (40, 140, 240) recessed downward from an upper end edge extending along the front surface, and the front surfaces are spaced apart from each other in parallel. A pair of
Between the support surfaces (40, 140, 240) of the respective supports (30, 130, 230), the rolling elements (20, 120, 240) are formed in a circular cross section and roll around their central axes. 220) The vibration damping device (10, 110, 210) according to claim 1, wherein the vibration damping device (10, 110, 210) is supported in a bridged state.

The present invention according to claim 3 provides
Arranging two pairs of the supports (130) in a line in two lateral directions;
The vibration control device (110) according to claim 2, wherein the rolling elements (120) in each of the groups are connected to each other so as to roll in synchronization with each other via a weight.

Furthermore, the present invention according to claim 4 provides:
A horizontal plate (260) for closing the upper opening of the support surface (240) is disposed on the upper end side of the support (230),
A plurality of the supports (230) are arranged side by side on an installation surface, and the horizontal plate (260) on each support (230) is continued on the same plane. Is the vibration damping device (210).

  According to the vibration damping device of the first aspect of the present invention, when the support body vibrates in both directions, the support body is supported on the support surface formed in the curved cross section of the support body in synchronization with the vibration. The rolling element rolls and absorbs the vibration energy of the support. Thus, it can be configured very simply with at least two components of the support and the rolling element, and not only can the cost be reduced, but also the entire apparatus can be configured more compactly.

  In particular, the radius of curvature of the curved line that defines the curved cross section gradually decreases as the support surface moves away from the lowermost part of the center in both directions, and as a principle of the pendulum, the oscillation period is delayed as the amplitude increases. Since the vibration period of the rolling elements can be made constant regardless of the magnitude of vibration, the vibration damping performance can be fully exerted even when large amplitudes are generated due to long-term vibration. .

  In addition, as the support surface moves away from the lowermost part of the center in both sides, the radius of curvature gradually decreases, and the center of the radius of curvature gradually falls on a vertical line passing through the lowermost part of the support surface. Since it is a shape, it is possible to suppress the dimension in the vertical direction as much as possible while keeping the vibration period constant as described above, and it is possible to further reduce the size and make the structure compact.

  According to the vibration damping device of claim 2 of the present invention, a pair of the support bodies arranged with their front surfaces spaced apart in parallel forms a pair, and the support surfaces of the respective support bodies Since the rolling elements formed in a circular cross section are supported in a state of being sandwiched between them, the relatively long and heavy rolling elements can be reliably supported in a swingable state. The vibration control effect can be further enhanced, and since only one rolling element is supported on each support surface, the support surface can be used longer in the direction along the front surface of the support body, and vibration with a larger amplitude can be used. The vibration control performance can be fully exhibited.

  According to the vibration damping device of claim 3 of the present invention, the two pairs of the support bodies are arranged in a row in both side directions, and the rolling elements in each of the pairs are weighted to each other. Since the pendulum principle and the rolling principle are more closely fused, the rolling element is not dependent on the size and size of the rolling element. The weight of the weight can be increased indirectly by the weight, and the swing distance of the weight can be increased, and in particular, it is possible to effectively synchronize with a low-order vibration (for example, 1 Hz or less). .

  Furthermore, according to the vibration damping device according to claim 4 of the present invention, a horizontal plate that closes the upper opening of the support surface is arranged on the upper end side of the support, and a plurality of the supports are arranged side by side on the installation surface. In addition, since the horizontal plates on the respective supports are continuously arranged on the same plane, it can be retrofitted to an existing structure, and the floor can be effectively utilized without occupying the floor space. In addition, the vibration control effect can be further enhanced by arranging a plurality of them side by side.

Hereinafter, various embodiments representing the present invention will be described with reference to the drawings.
1 and 2 show a first embodiment of the present invention.
FIG. 1 is a front view showing a vibration damping device 10 according to the present embodiment, and FIG. 2 is a plan view showing the vibration damping device 10.

  As shown in FIGS. 1 and 2, the vibration damping device 10 includes a rolling element 20 and a support body 30 that supports the rolling element 20 so as to be able to roll, and is installed in a structure. Thus, it is an apparatus for suppressing the shaking of the structure by the rolling of the rolling element 20 with respect to the support 30. Such a vibration damping device 10 is placed on the roof of the structure or the floor or wall of each floor, or is installed so as to be embedded, so that the structure of the structure can be changed based on a preset weight or size. The vibration energy is absorbed in synchronization with the vibration, and as a result, the shaking of the structure is suppressed.

  The support 30 is formed in a curved cross section that is recessed downward with respect to a horizontal plane, and has a support surface 40 for the rolling element 20 to roll. Specifically, the support 30 is originally processed from a rectangular plate having a predetermined thickness, and a pair of front surfaces thereof arranged at intervals in parallel form a pair. . The material of the support 30 can be a general structural rolled steel, a metal material such as copper or aluminum, a polymer material such as hard rubber or plastic, or other materials.

  Each support 30 is cut out in the thickness direction so as to form a predetermined curve line that is recessed downward from the upper end edge extending along the front surface, and the cut end is bent over the width of the plate thickness. An extending support surface 40 is formed. Alternatively, a flange-like rail that extends in a narrow shape along a cut surface (curved cross section) that represents the curve line may be integrally attached, and the rail upper surface may be used as the support surface 40 as it is.

  As shown in FIG. 1, as the support surface 40 moves away from the central lowermost portion 41 in both directions, the radius of curvature of the curved line defining the curved cross section gradually decreases, and the center of the radius of curvature is The shape is set so as to gradually descend on a virtual vertical line L passing through the lower portion 41. Details of the curved line and a calculation method thereof will be described later. Further, in FIG. 1, a curved line A shown by an imaginary line (two-dot broken line) for comparison defines a conventional support surface having an upward arc shape with a constant curvature radius.

  The rolling element 20 is formed in a circular cross section and rolls around its central axis, and is supported in a state of being bridged between the support surfaces 40 of the respective supports 30. Here, the rolling element 20 is solid and columnar. However, for example, if a hollow cylindrical shape is used, the center of mass of the mass approaches the outer periphery of the rolling element, and a better inertial mass distribution is formed. It leads to improvement. The rolling element 20 only needs to have a mass of about 1% of the effective mass (swaying weight) in the vibration suppression target vibration mode of the structure, and resonates and rolls at the natural frequency of the structure. The rolling element 20 rolls in the direction opposite to the movement of the structure on the support surface 40 to suppress vibration.

  In any case, the rolling element 20 appropriately sets the mass of itself, the radius of curvature of the outer peripheral surface, the radius of curvature of the supporting surface 40, the frictional force between the outer peripheral surface of the rolling element 20 and the supporting surface 40, or the like. By this, it is comprised so that it can roll smoothly, without producing a slip with respect to the support surface 40 of the support body 30. FIG. In addition, the material of the support surface 40 of the support body 30 can be a rail-shaped rolled steel for general structure, a metal such as copper or aluminum, a polymer material such as rubber or plastic, or other materials.

  Further, magnetic dampers 21 made of permanent magnets having the same diameter as the rolling element 20 and a circular cross section are mounted on both end surfaces of the rolling element 20. The magnetic damper 21 may be composed entirely of permanent magnets, but may be constructed, for example, by embedding a permanent magnet in the center of a synthetic resin disk having the same diameter as the rolling element 20.

  Further, although not shown in FIG. 1, as shown in FIG. 2, on the outside of each support body 30, the copper dampers facing the magnetic dampers 21 on both end surfaces of the rolling element 20 with a gap are respectively provided. A non-ferrous metal plate 50 such as aluminum is provided to face each other in parallel with each support 30. Thus, when the structure vibrates and the rolling element 20 rolls, the magnetic force lines coming out of the magnetic damper 21 of the rolling element 20 move while being blocked by the non-ferrous metal plate 50. 20 can be braked to obtain proper damping.

Next, the operation of the vibration damping device 10 according to the first embodiment will be described.
According to the vibration damping device 10 shown in FIG. 1 and FIG. 2, when the installed structure vibrates due to wind / traffic vibration, earthquake, or the like, and the support 30 vibrates in both directions along with this, the support In synchronization with the vibration of the support 30, the rolling element 20 supported on the support surface 40 of the support 30 rolls in the opposite direction to the shaking of the structure, and absorbs the vibration energy of the support 30.

  Thereby, the vibration of the structure which generate | occur | produces by a wind, an earthquake, etc. can be attenuated. Such a vibration damping device 10 according to the present embodiment can be configured very simply with at least two components, that is, the support body 30 and the rolling element 20, and not only can the cost be reduced, but also the entire device can be further improved. It can be configured compactly.

  As shown in FIG. 1, the curvature radius of the curved line that defines the curved cross section gradually decreases as the support surface 40 moves away from the central lowermost portion 41 in both directions, so that the amplitude increases as the principle of a pendulum. Accordingly, the inconvenience that the vibration period is delayed can be eliminated, and the vibration period of the rolling element 20 (the period in which the lowermost part 41 is swung in both directions) can be made constant regardless of the magnitude of vibration. it can.

  As a result, the vibration energy generated by the vibration is absorbed even in vibrations with large displacements, such as high-rise buildings that have a very slow natural vibration period of 1 second or more in the natural vibration mode of the structure. It becomes possible to do. Therefore, the damping performance can be sufficiently exhibited even when a large amplitude is generated due to long-term vibration.

  In particular, as the support surface 40 moves away from the central lowermost portion 41 in both directions, not only the curvature radius of the curved line gradually decreases, but the center of the curvature radius depresses the lowermost portion 41 of the support surface 40. Since the shape gradually descends on the passing vertical line L, as described above, it is possible to suppress the dimension in the vertical direction as much as possible while maintaining the vibration period always constant, and further downsizing and compact configuration. Can do.

  Further, as shown in FIG. 2, the magnetic damper 21 of the rolling element 20 faces the nonferrous metal plate 50, so that the magnetic flux of the magnetic damper 21 penetrates the nonferrous metal plate 50. In this state, when the magnetic damper 21 moves relative to the non-ferrous metal plate 50 along with the swing of the rolling element 20, the magnetic flux penetrating through the non-ferrous metal plate 50 is increased at a portion approaching the magnetic damper 21. There is less magnetic flux penetrating in the away part. As a result, electromagnetic induction occurs, and an eddy current flows through the non-ferrous metal plate 50 so as to cancel the change in magnetic flux.

  That is, in the non-ferrous metal plate 50, a repulsive magnetic field is generated at a portion approaching the magnetic damper 21 of the rolling element 20, while a attracting magnetic field is generated at a portion moving away. Since the rolling elements 20 are braked by these actions, the vibration damping effect can be further enhanced. In addition, the vibration damping speed of the structure can be increased by appropriately selecting the material of the rolling element 20 and the support 30 and effectively utilizing the viscoelasticity characteristic of the material. The same applies to various embodiments described later.

  As described above, the vibration damping device 10 that combines the principle of the pendulum and the rolling principle is structurally relatively simple and low in cost, and has a sufficient vibration damping function without the need for maintenance and inspection. In particular, the installation space can be small. Therefore, a 10-story pencil building or the like standing on a small site in an urban area has an eigenvalue of about 1 Hz. First, it is desirable to optimally install the vibration control device 10 for such a structure. .

3 to 9 show a second embodiment of the present invention.
FIG. 3 is a perspective view mainly showing the support body 130 of the vibration damping device 110 according to the present embodiment. FIG. 4 shows a pair of rolling elements 120 and 120, a carriage 160 that connects and supports them, and a weight. 161 is a perspective view showing a structure provided with a mounting cover 162. FIG. 6 is a perspective view showing the vibration damping device 110 in which the magnetic damper 170 is attached to the attachment cover 162, and FIG. 7 is a perspective view showing a structure further including a non-ferrous metal plate 150. FIG. FIG. 8 is a plan view of the vibration damping device 110, and FIG. 9 is a front view of the vibration damping device 110.

  Damping device 110 according to the present embodiment arranges a pair of support bodies 130 in a row in two lateral directions, and has rolling elements 120 in each set as carriage 160 and weights serving as weights. 161 is connected to a state of rolling in synchronization with each other. Here, in the example shown in FIG. 3, the pair of support members 130 are provided so as to be integrally connected on a single plate member that is continuous in both directions, but is separated, that is, in the first embodiment. You may comprise so that the two support bodies 30 demonstrated may be located in a line on both sides.

  The pair of plate members constituting the support 30 in each set is formed by processing a rectangular shape having a predetermined thickness and extending in a long direction in both sides, and the front faces are spaced apart from each other in parallel. In this state, it is erected on a base plate 111 placed substantially horizontally. Here, between the base plate 111 and the plate material, reinforcing ribs 112 are fixed at a plurality of locations. Approximately half of one side of each plate material forms a pair of supports 130 of the same set on one side, and approximately half of the other side forms a pair of supports 130 of the other set on the other side.

  The structure of each support 130 itself is basically the same as that of the support 30 in the first embodiment, and each support 130 is recessed below the upper edge extending along the front surface. The two support surfaces 140 are cut out in the thickness direction so as to form a curved line. A rail 113 that is flange-shaped and expands narrowly is integrally attached along the cut surface (curved cross section), and the upper surface of the rail 113 is the support surface 140 to be precise. In addition, the specific shape of the curved line that embodies the support surface 140 is the same as that of the support surface 40 of the first embodiment, and redundant description is omitted here.

  The rolling element 120 is formed in a circular cross section, rolls around its central axis, and is supported in a state of being spanned between the support surfaces 140 of the respective supports 130. The rolling element 120 is not formed in the same circular cross section over the entire length like the rolling element 20 of the first embodiment. Specifically, as shown in FIG. 4, the rolling element 120 includes a pair of rolling element bodies 121, 121 and an axle 122 for connecting the respective rolling element bodies 121.

  The diameter of the rolling element main body 121 that rolls on the support surface 140 is set in view of the natural frequency of the structure. The axles 122 that connect the respective rolling element bodies 121 can have a mass that obtains an appropriate rotational inertia force from the weight 161 and the like separately from the rolling elements 120. Can be formed. That is, the rolling element 120 only needs to have a mass of about 1% of the effective mass in the primary vibration mode of the structure together with the mass of the weight 161.

  As shown in FIG. 4, the rolling elements 120, 120 in each set are rotatably connected to the front and rear positions in the rolling direction of the carriage 160 via the axle 122 so as to constitute the wheels of the carriage 160. It is pivotally supported. A rotating flange 123 that abuts against the edge of the rail 113 and is prevented from coming off in order to stably roll on the support surface 140 on the surface side of the rolling element body 121 where the axle shaft 122 is connected. Are provided integrally.

  The carriage 160 is configured by connecting square steel pipes, and the central portion thereof is formed so as to be recessed downward in a step shape. A weight 161 mainly serving as a weight is mounted on the recess so as to be placed thereon. The weight of the weight 161 is preferably determined as appropriate for the material according to the effective mass of the structure. As shown in FIG. 5, a mounting cover 162 is mounted on the carriage 160 so as to cover the entire surface within a range that does not inhibit the rolling of the rolling element 120.

  As shown in FIG. 6, magnetic dampers 170 are attached to both end portions of the attachment cover 162. The magnetic damper 170 is made of a permanent magnet, and is connected to both ends of a narrow upper plate 171 spanning the upper surface of the mounting cover 162, and a large number of magnetic dampers 170 are mounted on the surface of the mounting plate 172 parallel to the front surface of each support 130. Are arranged so as to be closely arranged.

  In addition, as shown in FIG. 7, gaps are formed on the outer sides of the respective supporting bodies 130 with respect to the magnetic dampers 170 on both end surfaces of the mounting cover 162 supported on the pair of rolling elements 120, 120. The non-ferrous metal plates 150 that face each other in an open manner are arranged in opposition to each other so as to face each support 130 in parallel. As a result, when the structure vibrates and the rolling element 120 rolls, the magnetic force lines coming out of the magnetic damper 170 move while being blocked by the non-ferrous metal plate 150. The accompanying swinging of the carriage 160 and the weight 161 is braked.

Next, the operation of the vibration damping device 110 according to the second embodiment will be described.
According to the vibration damping device 110, as in the case of the first embodiment described above, when the support 130 vibrates in both directions, two shafts that are different from each other are synchronized with the vibration of the support 130. A pair of rolling elements 120, 120 on the line rolls in the opposite direction to the shaking of the structure along the support surface 140 of each support 130, and is further supported integrally on each rolling element 120. The trolley 160 and the weight 161 are also oscillated in synchronism with the direction in which each rotator 120 rolls.

  Accordingly, the structure can be applied to a structure having a larger effective mass, and the vibration energy of the support 130 can be sufficiently absorbed, and the vibration of the structure generated by a wind, an earthquake, or the like can be reliably damped. In particular, the weight of the rolling element 120 can be increased indirectly by the carriage 160 or the weight 161 without depending on the size and size of the rolling element 120 having an appropriate rotational inertia force, and the entire weight can be obtained. As a result, the oscillation distance can be increased, and in particular, it is possible to effectively synchronize with a low-order vibration (for example, 1 Hz or less).

  Moreover, as in the first embodiment, the support surface 140 of the support 130 has a shape in which the radius of curvature of the curve line that defines the curved section gradually decreases as the distance from the lowermost portion of the center increases in both directions. Therefore, a constant frequency can always be maintained even when a large amplitude is generated by long-term vibration. Therefore, the vibration control performance can be sufficiently exhibited not only for vibrations having a small amplitude but also for vibrations having a large amplitude, and the structure can be effectively protected from vibrations caused by earthquakes and winds. .

  Further, as in the first embodiment, the support surface 140 not only gradually decreases the radius of curvature of the curved line as it moves away from the lowermost part of the center, but also the center of the radius of curvature is Since the shape gradually descends on the vertical line passing through the lowermost part of the support surface 140, the size in the vertical direction can be suppressed as much as possible even if the structure is somewhat complicated, and the structure can be made as compact as possible.

10 to 14 show a third embodiment of the present invention.
FIG. 10 is a perspective view showing the support body 230 and the rolling element 220 that form one unit of the vibration damping device 210 according to the present embodiment, and FIG. 11 is an exploded perspective view showing the rolling element 220. is there. FIG. 12 is a plan view showing the support body 230 and the rolling element 220 forming one unit, and FIG. 13 is a side view showing the support body 230 and the rolling element 220 forming one unit. FIG. 14 is a perspective view showing an installation state of the vibration damping device 210.

Damping device 210 according to the present embodiment is a horizontal plate that is arranged on a plurality of support bodies 230 by arranging a plurality of units including support bodies 230 and rolling elements 220 on the floor (installation surface). The step and lid 260 is continuously arranged on the same plane. Here, the unit is a size reduction of the vibration damping device 10 according to the first embodiment, and the overall height is set to about 30 cm, and the weight of each unit is set to about 100 kg / m ^2. The floor load capacity of office slabs can be adapted to about 300 kgf / m ² and can be applied regardless of whether it is newly built or existing.

  As shown in FIG. 10, like the support 30 of the first embodiment, the support 230 is originally processed from a rectangular plate having a predetermined thickness. A pair is arranged in parallel and spaced apart from each other. The pair of plate members constituting the support 230 is erected on a base plate 211 placed substantially horizontally with the front surfaces thereof being spaced apart from each other in parallel. Here, between the base plate 211 and the support 230, reinforcing ribs 212 are fixed to both ends, respectively.

  Each support body 230 is cut out in the thickness direction so as to form a predetermined curved line recessed downward from the upper end edge extending along the front surface, and in a flange shape along the cut surface (curved cross section). An expanding rail 213 is integrally attached, and the upper surface of the rail 213 is a support surface 240. The specific shape of the curved line representing the support surface 240 is the same as that of the support surface 40 and the support surface 140 described above, and redundant description is omitted here. The base plate 211, the support 230, the rail 213, and the like may be made of general structural rolled steel, metals such as copper and aluminum, polymer materials such as rubber and plastic, and other materials.

  As shown in FIG. 11, the rolling element 220 is formed in a circular cross section and rolls around its central axis, and is supported in a state of being spanned between the support surfaces 240 of the respective supports 230. Is done. Specifically, the rolling element 220 includes a pair of rotor main bodies 221 and 221, a rotating flange 222 disposed inside each rotor main body 221, and a cycle adjusting disk appropriately disposed inside each rotating flange 222. 223, a central shaft 224 for connecting these on both sides, and a magnetic damper 225 attached to the outside of each rotor body 221.

  The rotor body 221 is a part that rolls on the support surface 240, and its diameter is set in consideration of the natural frequency of the structure. The rotation flange 222 is a part for ensuring a stable track of the rotor body 221 on the support surface 240 and abuts against the edge of the rail 213 to prevent it from coming off. The period adjusting disk 223 is formed by laminating a plurality of disks on the same axis, and finely adjusts the entire period of the rolling element 220 by increasing or decreasing the number of disks. The central shaft 224 is a part for ensuring the weight of the entire rolling element 220 appropriately. The magnetic damper 225 is preferably configured so that a permanent magnet is embedded in the center of a synthetic resin disk having the same diameter as the rotor body 221.

  As shown in FIGS. 12 and 14, on the outer side of each support 230, there are non-ferrous metal plates 250 that are opposed to the magnetic dampers 225 on both end surfaces of the rolling element 220 with a gap, respectively. It is arranged in a state of being opposed to the body 230 in parallel. As a result, when the structure vibrates and the rolling element 220 rolls, the magnetic force lines coming out of the magnetic damper 225 move while being blocked by the non-ferrous metal plate 250. Is braked. This is the same as the relationship between the magnetic dampers 21 and 170 and the non-ferrous metal plates 50 and 150 described above.

  As shown in FIG. 14, for each unit of the vibration damping device 210, a floor / bed lid 260 is arranged on each support body 230. Here, each of the floor / bed covers 260 continuously forms a floor surface on the same plane. In this embodiment, the step and lid 260 is horizontally supported on each support 230 via the adjuster 261. However, the step and lid 260 is directly mounted on the upper edge of each support 230. You may comprise so that it may place.

Next, the operation of the vibration damping device 210 according to the third embodiment will be described.
According to the vibration damping device 210, as in the case of the first and second embodiments described above, when the support 230 vibrates in both directions, the support 230 is synchronized with the vibration of the support 230. The rolling element 220 supported on the supporting surface 240 rolls in the direction opposite to the shaking of the structure and absorbs the vibration energy of the supporting body 230.

  Thereby, the vibration of the structure which generate | occur | produces by a wind, an earthquake, etc. can be damped reliably. In particular, in the present embodiment, as shown in FIG. 14, a unit including one support body 230 and one rolling element 220 is used to reduce 1% of the effective mass (swaying weight) of the vibration control target vibration mode. By disposing more devices than the number of rolling elements to be satisfied, the vibration damping effect can be sufficiently enhanced.

  Similarly to the first and second embodiments, as the support surface 240 of the support body 230 moves away from the lowermost part of the center in both directions, the radius of curvature of the curve line that defines the curve section gradually decreases. Because of the shape, a constant frequency can always be maintained even when a large amplitude is generated by long-term vibration. Therefore, the vibration control performance can be sufficiently exhibited not only for vibrations having a small amplitude but also for vibrations having a large amplitude, and the structure can be effectively protected from vibrations caused by earthquakes and winds. .

  Further, as in the first and second embodiments, as the support surface 240 moves away from the lowermost part of the center in both directions, not only the curvature radius of the curved line gradually decreases, but also the curvature radius. The center of the shape is a shape that gradually descends on a vertical line passing through the lowermost portion of the support surface 240, so even if the structure is somewhat complicated, the size in the vertical direction can be suppressed as much as possible, and the structure can be made as compact as possible. . In the present embodiment, as described below, the entire height of the vibration damping device 210 is suppressed to about 30 cm from the viewpoint of effective use of the floor space.

  In addition, a step / comb lid 260 is disposed on each support 230, and each of the step / cap covers 260 forms a continuous floor surface on the same plane. Therefore, it is possible to use the damping device 210 on the same level as a general floor without being interfered with the installation space of the damping device 210, and the floor space can be used effectively. By reducing the size of the vibration damping device 210 in this way, it can be installed under the floor, and without reducing the floor space, vibrations caused by earthquakes, winds, etc. are suppressed, and people inside the structure Can be safely protected.

  FIG. 15 is an explanatory diagram showing a situation in which the vibration damping device according to the present embodiment is installed in a slender high-rise building B having a height of about 10 floors as an example of a structure. The figure (a) is a front view which shows typically the high-rise building B, and the figure (b) is a front view which shows the attachment position of a damping device. The figure (c) is explanatory drawing which shows the primary mode (vibration direction; front-back) in the high-rise building B, The figure (d) shows the secondary mode (vibration direction; left-right) in the high-rise building B. It is explanatory drawing.

  As shown in FIG. 15 (b), the vibration damping device 110 according to the second embodiment is installed as a vibration damping device on the roof of the high-rise building B in correspondence with the primary mode of the high-rise building B. Further, in response to the secondary mode of the high-rise building B, the vibration damping device 210 according to the third embodiment is installed as a vibration damping device on the intermediate floor of the high-rise building B. Here, the vibration control device 110 on the roof is set to a natural frequency that is substantially equal to the natural frequency of the primary mode, and the vibration control device 210 on the intermediate floor is set to a natural frequency that is approximately equal to the natural frequency of the secondary mode. Has been.

  By installing such a vibration control device, the vibration control device 110 mainly exhibits a vibration suppression function for the vibration of the primary mode of the high-rise building B, and the secondary mode of the high-rise building B. Therefore, the vibration damping device 210 mainly exhibits a vibration damping function. Therefore, the high-rise building B is reliably and effectively damped against vibrations in both the primary mode and the secondary mode.

  FIG. 16 is an explanatory diagram showing an example of a curve line that defines a curved section of each support surface 40, 140, 240 in the vibration damping devices 10, 110, 210 according to the first to third embodiments described above. is there. FIG. 17 is an explanatory diagram showing coefficients of the calculation method for obtaining the curved line shown in FIG. Hereinafter, the vibration damping device 10 will be described as a representative.

  As shown in FIG. 16, when the conventional rolling type vibration damping device (TRMD) is designed with an arcuate curved line A having a constant curvature radius, the diameter of the outer support and the rolling element 20 is determined. The difference increases. Thus, if the rolling element 20 becomes smaller and the outer size of the device becomes larger, it becomes impractical. In addition, since the radius of curvature is constant, as the swaying width increases, the swaying becomes slow and does not match the vibration cycle of the structure.

  Therefore, in the vibration damping device 10, the curvature radius of the curved line 40 'gradually increases as the curved line 40' that defines the curved cross section of the support surface 40 moves away from the lowermost part of the center in both directions as described above. While shortening, it set to the shape where the center of this curvature radius descend | falls gradually on the vertical line which passes through the said lowest part. As a result, it is possible to greatly reduce the size and maintain a constant frequency even when a large amplitude is generated by long-term vibration.

In order to obtain the natural period in the vibration damping device 10 set to such a curved line 40 ', for example, the following equation can be used.

  That is, in such a calculation method, Te is a natural period. Referring to the symbols in the free object diagram of the rolling element shown in FIG. 17, k = R−r, g is the gravitational acceleration, and θmax is the maximum deflection angle. A cylindrical body is assumed as the rotator. Here, assuming that Te is constant, k = R−r curvature can be obtained with respect to the maximum deflection angle θmax by solving the equation (1) for k.

A curved line 40 ′ shown in FIG. 16 is obtained by changing the value of θmax to obtain the curvature and connecting them to form a curve. Here, in FIG. 17, m _t is the mass of the rolling element, θ is the deflection angle of the center of gravity of the rolling element, F is the frictional force received from the support surface, and N is the vertical drag. I is the moment of inertia of the rolling element, and β is the rotational angular acceleration of the rolling element calculated by the following equation (2). Further, as the attenuation of the device, taking into account the Coulomb friction damping and viscous damping at the contact surface between the rolling element and the support surface, there resultant force of the damping force as F _d.

  An endless continuous heart-shaped curve line calculated in this way may be formed as an annular surface of the support surface 40 as it is, but in the vibration damping device 10, a support capable of allowing the maximum amplitude of the rolling element 20. Since the surface 40 is sufficient, the upper surface of the heart-shaped annular surface is cut out to form the support surface 40. As a result, the vibration damping device 10 can be further reduced in size. In addition, since the curve line which embodies the specific support surface 40 is determined by the diameter and the vibration period of the rolling element 20, the width of the applicable vibration period is large, and the natural frequency of the structure can be easily and easily set. Can be matched.

  The embodiments of the present invention have been described above with reference to the drawings. However, the specific configuration is not limited to the above-described embodiments, and the present invention can be changed or added without departing from the scope of the present invention. Included in the invention. For example, as a safety measure, if the curvature of the support surface or rail is further changed at both ends, etc., so that the rolling element does not come off, or if the swing exceeds the allowable range, etc. It is preferable to add a rolling stop function or the like of the rotator under various circumstances as necessary.

1 is a front view showing a vibration damping device according to a first embodiment of the present invention. 1 is a plan view showing a vibration damping device according to a first embodiment of the present invention. It is a perspective view which mainly shows the support body of the vibration damping device which concerns on 2nd Embodiment of this invention. It is a perspective view which shows a pair of rolling element of the damping device which concerns on 2nd Embodiment of this invention, the trolley | bogie which connects and supports these, and a weight. It is a perspective view which shows the state which coat | covered the top of the trolley | bogie of the damping device which concerns on 2nd Embodiment of this invention with the mounting cover. It is a perspective view which shows the state which attached the magnetic damper to the mounting cover of the damping device which concerns on 2nd Embodiment of this invention. It is a perspective view showing the state where the vibration damping device concerning a 2nd embodiment of the present invention was provided with the nonferrous metal plate. It is a top view which shows the damping device which concerns on 2nd Embodiment of this invention. It is a front view which shows the vibration damping device which concerns on 2nd Embodiment of this invention. It is a perspective view which shows the support body and rolling element which comprise one unit of the damping device which concerns on 3rd Embodiment of this invention. It is a perspective view which decomposes | disassembles and shows the rolling element of the damping device which concerns on 3rd Embodiment of this invention. It is a top view which shows the support body and rolling element which comprise one unit of the damping device which concerns on 3rd Embodiment of this invention. It is a side view which shows the support body and rolling element which comprise one unit of the damping device which concerns on 3rd Embodiment of this invention. It is a perspective view which shows the installation state of the damping device which concerns on 3rd Embodiment of this invention. It is explanatory drawing which shows the slender high-rise building which has a height of about 10 floors as an example of a structure. It is explanatory drawing which shows an example of the curve line which prescribes | regulates a curved cross section. It is explanatory drawing which shows each count of the calculation method which calculates | requires a curved line. It is explanatory drawing which shows roughly the conventional various damping devices.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Damping device 20 ... Roller 21 ... Magnetic damper 30 ... Support body 40 ... Supporting surface 41 ... Bottom part 50 ... Nonferrous metal plate 110 ... Damping device 111 ... Base plate 112 ... Rib 113 ... Rail 120 ... Rolling Child 121 ... Roller body 122 ... Axle 123 ... Rotating flange 130 ... Support 140 ... Support surface 150 ... Nonferrous metal plate 160 ... Cargo 161 ... Weight 162 ... Mounting cover 170 ... Magnetic damper 171 ... Upper plate 210 ... Damping Device 211 ... Base plate 212 ... Rib 213 ... Rail 220 ... Roller 221 ... Rotor body 222 ... Rotating flange 223 ... Cycle adjusting disk 224 ... Central shaft 225 ... Magnetic damper 230 ... Support 240 ... Support surface 250 ... Nonferrous Metal plate 260 ... Lid for both floor and floor 261 ... Adjuster

Claims (4)

A rolling element and a support that supports the rolling element so that the rolling element can roll are provided, and in a state where the rolling element is installed in the structure, the structure is shaken by the rolling of the rolling element with respect to the support. In the damping device to suppress,
The support is formed in a curved cross section that is recessed downward with respect to a horizontal plane, and has a support surface for the rolling element to roll.
The radius of curvature of the curved line defining the curved cross section gradually decreases as the support surface moves away from the lowermost portion of the center thereof, and the center of the radius of curvature gradually descends on a vertical line passing through the lowermost portion. A vibration damping device characterized in that it is set in a shape to perform. The support body has the support surface recessed downward from the upper end edge extending along the front surface, and a pair of the front surfaces arranged in parallel with each other to form a pair,
2. The support according to claim 1, wherein the rolling elements are formed in a circular cross section between the support surfaces of the respective supports and roll around the central axis thereof. Damping device. Two pairs of the support are arranged in a row in both sides,
The vibration control device according to claim 2, wherein the rolling elements in each of the groups are coupled to each other so as to roll synchronously via a weight. A horizontal plate that closes the upper opening of the support surface is arranged on the upper end side of the support,
3. The vibration damping device according to claim 1, wherein a plurality of the support bodies are arranged side by side on an installation surface, and the horizontal plates on each support body are continuous on the same plane.

Images